Multi-gear electric drive axle structure

Abstract

The application provides a multi-gear electric drive axle structure, which has uninterrupted gear shifting power, good driving experience and no risk of coasting; the mass distribution is reasonable, the center of mass is close to the axle shaft axis, the cantilever is short, and the stress and vibration conditions are greatly improved; the structure is compact, and the vehicle arrangement is simple; the gear shifting mode is rich, suitable for various complex working conditions, and the overall energy consumption of the electric drive axle is low. It comprises: an A-side power input assembly; a B-side power input assembly; a front planetary gear assembly comprising a front sun gear, a front planetary gear, a front inner ring gear and a front planetary carrier; a three-gear shifting assembly comprising an inner ring gear hub, a shifting sleeve, a fixed combination tooth and a planetary carrier combination tooth; a rear planetary gear assembly comprising a rear sun gear, a rear planetary gear, a rear inner ring gear and a rear planetary carrier; a differential assembly comprising a differential, a left half shaft and a right half shaft; the left half shaft and the right half shaft are fixedly connected with the differential; and a front sun gear shaft assembly comprising a hollow front sun gear shaft and an input constant meshing tooth.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of drive axle structure, and particularly to a multi-gear electric drive axle structure. BACKGROUND

[0002] The existing multi-gear electric drive axle structure mostly has the problems of gear shifting power interruption, poor driving experience, and risk of hill coasting. Some multi-gear electric drive axle structures with uninterrupted gear shifting power have uneven mass distribution of the electric drive axle assembly relative to the position of the half shaft, far distance between the center of mass and the axle shaft axis, long cantilever, poor stress and vibration conditions, complex structure, difficult vehicle arrangement, insufficient gear expansion mode, and high overall energy consumption of the electric drive axle. SUMMARY

[0003] To solve the above problems, the present application provides a multi-gear electric drive axle structure, which has uninterrupted gear shifting power, good driving experience, no coasting risk, reasonable mass distribution, close center of mass to the axle shaft axis, short cantilever, greatly improved stress and vibration conditions, compact structure, simple vehicle arrangement, rich gear expansion mode, adaptation to various complex working conditions, and low overall energy consumption of the electric drive axle.

[0004] A multi-gear electric drive axle structure, characterized in that it comprises:

[0005] An A-side power input assembly comprising an A-side drive motor, an A-side input shaft, and an A-side input gear;

[0006] A B-side power input assembly comprising a B-side drive motor, a B-side input shaft, a coupling gear input gear, a two-coupling gear shifter, and a two-gear input gear, wherein the coupling gear input gear, the two-coupling gear shifter, and the two-gear input gear are sleeved on the B-side input shaft, the two-coupling gear shifter is used to switch between the neutral gear, the coupling gear, and the two-gear, and the two-gear input gear is directly or indirectly connected to the two-gear output gear;

[0007] A front planetary gear assembly comprising a front sun gear, a front planetary gear, a front inner ring gear, and a front carrier;

[0008] A three-gear shifter assembly comprising an inner ring gear hub, a shifter sleeve, a fixed coupling gear, and a carrier coupling gear;

[0009] A rear planetary gear assembly comprising a rear sun gear, a rear planetary gear, a rear inner ring gear, and a rear carrier;

[0010] A differential assembly comprising a differential, a left half shaft, and a right half shaft, wherein the left half shaft and the right half shaft are fixedly connected to the differential, and the differential transmits power to the outside world;

[0011] and a front sun gear shaft assembly comprising a hollow front sun gear shaft and an input constant mesh gear;

[0012] The output end of the front row sun gear shaft is connected with the front row sun gear, and the output end of the front row planet carrier is fixed with the second gear output gear and rear row sun gear,

[0013] The A-side power input assembly and the B-side power input assembly are arranged in parallel on two sides of one half shaft, and the two sides are front and rear sides. The front row sun gear shaft is coaxially sleeved on one half shaft. The front row planet carrier and the rear row planet carrier are sequentially sleeved on one half shaft. The front end of the front row planet carrier is provided with the planet carrier coupling gear. The outer ring of the front row inner gear ring is fixedly connected with the inner gear ring gear hub. The shift sleeve is axially moved to switch the gear position.

[0014] The A-side input gear is engaged with the input constant engagement gear. The coupling gear input gear is engaged with the input constant engagement gear. The rear row planet carrier is fixedly connected with the differential. The rear row gear ring is fixedly connected with the electric drive axle housing.

[0015] It further has the following characteristics:

[0016] It further has the following characteristics:

[0017] The intermediate shaft assembly includes an intermediate shaft, an intermediate shaft second gear, and an intermediate shaft constant engagement gear. The two ends of the intermediate shaft are fixedly sleeved with the intermediate shaft constant engagement gear and the intermediate shaft second gear. The intermediate shaft constant engagement gear is engaged with the second gear input gear. The intermediate shaft second gear is engaged with the second gear output gear.

[0018] The inner gear ring gear hub is arranged with an inner spline. The fixed coupling gear is arranged with an outer spline. The planet carrier coupling gear is arranged with an outer spline. The shift sleeve is arranged with splines on the inner and outer ring surfaces. The outer spline on the shift sleeve is matched with the inner spline on the inner gear ring gear hub and axially slides. Through the sliding, the inner spline on the shift sleeve is connected with the outer spline on the fixed coupling gear or the outer spline on the planet carrier coupling gear, so as to realize the gear position switching. The fixed coupling gear is fixedly connected with the electric drive axle housing.

[0019] The rear row planet gears are arranged on the rear convex planet shaft of the rear row planet carrier through a bearing. The rear row planet gears are engaged with the rear row inner gear ring and the rear row sun gear through gears.

[0020] One half shaft passes through the front row sun gear shaft. The input constant engagement gear and the front row sun gear are fixedly connected on the front row sun gear shaft. The rear end of the front row planet carrier is a hollow shaft. The rear end of the hollow shaft is fixedly connected with the rear row sun gear. One half shaft passes through the hollow shaft of the hollow front row planet carrier. The second gear output gear is fixedly sleeved on the hollow shaft and arranged between the front row planet carrier and the rear row planet carrier.

[0021] The front planetary gear assembly and the rear planetary gear assembly are arranged corresponding to the same half shaft;

[0022] The half shaft is specifically a left half shaft or a right half shaft.

[0023] After the application is adopted, the multi-gear electric drive axle structure comprises two motors, two shifters, two planetary gears and multiple gear sets; the shifting power is uninterrupted, the mass distribution of the electric drive axle power assembly is reasonable relative to the half shaft position, the center of mass is close to the axle shaft axis, the cantilever is short, and the stress and vibration conditions are greatly improved; the structure is compact, and the vehicle arrangement is simple. BRIEF DESCRIPTION OF DRAWINGS

[0024] Figure 1 It is a structural framework schematic diagram of the application;

[0025] The names corresponding to the serial numbers in the figure are as follows:

[0026] A side drive motor 1, A side input shaft 2, A side input tooth 3, fixed combination tooth 4, shift sleeve 5, inner tooth ring tooth hub 6, planetary carrier combination tooth 7, front row inner tooth ring 8, front row planetary gear 9, front row sun gear 10, front row planetary carrier 11, rear row gear ring 12, rear row planetary gear 13, rear row sun gear 14, rear row planetary carrier 15, right half shaft 16, differential 17, two-gear output tooth 18, intermediate shaft two-gear tooth 19, intermediate shaft 20, intermediate shaft constant mesh tooth 21, two-gear input tooth 22, two-coupling gear shifter 23, coupling gear input tooth 24, B side input shaft 25, B side drive motor 26, input constant mesh tooth 27, left half shaft 28, front row sun gear shaft 29. DETAILED DESCRIPTION

[0027] A multi-gear electric drive axle structure, as shown in Figure 1 , comprising:

[0028] An A side power input assembly, comprising an A side drive motor 1, an A side input shaft 2 and an A side input tooth 3 arranged in axial alignment, the A side drive motor 1 and the A side input tooth 3 being fixedly connected to the A side input shaft 2 respectively;

[0029] A B side power input assembly, comprising a B side drive motor 26, a B side input shaft 25, a coupling gear input tooth 24, a two-coupling gear shifter 23 and a two-gear input tooth 22 arranged in axial alignment; the B side drive motor 26 and the B side input shaft 25 are fixedly connected together, the coupling gear input tooth 24 and the two-gear input tooth 22 are sleeved on the B side input shaft 25 through bearings, the two-coupling gear shifter 23 is fixedly connected to the B side input shaft 25 and is arranged between the coupling gear input tooth 24 and the two-gear input tooth 22;

[0030] An intermediate shaft assembly, comprising an intermediate shaft 20, an intermediate shaft constant mesh tooth 21 and an intermediate shaft two-gear tooth 19 fixedly connected to the intermediate shaft 20;

[0031] The power input components on side A and side B are arranged in parallel to each other and on the front and rear sides of the left half shaft.

[0032] The intermediate shaft assembly is arranged in parallel with the power input assembly on side B.

[0033] The front planetary gear set includes a front sun gear 10, front planet gears 9, a front internal gear ring 8, a front planet carrier 11, and a first and third gear shift assembly. The front planet gears 9 are mounted on planet shafts on the front planet carrier 11 via bearings. The front planet gears 9 are connected to the front internal gear ring 8 and the front sun gear 10 via gear meshing. The first and third gear shift assembly includes an internal gear ring hub 6, a shift sleeve 5, a fixed engagement gear 4, and a planet carrier engagement gear 7. The inner circumference of the internal gear ring hub 6... The gear shift sleeve 5 is equipped with internal splines, external splines are arranged on the outer periphery of the fixed engagement tooth 4 and the outer periphery of the planetary carrier engagement tooth 7, and splines are evenly distributed on the inner and outer sides of the shift sleeve 5. The external splines on the shift sleeve 5 mate with the internal splines on the internal gear ring and can slide axially on it. Through sliding, the internal splines on the shift sleeve 5 can be splined with the external splines on the fixed engagement tooth 4 or the external splines on the planetary carrier engagement tooth 7, thus realizing gear shifting; the fixed engagement tooth 4 is fixedly connected to the electric drive bridge housing.

[0034] The rear planetary gear assembly includes a rear sun gear 14, rear planet gears 13, a rear internal gear ring, and a rear planet carrier 15. The rear planet gears 13 are mounted on planet shafts on the rear planet carrier 15 via bearings. The rear planet gears 13 are connected to the rear internal gear ring and the rear sun gear 14 via gear meshing. The rear planet carrier 15 is fixedly connected to the differential 17. The rear gear ring 12 is fixedly connected to the electric drive axle housing.

[0035] The differential 17 assembly includes a differential 17, a left half-shaft 28, and a right half-shaft 16; the left half-shaft 28 and the right half-shaft 16 are respectively fixedly connected to the differential 17, and the power is transmitted to the outside through differential.

[0036] The front sun gear shaft assembly specifically comprises an input constant meshing gear 27, a front sun gear shaft 29, and a front sun gear 10. The front sun gear shaft 29 is hollow, and the left half-shaft 28 passes through the front sun gear shaft 29. The input constant meshing gear 27 and the front sun gear 10 are fixedly connected to the front sun gear shaft 29. The input constant meshing gear 27 is simultaneously engaged with the input gear 3 on side A and the coupling gear input gear 24. The front planetary carrier 11 is connected to the rear sun gear 14 through the rear hollow shaft. The left half-shaft 28 passes through the hollow shaft of the front planetary carrier 11, and the second gear output gear 18 is fixedly sleeved on the shaft of the front planetary carrier 11 and arranged between the front and rear planetary gears.

[0037] The second-gear output tooth 18 is engaged with the second-gear tooth 19 on the intermediate shaft; the normally engaged tooth 21 on the intermediate shaft is engaged with the second-gear input tooth 22.

[0038] It comprises two motors, two shift assemblies, two planetary rows, multiple gear sets; it does not interrupt the shifting power, the mass distribution of the electric drive axle power assembly is reasonable relative to the half shaft position, the center of mass is close to the axle shaft axis, the cantilever is short, which greatly improves the stress and vibration conditions; compact structure, simple vehicle layout.

[0039] The working principle is as follows:

[0040] The multi-gear electric drive axle structure is composed of two parallel arranged motors, two shift assemblies, multiple gear assemblies, and two coaxially arranged planetary rows and a differential assembly with half shafts. The two motors and the two shift assemblies are used through two shift assemblies to realize different gear transmission combinations, further realizing non-interrupted shifting power and different speed ratios of multiple gears.

[0041] In first gear, the two-coupling shift gear 23 is maintained in the neutral position, and the shift sleeve 5 in the three-gear shift assembly is engaged to the left, connecting the front row inner ring gear 8 with the fixed combination tooth 4, so that the front row inner ring gear 8 is fixed.

[0042] At this time, the A-side drive motor 1 serves as a power source to drive the A-side input shaft 2 and the A-side input tooth 3 to rotate, and the A-side input tooth 3 further transmits power through meshing connection to the input constant meshing tooth 27, and then transmits power to the front row sun gear 10 through the front row sun gear shaft 29, drives the front row planetary gear 9 to rotate and revolve around the front row sun gear 10 through gear meshing, and then drives the front row planet carrier 11 to rotate, and then the power is transmitted to the rear row sun gear 14, which drives the rear row planetary gear 13 to rotate and revolve around the rear row sun gear 14 through gear meshing, and then drives the rear row planet carrier 15 to rotate, and finally, the power is transmitted to the outside through the differential 17 connected with the rear row planet carrier 15 and the left and right half shafts 16, completing the transmission of the first gear power flow; in this process, the initial torque of the A-side drive motor 1 is amplified through the gear ratio designed for the first gear and then transmitted to the outside, realizing speed reduction and torque increase;

[0043] In second gear, the one-three-gear shift assembly is maintained in the neutral position, and the two-coupling shift gear 23 is engaged to the right, connecting the B-side input shaft 25 with the two-gear input tooth 22.

[0044] At this time, the B-side driving motor 26 drives the B-side input shaft 25 as a power source to rotate, and further transmits power to the second gear input tooth 22 through the second coupling gear shifter 23. The second gear input tooth 22 further transmits power to the intermediate shaft constant mesh tooth 21 through meshing connection. The power is then transmitted to the intermediate shaft 20 arranged in parallel with the B-side input shaft 25. The intermediate shaft 20 drives the intermediate shaft second gear tooth 19 fixedly connected thereto to rotate. The intermediate shaft second gear tooth 19 drives the second gear output tooth 18 to rotate through meshing connection. The second gear output tooth 18 drives the rear planetary carrier 15 to rotate through the gear meshing. Finally, the power is transmitted to the outside through the differential 17 fixedly connected with the rear planetary carrier 15 and the left and right half shafts 16, completing the power flow transmission of the second gear. In this process, the initial torque of the B-side driving motor 26 is amplified through the gear ratio designed for the second gear and then transmitted to the outside, achieving speed reduction and torque increase.

[0045] When the third gear is engaged, the second coupling gear shifter 23 is maintained in the neutral position. The shift sleeve 5 in the first gear shift assembly is shifted to the right to connect the front row inner ring gear 8 with the planetary carrier combination tooth 7. Due to the inherent characteristics of the planetary gear train, the inner ring gear, the planetary carrier, and the sun gear rotate at the same speed.

[0046] At this time, the A-side driving motor 1 drives the A-side input shaft 2 and the A-side input tooth 3 as a power source to rotate. The A-side input tooth 3 further transmits power to the input constant mesh tooth 27 through meshing connection. The power is then transmitted to the front row sun gear 10 through the front row sun gear shaft 29. The entire planetary gear train is driven to rotate through gear meshing, i.e., the front row planetary carrier 11 is driven to rotate. The power is then transmitted to the rear planetary carrier 15 through the gear meshing. Finally, the power is transmitted to the outside through the differential 17 fixedly connected with the rear planetary carrier 15 and the left and right half shafts 16, completing the power flow transmission of the third gear. In this process, the initial torque of the A-side driving motor 1 is amplified through the gear ratio designed for the third gear and then transmitted to the outside, achieving speed reduction and torque increase.

[0047] When the vehicle continuously shifts gears, the two driving motors cooperate with the gear shift assembly to realize uninterrupted power flow during gear shifting. For example, when the first gear is switched to the second gear, the second gear is switched to the third gear, or the third gear is switched to the second gear, the power is uninterrupted. The principle of uninterrupted power during gear shifting is the same. The first gear is upgraded to the second gear as an example:

[0048] When the electric drive bridge is in the first gear, the second coupling gear shifter 23 is kept in the neutral position, and the shifter sleeve 5 in the third gear shifting assembly is engaged to the left, connecting the front inner ring gear 8 with the fixed combination gear 4, so that the front inner ring gear 8 is fixed. At this time, the A-side driving motor 1 drives the A-side input shaft 2, the A-side input gear 3, the input constant mesh gear 27, the front sun gear 10, the front planet carrier 11, the rear sun gear 14, and the rear planet carrier 15 as the power source, and finally, the power is transmitted to the outside through the half shafts via the differential 17 fixed to the rear planet carrier 15.

[0049] When the second gear needs to be switched, the first power transmission state remains unchanged, and the second coupling gear shifter 23 is engaged to the right, connecting the B-side input shaft 25 with the second gear input gear 22. At this time, the B-side driving motor 26 drives the B-side input shaft 25, the second gear input gear 22, the intermediate shaft constant mesh gear 21, the intermediate shaft 20, the intermediate shaft second gear 19, the second gear output gear 18, the rear sun gear 14, and the rear planet carrier 15 as the power source, and finally, the power is transmitted to the outside through the half shafts via the differential 17 fixed to the rear planet carrier 15.

[0050] At this time, the A-side driving motor 1 drives the first gear power and the B-side driving motor 26 drives the second gear power simultaneously, and the shifter sleeve 5 in the first-third gear shifting assembly returns to the neutral position, disconnecting the first gear power. The output power of the second gear remains unchanged, i.e., the output power of the half shaft is not interrupted. This process completes the switching from the first gear to the second gear without power interruption.

[0051] In addition, when the vehicle needs high-power output in the first or third gear, the power of the B-side driving motor 26 can be combined with the power of the A-side driving motor 1 through the coupling gear, and the combined power can be output through the first or third gear. The principle of coupling in the first gear is similar to that in the third gear. The first coupling is taken as an example for illustration:

[0052] When the first coupling is engaged, the A-side driving motor 1 drives the first gear, and the second coupling gear shifter 23 is engaged to the left, connecting the B-side input shaft 25 with the coupling gear input gear 24. At this time, the rotational power of the B-side driving motor 26 is transmitted to the input constant mesh gear 27 through the B-side input shaft 25 and the coupling gear input gear 24.

[0053] At this time, the power of the B-side driving motor 26 and the power of the A-side driving motor 1 are coupled on the input constant mesh gear 27. The combined power continues to drive the front sun gear 10, the front planet carrier 11, the rear sun gear 14, and the rear planet carrier 15 to rotate, and finally, the power is transmitted to the outside through the half shafts via the differential 17 fixed to the rear planet carrier 15, realizing the power output of the first coupling.

[0054] The multi-gear electric drive axle structure can improve the driving experience and reduce the risk of hill coasting, and the gear expansion mode is rich, which is suitable for various complex working conditions, and the overall energy consumption of the electric drive axle is low.

[0055] It is apparent for a person skilled in the art that the present application is not limited to the details of the above-described exemplary embodiments, but can be implemented in other concrete forms without departing from the spirit or essential characteristics of the present application. Therefore, the embodiments should be considered in all respects as illustrative and not restrictive, the scope of the present application being defined by the appended claims rather than the above description, and it is intended to embrace all changes and modifications that fall within the meaning and scope of the equivalent elements of the claims. Any reference signs in the claims should not be considered as limiting the claims involved.

[0056] Furthermore, it should be understood that although the present specification is described in terms of embodiments, not every embodiment according to the present specification needs to exhibit each and every characteristic specified in the specification. The specification can also be described in terms of a single preferred embodiment, it being understood that this single preferred embodiment can exhibit not every aspect or feature of the application. The specification can also be described in terms of a generic disclosure of several aspects or features of the application, it being understood that not every aspect or feature needs to be necessarily required by implementations of the application. The specification can also be described in terms of a generic disclosure of several aspects or features of the application, it being understood that not every aspect or feature needs to be necessarily required by implementations of the application.

Claims

1. A multi-speed electric drive bridge structure, characterized in that, It includes: The A-side power input assembly includes an A-side drive motor, an A-side input shaft, and an A-side input gear; The B-side power input assembly includes a B-side drive motor, a B-side input shaft, a coupling gear input tooth, a two-coupling gear shifter, and a second-gear input tooth. The B-side input shaft is fitted with the coupling gear input tooth, the two-coupling gear shifter, and the second-gear input tooth. The two-coupling gear shifter is used to switch between neutral, coupling gear, or second gear. The second-gear input tooth is indirectly connected to the second-gear output tooth. The front planetary gear assembly includes the front sun gear, the front planet gears, the front internal gear ring, and the front planet carrier; The first and third gear shift assembly includes an internal gear ring hub, a shift sleeve, a fixed engagement gear, and a planetary carrier engagement gear. The rear planetary gear assembly includes a rear sun gear, rear planet gears, a rear internal gear ring, and a rear planet carrier; A differential assembly includes a differential, a left half-shaft, and a right half-shaft; the left half-shaft and the right half-shaft are respectively fixedly connected to the differential, and differentially transmit power to the outside. And the front sun gear axle assembly, which includes a hollow front sun gear axle and input constant meshing teeth; The output end of the front sun gear shaft is connected to the front sun gear, and the output end of the front planetary carrier is fixedly equipped with the second output gear and the rear sun gear. The A-side power input component and the B-side power input component are respectively located on both sides of one half-shaft and arranged parallel to each other. The two sides are specifically the front and rear sides. The front sun gear shaft is coaxially mounted on one half-shaft. The front planetary gear assembly and the rear planetary gear assembly are set on the same half-shaft. The front planetary carrier and the rear planetary carrier are sequentially mounted on one half-shaft. The front outer circumference of the front planetary carrier is also provided with the planetary carrier engagement teeth. The outer ring of the front internal gear ring is fixedly connected to the internal gear ring hub. The shift sleeve moves axially to switch gears. The input gear on side A is engaged with the constant-mesh input gear, the coupling gear input gear is engaged with the constant-mesh input gear, the rear planetary carrier is fixedly connected to the differential, and the rear internal gear ring is fixedly connected to the electric drive axle housing. One half of the shaft passes through the hollow shaft arrangement of the front planetary carrier, and the second gear output gear is fixed on the hollow shaft and arranged between the front planetary carrier and the rear planetary carrier; It also includes an intermediate shaft assembly, which is arranged between the second-gear input gear and the second-gear output gear; The intermediate shaft assembly includes an intermediate shaft, an intermediate shaft second gear, and an intermediate shaft constant engagement gear. The intermediate shaft is fixedly fitted with an intermediate shaft constant engagement gear and an intermediate shaft second gear at its two ends, respectively. The intermediate shaft constant engagement gear meshes with the second gear input gear, and the intermediate shaft second gear meshes with the second gear output gear. The inner circumference of the internal gear ring hub is provided with internal splines, the outer circumference of the fixed engagement teeth is provided with external splines, the outer circumference of the planetary carrier engagement teeth is provided with external splines, and the inner and outer annular surfaces of the shift sleeve are evenly distributed with splines. The external splines on the shift sleeve mate with the internal splines on the internal gear ring hub and slide axially. Through sliding, the internal splines on the shift sleeve are splined to the external splines on the fixed engagement teeth or the external splines on the planetary carrier engagement teeth, thereby realizing gear switching. The fixed engagement teeth are fixedly connected to the electric drive axle housing.

2. The multi-stage electric drive bridge structure as described in claim 1, characterized in that: The rear planetary gears are mounted on the rear convex planetary shaft on the rear planetary carrier via bearing sleeves, and the rear planetary gears are respectively connected to the rear internal gear ring and the rear sun gear through gear meshing.

3. The multi-stage electric drive bridge structure as described in claim 1, characterized in that: One half of the shaft passes through the front sun gear shaft, with input constant meshing teeth, and the front sun gear is fixedly connected to the front sun gear shaft; the rear end of the front planetary carrier is a hollow shaft, and the rear end of the hollow shaft is fixedly connected to the rear sun gear.

4. The multi-stage electric drive bridge structure as described in claim 1, characterized in that: One half of the axis is either the left half or the right half.

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