Differential integrated with escape device

Abstract

The invention discloses a differential mechanism integrated with an escape device. The differential mechanism comprises a shell, a reduction gear mechanism and a differential mechanism body. The differential mechanism comprises a supporting assembly, a planetary gear assembly and a clutch assembly, the planetary gear assembly comprises a first planet carrier, a second planet carrier, a first planet shaft, a second planet shaft, a first planet wheel and a second planet wheel, wherein the first planet shaft and the second planet shaft are arranged between the first planet carrier and the second planet carrier, and the first planet wheel and the second planet wheel are arranged on the first planet shaft and the second planet shaft respectively. An inner gear ring is arranged between the reduction gear mechanism and the first planet gear for meshing connection, a sun gear is arranged on the clutch assembly and is in meshing connection with the second planet gear, and the sun gear, the first planet gear, the second planet gear and the inner gear ring are all of a straight tooth structure. The differential function is achieved through the four straight toothed spur gears, a traditional open bevel gear differential mechanism is omitted, the size, the weight and the envelope of a differential mechanism system are better, and arrangement of the whole vehicle is facilitated.

Description

Technical Field

[0001] The present invention relates to the technical field of new energy vehicles, and in particular to a differential with an integrated escape device. Background Art

[0002] In the field of mechanical engineering, especially in the field of automotive engineering and transmission systems, the differential is an important component. Its main function is to allow the two half-axles to rotate at different speeds during the driving process of the vehicle, so as to adapt to the vehicle's steering and different road conditions. However, in order to effectively improve the handling and stability of new energy vehicles, automobile manufacturers require the differential system to be equipped with a differential lock or a release function, which can intelligently distribute torque to different wheels according to the driving conditions of the vehicle and the driver's operation. In different off-road situations, the system can send torque to the wheels with better grip to ensure that the vehicle can pass through rugged terrain stably. More and more automobile manufacturers are developing new energy vehicles with differentials with release devices.

[0003] At present, the differential technology of new energy vehicles with escape devices on the market mostly adopts an open bevel gear structure, which transmits torque through the meshing of bevel gears and allows the speed of one wheel to be higher than the other side when necessary. The advantages of this structure are simple structure, low manufacturing cost and easy maintenance.

[0004] However, this structure also has the problems of low transmission efficiency, heavy weight and large volume, which in turn leads to a large volume of the differential, which is not conducive to flexible arrangement. Therefore, accordingly, it is desired to provide a differential structure of an escape device with a more compact arrangement and improved performance to meet the development trend of existing new energy vehicles. Summary of the invention

[0005] Based on this, the purpose of the present invention is to provide a differential with an integrated escape device, aiming to solve the problems of low transmission efficiency, heavy weight and large volume of the current open bevel gear structure, which leads to a large volume of the differential and is not conducive to flexible layout.

[0006] To achieve the above object, the present invention is implemented through the following technical solutions: a differential integrated with an escape device, the differential integrated with an escape device comprising a housing, a reduction gear mechanism disposed in the housing, and a differential mechanism meshingly connected with the reduction gear mechanism; A differential mechanism, comprising a support assembly, a planetary gear assembly and a clutch assembly disposed in the support assembly, wherein the planetary gear assembly comprises a first planet carrier, a second planet carrier, a first planet shaft and a second planet shaft disposed between the first planet carrier and the second planet carrier, and a first planet wheel and a second planet wheel disposed on the first planet shaft and the second planet shaft respectively; Among them, an inner gear ring is provided between the reduction gear mechanism and the first planetary gear for meshing connection, a sun gear is provided on the clutch assembly, and the sun gear is meshingly connected with the second planetary gear, and the sun gear, the first planetary gear, the second planetary gear, and the inner gear ring are all spur gear structures.

[0007] In summary, according to the differential with integrated escape device proposed by the present invention, four spur gears are used to realize the differential function. There is no traditional open bevel gear differential. The volume, weight and envelope of the differential system are better, which is conducive to the layout of the whole vehicle. The gears of the planetary gear differential are all spur gear designs. By improving the manufacturing process, such as precision forging, etc., the manufacturing accuracy and quality of the differential can be improved, and the finishing process can be reduced, thereby reducing the manufacturing cost and maintenance cost. The left and right half-axle torque can be dynamically adjusted, the vehicle's handling stability can be improved, and the escape ability and off-road performance can be increased. The spur gears in the planetary gear structure mesh with each other, which can achieve smoother torque transmission, reduce energy loss, and improve the transmission efficiency of the system. Compared with the traditional open bevel gear structure, the planetary gear structure has better adaptability. It can be flexibly configured and adjusted according to different vehicle requirements to meet the use requirements of different vehicles.

[0008] According to one aspect of the above technical solution, the ratio of the number of teeth of the inner ring gear to the number of teeth of the sun gear is 2:1.

[0009] According to one aspect of the above technical solution, the number of teeth, module, pressure angle, and diameter of the first planetary gear and the second planetary gear are equal.

[0010] According to one aspect of the above technical solution, the support assembly includes a first differential housing supported on the housing through a first bearing, and a second differential housing supported on the housing through a second bearing, and the first differential housing and the second differential housing jointly support the planetary gear assembly and the clutch assembly.

[0011] According to one aspect of the above technical solution, the first differential housing and the second differential housing respectively extend a first output shaft and a second output shaft to both sides for connecting to wheels.

[0012] According to one aspect of the above technical solution, the clutch assembly includes a clutch, a clutch inner hub, and a clutch outer hub, and the clutch assembly is disposed between the sun gear and the second planetary gear.

[0013] According to one aspect of the above technical solution, the reduction gear mechanism includes a power motor, a motor rotor shaft arranged on the power motor, a first gear arranged at one end of the motor rotor shaft away from the power motor, a second gear meshingly connected to the first gear, a first intermediate shaft connected to the second gear, a third gear arranged at the other end of the first intermediate shaft, and a fourth gear meshingly connected to the third gear, and the fourth gear meshingly connected to the inner ring gear for transmitting power.

[0014] Additional aspects and advantages of the present invention will be given in part in the following description and in part will be obvious from the following description or learned through practice of the present invention. BRIEF DESCRIPTION OF THE DRAWINGS

[0015] The above and / or additional aspects and advantages of the present invention will become apparent and easily understood from the description of the embodiments in conjunction with the following drawings, in which: Figure 1 This is a schematic structural diagram of a differential with an integrated escape device in Embodiment 1 of the present invention; Figure 2 This is a power transmission path diagram when there is no differential in the first embodiment of the present invention; Figure 3 A power transmission path diagram when there is a differential in the first embodiment of the present invention; Figure 4 The diagram is a power transmission path diagram when the left side slips in the first embodiment of the present invention; Figure 5 This is a power transmission path diagram when the right side is slipping in the first embodiment of the present invention; Figure 6 This is a schematic structural diagram of a differential with an integrated escape device in Embodiment 2 of the present invention; Figure 7 It is a schematic diagram of the structure of the differential with integrated escape device in the third embodiment of the present invention.

[0016] Component symbol description: Power motor 1, motor rotor shaft 2, first gear 3, second gear 4, first intermediate shaft 5, third gear 6, fourth gear 7, second differential housing 8, first planetary gear 9, first bearing 10, first planetary shaft 11, second planetary shaft 12, second planetary carrier 13, first planetary carrier 14, clutch outer hub 15, clutch 16, clutch inner hub 17, second planetary gear 18, sun gear 19, first differential housing 20, inner ring gear 21, first output shaft A, second output shaft B, second bearing 22, housing 23. DETAILED DESCRIPTION

[0017] In order to make the purpose, features and advantages of the present invention more obvious and easy to understand, the specific implementation methods of the present invention are described in detail below in conjunction with the accompanying drawings. Several embodiments of the present invention are shown in the accompanying drawings. However, the present invention can be implemented in many different forms and is not limited to the embodiments described herein. On the contrary, the purpose of providing these embodiments is to make the disclosure of the present invention more thorough and comprehensive.

[0018] It should be noted that when an element is referred to as being "fixed to" another element, it may be directly on the other element or there may be a central element. When an element is considered to be "connected to" another element, it may be directly connected to the other element or there may be a central element at the same time. The terms "vertical", "horizontal", "left", "right", "upper", "lower" and similar expressions used herein are for illustrative purposes only and do not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore should not be understood as limiting the present invention.

[0019] In the present invention, unless otherwise clearly specified and limited, the terms "installed", "connected", "connected", "fixed" and the like should be understood in a broad sense, for example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be a direct connection, or it can be indirectly connected through an intermediate medium, or it can be the internal communication of two components. For those of ordinary skill in the art, the specific meanings of the above terms in the present invention can be understood according to the specific circumstances. The term "and / or" used herein includes any and all combinations of one or more related listed items.

[0020] Embodiment 1 See also Figure 1-Figure 5 , which is a schematic structural diagram of a differential of an integrated escape device provided in Embodiment 1 of the present invention, wherein the differential of the integrated escape device comprises a housing 23, a reduction gear mechanism disposed in the housing 23, and a differential mechanism meshingly connected with the reduction gear mechanism, wherein: In this embodiment, the differential mechanism includes a support assembly, a planetary gear assembly and a clutch assembly arranged in the support assembly. The planetary gear assembly includes a first planet carrier 14, a second planet carrier 13, a first planetary shaft 11 and a second planetary shaft 12 arranged between the first planet carrier 14 and the second planetary shaft 13, and a first planetary gear 9 and a second planetary gear 18 respectively arranged on the first planetary shaft 11 and the second planetary shaft 12; an inner ring gear 21 is provided between the reduction gear mechanism and the first planetary gear 9 for meshing connection, a sun gear 19 is provided on the clutch assembly, and the sun gear 19 is meshingly connected with the second planetary gear 18, and the sun gear 19, the first planetary gear 9, the second planetary gear 18, and the inner ring gear 21 are all spur gear structures.

[0021] Further, the support assembly includes a first differential housing 20 supported on a housing 23 through a first bearing 10, and a second differential housing 8 supported on the housing 23 through a second bearing 22. The first differential housing 20 and the second differential housing 8 jointly support the planetary gear assembly and the clutch assembly. The first differential housing 20 and the second differential housing 8 extend a first output shaft A and a second output shaft B to both sides, respectively, for connecting to wheels.

[0022] Furthermore, the clutch assembly includes a clutch 16 , a clutch inner hub 17 , and a clutch outer hub 15 , and the clutch assembly is disposed between the sun gear 19 and the second planetary gear 18 .

[0023] According to another aspect of the above technical solution, the reduction gear mechanism includes a power motor 1, a motor rotor shaft 2 arranged on the power motor 1, a first gear 3 arranged at one end of the motor rotor shaft 2 away from the power motor 1, a second gear 4 meshingly connected to the first gear 3, a first intermediate shaft 5 connected to the second gear 4, a third gear 6 arranged at the other end of the first intermediate shaft 5, and a fourth gear 7 meshingly connected to the third gear 6, and the fourth gear 7 is fixedly connected to the second differential case 8 for transmitting power.

[0024] Among them, the first gear 3 is connected to the motor rotor shaft 2, the first gear 3 is meshed with the second gear 4, the second gear 4 is fixedly connected to the first intermediate shaft 5, and the other side of the first intermediate shaft 5 is fixedly connected with the third gear 6, which is meshed with the fourth gear 7, so that the power of the power motor 1 is transmitted to the housing 23 of the above-mentioned differential, and the axis of the motor rotor shaft 2 is arranged parallel to the axis of the intermediate shaft. The power motor 1 is detachably connected to the housing 23.

[0025] Specifically, the first output shaft A is provided with a first bearing 10, a first differential housing 20, a clutch 16, a clutch inner hub 17, a clutch outer hub 15, and a first planetary carrier 14 from left to right. The second output shaft B is provided with a sun gear 19, a first planetary gear 9, a second planetary gear 18, a first planetary shaft 11, a second planetary shaft 12, an inner gear ring 21, a second planetary carrier 13, a second differential housing 8, and a second bearing 22 from left to right. The first differential housing 20 and the second differential housing 8 are fixed together by welding or bolting, and are supported on the housing 23 by the first bearing 10 and the second bearing 22, respectively, and rotate around the axis of the first output shaft A and the second output shaft B.

[0026] It is worth noting that the sun gear 19 meshes with the second planetary gear 18, the first planetary gear 9 meshes with the inner gear ring 21, and the second planetary gear 18 meshes with the first planetary gear 9. The three can be installed in a straight line in space or at a certain angle. The first planetary gear 9 is loosely mounted on the first planetary shaft 11, and the second planetary gear 18 is loosely mounted on the second planetary shaft 12; the first planetary shaft 11 and the second planetary shaft 12 are supported between the first planetary carrier 14 and the second planetary carrier 13; the first planetary carrier 14 and the second planetary carrier 13 carry multiple pairs of first planetary gears 9 and second planetary gears 18 in a load-bearing manner, and are evenly arranged in the circumferential direction, preferably designed as three groups.

[0027] Preferably, the inner gear ring 21 is fixed to the inner cavity of the second differential housing 8 or is processed integrally therewith; the fourth gear 7 is installed on the outer circle of the second differential housing 8, which can be bolted or welded together; one end of the first planetary carrier 14 is fixedly connected to the outer hub of the clutch 16, and the second planetary carrier 13 is splined to the second output shaft B, and the second output shaft B is connected to the wheel; the sun gear 19 is fixedly connected to the clutch inner hub 17, and the inner hole of the sun gear 19 has a spline structure, which is connected to the first output shaft A, and the first output shaft A is connected to the wheel; there are friction plates and steel plates between the clutch outer hub 15 and the clutch inner hub 17; the above parts all rotate around the axis of the first output shaft A and the second output shaft B.

[0028] It is worth emphasizing that in order to achieve a 1:1 distribution of the left and right wheel torque of the vehicle, the number of teeth of each planetary gear in the spur planetary gear set needs to satisfy the relationship: the number of teeth of the inner ring gear 21 is twice the number of teeth of the sun gear 19, that is, the ratio of the number of teeth of the inner ring gear to the number of teeth of the sun gear is 2:1. The first planetary gear 9 and the second planetary gear 18 have the same number of teeth, module and pressure angle, and the diameter of the first planetary gear 9 is equal to the diameter of the second planetary gear 18. The planetary gear differential composed of the sun gear 19, the inner ring gear 21, the first planetary gear 9 and the second planetary gear 18 can be finished without heat treatment to reduce costs.

[0029] In addition, the housing 23 can form an oil pool to contain lubricating oil for lubricating and cooling the moving components. The oil passages designed on the housing 23 can guide the oil into the parts or positions that need lubrication and cooling. In some embodiments, an oil pump is also installed on the housing 23.

[0030] The following will describe the power transmission paths of the four working conditions of the planetary gear differential: Working condition 1: If Figure 2As shown, when the clutch is not working, the whole vehicle is in a straight-line driving condition, that is, when the ground adhesion coefficients of the left and right wheels are the same, since there is no speed difference between the left first output shaft A and the second output shaft B, the clutch is in a free state, and the driving force is output by the motor rotor shaft 2 of the power motor 1 → the first gear 3 → the second gear 4 → the first intermediate shaft 5 → the third gear 6 → the fourth gear 7 → the first differential case 20, the second differential case 8 → the inner ring 21, and the power is evenly distributed and output, respectively: the first planetary gear 9 → the second planetary gear 18 → the sun gear 19 → the first output shaft A; and the first planetary gear 9, the second planetary gear 18 (not rotating but only revolving) → the first planetary shaft 11, the second planetary shaft 12 → the second planetary carrier 13 → the second output shaft B output power.

[0031] Condition 2: If Figure 3 As shown, when the clutch is not working, the whole vehicle is in a turning driving condition, that is, when the ground adhesion coefficients of the left and right wheels are inconsistent, because there is a speed difference between the first output shaft A and the second output shaft B, and the clutch is in a free state, the first planetary gear 9 and the second planetary gear 18 rotate, and revolve around the axis of the first output shaft A and the second output shaft B, and the driving force is output by the motor rotor shaft 2 of the power motor 1 → the first gear 3 → the second gear 4 → the first intermediate shaft 5 → the third gear 6 → the fourth gear 7 → the first differential case 20, the second differential case 8 → the inner ring 21, and the power is output by the speed difference between the left and right wheels, respectively: the first planetary gear 9 → the second planetary gear 18 → the sun gear 19 → the first output shaft A and the first planetary gear 9, the second planetary gear 18 (rotation and revolution) → the first planetary shaft 11, the second planetary shaft 12 → the second planetary carrier 13 → the second output shaft B outputs power.

[0032] Condition 3: If Figure 4As shown, when the clutch is working, if the ground adhesion coefficient on the first output shaft A side is low and the ground adhesion coefficient on the second output shaft B is high, due to the speed difference between the left first output shaft A and the second output shaft B, a part of the driving force is output by the motor rotor shaft 2 of the power motor 1 → the first gear 3 → the second gear 4 → the first intermediate shaft 5 → the third gear 6 → the fourth gear 7 → the first differential case 20, the second differential case 8 → the inner ring 21, and the power is output by realizing the speed difference between the left and right wheels, which are respectively: the first planetary gear 9 → the second planetary gear 18 → the sun gear 19 → the first output shaft A and the first planetary gear 9, the second planetary gear 18 (rotation and revolution) → the first planetary shaft 11, the second planetary shaft 12 → the second planetary carrier 13 → the second output shaft B outputs power. As for the other part of the power, the tire slips and cannot provide enough grip because of the low ground adhesion coefficient on the side of the first output shaft A. However, due to the closing of the clutch, the sun gear 19 is locked with the first planet carrier 14 and the second planet carrier 13 in a rotationally fixed manner, which ultimately means that the sun gear 19 is fixed with the first planet carrier 14 and the second planet carrier 13 and rotates together to transmit power, sun gear 19→clutch inner hub 17→clutch 16→clutch outer hub 15→first planet carrier 14→second planet carrier 13→second output shaft B; the above two parts of power converge at the second output shaft B and are output together, which ultimately means that the output torque on the second output shaft B is increased, thereby increasing the ability to escape from difficulties.

[0033] Condition 4: If Figure 5 As shown: when the clutch is working, if the ground adhesion coefficient on the first output shaft A side is high and the ground adhesion coefficient on the second output shaft B is low, due to the speed difference between the left first output shaft A and the second output shaft B, part of the driving force is output by the motor rotor shaft 2 of the power motor 1 → first gear 3 → second gear 4 → first intermediate shaft 5 → third gear 6 → fourth gear 7 → first differential case 20, second differential case 8 → inner ring 21, and the power is output according to the speed difference between the left and right wheels, which are respectively: first planetary gear 9 → second planetary gear 18 → sun gear 19 → first output shaft A and first planetary gear 9, second planetary gear 18 (rotation and revolution) → first planetary shaft 11, second planetary shaft 12 → second planetary carrier 13 → second output shaft B output power. As for the other part of the power, the tire slips and cannot provide enough grip because of the low ground adhesion coefficient on the side of the second output shaft B. However, due to the closing of the clutch, the sun gear 19 is locked with the first planetary carrier 14 and the second planetary carrier 13 in a rotationally fixed manner, which ultimately means that the sun gear 19 is fixed with the first planetary carrier 14 and the second planetary carrier 13 and rotates together to transmit power, first planetary gear 9, second planetary gear 18 → first planetary shaft 11, second planetary shaft 12 → first planetary carrier 14 → clutch outer hub 15 → clutch 16 → clutch inner hub 17 → sun gear 19 → first output shaft A; the above two parts of power converge at the first output shaft A and are output together, which ultimately means that the output torque on the first output shaft A is increased, thereby increasing the ability to escape from difficulties.

[0034] In summary, according to the differential with integrated escape device proposed by the present invention, four spur gears are used to realize the differential function. There is no traditional open bevel gear differential. The volume, weight and envelope of the differential system are better, which is conducive to the layout of the whole vehicle. The gears of the planetary gear differential are all spur gear designs. By improving the manufacturing process, such as precision forging, etc., the manufacturing accuracy and quality of the differential can be improved, and the finishing process can be reduced, thereby reducing the manufacturing cost and maintenance cost. The left and right half-axle torque can be dynamically adjusted, the vehicle's handling stability can be improved, and the escape ability and off-road performance can be increased. The spur gears in the planetary gear structure mesh with each other, which can achieve smoother torque transmission, reduce energy loss, and improve the transmission efficiency of the system. Compared with the traditional open bevel gear structure, the planetary gear structure has better adaptability. It can be flexibly configured and adjusted according to different vehicle requirements to meet the use requirements of different vehicles.

[0035] Embodiment 2 See also Figure 6 , shown is a second embodiment of the present invention, the first differential housing 20 is fixedly connected to the above-mentioned clutch outer hub 15, the clutch inner hub 17 is fixedly connected to the shaft of the sun gear 19, and the grinding clutch plate can be placed between the first differential housing 20 and the sun gear 19.

[0036] Embodiment 3 See also Figure 7 , shown is a third embodiment of the present invention, the first differential housing 20 is fixedly connected to the above-mentioned clutch outer hub 15, the clutch inner hub 17 is fixedly connected to the first planetary carrier 14, and the grinding clutch plate can be placed between the first differential housing 20 and the first planetary carrier 14.

[0037] In the description of this specification, the description with reference to the terms "one embodiment", "some embodiments", "examples", "specific examples", or "some examples" means that the specific features, structures, materials or characteristics described in conjunction with the embodiment or example are included in at least one embodiment or example of the present invention. In this specification, the schematic representation of the above terms does not necessarily refer to the same embodiment or example. Moreover, the specific features, structures, materials or characteristics described may be combined in any one or more embodiments or examples in a suitable manner.

[0038] The above-mentioned embodiments only express several implementation methods of the present invention, and the descriptions thereof are relatively specific and detailed, but they cannot be understood as limiting the scope of the patent of the present invention. It should be pointed out that, for those of ordinary skill in the art, several variations and improvements can be made without departing from the concept of the present invention, and these all belong to the protection scope of the present invention. Therefore, the protection scope of the patent of the present invention shall be subject to the attached claims.

Claims

1. A differential with an integrated escape device, characterized in that: The differential of the integrated escape device comprises a housing, a reduction gear mechanism disposed in the housing, and a differential mechanism meshingly connected with the reduction gear mechanism; A differential mechanism, comprising a support assembly, a planetary gear assembly and a clutch assembly disposed in the support assembly, wherein the planetary gear assembly comprises a first planet carrier, a second planet carrier, a first planet shaft and a second planet shaft disposed between the first planet carrier and the second planet carrier, and a first planet wheel and a second planet wheel disposed on the first planet shaft and the second planet shaft respectively; Among them, an inner gear ring is provided between the reduction gear mechanism and the first planetary gear for meshing connection, a sun gear is provided on the clutch assembly, and the sun gear is meshingly connected with the second planetary gear, and the sun gear, the first planetary gear, the second planetary gear, and the inner gear ring are all spur gear structures.

2. The differential with integrated escape device according to claim 1, characterized in that: The ratio of the number of teeth of the inner gear ring to the number of teeth of the sun gear is 2:

1.

3. The differential with integrated escape device according to claim 2, characterized in that: The first planetary gear and the second planetary gear have the same number of teeth, module, pressure angle, and diameter.

4. The differential with integrated escape device according to claim 1, characterized in that: The support assembly includes a first differential housing supported on the housing through a first bearing, and a second differential housing supported on the housing through a second bearing, wherein the first differential housing and the second differential housing jointly support the planetary gear assembly and the clutch assembly.

5. The differential with integrated escape device according to claim 4, characterized in that: The first differential housing and the second differential housing respectively extend a first output shaft and a second output shaft to two sides for connecting with wheels.

6. The differential with integrated escape device according to claim 1, characterized in that: The clutch assembly includes a clutch, a clutch inner hub, and a clutch outer hub, and the clutch assembly is arranged between the sun gear and the second planetary gear.

7. The differential with integrated escape device according to claim 1, characterized in that: The reduction gear mechanism includes a power motor, a motor rotor shaft arranged on the power motor, a first gear arranged at one end of the motor rotor shaft away from the power motor, a second gear meshingly connected to the first gear, a first intermediate shaft connected to the second gear, a third gear arranged at the other end of the first intermediate shaft, and a fourth gear meshingly connected to the third gear, the fourth gear meshingly connected to the inner ring gear for transmitting power.

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