CN109442018B - Asymmetric self-locking differential mechanism - Google Patents
Asymmetric self-locking differential mechanism Download PDFInfo
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- CN109442018B CN109442018B CN201811625683.4A CN201811625683A CN109442018B CN 109442018 B CN109442018 B CN 109442018B CN 201811625683 A CN201811625683 A CN 201811625683A CN 109442018 B CN109442018 B CN 109442018B
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- 125000006850 spacer group Chemical group 0.000 claims description 28
- 238000006073 displacement reaction Methods 0.000 claims description 4
- RYGMFSIKBFXOCR-UHFFFAOYSA-N Copper Chemical compound [Cu] RYGMFSIKBFXOCR-UHFFFAOYSA-N 0.000 claims description 3
- 229910052802 copper Inorganic materials 0.000 claims description 3
- 239000010949 copper Substances 0.000 claims description 3
- 239000000463 material Substances 0.000 claims description 3
- 239000012212 insulator Substances 0.000 claims description 2
- 230000035939 shock Effects 0.000 claims description 2
- 230000005540 biological transmission Effects 0.000 description 4
- 230000000694 effects Effects 0.000 description 4
- 238000000034 method Methods 0.000 description 2
- 238000006243 chemical reaction Methods 0.000 description 1
- 239000003638 chemical reducing agent Substances 0.000 description 1
- 238000003754 machining Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000006467 substitution reaction Methods 0.000 description 1
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Classifications
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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
- F16H48/20—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
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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
- F16H48/20—Arrangements for suppressing or influencing the differential action, e.g. locking devices
- F16H2048/204—Control of arrangements for suppressing differential actions
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
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Abstract
The invention belongs to the technical field of differentials, and discloses an asymmetric self-locking differential, which comprises: a differential case, a first side gear, and a second side gear; the differential shell is provided with two opposite output shaft cylinders, and a helical gear is arranged outside the differential shell; the first half shaft gear and the second half shaft gear are respectively arranged in the differential shell and respectively correspond to the two output shaft cylinders; the pitch circle radius of the first side gear is twice the pitch circle radius of the second side gear; the asymmetric locking differential further comprises: a first planetary gear and a second planetary gear; the second planetary gear is rotatably arranged in the differential case and is meshed with the second side gear; the first planetary gears are rotatably disposed within the differential case and are respectively meshed with the second planetary gears and the first axle gear.
Description
Technical Field
The invention relates to the technical field of differentials, in particular to an asymmetric self-locking differential.
Background
In a multi-axle vehicle chassis, differentials are classified into a self-locking type antiskid differential and a forced locking type differential. The self-locking anti-skidding differential has the characteristics of sensitive reaction, stable transmission and the like, is suitable for being used on a chassis of an off-road vehicle, and improves the trafficability of the off-road vehicle. The conventional multi-axle vehicle adopts a 1:1 constant-torque symmetrical differential or a 2:1 constant-torque differential. However, according to practical use, the existing differential is not ideal in self-locking performance due to the design mode of the internal structure, and the adjustment range of the torque output ratio is small.
Disclosure of Invention
The invention provides an asymmetric self-locking differential, which improves the self-locking performance of the self-locking differential with the fixed torque distribution ratio of 2:1 and enlarges the adjustment range of the output torque ratio.
In order to solve the above technical problem, the present invention provides an asymmetric self-locking differential, comprising: a differential case, a first side gear, and a second side gear; the differential shell is provided with two opposite output shaft cylinders, and a helical gear is arranged outside the differential shell; the first half shaft gear and the second half shaft gear are respectively arranged in the differential shell and respectively correspond to the two output shaft cylinders;
the pitch circle radius of the first side gear is twice the pitch circle radius of the second side gear;
the asymmetric locking differential further comprises: a first planetary gear and a second planetary gear;
the second planetary gear is rotatably arranged in the differential case and is meshed with the second side gear;
the first planetary gears are rotatably disposed within the differential case and are respectively meshed with the second planetary gears and the first axle gear.
Further, the asymmetric locking differential further comprises: a spacer;
the spacer is disposed between an axial end portion of the first side gear and axial end portions of the second side gear and the second planetary gear.
Further, the spacer includes: a spacer body;
the spacer body is disposed between an axial end of the first side gear and an axial end of the second side gear;
the first end of the spacer body is provided with a radial extension portion which is arranged between the axial end of the first half-shaft gear and the axial end of the second planetary gear.
Furthermore, the shock insulator is integrally formed by adopting a copper material.
Furthermore, the number of the first planetary gears and the number of the second planetary gears are four, and the first planetary gears and the second planetary gears are uniformly arranged on a circular surface.
Furthermore, the two output shafts are fixed outside the cylinder through bearings respectively.
Further, the first side gear, the second side gear, the first planetary gear and the second planetary gear are all helical gears.
One or more technical solutions provided in the embodiments of the present application have at least the following technical effects or advantages:
according to the asymmetric self-locking differential provided by the embodiment of the application, the pitch circle radiuses of a first half shaft gear and a second half shaft gear of the differential are set according to a ratio of 2:1, so that an asymmetric output structure with a constant torque ratio of 2:1 is formed; the second planetary gear is meshed with the second half shaft gear, and the first planetary gear is respectively meshed with the first half shaft gear and the second planetary gear, so that on one hand, the adjusting range of the torque output ratio is expanded, and the torque output ratio can generally reach 2: 3-6: 1, namely, the maximum torque output ratio can reach 3 times; on the other hand, the stable automatic locking is realized through the positive pressure of the shell helical gear and the friction force between the shell helical gear and the shell and the spacer sleeve.
Specifically, in the no-load condition, all the planetary gears revolve with the differential case without rotating on its own axis, the rotation speed of the second side gear is half of that of the first side gear, and the output torque of the second side gear is twice that of the first side gear. In the daily work of the differential, when the torque difference exists between the front load and the rear load, the first planetary gear and the second planetary gear rotate relatively, the maximum relative rotating speed is limited by the friction force of the first planetary gear and the second planetary gear in a differential shell, and when the left torque ratio and the right torque ratio are deviated enough on the basis of 2:1, namely a certain shaft slips, the differential is limited by positive pressure and the friction force, so that the differential is locked; when the left-right torque ratio is reduced, the differential mechanism is loosened, so that the automatic adjustment effect is realized.
And further, a floating type spacer is arranged in the structure, so that the friction torque during limited slip is increased, and the damage of transmission system parts caused by untimely or incorrect manual operation of the differential lock is prevented.
Drawings
FIG. 1 is a cross-sectional view of a rotational aspect of an asymmetric locking differential provided by the present invention;
FIG. 2 is a half-sectional view of an asymmetric locking differential provided by the present invention.
Detailed Description
The embodiment of the application improves the self-locking performance of the self-locking differential with the constant torque distribution ratio of 2:1 and enlarges the adjusting range of the output torque ratio by providing the asymmetric self-locking differential.
In order to better understand the technical solutions, the technical solutions will be described in detail below with reference to the drawings and the specific embodiments of the specification, and it should be understood that the embodiments and specific features of the embodiments of the present invention are detailed descriptions of the technical solutions of the present application, and are not limitations of the technical solutions of the present application, and the technical features of the embodiments and examples of the present application may be combined with each other without conflict.
Referring to fig. 1 and 2, an asymmetric locking differential includes: a differential case, a first side gear 5, and a second side gear 6; the differential mechanism shell is provided with two opposite output shaft cylinders, and a helical gear 10 is arranged outside the differential mechanism shell; the first side gear 5 and the second side gear 6 are respectively arranged in the differential shell and respectively correspond to the two output shaft cylinders.
Generally, the differential case is formed by fastening the first case 1 and the second case 2 and fixing them by fastening bolts.
A first output shaft cylinder 11 is arranged on the first shell 1, and a second output shaft cylinder 12 is arranged on the second shell 2 and respectively used as a bearing structure of two output rotating shafts; the first side gear 5 is correspondingly arranged on one side of the first output shaft barrel 11, and the second side gear 6 is correspondingly arranged on one side of the second output shaft barrel 12.
A first limiting groove 13 is formed in the first shell 1, and the first half-shaft gear 5 is rotatably embedded in the first limiting groove 13; correspondingly, a second limit groove 14 is formed in the second shell 2, and the second side gear 6 is rotatably embedded in the second limit groove 14.
Wherein the pitch circle radius of the first side gear 5 is twice the pitch circle radius of the second side gear 6; and a 2:1 constant torque output structure is formed.
The asymmetric locking differential further comprises: a first planetary gear 7 and a second planetary gear 8;
the second planetary gears 8 are rotatably disposed in the differential case and are meshed with the second side gears 6; the first planetary gears 7 are rotatably disposed in the differential case, and are meshed with the second planetary gears 8 and the first carrier gear 5, respectively.
Wherein the first side gear 5, the second side gear 6, the first planetary gears 7 and the second planetary gears 8 are all helical gears.
A first axial limiting groove 15 and a second axial limiting groove 16 which are matched with the first planetary gear 7 and the second planetary gear 8 are arranged in the second shell 2, and limit axial displacement to be used as a friction locking structure.
Further, the asymmetric locking differential further comprises: a spacer 9; the spacers 9 are provided between the axial end portions of the first side gear 5 and the second side gear 6 and the second planetary gears 8, limit axial displacement, and serve as friction locking structures.
Further, the spacer 9 includes: a spacer body; the spacer body is disposed between the axial end portion of the first side gear 5 and the axial end portion of the second side gear 6; the first end of the spacer body is provided with a radial extension which is arranged between the axial end of the first half-shaft gear 5 and the axial end of the second planet gear 8.
Generally, the spacers are integrally formed of a copper material.
Further, the first planetary gears 7 and the second planetary gears 8 are all four and are uniformly arranged on a circular surface.
Further, the two output shafts are fixed outside the cylinder through a first bearing 3 and a second bearing 4 respectively.
The first planetary gear 7 and the second planetary gear 8 drive the first half shaft gear 5 and the second half shaft gear 6 which are meshed with the first planetary gear to rotate, and the splines inside the two half shaft gears are connected with the two output shafts to realize the output of torque.
The working process is described below.
The fixed torque distribution ratio of the differential mechanism depends on the ratio of pitch circle diameters of the two side gears, in the invention, the pitch circle diameter of the first side gear 5 is twice of the pitch circle diameter of the second side gear 6, and through the ratio calculation of the gears, the distribution circle diameters of the first selection planet gear 7 and the second planet gear 8 are used for enabling the two side gears to be meshed through four groups of planet gear pairs, thereby realizing the torque transmission and distribution. After the helical gear helical angle is planned and designed, the torque distribution ratio can reach more than 3 times of the fixed torque distribution, and the differential with the automatically-locked asymmetric torque distribution ratio is realized, wherein the torque distribution ratio is 2: 3-6: 1.
Power is input by the bevel gear 10 on the differential housing.
When the rotating speeds of the two half shafts are 1:2, the first planetary gear 7 and the second planetary gear 8 do not rotate, the differential does not play a differential role, the torque input by the differential shell is directly output to the left output shaft and the right output shaft according to the torque distribution ratio of 2:1 and then input into the main speed reducer of the chassis, and the driving of the multi-shaft chassis is realized.
When the rotating speed ratio of the left half shaft to the right half shaft is not 1:2, when the rotating speed difference is small, the first planetary gear 7 and the second planetary gear 8 rotate in the differential shell, so that the rotating speed difference is absorbed; when the difference of the rotation speeds is large, such as one axle of the chassis slips, the friction torque between the first planetary gear 7 and the second planetary gear 8 and the differential shell is increased along with the increase of the difference of the rotation speeds, and because the side gear and the planetary gear are helical gears with large helical angles, axial force is generated in the gear meshing process, so when the differential acts, positive pressure generated by the gears is increased, and the slip limiting torque of the differential is increased. In addition, the floating type spacer 9 is added in the two side gears, when the differential mechanism acts, the helical gears are meshed to generate larger axial force, the spacer 9 can be pressed towards the other side along with the axial force of the gear on one side, and the friction force between the spacer 9 and the end faces of the side gears or the planetary gears is increased, so that the limited slip torque of the whole system is increased. The floating type spacer 9 simultaneously solves the problem that the machining precision of the differential case is poor when the original spacer 9 and the differential case are integrated. The automatically-locked limited slip differential limits differential speed of the differential, distributes more torque to non-slipping chassis shafts, and improves the off-road property and the trafficability property of the multi-axle vehicle chassis.
One or more technical solutions provided in the embodiments of the present application have at least the following technical effects or advantages:
according to the asymmetric self-locking differential provided by the embodiment of the application, the pitch circle radiuses of a first half shaft gear and a second half shaft gear of the differential are set according to a ratio of 2:1, so that an asymmetric output structure with a constant torque ratio of 2:1 is formed; the second planetary gear is meshed with the second half shaft gear, and the first planetary gear is respectively meshed with the first half shaft gear and the second planetary gear, so that on one hand, the adjusting range of the torque output ratio is expanded, and the torque output ratio can generally reach 2: 3-6: 1, namely, the maximum torque output ratio can reach 3 times; on the other hand, the stable automatic locking is realized through the positive pressure of the shell helical gear and the friction force between the shell helical gear and the shell and the spacer sleeve.
Specifically, in the no-load condition, all the planetary gears revolve with the differential case without rotating on its own axis, the rotation speed of the second side gear is half of that of the first side gear, and the output torque of the second side gear is twice that of the first side gear. In the daily work of the differential, when the torque difference exists between the front load and the rear load, the first planetary gear and the second planetary gear rotate relatively, the maximum relative rotating speed is limited by the friction force of the first planetary gear and the second planetary gear in a differential shell, and when the left torque ratio and the right torque ratio are deviated enough on the basis of 2:1, namely a certain shaft slips, the differential is limited by positive pressure and the friction force, so that the differential is locked; when the left-right torque ratio is reduced, the differential mechanism is loosened, so that the automatic adjustment effect is realized.
And further, a floating type spacer is arranged in the structure, so that the friction torque during limited slip is increased, and the damage of transmission system parts caused by untimely or incorrect manual operation of the differential lock is prevented.
Finally, it should be noted that the above embodiments are only for illustrating the technical solutions of the present invention and not for limiting, and although the present invention has been described in detail with reference to examples, it should be understood by those skilled in the art that modifications or equivalent substitutions may be made on the technical solutions of the present invention without departing from the spirit and scope of the technical solutions of the present invention, which should be covered by the claims of the present invention.
Claims (5)
1. An asymmetric self-locking differential, comprising: a differential case, a first side gear, and a second side gear; the differential shell is provided with two opposite output shaft cylinders, and a helical gear is arranged outside the differential shell; the first half shaft gear and the second half shaft gear are respectively arranged in the differential shell and respectively correspond to the two output shaft cylinders;
the pitch circle radius of the first side gear is twice the pitch circle radius of the second side gear;
the asymmetric locking differential further comprises: a first planetary gear and a second planetary gear;
the second planetary gear is rotatably arranged in the differential case and is meshed with the second side gear;
the first planetary gear is rotatably arranged in the differential shell and is respectively meshed with the second planetary gear and the first axle gear;
the differential shell is formed by buckling a first shell and a second shell;
a first axial limiting groove and a second axial limiting groove which are matched with the first planetary gear and the second planetary gear are arranged in the second shell, and limit axial displacement to be used as a friction locking structure;
the asymmetric locking differential further comprises: a spacer;
the spacer is provided between the axial end portion of the first side gear and the axial end portions of the second side gear and the second planetary gear, limits axial displacement, and serves as a friction lock structure;
the spacer includes: a spacer body;
the spacer body is disposed between an axial end of the first side gear and an axial end of the second side gear;
the first end of the spacer body is provided with a radial extension portion which is arranged between the axial end of the first half-shaft gear and the axial end of the second planetary gear.
2. The asymmetric locking differential as set forth in claim 1 wherein: the shock insulator is integrally formed by adopting a copper material.
3. The asymmetric self-locking differential as claimed in any one of claims 1 to 2, wherein: the first planetary gears and the second planetary gears are all four and are uniformly arranged on a circular surface.
4. The asymmetric locking differential as set forth in claim 3 wherein: and the two output shafts are fixed outside the cylinders through bearings respectively.
5. The asymmetric locking differential as set forth in claim 4 wherein: the first side gear, the second side gear, the first planet gear and the second planet gear are all helical gears.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201811625683.4A CN109442018B (en) | 2018-12-28 | 2018-12-28 | Asymmetric self-locking differential mechanism |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201811625683.4A CN109442018B (en) | 2018-12-28 | 2018-12-28 | Asymmetric self-locking differential mechanism |
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| Publication Number | Publication Date |
|---|---|
| CN109442018A CN109442018A (en) | 2019-03-08 |
| CN109442018B true CN109442018B (en) | 2020-12-18 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201811625683.4A Active CN109442018B (en) | 2018-12-28 | 2018-12-28 | Asymmetric self-locking differential mechanism |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114001140A (en) * | 2021-11-30 | 2022-02-01 | 惠州兴为智能科技有限公司 | Differential mechanism of strength training instrument |
| CN113979229A (en) * | 2021-11-30 | 2022-01-28 | 惠州兴为智能科技有限公司 | Take-up device of strength training instrument |
Family Cites Families (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP2025973B1 (en) * | 2007-08-14 | 2015-07-29 | Autotech Sport Tuning Corporation | Differential gear assembly |
| CN203023426U (en) * | 2013-01-09 | 2013-06-26 | 天津天海同步科技股份有限公司 | Cylindrical gear power-shunting type limited slip differential |
| DE102013202092A1 (en) * | 2013-02-08 | 2014-08-14 | Schaeffler Technologies Gmbh & Co. Kg | Differential gear used in vehicle, has insertion elements that are fitted to drive gears to form guide structure, and are supported by bearing rings of roller bearings |
| CN204628482U (en) * | 2015-02-12 | 2015-09-09 | 舍弗勒技术股份两合公司 | Limited slip differential |
| US20170175868A1 (en) * | 2015-12-16 | 2017-06-22 | Atieva, Inc. | Parallel Axis Epicyclic Gear Differential |
| US9958049B1 (en) * | 2017-05-15 | 2018-05-01 | E-Aam Driveline Systems Ab | Electric drive module with Ravigneaux gearset |
| DE102017111049A1 (en) * | 2017-05-22 | 2018-04-19 | Schaeffler Technologies AG & Co. KG | Drive device for a motor vehicle |
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