CN116792477A - Through-axle speed reducer and inter-axle differential assembly - Google Patents

Abstract

The application provides a through axle speed reducer and inter-axle differential assembly, which comprises a first transmission assembly, a second transmission assembly and a sliding tooth sleeve, wherein the first transmission assembly comprises a driving shaft, a gear ring seat rotationally connected with the driving shaft, a gear ring fixedly connected with the gear ring seat, a driving cylindrical gear arranged on the outer side of the gear ring seat, a planetary gear unit meshed with the gear ring and an output gear meshed with the planetary gear unit, and the output gear is connected with a rear axle assembly. The second transmission component is meshed with the driving cylindrical gear and is connected with the intermediate axle assembly. The sliding tooth sleeve is connected with the driving shaft and can move relative to the driving shaft, the sliding tooth sleeve is provided with three positions, and when the sliding tooth sleeve is positioned at any position, the sliding tooth sleeve synchronously rotates with at least two of the driving shaft, the driving cylindrical gear and the gear ring seat, so that power transmitted to the rear axle assembly and the middle axle assembly is changed, three gears are switched, and the sliding tooth sleeve is simple in structure and low in cost.

Description

Through-axle speed reducer and inter-axle differential assembly

Technical Field

The application relates to the technical field of automobile axles, in particular to a through axle speed reducer and an inter-axle differential mechanism assembly.

Background

The commercial vehicle generally has two working conditions of loading and no-load, and in order to reduce oil consumption, the middle axle and the rear axle are driven simultaneously during loading so as to provide sufficient power; at idle, one of the intermediate and rear axles is driven. Therefore, a shift structure is required to switch between the double-axle drive and the single-axle drive, and in the related art, a commercial vehicle mostly adopts a separate shift structure to realize gear switching between the double-axle drive and the single-axle drive, however, this results in an increase in the overall weight and cost of the vehicle.

Disclosure of Invention

In order to solve the technical problems, the application provides the through-axle speed reducer and the inter-axle differential assembly which can realize the switching between double-axle drive and single-axle drive, and are simple in structure and low in cost.

The application provides a through axle speed reducer and inter-axle differential assembly, which comprises a first transmission assembly, a second transmission assembly and a sliding tooth sleeve, wherein the first transmission assembly comprises a driving shaft, a gear ring seat rotationally connected with the driving shaft, a gear ring fixedly connected with the gear ring seat, a driving cylindrical gear arranged on the outer side of the gear ring seat, a planetary gear unit meshed with the gear ring and an output gear meshed with the planetary gear unit, and the output gear is connected with a rear axle assembly; the second transmission assembly is meshed with the driving cylindrical gear and is connected with the intermediate axle assembly; the sliding tooth sleeve is connected with the driving shaft and can move relative to the driving shaft, the sliding tooth sleeve is provided with three positions, and when the sliding tooth sleeve is positioned at any position, the sliding tooth sleeve synchronously rotates with at least two of the driving shaft, the driving cylindrical gear and the gear ring seat.

In one embodiment, the three positions include a first position, a second position, and a third position; when the sliding tooth sleeve is positioned at the first position, the sliding tooth sleeve, the driving shaft and the gear ring seat synchronously rotate, and the driving cylindrical gear is rotationally connected with the gear ring seat; when the sliding tooth sleeve is positioned at the second position, the sliding tooth sleeve, the driving shaft, the gear ring seat and the driving cylindrical gear synchronously rotate; when the sliding tooth sleeve is positioned at the third position, the sliding tooth sleeve, the gear ring seat and the driving cylindrical gear synchronously rotate, and the sliding tooth sleeve is rotationally connected with the driving shaft.

In an embodiment, the driving cylindrical gear includes a first assembly portion and a second assembly portion extending from the first assembly portion toward the sliding gear sleeve, the ring gear seat includes a first assembly segment rotationally connected with the first assembly portion and a second assembly segment extending from the first assembly segment toward the sliding gear sleeve, in a direction parallel to an axis of the driving shaft, a size of the second assembly segment is larger than a size of the second assembly portion, so that the second assembly segment can protrude out of the second assembly portion in a direction toward the sliding gear sleeve, and a size of the second assembly segment is larger than or equal to a size of the sliding gear sleeve, so that the sliding gear sleeve can be separated from the driving shaft.

In an embodiment, the sliding tooth sleeve, the driving shaft, the driving cylindrical gear and the gear ring seat are connected by a spline to realize synchronous rotation.

In an embodiment, the gear ring includes a first mounting portion, a first accommodating portion extending from the first mounting portion toward the output gear, and an input tooth disposed on an inner peripheral surface of the first accommodating portion, where the first mounting portion is fixedly connected to the gear ring seat, at least a part of the planetary gear unit is disposed in the first accommodating portion, and the input tooth is meshed with the planetary gear unit.

In an embodiment, the output gear includes a second mounting portion, a second accommodating portion extending from the second mounting portion toward the gear ring, and output teeth disposed on an inner peripheral surface of the second accommodating portion, the second mounting portion is connected to the rear axle assembly, at least a part of the planetary gear unit is disposed in the first accommodating portion, and the output teeth are meshed with the planetary gear unit.

In one embodiment, the planetary gear unit includes a first planetary gear, a second planetary gear meshed with the first planetary gear, a planetary carrier for supporting the first planetary gear and the second planetary gear, a first planetary shaft for rotatably supporting the first planetary gear on the planetary carrier, a second planetary shaft 17 for rotatably supporting the second planetary gear on the planetary carrier, the planetary carrier is fixedly connected with the driving shaft, the first planetary gear is meshed with the input teeth, and the second planetary gear is meshed with the output teeth.

In one embodiment, the first planetary gear comprises a first input wheel meshed with the input teeth and a second input wheel meshed with the second planetary gear, wherein the outer diameters of the first input wheel and the second input wheel are different.

In one embodiment, the second planetary gear comprises a first output wheel meshed with the second input wheel and a second output wheel meshed with the output teeth, wherein the outer diameters of the first output wheel and the second output wheel are different.

In one embodiment, the second transmission assembly comprises a driven cylindrical gear meshed with the driving cylindrical gear, a driven shaft connected with the driven cylindrical gear, and a bevel gear fixedly connected with the driven shaft, wherein the bevel gear is connected with the intermediate axle assembly.

The sliding tooth sleeve of the through-axle speed reducer and the inter-axle differential mechanism assembly is provided with three positions, and when the sliding tooth sleeve is positioned at any position, the sliding tooth sleeve synchronously rotates with at least two of the driving shaft, the driving cylindrical gear and the gear ring seat, so that the power transmitted to the rear axle assembly and the middle axle assembly is changed, the three gears are switched, and the structure is simple and the cost is low.

Drawings

FIG. 1 is a cross-sectional view of a through-axle reduction and inter-axle differential assembly according to an embodiment of the present application with a sliding sleeve in a first position;

FIG. 2 is a cross-sectional view of an input unit of a through-axle reduction and interaxle differential assembly according to an embodiment of the present application;

FIG. 3 is a cross-sectional view of a ring gear of a through-axle reduction and interaxle differential assembly according to an embodiment of the present application;

FIG. 4 is a perspective view of a through-axle reduction gear and first and second planet gears of an inter-axle differential assembly of an embodiment of the present application mounted on a planet carrier;

FIG. 5 is a cross-sectional view of an output gear of the through-axle reduction and interaxle differential assembly of one embodiment of the present application;

FIG. 6 is a cross-sectional view of a combination of a sliding sleeve and a drive shaft, a drive spur gear, and a ring gear seat of a through-axle reduction and inter-axle differential assembly of an embodiment of the present application, wherein the sliding sleeve is in a second position;

fig. 7 is a cross-sectional view of a combination of a sliding sleeve and a drive shaft, a drive spur gear, and a ring gear seat of a through-axle reduction and inter-axle differential assembly according to an embodiment of the present application, wherein the sliding sleeve is in a third position.

Detailed Description

In order that the above objects, features and advantages of the application will be readily understood, a more particular description of the application will be rendered by reference to the appended drawings. In the following description, numerous specific details are set forth in order to provide a thorough understanding of the present application. The present application may be embodied in many other forms than described herein and similarly modified by those skilled in the art without departing from the spirit of the application, whereby the application is not limited to the specific embodiments disclosed below.

In order that the above objects, features and advantages of the application will be readily understood, a more particular description of the application will be rendered by reference to the appended drawings. In the following description, numerous specific details are set forth in order to provide a thorough understanding of the present application. The present application may be embodied in many other forms than described herein and similarly modified by those skilled in the art without departing from the spirit of the application, whereby the application is not limited to the specific embodiments disclosed below.

An embodiment of the application provides a differential lock and a drive conversion structure of a through-axle speed reducer, which are used for switching double-axle drive and single-axle drive by adding a gear on the basis of a traditional gear shifting structure, so that weight and cost are reduced. Specifically, referring to fig. 1, an embodiment of the present application provides a through-axle speed reducer and inter-axle differential assembly, which includes a first transmission assembly 1, a second transmission assembly 2 meshed with the first transmission assembly 1, and a housing 4 covering the first transmission assembly 1 and the second transmission assembly 2.

The first transmission assembly 1 comprises a driving shaft 10 connected with the output end of the driving unit, a driving input unit rotationally connected with the driving shaft 10, a planetary gear unit meshed with the driving input unit, an output gear 18 meshed with the planetary gear unit and a sliding tooth sleeve 19 connected with the driving shaft 10, wherein the output gear 18 is fixedly connected with the rear axle assembly. The sliding tooth sleeve 19 and the driving shaft 10 can move relatively in the axial direction, so that the sliding tooth sleeve 19 can be selectively connected with the driving shaft 10 and/or the driving input unit to realize gear switching. The planetary gears of the planetary gear units are all cylindrical gears, the cylindrical gears are adopted as the planetary gears, the axial arrangement space is reduced, in addition, the cylindrical gears have no axial component force, and the transmission efficiency is improved.

Referring to fig. 4, in the embodiment of the present disclosure, the planetary gear unit includes a first planetary gear 13, a second planetary gear 14 engaged with the first planetary gear 13, a carrier 15 for supporting the first planetary gear 13 and the second planetary gear 14, a first planetary shaft 16 for rotatably supporting the first planetary gear 13 on the carrier 15, and a second planetary shaft 17 for rotatably supporting the second planetary gear 14 on the carrier 15, and power transmission is achieved by using the first planetary gear 13 and the second planetary gear 14 engaged with each other.

In other embodiments, the first planet wheel 13 and the second planet wheel 14 of the planet wheel unit may be provided as a fixed connection, both rotating in synchronization, and accordingly, the planet shafts supporting the first planet wheel 13 and the second planet wheel 14 are provided as one only.

As shown in connection with fig. 1 and 2, the active input unit comprises an active spur gear 11 and an input gear 12. The input gear 12 includes a ring gear seat 121 rotatably connected to the driving shaft 10 and a ring gear 122 fixedly connected to the ring gear seat 121, and a needle bearing is disposed between the ring gear seat 121 and the driving shaft 10, so that the driving shaft 10 can rotatably support the ring gear seat 121. In one embodiment, the ring gear 122 and the ring gear seat 121 are fixedly connected by using ring welding.

As shown in fig. 1, 6 and 7, the sliding tooth sleeve 19 includes three positions, when the sliding tooth sleeve 19 is in the first position, the sliding tooth sleeve 19 rotates synchronously with the driving shaft 10 and the gear ring seat 121, and the driving cylindrical gear 11 is rotationally connected with the gear ring seat 121, and at this time, only the rear axle assembly is driven, and the intermediate axle assembly is not driven; when the sliding tooth sleeve 19 is positioned at the second position, the sliding tooth sleeve 19 rotates synchronously with the driving shaft 10, the gear ring seat 121 and the driving cylindrical gear 11, so that the rear axle assembly and the middle axle assembly are driven simultaneously, and the axle difference differential locking does not have a differential function; when the sliding tooth sleeve 19 is positioned at the third position, the gear ring seat 121 of the sliding tooth sleeve 19 and the driving cylindrical gear 11 synchronously rotate, and the sliding tooth sleeve 19 is rotationally connected with the driving shaft 10, so that the rear axle assembly and the intermediate axle assembly are driven simultaneously, and the rotating speeds after being transmitted by the first planet gears 13 and the second planet gears 14 are changed due to the different outer diameters of the first planet gears 13 and the second planet gears 14, so that the differential mechanism has a differential function. The sliding tooth sleeve 19 moves relative to the driving shaft 10, so that the sliding tooth sleeve 19 has three different positions, and the sliding tooth sleeve 19 synchronously rotates with at least two of the driving shaft 10, the driving cylindrical gear 11 and the gear ring seat 121 at the different positions, so that the power transmitted to the rear axle assembly and the middle axle assembly is changed, the three gears are switched, and the gear shifting mechanism is simple in structure and low in cost.

Referring to fig. 2, the driving cylindrical gear 11 is sleeved on the outer periphery of the ring gear seat 121, and the driving cylindrical gear 11 includes a first assembly portion 111 and a second assembly portion 112 extending from the first assembly portion 111 toward the sliding gear sleeve 19, wherein an inner diameter of the first assembly portion 111 is smaller than an inner diameter of the second assembly portion 112. The ring gear seat 121 includes a first assembly segment 1211 rotatably connected to the first assembly portion 111, and a second assembly segment 1212 extending from the first assembly segment 1211 toward the sliding sleeve 19, wherein outer diameters of the first assembly segment 1211 and the second assembly segment 1212 are different. In the direction parallel to the axis of the driving shaft 10, the size of the second assembly section 1212 is larger than the size of the second assembly portion 112, so that the second assembly section 1212 can protrude out of the second assembly portion 112 in the direction towards the sliding tooth sleeve 19, and the size of the second assembly section 1212 is larger than or equal to the size of the sliding tooth sleeve 19, so that the sliding tooth sleeve 19 can be separated from the driving shaft 10, and the sliding tooth sleeve 19 can be not contacted with the second assembly portion 112 or the driving shaft 10 while being fixedly connected with the second assembly section 1212, so that three gear positions can be switched.

In one embodiment, a bearing is provided between the first assembly portion 111 and the first assembly segment 1211 such that a rotational connection is provided between the first assembly portion 111 and the first assembly segment 1211. The inner peripheral surface of the second assembly part 112 and the outer peripheral surface of the second mounting section are both provided with spline holes or splines, and the sliding tooth sleeve 19 is provided with the splines or the spline holes, and the sliding tooth sleeve 19 can synchronously rotate with the driving cylindrical gear 11, the sliding tooth sleeve 19 and the gear ring seat 121 through the matching of the splines and the spline holes.

The driving cylindrical gear 11 further includes driving cylindrical teeth 115 provided on the outer peripheral surfaces of the first and second assembly parts 111 and 112, and the driving cylindrical teeth 115 are engaged with the second transmission assembly 2.

As shown in fig. 1 and 3, the ring gear 122 has a cylindrical shape as a whole, and includes a first body 1221 and input teeth 1222 provided on an inner peripheral surface of the first body 1221, wherein the input teeth 1222 mesh with the first planet gears 13. Further, the first body 1221 includes a first mounting portion 1225 and a first receiving portion 1226 extending from the first mounting portion 1225 toward the output gear 18. The inner diameter of the first mounting portion 1225 is smaller than the inner diameter of the first accommodating portion 1226, the first mounting portion 1225 is fixedly connected with the ring gear seat 121, the first accommodating portion 1226 is used for accommodating part of the planet carrier 15 and the first planet gears 13, the input teeth 1222 are disposed on the inner circumferential surface of the first accommodating portion 1226, and the input teeth 1222 are meshed with the first planet gears 13 of the planet gear unit.

The cylindrical teeth of the first planet wheel 13 are meshed with the input teeth 1222 of the gear ring 122, the second planet wheel 14 is meshed with the output gear 18, the first planet wheel 13, the input teeth 1222, the second planet wheel 14 and the output gear 18 are all provided with cylindrical teeth, power transmission is realized by adopting cylindrical teeth meshing, the radial arrangement space is reduced, the number of teeth of the gears is more, the indexing diameter is larger, and the integral strength is improved.

In one embodiment, one of the driving shaft 10 and the sliding gear sleeve 19 is provided with a splined hole, and the other is provided with a spline, and the driving shaft 10 and the sliding gear sleeve 19 are fixedly connected in the circumferential direction through the cooperation between the spline and the splined hole.

In one embodiment, a spacer 109 is disposed between the end face of the needle bearing and the end face of the driving shaft 10 to realize axial limiting of the needle bearing.

Referring to fig. 5, the output gear 18 is entirely cylindrical and is fitted around the outer periphery of the drive shaft 10, and the output gear 18 includes a second body 181 and output teeth 182 provided on the inner peripheral surface of the second body 181, the output teeth 182 meshing with the second planetary gears 14. Further, the second body 181 includes a second mounting portion 1811 and a second accommodating portion 1812 extending from the second mounting portion 1811 toward the ring gear 122, where an inner diameter of the second mounting portion 1811 is smaller than an inner diameter of the second accommodating portion 1812, the second mounting portion 1811 is fixedly connected with the driving shaft 10, the second accommodating portion 1812 is used for accommodating a part of the planet carrier 15 and the second planet gears 14, the output teeth 182 are disposed on an inner peripheral surface of the second accommodating portion 1812, and the output teeth 182 are meshed with the second planet gears 14 of the planet gear unit.

Further, the second mounting portion 1811 is provided with a round hole matched with the driving shaft 10 and a splined hole matched with the input end of the rear axle assembly, and the input end of the rear axle assembly is fixedly connected with the second mounting portion 1811.

As shown in fig. 1 and 4, the planet carrier 15 is fixedly connected to the driving shaft 10 and is located in a receiving space defined by the driving input unit and the output gear 18. The planet carrier 15 is provided with a splined hole, the driving shaft 10 is provided with a spline matched with the splined hole, and the planet carrier 15 and the driving shaft 10 are fixedly installed together through the matching of the spline and the splined hole. The carrier 15 is provided with a fixing hole 151 for mounting the first planetary shaft 16 and the second planetary shaft 17, and the first planetary shaft 16 and the second planetary shaft 17 are penetrated into the fixing hole 151 and fixedly connected with the carrier 15 by a pin.

Referring to fig. 4, in the embodiment of the present disclosure, the first planetary gear 13 includes a first input wheel 131 engaged with the input teeth 1222 of the active input unit and a second input wheel 132 engaged with the second planetary gear 14, wherein the outer diameters of the first input wheel 131 and the second input wheel 132 are different. Further, the second input wheel 132 is closer to the second planet wheels 14 than the first input wheel 131, and the outer diameter of the second input wheel 132 is larger than the outer diameter of the first input wheel 131. Through setting up the planet wheel of different external diameters, can adjust the transmission ratio according to the user demand, it is more nimble to use.

In the disclosed embodiment, the second planetary gear 14 includes a first output wheel 141 meshed with the second input wheel 132 of the first planetary gear 13 and a second output wheel 142 meshed with the output teeth 182 of the output gear 18, wherein the outer diameters of the first output wheel 141 and the second output wheel 142 are different. Further, the first output wheel 141 is closer to the first planet wheel 13 than the second output wheel 142, and the outer diameter of the second output wheel 142 is smaller than the outer diameter of the first output wheel 141. Through setting up the planet wheel of different external diameters, can adjust the transmission ratio according to the user demand, it is more nimble to use.

Referring to fig. 1, in order to ensure stable and smooth operation of the first transmission assembly 1, the first transmission assembly 1 is rotatably supported on the housing 4 by using bearings, and specifically, the first transmission assembly 1 further includes a first bearing 101 disposed between the output gear 18 and the housing 4 and a second bearing 102 disposed between the input shaft 3 and the housing 4. The first bearing 101 and the second bearing 102 are arranged on two sides of the driving input unit and the output gear 18 to form a cross-arm bearing structure, so that the stress performance can be improved, and the supporting stability can be improved.

Further, the first bearing 101 and the second bearing 102 are each provided with a mounting hole, the housing 4 is provided with a mounting hole for mounting the first bearing 101 and the second bearing 102, the shaft diameter of the input shaft 10 and the shaft diameter of the output gear 18 are respectively fitted with the mounting holes of the first bearing 101 and the second bearing 102, and the first bearing 101 and the second bearing 102 are fitted with the mounting holes of the housing 4, so that the first bearing 101 is stably mounted between the output gear 18 and the housing 4, and the second bearing 102 is stably mounted between the driving shaft 10 and the housing 4.

The output end of the second transmission assembly 2 is connected with the input end of the intermediate axle assembly, and the second transmission assembly 2 comprises a driven cylindrical gear 21 meshed with the driving cylindrical gear 11, a driven shaft 22 fixedly connected with the driven cylindrical gear 21 and a bevel gear 23 fixedly connected with the driven shaft 22. The bevel gear 23 is provided at one end of the driven shaft 22, and the driven cylindrical gear 21 is fixedly connected with the driven shaft 22 so as to be capable of rotating in synchronization with the driven shaft 22. In one embodiment, one of the driven shaft 22 and the driven cylindrical gear 21 is provided with a splined hole, and the other is provided with a spline, and the driven cylindrical gear 21 and the driven shaft 22 are fixedly connected together through the cooperation of the spline and the splined hole.

In order to ensure stable and smooth rotation of the driven cylindrical gear 21, the driven shaft 22 is rotatably supported on the housing 4 by adopting a bearing, and further, the second transmission assembly 2 further comprises a third bearing 25, a fourth bearing 26 and a spacer 27, wherein the third bearing 25 and the fourth bearing 26 are arranged between the driven cylindrical gear 21 and the bevel gear 23. The third bearing 25 and the fourth bearing 26 are adopted to support the driven shaft 22, so that the stress performance can be improved, and the support stability of the driven shaft 22 can be improved.

Compared with the third bearing 26 which is closer to the bevel gear 23, the third bearing 25 is in contact with the fourth bearing 26, the opposite sides of the spacer 27 are respectively in contact with the third bearing 25 and the fourth bearing 26, one side, close to the bevel gear 23, of the third bearing 25 is in contact with the end face of the bevel gear 23, one side, close to the driven cylindrical gear 21, of the fourth bearing 26 is in contact with the driven cylindrical gear 21, one end, far away from the bevel gear 23, of the driven shaft 22 is provided with a limit nut 29, one side, far away from the fourth bearing 26, of the driven cylindrical gear 21 is in contact with the limit nut 29, and therefore limiting of the driven cylindrical gear 21, the third bearing 25 and the fourth bearing 26 in the axial direction is achieved.

Further, the third bearing 25 and the fourth bearing 26 are provided with mounting holes, the housing 4 is provided with mounting holes for mounting the third bearing 25 and the fourth bearing 26, the shaft diameter of the driven shaft 22 is matched with the mounting holes of the third bearing 25 and the fourth bearing 26, and the third bearing 25 and the fourth bearing 26 are matched with the mounting holes of the housing 4, so that the third bearing 25 and the fourth bearing 26 are stably mounted between the driven shaft 22 and the housing 4.

In one embodiment, the through axle speed reducer and inter-axle differential assembly further comprises an adjusting ring and oil seal assembly 5, the adjusting ring and oil seal assembly 5 is in threaded connection with the shell 4, an oil seal lip of the adjusting ring and oil seal assembly 5 is matched with the shaft diameter of the flange 6, the flange 6 is in spline connection with the driving shaft 10, and the flange 6 is fixed with the driving shaft 10 by a fixing nut.

The first planetary gear 13 and the second planetary gear 14 of the through-axle speed reducer and inter-axle differential mechanism assembly adopt a cylindrical gear pair structure, the first planetary gear 13 and the second planetary gear 14 are connected with the planet carrier 15 through the first planetary shaft 16 and the second planetary shaft 17, the axial arrangement space is shortened, the whole weight is lightened, the cylindrical gear has no axial component force, and the transmission efficiency and the transmission reliability are improved.

The through-axle speed reducer and inter-axle differential assembly comprises three gears, the sliding tooth sleeve 19 moves relative to the driving shaft 10 to be capable of being switched among the three positions, so that the gears are switched, the three positions of the sliding tooth sleeve 19 correspond to three different gears respectively, and the three positions are specific:

as shown in fig. 1, when the sliding tooth sleeve 19 is in the first position, the through-axle reducer and inter-axle differential assembly are in a gear position where the intermediate axle assembly and the rear axle assembly are at a differential speed: the sliding tooth sleeve 19 is driven to move towards the direction approaching to the gear ring 122, so that the sliding tooth sleeve 19 is connected with the driving shaft 10 and the gear ring seat 121 but not connected with the driving cylindrical gear 11, in this case, the sliding tooth sleeve 19, the driving shaft 10 and the gear ring seat 121 cannot be oppositely rotated, the driving shaft 10 drives the input gear 12 and the planet carrier 15, and further drives the rear axle assembly through the output gear 18, and the middle axle assembly meshed with the second transmission assembly 2 cannot be driven because the driving shaft 10 cannot drive the driving cylindrical gear 11;

as shown in fig. 6, when the sliding gear sleeve 19 is located at the second position, the through-axle speed reducer and the inter-axle differential assembly are located at a gear where the intermediate axle assembly and the rear axle assembly are simultaneously driven and the differential has no differential function: the sliding tooth sleeve 19 is driven to move towards the direction approaching to the gear ring 122, so that the sliding tooth sleeve 19 is connected with the driving shaft 10, the gear ring seat 121 and the driving cylindrical gear 11, in this case, the sliding tooth sleeve 19 rotates synchronously with the driving shaft 10, the gear ring seat 121 and the driving cylindrical gear 11, the driving shaft 10 drives the input gear 12, the planet carrier 15 and the driving cylindrical gear 11, and thus the rear axle assembly and the middle axle assembly are driven at the same time, and the axle difference differential locking does not have a differential function;

as shown in fig. 7, when the sliding gear sleeve 19 is in the third position, the through-axle speed reducer and the inter-axle differential assembly are in a gear in which the intermediate axle assembly and the rear axle assembly drive simultaneously, and the differential has a differential function:

the sliding gear sleeve 19 is driven to move towards the direction close to the gear ring 122, so that the sliding gear sleeve 19 is connected with the gear ring seat 121 and the driving cylindrical gear 11, but is not connected with the driving shaft 10, in this case, the sliding gear sleeve 19 synchronously rotates with the gear ring seat 121 and the driving cylindrical gear 11, the driving shaft 10 drives the planet carrier 15, the planet carrier 15 simultaneously transmits power to the first planet gear 13 and the second planet gear 14, the second planet gear 14 drives the output gear 18 to rotate, the output gear 18 drives the rear axle assembly, the first planet gear 13 drives the gear ring 122, the gear ring 122 drives the driving cylindrical gear 11, the driving cylindrical gear 11 drives the second transmission component 2, and the second transmission component 2 drives the middle axle assembly, so that the rotating speed after being transmitted by the first planet gear 13 and the second planet gear 14 is changed due to the fact that the outer diameters of the first planet gear 13 and the second planet gear 14 are different, and the differential mechanism has a differential function.

In the description of the present application, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", "axial", "radial", "circumferential", etc. indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings are merely for convenience in describing the present application and simplifying the description, and do not indicate or imply that the device or element being referred to must have a specific orientation, be configured and operated in a specific orientation, and therefore should not be construed as limiting the present application.

Furthermore, the terms "first," "second," and the like, are used for descriptive purposes only and are not to be construed as indicating or implying a relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defining "a first" or "a second" may explicitly or implicitly include at least one such feature. In the description of the present application, the meaning of "plurality" means at least two, for example, two, three, etc., unless specifically defined otherwise.

In the present application, unless explicitly specified and limited otherwise, the terms "mounted," "connected," "secured," and the like are to be construed broadly, and may be, for example, fixedly connected, detachably connected, or integrally formed; can be mechanically or electrically connected; either directly or indirectly, through intermediaries, or both, may be in communication with each other or in interaction with each other, unless expressly defined otherwise. The specific meaning of the above terms in the present application can be understood by those of ordinary skill in the art according to the specific circumstances.

In the present application, unless expressly stated or limited otherwise, a first feature "up" or "down" a second feature may be the first and second features in direct contact, or the first and second features in indirect contact via an intervening medium. Moreover, a first feature being "above," "over" and "on" a second feature may be a first feature being directly above or obliquely above the second feature, or simply indicating that the first feature is level higher than the second feature. The first feature being "under", "below" and "beneath" the second feature may be the first feature being directly under or obliquely below the second feature, or simply indicating that the first feature is less level than the second feature.

It will be understood that when an element is referred to as being "fixed" or "disposed" on another element, it can be directly on the other element or intervening elements may also be present. When an element is referred to as being "connected" to another element, it can be directly connected to the other element or intervening elements may also be present. The terms "vertical," "horizontal," "upper," "lower," "left," "right," and the like are used herein for illustrative purposes only and are not meant to be the only embodiment.

The technical features of the above-described embodiments may be arbitrarily combined, and all possible combinations of the technical features in the above-described embodiments are not described for brevity of description, however, as long as there is no contradiction between the combinations of the technical features, they should be considered as the scope of the description.

The above examples illustrate only a few embodiments of the application, which are described in detail and are not to be construed as limiting the scope of the application. It should be noted that it will be apparent to those skilled in the art that several variations and modifications can be made without departing from the spirit of the application, which are all within the scope of the application. Accordingly, the scope of protection of the present application is to be determined by the appended claims.

Claims (10)

1. A through-axle reduction gear and interaxle differential assembly comprising:

the first transmission assembly comprises a driving shaft, a gear ring seat rotationally connected with the driving shaft, a gear ring fixedly connected with the gear ring seat, a driving cylindrical gear arranged on the outer side of the gear ring seat, a planetary gear unit meshed with the gear ring and an output gear meshed with the planetary gear unit, and the output gear is connected with the rear axle assembly; a kind of electronic device with high-pressure air-conditioning system

The second transmission assembly is meshed with the driving cylindrical gear and is connected with the intermediate axle assembly; a kind of electronic device with high-pressure air-conditioning system

The sliding tooth sleeve is connected with the driving shaft and can move relative to the driving shaft, the sliding tooth sleeve is provided with three positions, and when the sliding tooth sleeve is positioned at any position, the sliding tooth sleeve synchronously rotates with at least two of the driving shaft, the driving cylindrical gear and the gear ring seat.

2. The through-axle reducer and inter-axle differential assembly of claim 1, wherein the three positions comprise a first position, a second position, and a third position;

when the sliding tooth sleeve is positioned at the first position, the sliding tooth sleeve, the driving shaft and the gear ring seat synchronously rotate, and the driving cylindrical gear is rotationally connected with the gear ring seat;

when the sliding tooth sleeve is positioned at the second position, the sliding tooth sleeve, the driving shaft, the gear ring seat and the driving cylindrical gear synchronously rotate;

when the sliding tooth sleeve is positioned at the third position, the sliding tooth sleeve, the gear ring seat and the driving cylindrical gear synchronously rotate, and the sliding tooth sleeve is rotationally connected with the driving shaft.

3. The through-axle reduction and inter-axle differential assembly according to claim 1 or 2, wherein the driving spur gear comprises a first assembly portion and a second assembly portion extending from the first assembly portion toward the sliding sleeve;

the gear ring seat comprises a first assembly section rotationally connected with the first assembly part and a second assembly section extending from the first assembly section towards the sliding gear sleeve, the second assembly section can protrude out of the second assembly part in the direction towards the sliding gear sleeve in the direction parallel to the axis of the driving shaft, and the size of the second assembly section is larger than or equal to that of the sliding gear sleeve.

4. A through-axle reducer and inter-axle differential assembly as claimed in claim 3, wherein spline connections are employed between said sliding sleeve and said drive shaft, and between said drive spur gear and said ring gear mount.

5. The through-axle reduction gear and inter-axle differential assembly according to claim 1, wherein the ring gear includes a first mounting portion, a first receiving portion extending from the first mounting portion toward the output gear, and input teeth provided on an inner peripheral surface of the first receiving portion, the first mounting portion being fixedly connected to the ring gear seat, at least part of the planetary gear units being provided in the first receiving portion, the input teeth being engaged with the planetary gear units.

6. The through-axle reduction gear and inter-axle differential assembly according to claim 5, wherein the output gear includes a second mounting portion, a second receiving portion extending from the second mounting portion toward the ring gear, and output teeth provided on an inner peripheral surface of the second receiving portion, the second mounting portion being connected to the rear axle assembly, at least part of the planetary gear unit being provided in the first receiving portion, the output teeth being engaged with the planetary gear unit.

7. The through-axle reducer and inter-axle differential assembly of claim 6, wherein said planetary gear unit comprises a first planetary gear, a second planetary gear engaged with said first planetary gear, a carrier for supporting said first planetary gear and said second planetary gear, a first planetary shaft for rotatably supporting said first planetary gear on said carrier, a second planetary shaft for rotatably supporting said second planetary gear on said carrier, said carrier being fixedly connected with said drive shaft, said first planetary gear being engaged with said input teeth, and said second planetary gear being engaged with said output teeth.

8. The through-axle reducer and inter-axle differential assembly of claim 7, wherein the first planet wheel comprises a first input wheel meshed with the input teeth and a second input wheel meshed with the second planet wheel, wherein the outer diameters of the first input wheel and the second input wheel are not the same.

9. The through-axle reducer and inter-axle differential assembly of claim 8, wherein the second planet wheel comprises a first output wheel meshed with the second input wheel and a second output wheel meshed with the output tooth, wherein the outer diameters of the first output wheel and the second output wheel are not the same.

10. The through-axle reduction and inter-axle differential assembly of claim 1, wherein the second drive assembly includes a driven cylindrical gear engaged with the driving cylindrical gear, a driven shaft connected with the driven cylindrical gear, and a bevel gear fixedly connected with the driven shaft, the bevel gear being connected with the intermediate axle assembly.