CN116512893A - Two-gear hub integrated electric driving wheel set and vehicle comprising same - Google Patents
Two-gear hub integrated electric driving wheel set and vehicle comprising same Download PDFInfo
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- CN116512893A CN116512893A CN202310230643.4A CN202310230643A CN116512893A CN 116512893 A CN116512893 A CN 116512893A CN 202310230643 A CN202310230643 A CN 202310230643A CN 116512893 A CN116512893 A CN 116512893A
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- 230000007246 mechanism Effects 0.000 claims abstract description 123
- 230000005540 biological transmission Effects 0.000 claims abstract description 61
- 230000009467 reduction Effects 0.000 claims description 27
- 230000007704 transition Effects 0.000 claims description 18
- 239000000725 suspension Substances 0.000 claims description 14
- 230000008878 coupling Effects 0.000 claims description 8
- 238000010168 coupling process Methods 0.000 claims description 8
- 238000005859 coupling reaction Methods 0.000 claims description 8
- 230000002093 peripheral effect Effects 0.000 claims description 3
- 230000001360 synchronised effect Effects 0.000 claims description 2
- 238000000034 method Methods 0.000 description 12
- 230000008569 process Effects 0.000 description 11
- 239000003638 chemical reducing agent Substances 0.000 description 7
- 230000007935 neutral effect Effects 0.000 description 6
- 238000010586 diagram Methods 0.000 description 5
- 230000033001 locomotion Effects 0.000 description 5
- 238000010438 heat treatment Methods 0.000 description 4
- 238000004519 manufacturing process Methods 0.000 description 3
- 230000009286 beneficial effect Effects 0.000 description 2
- 230000007547 defect Effects 0.000 description 2
- 230000007812 deficiency Effects 0.000 description 2
- 238000013461 design Methods 0.000 description 2
- 230000010354 integration Effects 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000035939 shock Effects 0.000 description 2
- 238000009423 ventilation Methods 0.000 description 2
- 230000009471 action Effects 0.000 description 1
- 230000009194 climbing Effects 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 238000009826 distribution Methods 0.000 description 1
- 238000004134 energy conservation Methods 0.000 description 1
- 238000010862 gear shaping Methods 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 230000009191 jumping Effects 0.000 description 1
- 238000003754 machining Methods 0.000 description 1
- 230000009347 mechanical transmission Effects 0.000 description 1
- 238000002360 preparation method Methods 0.000 description 1
- 238000012545 processing Methods 0.000 description 1
- 230000002035 prolonged effect Effects 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
- 238000000926 separation method Methods 0.000 description 1
- 239000007787 solid Substances 0.000 description 1
- 230000003068 static effect Effects 0.000 description 1
Classifications
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- H—ELECTRICITY
- H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
- H02K—DYNAMO-ELECTRIC MACHINES
- H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
- H02K7/006—Structural association of a motor or generator with the drive train of a motor vehicle
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K7/00—Disposition of motor in, or adjacent to, traction wheel
- B60K7/0007—Disposition of motor in, or adjacent to, traction wheel the motor being electric
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
- B60T1/00—Arrangements of braking elements, i.e. of those parts where braking effect occurs specially for vehicles
- B60T1/02—Arrangements of braking elements, i.e. of those parts where braking effect occurs specially for vehicles acting by retarding wheels
- B60T1/06—Arrangements of braking elements, i.e. of those parts where braking effect occurs specially for vehicles acting by retarding wheels acting otherwise than on tread, e.g. employing rim, drum, disc, or transmission or on double wheels
- B60T1/065—Arrangements of braking elements, i.e. of those parts where braking effect occurs specially for vehicles acting by retarding wheels acting otherwise than on tread, e.g. employing rim, drum, disc, or transmission or on double wheels employing disc
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- H—ELECTRICITY
- H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
- H02K—DYNAMO-ELECTRIC MACHINES
- H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
- H02K7/10—Structural association with clutches, brakes, gears, pulleys or mechanical starters
- H02K7/116—Structural association with clutches, brakes, gears, pulleys or mechanical starters with gears
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- 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
- Y02T10/80—Technologies aiming to reduce greenhouse gasses emissions common to all road transportation technologies
- Y02T10/86—Optimisation of rolling resistance, e.g. weight reduction
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- Engineering & Computer Science (AREA)
- Power Engineering (AREA)
- Transportation (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Retarders (AREA)
Abstract
The invention discloses a two-gear hub integrated electric driving wheel set and a vehicle comprising the same. The whole set of electric drive system is arranged in the hub, so that the space utilization rate of the vehicle is greatly improved, the space arrangement of the vehicle is more flexible, the structure is more compact, and the transmission efficiency is high. In addition, the vehicle provided by the invention can realize different transmission ratios by adjusting different meshing relations between the gear shifting mechanism and the planetary gear train speed reducing mechanism, so that the vehicle is driven to output at different speed ratios, and the vehicle is suitable for complex and various running requirements.
Description
Technical Field
The invention relates to the technical field of electric drive wheel sets, in particular to a two-gear hub integrated electric drive wheel set and a vehicle comprising the same.
Background
In recent years, new energy automobiles are affected by global energy conservation and emission reduction, and rapid development is achieved. At present, the new energy automobile mainly uses electric drive, the driving mode mainly comprises a central driving mode and a distributed driving mode, compared with the central driving mode, the power source is single, the transmission system is more complex, the preparation quality is large, the distributed driving mode integrates the components such as a motor, a speed reducer mechanism, a hub and the like into a whole and places the components in the wheel, the components such as a clutch, a transmission system, a mechanical differential mechanism and the like in the traditional central driving system are abandoned, the mechanical transmission structure is simplified, and the vehicle-mounted dead weight is reduced. In addition, the distributed driving occupies less space, and each wheel is driven by an independent motor, so that the distributed driving is more flexible.
The distributed hub electric drive vehicle is generally provided with a single speed reducer, is usually hard to express in front of complex and various terrain road conditions, and particularly for vehicles which need to pass through various complex road conditions, such as all-terrain vehicles, off-road vehicles and the like, the single speed reducer often cannot meet the running requirements of vehicles with high performance requirements, for example, when the vehicles run on a road surface with a larger gradient, a low-speed and high-torque reducer needs to be provided, and when the vehicles need a higher running speed, a high-speed and low-torque reducer needs to be provided; in addition, a single speed reducer cannot keep the driving motor within a relatively ideal operating characteristic range.
The published patent "second gear speed-changing hub motor driving device" (application number: cn201610842890. X) provides that the switching of the gear, neutral and high gears is achieved by combining the gear sleeve to reciprocate in the axial direction, however, the combined gear sleeve in this structure has the following disadvantages: (1) The structure diagram shows that the combined tooth sleeve occupies a larger space in the rim, and the radial and axial dimensions are larger, so that the structural mass is increased, and the design principle of light structure cannot be realized; (2) The gear shifting mechanism is combined with the last-stage planetary gear train to jointly realize a high-low gear mode, and the driving force output by the driving motor can generate larger moment after being amplified by the first two-stage planetary gear reduction, and the mode can cause larger gear shifting impact on gear shifting combining teeth in the gear shifting process, so that the service life of the gear shifting combining teeth is shortened.
The publication "an electric vehicle double-reduction driving device" (application number: CN 202020551939.8) provides an in-wheel motor with a planetary reduction mechanism, however, in this structure, the motor rotor is always in rotary motion, which affects the arrangement of the shift driving lever.
Therefore, the arrangement of the distributed hub which can realize compact layout and light weight, ensure the high-efficiency operation of the motor under different road conditions and improve the power economy and the strength reliability of the vehicle is still required to be improved.
Disclosure of Invention
In order to overcome the defects in the prior art, the invention provides a two-gear hub integrated electric driving wheel set and a vehicle comprising the electric wheel set, and the technical scheme of the invention is as follows:
as a first aspect of the present invention, there is provided a two-gear hub integrated electric drive wheel set including a front end housing, a middle section housing i, a middle section housing ii, a rear end housing, a drive motor, a fixed gear train reduction mechanism, a first planetary gear train reduction mechanism, a second planetary gear train reduction mechanism, a gear shift mechanism, a transition flange, and a rim;
the driving motor, the front end shell and the middle section shell I are positioned on the outer side of the rim, and the driving motor and the front end shell are of an integrated structure; one end of the middle section shell II is connected with the middle section shell I, and the other end of the middle section shell II penetrates through the rim and then is connected with the rear end shell. The front end shell, the middle section shell I, the middle section shell II and the rear end shell are sequentially connected, and toe openings are formed in the connecting positions of the two adjacent shells so as to ensure the transmission precision requirement of coaxial arrangement of the transmission mechanism; the output shaft of the driving motor is connected with the input shaft of the fixed-axis gear train speed reducing mechanism, and the output power of the high-speed driving motor is transmitted to the wheels sequentially through the fixed-axis gear train speed reducing mechanism, the first planetary gear train speed reducing mechanism, the second planetary gear train speed reducing mechanism, the transition flange plate and the rim;
The gear shifting mechanism is arranged between the first planetary gear train speed reducing mechanism and the second planetary gear train speed reducing mechanism;
the first planetary gear train speed reducing mechanism comprises a first sun gear, a first planetary shaft, a first gear ring, a first inner planet carrier, a first outer planet carrier and a gear ring carrier;
the gear shifting mechanism comprises a fixed bracket, a joint sleeve, a first spline hub and a second spline hub, and power is transmitted between the gear shifting mechanism and a gear ring bracket combining tooth and a first outer planet carrier combining tooth in the first planet gear system speed reducing mechanism in a matched mode; the gear ring support of the first planetary gear train speed reducing mechanism is supported on a fixed support in the gear shifting mechanism through two angular contact ball bearings, and a boss is arranged on the fixed support and used as a shaft shoulder of the two angular contact ball bearings; the joint sleeve is arranged at the periphery of the fixed bracket and the first spline hub; the fixed support in the gear shifting mechanism is fixedly connected to the middle section shell I and is provided with a spline connected with the engagement sleeve matched teeth, the first spline hub and the second spline hub are respectively axially fixed on the gear ring support and the first outer planet carrier by using snap springs, the inner ring spline of the first spline hub is connected with the combination teeth of the gear ring support in a matched mode, the inner ring spline of the second spline hub is connected with the combination teeth of the first outer planet carrier in a matched mode, and the fixed support, the first spline hub and the outer ring spline of the second spline hub are connected with the combination teeth of the joint sleeve in a matched mode.
In the structure provided by the invention, the gear shifting driving system and the power transmission system are coaxially arranged, so that the compactness of the axial direction of the whole structure is improved, meanwhile, the joint sleeve provided by the invention is arranged at the central shaft of the first outer planet carrier, the radial and axial dimensions of the gear shifting joint sleeve are smaller, the structure is more compact, other parts are convenient to arrange, and the torsion resistance and the structural strength of the gear shifting mechanism are enhanced.
Preferably, the fixed gear train speed reducing mechanism comprises a high-speed gear shaft, a low-speed gear and a low-speed gear shaft, wherein the high-speed gear shaft is fixedly connected with an output shaft of the driving motor, the low-speed gear is arranged on the periphery of one end of the low-speed gear shaft, and peripheral teeth of the high-speed gear shaft are meshed with the low-speed gear shaft to transmit power to the low-speed gear shaft; the high-speed gear shaft and the low-speed gear are respectively arranged at the connecting positions of the front end shell and the middle section shell I and are supported by adopting deep groove ball bearings, so that the transmission precision of the fixed-axis gear train can be ensured.
Preferably, in the first planetary gear train speed reducing mechanism, the first sun gear inner ring is provided with an internal spline, connected with the low-speed gear shaft, the outer ring is meshed with the first planetary gear, the first planetary gear is sleeved on the first planetary shaft through a needle bearing and rotates relative to the first planetary shaft, the first inner planetary gear and the first outer planetary gear are both provided with holes matched with the first planetary shaft, two ends of the first planetary gear are respectively supported in the first outer planetary gear and the first inner planetary gear train speed reducing mechanism through interference and clearance fit, the first inner planetary gear and the first outer planetary gear train are respectively supported on the second outer planetary gear train speed reducing mechanism through tapered roller bearings, and in addition, wear between the two ends of the first sun gear and the first planetary gear and the first inner planetary gear and between the first outer planetary gear and wear between the first sun gear, the first inner planetary gear and the first outer planetary gear are respectively provided with a heat treatment pad. The first gear ring is meshed with the first planet gears and the gear ring support respectively through meshing teeth, the combined tooth heights of the first gear ring and the first planet gears are larger than those of the gear ring support, the combined tooth height difference on the first gear ring can play a role in positioning a shaft shoulder and is matched with a clamp spring, the gear ring support is axially fixed on the first gear ring, and the gear ring support and the first outer planet carrier are respectively provided with combined teeth matched with a gear shifting mechanism.
Preferably, the second planetary gear train reduction mechanism includes: the second sun gear, the second planet gears, the second planet shafts, the second gear ring, the second inner planet carrier and the second outer planet carrier. The inner ring of the second sun gear is provided with an internal spline, the second sun gear is connected with the first outer planet carrier, the outer ring is meshed with the second planet gear, the second planet gear is sleeved on the second planet shaft through a needle bearing in an empty mode and rotates relative to the second planet shaft, the second inner planet carrier and the second outer planet carrier are both provided with holes matched with the second planet shaft, two ends of the second planet shaft are respectively supported in the second outer planet carrier and the holes matched with the second inner planet carrier in an interference and clearance fit mode, and the second inner planet carrier and the second outer planet carrier are respectively supported on the middle section shell II and the rear end shell through tapered roller bearings. In addition, in order to reduce wear between the two ends of the second sun gear and the second planet gears and between the second inner planet carrier and the second outer planet carrier in the meshing movement process, gaskets with higher hardness after heat treatment are respectively arranged among the second sun gear, the second planet gears and the second inner planet carrier and the second outer planet carrier. Furthermore, in order to follow the principles of high transmission efficiency, small volume, light weight and easy manufacture, the gear transmission types in the first planetary gear train speed reducing mechanism and the second planetary gear train speed reducing mechanism are both NGW type.
Preferably, the gear shifting mechanism is arranged between the first planetary gear train speed reducing mechanism and the second planetary gear train speed reducing mechanism, and the outer surface of the joint sleeve is I-shaped.
Specifically, in the gear shifting mechanism, larger chamfers are formed at two ends of a spline at the spline fit positions of the joint sleeve, the fixed support and the second spline hub, so that the joint sleeve can be ensured to smoothly slide to the fixed support or the second spline hub.
The width of the engagement sleeve is less than the width of the outer spline coupling teeth in the first spline hub.
Preferably, the two-gear hub integrated electric driving wheel set provided by the invention further comprises a gear shifting driving mechanism, wherein the gear shifting driving mechanism comprises: the gear shifting fork, the bevel gear shifting fork shaft, the driving bevel gear shaft, the driving device and the oil seal seat are respectively supported in the middle section shell II through an angular contact ball bearing, the gear shifting fork is clamped in the middle of the I-shaped outer surface of the joint sleeve, the bevel gear shifting fork shaft and the driving bevel gear shaft are in meshed transmission through a bevel gear structure, the bevel gear shifting fork shaft penetrates through the gear shifting fork, the gear shifting fork and the bevel gear shifting fork shaft are respectively provided with rectangular or trapezoidal transmission threads at the contact position to realize transmission, the driving device is connected to the driving bevel gear shaft to provide rotary power for the driving bevel gear shaft, the driving bevel gear shaft penetrates through the oil seal seat fixed to the middle section shell II through a thread structure, the output power of the driving device is transmitted to the threaded matching position of the bevel gear shifting fork shaft and the gear shifting fork after being meshed and changed, the bevel gear shifting fork shaft is driven to rotate under the action of the angular contact ball bearing, and then moves relative to the joint sleeve by means of the rectangular or trapezoidal transmission threads at the matched position.
The driving mode of the driving device in the gear shifting driving mechanism is electric or electromagnetic driving. The driving bevel gear shaft is provided with an external spline at the other end of the bevel gear, and is matched with an internal spline of the driving device to realize power transmission.
Furthermore, the invention also comprises a Vehicle Control Unit (VCU), wherein the vehicle control unit is respectively connected with the driving motors of the wheels in a model mode, and sends out different torque signals to the four driving motors. Typically, the electric wheel set is operated in a high gear and is shifted to a low gear state only when a torque deficiency is encountered.
In addition, in order to avoid the collision impact of the combination teeth caused by the high rotation speed difference in the gear shifting process, the driving device is matched with the driving motor in a coordinated manner, namely when the driving device drives the engagement sleeve to slide to a neutral position, the driving motor rapidly adjusts the speed according to the rotation speed of the engagement sleeve, so that the rotation speed difference of the combination teeth tends to be minimum, and gear shifting is realized.
Preferably, the gear shifting driving device is a servo motor or a stepping motor.
Specifically, oil sealing devices are arranged between the front end shell and the high-speed gear shaft, between the middle section shell II and the driving bevel gear shaft, and between the rear end shell and the second outer planet carrier. In order to maintain the stable air pressure in the wheel set, the middle section shell I is provided with a ventilation plug.
Preferably, the two-gear hub integrated electric drive wheel set further comprises a braking system, wherein the braking system comprises a brake caliper and a brake disc, and the brake caliper is fixedly connected to the rear end shell. The transition flange plate is fixedly connected with the brake disc and the rim, and a toe opening matched with the rim is formed in the transition flange plate in order to ensure the coaxiality requirement of the wheel and the transmission system. The conical surface interference connection between the transition flange plate and the second outer planet carrier is realized by means of stud bolts and hexagonal flange surface nuts.
As a second aspect of the present invention, there is also provided a vehicle comprising the two-speed hub integrated electric drive wheel set connected to a frame of the vehicle through an upper suspension swing arm mount fixed to an upper end of the center section housing i and a lower suspension swing arm mount fixed to a lower end of the center section housing i, respectively.
Compared with the prior art, the invention has the beneficial effects that:
the power system, the transmission system and the braking system are arranged in the hub, the gear shifting driving system and the power transmission system are coaxially arranged to increase the compactness of the structure in the axial direction, meanwhile, the joint sleeve is arranged at the central shaft of the first outer planet carrier, and the radial and axial dimensions of the gear shifting joint sleeve are small, so that the structure is more compact, and other parts are convenient to arrange; the invention selects the disc brake to arrange the brake caliper in the radial direction of the wheel edge so as to fully utilize the radial size space of the structure.
2, the gear shifting transmission system provided by the invention is a two-gear three-stage speed reducer, wherein the arrangement of the fixed-axis gear train speed reducing mechanism in the gear shifting transmission system can bias the high-speed driving motor, so that more space is reserved for the arrangement of the lower swing arm of the suspension, and the phenomenon that the gear shifting transmission system is interfered with the high-speed driving motor when the downward jumping travel of the automobile suspension reaches the maximum is avoided; the gear shifting driving mode is electric control and electric, so that the accuracy and operability of gear shifting are guaranteed. The fixed-axis gear train reducing mechanism, the first planetary gear train reducing mechanism and the second planetary gear train reducing mechanism are combined and matched with a gear shifting transmission arrangement mode, so that transmission ratio distribution in a transmission system is more flexible.
And 3, the gear shifting mechanism is respectively combined with the gear ring support of the first planetary gear train speed reducing mechanism and the outer planet carrier through the matching teeth of the two spline hubs, the transmission ratio of the first planetary gear train speed reducing mechanism is controlled through the joint and the separation of the joint sleeve and the spline hubs, meanwhile, the gear shifting mechanism is matched with the planetary gear train speed reducing mechanism, so that a larger transmission ratio difference can be ensured between a high-speed gear and a low-speed gear, the requirements of a vehicle on two different working conditions of low-speed high torque and high-speed low torque are met, the vehicle is better adapted to complex running road conditions, meanwhile, the output torque is improved, the motor always works in a high-efficiency interval, the power economy of the vehicle is improved, and the running mileage is prolonged.
And 4, the gear shifting driving mechanism adopts a bevel gear meshing reversing mode and combines a threaded transmission mode to drive a gear shifting fork to axially move, so that a joint sleeve is driven to realize gear shifting.
And 5, the gear shifting driving mode is electric or electromagnetic driving, so that the gear shifting driving mode is high in precision, easy to control, accurate in reflection, high in reliability and more beneficial to integration. The gear shifting process is coordinated with the gear shifting driving mechanism through the high-speed driving motor, so that the gear shifting structure is simpler, and the feasibility of gear shifting without a synchronizer is realized.
The power output of the second planetary gear train speed reducing mechanism is ensured by means of interference fit of the conical surfaces of the second outer planet carrier and the transition flange, the axial space is effectively utilized, larger output torque can be transmitted, the output is stable, the impact problem caused by meshing gaps in spline connection is avoided, meanwhile, in order to ensure centering of the conical surface fit, the central positions of the second outer planet carrier and the transition flange are connected by adopting a double-end stud and a hexagonal flange nut, and the eccentric problem of the conical surface fit caused by a gap between the second outer planet carrier and the transition flange is prevented. In addition, the two end faces of the transition flange plate are respectively matched with the brake disc and the rim, and are fastened through the wheel bolt and the nut, so that the structure has a central positioning function, and the problem that the wheel bolt and the nut are tightened and then the rim presses the brake disc to deform the brake disc can be prevented.
And 7, the engagement sleeve provided by the invention is matched with the first spline hub and the second spline hub which are connected with the gear ring support to finish the gear shifting process, the matched positions of the engagement sleeve and the first spline hub and the second spline hub are tightly attached to the central shaft, the radial size is small, the defect that the strength is weakened due to the fact that the radial size of the conventional engagement sleeve is large and a certain torsion force is generated is avoided, and the structural strength is improved.
8, the device fully utilizes the axial and radial dimensions of the structure, has compact structure, more flexible overall arrangement, light weight, high integration level and high transmission efficiency, and the arrangement of the gear shifting mechanism greatly improves the climbing, trench crossing and obstacle crossing capabilities of the vehicle, thereby being particularly suitable for the cross-country vehicles with four-wheel drive and rugged working pavement.
Drawings
The accompanying drawings, which are included to provide a further understanding of the invention and are incorporated in and constitute a part of this specification, illustrate embodiments of the invention and together with the description serve to explain the invention.
FIG. 1 is an assembled cross-sectional view of an electrically driven wheelset of the present invention;
FIG. 2 is a three-dimensional block diagram of an electrically driven wheelset of the present invention;
FIG. 3 is a diagram of the shift transmission of the electric drive wheel set of the present invention;
FIG. 4 is a block diagram of a low gear of the electric drive wheel set of the present invention;
FIG. 5 is a block diagram of a high gear of the electric drive wheel set of the present invention;
FIG. 6 is an exploded view of a first planetary gear train of the electrically-driven wheelset of the present invention;
FIG. 7 is an exploded view of the shifting mechanism and the shifting drive mechanism of the present invention;
FIG. 8 is an exploded view of the second planetary gear train and wheel-side transmission structure of the electrically driven wheelset of the present invention;
the high-speed drive motor, the 2-front end housing, the 3-suspension upper swing arm support, the 4-suspension lower swing arm support, the 5-middle section housing I, the 6-vent plug, the 7-high-speed gear shaft, the 8-low-speed gear shaft, the 9-low-speed gear, the 10-first sun gear, the 11-first planetary gear, the 12-first planetary gear shaft, the 13-first gear ring, the 14-first inner planetary gear, the 15-first outer planetary gear, the 16-gear ring support, the 17-fixed support, the 18-joint sleeve, the 19-first spline hub, the 20-second spline hub, the 21-shift fork, the 22-bevel gear shift fork shaft, the 23-drive device, the 24-driving bevel gear shaft, the 25-oil seal seat, the 26-middle section housing II, the 27-second inner planetary gear shaft, the 28-second sun gear, the 29-second gear ring, the 30-second planetary gear, the 31-second planetary gear shaft, the 32-second outer planetary gear shaft, the 33-transition flange disc, the 34-hexagonal flange nut, the 35-second planetary gear disc, the 36-brake caliper, the 37-brake caliper, the 38-brake disc, the 37-brake disc, the 101-brake mechanism, the brake disc, the brake system, the brake disc and the brake system, the brake system and the brake system.
Detailed Description
It should be noted that the following detailed description is exemplary and is intended to provide further explanation of the invention. Unless defined otherwise, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this invention belongs.
It is noted that the terminology used herein is for the purpose of describing particular embodiments only and is not intended to be limiting of exemplary embodiments according to the present invention. As used herein, the singular is also intended to include the plural unless the context clearly indicates otherwise, and furthermore, it is to be understood that the terms "comprises" and/or "comprising" when used in this specification are taken to specify the presence of stated features, steps, operations, devices, components, and/or combinations thereof.
Example 1: two-gear hub integrated type electric driving wheel set
As shown in fig. 1 to 3, a two-gear hub integrated electric drive wheel set includes a front end housing 2, a middle section housing i 5, a middle section housing ii 26, a rear end housing 39, a high-speed drive motor 1, a fixed-axis gear train reduction mechanism 101, a first planetary gear train reduction mechanism 102, a second planetary gear train reduction mechanism 103, a gear shift mechanism 201, a gear shift drive mechanism 202, a transition flange 33, a suspension upper swing arm support 3, a suspension lower swing arm support 4, a brake system 301, and a rim 38.
The high-speed driving motor 1, the front end housing 2 and the middle section housing I5 are positioned outside the rim 38, the high-speed driving motor 1 and the front end housing 2 are connected in a mode of adopting a common end cover, namely one end of the front end housing 2 is used as the front end cover of the high-speed driving motor, so that the integrated design of the motor and the housing is realized, the front end housing 2, the middle section housing I5, the middle section housing II 26 and the rear end housing 39 are sequentially connected, and toe openings are formed in the connecting positions of the two adjacent housings, so that the requirement of the transmission precision of the coaxial arrangement of the transmission mechanism is ensured. An output shaft of the high-speed driving motor 1 is connected with an input shaft of the fixed-axis gear train speed reducing mechanism 101, and output power of the high-speed driving motor 1 is transmitted to wheels sequentially through the fixed-axis gear train speed reducing mechanism 101, the first planetary gear train speed reducing mechanism 102, the second planetary gear train speed reducing mechanism 103, the transition flange 33 and the rim 38. The power is transmitted between the high-speed driving motor 1 and the second planetary gear train reduction mechanism 102 in a gear tooth meshing mode, and the power is transmitted between the output shaft of the second planetary gear train reduction mechanism 102 and the transition flange 33 in a conical interference fit mode.
The fixed gear train speed reducing mechanism 101 includes: the high-speed gear shaft 7 is an input shaft of the fixed-axis gear train speed reducing mechanism 101 and is in spline connection with an output shaft of the high-speed driving motor 1, the low-speed gear 9 is fixedly arranged on the periphery of one end of the low-speed gear shaft 8, peripheral teeth of the high-speed gear shaft 7 are meshed with the low-speed gear 9, and power is transmitted to the low-speed gear shaft 8; the high-speed gear shaft 7 and the low-speed gear 9 are respectively arranged between the front end shell 2 and the middle section shell I5 and are respectively supported by deep groove ball bearings, so that the transmission precision of the fixed-axis gear train can be ensured. As shown in fig. 1 and 6, the first planetary gear train reduction mechanism 102 is provided at the other end of the low-speed gear shaft 8, and structurally includes: the first sun gear 10, the first planet gears 11, the first planet shaft 12, the first gear ring 13, the first inner planet carrier 14, the first outer planet carrier 15 and the gear ring carrier 16, wherein the inner ring of the first sun gear 10 is provided with an inner spline which is connected with the low-speed gear shaft 8 in a matching way, the outer ring of the first sun gear 10 is meshed with the first planet gears 11, the first planet gears 11 are sleeved on the first planet shaft 12 in a hollow way through needle bearings and do rotary motion relative to the first planet shaft 12, the first planet gears 11 are arranged between the first inner planet carrier 14 and the first outer planet carrier 15, the first inner planet carrier 14 and the first outer planet carrier 15 are respectively provided with holes matched with the first planet shaft 12, the two ends of the first planet axle 12 are respectively supported in the holes where the first outer planet carrier 15 and the first inner planet carrier 14 are matched in an interference and clearance fit manner, the first inner planet carrier 14 and the first outer planet carrier 15 are respectively supported on the middle section casing i 5 and the second outer planet carrier 32 through tapered roller bearings, and in addition, in order to reduce wear between the two ends of the first sun gear 10 and the first planet gear 11 and between the first inner planet carrier 14 and the first outer planet carrier 15 in the meshing movement process, gaskets with higher hardness after heat treatment are respectively arranged between the first sun gear 10, the first planet gear 11 and the first inner planet carrier 14 and the first outer planet carrier 15. The first gear ring 13 is arranged on the periphery of the first planet wheel 11, meshing teeth meshed with the first planet wheel 11 and the gear ring support 16 are respectively arranged on the inner ring of the first gear ring 13, the combined tooth height of the first gear ring 13 and the first planet wheel 11 is larger than that of the first gear ring support 16, the combined tooth height difference on the first gear ring 13 can play a role in shaft shoulder positioning and is matched with a clamp spring, the gear ring support 16 is axially fixed on the first gear ring 13, and combining teeth matched with the first gear ring 13 and a first spline hub 19 in a gear shifting mechanism are respectively arranged on the gear ring support 16. As shown in fig. 6, the first outer planet carrier 15 includes a carrier body located at the periphery of the first planet wheel 11 and a central shaft connected to the carrier body, the central shaft of the first outer planet carrier 15 is solid, combined teeth matched with the second spline hub 20 in the gear shifting mechanism and the second sun gear in the second planetary gear train reduction mechanism are respectively arranged on the outer part, the gear ring support 16 is supported on a fixed support 17 in the gear shifting mechanism through two angular contact ball bearings, a boss is arranged on the fixed support 17 as the shoulders of the two angular contact ball bearings, and is matched with a snap spring to perform an axial limiting function on the first gear ring 13, so that a gap between the first outer planet carrier 15 and the gear ring support 16 is ensured.
As shown in fig. 1 and 8, the second planetary gear train reduction mechanism 103 includes: a second sun gear 28, second planet gears 30, second planet shafts 31, a second ring gear 29, a second inner planet carrier 27, a second outer planet carrier 32. The second planet wheel 30 is disposed between the second inner planet carrier 27 and the second outer planet carrier 32, the inner ring of the second sun gear 28 is provided with an inner spline, and is connected with the central shaft of the first outer planet carrier 15 in a matching manner, the first outer planet carrier 15 is used as an input shaft of a second planetary gear train speed reducing mechanism, the outer ring of the second sun gear 28 is meshed with the second planet wheel 30, the second planet wheel 30 is sleeved on the second planet shaft 31 in an empty manner through a needle bearing and rotates relative to the second planet shaft 31, the second inner planet carrier 27 and the second outer planet carrier 32 are both provided with holes matched with the second planet shaft 31, two ends of the second planet shaft 31 are respectively supported in the holes matched with the second outer planet carrier 32 and the second inner planet carrier 27 in an interference and clearance fit manner, and the second inner planet carrier 27 and the second outer planet carrier 32 are respectively supported on the housing II 26 and the rear end housing 39 through tapered roller bearings. In addition, in order to reduce wear between both ends of the second sun gear 28 and the second planetary gears 30 and between the second inner carrier 27 and the second outer carrier 32 during the meshing movement, shims having a high hardness after heat treatment are provided between the second sun gear 28, the second planetary gears 30 and the second inner carrier 27 and the second outer carrier 32, respectively. The end of the first outer carrier 15 is supported on the second outer carrier 32 by angular ball bearings. In order to follow the principles of high transmission efficiency, small volume, light weight and easy manufacture, the two groups of planetary gear transmission types are NGW type.
Specifically, the gear matching parameters of the first gear ring 13 and the gear ring support 16 are the same as the gear parameters of the first gear ring 13, and the first gear ring 13 can be formed by one-step machining.
As shown in fig. 1 and 7, the shift mechanism 201 is provided between the first planetary gear train reduction mechanism 102 and the second planetary gear train reduction mechanism 103, and includes: the gear shifting mechanism 201 is matched with the gear ring support 16 coupling teeth and the first outer planet carrier 15 coupling teeth in the first planetary gear train speed reducing mechanism 201 to transmit power, and the fixed support 17, the joint sleeve 18, the first spline hub 19 and the second spline hub 20 are arranged on the gear shifting mechanism. The gear ring bracket 16 is supported on a fixed bracket 17 in the gear shifting mechanism through two angular contact ball bearings; the outer surface of the joint sleeve 18 is I-shaped and is arranged at the periphery of the fixed bracket 17 and the first spline hub 19; the fixed support 17 in the gear shifting mechanism 201 is fixedly connected to the middle section casing i 5, and is provided with a spline connected with the engagement sleeve 18 in a matched manner, the first spline hub 19 and the second spline hub 20 are respectively axially fixed on the gear ring support 16 and the first outer planet carrier 15 by using snap springs, an inner spline of the first spline hub 19 is connected with a combined tooth of the gear ring support 16 in a matched manner, an inner spline of the second spline hub 20 is connected with a combined tooth of the first outer planet carrier 15 in a matched manner, and the fixed support 17, the first spline hub 19 and an outer spline of the second spline hub 20 are all connected with the combined tooth of the engagement sleeve 18 in a matched manner.
The transmission method of the two-gear hub integrated electric driving wheel set provided by the invention is that, as shown in fig. 4, when the combination teeth of the joint sleeve 18 are simultaneously engaged with the outer ring splines of the fixed bracket 17 and the first spline hub 19, the first gear ring 13 is kept in a static state, and the transmission state of the first planetary gear system speed reducing mechanism 102 is as follows: the power is input by the first sun gear 10, a larger reduction transmission ratio is realized after the first planet gears 11, the first sun gear 10 and the first gear ring 13 are matched for transmission, the power is output by the first outer planet carrier 15, at the moment, the first planet train reduction mechanism 102, the fixed shaft train reduction mechanism 101 and the second planet train reduction mechanism 103 form a three-stage reduction mechanism, namely, low-gear transmission is realized, and the low-gear transmission ratio is the product of the fixed shaft train, the first planet train and the second planet train; as shown in fig. 5, when the coupling teeth of the coupling sleeve 18 are simultaneously engaged with the outer ring splines of the first spline hub 19 and the second spline hub 20, the first gear ring 13 and the first outer planet carrier 15 will always maintain synchronous rotation speed, and after the power is input by the first sun gear 10, a 1:1 transmission ratio will be maintained and output by the first outer planet carrier 15, at this time, since the transmission ratio of the first planetary gear train reduction mechanism 102 is 1:1, the three-stage reduction mechanism is reduced to a two-stage reduction mechanism, that is, a high-gear transmission, and the high-gear transmission ratio is the product of the fixed-axis gear train and the second planetary gear train transmission ratio.
Specifically, in the gear shifting mechanism 201, at the position where the engagement sleeve 18 is in spline fit with the fixed bracket 17 and the second spline hub 20, both ends of the spline are provided with larger chamfers, so that the engagement sleeve 18 is ensured to smoothly slide to the fixed bracket 17 or the second spline hub 20.
The shift drive mechanism 202 includes: the gear shifting fork 21, the bevel gear shifting fork shaft 22, the driving bevel gear shaft 24, the driving device 23 and the oil seal seat 25, wherein the bevel gear shifting fork shaft 22 and the driving bevel gear shaft 24 are respectively supported in the middle section shell II 26 through angular contact ball bearings, the gear shifting fork 21 is clamped in the middle of the I-shaped outer surface of the joint sleeve 18, the bevel gear shifting fork shaft 22 and the driving bevel gear shaft 24 are in meshed transmission through a bevel gear structure, the bevel gear shifting fork shaft 22 penetrates through the gear shifting fork 21, the gear shifting fork 21 and the bevel gear shifting fork shaft 22 are respectively provided with rectangular or trapezoidal transmission threads at the contact position, the driving device 23 is connected to the driving bevel gear shaft 24 to provide rotary power for the driving bevel gear shaft 24, the driving bevel gear shaft 24 penetrates through the oil seal seat 25 fixed to the middle section shell II 26 through a thread structure, the output power of the driving bevel gear shaft 23 is transmitted to the bevel gear shifting fork shaft 22 after being meshed and changed in directions through the bevel gear between the driving bevel gear shaft 24 and the gear shifting fork shaft 22, the power is transmitted to the bevel gear shifting fork shaft 22 and the bevel gear shifting fork shaft 21 at the matched position, the gear shifting fork shaft 22 is in the matched position of the rectangular or trapezoidal transmission threads at the contact position, the gear shifting fork shaft 22 is in the matched with the angular contact position of the bevel gear shaft, and the bevel gear shaft is in the matched with the rectangular or trapezoidal transmission threads at the gear shifting fork shaft 22, and the rotary power is in the matched position with the gear shaft. The drive means 23 of the gear shift drive 202 is electrically or electromagnetically driven. The driving bevel gear shaft 24 is provided with an external spline at the other end of the bevel gear, and is matched with an internal spline of the driving device 23 to realize power transmission.
The invention also comprises a Vehicle Control Unit (VCU), wherein the vehicle control unit is respectively connected with the high-speed driving motors of the wheels in a model mode, and sends out different torque signals to the four motors. Typically, the electric wheel set is operated in a high gear and is shifted to a low gear state only when a torque deficiency is encountered.
In addition, in order to avoid the collision impact of the coupling teeth caused by the high rotational speed difference during the gear shifting process, the driving device 23 is in coordination with the high-speed driving motor 1, that is, when the driving device 23 drives the engagement sleeve 18 to slide to the first spline hub 19, at this time, the internal spline of the engagement sleeve 18 is only meshed with the external spline of the first spline hub, and is disengaged from the external spline of the fixed bracket 17 and the external spline of the second spline hub 20, that is, the engagement sleeve 18 is in a neutral position, and the width of the engagement sleeve 18 should be slightly smaller than the width of the external spline coupling teeth in the first spline hub 19; after entering the neutral position, when the high-speed mode is to be entered, the driving device 23 drives the engagement sleeve 18 to slide rightwards from the neutral position, and at the moment, the internal spline of the engagement sleeve 18 and the external spline of the first spline hub 19 and the second spline hub 20 are simultaneously meshed for transmission; when the low gear mode is to be entered, the driving device 23 drives the engagement sleeve 18 to slide leftwards from the neutral position, at which time the internal splines of the engagement sleeve 18 simultaneously engage with the external splines of the first spline hub 19 and the stationary bracket 17 for transmission. In the gear shifting process, only the second spline hub 20 rotates along with the first outer planet carrier 15 during the running process of the vehicle, and the first gear ring 13 enters a free mode state, so that great gear shifting impact is not caused when the gear shifting process is switched to a low-speed gear mode, and great gear shifting impact is not caused when the gear shifting process is switched to a high-speed gear mode because the first gear ring 13 connected with the first spline hub 19 is in the free mode state, the vehicle speed can be controlled, and the internal spline of the joint sleeve 18 is simultaneously meshed with the external splines of the first spline hub 19 and the second spline hub 20. If a high requirement is placed on the shift shock, a shift synchronizer is arranged between the first spline hub 19 and the fixed bracket 17 and between the first spline hub 20, so that the shift shock degree can be further reduced.
Preferably, the gear shift driving device 23 is a servo motor or a stepper motor.
Specifically, oil seals are provided between the front end housing 2 and the high-speed gear shaft 7, between the intermediate housing ii 26 and the driving bevel gear shaft 24, and between the rear end housing 39 and the second outer carrier 32. In order to maintain the air pressure in the wheel set stable, a ventilation plug 6 is arranged in the middle section shell I5.
The brake system 301 comprises a brake caliper 36 and a brake disc 37, the brake caliper 36 being fixedly connected to the rear end housing 39. Bolt holes are formed in the transition flange 33, the brake disc 37 and the rim 38, and the transition flange, the brake disc and the rim 38 are fixedly connected with nuts through bolts. To ensure the coaxiality requirements of the wheel and the transmission system, a toe opening matched with the rim 38 is arranged on the transition flange 33. The conical surface interference connection between the transition flange 33 and the second outer planet carrier 32 is realized by means of a stud 35 and a hexagonal flange surface nut 34 pre-tightening.
Specifically, considering the cost and the difficulty in processing and manufacturing, the gears and the splines in the electric drive wheel set can be processed in a hobbing and gear shaping mode, and the splines with partial structures are provided with tool retracting grooves for hobbing.
Example 2 vehicle comprising an electric wheelset
The integrated electric drive wheel set with the two gears and the hub comprises the two gears provided by the embodiment 1, as shown in fig. 1, an upper suspension swing arm support 3 is fixed to the upper end of a middle section shell I5, a lower suspension swing arm support 4 is fixed to the lower end of the middle section shell I5, and the upper suspension swing arm support 3 and the lower suspension swing arm support 4 are connected to a frame.
The above description is only of the preferred embodiments of the present invention and is not intended to limit the present invention, but various modifications and variations can be made to the present invention by those skilled in the art. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present invention should be included in the protection scope of the present invention.
Claims (10)
1. The integrated electric driving wheel set with the two gears and the hubs is characterized by comprising a front end shell, a middle section shell I, a middle section shell II, a rear end shell, a driving motor, a fixed shaft gear train speed reducing mechanism, a first planetary gear train speed reducing mechanism, a second planetary gear train speed reducing mechanism, a gear shifting mechanism, a transition flange plate and a rim;
the driving motor, the front end shell and the middle section shell I are positioned on the outer side of the rim, and the driving motor and the front end shell are of an integrated structure; one end of the middle section shell II is connected with the middle section shell I, and the other end of the middle section shell II penetrates through the rim and then is connected with the rear end shell; the output power of the driving motor is transmitted to the wheels through the fixed-axis gear train speed reducing mechanism, the first planetary gear train speed reducing mechanism, the second planetary gear train speed reducing mechanism, the transition flange and the rim in sequence;
The gear shifting mechanism is arranged between the first planetary gear train speed reducing mechanism and the second planetary gear train speed reducing mechanism;
the first planetary gear train speed reducing mechanism comprises a first sun gear, a first planetary shaft, a first gear ring, a first inner planet carrier, a first outer planet carrier and a gear ring carrier;
the gear shifting mechanism comprises a fixed bracket, a joint sleeve, a first spline hub and a second spline hub, and power is transmitted between the gear shifting mechanism and a gear ring bracket combining tooth and a first outer planet carrier combining tooth in the first planet gear system speed reducing mechanism in a matched mode; the gear ring support of the first planetary gear train speed reducing mechanism is supported on a fixed support in the gear shifting mechanism through two angular contact ball bearings, and a boss is arranged on the fixed support and used as a shaft shoulder of the two angular contact ball bearings; the joint sleeve is arranged at the periphery of the fixed bracket and the first spline hub; the fixed support in the gear shifting mechanism is fixedly connected to the middle section shell I and is provided with a spline connected with the engagement sleeve matched teeth, the first spline hub and the second spline hub are respectively axially fixed on the gear ring support and the first outer planet carrier by using snap springs, the inner ring spline of the first spline hub is connected with the combination teeth of the gear ring support in a matched mode, the inner ring spline of the second spline hub is connected with the combination teeth of the first outer planet carrier in a matched mode, and the fixed support, the first spline hub and the outer ring spline of the second spline hub are connected with the combination teeth of the joint sleeve in a matched mode.
2. The two-gear hub integrated electric drive wheel set according to claim 1, wherein the fixed gear train speed reducing mechanism comprises a high-speed gear shaft, a low-speed gear and a low-speed gear shaft, the high-speed gear shaft is fixedly connected with an output shaft of the drive motor, the low-speed gear is arranged on the periphery of one end of the low-speed gear shaft, peripheral teeth of the high-speed gear shaft and the low-speed gear are meshed with each other, and power is transmitted to the low-speed gear shaft; the high-speed gear shaft and the low-speed gear are respectively arranged at the connecting positions of the front end shell and the middle section shell I and are supported by deep groove ball bearings.
3. The integrated electric drive wheel set of two-gear hub according to claim 2, wherein in the first planetary gear train speed reducing mechanism, the first sun gear inner ring is fixedly connected with a low-speed gear shaft, the outer ring is meshed with the first planetary gear, the first planetary gear is sleeved on the first planetary shaft in a hollow manner through a needle bearing and rotates relative to the first planetary shaft, the first inner planetary carrier and the first outer planetary carrier are respectively provided with holes matched with the first planetary shaft, two ends of the first planetary shaft are respectively supported in the holes matched with the first outer planetary carrier and the first inner planetary carrier in an interference and clearance fit manner, and the first inner planetary carrier and the first outer planetary carrier are respectively supported on the middle section shell I and the second planetary gear train speed reducing mechanism through tapered roller bearings; the first gear ring is meshed with the first planet gears and the gear ring support respectively through meshing teeth, the combined tooth height of the first gear ring and the first planet gears is larger than that of the first gear ring and the gear ring support, and the gear ring support is axially fixed on the first gear ring.
4. A two-speed hub integrated electric drive wheel set as in claim 3 wherein the second planetary gear train reduction mechanism comprises: the second sun gear, the second planet gears, the second planet shafts, the second gear ring, the second inner planet carrier and the second outer planet carrier; the inner ring of the second sun gear is provided with an internal spline, the internal spline is connected with the first outer planet carrier, the outer ring is meshed with the second planet gear, the second planet gear is sleeved on the second planet shaft through a needle bearing in an empty mode and rotates relative to the second planet shaft, the second inner planet carrier and the second outer planet carrier are both provided with holes matched with the second planet shaft, two ends of the second planet shaft are respectively supported in the second outer planet carrier and the holes matched with the second inner planet carrier in an interference and clearance fit mode, and the second inner planet carrier and the second outer planet carrier are respectively supported on the middle section shell II and the rear end shell through tapered roller bearings.
5. The two-speed hub integrated electric drive wheel set of claim 4, wherein the outer surface of the engagement sleeve is i-shaped.
6. The two speed hub integrated electric drive wheel set of claim 5, wherein the width of the engagement sleeve is less than the width of the outer spline coupling teeth in the first spline hub.
7. The two-speed hub integrated electric drive wheel set of claim 5, further comprising a shift drive mechanism comprising: the gear shifting fork comprises a gear shifting fork, a bevel gear shifting fork shaft, a driving bevel gear shaft, an electric driving device and an oil seal seat, wherein the bevel gear shifting fork shaft and the driving bevel gear shaft are respectively arranged in a middle section shell II, the gear shifting fork is clamped in the middle of the I-shaped outer surface of a joint sleeve, the bevel gear shifting fork shaft and the driving bevel gear shaft are in meshed transmission through a bevel gear structure, the bevel gear shifting fork shaft penetrates through the gear shifting fork, the gear shifting fork and the bevel gear shifting fork shaft are respectively provided with transmission threads at contact positions to realize transmission, and the electric driving device is connected to the driving bevel gear shaft which penetrates through the oil seal seat fixed to the middle section shell II through a thread structure.
8. The two-gear hub integrated electric drive wheel set according to claim 7, further comprising a whole vehicle controller, wherein the whole vehicle controller is in signal connection with the drive motors of the wheels respectively, and the whole vehicle controller sends different torque signals to the four drive motors.
9. The two-gear hub integrated electric drive wheel set according to claim 8, wherein when the engaging teeth of the engaging sleeve are simultaneously engaged with the fixed bracket and the outer ring spline of the first spline hub, the first gear ring is kept in a stationary state, and the transmission state of the first planetary gear train reduction mechanism is: the power is input by the first sun gear, and is output by the first outer planet carrier after being transmitted by the first planet gears, the first sun gear and the first gear ring, at the moment, the first planet gear train reducing mechanism, the fixed shaft train reducing mechanism and the second planet train reducing mechanism form a three-stage reducing mechanism, and the low-speed gear transmission ratio is the product of the fixed shaft train, the first planet train and the second planet train transmission ratio; when the combination teeth of the joint sleeve are simultaneously matched and connected with the outer ring spline of the first spline hub and the outer ring spline of the second spline hub, the first gear ring and the first outer planet carrier always keep synchronous rotation speed, and after power is input by the first sun gear, the 1:1 transmission ratio is kept to be output by the first outer planet carrier.
10. A vehicle comprising the two-speed hub integrated electric drive wheel set of any one of claims 1 to 9 connected to a frame of the vehicle by an upper suspension swing arm mount fixed to an upper end of the center section housing i and a lower suspension swing arm mount fixed to a lower end of the center section housing i, respectively.
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| CN202310230643.4A CN116512893A (en) | 2023-03-07 | 2023-03-07 | Two-gear hub integrated electric driving wheel set and vehicle comprising same |
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| CN202310230643.4A CN116512893A (en) | 2023-03-07 | 2023-03-07 | Two-gear hub integrated electric driving wheel set and vehicle comprising same |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN117072667A (en) * | 2023-10-18 | 2023-11-17 | 宁波东力传动设备有限公司 | Novel speed reducer shifting fork gear shifting device and assembly method |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN117072667A (en) * | 2023-10-18 | 2023-11-17 | 宁波东力传动设备有限公司 | Novel speed reducer shifting fork gear shifting device and assembly method |
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