WO2016052655A1 - Structure de support d'arbre d'entrée pour transmission à double embrayage - Google Patents

Structure de support d'arbre d'entrée pour transmission à double embrayage Download PDF

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Publication number
WO2016052655A1
WO2016052655A1 PCT/JP2015/077821 JP2015077821W WO2016052655A1 WO 2016052655 A1 WO2016052655 A1 WO 2016052655A1 JP 2015077821 W JP2015077821 W JP 2015077821W WO 2016052655 A1 WO2016052655 A1 WO 2016052655A1
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Prior art keywords
input shaft
gear
shaft
bearing
input
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Application number
PCT/JP2015/077821
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English (en)
Japanese (ja)
Inventor
浩平 明石
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いすゞ自動車株式会社
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Filing date
Publication date
Application filed by いすゞ自動車株式会社 filed Critical いすゞ自動車株式会社
Publication of WO2016052655A1 publication Critical patent/WO2016052655A1/fr

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    • 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
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H57/021—Shaft support structures, e.g. partition walls, bearing eyes, casing walls or covers with bearings

Definitions

  • the present invention relates to an input shaft support structure for a dual clutch transmission.
  • Patent Document 1 describes a double clutch transmission.
  • the double clutch transmission has two load switching clutches and two intermediate shafts.
  • One intermediate shaft (second intermediate shaft) is designed as a radially outer hollow shaft and the other intermediate shaft (first intermediate shaft). Is designed as a radially inner intermediate shaft.
  • the two intermediate shafts are arranged concentrically with each other and can be operatively connected to the input shaft via load switching clutches.
  • the first intermediate shaft can be operatively connected to a counter shaft parallel to the transmission output shaft via a first gear fixing portion, and the second intermediate shaft can be countered via a second gear fixing portion. Can be operably connected to the shaft.
  • the fourth taper roller bearing is attached in front of the fixed gear of the second gear fixing portion of the second intermediate shaft, and is supported by the bearing hole of the partition wall of the clutch housing of the gear box case.
  • the needle bearing and the third taper roller bearing are attached to an annular intermediate space between the two intermediate shafts to form a two-point support structure for the first intermediate shaft with respect to the second intermediate shaft.
  • the second intermediate shaft (input shaft) is provided with a bearing hole (partition wall) in a partition wall of the clutch housing via a fourth taper roller bearing ( Since the second intermediate shaft rotates to rotate the counter shaft, the gear reaction force of the fixed gear of the second gear fixing portion is changed to the clutch through the fourth taper roller bearing. Enter in the partition wall of the housing.
  • the first intermediate shaft (input shaft) is supported on the inner peripheral surface of the second intermediate shaft via a needle bearing and a third taper roller bearing. That is, since the first intermediate shaft is supported by the bearing hole of the partition wall of the clutch housing via the fourth taper roller bearing together with the second intermediate shaft, the first intermediate shaft rotates to rotate the counter shaft.
  • the gear reaction force of the fixed gear of the first gear fixing portion is also input to the partition wall of the clutch housing via the fourth taper roller bearing.
  • the gear reaction force of the fixed gears of both the first intermediate shaft and the second intermediate shaft is input to the fourth taper roller bearing, it is necessary to provide the fourth taper roller bearing having a large load allowance. .
  • an object of the present invention is to provide an input shaft support structure for a dual clutch transmission that can suppress a gear reaction force input to a bearing between the shaft insertion hole of the partition wall and the input shaft.
  • An input shaft support structure for a transmission of the type includes a housing, a partition wall, a first bearing, a first input shaft, a second input shaft, a second input shaft support portion, and a second bearing.
  • the partition wall has a first shaft insertion hole, is fixed to the housing, and an input side space in which the first clutch and the second clutch are arranged and an output side in which the first gear and the second gear are arranged in the housing Partition into space.
  • the first bearing is fixed to the first shaft insertion hole.
  • the first input shaft has a cylindrical shape that is rotatably supported by the first bearing through the first shaft insertion hole, and the first gear is fixed.
  • the second input shaft is coaxial with the first input shaft, is inserted through the inner diameter portion of the first input shaft, is rotatably supported by the first input shaft, and the second gear is fixed.
  • the second input shaft support portion has a second shaft insertion hole, is disposed between the first gear and the second gear in the output side space, and is fixed to the housing.
  • the second bearing is fixed to the second shaft insertion hole.
  • the second input shaft is rotatably supported by the second bearing through the second shaft insertion hole.
  • the second bearing is fixed to the second shaft insertion hole of the second input shaft support portion fixed to the housing, and the second input shaft passes through the second shaft insertion hole and is freely rotatable to the second bearing. Supported. That is, the second input shaft is supported by the housing via the second input shaft support portion on the output side (second gear side) from the partition wall. For this reason, it is possible to increase the support rigidity of the second input shaft as compared with the case where the second input shaft is supported only on the partition wall side (first bearing side), and the occurrence of bending when the second input shaft rotates. Can be suppressed.
  • the second input shaft is supported by the partition wall through the first bearing together with the first input shaft. Further, the output side (first gear side) of the second input shaft is supported by a second input shaft support portion fixed to the housing. For this reason, the gear reaction force of the second gear when the second input shaft rotates and the second gear rotates another gear is caused by the housing side via the second input shaft support portion and the first bearing. Input to the partition wall side. Therefore, the gear reaction force input to the first bearing can be suppressed by the amount that the gear reaction force is input to the housing side via the second input shaft support portion, and the allowable load of the first bearing can be reduced. it can.
  • first bearing is fixed to the first shaft insertion hole of the partition wall, by arranging the first gear of the first input shaft in the vicinity of the partition wall, in the vicinity of the first gear of the first input shaft. Can be supported by the first bearing.
  • second bearing is fixed to the second shaft insertion hole of the second input shaft support portion disposed between the first gear and the second gear, the second bearing is located in the vicinity of the first gear of the first input shaft. By disposing the second bearing and disposing the second gear of the second input shaft in the vicinity of the second bearing, the vicinity of the first gear and the second gear can be supported by the second bearing.
  • the distance between each gear and each bearing is shortened, and the first input shaft And the support rigidity of a 2nd input shaft can be improved reliably.
  • the second input shaft support part may be formed separately from the housing and fixed to the partition wall.
  • the second input shaft support portion is formed separately from the housing, the second input shaft support portion and the second bearing can be unitized. In this case, the assembling work can be facilitated by the unitized amount.
  • the housing structure is not complicated.
  • FIG. 5 is a cross-sectional view taken along line VV in FIG. 4.
  • FR indicates the front of the vehicle
  • UP indicates the upper side
  • the transmission 1 to which the input shaft support structure according to the present invention is applied is a dual clutch transmission that is connected to a dual clutch 2.
  • the dual clutch 2 includes a first clutch 3 and a second clutch 4, and can be connected to and disconnected from an output shaft of an engine (not shown).
  • a control device or the like not shown
  • the rotational force from the engine is transmitted to the transmission 1 via the one clutch. Communicated.
  • the transmission 1 has a housing 7 constituted by a clutch case 5 and a gear case 6. Inside the housing 7, as will be described later, an outer input shaft (first input shaft) 14 and an inner input shaft (first input shaft). 2 input shaft) 15 and the output shaft 16 are arranged coaxially, and an intermediate shaft 17 is arranged in parallel with the outer input shaft 14, the inner input shaft 15, and the output shaft 16. As will be described later, each of the shafts 14 to 17 is provided with a gear, and each gear forms a plurality of gear trains 18 to 23.
  • the clutch case 5 is formed in a bottomed cylindrical shape that opens forward, and a clutch housing space (input side space) 8 is defined inside.
  • An input shaft insertion hole (first shaft insertion hole) 10 penetrating in the front-rear direction is formed in the rear wall portion (partition wall) 9 of the rear end of the clutch case 5.
  • the front end side of the clutch case 5 is connected to the engine side.
  • the first clutch 3 and the second clutch 4 are disposed in the clutch housing space 8.
  • the rear wall portion 9 of the clutch case 5 is fixed to the clutch case 5 by being integrally formed with the clutch case 5, the present invention is not limited to this.
  • the separate rear wall 9 may be fixed to a substantially cylindrical tubular body extending in the front-rear direction.
  • the gear case 6 is formed in a bottomed cylindrical shape that opens forward, and a gear housing space (output-side space) 11 is defined therein.
  • the rear wall portion 12 of the rear end of the gear case 6 is formed with an output shaft insertion hole 13 that is arranged coaxially with the shaft insertion hole 10 of the rear wall portion 9 of the clutch case 5 and penetrates in the front-rear direction.
  • the front end portion of the gear case 6 is fixed to the peripheral edge portion of the rear wall portion 9 of the clutch case 5.
  • the outer input shaft 14 is formed in a substantially cylindrical shape, is inserted through the input shaft insertion hole 10 in the rear wall portion 9 of the clutch case 5, and is inserted through a bearing (first bearing) 24.
  • the clutch case 5 is rotatably supported by the rear wall portion 9.
  • the bearing 24 is disposed between the outer peripheral surface of the outer input shaft 14 and the inner peripheral surface of the input shaft insertion hole 10 and is fixed to the inner peripheral surface of the input shaft insertion hole 10.
  • a front end portion of the outer input shaft 14 is fixed to the first clutch 3. That is, when the first clutch 3 is connected to the output shaft of the engine, the rotational force from the engine is transmitted to the outer input shaft 14 and input to the transmission 1.
  • a first input gear (first gear) 26 is fixed to the rear end portion of the outer input shaft 14. The first input gear 26 is disposed in the vicinity of the rear wall portion 9 of the clutch case 5 in the gear housing space 11.
  • the inner input shaft 15 is formed to be slightly smaller in diameter than the inner diameter portion 25 of the outer input shaft 14 and passes through the inner diameter portion 25 of the outer input shaft 14, and radially outward from the rear end of the insertion portion 27.
  • the shoulder portion 28 that extends and the tubular portion 29 that extends rearward from the peripheral edge portion of the shoulder portion 28 are integrally formed.
  • the insertion portion 27 is connected to the outer input shaft 14 via a needle bearing 30 that is disposed between the inner peripheral surface of the outer input shaft 14 that defines the inner diameter portion 25 of the outer input shaft 14 and the outer peripheral surface of the insertion portion 27. It is coaxially supported rotatably on the outer input shaft 14.
  • the distal end portion of the insertion portion 27 is fixed with respect to the second clutch 4.
  • the shoulder 28 has a front surface 32 that faces the rear end surface 31 of the outer input shaft 14 and is disposed in the vicinity of the rear end of the outer input shaft 14.
  • the cylindrical part 29 includes a supported part 33 extending rearward from the shoulder part 28, a protruding part 55 protruding radially outward from the rear end of the supported part 33, and a second input fixed to the rear of the protruding part 55.
  • a gear (second gear) 34 and a rear-end output shaft connecting portion 35 are provided.
  • the insertion portion 27 of the inner input shaft 15 With the insertion portion 27 of the inner input shaft 15 inserted through the inner diameter portion 25 of the outer input shaft 14, the insertion portion 27 is rotatable to the outer input shaft 14 via the needle bearing 30 of the inner diameter portion 25 of the outer input shaft 14.
  • the protruding portion 55 and the cylindrical portion 29 are supported behind the outer input shaft 14, and the cylindrical portion 29 is supported by the rear wall portion 9 of the clutch case 5 via a bearing holder 36 described later.
  • the bearing holder 36 is a substantially cylindrical body through which an input shaft insertion hole (second shaft insertion hole) 40 penetrates in the front-rear direction, and the rear wall portion 9 ( 2), and a body portion 38 extending rearward from the rear surface of the flange portion 37, and a shaft support portion (second input shaft support portion) 39 behind the body portion 38.
  • the flange portion 37 is formed in a substantially donut plate shape centered on the axis of the input shaft insertion hole 40, and is centered on an axis extending in parallel with the axis of the input shaft insertion hole 40 (a central axis of the intermediate shaft 17 described later).
  • An arcuate cutout 41 is provided.
  • a locking portion 45 that extends in the circumferential direction along the front end opening 44 of the input shaft insertion hole 40 and protrudes forward is formed on the front surface of the flange portion 37.
  • the outer diameter of the locking portion 45 is slightly smaller than the inner diameter of the rear end of the input shaft insertion hole 10 (see FIG. 2) of the clutch case 5.
  • the flange portion 37 is formed with a plurality of bolt holes 59 (in this embodiment, 10 locations) that are arranged at predetermined intervals in the circumferential direction and penetrate in the front-rear direction.
  • the body portion 38 is a substantially cylindrical body centered on the axis of the input shaft insertion hole 40, and has an inner diameter slightly larger than the inner diameter of the flange portion 37.
  • the shaft support portion 39 is formed in an annular shape around the axis of the input shaft insertion hole 40.
  • the inner diameter of the shaft support portion 39 (the inner diameter of the rear end portion of the input shaft insertion hole 40) is formed slightly larger than the inner diameter of the body portion 38, and the outer diameter of the shaft support portion 39 is outside the body portion 38. The diameter is slightly larger than the diameter.
  • an accommodation groove 43 that fits with the snap ring 47 (see FIG. 3) is formed in the circumferential direction.
  • a bearing 48 is fixed in advance to the shaft support portion 39 of the bearing holder 36, and the bearing holder 36 and the bearing 48 are unitized.
  • the bearing 48 includes an inner ring 49, an outer ring 50 arranged radially away from the outer peripheral surface of the inner ring 49, and a plurality of balls 51 (two in the figure) arranged between the inner ring 49 and the outer ring 50. Is a ball bearing.
  • grooves having an arcuate cross section for supporting the ball 51 are formed along the circumferential direction.
  • the outer peripheral surface of the outer ring 50 is in contact with the inner peripheral surface 52 of the shaft support portion 39 of the bearing holder 36, and the inner peripheral surface 53 of the body portion 38 of the bearing holder 36 and the inner peripheral surface 52 of the shaft support portion 39.
  • the shaft support part 39 of the bearing holder 36 is accommodated inside.
  • An accommodation groove 54 for accommodating the snap ring 47 is formed in the circumferential direction on the outer peripheral surface of the outer ring 50 of the bearing 48, and the accommodation groove 54 is in a state in which the bearing 48 is accommodated inside the shaft support portion 39 of the bearing holder 36.
  • the snap ring 47 is a C-shaped snap ring that is accommodated in the accommodation groove 54 of the bearing 48 and can be expanded and contracted.
  • the bearing 48 is fixed to the bearing holder 36, the bearing 48 is inserted into the shaft support portion 39 of the bearing holder 36 with the snap ring 47 received in the receiving groove 54 of the bearing 48 and reduced in diameter.
  • the outer peripheral surface of the snap ring 47 is caused to return to the original shape of the snap ring 47, and the inner peripheral surface 52 of the shaft support part 39 of the bearing holder 36. Abut.
  • the outer diameter of the supported portion 33 of the cylindrical portion 29 of the inner input shaft 15 is slightly smaller than the inner diameter of the bearing 48.
  • the inner input shaft 15 is inserted into the input shaft insertion hole 40 of the bearing holder 36 from the rear.
  • An inner diameter groove 57 is formed in the circumferential direction on the outer peripheral surface of the supported portion 33 of the inner input shaft 15, and the inner diameter groove 57 is a bearing in a state where the protruding portion 55 of the inner input shaft 15 contacts the rear end of the bearing 48. 48 is positioned slightly forward.
  • the bearing holder 36 inserts the insertion portion 27 of the inner input shaft 15 into the inner diameter portion 25 of the outer input shaft 14, and inserts the locking portion 45 of the flange portion 37 into the input shaft insertion hole 10 of the clutch case 5.
  • the 36 gear openings 42 are opened downward, and are fixed to the rear wall portion 9 of the clutch case 5 by a plurality of bolts 58 (only one is shown in the figure).
  • the inner input shaft 15 is rotatably supported by the needle bearing 30 and the bearing 48.
  • the locking portion 45 of the flange portion 37 is inserted and locked in the input shaft insertion hole 10 of the clutch case 5 and restricts the movement of the bearing holder 36 in the direction intersecting the shaft.
  • the first input gear 26 of the outer input shaft 14 is near the rear of the rear wall portion 9 of the clutch case 5 and the input shaft of the bearing holder 36.
  • the shaft support portion 39 of the bearing holder 36 is disposed in the vicinity of the rear of the first input gear 26 of the outer input shaft 14 and is disposed in the insertion hole 40 (see FIG. 4).
  • 34 is arranged in the vicinity of the rear of the shaft support 39 of the bearing holder 36.
  • the shaft support portion 39 of the bearing holder 36 includes the first input gear 26 at the rear end of the outer input shaft 14 and the inner input shaft 15 adjacent to the first input gear 26 in the axial direction behind the first input gear 26. It is arranged between the two input gears 34.
  • the output shaft 16 is arranged coaxially and in series with the inner input shaft 15 and the outer input shaft 14 behind the inner input shaft 15 in the gear housing space 11 of the gear case 6.
  • the rear end portion 60 of the output shaft 16 is inserted through the output shaft insertion hole 13 of the gear case 6 and protrudes rearward from the output shaft insertion hole 13, and is formed between the inner peripheral surface of the output shaft insertion hole 13 and the outer peripheral surface of the output shaft 16. It is rotatably supported by a bearing 62 between them.
  • the front end portion 61 of the output shaft 16 is inserted into the cylindrical portion 29 of the inner input shaft 15 from the rear, and is rotatably supported by a bearing 63 between the inner peripheral surface of the cylindrical portion 29 and the outer peripheral surface of the output shaft 16.
  • the output shaft 16 is provided so as to be rotatable with respect to the output shaft 16 in the order of the first output gear 64, the second output gear 65, and the third output gear 66 from the front side.
  • An output gear 67 is fixedly provided on the output shaft 16.
  • the first output gear 64, the second output gear 65, and the third output gear 66 can be connected to and disconnected from the output shaft 16 by two synchromesh mechanisms 68 and 69 provided in the gear housing space 11 of the gear case 6. ing.
  • a claw of a synchronizer (not shown) fixed to the output shaft 16 and a claw of a synchro cone (not shown) pressed into the side surfaces of the output gears 64 to 66 are engaged.
  • the output shaft 16 and the output gears 64 to 66 are fixed by the engagement of these claws, and the rotational force from the engine is transmitted to the output shaft 16.
  • the intermediate shaft 17 is disposed in the gear housing space 11 of the gear case 6 in parallel with the inner input shaft 15, the outer input shaft 14, and the output shaft 16, and below the inner input shaft 15, the outer input shaft 14, and the output shaft 16. Be placed.
  • the intermediate shaft 17 is rotatably supported by the rear wall portion 9 and the gear case 6 of the clutch case 5.
  • the intermediate shaft 17 is fixed to the intermediate shaft 17 in the order of the first intermediate gear 70, the second intermediate gear 71, the third intermediate gear 72, the fourth intermediate gear 73, and the fifth intermediate gear 74 from the front side.
  • a sixth intermediate gear 75 is provided behind the fifth intermediate gear 74 so as to be rotatable with respect to the intermediate shaft 17.
  • the sixth intermediate gear 75 can be connected to and disconnected from the intermediate shaft 17 by a synchromesh mechanism 76 at the rear end of the intermediate shaft 17.
  • a claw of a synchronizer (not shown) that is fixed to the intermediate shaft 17
  • a claw of a synchro cone (not shown) that is press-fitted into the side surface of the sixth intermediate gear 75 can be engaged and disengaged.
  • the intermediate shaft 17 and the sixth intermediate gear 75 are fixed by the engagement of these claws, and the rotational force from the engine is transmitted to the sixth intermediate gear 75.
  • Part of the first intermediate gear 70 is inserted into the input shaft insertion hole 40 of the bearing holder 36 from the gear opening 42 of the bearing holder 36 and meshed with the first input gear 26 of the outer input shaft 14.
  • the second intermediate gear 71 is engaged with the second input gear 34 of the inner input shaft 15 in the vicinity of the rear of the shaft support portion 39 of the bearing holder 36.
  • the plurality of gear trains 18 to 23 include the first input gear 26 of the outer input shaft 14, the second input gear 34 of the inner input shaft 15, the output gears 64 to 67 of the output shaft 16, and the intermediate shaft 17. It is configured by a combination with gears 70-75.
  • the first input gear 26 of the outer input shaft 14 and the first intermediate gear 70 of the intermediate shaft 17 constitute a first reduction gear train 18.
  • the second input gear 34 and the second intermediate gear 71 of the inner input shaft 15 constitute a second reduction gear train 19.
  • the first output gear 64 and the third intermediate gear 72 constitute the third speed fourth speed gear train 20.
  • the second output gear 65 and the fourth intermediate gear 73 constitute a first-speed second-speed gear train 21.
  • the third output gear 66, the fifth intermediate gear 74, and the idler gear 77 constitute the reverse gear train 22.
  • the fourth output shaft 67 and the sixth intermediate gear 75 constitute a seventh speed eighth gear train 23.
  • the first output gear 64 and the output shaft 16 are connected by the synchromesh mechanism 68, and the first output gear 64 and the output shaft 16 are transmitted from the intermediate shaft 17 to the output shaft 16 through the third and fourth gear train 20.
  • the clutch 3 is connected to the engine output shaft, the third speed is obtained, and when the second clutch 4 is connected to the engine output shaft, the fourth speed is obtained.
  • shifting up from the 2nd speed to the 3rd speed the connection between the second output gear 65 and the output shaft 16 by the synchromesh mechanism 69 is disconnected, and the first output gear 64 and the output shaft are connected by the synchromesh mechanism 68. 16 is connected.
  • the fifth speed is achieved. If it is connected to the output shaft, it will be 6-speed.
  • the rotational force from the engine is transmitted from the outer input shaft 14 to the intermediate shaft 17 via the first reduction gear train 18 and from the intermediate shaft 17 to the output shaft 16 via the second reduction gear train 19. Is done.
  • the rotational force from the engine is directly transmitted from the inner input shaft 15 to the output shaft 16 without the intermediate shaft 17.
  • the sixth intermediate gear 75 and the intermediate shaft 17 are connected by the synchromesh mechanism 76, and the rotational force from the engine is transmitted from the intermediate shaft 17 to the output shaft 16 via the seventh and eighth gear train 23.
  • the speed is 7th
  • the second clutch 4 is connected to the engine output shaft
  • the speed is 8th.
  • a reverse gear is achieved.
  • the rotational force from the engine is the intermediate shaft through either the first input gear 26 of the outer input shaft 14 or the second input gear 34 of the inner input shaft 15 at all gear speeds except the sixth speed. 17 and transmitted to the output shaft 16.
  • the gear reaction force of the first input gear 26 when the rotational force from the engine is transmitted to the output shaft 16 side via the first input gear 26 of the outer input shaft 14 is applied to the rear of the clutch case 5 via the bearing 24. Input to the wall 9 (housing 7 side).
  • the gear reaction force of the second input gear 34 when the rotational force from the engine is transmitted to the output shaft 16 side via the second input gear 34 of the inner input shaft 15 is the needle bearing on the insertion portion 27 side. 30 to the outer input shaft 14 and input from the outer input shaft 14 to the housing 7 side via the bearing 24, and on the cylindrical portion 29 side, the shaft support portion 39 of the bearing holder 36 via the bearing 48.
  • the inner input shaft 15 is supported by the housing 7 via the outer input shaft 14 on the insertion portion 27 side, and via the bearing holder 36 on the cylindrical portion 29 side. It is supported by the housing 7. That is, since the inner input shaft 15 is supported by the housing 7 at two positions spaced apart in the axial direction, for example, the support rigidity of the inner input shaft 15 is higher than that supported by the housing 7 only on the insertion portion 27 side. This increases and the occurrence of bending when the inner input shaft 15 rotates is suppressed.
  • the gear reaction force of the second input gear 34 is related to the insertion portion 27 side and the cylindrical portion. Input to the housing 7 side from two paths with the 29 side.
  • the gear reaction force input to the bearing 24 on the insertion portion 27 side is suppressed by the amount that the gear reaction force of the second input gear 34 is input to the housing 7 side via the bearing holder 36 on the cylindrical portion 29 side. Therefore, the allowable load of the bearing 24 can be kept small.
  • the first input gear 26 of the outer input shaft 14 is arranged in the vicinity of the rear of the rear wall portion 9 of the clutch case 5, the vicinity of the first input gear 26 of the outer input shaft 14 is the input shaft of the clutch case 5. It is supported by the bearing 24 of the insertion hole 10. Further, the shaft support portion 39 of the bearing holder 36 is disposed in the vicinity of the rear of the first input gear 26 of the outer input shaft 14, and the second input gear 34 of the inner input shaft 15 is connected to the shaft support portion 39 of the bearing holder 36. Since it is arranged in the vicinity of the rear, the vicinity of the rear of the first input gear 26 of the outer input shaft 14 and the vicinity of the front of the second input gear 34 of the inner input shaft 15 are supported by the bearing 48 of the bearing holder 36.
  • the bearing 24, the first input gear 26, the bearing 48, and the second input gear 34 are disposed within a short axial range, and the first input gear 26 and the second input gear 34 are adjacent to each other. Therefore, the support rigidity of the inner input shaft 15 and the outer input shaft 14 is high.
  • the assembly work of the transmission 1 is facilitated by the amount that the bearing holder 36 and the bearing 48 are unitized.
  • the inner input shaft 15 is supported by a bearing holder 36 that is separate from the housing 7. That is, since the support part etc. for supporting the supported part 33 of the inner side input shaft 15 are not formed in the housing 7, the structure of the housing 7 is not complicated.
  • the housing 7 is constituted by two cases of the clutch case 5 and the gear case 6.
  • the present invention is not limited to this, and the clutch case 5 and the gear case 6 may be integrally formed. Alternatively, it may be constituted by three or more cases.
  • the rear wall portion 9 of the clutch case 5 partitions the interior of the housing 7 into the clutch housing space 8 and the gear housing space 11, the present invention is not limited to this. If the gear case 6 has a front wall portion, the front wall portion (partition wall) of the gear case 6 may partition the interior of the housing 7 into a clutch housing space 8 and a gear housing space 11.
  • the inside of the housing 7 is partitioned into the input side clutch housing space 8 and the output side gear housing space 11 by the rear wall portion 9 of the clutch case 5.
  • the space 11 may be further partitioned into two or more spaces, and the interior of the housing 7 may be partitioned into three or more spaces.
  • the inner input shaft 15 is supported by the bearing holder 36 separate from the housing 7.
  • the inner input shaft 15 is integrated with the housing 7 at the position of the supported portion 33 of the inner input shaft 15 along the axial direction.
  • a wall portion (second input shaft support portion) to be formed may be provided, an input shaft insertion hole (second shaft insertion hole) may be formed in the wall portion, and the inner input shaft 15 may be supported by the wall portion.
  • the support relationship between the output shaft 16 and the output gears 64 to 66, and the intermediate shaft 17 and the intermediate gears 70 is fixed or rotatable.
  • the support relationship with .about.75 is an example and is not limited to the above.
  • the arrangement of the plurality of gear trains 18 to 23 is an example, and is not limited to the above.
  • the first input gear 26 is fixed to the outer input shaft 14 and the second input gear 34 is fixed to the inner input shaft 15.
  • two or more input gears are connected to the outer input shaft 14. It may be fixed, or two or more input gears may be fixed to the inner input shaft 15.
  • the shaft support portion 39 of the bearing holder 36 includes an input gear on the rearmost side of the outer input shaft 14 and an input on the frontmost side of the inner input shaft 15 that is axially adjacent to the input gear behind the input gear. You may arrange

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

Abstract

Selon l'invention, un arbre d'entrée externe (14) est porté rotatif sur une partie paroi arrière (9) d'un carter d'embrayage (5) par l'intermédiaire d'un palier (24). Une partie d'introduction (23) d'un arbre d'entrée interne (15) est introduite dans une partie de diamètre interne (25) de l'arbre d'entrée externe (4), et la partie d'introduction est portée rotative, de façon concentrique par rapport à l'arbre d'entrée externe (14), sur l'arbre d'entrée externe (14), par l'intermédiaire d'un roulement à aiguilles (30). Une partie portée (33) de l'arbre d'entrée interne (15) est portée sur une partie de support d'arbre (39) d'un support de palier (36) par l'intermédiaire d'un palier (48). Une partie bride (37) du support de palier (36) est fixée entre la partie paroi arrière (9) du carter d'embrayage (5) par une pluralité de boulons (58).
PCT/JP2015/077821 2014-10-02 2015-09-30 Structure de support d'arbre d'entrée pour transmission à double embrayage WO2016052655A1 (fr)

Applications Claiming Priority (2)

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JP2014-204103 2014-10-02
JP2014204103A JP6429110B2 (ja) 2014-10-02 2014-10-02 デュアルクラッチ式変速機の入力軸支持構造

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JP2020139613A (ja) * 2019-03-01 2020-09-03 本田技研工業株式会社 出力シャフト支持構造及び出力シャフトの組立方法

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JP2000355225A (ja) * 1999-06-14 2000-12-26 Kanzaki Kokyukoki Mfg Co Ltd 作業車両のトランスミッション
JP2005003073A (ja) * 2003-06-11 2005-01-06 Nissan Motor Co Ltd 車両用変速機
JP2006077987A (ja) * 2004-09-08 2006-03-23 Zahnradfab Friedrichshafen Ag 副軸構造の変速機
JP2012159094A (ja) * 2011-01-28 2012-08-23 Isuzu Motors Ltd 変速機の回転軸支持構造
US20140171259A1 (en) * 2012-12-14 2014-06-19 Eaton Corporation Electric hybrid module for a dual clutch transmission

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2000355225A (ja) * 1999-06-14 2000-12-26 Kanzaki Kokyukoki Mfg Co Ltd 作業車両のトランスミッション
JP2005003073A (ja) * 2003-06-11 2005-01-06 Nissan Motor Co Ltd 車両用変速機
JP2006077987A (ja) * 2004-09-08 2006-03-23 Zahnradfab Friedrichshafen Ag 副軸構造の変速機
JP2012159094A (ja) * 2011-01-28 2012-08-23 Isuzu Motors Ltd 変速機の回転軸支持構造
US20140171259A1 (en) * 2012-12-14 2014-06-19 Eaton Corporation Electric hybrid module for a dual clutch transmission

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