Speed reducer and vehicle

Abstract

The present application relates to the technical field of speed reducers, and in particular to a speed reducer and a vehicle. The speed reducer comprises a differential assembly and a housing, wherein the differential assembly comprises a planetary gear, a linear shaft and a half-shaft gear, the planetary gear being sleeved on the outer side of the linear shaft, and the half-shaft gear being arranged on one side of the linear shaft and engaging with the planetary gear; a lubricating liquid flow channel is provided in the linear shaft, and an oil path outlet in communication with the lubricating liquid flow channel is provided at the joint of the planetary gear and the linear shaft; and the housing is provided with an oil path inlet, and the lubricating liquid flow channel is in communication with the oil path inlet. On the basis of the speed reducer and the vehicle, which are provided in the present application, the lubricating effect of the differential assembly is effectively improved, thereby prolonging the service life of the differential assembly, and effectively avoiding a sintering phenomenon possibly caused by poor lubrication of the planetary gear of the differential assembly.

Description

Reducer and vehicle

[0001] CROSS-REFERENCE TO RELATED APPLICATIONS

[0002] This application claims priority to the Chinese patent application with application number CN202311715250.9 and title “Speed ​​Reducer and Vehicle” filed with the Patent Office of China on December 14, 2023, the entire contents of which are incorporated by reference into this application. Technical Field

[0003] The present application relates to the technical field of speed reducers, and in particular to a speed reducer and a vehicle. Background Art

[0004] With the rapid development of electric vehicles, to meet the diverse demands of future vehicles and electric drive systems, reducers require more groundbreaking and innovative new configurations. Currently, the majority of pure electric vehicle reducers on the market are single-speed reducers. Single-speed reduction schemes utilize a fixed transmission ratio, which typically fails to balance the power and economy of pure electric vehicles. This single-ratio design fails to simultaneously achieve low-speed starting acceleration, high-speed cruising speed, and gradeability. Furthermore, high-speed cruising economy is poor, resulting in high power consumption at high speeds.

[0005] In the long term, two-speed transmissions will become a trend, optimizing motor operation, reducing motor output torque, reducing motor size and cost, and offering improved high-speed performance. However, existing two-speed reducers fail to adequately consider the lubrication of high-torque differentials, which can lead to poor lubrication and shortened differential life. Under extreme differential conditions, the differential's planetary gears can even sinter, causing the differential assembly to fail and rendering the vehicle unable to differentially drive the wheels.

[0006] In addition, the current two-speed reducer shift actuator has low integration and occupies a large space.

[0007] Application Contents

[0008] The purpose of this application is to provide a reducer and a vehicle, so as to solve, to a certain extent, the technical problem that the two-speed reducer in the prior art does not give sufficient consideration to the lubrication of the high-torque differential, which easily causes poor lubrication of the differential and reduces its service life. Under extreme differential conditions, the planetary gears of the differential may even sinter, thereby causing the differential assembly to fail and making it impossible for the entire vehicle to perform differential speed on both sides of the wheels.

[0009] According to a first aspect of the present application, a speed reducer is provided, comprising a differential assembly and a housing, wherein the differential assembly comprises planetary gears, a straight shaft, and side gears, wherein the planetary gears are sleeved on the outside of the straight shaft, and the side gears are arranged on one side of the straight shaft and mesh with the planetary gears;

[0010] A lubricating fluid flow channel is provided in the inline shaft, and an oil outlet communicating with the lubricating fluid flow channel is provided at the connection between the planetary gear and the inline shaft;

[0011] The housing is provided with an oil circuit inlet, and the lubricating fluid flow channel is communicated with the oil circuit inlet.

[0012] Furthermore, the differential assembly also includes a transmission housing portion, the straight shaft is fixedly arranged in the transmission housing portion, a portion of the transmission housing portion is embedded in the housing, and an annular flow channel is provided on the outside of the portion of the transmission housing portion embedded in the housing, the annular flow channel is coaxially arranged with the half-shaft gear, and the lubricating fluid flow channel and the oil circuit inlet are both connected via the annular flow channel.

[0013] Furthermore, the differential assembly further includes at least two sealing rings, which are arranged between the transmission housing portion and the housing, and are arranged on both sides of the annular flow channel in the axial direction of the side gear.

[0014] Furthermore, the straight shaft includes a positioning pin hole and an oil inlet hole, the positioning pin hole and the oil inlet hole are respectively arranged at both ends of the straight shaft in the axial direction, and the positioning pin hole and the oil inlet hole are symmetrically arranged about the axis of the side gear;

[0015] The straight shaft is pin-connected to the transmission housing via the positioning pin hole, and the straight shaft is communicated with the annular flow channel via the oil inlet hole.

[0016] Furthermore, the lubricating fluid flow channel includes a connecting portion and an outflow portion that are connected to each other, the connecting portion extends along the axial direction of the straight shaft, the outflow portion extends along the radial direction of the straight shaft, and the opening formed by the outflow portion on the surface of the straight shaft is the oil circuit outlet.

[0017] Furthermore, a side surface of the straight shaft is provided with a notch, and the notch is provided corresponding to the oil outlet, so that each of the oil outlets is provided in the notch.

[0018] Furthermore, in any cross section perpendicular to the axial direction of the straight axis, the cross-sectional area of ​​the straight axis is 10 to 20 times the area of ​​the pattern formed by the connecting portion.

[0019] Furthermore, the differential assembly includes two planetary gears, the two planetary gears are symmetrically arranged about the axis of the side gear, and the outflow portion is arranged corresponding to the planetary gears.

[0020] Furthermore, it also includes a shift execution assembly, a synchronizer, an input shaft, a first gear gear, and a second gear gear, wherein the first gear gear, the synchronizer, and the second gear gear are all sleeved on the input shaft and are arranged in sequence along the axis direction of the input shaft;

[0021] The shift execution assembly is in driving connection with the synchronizer to control the synchronizer to engage with the first gear or the second gear.

[0022] Furthermore, the shift execution assembly includes a shift driving portion and a shift fork portion that are transmission-connected to each other, the shift fork portion is arranged parallel to the input shaft, and the shift fork portion is transmission-connected to the synchronizer to drive the synchronizer to move along the input shaft.

[0023] Furthermore, the shift execution assembly further includes a driving gear and an idler gear, the driving gear is coaxially arranged with the shift drive portion, and the shift fork portion is provided with transmission teeth capable of meshing with the idler gear.

[0024] Furthermore, the fork portion is a ball screw fork.

[0025] Furthermore, it also includes an intermediate shaft assembly, which is arranged between the input shaft and the differential assembly, and the first gear gear or the second gear gear is transmission-connected to the transmission housing via the intermediate shaft assembly.

[0026] Furthermore, the transmission housing portion includes a housing body and a transmission ring gear, the transmission ring gear is arranged on the outside of the housing body, and the transmission ring gear is coaxially arranged with the half-shaft gear, and the transmission housing portion is transmission-connected to the intermediate shaft assembly via the transmission ring gear.

[0027] According to the second aspect of the present application, a vehicle is provided, comprising a reducer as described in any of the above technical solutions, and thus having all the beneficial technical effects of the reducer, which will not be described in detail here.

[0028] Compared with the prior art, the present invention has the following advantages:

[0029] The reducer provided in this application provides a lubricating fluid flow channel on the straight shaft, an oil inlet on the housing, and an oil outlet at the connection between the planetary gears and the straight shaft, and the lubricating fluid flow channel is connected to the oil inlet and the oil outlet respectively. In this way, the lubricating fluid can enter the differential assembly through the lubricating fluid flow channel and the oil inlet in sequence through the oil inlet on the housing to lubricate the planetary gears of the differential assembly, effectively improving the lubrication effect of the differential assembly, thereby increasing the service life of the differential assembly and effectively preventing the planetary gears of the differential assembly from even sintering. After calculation, the reducer provided by this solution can achieve a CLTC (China Light-duty Vehicle Test Cycle) comprehensive efficiency of 98% through the above-mentioned lubrication means.

[0030] In order to make the above-mentioned objects, features and advantages of the present application more obvious and easy to understand, preferred embodiments are given below and described in detail with reference to the accompanying drawings. BRIEF DESCRIPTION OF THE DRAWINGS

[0031] In order to more clearly illustrate the specific implementation methods of the present application or the technical solutions in the prior art, the following is a brief introduction to the drawings required for use in the specific implementation methods or the description of the prior art. Obviously, the drawings described below are some implementation methods of the present application. For ordinary technicians in this field, other drawings can be obtained based on these drawings without any creative work.

[0032] FIG1 is a schematic cross-sectional view of a reducer according to an embodiment of the present application;

[0033] FIG2 is a schematic cross-sectional view of a differential assembly according to an embodiment of the present application;

[0034] FIG3 is a schematic diagram of the axonometric structure of a straight shaft provided in an embodiment of the present application;

[0035] FIG4 is a schematic diagram of the internal axonometric structure of a reducer provided in an embodiment of the present application;

[0036] FIG5 is an enlarged structural diagram of the reducer provided in FIG4 at position A;

[0037] FIG6 is another schematic diagram of the internal isometric structure of the reducer provided in an embodiment of the present application;

[0038] FIG7 is a schematic side view of the structure of a reducer provided in an embodiment of the present application;

[0039] FIG8 is a schematic diagram of the cross-sectional structure of the reducer provided in FIG7 obtained by cutting along the BB direction.

[0040] Figure numerals: 11-straight shaft; 111-missing part; 12-lubricating fluid flow channel; 121-connecting part; 122-outflow part; 123-oil inlet hole; 124-oil outlet; 125-locating pin hole; 13-planetary gear; 14-side shaft gear; 15-transmission housing; 151-housing body; 1511-injection flow channel; 152-transmission ring gear; 16-annular flow channel; 17-sealing ring; 18-fixing pin; 2-housing; 21-front housing; 22-rear housing; 221-oil inlet; 31-shift drive part; 321-driving gear; 322-idler gear; 33-shift fork part; 331-transmission tooth; 34-synchronizer; 4-input shaft; 5-first gear; 6-second gear; 7-intermediate shaft assembly; 70-intermediate shaft; 71-first gear; 72-second gear; 73-intermediate gear. DETAILED DESCRIPTION

[0041] The technical solution of the present application will be clearly and completely described below in conjunction with the accompanying drawings. Obviously, the described embodiments are only part of the embodiments of the present application, rather than all the embodiments.

[0042] The components of the embodiments of the present application generally described and shown in the drawings herein may be arranged and designed in a variety of different configurations. Therefore, the following detailed description of the embodiments of the present application provided in the drawings is not intended to limit the scope of the claimed application, but merely represents selected embodiments of the present application.

[0043] Based on the embodiments in this application, all other embodiments obtained by ordinary technicians in this field without making any creative work shall fall within the scope of protection of this application.

[0044] In the description of this application, it should be noted that the terms "center," "upper," "lower," "left," "right," "vertical," "horizontal," "inner," and "outer," etc., indicating orientations or positional relationships, are based on the orientations or positional relationships shown in the accompanying drawings and are intended solely to facilitate the description of this application and simplify the description. They do not indicate or imply that the devices or components referred to must have a specific orientation, be constructed, or operate in a specific orientation. Therefore, they should not be construed as limitations on this application. Furthermore, the terms "first," "second," and "third" are used for descriptive purposes only and should not be construed as indicating or implying relative importance.

[0045] In the description of this application, it should be noted that, unless otherwise expressly specified or limited, the terms "mounted," "connected," and "connected" should be understood in a broad sense. For example, they can refer to fixed connections, detachable connections, or integral connections; mechanical connections or electrical connections; direct connections or indirect connections through an intermediate medium; and internal connections between two components. Those skilled in the art will understand the specific meanings of the above terms in this application based on the specific circumstances.

[0046] The following describes a speed reducer and a vehicle according to some embodiments of the present application with reference to FIG. 1 to FIG. 8 .

[0047] Referring to Figures 1 to 8 , an embodiment of the first aspect of the present application provides a speed reducer comprising a differential assembly and a housing 2. The differential assembly comprises planetary gears 13, a straight shaft 11, and side gears 14. The planetary gears 13 are sleeved on the outside of the straight shaft 11, and the side gears 14 are disposed on both sides of the straight shaft 11 and mesh with the planetary gears 13. A lubricating fluid flow channel 12 is disposed within the straight shaft 11, and an oil outlet 124 communicating with the lubricating fluid flow channel 12 is disposed at the connection between the planetary gears 13 and the straight shaft 11. The housing 2 is provided with an oil inlet 221, and the lubricating fluid flow channel 12 is communicated with the oil inlet 221.

[0048] The reducer provided by the above technical features is provided with a lubricating liquid flow channel 12 on the straight shaft 11, an oil circuit inlet 221 on the housing 2, and an oil circuit outlet 124 at the connection between the planetary gears 13 and the straight shaft 11, and the lubricating liquid flow channel 12 is connected to the oil circuit inlet 221 and the oil circuit outlet 124 respectively. In this way, through the oil circuit inlet 221 on the housing 2, the lubricating liquid can enter the differential assembly through the lubricating liquid flow channel 12 and the oil circuit inlet 221 in sequence to lubricate the planetary gears 13 of the differential assembly, effectively improving the lubrication effect of the differential assembly, thereby increasing the service life of the differential assembly and effectively avoiding the planetary gears 13 of the differential assembly from even sintering. After calculation, the reducer provided by this solution can achieve a CLTC (China Light-duty Vehicle Test Cycle) comprehensive efficiency of 98% through the above lubrication means.

[0049] Preferably, as shown in Figures 1 and 2 , the differential assembly typically includes two side gears 14 , which are disposed on either side of the straight shaft 11 and mesh with the planetary gears 13 to achieve differential power output between the left and right half shafts. The axes of the two side gears 14 coincide with each other.

[0050] Optionally, as shown in Figures 7 and 8, the above-mentioned housing 2 may include a front shell 21 and a rear shell 22, which are engaged with each other to form an accommodation space, and the above-mentioned differential assembly, the following shift execution assembly, the synchronizer 34, the input shaft 4, the first gear gear 5 and the second gear gear 6 are all arranged in the accommodation space.

[0051] Preferably, as shown in FIG. 7 , the oil passage inlet 221 may be provided on the rear housing 22 .

[0052] Preferably, as shown in Figures 1, 2, 4 to 6, the differential assembly may further include a transmission housing portion 15, in which the above-mentioned straight shaft 11 is fixedly arranged in the transmission housing portion 15, and a portion of the transmission housing portion 15 is embedded in the housing 2. An annular flow channel 16 is provided on the outside of the portion of the transmission housing portion 15 embedded in the housing 2, and the annular flow channel 16 is coaxially arranged with the half-shaft gear 14. The lubricating fluid flow channel 12 and the oil circuit inlet 221 are connected via the annular flow channel 16. In this way, when the transmission housing portion 15 rotates under the drive of the intermediate shaft assembly 7 described below, a portion of the annular flow channel 16 always docks with the above-mentioned oil circuit inlet 221, so that the oil circuit inlet 221 fixedly arranged on the rear housing 22 is always connected to the rotating transmission housing portion 15.

[0053] It should be noted that part of the transmission housing 15 is embedded in the housing 2 , which can be understood as a groove provided on the housing 2 that can accommodate the part of the transmission housing 15 embedded in the housing 2 , so as to ensure the compactness of the reducer structure.

[0054] Preferably, as shown in Figures 1, 2, and 4 to 6, the transmission housing 15 may include a housing body 151 and a transmission ring gear 152. The transmission ring gear 152 is disposed outside the housing body 151 to facilitate power transmission of the differential assembly. The housing body 151 may form a housing space within which the side gears 14, planetary gears 13, and straight shaft 11 may be disposed, providing a stable and independent space for the transmission of the differential assembly.

[0055] Preferably, as shown in Figures 5 and 6 , the housing body 151 may be cylindrical, with the axis of the housing body 151 coinciding with the axis of the side gear 14. Correspondingly, as shown in Figure 6 , the transmission ring gear 152 may be sleeved on the outside of the housing body 151. In other words, the transmission ring gear 152 may also be coaxially disposed with the side gear 14.

[0056] Optionally, the transmission ring gear 152 and the housing body 151 can be detachably connected to ensure the replaceability and maintainability of both the transmission ring gear 152 and the housing body 151, effectively reducing maintenance costs. For example, as shown in Figures 1 and 2, the outer side of the housing body 151 can be provided with a flange, and the transmission ring gear 152 can be bolted to the flange.

[0057] Alternatively, as shown in FIG2 , the annular flow channel 16 may be provided at one end of the housing body 151 near the rear housing 22. The annular flow channel 16 may be an annular groove surrounding the outer side of the housing body 151. However, the annular flow channel 16 is not limited to an annular groove. Any form of an annular passage for the lubricating liquid to flow into the injection channel 1511 described below can be provided on the outer side of the housing body 151. For example, the annular flow channel 16 may be formed by two annular protrusions arranged side by side on the outer side of the housing body 151.

[0058] Preferably, as shown in Figures 1 and 2, the differential assembly also includes at least two sealing rings 17, which are arranged between the transmission housing portion 15 and the housing 2, and the sealing rings 17 are arranged on both sides of the annular flow channel 16 in the axial direction of the side gear 14 to prevent the lubricating fluid in the annular oil channel from leaking from the annular flow channel 16, thereby ensuring the sealing of the annular flow channel 16.

[0059] Preferably, as shown in FIG. 2 and FIG. 5 , the transmission housing 15 is provided with a liquid injection channel 1511 , one end of which is communicated with the annular channel 16 , and the other end of which is communicated with the oil inlet hole 123 .

[0060] In the embodiment, as shown in Figures 1 and 2 , the straight shaft 11 is preferably positioned perpendicular to the axis of the side gears 14. A locating pin hole 125 is provided at one end of the straight shaft 11, extending through the shaft 11 in the direction of the axis of the side gears 14. The differential assembly may further include a retaining pin 18, which extends through the locating pin hole 125 and is secured to the housing 151, thereby securing the straight shaft 11 to the housing 151.

[0061] Preferably, as shown in FIG. 1 to FIG. 3 , the straight shaft 11 may include an oil inlet hole 123 , and the oil inlet hole 123 may be communicated with the injection channel 1511 and the lubricating liquid channel 12 , respectively.

[0062] Preferably, as shown in Figures 1 to 3, the oil inlet hole 123 and the positioning pin hole 125 can be respectively arranged at both ends of the axis direction of the straight shaft 11, and the positioning pin hole 125 and the oil inlet hole 123 can be symmetrically arranged about the axis of the half-shaft gear 14 to ensure the rotational stability of the straight shaft 11 and avoid the straight shaft 11 being heavier on one side during the rotation process with the axis of the half-shaft gear 14 as the axis, causing the straight shaft 11 to be dislocated, thereby affecting the engagement between the planetary gear 13 and the half-shaft gear 14.

[0063] Furthermore, as shown in Figures 1 and 2, the differential assembly may include two planetary gears 13, which are symmetrically arranged about the axis of the half-shaft gear 14. This not only improves the stability of the power transmission of the two half-shaft gears 14, but also further ensures the rotational stability of the straight shaft 11, thereby preventing the straight shaft 11 from being overweight on one side during the rotation about the axis of the half-shaft gear 14.

[0064] Preferably, as shown in Figures 1 to 3, the lubricating fluid flow channel 12 may include a connecting portion 121 and an outflow portion 122 that communicate with each other. The connecting portion 121 extends along the axis of the straight shaft 11, and the outflow portion 122 extends radially of the straight shaft 11. The opening formed by the outflow portion 122 on the surface of the straight shaft 11 is the aforementioned oil outlet 124.

[0065] Preferably, as shown in Figures 1 and 2, the outflow portion 122 can penetrate the straight shaft 11 along the radial direction of the straight shaft 11. In other words, each of the above-mentioned outflow portions 122 can form two oil outlets 124 opposite to each other on the straight shaft 11, which not only effectively improves the outflow efficiency of the lubricating fluid, but also improves the uniformity of the circumferential distribution of the lubricating fluid along the straight shaft 11, further improving the lubrication effect of the differential assembly.

[0066] It should be noted that Figures 1 to 3 above show an example in which only one outflow portion 122 is provided at the connection between the planetary gear 13 and the straight shaft 11. However, this is not limited to this. As long as the bending strength of the straight shaft 11 can be guaranteed, multiple outflow portions 122 can be provided at the connection between the planetary gear 13 and the straight shaft 11. The multiple outflow portions 122 can be evenly distributed along the circumference of the straight shaft 11.

[0067] Correspondingly, the outflow portion 122 can be provided corresponding to both the planetary gears 13. As shown in Figures 1 to 3, an example is shown in which there are two planetary gears 13. Correspondingly, the portions of the straight shaft 11 connected to the two planetary gears 13 can both be provided with the outflow portion 122.

[0068] Preferably, as shown in Figures 1 to 3, a notch 111 is provided on the side of the straight shaft 11, and the notch 111 is provided corresponding to the oil outlet 124, so that each oil outlet 124 is provided in the notch 111. In this way, the notch 111 forms a gap at the connection between the straight shaft 11 and the planetary gear 13, so that the lubricating fluid can flow out from the connection between the straight shaft 11 and the planetary gear 13.

[0069] Preferably, as shown in FIG1 , the notch 111 may extend from the connection between the straight shaft 11 and the planetary gear 13 toward the side where the axis of the side gear 14 is located, and the notch 111 extends toward the side where the axis of the side gear 14 is located to an end beyond the planetary gear 13 that is close to the axis of the side gear 14. In this way, the lubricating fluid can be effectively directed to the side gear 14, further improving the lubrication effect.

[0070] FIG3 shows an example in which the number of cutouts 111 and oil outlets 124 corresponds one to one. The cutouts 111 form guide grooves extending axially along the straight shaft 11. However, the present invention is not limited thereto. As long as all oil outlets can be located within the cutout, multiple oil outlets may be provided within a single cutout. (Not shown in the figure) For example, the cutout may be an annular groove extending circumferentially along the straight shaft.

[0071] Preferably, in the cross section perpendicular to the axial direction of the straight shaft 11, the cross-sectional area of ​​the straight shaft 11 is 10 to 20 times the area of ​​the pattern formed by the connecting portion 121. In this way, not only the bending strength of the straight shaft 11 can be guaranteed, but also the flow rate of the lubricating liquid can be guaranteed.

[0072] In an embodiment, as shown in Figures 1, 4 and 6, the above-mentioned reducer may further include a shift execution assembly, a synchronizer 34, an input shaft 4, a first gear 5 and a second gear 6. The first gear 5, the synchronizer 34 and the second gear 6 are all sleeved on the input shaft 4, and the three are arranged in sequence along the axial direction of the input shaft 4. The shift execution assembly is in transmission connection with the synchronizer 34 to control the synchronizer 34 to dock with the first gear 5 or the second gear 6. In this way, the synchronizer 34 is arranged on the input shaft 4, which can reduce the inertia during synchronization, increase the service life of the synchronizer 34, facilitate the arrangement of the transmission structure of the reducer, and effectively reduce the height of the reducer. In addition, the synchronizer 34 is directly arranged between the first gear 5 and the second gear 6, which can effectively shorten the size of the reducer in the axial direction of the input shaft 4, making the structure of the reducer compact.

[0073] Preferably, as shown in FIG. 1 , both ends of the input shaft 4 may be disposed on the front housing 21 and the rear housing 22 via bearings, respectively, which not only ensures the rotatability of the input shaft 4 but also further ensures the compactness between the input shaft 4 and the housing 2 .

[0074] Preferably, as shown in Figures 1 and 6, the above-mentioned shift execution assembly may include a shift driving part 31 and a fork part 33 that are transmission-connected to each other, the fork part 33 is arranged parallel to the input shaft 4, and the fork part 33 is transmission-connected to the synchronizer 34 to drive the synchronizer 34 to move along the input shaft 4 to realize the switching of the synchronizer 34 between the first gear 5 and the second gear 6.

[0075] Optionally, both the first gear gear 5 and the second gear gear 6 are rotatably sleeved on the outside of the input shaft 4 (i.e., both the first gear gear 5 and the second gear gear 6 can freely rotate relative to the input shaft 4 in the circumferential direction of the input shaft 4). For example, a spline extending along the axial direction of the input shaft 4 can be provided between the synchronizer 34 and the input shaft 4, so that the synchronizer 34 and the input shaft 4 can be slidably connected in the axial direction of the input shaft 4, and the synchronizer 34 and the input shaft 4 can be relatively fixed in the circumferential direction of the input shaft 4. In this way, when first gear is engaged, the input shaft 4 drives the synchronizer 34 to rotate, and the shift fork portion 33 shifts the synchronizer 34 to slide along the input shaft 4 and engage with the first gear gear 5. The first gear gear 5 and the synchronizer 34 are fixedly engaged. The first gear gear 5 rotates under the drive of the synchronizer 34, causing the first gear gear 5 to rotate the first gear 71 of the intermediate shaft 70 described below. In turn, the intermediate gear 73 drives the transmission ring gear 152 to rotate, thereby transmitting power to the differential assembly. Similarly, the operation process and principle of shifting into second gear are similar to those of shifting into first gear and will not be described in detail.

[0076] Preferably, as shown in Figure 1 , the fork portion 33 can be a ball screw fork, which achieves axial motion and integrated fork functionality, offering high integration, rapid response, precise control, compact size, and high axial load capacity. Furthermore, the ball screw can be flexibly designed with axial travel according to actual needs to accommodate various layouts. Optionally, as shown in Figure 1 , the ends of the ball screw fork are respectively connected to the front housing 21 and rear housing 22 to further enhance the integration of the reducer.

[0077] It should be noted that the above-mentioned ball screw fork is an existing structure in the field and will not be described in detail here.

[0078] Preferably, as shown in FIG. 1 , the ball screw fork may be provided with a transmission tooth 331 , and the shift driving portion 31 may be in transmission connection with the transmission tooth 331 .

[0079] Preferably, as shown in Figures 1 and 6, the shift execution assembly may further include a driving gear 321 and an idler gear 322. The driving gear 321 is coaxially arranged with the shift drive unit 31, and the shift drive unit 31 is engaged with the above-mentioned transmission tooth 331 via the idler gear 322. In this way, on the one hand, the power is transmitted between the ball screw fork and the shift drive unit 31 through two stages of gears, which can effectively amplify the torque of the shift drive unit 31; on the other hand, it can effectively reduce the size of the shift execution assembly, further compress the space of the reducer, and improve the structural compactness of the reducer; on the third hand, the reducer structure can be flexibly designed by adjusting the idler gear 322 and the center distance, so that the structure of the reducer can adapt to different structural space sizes and has layout flexibility.

[0080] Optionally, the shift driving unit 31 may be a rotary motor, and the rotary motor may be embedded in the front housing 21 to further improve the compactness of the reducer.

[0081] Preferably, as shown in Figures 1, 4 and 6, the above-mentioned reducer may further include an intermediate shaft assembly 7, which is arranged between the input shaft 4 and the differential assembly. The synchronizer 34 is connected to the transmission housing 15 via the intermediate shaft assembly 7. In this way, the shaft system of the reducer is subjected to more balanced force, which is beneficial to improving the life of the reducer.

[0082] Optionally, as shown in FIG6 , the intermediate shaft assembly 7 may include an intermediate gear 73 and an intermediate shaft 70 , wherein the intermediate gear 73 is sleeved on the intermediate shaft 70 , and the intermediate shaft assembly 7 is in transmission connection with the transmission ring gear 152 via the intermediate gear 73 .

[0083] Optionally, as shown in FIG6 , the intermediate shaft assembly 7 may further include a first gear 71 and a second gear 72 , both of which are sleeved on the intermediate shaft 70 and respectively disposed on either side of the intermediate gear 73 . The first gear 5 is meshed with the first gear 71 . When the synchronizer 34 engages with the first gear 5 , the first gear 5 drives the first gear 71 to rotate, thereby driving the intermediate shaft 70 to rotate, which in turn drives the intermediate gear 73 to drive the transmission ring gear 152 to rotate at the first gear speed. Similarly, the second gear 6 is meshed with the second gear 72 . When the synchronizer 34 engages with the second gear 6 , the second gear 6 drives the second gear 72 to rotate, thereby driving the intermediate shaft 70 to rotate, which in turn drives the intermediate gear 73 to drive the transmission ring gear 152 to rotate at the second gear speed.

[0084] The first gear 71 , the second gear 72 and the intermediate gear 73 can all be fixed relative to the input shaft 4 in the circumferential direction of the input shaft 4 to facilitate power transmission of the intermediate shaft assembly 7 .

[0085] An embodiment of the second aspect of the present application further provides a vehicle, comprising the reducer described in any of the above embodiments, and thus having all the beneficial technical effects of the reducer, which will not be repeated here.

[0086] Alternatively, the vehicle may be an electric vehicle.

[0087] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present application, rather than to limit them. Although the present application has been described in detail with reference to the aforementioned embodiments, those skilled in the art should understand that they can still modify the technical solutions described in the aforementioned embodiments, or make equivalent replacements for some or all of the technical features therein. These modifications or replacements do not deviate the essence of the corresponding technical solutions from the scope of the technical solutions of the embodiments of the present application. Industrial Applicability

[0088] By providing a lubricating fluid flow channel on the straight shaft, an oil inlet on the housing, and an oil outlet at the connection between the planetary gears and the straight shaft, and connecting the lubricating fluid flow channel to the oil inlet and the oil outlet respectively, the lubricating fluid can be sequentially introduced into the differential assembly through the oil inlet on the housing via the lubricating fluid flow channel and the oil inlet to lubricate the planetary gears of the differential assembly, effectively improving the lubrication effect of the differential assembly, thereby increasing the service life of the differential assembly and effectively preventing the planetary gears of the differential assembly from even sintering. According to calculations, the reducer provided by this application can achieve a CLTC (China Light-duty Vehicle Test Cycle) comprehensive efficiency of 98% through the above-mentioned lubrication means.

Claims

1. A reducer, characterized in that: The differential assembly comprises a differential assembly and a housing, wherein the differential assembly comprises a planetary gear, a straight shaft and a half-shaft gear, wherein the planetary gear is sleeved on the outer side of the straight shaft, and the half-shaft gear is arranged on one side of the straight shaft and meshes with the planetary gear; A lubricating fluid flow channel is provided in the straight shaft, and an oil outlet communicating with the lubricating fluid flow channel is provided at the connection between the planetary gear and the straight shaft; The housing is provided with an oil circuit inlet, and the lubricating fluid flow channel is communicated with the oil circuit inlet.

2. The reducer according to claim 1, characterized in that: The differential assembly also includes a transmission housing portion, the straight shaft is fixedly arranged in the transmission housing portion, a portion of the transmission housing portion is embedded in the housing, an annular flow channel is arranged on the outer side of the portion of the transmission housing portion embedded in the housing, the annular flow channel is coaxially arranged with the half-shaft gear, and the lubricating fluid flow channel and the oil circuit inlet are both connected via the annular flow channel.

3. The reducer according to claim 2, characterized in that: The differential assembly further includes at least two sealing rings, which are arranged between the transmission housing portion and the housing, and are arranged on both sides of the annular flow channel in the axial direction of the side gear.

4. The reducer according to claim 2, characterized in that: The straight shaft includes a positioning pin hole and an oil inlet hole, the positioning pin hole and the oil inlet hole are respectively arranged at two ends of the straight shaft in the axial direction, and the positioning pin hole and the oil inlet hole are symmetrically arranged about the axis of the half-shaft gear; The straight shaft is pin-connected with the transmission housing via the positioning pin hole, and the straight shaft is communicated with the annular flow channel via the oil inlet hole.

5. The reducer according to claim 2, characterized in that: The lubricating fluid flow channel includes a connecting portion and an outflow portion which are connected to each other, the connecting portion extends along the axial direction of the straight shaft, the outflow portion extends along the radial direction of the straight shaft, and the opening formed by the outflow portion on the surface of the straight shaft is the oil circuit outlet.

6. The reducer according to claim 2, characterized in that: A notch is provided on the side surface of the straight shaft, and the notch is provided corresponding to the oil passage outlet, so that each of the oil passage outlets is provided in the notch.

7. The reducer according to claim 5, characterized in that: In any cross section perpendicular to the axial direction of the straight axis, the cross-sectional area of ​​the straight axis is 10 to 20 times the area of ​​the pattern formed by the connecting portion.

8. The reducer according to claim 5, characterized in that: The differential assembly includes two planetary gears, which are symmetrically arranged about the axis of the side gears, and the outflow portion is arranged corresponding to the planetary gears.

9. The reducer according to any one of claims 2 to 8, characterized in that: It also includes a shift execution assembly, a synchronizer, an input shaft, a first gear gear and a second gear gear, wherein the first gear gear, the synchronizer and the second gear gear are all sleeved on the input shaft and are sequentially arranged along the axis direction of the input shaft; The shift execution assembly is drivingly connected to the synchronizer to control the synchronizer to engage with the first gear or the second gear.

10. The reducer according to claim 9, characterized in that: The shift execution assembly includes a shift driving portion and a fork portion which are transmission-connected to each other, the fork portion is arranged parallel to the input shaft, and the fork portion is transmission-connected to the synchronizer to drive the synchronizer to move along the input shaft.

11. The reducer according to claim 10, characterized in that: The shift execution assembly further includes a driving gear and an idler gear, wherein the driving gear is coaxially arranged with the shift driving portion, and the shift fork portion is provided with a transmission tooth capable of meshing with the idler gear.

12. The reducer according to claim 10, characterized in that: The fork portion is a ball screw fork.

13. The reducer according to claim 9, characterized in that: It also includes an intermediate shaft assembly, which is arranged between the input shaft and the differential assembly. The first gear or the second gear is transmission-connected to the transmission housing via the intermediate shaft assembly.

14. The reducer according to claim 13, characterized in that: The transmission housing portion comprises a housing body and a transmission ring gear, wherein the transmission ring gear is arranged outside the housing body and is coaxially arranged with the half-shaft gear, and the transmission housing portion is transmission-connected to the intermediate shaft assembly via the transmission ring gear.

15. A vehicle, characterized in that: A reducer comprising the reducer according to any one of claims 1 to 14.

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