CN113719591A - Distance-reducing type multi-reverse gear transmission mechanism - Google Patents

Distance-reducing type multi-reverse gear transmission mechanism Download PDF

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Publication number
CN113719591A
CN113719591A CN202111062149.9A CN202111062149A CN113719591A CN 113719591 A CN113719591 A CN 113719591A CN 202111062149 A CN202111062149 A CN 202111062149A CN 113719591 A CN113719591 A CN 113719591A
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CN
China
Prior art keywords
planet
planet row
gear
row
gears
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Pending
Application number
CN202111062149.9A
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Chinese (zh)
Inventor
邱文刚
张正富
田海勇
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Guizhou Winstar Hydraulic Transmission Machinery Co Ltd
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Guizhou Winstar Hydraulic Transmission Machinery Co Ltd
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Publication date
Application filed by Guizhou Winstar Hydraulic Transmission Machinery Co Ltd filed Critical Guizhou Winstar Hydraulic Transmission Machinery Co Ltd
Priority to CN202111062149.9A priority Critical patent/CN113719591A/en
Publication of CN113719591A publication Critical patent/CN113719591A/en
Pending legal-status Critical Current

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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
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/62—Gearings having three or more central gears
    • F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H57/023—Mounting or installation of gears or shafts in the gearboxes, e.g. methods or means for assembly
    • 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
    • F16H57/08—General details of gearing of gearings 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
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H2057/02039—Gearboxes for particular applications
    • F16H2057/02043—Gearboxes for particular applications for vehicle transmissions
    • F16H2057/02056—Gearboxes for particular applications for vehicle transmissions for utility vehicles, e.g. tractors or agricultural machines
    • 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
    • F16H2057/02086—Measures for reducing size of gearbox, e.g. for creating a more compact transmission casing
    • 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
    • F16H2057/02091—Measures for reducing weight of gearbox
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0052—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising six forward speeds
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/0082—Transmissions for multiple ratios characterised by the number of reverse speeds
    • F16H2200/0091—Transmissions for multiple ratios characterised by the number of reverse speeds the gear ratios comprising three reverse speeds
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
    • F16H2200/2012—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with four sets of orbital gears
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
    • F16H2200/2046—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with six engaging means

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

Abstract

The invention provides a distance-reducing type multi-reverse gear transmission mechanism which comprises an input shaft, a front output shaft, a rear output shaft, a middle shaft, a planet row P1, a planet row P2, a planet row P3 and a planet row P4, wherein a planet row P1 sun gear, a planet row P2 sun gear and a planet row P3 sun gear are connected in parallel and then connected with the input shaft, a planet row P1 planet carrier is connected with a planet row P2 gear ring through a spline, a planet row P2 planet carrier, a planet row P4 sun gear and a planet row P3 gear ring are respectively connected with the spline, the planet row P3 planet carrier is also connected with a planet row P4 gear ring in parallel and then connected to one end of the middle shaft, the other end of the middle shaft is sequentially meshed with a plurality of gears in series, and the front output shaft and the rear output shaft are respectively connected with the last gear. By adopting the technical scheme of the invention, the large bearing capacity of the inner gear and the whole available space of the inner gear ring can be fully utilized, so that the structure is more compact, the transmission ratio is large, and the invention has the advantages of stable motion, strong impact resistance and vibration resistance and the like.

Description

Distance-reducing type multi-reverse gear transmission mechanism
Technical Field
The invention belongs to the technical field of transmission mechanisms, and particularly relates to a distance-reducing type multi-reverse gear transmission mechanism.
Background
At present, a speed change mechanism is widely applied to various vehicles and machine tools, the speed change mechanism enables important parts in the mechanical equipment, along with the development of technology, the speed change gear positions of the existing speed change mechanism are more and more, however, along with the continuous increase of the gear number, the number of the parts in the speed change mechanism is inevitably increased, the structure of the speed change mechanism is more and more complicated, the size is more and more large, the weight is more and more heavy, the requirement of people on the control flexibility of engineering machinery such as forklifts, cranes, bulldozers and the like is higher and more, correspondingly, the requirement on the gear number is more and more, the power input and the power output of the existing speed change mechanism are not at the same height and have the distance reduction requirement, the speed change mechanism has the front and back output functions, the speed changer also ensures that the forklifts have higher power and economy, the axial size is required to be as small as possible, the transmission efficiency is high, no noise and the like, and the fixed-axis structure is commonly used in China at present, however, the fixed shaft type speed change mechanism has larger volume, heavy weight, is mostly imported and has high cost, thereby increasing the production cost.
Disclosure of Invention
In order to solve the technical problem, the invention provides a distance-reducing type multi-reverse gear transmission mechanism.
The invention is realized by the following technical scheme.
The invention provides a distance-reducing type multi-reverse gear transmission mechanism which comprises an input shaft, a front output shaft, a rear output shaft, a middle shaft, a planet row P1, a planet row P2, a planet row P3 and a planet row P4, wherein the planet row P1, the planet row P2, the planet row P3 and the planet row P4 respectively comprise a sun gear, planet wheels meshed with the corresponding sun gear, a planet carrier connecting all the planet wheels in the planet row together and a gear ring meshed with the corresponding planet wheels, the sun gear of the planet row P1, the sun gear of the planet row P2 and the sun gear of the planet row P3 are connected with the input shaft after being connected in parallel, the planet carrier of the planet row P1 is connected with the gear ring of the planet row P2 through splines, the planet carrier of the planet row P2, the sun gear of the planet row P4 and the gear ring of the planet row P3 are respectively connected with the splines, the planet carrier of the planet row P3 is also connected with the P4 in parallel and then connected with one end of the middle shaft, the other end of the intermediate shaft is sequentially meshed with a plurality of gears in series, and the front output shaft and the rear output shaft are respectively connected to the last gear.
The sun gear of the planetary row P2 and the sun gear of the planetary row P3 are connected in parallel, then are connected with the C1 clutch in series, and then are connected to the input shaft.
The sun gear of the planetary row P1 is connected in parallel with the planet carrier of the planetary row P2, then connected in series with the C2 clutch, and then connected to the input shaft.
The ring gear of the planet row P1 is also connected with a C3 brake.
The ring gear of the planet row P2 is also connected with a C4 brake.
The ring gear of the planet row P3 is also connected with a C5 brake.
The planet carrier of the planet row P4 is also connected with a C6 brake.
The planet carrier of the planet row P3 is connected with the ring gear of the planet row P4 in parallel and then is connected with the intermediate shaft through a spline.
The intermediate shaft is connected with the gear through a spline.
The invention has the beneficial effects that: by adopting the technical scheme of the invention, the planetary gear type speed change mechanism is adopted, parts in the speed change mechanism are meshed together in an inner meshing mode as much as possible, the planetary gear type speed change mechanism has the advantages of compact structure, small volume, light weight and the like, in addition, the planetary gear type speed change mechanism also has the transmission characteristics of planetary motion and power split, the large bearing capacity of inner meshing teeth and the whole available space of an inner gear ring can be fully utilized, the structure is more compact, the transmission ratio is large, the planetary gear type speed change mechanism has the advantages of stable motion, strong impact resistance and vibration resistance and the like, the planetary gear is specially arranged and combined, the control is carried out through a plurality of hydraulic clutches or hydraulic brakes, the speed change mechanism can output a plurality of forward gears and reverse gears, the impact during gear shifting is relieved, and different gears can be selected according to needs.
Drawings
Fig. 1 is a schematic structural view of the present invention.
In the figure: 1-C1 clutch, 2-C2 clutch, 3-planet row P1 sun gear, 4-planet row P1 planet carrier, 5-planet row P1 ring gear, 6-C3 brake, 7-planet row P2 ring gear, 8-C4 brake, 9-planet row P2 planet carrier, 10-C5 brake, 11-planet row P3 ring gear, 12-C6 brake, 13-planet row P4 planet carrier, 14-planet row P4 ring gear, 15-planet row P4 sun gear, 16-countershaft, 17-gear, 20-rear output shaft, 21-front output shaft, 22-planet row P3 planet carrier, 23-planet row P3 sun gear, 24-planet row P2 sun gear, 25-input shaft.
Detailed Description
The technical solution of the present invention is further described below, but the scope of the claimed invention is not limited to the described.
As shown in FIG. 1, the invention provides a distance-reducing type multi-reverse gear transmission mechanism, which comprises an input shaft 25, a front output shaft 21, a rear output shaft 20, an intermediate shaft 16, a planet row P1, a planet row P2, a planet row P3 and a planet row P4, wherein each of the planet row P1, the planet row P2, the planet row P3 and the planet row P4 comprises a sun gear, planet wheels meshed with the corresponding sun gear, a planet carrier connecting all the planet wheels in the planet row together and a ring gear meshed with the corresponding planet wheels, the sun gear 3, the sun gear 24 and the sun gear 23 of the planet row P1 are connected with the input shaft 25 in parallel, the planet carrier 4 of the planet row P1 is connected with the ring gear 7 of the planet row P2 through splines, the planet carrier P2, the sun gear 15 and the planet row P3 are connected with the ring gear 11 through the intermediate shaft, the planet carrier P3 is also connected with the ring gear 14 in parallel and connected with one end of the ring gear 59616, the other end of the intermediate shaft 16 is sequentially engaged with a plurality of gears 17 in series, and a front output shaft 21 and a rear output shaft 20 are respectively connected to the last gear 17.
Further, the sun gear 24 of the planetary row P2 is connected in parallel with the sun gear 23 of the planetary row P3, then connected in series with the C1 clutch 1, and then connected to the input shaft 25. The sun gear 3 of the planetary row P1 is also connected in parallel with the planet carrier 9 of the planetary row P2, then in series with the C2 clutch 2, and then on to the input shaft 25.
In addition, the ring gear 5 of the planet row P1 is also connected with a C3 brake 6. The planet row P2 ring gear 7 is also connected with a C4 brake 8. The planet row P3 ring gear 11 is also connected with the C5 brake 10. The planet carrier 13 of the row P4 is also connected to the C6 brake 12. The planet carrier 22 of the planet row P3 is connected with the ring gear 14 of the planet row P4 in parallel and then connected with the intermediate shaft 16 through a spline. The number of the gears 17 is 3. The intermediate shaft 16 is splined to the gear 17. The front output shaft 21 and the rear output shaft 20 are connected to the gear 17 by splines, respectively.
So that the sun gear 3 of the planet row P1 drives the planet gears in the planet carrier 4 of the planet row P1, and the planet gears in the planet carrier 4 of the planet row P1 drive the ring gear 5 of the planet row P1; the sun gear 24 of the planet row P2 drives the planet gears in the planet carrier 9 of the planet row P2, and then the planet gears in the planet carrier 9 of the planet row P2 drive the ring gear 7 of the planet row P2; the sun gear 23 of the planet row P3 drives the planet gears in the planet carrier 22 of the planet row P3, and then the planet gears in the planet carrier 22 of the planet row P3 drive the sun gear 15 of the planet row P4; the sun gear 15 of the planet row P4 drives the planet gears in the planet carrier of the planet row P4, and the planet gears in the planet carrier of the planet row P4 drive the ring gear of the planet row P4.
By adopting the technical scheme of the invention, the planetary gear type speed change mechanism is adopted, parts in the speed change mechanism are meshed together in an inner meshing mode as much as possible, the planetary gear type speed change mechanism has the advantages of compact structure, small volume, light weight and the like, in addition, the planetary gear type speed change mechanism also has the transmission characteristics of planetary motion and power split, the large bearing capacity of inner meshing teeth and the whole available space of an inner gear ring can be fully utilized, the structure is more compact, the transmission ratio is large, the planetary gear type speed change mechanism has the advantages of stable motion, strong impact resistance and vibration resistance and the like, the planetary gear is specially arranged and combined, the control is carried out through a plurality of hydraulic clutches or hydraulic brakes, the speed change mechanism can output a plurality of forward gears and reverse gears, the impact during gear shifting is relieved, and different gears can be selected according to needs.
By adopting the technical scheme of the invention, the gear shifting operation process is as follows:
neutral gear: the C1 clutch 1 is engaged, the other clutches and brake are not engaged, and no power output is provided, i.e., neutral.
1, gear 1: the C1 clutch 1 is connected, the C6 brake 12 is connected, the C1 clutch 1 is connected, the planet row P3 sun gear 23 is driven to rotate together, the planet row P3 sun gear 23 drives the planet wheels in the planet row P3 planet carrier 22 to rotate, the planet wheels in the planet row P3 planet carrier 22 drive the planet row P3 ring gear 11 to rotate, the planet row P3 ring gear 11 drives the planet row P4 sun gear 15 to rotate together, and the planet row P4 sun gear 15 drives the planet wheels in the planet carrier 13 of the planet row P4 to rotate.
The C6 brake 12 is combined, the planet carrier 13 of the planet row P4 is fixed, the planet wheel in the planet carrier 13 of the planet row P4 drives the ring gear 14 of the planet row P4 to rotate, the ring gear 14 of the planet row P4 drives the intermediate shaft 16 and the gear 17 to rotate together, and after the meshing transmission of the plurality of gears 17, the rear output shaft 20 and the front output shaft 21 are driven to rotate together, so that the 1 gear is realized.
2, gear; the C1 clutch 1 is combined, the C5 brake 10 is combined, the C1 clutch 1 is combined to drive the P3 sun gear 23 of the planet row to rotate together, the P3 sun gear 23 of the planet row drives the planet gears in the P3 planet carrier 22 to rotate, the C5 brake 10 is combined to fix the P3 gear ring 11 of the planet row, the planet gears in the P3 planet carrier 22 of the planet row drive the P3 planet carrier 22 of the planet row to rotate, the P3 planet carrier 22 of the planet row drives the intermediate shaft 16 and the gear 17 to rotate together, and finally the rear output shaft 20 and the front output shaft 21 are driven to rotate together after meshing transmission of the gears 17, so that the 2-gear is realized.
3, gear; the C1 clutch 1 is engaged and the C4 brake 8 is engaged. The C1 clutch 1 is combined to drive the sun gear 24 of the planet row P2 and the sun gear 23 of the planet row P3 to rotate together, and the sun gear 24 of the planet row P2 drives the planet gears in the planet carrier 9 of the planet row P2 to rotate.
The C4 brake 8 is combined to fix the gear ring 7 of the planet row P2, the planet row P2 planet carrier 9 is driven to rotate by the planet wheels in the planet carrier 9 of the planet row P2, the planet carrier 9 of the planet row P2 drives the gear ring 11 of the planet row P3 to rotate together, due to the difference of the rotating speeds between the gear ring 11 of the planet row P3 and the sun wheel 23 of the planet row P3, the planet carrier 22 of the planet row P3 is driven to rotate by the planet wheels, the planet carrier 22 of the planet row P3 drives the intermediate shaft 16 and the gear 17 to rotate together, and finally the rear output shaft 20 and the front output shaft 21 are driven to rotate together after being meshed with a plurality of gears 17, so that the 3-gear is realized.
4, gear shifting; the C1 clutch 1 is engaged, the C3 brake 6 is engaged, the C1 clutch 1 is engaged to drive the sun gear 3 of the planet row P1, the sun gear 24 of the planet row P2 and the sun gear 23 of the planet row P3 to rotate together, the sun gear 3 of the planet row P1 drives the planet gears in the planet carrier 4 of the planet row P1 to rotate, the C3 brake 6 is engaged to fix the ring gear 5 of the planet row P1, the planet carrier 4 of the planet row P1 drives the planet carrier 4 of the planet row P1 to rotate, and the planet carrier 4 of the planet row P1 drives the ring gear 7 of the planet row P2 to rotate together.
The sun gear 24 of the planet row P2 drives the planet gears in the planet carrier 9 of the planet row P2 to rotate, and due to the rotation speed difference between the ring gear 7 of the planet row P2 and the sun gear 24 of the planet row P2, the planet carrier 9 of the planet row P2 is red by the planet gears in the planet carrier 9 of the planet row P2, and the planet carrier 9 of the planet row P2 drives the ring gear 11 of the planet row P3 to rotate together.
The sun gear 23 of the planet row P3 drives the planet in the planet carrier 22 of the serial planet row P3 to rotate, and due to the difference of the rotating speeds between the ring gear 11 of the planet row P3 and the sun gear 23 of the planet row P3, the planet carrier 22 of the planet row P3 in the planet carrier 22 of the planet row P3 rotates, and the planet carrier 22 of the planet row P3 drives the intermediate shaft 16 and the gear 17 to rotate together, and finally drives the rear output shaft 20 and the front output shaft 21 to rotate together after being meshed and transmitted by a plurality of gears 17, so that the 4-gear is realized.
5, gear; the C1 clutch 1 is combined, the C2 clutch 2 is combined, the C1 clutch 1 and the C2 clutch 2 are combined to drive the planet carrier 9 of the planet row P2, the ring gear 11 of the planet row P3 and the sun gear 23 of the planet row P3 to rotate together, the planet carrier 22 of the planet row P3 rotates at the same speed, the planet carrier 22 of the planet row P3 drives the intermediate shaft 16 and the gear 17 to rotate together, and finally the rear output shaft 20 and the front output shaft 21 are driven to rotate together after meshing transmission of a plurality of gears 17, so that 5-gear is realized.
6, gear; the C2 clutch 2 is combined, the C3 brake 6 is combined, the C2 clutch 2 is combined to drive the planet row P2 planet carrier 9 and the planet row P3 ring gear 11 to rotate together, the C3 brake 6 is combined, the planet row P1 ring gear 5 is fixed, the planet row P1 sun gear 3 drives the planet wheels in the planet row P1 planet carrier 4 to rotate, the planet wheels in the planet row P1 planet carrier 4 drive the planet row P1 planet carrier 4 to rotate, the planet row P1 planet carrier 4 drives the planet row P2 ring gear 7 to rotate together, and the planet row P2 sun gear 24 is driven to rotate and drives the planet row P3 sun gear 23 to rotate together due to the differential between the planet row P2 ring gear 7 and the planet row P2 planet carrier 9.
Due to the differential motion between the gear ring 11 of the planet row P3 and the sun gear 23 of the planet row P3, the gear ring 11 of the planet row P3 drives the planet gears in the planet carrier 22 of the planet row P3 to rotate, the planet carrier 22 of the planet row P3 is driven to rotate, the planet carrier 22 of the planet row P3 drives the intermediate shaft 16 and the gear 17 to rotate together, and after meshing transmission of a plurality of gears 17, the rear output shaft 20 and the front output shaft 21 are driven to rotate together finally, so that the 6-gear is realized.
6, gear; the C2 clutch 2 is combined, the C4 brake 8 is combined, the C2 clutch 2 is combined to drive the planet carrier 9 and 11 of the planet row P2 to rotate together, the C4 brake 8 is combined, the ring gear 7 of the planet row P2 is fixed, the planet carrier 9 of the planet row P2 is rotated to drive the planet wheels in the planet carrier 9 of the planet row P2 to rotate, the planet wheels in the planet carrier 9 of the planet row P2 drive the sun gear 24 of the planet row P2 to rotate, and the sun gear 23 of the planet row P3 is driven to rotate together.
Due to the differential motion between the gear ring 11 of the planet row P3 and the sun gear 23 of the planet row P3, the gear ring 11 of the planet row P3 drives the planet gears in the planet carrier 22 of the planet row P3 to rotate, the planet carrier 22 of the planet row P3 is driven to rotate, the planet carrier 22 of the planet row P3 drives the intermediate shaft 16 and the gear 17 to rotate together, and after meshing transmission of a plurality of gears 17, the rear output shaft 20 and the front output shaft 21 are driven to rotate together finally, so that the gear 7 is realized.
Reverse gear 1; the C3 brake 6 is combined, the C5 brake 10 is combined, the C3 brake 6 is combined, the planet row P1 gear ring 5 is fixed, the planet row P1 sun gear 3 drives the planet wheels in the planet carrier 4 of the planet row P1 to rotate, the planet wheels in the planet carrier 4 of the planet row P1 drive the planet carrier 4 of the planet row P1 to rotate, and the planet carrier 4 of the planet row P1 drives the planet carrier 7 of the planet row P2 to rotate together.
The planet row P2 gear ring 7 drives the planet wheels in the planet carrier 9 of the planet row P2 to rotate and drives the planet carrier 9 of the planet row P2 to rotate, the planet carrier 9 of the planet row P2 drives the planet row P3 gear ring 11 to rotate together, the planet wheel in the planet carrier 9 of the planet row P2 drives the sun gear 24 of the planet row P2 to rotate reversely, and the sun gear 24 of the planet row P2 drives the sun gear 23 of the planet row P3 to rotate together.
Due to the differential motion between the sun gear 23 of the planet row P3 and the gear ring 11 of the planet row P3, the planet carrier 22 of the planet row P3 rotates reversely, the planet carrier 22 of the planet row P3 drives the intermediate shaft 16 and the gear 17 to rotate together, and finally drives the rear output shaft 20 and the front output shaft 21 to rotate together after meshing transmission of the gears 17, so that the reverse gear 1 is realized.
Reverse gear 2; the C2 clutch 2 is combined, the C6 brake 12 is combined, the C6 brake 12 is combined, the planet carrier 13 of the planet row P4 is fixed, the C2 clutch 2 is combined to drive the planet carrier 9, 11 and 15 of the planet row P2 to rotate together, the sun gear 15 of the planet row P4 drives the planet gears in the planet carrier 13 of the planet row P4 to rotate in the reverse direction, the planet gears in the planet carrier 13 of the planet row P4 drive the planet gear ring 14 of the planet row P4 to rotate in the same direction, the planet gear ring 14 of the planet row P4 drives the intermediate shaft 16 and the gear 17 to rotate together, and after meshing transmission through a plurality of gears 17, the rear output shaft 20 and the front output shaft 21 are finally driven to rotate together, so that the reverse gear 2 is realized.
A reverse gear 3; the C3 brake 6 is combined, the C6 brake 12 is combined, the C3 brake 6 is combined, a planet row P1 gear ring 5 is fixed, a planet row P1 sun gear 3 drives planet wheels in a planet row P1 planet carrier 4 to rotate, planet wheels in a planet row P1 planet carrier 4 drive a planet row P1 planet carrier 4 to rotate, a planet row P1 planet carrier 4 drives a planet row P2 gear ring 7 to rotate together, a planet row P2 gear ring 7 drives planet wheels in a planet carrier 9 of a planet row P2 to rotate in the same direction, planet wheels in a planet carrier 9 of a planet row P2 simultaneously drive a planet carrier 9 of a planet row P2 to rotate, and the planet carrier 9 of the planet row P2 drives a planet row P3 gear ring 11 and a planet row P4 sun gear 15 to rotate together.
The C6 brake 12 is combined, the planet carrier 13 of the planet row P4 is fixed, the sun gear 15 of the planet row P4 drives the planet gears in the planet carrier 13 of the planet row P4 to rotate, the planet gears in the planet carrier 13 of the planet row P4 drive the ring gear 14 of the planet row P4 to rotate reversely, the ring gear 14 of the planet row P4 drives the intermediate shaft 16 and the gear 17 to rotate together, and finally the rear output shaft 20 and the front output shaft 21 are driven to rotate together after meshing transmission of a plurality of gears 17, so that the reverse gear 3 is realized.

Claims (9)

1. A distance-reducing type multi-reverse gear transmission mechanism comprises an input shaft (25), a front output shaft (21), a rear output shaft (20), an intermediate shaft (16), a planet row P1, a planet row P2, a planet row P3 and a planet row P4, wherein the planet row P1, the planet row P2, the planet row P3 and the planet row P4 respectively comprise sun gears, planet gears meshed with the corresponding sun gears, planet carriers connecting all the planet gears in the planet row together and ring gears meshed with the corresponding planet gears, the planet row P1 sun gears (3), the planet row P2 sun gears (24) and the planet row P3 sun gears (23) are connected with the input shaft (25) after being connected in parallel, the planet carrier (4) of the planet row P1 is connected with the ring gears (7) of the planet row P2 through splines, the planet carrier (9) of the planet row P4 sun gears (15) and the ring gears (11) of the planet row P3 are respectively connected through splines, the planet carrier (22) of the planet row P3 is connected with the ring gear (14) of the planet row P4 in parallel and then connected to one end of the intermediate shaft (16), the other end of the intermediate shaft (16) is sequentially meshed with a plurality of gears (17) in series, and the front output shaft (21) and the rear output shaft (20) are respectively connected to the last gear (17).
2. The step-down multiple reverse drive mechanism of claim 1, wherein: the sun gear (24) of the planet row P2 is connected with the sun gear (23) of the planet row P3 in parallel, then is connected with the C1 clutch (1) in series, and then is connected to the input shaft (25).
3. The step-down multiple reverse drive mechanism of claim 1, wherein: the sun gear (3) of the planet row P1 is connected with the planet carrier (9) of the planet row P2 in parallel, then connected with the C2 clutch (2) in series, and then connected with the input shaft (25).
4. The step-down multiple reverse drive mechanism of claim 1, wherein: the ring gear (5) of the planet row P1 is also connected with a C3 brake (6).
5. The step-down multiple reverse drive mechanism of claim 1, wherein: the ring gear (7) of the planet row P2 is also connected with a C4 brake (8).
6. The step-down multiple reverse drive mechanism of claim 1, wherein: the planet row P3 is also connected with a C5 brake (10) through a ring gear (11).
7. The step-down multiple reverse drive mechanism of claim 1, wherein: the planet carrier (13) of the planet row P4 is also connected with a C6 brake (12).
8. The step-down multiple reverse drive mechanism of claim 1, wherein: the planet carrier (22) of the planet row P3 is connected with the ring gear (14) of the planet row P4 in parallel and then connected with the intermediate shaft (16) through a spline.
9. The step-down multiple reverse drive mechanism of claim 1, wherein: the intermediate shaft (16) is connected with the gear (17) through a spline.
CN202111062149.9A 2021-09-10 2021-09-10 Distance-reducing type multi-reverse gear transmission mechanism Pending CN113719591A (en)

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CN202111062149.9A CN113719591A (en) 2021-09-10 2021-09-10 Distance-reducing type multi-reverse gear transmission mechanism

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Application Number Priority Date Filing Date Title
CN202111062149.9A CN113719591A (en) 2021-09-10 2021-09-10 Distance-reducing type multi-reverse gear transmission mechanism

Publications (1)

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CN113719591A true CN113719591A (en) 2021-11-30

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Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102004041509A1 (en) * 2004-08-27 2006-03-16 Zf Friedrichshafen Ag Automobile multi-speed gearbox, with eight forward and two reverse gears, has three planet wheel sets and six switch units between the drive input and output shafts
JP2015081667A (en) * 2013-10-24 2015-04-27 アイシン精機株式会社 Automatic transmission for vehicle
CN112324877A (en) * 2020-11-19 2021-02-05 中国地质大学（武汉） Nine-gear automatic transmission
CN112555364A (en) * 2020-11-27 2021-03-26 贵州凯星液力传动机械有限公司 Planetary gear transmission mechanism
CN216078164U (en) * 2021-09-10 2022-03-18 贵州凯星液力传动机械有限公司 Internal-meshing multi-gear planetary transmission mechanism

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102004041509A1 (en) * 2004-08-27 2006-03-16 Zf Friedrichshafen Ag Automobile multi-speed gearbox, with eight forward and two reverse gears, has three planet wheel sets and six switch units between the drive input and output shafts
JP2015081667A (en) * 2013-10-24 2015-04-27 アイシン精機株式会社 Automatic transmission for vehicle
CN112324877A (en) * 2020-11-19 2021-02-05 中国地质大学（武汉） Nine-gear automatic transmission
CN112555364A (en) * 2020-11-27 2021-03-26 贵州凯星液力传动机械有限公司 Planetary gear transmission mechanism
CN216078164U (en) * 2021-09-10 2022-03-18 贵州凯星液力传动机械有限公司 Internal-meshing multi-gear planetary transmission mechanism

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