WO1997013990A1 - Motor vehicle gearbox - Google Patents

Motor vehicle gearbox Download PDF

Info

Publication number
WO1997013990A1
WO1997013990A1 PCT/SE1996/001283 SE9601283W WO9713990A1 WO 1997013990 A1 WO1997013990 A1 WO 1997013990A1 SE 9601283 W SE9601283 W SE 9601283W WO 9713990 A1 WO9713990 A1 WO 9713990A1
Authority
WO
WIPO (PCT)
Prior art keywords
bearing
input shaft
gears
shaft
gear
Prior art date
Application number
PCT/SE1996/001283
Other languages
French (fr)
Inventor
Grzegorz Janiszewski
Original Assignee
Ab Volvo
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 Ab Volvo filed Critical Ab Volvo
Priority to AU73509/96A priority Critical patent/AU7350996A/en
Publication of WO1997013990A1 publication Critical patent/WO1997013990A1/en

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
    • 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
    • B60K17/02—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of clutch
    • 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
    • F16H2003/0931—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 each countershaft having an output gear meshing with a single common gear on 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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0052—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising six 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
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H57/023—Mounting or installation of gears or shafts in the gearboxes, e.g. methods or means for assembly

Definitions

  • the present invention relates to a motor vehicle gearbox, comprising a housing in which an input shaft is carried in a first bearing in a first housing end wall on the input side ofthe input shaft and in a second bearing in a second opposite housing end wall and at least one countershaft mounted in bearings in said end walls and having gears meshing with gears on the input shaft, at least one gear in each pair of intermeshing gears on said shafts being disengageable on its shaft.
  • gearboxes used in automobiles with transverse engines must be made short in order to make room for the entire drive unit. The more cylinders an engine has. the shorter the gearbox and clutch must be.
  • a known method of achieving a short five-speed gearbox for a transverse engine is to provide it with two countershafts instead of one.
  • the purpose of the present invention is to achieve a design in a gearbox of the type described by way of introduction which can be used either as an alternative to the design with two countershafts or as a supplement thereto, to permit, for example, the expansion of an existing short five-speed gearbox to a six-speed without having to increase the total length ofthe gearbox and clutch.
  • the invention is based on the idea of moving the first bearing farther into the gear ⁇ box housing and thus creating more space outside the end wall for the clutch dis- engaging mechanism so that it can be sunk into the end wall, thus making it possible to place the entire clutch arrangement closer to the gearbox. This makes it possible to shorten the entire gearbox - clutch installation.
  • a bearing-overlapping reversing gear meshes with a reversing gear which is mounted on a second countershaft and which is arranged so that it overlaps the first bearing of the input shaft.
  • gearbox housing which has a central housing portion 2 and front and rear end walls 3 and 4. respectively, screwed securely to the central housing portion 2.
  • a clutch housing 5 is cast in one piece with the forward end wall 3, which is made with a depression 6. which at its bottom portion 7 forms a seat for a taper roller bearing 8, which forms a bearing for an input shaft 9 on the input side.
  • a second taper roller bearing 10 seated in the opposite end wall 4 carries the opposite end ofthe input shaft 9.
  • six gears 11.12.13.1-t.l 5 and 16 are non-rotatably fixed for torque transmission in first, second, sixth, third, fourth and fifth gear (in said order) via gears 19.
  • 20. 21, 22, 23 and 24 rotatably mounted on a first and a second countershaft 17 and 18. respectively.
  • the rotatably mounted gears are engageable to the respective shafts by means of associated engaging and synchronizing devices
  • the countershafts 17 and 18 are mounted in taper roller bearinss 28. 29 and 30. 3 1 in the front and rear end walls 3 and 4. respectively.
  • the gear 19 for the first gear speed is non-rotatably joined to a first reverse gear 32 meshing with a second reverse sear 33. which is rotatablv mounted on the second countershaft 18 and can be engaged thereto by means of an engaging and synchro ⁇ nizing device 34.
  • the placement ofthe bearing 8 in the bottom ofthe depression 6 will mean that the bearing 8 overlaps the gears 32. 33. so that the end surface 35 ofthe inner ring of the bearing 8 is almost co-planar with the inner surface 36 of the gear 32.
  • a disengaging device for a clutch 41 is mounted.
  • the disengaging device 40 comprises a first sleeve 42 arranged concentrically with the input shaft 9, and a second sleeve 43 arranged concentrically therewith.
  • the sieeves define an annular cylinder space 44 for a ring piston 45, which abuts against a release bearing 46 slidable on sleeve 42.
  • the clutch 41 is of conventional type and comprises a cover 48 securely screwed to the engine flywheel 47.
  • the cover 48 supports a pressure plate 49 and a plate spring 50.
  • the release bearing 46 abuts against a central portion ofthe spring 50 and as it is moved to the right in the Figure, due to supply of pressure medium to the cylinder chamber 44. the pressure plate 49 is lifted from the disc 51 non-rotatably carried by the input shaft 9. thus releasing the clutch.
  • the depression 6 for the release arrangement 40 enables the clutch to be placed as close as is at all possible to the end wall 3 ofthe gearbox housing, i.e. the cover 48 has po ⁇ ions which lie immediately adjacent to those portions ofthe housing end wall 3 which form seats for the countershaft bearings 28 and 30.
  • the total axial extent ofthe transmission unit will be as short as possible. In practice this means that the described six-speed gearbox with associated clutch need not take up more space than the previously known five-speed version.
  • the complete transmission unit has a final drive, generally designated 52, the crown gear 53 of which engages two gears 54, 55 each non-rotatably joined to an individual countershaft 17 and 18, respective ⁇ ly.
  • the gears 54, 55 in the example shown are of equal size and partially overlap the bearing 8 and the release arrangement 40.

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)
  • General Details Of Gearings (AREA)

Abstract

Six-speed motor vehicle gearbox with two countershafts (17, 18) on which intermeshing reverse gears (32, 33) for reverse gear are rotatably mounted and engageable to the respective shaft by means of engaging sleeves (25, 34). The input shaft (9) is carried on the input side in a bearing (8) which is overlapped by the reverse gears. In a depression (6) in the end wall (3) of the gearbox housing on the outside of the housing, a hydraulic release cylinder (40) is arranged with a release bearing (46).

Description

Motor vehicle gearbox
The present invention relates to a motor vehicle gearbox, comprising a housing in which an input shaft is carried in a first bearing in a first housing end wall on the input side ofthe input shaft and in a second bearing in a second opposite housing end wall and at least one countershaft mounted in bearings in said end walls and having gears meshing with gears on the input shaft, at least one gear in each pair of intermeshing gears on said shafts being disengageable on its shaft.
It is a known fact that gearboxes used in automobiles with transverse engines must be made short in order to make room for the entire drive unit. The more cylinders an engine has. the shorter the gearbox and clutch must be. A known method of achieving a short five-speed gearbox for a transverse engine is to provide it with two countershafts instead of one.
The purpose of the present invention is to achieve a design in a gearbox of the type described by way of introduction which can be used either as an alternative to the design with two countershafts or as a supplement thereto, to permit, for example, the expansion of an existing short five-speed gearbox to a six-speed without having to increase the total length ofthe gearbox and clutch.
This is achieved according to the invention by virtue ofthe fact that a gear which is carried by one ofthe countershafts and which is arranged to transmit torque to the reverse shaft and the first bearing ofthe input shaft are disposed so that they overlap each other axially.
The invention is based on the idea of moving the first bearing farther into the gear¬ box housing and thus creating more space outside the end wall for the clutch dis- engaging mechanism so that it can be sunk into the end wall, thus making it possible to place the entire clutch arrangement closer to the gearbox. This makes it possible to shorten the entire gearbox - clutch installation.
In a preferred embodiment which constitutes a further development ofthe gearbox described in SE-A-8601247-3, a bearing-overlapping reversing gear meshes with a reversing gear which is mounted on a second countershaft and which is arranged so that it overlaps the first bearing of the input shaft.
By modifying the gearbox shown and described in said specification so that the intermeshing reverse gears are placed at the input side o the gearbox, the input bearing can be moved further into the gearbox housing since there is no gear on the input shaft in engagement with the reverse gears. This solution makes it possible to expand the known five-speed gearbox to a six-speed gearbox without requiring more total space for the engine and transmission.
The invention will be described in more detail below with reference to the examples shown in the accompanying drawing, where the Figure shows a longitudinal section through one embodiment o a gearbox according to the invention with a clutch device connected thereto.
1 in the Figure generally designates a gearbox housing, which has a central housing portion 2 and front and rear end walls 3 and 4. respectively, screwed securely to the central housing portion 2. A clutch housing 5 is cast in one piece with the forward end wall 3, which is made with a depression 6. which at its bottom portion 7 forms a seat for a taper roller bearing 8, which forms a bearing for an input shaft 9 on the input side. A second taper roller bearing 10 seated in the opposite end wall 4 carries the opposite end ofthe input shaft 9. To the input shaft 9. six gears 11.12.13.1-t.l 5 and 16 are non-rotatably fixed for torque transmission in first, second, sixth, third, fourth and fifth gear (in said order) via gears 19. 20. 21, 22, 23 and 24 rotatably mounted on a first and a second countershaft 17 and 18. respectively. The rotatably mounted gears are engageable to the respective shafts by means of associated engaging and synchronizing devices
25, 26 and 27.
The countershafts 17 and 18 are mounted in taper roller bearinss 28. 29 and 30. 3 1 in the front and rear end walls 3 and 4. respectively.
The gear 19 for the first gear speed is non-rotatably joined to a first reverse gear 32 meshing with a second reverse sear 33. which is rotatablv mounted on the second countershaft 18 and can be engaged thereto by means of an engaging and synchro¬ nizing device 34. As can be seen in the Figure, the placement ofthe bearing 8 in the bottom ofthe depression 6 will mean that the bearing 8 overlaps the gears 32. 33. so that the end surface 35 ofthe inner ring of the bearing 8 is almost co-planar with the inner surface 36 of the gear 32.
In the depression 6 on the outside ofthe bearing 8, a disengaging device, generally designated 40. for a clutch 41 is mounted. The disengaging device 40 comprises a first sleeve 42 arranged concentrically with the input shaft 9, and a second sleeve 43 arranged concentrically therewith. The sieeves define an annular cylinder space 44 for a ring piston 45, which abuts against a release bearing 46 slidable on sleeve 42. The clutch 41 is of conventional type and comprises a cover 48 securely screwed to the engine flywheel 47. The cover 48 supports a pressure plate 49 and a plate spring 50. The release bearing 46 abuts against a central portion ofthe spring 50 and as it is moved to the right in the Figure, due to supply of pressure medium to the cylinder chamber 44. the pressure plate 49 is lifted from the disc 51 non-rotatably carried by the input shaft 9. thus releasing the clutch. As can be seen in the Figure, the depression 6 for the release arrangement 40 enables the clutch to be placed as close as is at all possible to the end wall 3 ofthe gearbox housing, i.e. the cover 48 has poπions which lie immediately adjacent to those portions ofthe housing end wall 3 which form seats for the countershaft bearings 28 and 30. Thus the total axial extent ofthe transmission unit will be as short as possible. In practice this means that the described six-speed gearbox with associated clutch need not take up more space than the previously known five-speed version.
In addition to the above described components, the complete transmission unit has a final drive, generally designated 52, the crown gear 53 of which engages two gears 54, 55 each non-rotatably joined to an individual countershaft 17 and 18, respective¬ ly. The gears 54, 55 in the example shown are of equal size and partially overlap the bearing 8 and the release arrangement 40.

Claims

Claims
1. Motor vehicle gearbox, comprising a housing in which an input shaft is carried in a first bearing in a first housing end wall on the input side ofthe input shaft and in a second bearing in a second opposite housing end wall and at least one countershaft mounted in bearings in said end walls and having gears meshing with gears on the input shaft, at least one gear in each pair of intermeshing gears on said shafts being disengageable on its shaft, characterized in that a gear (32). which is carried bv the counter-shaft (17) and which is arranged to transmit torque to the reverse shaft, and the first bearing (8) of the input shaft (9) are disposed so that they overlap each other axially.
2. Gearbox according to Claim 1. characterized in that said bearing-overlapping reverse gear (32) meshes with a reverse gear (33) which is mounted on a second intermediate shaft ( 18) and which is also disposed so that it axially overlaps the first bearing (8) ofthe input shaft.
3. Gearbox according to Claim 1 or 2. characterized in that the first housing end wall (3) has a depression (6) which is formed concentrically with the input shaft (9) and receives an annular pressure medium actuated piston-cylinder device (40). through which there extends a portion of he input shaft protruding out ofthe housing, the piston (45) of said piston-cylinder device (40) cooperating with a release bearing (46).
4. Gearbox according to Claims 2 and 3. characterized in that the countershafts
(17,18) each have a gear (54,55) non-rotatably joined to the respective shaft, each of said gears being arranged to transmit torque from the respective countershaft to a final drive (52) and that said gears partially overlap axially both said first bearing (8) and the piston-cylinder device (40).
5. Gearbox according to Claim 3 or 4, characterized in that the input shaft (9) has six gears ( 1 1-16) meshing with gears ( 19-24) on the countershafts (17.18) for trans¬ mitting torque to the final drive (52) for driving forward at six different gear ratios.
PCT/SE1996/001283 1995-10-10 1996-10-09 Motor vehicle gearbox WO1997013990A1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AU73509/96A AU7350996A (en) 1995-10-10 1996-10-09 Motor vehicle gearbox

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
SE9503525A SE505129C2 (en) 1995-10-10 1995-10-10 Motor vehicle gearbox
SE9503525-9 1995-10-10

Publications (1)

Publication Number Publication Date
WO1997013990A1 true WO1997013990A1 (en) 1997-04-17

Family

ID=20399770

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/SE1996/001283 WO1997013990A1 (en) 1995-10-10 1996-10-09 Motor vehicle gearbox

Country Status (3)

Country Link
AU (1) AU7350996A (en)
SE (1) SE505129C2 (en)
WO (1) WO1997013990A1 (en)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2799252A1 (en) * 1999-10-01 2001-04-06 Renault Gearbox design for automotive vehicle, has a more compact and more standard design which is adaptable to a range of vehicles
US6513400B2 (en) 2000-03-30 2003-02-04 Aisin Ai Co., Ltd. Manual transmission
US6619150B2 (en) 2000-05-19 2003-09-16 Aisin Ai Co., Ltd. Manual transmission
EP1482208A3 (en) * 2003-05-24 2006-07-26 DaimlerChrysler AG Three shafts transmission

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0224407A1 (en) * 1985-10-25 1987-06-03 Regie Nationale Des Usines Renault Gear transmission with one input shaft and two counter shafts
US5385065A (en) * 1992-03-13 1995-01-31 Ford Motor Company Multispeed manual transmission for motor vehicles
EP0648958A2 (en) * 1993-10-06 1995-04-19 Ford-Werke Aktiengesellschaft Motor vehicle gear-box, particularly with low speed gear train
EP0675299A2 (en) * 1994-03-29 1995-10-04 Saturn Corporation Multi-axis countershaft power transmission

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0224407A1 (en) * 1985-10-25 1987-06-03 Regie Nationale Des Usines Renault Gear transmission with one input shaft and two counter shafts
US5385065A (en) * 1992-03-13 1995-01-31 Ford Motor Company Multispeed manual transmission for motor vehicles
EP0648958A2 (en) * 1993-10-06 1995-04-19 Ford-Werke Aktiengesellschaft Motor vehicle gear-box, particularly with low speed gear train
EP0675299A2 (en) * 1994-03-29 1995-10-04 Saturn Corporation Multi-axis countershaft power transmission

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2799252A1 (en) * 1999-10-01 2001-04-06 Renault Gearbox design for automotive vehicle, has a more compact and more standard design which is adaptable to a range of vehicles
US6513400B2 (en) 2000-03-30 2003-02-04 Aisin Ai Co., Ltd. Manual transmission
US6619150B2 (en) 2000-05-19 2003-09-16 Aisin Ai Co., Ltd. Manual transmission
DE10124401B4 (en) * 2000-05-19 2015-02-26 Aisin Ai Co., Ltd. Manual transmission
EP1482208A3 (en) * 2003-05-24 2006-07-26 DaimlerChrysler AG Three shafts transmission

Also Published As

Publication number Publication date
SE505129C2 (en) 1997-06-30
SE9503525L (en) 1997-04-11
AU7350996A (en) 1997-04-30
SE9503525D0 (en) 1995-10-10

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