CN108413003B - Differential mechanism with inner-outer double-layer planetary bevel gear mechanism - Google Patents

Differential mechanism with inner-outer double-layer planetary bevel gear mechanism Download PDF

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CN108413003B
CN108413003B CN201810356403.8A CN201810356403A CN108413003B CN 108413003 B CN108413003 B CN 108413003B CN 201810356403 A CN201810356403 A CN 201810356403A CN 108413003 B CN108413003 B CN 108413003B
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gear
layer
planetary
bevel gear
shaft
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CN108413003A (en
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包世萍
翟小兵
张宁
曾德江
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Guangdong Mechanical and Electrical College
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Guangdong Mechanical and Electrical College
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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
    • F16H48/00—Differential gearings
    • F16H48/05—Multiple interconnected differential sets
    • 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
    • F16H48/00—Differential gearings
    • F16H48/06—Differential gearings with gears having orbital motion
    • F16H48/08—Differential gearings with gears having orbital motion comprising bevel 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
    • F16H48/00—Differential gearings
    • F16H48/20—Arrangements for suppressing or influencing the differential action, e.g. locking devices
    • F16H48/28—Arrangements for suppressing or influencing the differential action, e.g. locking devices using self-locking gears or self-braking 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
    • F16H48/00—Differential gearings
    • F16H48/38—Constructional details
    • F16H48/40—Constructional details characterised by features of the rotating cases
    • 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
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H57/029—Gearboxes; Mounting gearing therein characterised by means for sealing the gearboxes, e.g. to improve airtightness
    • 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
    • F16H57/082—Planet carriers
    • 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
    • F16H48/00—Differential gearings
    • F16H48/06—Differential gearings with gears having orbital motion
    • F16H48/08—Differential gearings with gears having orbital motion comprising bevel gears
    • F16H2048/085—Differential gearings with gears having orbital motion comprising bevel gears characterised by shafts or gear carriers for 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
    • F16H48/00—Differential gearings
    • F16H48/06—Differential gearings with gears having orbital motion
    • F16H48/08—Differential gearings with gears having orbital motion comprising bevel gears
    • F16H2048/087—Differential gearings with gears having orbital motion comprising bevel gears characterised by the pinion gears, e.g. their type or arrangement

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Retarders (AREA)

Abstract

The invention discloses a differential mechanism of an internal and external double-layer planetary bevel gear mechanism, which comprises a left box body, the differential mechanism comprises a middle box body and a right box body, wherein the left box body is connected with an input large bevel gear, two inner-layer planetary bevel gears are arranged inside the differential mechanism and are in meshing transmission with inner-layer sun bevel gears on two sides, a pair of tapered roller bearings is arranged at the center of each inner-layer planetary bevel gear and sleeved on the outer peripheral surface of a long shaft, the inner-layer sun bevel gears are fixedly connected with a central gear shaft, two outer-layer planetary bevel gears are arranged inside the differential mechanism and are in meshing transmission with the outer-layer sun bevel gears on two sides, the two outer-layer planetary bevel gears are respectively connected with the long shaft, an inner gear ring of each outer-layer planetary bevel gear is in meshing transmission with a planetary cylindrical gear, the planetary cylindrical gear is in meshing transmission with a. Compared with the prior art, the invention has the advantages of balanced stress, reliable work and the like, and can realize size reduction and more compact structure.

Description

Differential mechanism with inner-outer double-layer planetary bevel gear mechanism
Technical Field
The invention relates to the technical field of automobile differential transmission, in particular to a differential mechanism with an internal and external double-layer planetary bevel gear mechanism.
Background
In the prior art, the differential mechanism is mainly applied to the technical field of automobiles, and when an automobile turns, the rotation speeds of the left side wheels and the right side wheels are different, so that the slippage of the automobile caused by the difference of the rotation speeds of the wheels on two sides is not easy to occur in the turning process of the whole automobile, and the work of the wheels on two sides of the automobile at different rotation speeds is realized by the differential mechanism.
The planetary bevel gear differential mechanism in the prior art mainly comprises a pair of planetary bevel gears, a pair of sun bevel gears, a planetary gear carrier, a differential mechanism shell, a half axle gear and other parts, and has important significance for optimizing the structure of the planetary bevel gear differential mechanism due to the fact that the structure is too simple, the stress of part of the structure is unbalanced, and the volume is too large to influence the fuel economy of the whole vehicle.
Disclosure of Invention
The invention mainly aims to provide an inner-outer double-layer planetary bevel gear mechanism differential mechanism with balanced stress and reliable work, and aims to optimally design the inner-outer double-layer planetary bevel gear mechanism differential mechanism so as to realize size reduction, more compact structure and improvement on the work reliability.
In order to achieve the purpose, the differential mechanism of the internal and external double-layer planetary bevel gear mechanism comprises a left box body, a middle box body and a right box body which are sequentially connected to form an internal space, wherein the left box body is fixedly connected with an input large bevel gear, two inner-layer planetary bevel gears which are arranged in parallel are arranged in the differential mechanism and are simultaneously in meshing transmission with a left inner-layer sun bevel gear and a right inner-layer sun bevel gear, a pair of conical roller bearings are arranged in the center of each inner-layer planetary bevel gear and sleeved on the outer peripheral surface of a long shaft, the left inner-layer sun bevel gear is fixedly connected with a left central gear shaft, the middle part of the right inner-layer sun bevel gear is fixedly connected with a right central gear shaft, two outer-layer planetary bevel gears which are arranged in parallel are simultaneously in meshing transmission with a left outer-layer sun bevel, the outer-layer planetary bevel gear, the left outer-layer sun bevel gear and the right outer-layer sun bevel gear are arranged outside a structure consisting of the inner-layer planetary bevel gear, the left inner-layer sun bevel gear and the right inner-layer sun bevel gear; the two outer-layer planetary bevel gears are fixedly connected with the long shaft respectively, the inner gear ring of the left outer-layer sun bevel gear is in meshing transmission with the left planetary cylindrical gear, the inner gear ring of the right outer-layer sun bevel gear is in meshing transmission with the right planetary cylindrical gear, the left planetary cylindrical gear is in meshing transmission with the gear of the left central gear shaft, the right planetary cylindrical gear is in meshing transmission with the gear of the right central gear shaft, the left planetary cylindrical gear extends outwards to be connected with a bearing mounted on a left planetary frame, the right planetary cylindrical gear extends outwards to be connected with a bearing mounted on a right planetary frame, the left planetary frame is fixedly connected with the left output half shaft, and the right planetary frame is fixedly connected with the right output half shaft; the central axes of the left central gear shaft, the right central gear shaft and the long shaft are respectively vertical to the side surface of the central bracket.
Preferably, the left box body is fixedly connected with the input large bevel gear through screws, the left box body and the right box body are respectively positioned with the middle box body through positioning spigots and are fastened and connected through screws to form a combined box body, the left planet carrier is fixedly connected with the left output half shaft through splines, and the right planet carrier is fixedly connected with the right output half shaft through splines.
Preferably, the two inner layer planet bevel gears and the left inner layer sun bevel gear and the right inner layer sun bevel gear are arranged in a rectangular shape; the two outer-layer planet bevel gears, the left outer-layer sun bevel gear and the right outer-layer sun bevel gear are arranged in a rectangular shape.
Preferably, the left inner layer sun cone gear is connected with the left central gear shaft through a flat key, and the right inner layer sun cone gear is connected with the right central gear shaft through a flat key.
Preferably, the left side of the left outer layer sun conical gear is supported by a left support frame, and the right side of the right outer layer sun conical gear is supported by a right support frame; the left support frame is connected with the left output half shaft through a tapered roller bearing, and the right support frame is connected with the right output half shaft through a tapered roller bearing.
Preferably, one end of the long shaft close to the middle box body is connected with two tapered roller bearings, the tapered roller bearings are mounted in a sleeve, and the sleeve penetrates through a shell of the middle box body, is limited by an end cover and is fixedly connected with the middle box body; one end of the long shaft close to the center of the differential is connected with a tapered roller bearing, and the tapered roller bearing is arranged in the center bracket; one end of the left central gear shaft, which is close to the central bracket, is connected with a tapered roller bearing, and the other end of the left central gear shaft is connected with the tapered roller bearing arranged on the left planet carrier; one end of the right central gear shaft, which is close to the central support, is connected with a tapered roller bearing, and the other end of the right central gear shaft is connected with the tapered roller bearing arranged on the right planet carrier.
Preferably, the shape of the central bracket is rectangular, and a T-shaped supporting rib is arranged on the side surface of the central bracket.
Preferably, the number of the left planetary cylindrical gear and the right planetary cylindrical gear is an integer greater than or equal to 2, and the left planetary cylindrical gear and the right planetary cylindrical gear are uniformly distributed around the center.
Preferably, the left output half shaft and the right output half shaft are sealed on the outer peripheral surfaces by felt.
Compared with the prior art, the technical scheme of the invention has the following advantages:
when the differential mechanism with the inner and outer double-layer planetary bevel gear mechanisms adopts the technical scheme, the input large bevel gear drives the combined box body to rotate, and the combined box body can drive the long shaft and the central support to rotate around the central axis of the middle box body. At this time, the outer planetary bevel gear and the inner planetary bevel gear mounted on the long shaft start to revolve around the central axis of the middle box body. When the left rotating speed is the same as the right rotating speed, namely the vehicle travels in a straight line mode, the structure of the left part of the differential mechanism of the inner-outer double-layer planetary bevel gear mechanism is stressed as same as the structure of the right part. At this time, the inner planetary bevel gear and the outer planetary bevel gear only revolve, but do not rotate. When the left rotating speed is different from the right rotating speed, the structure of the left part of the differential mechanism of the inner-outer double-layer planetary bevel gear mechanism is stressed differently from the structure of the right part. At the moment, the inner-layer planet bevel gear and the outer-layer planet bevel gear not only revolve around the center but also respectively rotate due to different stress, so that the rotating speeds of the inner gear rings of the left outer-layer sun bevel gear and the right outer-layer sun bevel gear on the right side are different, correspondingly, the rotating speeds of the left central gear shaft and the right central gear shaft on the left side and the right side are different, differential output is formed between the planet transmission mechanisms on the two sides, transmission power split is realized, and the working pressure of a single gear is effectively reduced.
Drawings
In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings used in the description of the embodiments or the prior art will be briefly described below, it is obvious that the drawings in the following description are only some embodiments of the present invention, and for those skilled in the art, other drawings can be obtained according to the structures shown in the drawings without creative efforts.
FIG. 1 is a schematic view of the internal structure of the differential of the internal and external double-layer planetary bevel gear mechanism of the present invention;
FIG. 2 is a cross-sectional view taken at A-A of FIG. 1;
FIG. 3 is a cross-sectional view taken at B-B of FIG. 1;
fig. 4 is a cross-sectional view at C-C in fig. 2.
The reference numbers illustrate:
Figure BDA0001634787220000031
Figure BDA0001634787220000041
the implementation, functional features and advantages of the objects of the present invention will be further explained with reference to the accompanying drawings.
Detailed Description
The technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.
It should be noted that, if directional indications (such as up, down, left, right, front, and back … …) are involved in the embodiment of the present invention, the directional indications are only used to explain the relative positional relationship between the components, the movement situation, and the like in a specific posture (as shown in the drawing), and if the specific posture is changed, the directional indications are changed accordingly.
In addition, if there is a description of "first", "second", etc. in an embodiment of the present invention, the description of "first", "second", etc. is for descriptive purposes only and is not to be construed as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include at least one such feature. In addition, technical solutions between various embodiments may be combined with each other, but must be realized by a person skilled in the art, and when the technical solutions are contradictory or cannot be realized, such a combination should not be considered to exist, and is not within the protection scope of the present invention.
The invention provides a differential mechanism of an internal and external double-layer planetary bevel gear mechanism.
Referring to fig. 1 to 4, in the embodiment of the present invention, the differential mechanism of the inner-outer double-layer planetary bevel gear mechanism includes a left case 13 ', a middle case 2 and a right case 13 which are connected in sequence to form an internal space, the left case 13 ' is fixedly connected to the input large bevel gear 1, two inner planetary bevel gears 5 which are arranged in parallel are arranged inside the differential mechanism and are simultaneously in meshing transmission with the left inner sun bevel gear 6 ' and the right inner sun bevel gear 6, and a pair of tapered roller bearings is arranged in the center of the inner planetary bevel gears 5 and sleeved on the outer circumferential surface of a long shaft 3 which is arranged along the radial direction of the middle case 2, so that when the long shaft 3 drives the outer planetary bevel gears to rotate, the inner planetary bevel gears 5 are not affected. The left inner layer sun cone gear 6 ' is fixedly connected with a left central gear shaft 10 ', the middle part of the right inner layer sun cone gear 6 is fixedly connected with a right central gear shaft 10, so that the left inner layer sun cone gear 6 ' and the left central gear shaft 10 ' rotate together, the middle part of the right inner layer sun cone gear 6 and the right central gear shaft 10 rotate together, two outer layer planet cone gears 4 which are arranged in parallel are arranged in the differential mechanism and are meshed with the left outer layer sun cone gear 7 ' and the right outer layer sun cone gear 7 for transmission in a transmission and meshing manner, and the outer layer planet cone gears 4, the left outer layer sun cone gear 7 ' and the right outer layer sun cone gear 7 are arranged outside a structure consisting of the inner layer planet cone gear 5, the left inner layer sun cone gear 6 ' and the right inner layer sun cone gear 6; the two outer-layer planetary bevel gears 4 are respectively fixedly connected with the long shaft 3, so that the long shaft 3 drives the outer-layer planetary bevel gears 4 to rotate together, the inner gear ring of a left outer-layer sun bevel gear 7 'is in meshing transmission with a left planetary cylindrical gear 8', the inner gear ring of a right outer-layer sun bevel gear 7 is in meshing transmission with a right planetary cylindrical gear 8, the left planetary cylindrical gear 8 'is in meshing transmission with a gear of a left central gear shaft 10', the right planetary cylindrical gear 8 is in meshing transmission with a gear of a right central gear shaft 10, the left planetary cylindrical gear 8 'extends outwards and is connected with a bearing arranged on a left planet carrier 12', the bearing is preferably a deep groove ball bearing and is fixed through a bearing end cover and a shaft elastic retainer ring, the right planetary cylindrical gear 8 extends outwards and is connected with a bearing arranged on the right planet carrier 12, the bearing is preferably a deep groove ball bearing and is fixed through a bearing end cover and a shaft elastic retainer ring, the left planet carrier 12 'is fixedly connected with the left output half shaft 11', and the right planet carrier 12 is fixedly connected with the right output half shaft 12; the central axes of the left central gear shaft 10', the right central gear shaft 10 and the long shaft 3 are perpendicular to the side faces of the central bracket 14, respectively. As shown in FIG. 4, the two ends of the central support 14 are connected with the middle box 2 by using connecting frames 15, and the connecting frames 15 are positioned with the middle box 2 by using positioning pins and then fixedly connected by using screws. The central support 14 and the connecting frame 15 are connected by screws, so that a positioning relationship exists between the two.
Preferably, the left box 13 'is fixedly connected with the input large bevel gear 1 by screws, the left box 13' and the right box 13 are respectively positioned with the middle box 2 by positioning spigots and are fastened and connected by screws to form a combined box, as shown in fig. 3, the left planet carrier 12 'of the present embodiment is fixedly connected with the left output half shaft 11' by splines, and the right planet carrier 12 is fixedly connected with the right output half shaft 11 by splines.
Preferably, the two inner layer planet bevel gears 5 and the left inner layer sun bevel gear 6' and the right inner layer sun bevel gear 6 are arranged in a rectangle shape; the two outer layer planet conical gears 4, the left outer layer sun conical gear 7' and the right outer layer sun conical gear 7 are arranged in a rectangular shape.
Preferably, the left inner sun-cone gear 6 'is flat-keyed to the left central gear shaft 10', and the right inner sun-cone gear 6 is flat-keyed to the right central gear shaft 10. So that the left inner layer sun-cone gear 6 'and the left central gear shaft 10', and the right inner layer sun-cone gear 6 and the right central gear shaft 10 rotate synchronously.
Preferably, the left side of the left outer layer sun cone gear 7 ' is supported by the left support frame 9 ', and the right side of the right outer layer sun cone gear 7 is supported by the right support frame 9, so that the positioning accuracy of the left outer layer sun cone gear 7 ' and the right outer layer sun cone gear 7 can be ensured, and the normal operation of the gears can be ensured. The left support frame 9 'is connected with the left output half shaft 11' through a tapered roller bearing, and the right support frame 9 is connected with the right output half shaft 11 through a tapered roller bearing.
Preferably, one end of the long shaft 3 close to the middle box body 2 is connected with two tapered roller bearings, the cylindrical roller bearings are arranged in a sleeve, and the sleeve penetrates through the shell of the middle box body 2, is limited by an end cover and is fixedly connected with the middle box body 2; one end of the long shaft 3 close to the center of the differential is connected with a tapered roller bearing, and the tapered roller bearing is arranged in a central bracket 14; one end of the left central gear shaft 10 ' close to the central bracket 14 is connected with a tapered roller bearing, and the other end of the left central gear shaft 10 ' is connected with the tapered roller bearing arranged on the left planet carrier 12 '; one end of the right central gear shaft 10 close to the central bracket 14 is connected with a tapered roller bearing, and the other end of the right central gear shaft 10 is connected with the tapered roller bearing arranged on the right planet carrier 12. Through the structure, after the long shaft 3, the left central gear shaft 10' and the right central gear shaft 10 are installed, two ends of the long shaft are simultaneously supported, so that the stress is more uniform.
Preferably, the shape of the center frame 14 is rectangular, and the side of the center frame 14 is provided with T-shaped supporting ribs, so as to ensure that the entire center frame 14 has good bending structural strength.
Preferably, the number of the left planetary cylindrical gear 8 'and the right planetary cylindrical gear 8 is an integer greater than or equal to 2, and the left planetary cylindrical gear 8' and the right planetary cylindrical gear 8 are uniformly distributed around the center.
Preferably, the left output half shaft 11' and the right output half shaft 11 are sealed on the outer peripheral surfaces by felt.
Referring to fig. 1 to 4, the operating principle of the differential mechanism with the inner and outer double-layer planetary bevel gear mechanism according to the embodiment of the present invention is as follows:
when the differential mechanism works, the input large bevel gear 1 drives the combined box body to rotate, and the combined box body can drive the long shaft 3 and the central support 14 to rotate around the central axis of the middle box body. At this time, the outer planetary bevel gear 4 and the inner planetary bevel gear 5 mounted on the long shaft 3 start to revolve around the central axis of the middle box body.
When the left rotating speed is the same as the right rotating speed, namely the vehicle travels in a straight line mode, the structure of the left part of the differential mechanism of the inner-outer double-layer planetary bevel gear mechanism is stressed as same as the structure of the right part. At this time, the inner planetary bevel gear 5 and the outer planetary bevel gear 4 only revolve, but do not rotate.
When the left rotating speed is different from the right rotating speed, the structure of the left part of the differential mechanism of the inner-outer double-layer planetary bevel gear mechanism is stressed differently from the structure of the right part. At this time, the inner planetary bevel gear 5 and the outer planetary bevel gear 4 not only revolve around the center but also respectively rotate due to different stresses, so that the inner gear rings of the left outer sun bevel gear 7 'and the right outer sun bevel gear 7 on the right side have different rotating speeds, correspondingly, the left central gear shaft 10' and the right central gear shaft 10 on the left side and the right side have different rotating speeds, and further, differential output is formed between the planetary transmission mechanisms on the two sides, transmission power split is realized, and the working pressure of a single gear is effectively reduced.
When the differential mechanism of the inner-outer double-layer planetary bevel gear mechanism of the embodiment of the invention forms differential output, the stress of a single gear can be reduced, power split is realized to prolong the service life of the gear, and speed reduction can be realized. Meanwhile, the structure of the parts can be optimized, and the structure is compact and the size is reduced.
The above description is only a preferred embodiment of the present invention, and is not intended to limit the scope of the present invention, and all modifications and equivalents of the present invention, which are made by the contents of the present specification and the accompanying drawings, or directly/indirectly applied to other related technical fields, are included in the scope of the present invention.

Claims (9)

1. The differential mechanism of the inner-outer double-layer planetary bevel gear mechanism is characterized by comprising a left box body, a middle box body and a right box body which are sequentially connected to form an inner space, wherein the left box body is fixedly connected with an input large bevel gear, two inner-layer planetary bevel gears which are arranged in parallel are arranged in the differential mechanism and are simultaneously in meshing transmission with a left inner-layer sun bevel gear and a right inner-layer sun bevel gear, a pair of conical roller bearings are arranged at the center of each inner-layer planetary bevel gear and sleeved on the outer peripheral surface of a long shaft, the left inner-layer sun bevel gear is fixedly connected with a left central gear shaft, the middle of the right inner-layer sun bevel gear is fixedly connected with a right central gear shaft, two outer-layer planetary bevel gears which are arranged in parallel are also arranged in the differential mechanism and are simultaneously in meshing transmission with a left outer-layer, The left outer layer sun bevel gear and the right outer layer sun bevel gear are arranged outside a structure consisting of the inner layer planet bevel gear, the left inner layer sun bevel gear and the right inner layer sun bevel gear; the two outer-layer planetary bevel gears are fixedly connected with the long shaft respectively, the inner gear ring of the left outer-layer sun bevel gear is in meshing transmission with the left planetary cylindrical gear, the inner gear ring of the right outer-layer sun bevel gear is in meshing transmission with the right planetary cylindrical gear, the left planetary cylindrical gear is in meshing transmission with the gear of the left central gear shaft, the right planetary cylindrical gear is in meshing transmission with the gear of the right central gear shaft, the left planetary cylindrical gear extends outwards to be connected with a bearing mounted on a left planetary frame, the right planetary cylindrical gear extends outwards to be connected with a bearing mounted on a right planetary frame, the left planetary frame is fixedly connected with a left output half shaft, and the right planetary frame is fixedly connected with a right output half shaft; the central axes of the left central gear shaft, the right central gear shaft and the long shaft are respectively vertical to the side surface of the central bracket;
and two ends of the central support are connected with the middle box body through connecting frames.
2. The differential mechanism with inner and outer double-layer planetary bevel gear mechanism as claimed in claim 1, wherein the left case and the input large bevel gear are fixedly connected by screws, the left case and the right case are respectively positioned with the middle case through positioning spigots and are fastened and connected by screws to form a combined case, the left planet carrier is fixedly connected with the left output half shaft by splines, and the right planet carrier is fixedly connected with the right output half shaft by splines.
3. The differential of inner and outer double-layer planetary bevel gear mechanism according to claim 1, wherein two inner planetary bevel gears are arranged in a rectangular shape with the left inner sun bevel gear and the right inner sun bevel gear; the two outer-layer planet bevel gears, the left outer-layer sun bevel gear and the right outer-layer sun bevel gear are arranged in a rectangular shape.
4. The differential of inner and outer double planetary-cone gear mechanism as claimed in claim 1, wherein said left inner sun-cone gear is flat-keyed to said left sun gear shaft and said right inner sun-cone gear is flat-keyed to said right sun gear shaft.
5. The differential of inner and outer double-layer planetary bevel gear mechanism according to claim 1, wherein the left side of the left outer layer sun bevel gear is supported by a left support frame, and the right side of the right outer layer sun bevel gear is supported by a right support frame; the left support frame is connected with the left output half shaft through a tapered roller bearing, and the right support frame is connected with the right output half shaft through a tapered roller bearing.
6. The differential mechanism with inner and outer double-layer planetary bevel gear mechanism as claimed in claim 1, wherein one end of the long shaft close to the middle box body is connected with two tapered roller bearings which are arranged in a sleeve, and the sleeve penetrates through the shell of the middle box body, is limited by an end cover and is fixedly connected with the middle box body; one end of the long shaft close to the center of the differential is connected with a tapered roller bearing, and the tapered roller bearing is arranged in the center bracket; one end of the left central gear shaft, which is close to the central bracket, is connected with a tapered roller bearing, and the other end of the left central gear shaft is connected with the tapered roller bearing arranged on the left planet carrier; one end of the right central gear shaft, which is close to the central support, is connected with a tapered roller bearing, and the other end of the right central gear shaft is connected with the tapered roller bearing arranged on the right planet carrier.
7. The differential of inner and outer double-layer planetary bevel gear mechanism according to claim 1, wherein the central carrier has a rectangular shape, and a T-shaped support rib is provided on a side surface of the central carrier.
8. The differential mechanism of inner and outer double-layer planetary bevel gear mechanism according to claim 1, wherein the number of the left planetary cylindrical gear and the right planetary cylindrical gear is an integer of 2 or more, and the left planetary cylindrical gear and the right planetary cylindrical gear are evenly distributed at the center.
9. The differential of inner and outer double-layer planetary bevel gear mechanism according to claim 1, wherein said left output half shaft and said right output half shaft are sealed on the outer peripheral surfaces by felt.
CN201810356403.8A 2018-04-19 2018-04-19 Differential mechanism with inner-outer double-layer planetary bevel gear mechanism Expired - Fee Related CN108413003B (en)

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