CN116658591A - Planetary gear differential control system - Google Patents

Planetary gear differential control system Download PDF

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Publication number
CN116658591A
CN116658591A CN202310856056.6A CN202310856056A CN116658591A CN 116658591 A CN116658591 A CN 116658591A CN 202310856056 A CN202310856056 A CN 202310856056A CN 116658591 A CN116658591 A CN 116658591A
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CN
China
Prior art keywords
gear
differential
control system
planetary gear
planetary
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
CN202310856056.6A
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Chinese (zh)
Inventor
吕枫
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Individual
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Individual
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Filing date
Publication date
Application filed by Individual filed Critical Individual
Priority to CN202310856056.6A priority Critical patent/CN116658591A/en
Publication of CN116658591A publication Critical patent/CN116658591A/en
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H48/00—Differential gearings
    • F16H48/06—Differential gearings with gears having orbital motion
    • F16H48/10—Differential gearings with gears having orbital motion with orbital spur 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
    • F16H48/30—Arrangements for suppressing or influencing the differential action, e.g. locking devices using externally-actuatable means
    • F16H48/34—Arrangements for suppressing or influencing the differential action, e.g. locking devices using externally-actuatable means using electromagnetic or electric actuators
    • 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
    • F16H48/36—Differential gearings characterised by intentionally generating speed difference between outputs
    • 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
    • F16H48/10—Differential gearings with gears having orbital motion with orbital spur gears
    • F16H2048/106—Differential gearings with gears having orbital motion with orbital spur gears characterised by two sun 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
    • F16H48/30—Arrangements for suppressing or influencing the differential action, e.g. locking devices using externally-actuatable means
    • F16H48/34—Arrangements for suppressing or influencing the differential action, e.g. locking devices using externally-actuatable means using electromagnetic or electric actuators
    • F16H2048/343—Arrangements for suppressing or influencing the differential action, e.g. locking devices using externally-actuatable means using electromagnetic or electric actuators using a rotary motor
    • 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
    • F16H48/36—Differential gearings characterised by intentionally generating speed difference between outputs
    • F16H2048/364—Differential gearings characterised by intentionally generating speed difference between outputs using electric or hydraulic motors
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/60—Other road transportation technologies with climate change mitigation effect
    • Y02T10/72—Electric energy management in electromobility

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Retarders (AREA)

Abstract

The application relates to the technical field of automobile differentials, and discloses a planetary gear differential control system, which comprises a differential box body, wherein a differential gear is connected with an external differential wheel positioned outside the differential box body, the external differential wheel is in transmission connection with a control system, the control system comprises a worm in meshed connection with the external differential wheel, one end of the worm is fixedly connected with a first gear, and the first gear is in meshed connection with a band-type brake motor. According to the planetary gear differential control system, through the cooperation arrangement among the band-type brake motor, the worm and the external differential wheel, the rotation speed difference between the left and right wheels of the automobile can be actively distributed, meanwhile, the wheels can be guaranteed to be differential while limited in slip, the abrasion of tires can be reduced and the stability of the automobile in turning can be improved through actively distributing the rotation speed difference between the two wheels, and the differential part and the limited slip part are separated in hardware, so that independent maintenance is facilitated.

Description

Planetary gear differential control system
Technical Field
The application relates to the technical field of automobile differentials, in particular to a planetary gear differential control system.
Background
In the planetary gear differential mechanism, the planetary gear and the planetary carrier are usually in running fit in a form of arranging a bearing or a bearing bush, and radial gaps are required to be arranged when the bearing or the bearing bush is matched, so that the planetary gear differential mechanism has larger noise when in operation; when the size of the planet wheel is changed, the types of the bearing and the bearing bush need to be changed, so that the universality is poor; the bearing and the bearing bush have high unit price, and the use cost is high as a vulnerable part; the radial dimension of the planetary gear differential mechanism can be enlarged by installing the bearing, the miniaturization requirement is not met, and the radial bearing capacity is low and the bearing bush is easy to wear although the miniaturization requirement is met.
In order to solve the technical problems, the Chinese patent application publication No. CN1 10873165A discloses a planetary gear differential, the planetary gear differential is provided with a planetary gear in a form of combining a wheel shaft with an outer gear ring, and a rolling needle is arranged between the outer circumferential surface of the wheel shaft and the inner circumferential surface of the outer gear ring, so that the outer gear ring of the planetary gear can rotate relative to a planet carrier, a radial clearance is eliminated by enabling the diameter of the rolling needle to be equal to the difference value between the inner diameter of the outer gear ring and the outer diameter of the wheel shaft, the noise in use is reduced, the radial size of the planetary gear differential can be reduced by installing the rolling needle, and the planetary gear differential is high in radial bearing capacity and strong in abrasion resistance;
although the technical scheme provided by the application solves the problems of low radial bearing capacity and easy abrasion of the planetary gear differential mechanism, the existing limited slip differential mechanisms are inconvenient to actively distribute the rotating speed difference between the left wheel and the right wheel of the automobile, the existing limited slip differential mechanisms mostly use a multi-disc clutch to distribute torque, namely when slip is detected, the clutch drives the wheel with the other side not slipping through friction to obtain power, but the rotating speeds of the two wheels are the same at the moment, and the distributed torque is different. The design cannot be suitable for the situation of turning sliding, and because the power and the rotation speed of two wheels are unequal when the turning sliding occurs, a limited-sliding differential mechanism capable of carrying out differential speed and not sliding is needed. In addition, the limited slip differential based on the multi-plate clutch is that the differential and the limited slip clutch plates are integrated, the clutch itself can rub, the heating performance can be reduced after a long time, in a word, some existing limited slip differentials with multi-plate clutch cannot achieve limited slip and differential at the same time, the differential cannot be definitely differentiated when the limited slip is complete, the limited slip is definitely not complete when the differential is present, and the effect is poor when the limited slip differential is actually applied.
Disclosure of Invention
The present application is directed to a planetary differential control system to solve the above-mentioned problems.
The embodiment of the application adopts the following technical scheme:
the planetary gear differential control system comprises a differential box body, wherein two groups of planetary gear assemblies and a power input shaft which is meshed with the two groups of planetary gear assemblies are symmetrically arranged in the differential box body, sun gears are fixedly connected to two ends of the power input shaft, each group of planetary gear assemblies comprises three planetary gears which are meshed with the sun gears and gear rings which are meshed with the three planetary gears, one side of each planetary gear is fixedly connected with a planetary carrier assembly for outputting power, a differential gear is meshed between the gear rings in the two groups of planetary gear assemblies, the differential gear is connected with an external differential gear which is positioned outside the differential box body, and a control system is connected to the external differential gear in a transmission manner;
the control system comprises a worm in meshed connection with an external differential gear, one end of the worm is fixedly connected with a first gear, and the first gear is in meshed connection with a band-type brake motor.
The beneficial effects are that:
according to the application, through the cooperation arrangement among the band-type brake motor, the worm and the external differential wheel, the rotation speed difference between the left and right wheels of the automobile can be actively distributed, meanwhile, the wheels can be ensured to be limited to slide and simultaneously can be differentiated, the abrasion of tires can be reduced and the stability of the automobile in turning can be increased through actively distributing the rotation speed difference between the two wheels, and the differential part and the limited-slide part are separated in hardware, so that the device is convenient for independent maintenance and reduces the maintenance cost.
Preferably, springs are fixedly connected to two ends of the worm, one of the springs is fixedly installed on one side of the first gear, the other spring is installed at one end of the worm, pressure sensors are fixedly connected to two opposite sides of the springs, and an installation shell is rotatably connected to one side of the pressure sensors.
Preferably, the installation shell is fixedly installed on one side of the differential box body, an internal bottom wall of the installation shell is fixedly provided with a band-type brake motor, the output end of the band-type brake motor is fixedly connected with a second gear through a rotating shaft, and the second gear is meshed with the first gear.
Preferably, a control chip inside the band-type brake motor is in communication connection with an external main control chip, and the main control chip is also in communication connection with a speed measuring sensor and an inclination sensor.
Preferably, the power input shaft is connected with a first bevel gear in a key manner, the first bevel gear is meshed with a second bevel gear, the second bevel gear is arranged on a rotating shaft, one end of the rotating shaft extends out of the differential box, and one end of the rotating shaft extending out of the differential box is connected with a driving motor fixed on the differential box.
Preferably, the planet carrier assembly is respectively connected with the middle parts of the three planet gears in a rotating way through connecting shafts, and a power output shaft for outputting power is fixedly connected with the middle part of one side of the planet carrier assembly.
Preferably, the differential gear is meshed with the two gear rings, a transmission shaft is fixedly connected to the middle part of one side of the differential gear, and one end of the transmission shaft is fixedly connected with an external differential gear.
Preferably, the inner side wall of the gear ring is provided with a plurality of first teeth meshed with the planetary gears along the circumferential direction of the gear ring, the opposite side surfaces of the two gear rings are inclined surfaces, and the inclined surfaces of the gear ring are provided with a plurality of second teeth meshed with the differential gears.
Preferably, the output end of the power output shaft penetrates through the inner wall of the differential case and extends to the outside thereof.
Drawings
The accompanying drawings, which are included to provide a further understanding of the application and are incorporated in and constitute a part of this specification, illustrate embodiments of the application and together with the description serve to explain the application and do not constitute a limitation on the application. In the drawings:
FIG. 1 is a schematic top view of the present application;
FIG. 2 is a schematic diagram of the control part of the present application;
FIG. 3 is a schematic right-side elevational view of the planetary gear set of the present application;
FIG. 4 is a schematic left-hand structural view of the planetary gear set of the present application.
In the figure: 1. a differential case; 2. a gear ring; 3. a planetary gear; 4. a sun gear; 5. a planet carrier assembly; 6. a power output shaft; 7. a power input shaft; 8. a first bevel gear; 9. a second bevel gear; 10. a rotating shaft; 11. a driving motor; 12. a differential gear; 13. a transmission shaft; 14. an outer differential wheel; 15. a worm; 16. a first gear; 17. a spring; 18. a pressure sensor; 19. a second gear; 20. and a band-type brake motor.
Detailed Description
In order to make the objects, technical solutions and advantages of the present application more apparent, the technical solutions of the present application will be clearly and completely described below with reference to specific embodiments of the present application and corresponding drawings. It will be apparent that the described embodiments are only some, but not all, embodiments of the application. All other embodiments, which can be made by those skilled in the art based on the embodiments of the application without making any inventive effort, are intended to be within the scope of the application.
The following describes in detail the technical solutions provided by the embodiments of the present application with reference to the accompanying drawings.
Referring to FIGS. 1-4, a planetary gear differential control system; the differential box body 1 is symmetrically arranged in the differential box body 1, two groups of planetary gear assemblies and a power input shaft 7 which is in meshed connection with the two groups of planetary gear assemblies are symmetrically arranged in the differential box body 1, two ends of the power input shaft 7 are fixedly connected with a sun gear 4, each group of planetary gear assemblies comprises three planetary gears 3 which are in meshed connection with the sun gear 4 and a gear ring 2 which is meshed with the three planetary gears 3, one side of each planetary gear 3 is fixedly connected with a planet carrier assembly 5 which is used for outputting power, a differential gear 12 is meshed between the gear rings 2 in the two groups of planetary gear assemblies, the differential gear 12 is connected with an external differential gear 14 which is positioned outside the differential box body 1, and the external differential gear 14 is in transmission connection with a control system;
the control system comprises a worm 15 in meshed connection with an external differential gear 14, one end of the worm 15 is fixedly connected with a first gear 16, and the first gear 16 is in meshed connection with a band-type brake motor 20;
springs 17 are fixedly connected to two ends of the worm 15, one spring 17 is fixedly installed on one side of the first gear 16, the other spring 17 is installed at one end of the worm 15, pressure sensors 18 are fixedly connected to two opposite sides of the springs 17, and an installation shell is rotatably connected to one side of the pressure sensors 18;
the mounting shell is fixedly arranged on one side of the differential box body 1, the internal bottom wall of the mounting shell is fixedly provided with a band-type brake motor 20, the output end of the band-type brake motor 20 is fixedly connected with a second gear 19 through a rotating shaft, the second gear 19 is meshed with the first gear 16, two bearing seats are fixedly arranged on the internal bottom wall of the mounting shell, a worm 15 is slidably connected on the two bearing seats, and the worm 15 can conveniently move leftwards or rightwards under the drive of an external differential gear 14;
the control chip inside the band-type brake motor 20 is in communication connection with an external main control chip, and the main control chip is also in communication connection with a speed measuring sensor and an inclination angle sensor;
the power input shaft 7 is connected with a first bevel gear 8 in a key way, the first bevel gear 8 is meshed with a second bevel gear 9, the second bevel gear 9 is arranged on a rotating shaft 10, one end of the rotating shaft 10 extends out of the differential case 1, and one end of the rotating shaft 10 extending out of the differential case 1 is connected with a driving motor 11 fixed on the differential case 1;
the planet carrier assembly 5 is respectively and rotatably connected with the middle parts of the three planet gears 3 through connecting shafts, and a power output shaft 6 for outputting power is fixedly connected with the middle part of one side of the planet carrier assembly 5;
the differential gear 12 is meshed with the two gear rings 2, a transmission shaft 13 is fixedly connected to the middle part of one side of the differential gear 12, and one end of the transmission shaft 13 is fixedly connected with an external differential gear 14;
the inner side walls of the gear rings 2 are provided with a plurality of first teeth meshed with the planetary gears 3 along the circumferential direction of the inner side walls, the opposite side surfaces of the two gear rings 2 are inclined surfaces, and the inclined surfaces of the gear rings 2 are provided with a plurality of second teeth meshed with the differential gears 12;
the output end of the power output shaft 6 penetrates through the inner wall of the differential case 1 and extends to the outside of the differential case 1, and bearings are arranged at the joints of the power output shaft 6, the rotating shaft 10 and the transmission shaft 13 and the differential case 1 and are used for ensuring the normal rotation of the output shaft 6, the rotating shaft 10 and the transmission shaft 13, so that the differential case 1 is prevented from being worn;
when the device works, the driving motor 11 is electrically connected with an external power supply, and when the driving motor 11 is started, the power can be provided for the whole device, so that the normal operation of the device is ensured;
when the external differential gear 14 is in a free state, the driving motor 11 is started to drive the rotating shaft 10 and the second bevel gear 9 to rotate, so that the first bevel gear 8 and the power input shaft 7 can be driven to rotate, when the power input shaft 7 rotates, the sun gears 4 at two ends can be simultaneously driven to rotate, so that the planetary gears 3 at two ends can be simultaneously driven to rotate and rotate around the sun gears 4, when the planetary gears 3 rotate, the planetary carrier assembly 5 and the power output shaft 6 can be driven to rotate, so that power can be transmitted to driving wheels at two sides of a vehicle through the power output shaft 6, and at the moment, the driving wheels at two sides of the vehicle can be freely differentiated;
when the external differential gear 14 is in a locking state, the gear ring 2 is also in the locking state through the cooperation of the transmission shaft 13 and the differential gear 12, and at the moment, the planetary gears 3 on the left side and the right side can rotate around the sun gear 4 under the drive of the sun gear 4, so that the planet carrier assembly 5 can be driven to rotate, and further, the power can be transmitted to the driving wheels on the two sides of the vehicle through the power output shaft 6, and at the moment, the two sides of the vehicle cannot be differentiated and only can keep the same rotation speed;
when no slip occurs in the vehicle traveling in a straight line: the angle of the wheels is monitored through the inclination sensor, so that whether the vehicle runs straight or not is judged, the wheels on two sides of the vehicle do not generate rotation speed difference theoretically when running straight, but tiny rotation speed difference is generated if the abrasion degree of the tires of the vehicle is different, at the moment, the outer differential wheel 14 slowly rotates, so that the worm 15 is driven to move to one side, the spring 17 plays a buffering role, the value of the pressure sensor 18 on one side is slowly increased, the main control chip collects pressure data in real time to judge, if the data is slowly increased, the current rotation speed difference is judged not to be caused by slipping of the vehicle, the band-type brake motor 20 is controlled to rotate according to the vehicle speed and the pressure data, and the pressure on two sides of the pressure sensor 18 is always in a balanced state;
when the vehicle slides on the straight running side: when one side of the straight-line running vehicle suddenly slips, a rotation speed difference is suddenly generated between the two wheels, at the moment, the value of the pressure sensor 18 is suddenly increased, at the moment, the main control chip can judge that the vehicle is in a slipping state at present, the band-type brake motor 20 is controlled to be motionless, and further, the worm 15 and the external differential gear 14 are ensured to be motionless, so that the rotation speed difference is not distributed, or only a small rotation speed difference is distributed to offset the abrasion condition of one side of the tire, and therefore, all power exists between the two wheels;
when the vehicle turns without slipping: when turning, the two wheels should have rotational speed difference, the data of the inclination angle sensor will increase, then the main control chip calculates theoretical rotational speed difference according to the data monitored by the speed sensor in real time, then the band-type brake motor 20 is controlled to rotate, the rotational speed difference of the two wheels is actively distributed, if the two wheels are different in size, the actual speed difference and the calculated speed difference have small deviation, and at the moment, small-range speed compensation is needed according to the pressure values of the two sides;
when the vehicle turns and slips: still calculate the rotational speed difference of two-wheeled according to speed data and angle data, if skid, the pressure sensor 18 on both sides will have great numerical value, judges to skid the state this moment, can do the speed compensation of small range according to the numerical value of pressure sensor 18, can realize limiting the slip when differentiating.
The foregoing is merely exemplary of the present application and is not intended to limit the present application. Various modifications and variations of the present application will be apparent to those skilled in the art. Any modification, equivalent replacement, improvement, etc. which come within the spirit and principles of the application are to be included in the scope of the claims of the present application.

Claims (9)

1. The planetary gear differential control system comprises a differential box body, and is characterized in that two groups of planetary gear assemblies and a power input shaft which is meshed with the two groups of planetary gear assemblies are symmetrically arranged in the differential box body, sun gears are fixedly connected to two ends of the power input shaft, each group of planetary gear assemblies comprises three planetary gears which are meshed with the sun gears and gear rings which are meshed with the three planetary gears, one side of each planetary gear is fixedly connected with a planetary carrier assembly for outputting power, a differential gear is meshed between the gear rings in the two groups of planetary gear assemblies, the differential gear is connected with an external differential gear which is positioned outside the differential box body, and a control system is connected to the external differential gear in a transmission manner;
the control system comprises a worm in meshed connection with an external differential gear, one end of the worm is fixedly connected with a first gear, and the first gear is in meshed connection with a band-type brake motor.
2. The planetary gear differential control system according to claim 1, wherein springs are fixedly connected to both ends of the worm, one of the springs is fixedly mounted on one side of the first gear, the other spring is mounted on one end of the worm, pressure sensors are fixedly connected to opposite sides of the two springs, and a mounting housing is rotatably connected to one side of the pressure sensors.
3. The planetary gear differential control system according to claim 2, wherein the mounting housing is fixedly mounted on one side of the differential case, a band-type brake motor is fixedly mounted on an inner bottom wall of the mounting housing, an output end of the band-type brake motor is fixedly connected with a second gear through a rotating shaft, and the second gear is meshed with the first gear.
4. The planetary gear differential control system according to claim 3, wherein a control chip inside the band-type brake motor is in communication connection with an external main control chip, and the main control chip is also in communication connection with a speed sensor and an inclination sensor.
5. The planetary gear differential control system according to claim 1, wherein the power input shaft is keyed with a first bevel gear, the first bevel gear is meshed with a second bevel gear, the second bevel gear is mounted on a rotating shaft with one end extending out of the differential case, and a driving motor fixed on the differential case is connected to one end of the rotating shaft extending out of the differential case.
6. The planetary gear differential control system according to claim 1, wherein the carrier assemblies are respectively rotatably connected with the middle parts of the three planetary gears through connecting shafts, and a power output shaft for outputting power is fixedly connected with the middle part of one side of the carrier assemblies.
7. The planetary gear differential control system according to claim 1, wherein the differential gear is engaged with the two ring gears, a transmission shaft is fixedly connected to a middle portion of one side of the differential gear, and an external differential gear is fixedly connected to one end of the transmission shaft.
8. The planetary gear differential control system according to claim 1, wherein the inner side wall of the ring gear is provided with a plurality of first teeth engaging with the planetary gears along the circumferential direction thereof, two of the opposite sides of the ring gear are inclined surfaces, and the inclined surfaces of the ring gear are provided with a plurality of second teeth engaging with the differential gears.
9. The planetary gear differential control system of claim 6, wherein the output end of the power take-off shaft extends through the inner wall of the differential housing and out of the differential housing.
CN202310856056.6A 2023-07-12 2023-07-12 Planetary gear differential control system Withdrawn CN116658591A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN202310856056.6A CN116658591A (en) 2023-07-12 2023-07-12 Planetary gear differential control system

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN202310856056.6A CN116658591A (en) 2023-07-12 2023-07-12 Planetary gear differential control system

Publications (1)

Publication Number Publication Date
CN116658591A true CN116658591A (en) 2023-08-29

Family

ID=87728160

Family Applications (1)

Application Number Title Priority Date Filing Date
CN202310856056.6A Withdrawn CN116658591A (en) 2023-07-12 2023-07-12 Planetary gear differential control system

Country Status (1)

Country Link
CN (1) CN116658591A (en)

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Application publication date: 20230829