WO2015188312A1 - 牵引驱动同步调速器及具有该调速器的多驱动轴变速箱 - Google Patents

牵引驱动同步调速器及具有该调速器的多驱动轴变速箱 Download PDF

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Publication number
WO2015188312A1
WO2015188312A1 PCT/CN2014/079579 CN2014079579W WO2015188312A1 WO 2015188312 A1 WO2015188312 A1 WO 2015188312A1 CN 2014079579 W CN2014079579 W CN 2014079579W WO 2015188312 A1 WO2015188312 A1 WO 2015188312A1
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WO
WIPO (PCT)
Prior art keywords
gear
shaft
governor
drive
group
Prior art date
Application number
PCT/CN2014/079579
Other languages
English (en)
French (fr)
Inventor
孙振台
Original Assignee
孙振台
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 孙振台 filed Critical 孙振台
Priority to US15/314,849 priority Critical patent/US9845842B2/en
Priority to PCT/CN2014/079579 priority patent/WO2015188312A1/zh
Publication of WO2015188312A1 publication Critical patent/WO2015188312A1/zh

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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
    • F16H3/12—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 with means for synchronisation not incorporated in the clutches
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D11/00—Clutches in which the members have interengaging parts
    • F16D11/08—Clutches in which the members have interengaging parts actuated by moving a non-rotating part axially
    • F16D11/10—Clutches in which the members have interengaging parts actuated by moving a non-rotating part axially with clutching members movable only axially
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D11/00—Clutches in which the members have interengaging parts
    • F16D11/14—Clutches in which the members have interengaging parts with clutching members movable only axially
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D23/00—Details of mechanically-actuated clutches not specific for one distinct type
    • F16D23/02—Arrangements for synchronisation, also for power-operated clutches
    • F16D23/04—Arrangements for synchronisation, also for power-operated clutches with an additional friction 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
    • F16H13/00—Gearing for conveying rotary motion with constant gear ratio by friction between rotary members
    • F16H13/06—Gearing for conveying rotary motion with constant gear ratio by friction between rotary members with members having orbital motion
    • 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
    • F16H3/006—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion power being selectively transmitted by either one of the parallel flow paths
    • 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
    • F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
    • F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
    • F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
    • F16H37/08—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
    • F16H37/0806—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with a plurality of driving or driven shafts

Definitions

  • This invention relates to a gearbox, and more particularly to a vehicular gearbox that utilizes a traction drive synchronous governor and is multi-shaft driven. Background technique
  • the prior art vehicle shifting devices mainly include: manual shifting, dual clutch self-hand shifting, automatic shifting, and stepless shifting; the structure of the manual shifting is simple, but the clutch and the shifting lever are frequently operated, and Frequent or improper operation of the clutch causes the clutch plate to wear; the double clutch shifts from the hand.
  • the dual clutch structure is complicated and difficult to repair, and the clutch piece is also provided. Wear condition; the automatic shifting structure is complicated, and the transmission efficiency is poor due to the non-direct transmission of the hydraulic torque converter and the inertial resistance of the planetary gear set; the stepless gearbox utilizes the friction between the steel belt or the roller.
  • the transmission in which the steel belt is driven, is limited to the steel belt strength, and can only be used for small vehicles.
  • the roller control mechanism is also quite complicated and difficult to maintain; therefore, the prior art shifting device has components that are easy to wear, Defects such as complex construction and poor efficiency.
  • the object of the present invention is to improve the defects of the components of the prior art transmission that are easy to wear, difficult to maintain, and inefficient, and at the same time, increase the number of gears of the transmission in a limited space, thereby providing a transmission.
  • the technical means adopted by the present invention is a traction drive synchronous governor connected to a drive shaft which is a power output, and has the following features: a shaft, an input member, an output member, a bracket, at least three roller sets and a tooth sleeve;
  • the input member is a gear
  • the gear has a perforation in the center and is recessed on one side a groove, the groove forms an inclined surface with the side surface, the gear is recessed toward the groove adjacent to the ring wall surface of the groove to form a ring seat, and the ring seat outer ring wall surface is provided with convex teeth;
  • the central perforation is sleeved on the shaft;
  • the tooth sleeve is a hollow ring body, and a side groove of the ring body is recessed to form a tooth groove, the tooth groove is a continuous wave shape and the peaks and troughs have the same radius, and the tooth sleeve is The ring wall surface is provided with a tooth groove
  • the traction drive synchronous speed controller wherein the roller set has a first disk body, a second disk body and a spring; the first disk body is a disk body, and the disk body is convexly formed at the center a cylindrical body; the second disk body is a disk body, the disk body protrudes from the center to form a cylinder, and a continuous hole is formed in the center of the cylinder; the cylindrical outer ring wall surface of the second disk body is sleeved with the spring a bearing disposed in the through hole of the bracket, the cylinder of the first disc body passes through the through hole of the second disc cylinder and is fixed to the second disc body, and the two ends of the spring abut against the bracket and the second disc Between the bodies, the second disc body is moved away from the bracket, and the first disc body abuts against the bracket.
  • the invention also provides a multi-drive shaft transmission with a traction drive synchronous governor, having a governor chamber and a shift gear chamber; the governor chamber is adjacent to an engine, and the governor chamber has a combination a driving gear of the input shaft of the engine and at least two governors; one end of the shaft of the governor is fixed on an inner wall surface of the governor chamber, and each shaft is arranged around the input shaft of the engine a parallel arrangement of equidistant distances, the drive gear meshes with an input member of the governor; the shift gear chamber has at least two drive groups, an output set and a reverse turn wheel set, the shift gear chamber being connected to the speed control
  • the drive unit has a shaft and at least three gears; the shaft is disposed on the shift gear chamber, the gear is disposed on the shaft; the drive group has a shaft, at least three gears and at least two a synchronizing device; the outer ring wall surface of the driving group forms a convex tooth, the shaft passes through the shifting gear chamber to the governor chamber, and is
  • the multi-drive shaft transmission wherein the governor chamber has three governors, respectively a first governor, a second governor and a third governor; the shift gear chamber has three drive groups, The first driving group, the second driving group and the third driving group are respectively connected to the first governor, the shaft of the second driving group is connected to the second governor, the third a shaft of the driving group is connected to the third governor; the output group has a first gear, a second gear, a third gear and a fourth gear, wherein the gears are sequentially disposed on the shaft of the output group; the first driving group
  • the setting on the shaft is reverse gear, first synchronizer, third gear, sixth gear, second synchronizer and nine gear;
  • the second drive set shaft is arranged in the first gear, a three-synchronizer, a fourth-speed gear, a seven-speed gear, a fourth synchronizer, and a ten-speed gear;
  • the third drive group is arranged in the second gear, the fifth synchronizer, the fifth gear, the eighth gear, a sixth synchron
  • the multi-drive shaft gearbox has an axle outside the gearbox, and has a differential; the differential has a driving gear and a driven gear, and the driving gear is disposed on the shaft of the output group
  • the driven gear is disposed on an axle outside the transmission, and the driving gear meshes with the driven gear, and the axle is arranged in parallel with the shaft of the output group.
  • the multi-drive shaft transmission has an axle outside the transmission, and is characterized by: having a differential; the differential has a driving gear and a driven gear, and the driving gear is disposed outside the transmission gear On the shaft of the output group, the driven gear is disposed on an axle outside the transmission, the driving gear meshes with the driven gear, and the axle is vertically aligned with the shaft of the output group.
  • the outer ring wall surface of the governor sleeve is recessed to form a groove for receiving the fork; the sleeve of the output member of the governor is recessed to form a recess The groove of the fork.
  • the traction drive synchronous governor wherein the continuous corrugated tooth groove of the tooth sleeve and the continuous corrugated convex tooth of the output member are made by: drawing a ring-shaped wavy line having the same radius of all peaks and troughs; A two-ring type wavy line is drawn from the ring-shaped wavy line to the opposite sides of the ring-shaped wavy line; the ring-shaped continuous wave-shaped gullet and the convex tooth are made based on the two newly drawn ring-shaped wavy lines; the ring type is continuous The intersection of all the planes of the corrugated tooth groove and the convex tooth is rounded with the same radius.
  • the traction drive synchronous speed controller wherein the roller group is assembled in the following manner: the outer side of the hollow cylinder of the second disk body is sleeved into the spring; the hollow cylinder of the second disk body is close to the power output side sleeve by the bracket a bearing inserted into the through hole of the bracket, the bearing needs to make the hollow cylinder of the second disc body move axially back and forth in the bearing; the cylinder of the first disc body is nested into the first side of the bracket a hollow cylinder of the two-disc body; a cylindrical protrusion of the first disc body is provided with a buckle at the other side of the second disc body.
  • the utility model has the beneficial effects that: by the parallel arrangement of the unequal wheelbases around the output shafts of the drive shafts in the gearbox, the gear position of the gearbox is increased without increasing the length of the gearbox, and at the same time, the shifting speed
  • the governor of the roller set containing the planetary arrangement is used in the box, and the output member of the governor is pushed against the roller set to move axially to contact the input member of the governor, thereby driving the input power of the engine.
  • the gears are transmitted directly to the output gear of the gearbox to avoid problems with prior art transmission inefficiencies or clutch wear due to frequent or improper operation.
  • FIG. 1 is a schematic view of the present invention when it is placed on a transverse engine
  • FIG. 2 is a schematic view showing a gear arrangement of each shaft when the engine is placed transversely according to the present invention
  • Figure 3 is a cross-sectional view of the traction drive synchronous speed governor of the present invention.
  • Figure 4 is a cross-sectional view taken along line A-A of Figure 3 of the present invention.
  • Figure 5 is a first state diagram of the operation of the traction drive synchronous governor of the present invention.
  • Figure 6 is a second state diagram of the operation of the traction drive synchronous governor of the present invention.
  • Figure 7 is a third state diagram of the operation of the traction drive synchronous governor of the present invention.
  • Figure 8 is a first state diagram of an embodiment of the present invention.
  • Figure 9 is a second state diagram of an embodiment of the present invention.
  • Figure 10 is a view showing another embodiment of the present invention.
  • Figure 11 is a schematic view of the present invention when it is disposed in a vertical engine.
  • FIG. 1 The specific embodiment shown in FIG. 1 is an embodiment of a multi-drive shaft transmission having a traction drive synchronous governor disposed in a transverse engine having a governor chamber 20 and a shifting gear chamber 30. .
  • one end of the governor chamber 20 is adjacent to an engine 10 , and the governor chamber 20 has a driving gear 11 coupled to the input shaft 110 of the engine 10 , a first governor 21 , a second governor 22 and a third governor 23; the drive gear 11 simultaneously meshes with the first governor 21, the second governor 22 and the third governor 23, the first governor 21
  • the first shaft 210 is fixed to the inner wall surface of the governor chamber 20, and the first governor 21, the second governor 22 and the third governor 23 are fixed. The specific structure is described in detail later; the first shaft 210, the second shaft 220, and the third shaft 230 are arranged in an equidistant parallel arrangement around the input shaft 110; the power of the engine 10 is transmitted to the drive gear 11 via the drive gear 11.
  • the shift gear chamber 30 has a first drive group 31 , a second drive group 32 , a third drive group 33 , an output group 34 , a reverse idler gear set 35 , and a differential gear 36 .
  • the chamber 30 is connected to one end of the governor chamber 20 away from the engine 10; the number of the drive groups corresponds to the number of the governor, which is illustrated in the present embodiment by three drive groups.
  • the first driving group 31 has a first driving shaft 310 , a reverse gear 311 , a third gear 312 , a sixth gear 313 , a nine gear 314 , a first synchronizer 315 , and a second synchronizer 316;
  • the first drive shaft 310 is disposed on the front and rear ends of the shift gear chamber 30, one end of which is inserted into the governor chamber 20, the reverse gear 311,
  • the third gear 312, the sixth gear 313 and the nine gear 314 are sequentially disposed on the first drive shaft 310 by the front end of the shift gear chamber 30.
  • the first synchronizer 315 is mounted on the reverse gear 311 and the Between the third gears 312, the second synchronizer 316 is disposed between the sixth gear 313 and the nine gear 314; the tang gear side of the reverse gear 311 and the third gear 312 faces the first synchronizer 315, the sixth gear 313 and the canine side of the nine gear 314 face the second synchronizer 316, each of the synchronizers has a tooth sleeve;
  • the number of gears and synchronizers required for the drive group is at least three and at least two, respectively, which is illustrated by four gears and two synchronizers in this embodiment.
  • the structure of the second driving group 32 and the third driving group 33 is the same as that of the first driving group 31 .
  • the difference is that the second driving shaft 320 is connected to the first driving gear 320 .
  • a third synchronizer 325, a fourth gear 322, a seventh gear 323, a fourth synchronizer 326, and a tenth gear 324, and connected to the third drive shaft 330 are a second gear 331 , a fifth synchronizer 335 , and five a gear 332, an eighth gear 333, a sixth synchronizer 336, and an eleven gear 334;
  • the first drive shaft 310, the second drive shaft 320, and the third drive shaft 330 are respectively coupled to the first of the governor chambers 20
  • the shaft 210, the second shaft 220, and the third shaft 230 are coaxially disposed opposite to each other, and are coupled to the first governor 21, the second governor 22, and the third governor 23.
  • the output set 34 has an output shaft 340, a first gear 341, a second gear 342, a third gear 343, and a fourth gear 344.
  • the output shaft 340 is provided.
  • the first gear 341, the second gear 342, the third gear 343, and the fourth gear 344 are sequentially disposed at the front end of the shift gear chamber 30 at the output of the front and rear ends of the shift gear chamber 30.
  • the first gear 341 simultaneously engages the reverse gear 311, the first gear 321 and the second gear 331, and the second gear 342 simultaneously engages the third gear 312, the fourth gear 322 and the fifth gear 332.
  • the third gear 343 simultaneously engages the sixth gear 313, the seventh gear 323 and the eighth gear 333, and the fourth gear 344 simultaneously engages the nine gear 314, the tenth gear 324 and the eleven gear 334;
  • the drive shaft 310, the second drive shaft 320 and the third drive shaft 330 are centered on the output shaft 340, and are arranged in parallel around the output shaft 340 in an unequal wheelbase.
  • the output group 34 and the third drive are shown in FIG. Group 33
  • the dashed line represents the meshing relationship between the gears; the output set 34 requires at least three gears, which are illustrated in the present embodiment by four gears.
  • the reverse wheel set 35 has a wheel axle 350 and a wheel 351.
  • the wheel axle 350 is fixed at the front end inner wall surface of the gear case 30.
  • the wheel 351 is disposed on the wheel axle 350 and simultaneously engages the reverse gear 311 of the first drive group 31 and the first gear 341 of the output group 34; the wheel axle 350 is arranged in parallel with the output shaft 340, as shown in FIG.
  • the broken line between the wheel 351 and the first gear 341 represents an engagement relationship.
  • the differential 36 has a driving gear 361 and a driven gear 362.
  • the driving gear 361 is disposed on the output shaft 340 of the output group 34 of the shifting gear chamber 30.
  • the gear 362 is disposed on the axle 360 outside the transmission.
  • the driving gear 361 engages the driven gear 362.
  • the axle 360 is arranged in parallel with the output shaft 340.
  • the driving gear 361 and the driven gear 362 are shown in FIG. The dotted line between them represents the meshing relationship.
  • the first governor 21 is used as an illustration, and the first governor 21 has a The input member 211, an output member 212, a bracket 213, a six-roller set 214 and a tooth sleeve 215;
  • the number of 214 is at least three, and is illustrated by six in this embodiment.
  • the input member 211 is a gear having a through hole at a center thereof and recessed on one side to form a groove.
  • the groove forms an inclined surface with the side of the gear, and the gear faces the concave wall adjacent to the groove.
  • the slot recesses form a ring seat 2111; the input member 211 is disposed at the first shaft 210 with a central through hole, the input member 211 is engaged with the drive gear 11, and the input member 211 of the first governor 21 passes through the drive gear 11 The power of the engine 10 is transmitted and rotated.
  • the sleeve 215 is a hollow ring body, and one side of the ring body is recessed to form a slot.
  • the tooth groove 2151 is a continuous wave shape and the peaks and troughs have the same radius, and the outer ring wall surface of the tooth sleeve 215 is recessed to form a groove; the inner wall surface of the tooth sleeve 215 has a tooth groove, and the inner portion of the tooth sleeve 215
  • the ring sleeve is disposed on the outer ring wall surface of the ring member 2111 of the input member 211, and the groove of the outer ring wall surface of the tooth sleeve 215 receives the fork F to push the sleeve
  • the 215 is axially displaced relative to the input member 211.
  • the output member 212 is a disk body having a through hole at the center thereof and recessed on one side to form a groove, and the groove forms an inclined surface with the intersection of the side faces of the disk body.
  • the disk body protrudes from a side surface of the groove to form a convex tooth 2121.
  • the convex tooth 2121 has a continuous wave shape and the peaks and troughs have the same radius, and the end face of the convex tooth 2121 and the side wall are rounded.
  • the output member 212 has a central perforation and a sleeve portion
  • the groove formed by the inner wall of the inner wall of the inner wall 310 is disposed at a convex tooth of the outer ring wall surface of the first drive shaft 310.
  • the convex tooth 2121 corresponds to the tooth groove 2151 of the tooth sleeve 215, and the groove of the sleeve portion 2122 is The shift fork F is received to push the output member axially displaced relative to the first drive shaft 310.
  • the bracket 213 is a disc body having a through hole in the center of the disc body, and the disc body is formed through six through holes, and the six through holes are planetaryally surrounding the central perforation. ; mounting bearings on the inner edge of the through hole
  • the number of through holes of the bracket 213 corresponds to the number of the roller sets 214, which is illustrated by six in this embodiment.
  • the roller set 214 has a first disc body 2141, a second disc body 2142 and a spring 2143.
  • the first disc body 2141 is a disc body, and the disc body is central.
  • the second disk body 2142 is a disk body, the disk body is convexly formed at the center to form a cylinder, and a continuous hole is formed through the center of the cylinder; the cylindrical outer ring wall surface of the second disk body 2142
  • the spring 2143 is sleeved and mounted on the bearing 2131 of the bracket 213.
  • the cylinder of the first disc body 2141 passes through the through hole of the cylinder of the second disc body 2142 and is fixed to the second disc body 2142.
  • the sleeve 215 is pushed toward the output member 212 by the fork F, and the slot 2151 of the sleeve 215 is The protruding teeth 2121 of the output member 212 are correspondingly engaged, and the sleeve 215 is further pushed by the fork F to push the output member 212 to move away from the input member 211 along the first driving shaft 310;
  • the second disk body 2142 is pushed against the tension of the spring 2143 to move the second disk body 2142 away from the bracket 213, and the first disk body 2141 is away from the input member 211 against the bracket 213;
  • the sleeve 215 of the input member 211 is directly transmitted to the output member 212 and drives the first drive shaft 310 to rotate.
  • the configurations of the second governor 22 and the third governor 23 are the same as those of the first governor 21, and therefore will not be repeatedly described.
  • the fifth synchronizer 335 has a sleeve.
  • the fork F is pushed to engage the canine side of the second gear 331, and the sleeve 3151 of the first synchronizer 315 is pushed by the fork F to engage the dog side of the third gear 312, and the third synchronizer 325
  • the toothed sleeve 3251 is pushed by the fork F to engage the canine side of the fourth gear 322, and the sleeve 215 of the first governor 21 engages the output member 212, so that the power of the engine 10 is transmitted to the first drive shaft 310.
  • the third gear 312 transmits power to the second gear 342 of the output group 34.
  • the gear cover of the second governor 22 is The 225 is disengaged from the output member 222, and the sleeve 3151 of the first synchronizer 315 is pushed by the fork F to be withdrawn from the canine side of the third gear 312, and the sleeve 3161 of the second synchronizer 316 is dialed.
  • the fork F is pushed into engagement with the canine side of the sixth gear 313.
  • the fourth gear 322 and the fifth gear 332 are kept in mesh with the sleeve of the synchronizer.
  • the sleeve 235 of the third governor 23 engages the output member 232.
  • the power of the engine 10 is transmitted to the third drive shaft 330, and the fifth gear 332 transmits power to the second gear 342.
  • the multi-drive shaft transmission with the traction drive synchronous governor of the present invention is disposed in the longitudinal direction of the engine, and the output shaft 340 extends to the outside of the transmission gear chamber 30 of the transmission.
  • the driving gear 361 of the differential 36 is disposed on an output shaft 340 outside the shifting gear chamber 30.
  • the driven gear 362 is disposed on an axle 360 outside the transmission, and the driving gear 361 engages the driven gear 362;
  • the axle 360 is vertically aligned with the output shaft 340.
  • the third synchronizer 325 is preset to the disengaged tooth sleeve 3251.
  • the operation of the fork controlled by the power mechanism is moved forward to mesh with the canine side of the first gear 321 , fifth
  • the synchronizer 335 is preset to be in a disengaged state.
  • the operation of the shifting fork controlled by the power mechanism is forwardly moved to engage with the canine side of the second gear 331, and the first synchronizer 315 is preset to be in a separated state.
  • the third governor 23 When the gearbox is to be upshifted from the first gear to the second gear, the third governor 23 is engaged by the operation of the fork controlled by the power mechanism, and the second governor 22 is operated by the fork controlled by the power mechanism. And separating, at this time, the power of the engine is transmitted to the output member of the third governor 23 and the third drive shaft 33 via the input shaft 110 and the drive gear 11, and the second gear 331 is driven by the second gear 331 to form the second gear output. ;
  • the first governor 21 When the gearbox is to be upshifted from the second gear to the third gear, the first governor 21 is engaged by the operation of the shifting fork controlled by the power mechanism, and the third governor 23 is operated by the shifting fork controlled by the power mechanism. Separating, the sleeve 3251 of the third synchronizer 325 meshing with the canine side of the first gear 321 is moved backward by the operation of the shift fork to be separated from the canine side of the first gear 321 and further meshed with the canine side of the fourth gear 322. At this time, the power of the engine is transmitted to the output member 212 of the first governor 21 and the first drive shaft 310 via the input shaft 110 and the drive gear 11, and the third gear 342 is driven by the third gear 312 to form a third output.
  • the first governor 21 When the gearbox is to be upshifted from the fifth gear to the sixth gear, the first governor 21 is engaged by the operation of the shift fork, and at the same time The governor 23 is separated by the operation of the shift fork, and the sleeve 3161 of the second synchronizer 316 that meshes with the canine side of the fourth gear 322 is moved forward by the operation of the shift fork to be separated from the canine side of the fourth gear 322.
  • the fourth synchronizer 326 is preset to the disengaged state
  • the operation of the fork is forwardly moved to mesh with the canine side of the seventh gear 323, and the power of the engine is driven and driven via the input shaft 110.
  • the gear 11 is transmitted to the output member 212 of the first governor 21 and the first drive shaft 310, and the sixth gear 313 is driven by the sixth gear 313 to form a sixth gear output;
  • the second governor 22 When the gearbox is to be upshifted from the sixth gear to the seventh gear, the second governor 22 is engaged by the operation of the fork controlled by the power mechanism, and the first governor 21 is separated by the operation of the shift fork, and The tooth sleeve 3351 of the fifth synchronizer 335 of the canine-tooth side of the fifth gear 332 is moved forward by the operation of the fork and is separated from the canine side of the fifth gear 332 to return to a predetermined separation state, while the sixth synchronizer 336 is pre- The operation of the fork that is set to the disengaged state is forwardly moved by the shifting fork controlled by the power mechanism to mesh with the canine side of the eighth gear 333, and the power of the engine is transmitted to the second governor 22 via the input shaft 110 and the drive gear 11 at this time.
  • the output member and the second drive shaft 320 are further driven by the seventh gear 323 to form the seventh gear output.
  • the third governor 23 When the gearbox is to be upshifted from the seventh gear to the eighth gear, the third governor 23 is engaged by the operation of the fork controlled by the power mechanism, and the second governor 22 is separated by the fork operation, and six The sleeve 3161 of the second synchronizer 316 of the dog gear side of the gear 313 is moved backward by the operation of the fork controlled by the power mechanism to be separated from the dog side of the sixth gear, and further to the dog side of the nine gear 314. Engagement, the power of the engine is transmitted to the output member of the third governor 23 and the third drive shaft 330 via the input shaft 110 and the drive gear 11, and the third gear 343 is driven by the eighth gear 333 to form an eighth gear output.
  • the first governor 21 When the gearbox is to be upshifted from the eighth gear to the ninth gear, the first governor 21 is engaged by the operation of the fork controlled by the power mechanism, and the third governor 23 is separated by the shifting operation, and seven The tooth cover of the fourth synchronizer 326 of the canine-toothed side of the gear 323 is moved backward by the shifting fork to be separated from the canine side of the seventh gear 323, and further meshed with the canine side provided on the tenth gear 324, at this time the engine The power is transmitted to the output member 212 of the first governor 21 and the first drive shaft 310 via the input shaft 110 and the drive gear 11, and the fourth gear 344 is driven by the nine-speed gear 314 to form a ninth output.
  • the second governor 22 When the gearbox is to be upshifted from the ninth gear to the tenth gear, the second governor 22 is engaged by the operation of the fork controlled by the power mechanism, and the first governor 21 is separated by the operation of the shift fork, The tooth cover of the sixth synchronizer 336 of the dog gear side of the eighth gear 333 is moved backward by the shift fork operation to be separated from the dog side of the eighth gear 333, and is further engaged with the dog side provided on the eleven gear 334.
  • the power of the engine is transmitted to the output member of the second governor 22 and the second drive shaft 320 via the input shaft 110 and the drive gear 11, and the fourth gear 44 is driven by the tenth gear 324 to form a tenth output.
  • the third governor 23 When the gearbox is to be upshifted from the tenth gear to the eleventh gear, the third governor 23 is engaged by the operation of the fork controlled by the power mechanism, and the second governor 22 is separated by the fork operation, The power of the engine is transmitted to the output member of the third device 23 and the third drive shaft 330 via the input shaft 110 and the drive gear 11, and the fourth gear 344 is driven by the eleven-speed gear 334 to form an eleventh output.
  • both the continuous corrugated tooth groove of the toothed sleeve 215 and the continuous corrugated convex tooth of the output member 212 are formed by: drawing a ring-shaped wavy line having the same radius of all peaks and troughs; The ring-shaped wavy line is drawn equidistantly from the center to draw a two-ring wavy line; the ring-shaped continuous wavy cogging and the convex tooth are made based on the two newly drawn ring-shaped wavy lines; the ring-shaped continuous wave shape The intersection of the tooth groove 2151 and all the planes of the convex teeth 2121 is rounded at the same radius.
  • the roller set 214 is assembled in such a manner that the outer side of the hollow cylinder of the second disc body 2142 is inserted into the spring 2143;
  • the hollow cylinder of the second disk body 2142 is sleeved into the bearing 2131 of the bracket 213 through the side of the bracket 213 near the power output.
  • the bearing 2131 needs to make the hollow cylinder of the second disk body 2142 fit in the bearing 2131.
  • the axial direction of the second disk body 2141 is inserted into the hollow cylinder of the second disk body 2142 from the other side of the bracket 213; the cylinder of the first disk body 2141 protrudes from the second disk body A buckle is fastened on the other side of the 2142.
  • the first drive shaft 310, the second drive shaft 320, and the third drive shaft 330 are arranged around the output shaft 340 around the output shaft 340 in a parallel arrangement of unequal wheelbases, and are driven by the respective drives.
  • Each gear gear and synchronizer are arranged on the shaft to achieve the effect of increasing the number of power transmission gears in a limited space; in FIG. 5 to FIG.
  • the gear sleeve 3251 of the third synchronizer and the tooth sleeve 3351 of the fifth synchronizer are engaged, so that the gearbox of the present invention can control the first governor 21, the second governor 22 and the third governor 23
  • the clutch is upshifted from the third gear to the fifth gear quickly; since the gearbox of the present invention has the first gear and the eleventh gear, the remaining gears are adjacent to the front and rear gears of the dog gear synchronizer. All of them are pre-engaged, so if the sudden downshift is required in the process of upshifting, the clutching of the first governor 21, the second governor 22 and the third governor 23 can be controlled.
  • the sleeve 3151 of the first synchronizer 315 is moved toward the front end of the shifting gear chamber 30 by the operation of the shifting fork controlled by the power mechanism to engage the canine side of the reverse gear 311,
  • the first governor 21 is engaged by the operation of the shifting fork F controlled by the power mechanism.
  • the power of 10 is transmitted to the output member 212 of the first governor 21 and the first drive shaft 310 via the input shaft 110 and the drive gear 11, the brake wheel 351 is driven via the reverse gear 311, and the output shaft 340 is driven by the brake wheel 351.
  • the first gear 341 forms a reverse output; the fork referred to in the present invention is a fork mechanism of an additional hydraulic or electric actuator in the prior art.

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Abstract

一种牵引驱动同步调速器及具有该调速器的多驱动轴变速箱，该多驱动轴变速箱具有一调速器室（20）及一变速齿轮室（30），通过该调速器室（20）内的牵引驱动同步调速器（21、22、23）以牵引驱动方式传递引擎的动力至变速箱的输出组（34），该调速器于其输入件（211）及输出件（212）间采行星式设置复数滚轮组（214），以该输出件（212）推抵该滚轮组（214）轴向移动以接触该输入件（212），从而达成传递动力的功效，同时，该变速齿轮室（30）中各驱动组（31、32、33）的轴（310、320、330）是以该输出组（34）的轴（340）为中心环绕该输出组（34）的轴（340）成不等轴距的平行排列，可在有限的空间中增加变速箱的档位数；经由该牵引驱动同步调速器及各驱动组的轴布置的技术手段的实施，从而改善现有技术中变速箱传动效率低下、离合器磨损及增加变速档位时需占据较大空间的问题。

Description

牵引驱动同歩调速器及具有该调速器的多驱动轴变速箱 技术领域
本发明涉及变速箱， 尤指一种采用牵引驱动同步调速器， 并且为多轴驱动的车用变 速箱。 背景技术
现有技术的车用变速装置主要有： 手排变速、 双离合器自手排变速、 自动变速及无 段变速等形式； 手排变速的结构简单， 但需频繁操作离合器与排档杆， 且易因离合器的 频繁或不当操作而令离合器片发生磨耗； 双离合器自手排变速， 加入双离合器与电脑控 制油压系统后， 虽具有自动变速功能， 但双离合器结构复杂不易维修， 并且同样有离合 器片磨耗的情形； 而自动变速结构复杂， 并且因采用液压扭力转换器非直接传动， 以及 行星齿轮组的惯性阻力， 从而造成传动效率不佳； 无段变速箱是利用钢带或滚轮间的摩 擦力传动， 其中以钢带传动者， 受限于钢带强度仅能用于小型车辆， 而以滚轮传动者， 滚轮控制机构亦相当复杂不易维修； 因此， 现有技术的变速装置具有部件易磨耗、 构造 复杂及效率不佳等缺陷。
同时， 在节能减碳的环保考量下， 现有技术欲以增加变速装置的档位数， 以确保引 擎动力适宜的输出， 从而提升引擎的动力效率， 然而， 欲增加变速装置的档位势必将增 长驱动轴， 以配置所增加的传动齿轮， 此举将扩大变速装置的尺寸， 但是， 车辆设置变 速装置的空间有限， 故如何于有限空间的条件下， 增加变速装置的档位数是目前应着手 解决的课题。 发明内容
因此， 本发明的目的在于： 改善现有技术中变速装置的部件易磨耗、 维修不易及效 率不佳等缺陷， 同时， 于一有限空间中， 增加变速装置的档位数， 从而提供一种传动效 率佳、 部件不易磨耗且多档位数的变速箱。
为达到上述的目的， 本发明所采用的技术手段为一种牵引驱动同步调速器， 其连接 于一为动力输出的驱动轴， 其特征在于： 具有一轴、 一输入件、 一输出件、 一支架、 至 少三滚轮组及一齿套； 该输入件为一齿轮， 该齿轮中央具有一穿孔并于一侧面凹陷形成 凹槽， 该凹槽与该侧面的交接处形成一倾斜面， 该齿轮邻近该凹槽的环壁面朝该凹槽凹 陷形成一环座， 该环座外环壁面设有凸齿； 该输入件的中央穿孔套设于该轴； 该齿套为 一中空环体， 该环体一侧面凹陷形成一齿槽， 该齿槽是一连续波状且波峰及波谷均具有 相同的半径， 该齿套内环壁面设有齿槽， 该齿槽套设于该输入件的环座的凸齿， 两者之 间可轴向位移； 该输出件为一圆盘体， 该圆盘体中央具有一穿孔并于一侧面凹陷形成凹 槽， 该凹槽与该圆盘体侧面的交接处形成一倾斜面， 该圆盘体邻近该凹槽的侧面凸伸形 成一连续波状凸齿， 该圆盘体的中央穿孔于远离该凹槽的侧面凸伸形成一套部， 该穿孔 及套部的内缘壁面形成齿槽； 该输出件与该输入件相对应设置， 该输出件的连续波状凸 齿与该齿套的连续波状齿槽相对应； 该输出件的穿孔及套部连接于该驱动轴， 该输出件 可相对于该驱动轴轴向位移； 该支架为一圆盘体， 该圆盘体中央具有一穿孔， 该圆盘体 贯穿成形至少三个通孔， 该通孔呈行星式环绕该中央穿孔， 并于该通孔内缘装设轴承， 该支架的中央穿孔套设于该轴； 该滚轮组承设于该支架的通孔的轴承。
所述的牵引驱动同步调速器， 其中该滚轮组具有一第一盘体、 一第二盘体及一弹 簧； 该第一盘体为一圆盘体， 该圆盘体中央凸伸形成一圆柱； 该第二盘体为一圆盘体， 该圆盘体中央凸伸形成一圆柱， 并且于该圆柱中心贯穿成形一贯孔； 该第二盘体的圆柱 外环壁面套设该弹簧并承设于该支架的通孔的轴承， 该第一盘体的圆柱穿设该第二盘体 圆柱的贯孔并与该第二盘体固设， 该弹簧两端抵顶在支架与第二盘体之间， 使该第二盘 体远离该支架， 而该第一盘体抵靠该支架。
本发明同时提供一种具有牵引驱动同步调速器的多驱动轴变速箱， 具有一调速器室 及一变速齿轮室； 该调速器室邻近一引擎， 该调速器室具有一结合于该引擎的输入轴的 驱动齿轮及至少两个调速器； 该调速器的轴一端固设于该调速器室的内缘壁面上， 各轴 以该引擎的输入轴为中心环绕设置成等轴距的平行排列， 该驱动齿轮啮合该调速器的输 入件； 该变速齿轮室具有至少两个驱动组、 一输出组及一倒档怠轮组， 该变速齿轮室连 接于该调速器室远离该引擎的一端； 该输出组具有一轴及至少三齿轮； 该轴置设于该变 速齿轮室， 该齿轮设置于该轴上； 该驱动组具有一轴、 至少三齿轮及至少两个同步器； 该驱动组的轴外环壁面形成凸齿， 该轴穿设该变速齿轮室至该调速器室内， 并与相应的 调速器连结， 该轴的凸齿穿设于该调速器的输出件中央穿孔及套部的齿槽， 该驱动组的 轴以该输出轴为中心环绕该输出轴成不等轴距的平行排列； 该齿轮及该同步器交错排列 的设置在该驱动组的轴上； 各驱动组的齿轮分别与该输出组的齿轮相对应啮合； 该倒档 怠轮组具有一怠轮轴及一怠轮； 该怠轮轴一端固设于该变速齿轮室邻近该调速器室之 端， 该怠轮设置于该怠轮轴上， 并同时啮合该驱动组及该输出组的相应齿轮； 该怠轮轴 与该输出轴平行排列。
所述的多驱动轴变速箱， 其中该调速器室具有三调速器， 分别为第一调速器、 第二 调速器及第三调速器； 该变速齿轮室具有三驱动组， 分别为第一驱动组、 第二驱动组及 第三驱动组； 该第一驱动组的轴连接该第一调速器， 该第二驱动组的轴连接该第二调速 器， 该第三驱动组的轴连接该第三调速器； 该输出组具有第一齿轮、 第二齿轮、 第三齿 轮及第四齿轮， 上述齿轮依序设置于该输出组的轴上； 该第一驱动组轴上的设置依序为 倒档齿轮、 第一同步器、 三档齿轮、 六档齿轮、 第二同步器及九档齿轮； 该第二驱动组 轴上的设置依序为一档齿轮、 第三同步器、 四档齿轮、 七档齿轮、 第四同步器及十档齿 轮； 该第三驱动组轴上的设置依序为二档齿轮、 第五同步器、 五档齿轮、 八档齿轮、 第 六同步器及十一档齿轮； 该第一齿轮同时啮合上述倒档齿轮、 一档齿轮及二档齿轮， 该 第二齿轮同时啮合上述三档齿轮、 四档齿轮及五档齿轮， 该第三齿轮同时啮合上述六档 齿轮、 七档齿轮及八档齿轮， 该第四齿轮同时啮合上述九档齿轮、 十档齿轮及十一档齿 轮； 该怠轮同时啮合该第一驱动组的倒档齿轮及该输出组的第一齿轮。
所述的多驱动轴变速箱， 该变速箱外具有一轮轴， 其特征在于： 具有一差速器； 该 差速器具有一主动齿轮及一从动齿轮， 该主动齿轮设置于该输出组的轴上， 该从动齿轮 设置于该变速箱外的轮轴上， 该主动齿轮啮合该从动齿轮， 该轮轴与该输出组的轴呈平 行排列。
所述的多驱动轴变速箱， 该变速箱外具有一轮轴， 其特征在于： 具有一差速器； 该 差速器具有一主动齿轮及一从动齿轮， 该主动齿轮设置于该变速齿轮室外的输出组的轴 上， 该从动齿轮设置于该变速箱外的轮轴上， 该主动齿轮啮合该从动齿轮， 该轮轴与该 输出组的轴呈垂直排列。
所述的多驱动轴变速箱， 其中该调速器齿套的外环壁面凹陷形成一用以容设拨叉的 凹槽； 该调速器的输出件的套部凹陷形成一用以容设拨叉的凹槽。
所述的牵引驱动同步调速器， 其中该齿套的连续波状齿槽与输出件的连续波状凸齿 两者的制作方式为： 绘制一所有波峰与波谷均为相同半径的环型波状线； 以该环型波状 线为中心向两侧等距平移后绘制两环型波状线； 以该两新绘的环型波状线为基准制作该 环型连续波状齿槽与凸齿； 该环型连续波状齿槽与凸齿所有平面的交线均以相同的半径 作圆角处理。 所述的牵引驱动同步调速器， 其中该滚轮组的组装方式为： 该第二盘体的中空圆柱 外侧套入该弹簧； 该第二盘体的中空圆柱由该支架靠近动力输出的侧面套入该支架通孔 内的轴承， 该轴承需使该第二盘体的中空圆柱可于该轴承内作轴向的前后移动； 第一盘 体的圆柱由该支架的另一侧面套入该第二盘体的中空圆柱； 该第一盘体的圆柱凸出于该 第二盘体另一侧面处扣设一扣环。
本发明的有益效果在于： 通过变速箱内各驱动轴环绕输出轴成不等轴距的平行排 列， 在不增加变速箱的长度的前提下， 增加变速箱的档位数， 同时， 于该变速箱中采用 内含采行星布置的滚轮组的调速器， 以该调速器的输出件推抵该滚轮组轴向移动以接触 该调速器的输入件， 从而将引擎的输入动力由驱动齿轮直接传递至变速箱的输出齿轮， 以避免现有技术中传动效率低下或离合器因频繁或不当操作造成磨损的问题。 附图说明
图 1为本发明配置于横置引擎时的示意图；
图 2为本发明配置于横置引擎时各轴的齿轮配置的示意图;
图 3为本发明牵引驱动同步调速器的剖面图；
图 4为本发明图 3的 A-A剖视图；
图 5为本发明牵引驱动同步调速器作动的第一状态图；
图 6为本发明牵引驱动同步调速器作动的第二状态图；
图 7为本发明牵引驱动同步调速器作动的第三状态图；
图 8为本发明一实施例作动的第一状态图；
图 9为本发明一实施例作动的第二状态图；
图 10为本发明另一实施例图；
图 11为本发明配置于纵置引擎时的示意图。
附图标记
10 引擎
11 驱动齿轮 110 输入轴
20 调速器室
21 第一调速器 210 第一轴
211 输入件 2111 环座
212 输出件 2121 凸齿 2122 套部 213 支架
2131 轴承 214 滚轮组
2141 第一盘体 2142 第二盘体
2143 弹簧 215 凶 ¾r
2151 22 第二调速器
220 第二轴 222 输出件
225 凶 ¾r 23 第三调速器
230 第三轴 232 输出件
235 凶 ¾r
30 变速齿轮室
31 第一驱动组 310 第一驱动轴
311 倒档齿轮 312 三档齿轮
313 六档齿轮 314 九档齿轮
315 第一同步器 3151 凶 ¾r
316 第二同步器 3161 凶 ¾r
32 第二驱动组 320 第二驱动轴
321 一档齿轮 322 四档齿轮
323 七档齿轮 324 十档齿轮
325 第三同步器 3251 凶 ¾r
326 第四同步器 33 第三驱动组
330 第三驱动轴 331 二档齿轮
332 五档齿轮 333 八档齿轮
334 十一档齿轮 335 第五同步器
3351 凶 ¾r 336 第六同步器
34 输出组 340 输出轴
341 第一齿轮 342 第二齿轮
343 第三齿轮 344 第四齿轮
35 倒档怠轮组 350 怠轮轴
351 怠轮 36 差速器
360 轮轴 361 主动齿轮 362 从动齿轮
F 拨叉 具体实施方式
以下配合图式及本发明的较佳实施例， 进一步阐述本发明为达成预定发明目的所采 取的技术手段。
图 1所示具体实施例， 是本发明具牵引驱动同步调速器的多驱动轴变速箱配置于横 置引擎的实施态样， 该变速箱具有一调速器室 20及一变速齿轮室 30。
请参照图 1所示， 该调速器室 20的一端邻近一引擎 10， 该调速器室 20具有一结合 于该引擎 10的输入轴 110的驱动齿轮 11、 一第一调速器 21、 一第二调速器 22及一第三 调速器 23 ; 驱动齿轮 11与第一调速器 21、 第二调速器 22及第三调速器 23同时啮合， 该第一调速器 21具有一第一轴 210， 该第一轴 210—端固设于该调速器室 20的内缘壁 面上， 该第一调速器 21、 第二调速器 22及第三调速器 23的具体构造在后文详细描述； 上述第一轴 210、 第二轴 220及第三轴 230环绕该输入轴 110成等轴距的平行排列； 该 引擎 10的动力是经由该驱动齿轮 11传递予该第一调速器 21、 该第二调速器 22及该第 三调速器 23， 图上在该驱动齿轮 11与第三调速器 23间所标示的虚线代表该驱动齿轮 11 与第三调速器 23间的啮合关系； 所需该调速器的数量为至少两个， 于本实施例中是以三 个调速器作为说明。
请参照图 1所示， 该变速齿轮室 30具有第一驱动组 31、 第二驱动组 32、 第三驱动 组 33、 输出组 34、 倒档怠轮组 35及差速器 36， 该变速齿轮室 30连接于该调速器室 20 远离该引擎 10的一端； 该驱动组的数量对应于该调速器的数量， 于本实施例中是以三个 驱动组作为说明。
请参照图 1及图 2所示， 该第一驱动组 31具有一第一驱动轴 310、 倒档齿轮 311、 三档齿轮 312、 六档齿轮 313、 九档齿轮 314、 第一同步器 315及第二同步器 316; 该第 一驱动轴 310承设于该变速齿轮室 30前、 后两端所设置的轴承， 其中一端并穿设至该调 速器室 20内， 上述倒档齿轮 311、 三档齿轮 312、 六档齿轮 313及九档齿轮 314依序由 该变速齿轮室 30的前端设置于该第一驱动轴 310上， 该第一同步器 315装设于该倒档齿 轮 311与该三档齿轮 312之间， 该第二同步器 316装设于该六档齿轮 313与该九档齿轮 314之间； 该倒档齿轮 311及该三档齿轮 312的犬齿侧朝向该第一同步器 315， 该六档齿 轮 313及该九档齿轮 314的犬齿侧朝向该第二同步器 316， 上述同步器各具有一齿套； 驱动组所需齿轮及同步器的数量分别为至少三个及至少两个， 于本实施例中是以四个齿 轮及两个同步器做说明。
请参照图 1及图 2所示， 该第二驱动组 32及该第三驱动组 33的结构同该第一驱动 组 31所述， 差别在于连接于第二驱动轴 320上是一档齿轮 321、 第三同步器 325、 四档 齿轮 322、 七档齿轮 323、 第四同步器 326及十档齿轮 324， 以及连接于第三驱动轴 330 上是二档齿轮 331、 第五同步器 335、 五档齿轮 332、 八档齿轮 333、 第六同步器 336及 十一档齿轮 334; 上述第一驱动轴 310、 第二驱动轴 320及第三驱动轴 330分别与上述调 速器室 20的第一轴 210、 第二轴 220及第三轴 230同轴相对设置， 并且与上述第一调速 器 21、 第二调速器 22及第三调速器 23连接。
请参照图 1及图 2所示， 该输出组 34具有一输出轴 340、 一第一齿轮 341、 一第二 齿轮 342、 一第三齿轮 343及一第四齿轮 344; 该输出轴 340承设于该变速齿轮室 30 前、 后两端所设置的轴承， 上述第一齿轮 341、 第二齿轮 342、 第三齿轮 343及第四齿轮 344依序由该变速齿轮室 30的前端设置于该输出轴 340上， 该第一齿轮 341同时啮合上 述倒档齿轮 311、 一档齿轮 321及二档齿轮 331， 该第二齿轮 342同时啮合上述三档齿轮 312、 四档齿轮 322及五档齿轮 332， 该第三齿轮 343同时啮合上述六档齿轮 313、 七档 齿轮 323及八档齿轮 333， 该第四齿轮 344同时啮合上述九档齿轮 314、 十档齿轮 324及 十一档齿轮 334; 上述第一驱动轴 310、 第二驱动轴 320及第三驱动轴 330以该输出轴 340为中心， 环绕该输出轴 340成不等轴距的平行排列， 于图 1中该输出组 34与该第三 驱动组 33间的虚线代表齿轮间的啮合关系； 该输出组 34所需齿轮至少三个， 于本实施 例中是以四个齿轮做说明。
请参照图 1及图 2所示， 该倒档怠轮组 35具有一怠轮轴 350及一怠轮 351 ; 该怠轮 轴 350—端固设于该变速齿轮室 30的前端内缘壁面， 该怠轮 351设置于该怠轮轴 350 上， 并同时啮合该第一驱动组 31的倒档齿轮 311及该输出组 34的第一齿轮 341 ; 该怠 轮轴 350与该输出轴 340平行排列， 于图 1中该怠轮 351与该第一齿轮 341间的虚线代 表啮合关系。
请参照图 1及图 2所示， 该差速器 36具有一主动齿轮 361及一从动齿轮 362; 该主 动齿轮 361设置于该变速齿轮室 30输出组 34的输出轴 340上， 该从动齿轮 362设置于 该变速箱外的轮轴 360上， 该主动齿轮 361啮合该从动齿轮 362; 该轮轴 360与该输出 轴 340呈平行排列， 于图 1中该主动齿轮 361与该从动齿轮 362间的虚线代表啮合关系。
图 3及图 4具体实施例， 是以该第一调速器 21作为说明， 该第一调速器 21具有一 输入件 211、 一输出件 212、 一支架 213、 六滚轮组 214及一齿套 215 ; 所需该滚轮组
214的数量至少三个， 于本实施例中是以六个作为说明。
该输入件 211 为一齿轮， 该齿轮中央具有一穿孔并于一侧面凹陷形成凹槽， 该凹槽 与该齿轮侧面的交接处形成一倾斜面， 该齿轮邻近该凹槽的环壁面朝该凹槽凹陷形成一 环座 2111 ; 该输入件 211以中央穿孔设置于该第一轴 210， 该输入件 211与该驱动齿轮 11 啮合， 该第一调速器 21的输入件 211通过该驱动齿轮 11传递该引擎 10的动力而转动。
请参照图 3及图 4所示， 该齿套 215为一中空环体， 该环体一侧面凹陷形成一齿槽
2151 , 该齿槽 2151是一连续波状且波峰及波谷均具有相同的半径， 该齿套 215的外环壁 面凹陷形成凹槽； 该齿套 215 内环壁面具有齿槽， 该齿套 215 的内环套设于该输入件 211的环座 2111外环壁面的凸齿， 该齿套 215外环壁面的凹槽容设拨叉 F以推抵该齿套
215相对于该输入件 211轴向位移。
请参照图 3所示， 该输出件 212为一圆盘体， 该圆盘体中央具有一穿孔并于一侧面 凹陷形成凹槽， 该凹槽与该圆盘体侧面的交接处形成一倾斜面， 该圆盘体邻近该凹槽的 侧面凸伸形成一凸齿 2121， 该凸齿 2121 呈连续波状并且波峰及波谷均具有相同的半 径， 该凸齿 2121的端面与侧壁交接处是倒圆角， 该圆盘体的中央穿孔于远离该凹槽的侧 面凸伸形成一套部 2122， 该套部 2122凹陷形成凹槽； 该输出件 212以中央穿孔及套部
2122 内缘壁面所形成的齿槽套设于该第一驱动轴 310外环壁面的凸齿处， 该凸齿 2121 与该齿套 215的齿槽 2151相对应， 该套部 2122的凹槽是用以容设拨叉 F以推抵该输出 件相对于该第一驱动轴 310轴向位移。
请参照图 3及图 4所示， 该支架 213为一圆盘体， 该圆盘体中央具有一穿孔， 该圆 盘体贯穿成形六个通孔， 该六通孔呈行星式环绕该中央穿孔； 于该通孔内缘装设轴承
2131； 该支架 213的通孔数量是对应于该滚轮组 214的数量， 于本实施例中是以六个作 为说明。
请参照图 3及图 4所示， 该滚轮组 214具有一第一盘体 2141、 一第二盘体 2142及 一弹簧 2143 ; 该第一盘体 2141 为一圆盘体， 该圆盘体中央凸伸形成一圆柱， 该第二盘 体 2142为一圆盘体， 该圆盘体中央凸伸形成一圆柱， 并且于该圆柱中心贯穿成形一贯 孔； 该第二盘体 2142 的圆柱外环壁面套设该弹簧 2143 并承设于该支架 213 的轴承 2131 , 该第一盘体 2141的圆柱穿设该第二盘体 2142圆柱的贯孔并与该第二盘体 2142固 设， 该弹簧 2143的张力使该第二盘体 2142远离该支架 213—侧面， 而该第一盘体 2141 抵靠该支架 213另一侧面。 图 5至图 7中， 因调速器内部的构造对称， 故仅以上半部的剖视图作为说明。 请参 照图 5至图 6所示， 当输出件 212受拨叉 F推动时， 该输出件 212沿该第一驱动轴 310 朝该输入件 211轴向移动， 该输出件 212凹槽的倾斜面推抵该滚轮组 214 的第二盘体 2142， 使该第二盘体 2142相对该支架 213朝该输入件 211移动， 该第二盘体 2142抵压 该弹簧 2143使之压缩， 由于第一盘体 2141与该第二盘体 2142固设， 以致该第一盘体 2141同时远离该支架 213而推抵该输入件 211凹槽的倾斜面； 通过该滚轮组 214牵引传 动该输入件 211的转动动力至该输出件 212， 使该输出件 212的转速趋近于该输入件 211 的转速， 并带动该第一驱动轴 310转动。
请参照图 7所示， 当该输出件 212 的转速趋近于该输入件 211 的转速时， 该齿套 215受拨叉 F推动朝该输出件 212移动， 该齿套 215的齿槽 2151与该输出件 212的凸齿 2121相应啮合， 该齿套 215继续受拨叉 F推动而推抵该输出件 212沿该第一驱动轴 310 朝远离该输入件 211 方向移动； 该滚轮组 214的该第二盘体 2142受弹簧 2143张力推 抵， 使该第二盘体 2142远离该支架 213， 同时该第一盘体 2141远离该输入件 211而抵 靠该支架 213 ; 使得引擎 10的动力通过该输入件 211的该齿套 215直接传递至该输出件 212， 并带动该第一驱动轴 310转动。
当该齿套 215受拨叉 F推动朝远离该输出件 212移动时， 该第一调速器 21即回复预 设的分离状态。
第二调速器 22及第三调速器 23的构造与第一调速器 21的构造相同， 故不再重复 描述。
请参照图 8至图 9所示， 当变速箱输出档位为第三档时， 该第五同步器 335的齿套
3351受拨叉 F推抵啮合该二档齿轮 331的犬齿侧， 该第一同步器 315的齿套 3151受拨 叉 F推抵啮合该三档齿轮 312的犬齿侧， 该第三同步器 325的齿套 3251受拨叉 F推抵啮 合该四档齿轮 322的犬齿侧， 该第一调速器 21的齿套 215啮合该输出件 212， 使得引擎 10的动力传输至该第一驱动轴 310， 再由该三档齿轮 312传递动力至该输出组 34的第二 齿轮 342; 档位由第三档升为第四档时， 该第一调速器 21 的齿套 215退出与该输出件 212的啮合， 该第五同步器 335的齿套 3351受拨叉 F推抵朝另一方向移动以啮合该五档 齿轮 332的犬齿侧， 该三档齿轮 312及该四档齿轮 322与同步器的齿套间保持啮合， 该 第二调速器 22 的齿套 225 啮合该输出件 222， 则引擎 10的动力传输至该第二驱动轴 320， 该四档齿轮 322传递动力至该第二齿轮 342。
请参照图 9及图 10所示， 变速箱输出档位为第五档时， 该第二调速器 22 的齿套 225退出与该输出件 222的啮合， 该第一同步器 315的齿套 3151受拨叉 F推抵退出与该 三档齿轮 312犬齿侧的啮合， 该第二同步器 316的齿套 3161受拨叉 F推抵啮合该六档齿 轮 313的犬齿侧， 该四档齿轮 322及该五档齿轮 332与同步器的齿套间保持啮合， 该第 三调速器 23的齿套 235啮合该输出件 232， 引擎 10的动力传输至该第三驱动轴 330， 该 五档齿轮 332传递动力至该第二齿轮 342。
请参照图 11所示， 本发明具牵引驱动同步调速器的多驱动轴变速箱配置于纵置引擎 时的实施态样， 该输出轴 340延伸至该变速箱的变速齿轮室 30外， 该差速器 36的主动 齿轮 361设置于该变速齿轮室 30外的输出轴 340上， 该从动齿轮 362设置于该变速箱外 的轮轴 360上， 该主动齿轮 361啮合该从动齿轮 362; 该轮轴 360与该输出轴 340呈垂 直排列。
当变速箱的档位选择为空档或停车档时， 上述调速器及同步器均为预设的分离状 态， 此时引擎的动力即不经由该变速箱输出。
当变速箱的档位选择为前进档时， 第三同步器 325预设为分离状态的齿套 3251受动 力机构控制的拨叉的操作向前移动与一档齿轮 321 的犬齿侧啮合， 第五同步器 335预设 为分离状态的齿套 3351受动力机构控制的拨叉的操作向前移动与二档齿轮 331的犬齿侧 啮合， 第一同步器 315预设为分离状态的齿套 3151受动力机构控制的拨叉的操作向后移 动与三档齿轮 312的犬齿侧啮合， 同时第二调速器 22受动力机构控制的拨叉的操作而啮 合， 此时引擎的动力经由输入轴 110及驱动齿轮 11传递至第二调速器 22的输出件及第 二驱动轴 320， 再由一档齿轮 321驱动第一齿轮 341形成第一档输出；
当变速箱要由第一档升档为第二档时， 第三调速器 23受动力机构控制的拨叉的操作 而啮合， 同时第二调速器 22受动力机构控制的拨叉的操作而分离， 此时引擎的动力经由 输入轴 110及驱动齿轮 11传递至第三调速器 23的输出件及第三驱动轴 33， 再由二档齿 轮 331驱动第一齿轮 341形成第二档输出；
当变速箱要由第二档升档为第三档时， 第一调速器 21受动力机构控制的拨叉的操作 而啮合， 第三调速器 23受动力机构控制的拨叉的操作而分离， 与一档齿轮 321的犬齿侧 啮合的第三同步器 325 的齿套 3251受拨叉的操作向后移动与一档齿轮 321 的犬齿侧分 离， 进而与四档齿轮 322的犬齿侧啮合， 此时引擎的动力经由输入轴 110及驱动齿轮 11 传递至第一调速器 21的输出件 212及第一驱动轴 310， 再由三档齿轮 312驱动第二齿轮 342形成第三档输出。
当变速箱要由第五档升档为第六档时， 第一调速器 21受拨叉的操作啮合， 同时第三 调速器 23受拨叉的操作而分离， 与四档齿轮 322的犬齿侧啮合的第二同步器 316的齿套 3161， 受拨叉的操作向前移动与四档齿轮 322 的犬齿侧分离， 回复预设的分离状态， 同 时第四同步器 326预设为分离状态的齿套受拨叉的操作向前移动与七档齿轮 323的犬齿 侧啮合， 此时引擎的动力经由输入轴 110及驱动齿轮 11传递至第一调速器 21的输出件 212及第一驱动轴 310， 再由六档齿轮 313驱动第三齿轮 343形成第六档输出；
当变速箱要由第六档升档为第七档时， 第二调速器 22受动力机构控制的拨叉的操作 而啮合， 同时第一调速器 21受拨叉的操作而分离， 与五档齿轮 332的犬齿侧啮合的第五 同步器 335的齿套 3351， 受拨叉的操作向前移动与五档齿轮 332的犬齿侧分离回复预设 的分离状态， 同时第六同步器 336预设为分离状态的齿套受动力机构控制的拨叉的操作 向前移动与八档齿轮 333的犬齿侧啮合， 此时引擎的动力经由输入轴 110及驱动齿轮 11 传递至第二调速器 22的输出件及第二驱动轴 320， 再由七档齿轮 323驱动第三齿轮 343 形成第七档输出。
当变速箱要由第七档升档为第八档时， 第三调速器 23受动力机构控制的拨叉的操作 而啮合， 同时第二调速器 22受拨叉操作而分离， 与六档齿轮 313的犬齿侧啮合的第二同 步器 316 的齿套 3161， 受动力机构控制的拨叉的操作向后移动与六档齿轮的犬齿侧分 离， 进而与设置于九档齿轮 314的犬齿侧啮合， 此时引擎的动力经由输入轴 110及驱动 齿轮 11传递至第三调速器 23的输出件及第三驱动轴 330， 再由八档齿轮 333驱动第三 齿轮 343形成第八档输出。
当变速箱要由第八档升档为第九档时， 第一调速器 21受动力机构控制的拨叉的操作 而啮合， 同时第三调速器 23受拨叉操作而分离， 与七档齿轮 323的犬齿侧啮合的第四同 步器 326的齿套受拨叉操作向后移动与七档齿轮 323的犬齿侧分离， 进而与设置于十档 齿轮 324的犬齿侧啮合， 此时引擎的动力经由输入轴 110及驱动齿轮 11传递至第一调速 器 21的输出件 212及第一驱动轴 310， 再由九档齿轮 314驱动第四齿轮 344形成第九档 输出。
当变速箱要由第九档升档为第十档时， 第二调速器 22受动力机构控制的拨叉的操作 而啮合， 同时第一调速器 21受拨叉的操作而分离， 与八档齿轮 333的犬齿侧啮合的第六 同步器 336的齿套受拨叉操作向后移动与八档齿轮 333的犬齿侧分离， 进而与设置于十 一档齿轮 334的犬齿侧啮合， 此时引擎的动力经由输入轴 110及驱动齿轮 11传递至第二 调速器 22的输出件及第二驱动轴 320， 再由十档齿轮 324驱动第四齿轮 44形成第十档 输出。 当变速箱要由第十档升档为第十一档时， 第三调速器 23受动力机构控制的拨叉的操 作而啮合， 同时第二调速器 22受拨叉操作而分离， 此时引擎的动力经由输入轴 110及驱 动齿轮 11传递至第三器 23的输出件及第三驱动轴 330， 再由十一档齿轮 334驱动第四 齿轮 344形成第十一档输出。
该第一调速器 21中， 齿套 215的连续波状齿槽与输出件 212的连续波状凸齿两者的 制作方式为： 绘制一所有波峰与波谷均为相同半径的环型波状线； 以该环型波状线为中 心向两侧等距平移后绘制两环型波状线； 以该两新绘的环型波状线为基准制作该环型连 续波状齿槽与凸齿； 该环型连续波状齿槽 2151与凸齿 2121所有平面的交线均以相同的 半径作圆角处理。
该第一调速器 21中， 滚轮组 214的组装方式为： 该第二盘体 2142的中空圆柱外侧 套入该弹簧 2143;
该第二盘体 2142的中空圆柱由该支架 213靠近动力输出的侧面套入该支架 213通孔 内的轴承 2131， 该轴承 2131需使该第二盘体 2142的中空圆柱可于该轴承 2131 内作轴 向的前后移动； 第一盘体 2141的圆柱由该支架 213的另一侧面套入该第二盘体 2142的 中空圆柱； 该第一盘体 2141的圆柱凸出于该第二盘体 2142另一侧面处扣设一扣环。
于本发明中， 通过将第一驱动轴 310、 第二驱动轴 320及第三驱动轴 330以该输出 轴 340为中心环绕该输出轴 340而成不等轴距的平行排列， 并于各驱动轴上设置各档位 齿轮及同步器， 从而达成于有限空间内增加动力传递档位数的功效； 图 5至图 7中， 由 于该滚轮组 214牵引驱动力的大小是与该滚轮组 214与该输入件 211及该输出件 212间 压合点的压力大小成正比， 因此通过控制受动力机构控制的拨叉 F施加于该第一调速器 21的输出件 212的压力大小， 使本发明的变速箱可在低速起步或上坡状态时提供车辆平 顺的蠕行功能， 而不会造成该调速器室 20内的各调速器组件过度磨耗， 从而避免现有技 术中离合器片因频繁或不当操作造成过热磨损的问题发生； 于图 3 中， 由于该齿套 215 形成该连续波状齿槽 2151的侧面及该输出件 212的连续波状凸齿 2121的端面均为垂直 于该第一轴 210的平面， 因此当该齿套 215形成该齿槽 2151的侧面与该输出件 212的凸 齿 2121的端面接触时， 形成面与面的平滑接触， 同时， 由于该凸齿 2121的端面与侧壁 的交接处是倒圆角， 以便于该凸齿 2121 啮合该齿槽 2151， 在该输出件 212受拨叉施 压， 并且该输入件 211及该输出件 212处于旋转的状态下， 因而使该凸齿 2121得以通过 该输入件 211 与该输出件 212 的转速差滑入该齿槽 2151， 故在该凸齿 2121 与该齿槽 2151啮合的过程中， 无需降低过多该输入件 211的转数， 即可完成动力的传递， 从而避 免产生如现有技术中犬齿式同步器接触时的齿轮撞击声； 于图 8至 10中， 第三档、 第四 档及第五档齿轮的犬齿侧分别为第一同步器的齿套 3151、 第三同步器的齿套 3251及第 五同步器的齿套 3351所啮合， 因此本发明的变速箱可通过控制第一调速器 21、 第二调 速器 22及第三调速器 23的离合而迅速的由第三档升档至第五档； 由于本发明的变速箱 除第一档及第十一档外， 其余的各档位其相邻前后两档位的犬齿式同步器均已预先啮 合， 因此在升档的过程中如果遇到突发状况需立刻降档时， 可通过控制第一调速器 21、 第二调速器 22及第三调速器 23 的离合而迅速降档； 当变速箱为倒档时， 第一同步器 315的齿套 3151受动力机构控制的拨叉的操作向该变速齿轮室 30的前端移动以啮合倒 档齿轮 311的犬齿侧， 同时第一调速器 21受动力机构控制的拨叉 F的操作而啮合， 此时 引擎 10的动力经由输入轴 110及驱动齿轮 11传递至第一调速器 21的输出件 212及第一驱 动轴 310， 经由倒档齿轮 311驱动怠轮 351， 再由怠轮 351驱动输出轴 340的第一齿轮 341 形成倒档输出； 本发明所提及的拨叉是现有技术中附加液压或电力致动器的拨叉机构。
以上所述仅是本发明的较佳实施例而已， 并非对本发明做任何形式上的限制， 虽然 本发明已以较佳实施例揭露如上， 然而并非用以限定本发明， 任何熟悉本专业的技术人 员， 在不脱离本发明技术方案的范围内， 当可利用上述揭示的技术内容作出些许更动或 修饰为等同变化的等效实施例， 但凡是未脱离本发明技术方案的内容， 依据本发明的技 术实质对以上实施例所作的任何简单修改、 等同变化与修饰， 均仍属于本发明技术方案 的范围内。

Claims

权利要求书
1.一种牵引驱动同步调速器， 其连接于一为动力输出的驱动轴， 其特征在于： 所述 牵引驱动同步调速器具有一轴、 一输入件、 一输出件、 一支架、 至少三滚轮组及一齿套； 所述输入件为一齿轮， 所述齿轮中央具有一穿孔并于一侧面凹陷形成凹槽， 所述凹 槽与所述侧面的交接处形成一倾斜面， 所述齿轮邻近所述凹槽的环壁面朝所述凹槽凹陷 形成一环座， 所述环座外环壁面设有凸齿； 所述输入件的中央穿孔套设于所述轴；
所述齿套为一中空环体， 所述中空环体一侧面凹陷形成一齿槽， 所述齿槽是一连续 波状且波峰及波谷均具有相同的半径， 所述齿套内环壁面设有齿槽， 所述齿套的齿槽套 设于所述输入件的环座的凸齿， 两者之间可轴向位移；
所述输出件为一圆盘体， 所述圆盘体中央具有一穿孔并于一侧面凹陷形成凹槽， 所 述输出件的凹槽与所述圆盘体侧面的交接处形成一倾斜面， 所述圆盘体邻近所述输出件 的凹槽的侧面凸伸形成一连续波状凸齿， 所述圆盘体的中央穿孔于远离所述输出件的凹 槽的侧面凸伸形成一套部， 所述穿孔及套部的内缘壁面形成齿槽； 所述输出件与所述输 入件相对应设置， 所述输出件的连续波状凸齿与所述齿套的连续波状齿槽相对应； 所述 输出件的穿孔及套部连接于所述驱动轴， 所述输出件可相对于所述驱动轴轴向位移； 所述支架为一圆盘体， 所述支架中央具有一穿孔， 所述支架贯穿成形至少三个通 孔， 所述通孔呈行星式环绕中央的所述穿孔， 并于所述通孔内缘装设轴承， 所述支架的 中央穿孔套设于所述轴；
所述滚轮组承设于所述支架的通孔的轴承。
2.根据权利要求 1所述的牵引驱动同步调速器， 其特征在于， 所述滚轮组具有一第 一盘体、 一第二盘体及一弹簧；
所述第一盘体为一圆盘体， 所述第一盘体中央凸伸形成一圆柱；
所述第二盘体为一圆盘体， 所述第二盘体中央凸伸形成一圆柱， 并且于所述第二盘 体的圆柱中心贯穿成形一贯孔；
所述第二盘体的圆柱外环壁面套设所述弹簧并承设于所述支架的通孔的轴承， 所述 第一盘体的圆柱穿设所述第二盘体圆柱的贯孔并与所述第二盘体固设， 所述弹簧两端抵顶 在支架与第二盘体之间， 使所述第二盘体远离所述支架， 而所述第一盘体抵靠所述支架。
3.一种具有根据权利要求 1至 2中任一项所述的牵引驱动同步调速器的多驱动轴变 速箱， 其特征在于， 所述多驱动轴变速箱具有一调速器室及一变速齿轮室； 所述调速器室邻近一引擎， 所述调速器室具有一结合于所述引擎的输入轴的驱动齿 轮及至少两个调速器； 所述调速器的轴一端固设于所述调速器室的内缘壁面上， 各轴以 所述引擎的输入轴为中心环绕设置成等轴距的平行排列， 所述驱动齿轮啮合所述调速器 的输入件；
所述变速齿轮室具有至少两个驱动组、 一输出组及一倒档怠轮组， 所述变速齿轮室 连接于所述调速器室远离所述引擎的一端；
所述输出组具有一轴及至少三齿轮； 所述输出组的轴置设于所述变速齿轮室， 所述 输出组的齿轮设置于所述输出组的轴上；
所述驱动组具有一轴、 至少三齿轮及至少两个同步器； 所述驱动组的轴外环壁面形 成凸齿， 所述驱动组的轴穿设所述变速齿轮室至所述调速器室内， 并与相应的调速器连 结， 所述驱动组的轴的凸齿穿设于所述调速器的输出件中央穿孔及套部的齿槽， 所述驱 动组的轴以所述输出组的轴为中心环绕所述输出组的轴成不等轴距的平行排列； 所述驱 动组的齿轮及所述同步器交错排列的设置在所述驱动组的轴上； 各驱动组的齿轮分别与 所述输出组的齿轮相对应啮合；
所述倒档怠轮组具有一怠轮轴及一怠轮； 所述怠轮轴一端固设于所述变速齿轮室邻 近所述调速器室之端， 所述怠轮设置于所述怠轮轴上， 并同时啮合所述驱动组及所述输 出组的相应齿轮； 所述怠轮轴与所述输出轴平行排列。
4.根据权利要求 3所述的多驱动轴变速箱， 其特征在于， 所述调速器室具有三调速 器， 分别为第一调速器、 第二调速器及第三调速器；
所述变速齿轮室具有三驱动组， 分别为第一驱动组、 第二驱动组及第三驱动组； 所述第一驱动组的轴连接所述第一调速器， 所述第二驱动组的轴连接所述第二调速 器， 所述第三驱动组的轴连接所述第三调速器；
所述输出组具有第一齿轮、 第二齿轮、 第三齿轮及第四齿轮， 所述第一齿轮、 第二 齿轮、 第三齿轮及第四齿轮依序设置于所述输出组的轴上；
所述第一驱动组轴上的设置依序为倒档齿轮、 第一同步器、 三档齿轮、 六档齿轮、 第二同步器及九档齿轮；
所述第二驱动组轴上的设置依序为一档齿轮、 第三同步器、 四档齿轮、 七档齿轮、 第四同步器及十档齿轮；
所述第三驱动组轴上的设置依序为二档齿轮、 第五同步器、 五档齿轮、 八档齿轮、 第六同步器及 ^一档齿轮； 所述第一齿轮同时啮合所述倒档齿轮、 一档齿轮及二档齿轮， 所述第二齿轮同时啮 合上述三档齿轮、 四档齿轮及五档齿轮， 所述第三齿轮同时啮合所述六档齿轮、 七档齿 轮及八档齿轮， 所述第四齿轮同时啮合所述九档齿轮、 十档齿轮及十一档齿轮；
所述怠轮同时啮合所述第一驱动组的倒档齿轮及所述输出组的第一齿轮。
5.根据权利要求 3至 4任一项所述的多驱动轴变速箱， 所述变速箱外具有一轮轴， 其特征在于： 所述变速齿轮室具有一差速器；
所述差速器具有一主动齿轮及一从动齿轮， 所述主动齿轮设置于所述输出组的轴 上， 所述从动齿轮设置于所述变速箱外的轮轴上， 所述主动齿轮啮合所述从动齿轮， 所 述轮轴与所述输出组的轴呈平行排列。
6.根据权利要求 3至 4任一项所述的多驱动轴变速箱， 所述变速箱外具有一轮轴， 其特征在于： 所述变速齿轮室具有一差速器；
所述差速器具有一主动齿轮及一从动齿轮， 所述主动齿轮设置于所述变速齿轮室外 的输出组的轴上， 所述从动齿轮设置于所述变速箱外的轮轴上， 所述主动齿轮啮合所述 从动齿轮， 所述轮轴与所述输出组的轴呈垂直排列。
7.根据权利要求 4所述的多驱动轴变速箱， 其特征在于， 所述调速器齿套的外环壁 面凹陷形成一用以容设拨叉的凹槽；
所述调速器的输出件的套部凹陷形成一用以容设拨叉的凹槽。
8.根据权利要求 2所述的牵引驱动同步调速器， 其特征在于，
所述齿套的连续波状齿槽与输出件的连续波状凸齿两者的制作方式为：
绘制一所有波峰与波谷均为相同半径的环型波状线；
以所述环型波状线为中心向两侧等距平移后绘制两环型波状线；
以两新绘的所述环型波状线为基准制作所述环型连续波状齿槽与凸齿；
所述环型连续波状齿槽与凸齿所有平面的交线均以相同的半径作圆角处理。
9.根据权利要求 2所述的牵引驱动同步调速器， 其特征在于， 所述滚轮组的组装方 式为：
所述第二盘体的中空圆柱外侧套入所述弹簧；
所述第二盘体的中空圆柱由所述支架靠近动力输出的侧面套入所述支架通孔内的轴 承， 所述轴承需使所述第二盘体的中空圆柱可于所述轴承内作轴向的前后移动；
第一盘体的圆柱由所述支架的另一侧面套入所述第二盘体的中空圆柱；
所述第一盘体的圆柱凸出于所述第二盘体另一侧面处扣设一扣环。
PCT/CN2014/079579 2014-06-10 2014-06-10 牵引驱动同步调速器及具有该调速器的多驱动轴变速箱 WO2015188312A1 (zh)

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