Intermediate shaft assembly, transmission and vehicle
By employing an interference fit design with interlocking key teeth and keyways between the intermediate shaft and the driven large gear, the slippage problem between the intermediate shaft and the gear is solved, thereby improving the stability and service life of the transmission.
Patent Information
- Authority / Receiving Office
- CN · China
- Patent Type
- Utility models(China)
- Current Assignee / Owner
- Filing Date
- 2025-05-16
- Publication Date
- 2026-03-03
AI Technical Summary
In the prior art, the interference fit between the intermediate shaft and the gear can easily lead to metal fatigue and relative slippage, affecting the stability and service life of the transmission.
The design employs an intermediate driven shaft and a driven large gear. Through the interference fit of the interlocking key teeth and interlocking keyways, combined with the matching connection between the sleeve and the connecting shaft section, the interference amount is reduced and the risk of slippage is lowered.
This effectively reduces the risk of relative slippage between the intermediate driven shaft and the driven large gear, improving the stability and service life of the transmission.
Smart Images
Figure CN223964786U_ABST
Abstract
Description
Technical Field
[0001] This application relates to the field of transmission technology, and in particular to an intermediate shaft assembly, a transmission, and a vehicle. Background Technology
[0002] As an important means of transportation, automobiles require different driving skills in various road conditions. The transmission coordinates the speed of the engine and wheels by changing the gear ratio. A transmission typically consists of an input end and an output end, with the input end indirectly connected to the output end via an intermediate shaft, thus enabling different gear ratios at the input and output ends.
[0003] The intermediate shaft includes a shaft body and gears of different sizes press-fitted onto the shaft body. Existing technology usually press-fits the gears onto the shaft body through an interference fit of a smooth shaft or spline. When this method results in a large interference fit between the shaft body and the gear, metal fatigue is likely to occur, which can easily lead to relative slippage. Utility Model Content
[0004] The main objective of this application is to provide an intermediate shaft assembly, a transmission, and a vehicle, which aims to solve the aforementioned technical problems existing in the prior art.
[0005] To address the aforementioned technical problems, this application provides an intermediate shaft assembly, which includes an intermediate driven shaft and a driven large gear. The intermediate driven shaft includes a connecting shaft segment and multiple mating key teeth. The connecting shaft segment has a first mating surface on its outer side in the radial direction, and the multiple mating key teeth are spaced apart on the first mating surface in the circumferential direction of the connecting shaft segment. The driven large gear includes a sleeve and a mating sleeve, which are sequentially sleeved on the connecting shaft segment in the axial direction. The inner sidewall of the sleeve serves as a second mating surface, which is mated and connected to a portion of the first mating surface. The mating sleeve is connected to the end of the sleeve near the mating key teeth, and the end face of the mating sleeve away from the sleeve has multiple mating keyways spaced apart in the circumferential direction, with each mating key tooth mating into one mating keyway.
[0006] In some embodiments, the mating keyway penetrates the inner wall of the mating sleeve in the radial direction to form a keyway protrusion. The two sides of the keyway protrusion are provided with arc-shaped chamfers near the end of the connecting shaft section. Each mating key tooth includes an arc-shaped matching surface, and each arc-shaped matching surface matches the corresponding arc-shaped chamfer.
[0007] In some embodiments, the extension lines of the sidewalls of each mating key tooth and each mating keyway converge at the axis of the intermediate driven shaft.
[0008] In some embodiments, the mating keyway extends radially through the outer wall of the mating sleeve.
[0009] In some embodiments, the mating key teeth and the mating keyway are interference-fitted.
[0010] In some embodiments, the ratio of the axial dimension of the mating keyway to the total axial dimension of the sleeve and the mating sleeve is 0.1 to 0.3.
[0011] In some embodiments, the ratio of the radial dimension of the mating key relative to the first mating surface to the dimension of the first mating surface of the connecting shaft segment is 0.1 to 0.3.
[0012] In some embodiments, the intermediate driven shaft includes a small spline shaft segment, which includes a body shaft segment and a small external spline segment. The body shaft segment is connected to the end of the connecting shaft segment away from the sleeve, and the small external spline segment is sleeved on the body shaft segment. The end of each mating key tooth away from the sleeve is connected to the body shaft segment.
[0013] To address the aforementioned technical problems, this application provides a transmission that includes the aforementioned intermediate shaft assembly.
[0014] To solve the above-mentioned technical problems, this application provides a vehicle that includes the aforementioned transmission.
[0015] Compared with the prior art, the intermediate shaft assembly provided in this application includes an intermediate driven shaft and a driven large gear. The intermediate driven shaft includes a connecting shaft section and a plurality of mating key teeth. The connecting shaft section has a first mating surface on its outer side in the radial direction. The plurality of mating key teeth are spaced apart on the first mating surface in the circumferential direction of the connecting shaft section. The driven large gear includes a sleeve and a mating sleeve. The sleeve and the mating sleeve are sequentially sleeved on the connecting shaft section in the axial direction. The inner sidewall of the sleeve serves as a second mating surface. The second mating surface is mated and connected with a portion of the first mating surface. The mating sleeve is connected to the end of the sleeve near the mating key teeth. The end face of the mating sleeve away from the sleeve has a plurality of mating keyways spaced apart in the circumferential direction. Each mating key tooth is respectively fitted into a mating keyway. Through the above implementation method, the driven large gear is rotatably connected to the intermediate driven shaft by matching the sleeve and the connecting shaft section, and by matching the keyway and key teeth provided on one end face of the sleeve. This reduces the interference fit between the intermediate driven shaft and the driven large gear, and also reduces the risk of relative slippage between the two. Attached Figure Description
[0016] To more clearly illustrate the technical solutions in the embodiments of this application or the prior art, the drawings used in the embodiments will be briefly introduced below. Obviously, the drawings described below are only some embodiments of this application. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.
[0017] Figure 1 This is a schematic diagram of the structure of an embodiment of the intermediate shaft assembly provided in this application;
[0018] Figure 2 yes Figure 1 A schematic diagram of the disassembled structure of the intermediate shaft assembly shown;
[0019] Figure 3 yes Figure 2 A schematic diagram of one embodiment of the driven large gear is shown;
[0020] Figure 4 yes Figure 1 The cross-sectional view of the intermediate shaft assembly shown along the AA direction;
[0021] Figure 5 yes Figure 4 An enlarged structural schematic diagram of the section shown within the dashed frame;
[0022] Figure 6 yes Figure 3 The cross-sectional view of the driven large gear along the BB direction shown;
[0023] Figure 7 yes Figure 2 A schematic diagram of one embodiment of the intermediate driven shaft is shown;
[0024] Figure 8 yes Figure 7 The cross-sectional view of the intermediate driven shaft along the CC direction is shown.
[0025] Reference numerals: Intermediate shaft assembly 10; Intermediate driven shaft 100; Connecting shaft segment 110; First mating surface 111; Engaging key 112; Arc-shaped mating surface 1121; Small spline shaft segment 120; Body shaft segment 121; Small external spline 122; Driven large gear 200; Sleeve bushing 210; Second mating surface 211; Engaging bushing 220; Engaging keyway 221; Keyway protrusion 222; Arc-shaped chamfer 2221. Detailed Implementation
[0026] The embodiments of the technical solution of this application will now be described in detail with reference to the accompanying drawings. These embodiments are only used to more clearly illustrate the technical solution of this application and are therefore merely examples, and should not be used to limit the scope of protection of this application.
[0027] Unless otherwise defined, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this application pertains; the terminology used herein is for the purpose of describing particular embodiments only and is not intended to limit the application; the terms “comprising” and “having”, and any variations thereof, in the specification, claims, and foregoing description of the drawings are intended to cover non-exclusive inclusion.
[0028] In the description of the embodiments of this application, technical terms such as "first" and "second" are used only to distinguish different objects and should not be construed as indicating or implying relative importance or implicitly indicating the number, specific order, or primary and secondary relationship of the indicated technical features.
[0029] In this document, the term "embodiment" means that a particular feature, structure, or characteristic described in connection with an embodiment may be included in at least one embodiment of this application. The appearance of this phrase in various places throughout the specification does not necessarily refer to the same embodiment, nor is it a separate or alternative embodiment mutually exclusive with other embodiments. It will be explicitly and implicitly understood by those skilled in the art that the embodiments described herein can be combined with other embodiments.
[0030] In the description of the embodiments in this application, the term "and / or" is merely a description of the relationship between related objects, indicating that three relationships can exist. For example, A and / or B can represent: A existing alone, A and B existing simultaneously, and B existing alone. Additionally, the character " / " in this document generally indicates that the preceding and following related objects have an "or" relationship.
[0031] In the description of the embodiments of this application, the term "multiple" refers to two or more (including two), similarly, "multiple sets" refers to two or more (including two sets), and "multiple pieces" refers to two or more (including two pieces).
[0032] In the description of the embodiments of this application, the technical terms "center," "longitudinal," "lateral," "length," "width," "thickness," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," "clockwise," "counterclockwise," "axial," "radial," and "circumferential" indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are only for the convenience of describing the embodiments of this application and simplifying the description, and are not intended to indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on the embodiments of this application.
[0033] In the description of the embodiments of this application, unless otherwise expressly specified and limited, technical terms such as "installation," "connection," "joining," and "fixing" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication of two components or the interaction between two components. For those skilled in the art, the specific meaning of the above terms in the embodiments of this application can be understood according to the specific circumstances.
[0034] As a vital means of transportation, automobiles present varying driving needs under different road conditions. The transmission coordinates the speed of the engine and wheels by changing the gear ratio. A transmission typically includes an input and an output, with the input indirectly connected to the output via an intermediate shaft, thus enabling different gear ratios at the input and output. The intermediate shaft comprises a shaft body and gears of varying sizes press-fitted onto it. Current technology typically uses an interference fit between the shaft and gears via a smooth shaft or splines. However, this method results in a large interference fit between the shaft and gears, making relative slippage prone to occur.
[0035] To address the related technical problems, this application provides a vehicle including a transmission as described below. The vehicle may also include a motor and an axle. The motor is connected to the axle via the transmission, and the axle is connected to the wheel, thus the motor can be indirectly connected to the wheel. By changing the wheel speed through the transmission, the motor speed and the actual driving speed of the wheel are coordinated to achieve optimal motor performance. Of course, when the vehicle is a gasoline-powered vehicle, the motor can also be an engine, connected to the axle via the transmission.
[0036] To address the related technical problems, this application provides a transmission, which includes an intermediate shaft assembly, an input shaft, and an output shaft. The intermediate shaft assembly is connected to the input shaft and output shaft of the transmission, respectively. The input shaft of the transmission is connected to the output end of a motor, and the output shaft of the transmission is connected to a wheel axle. The intermediate shaft assembly, as well as the input shaft and output shaft of the transmission, may each include multiple gears with different radial dimensions. By connecting the different gears of the intermediate shaft assembly to different gears on the input shaft and output shaft of the transmission, the speed difference between the engine and the wheels can be changed to achieve different gear shifts, thereby maximizing the performance of the motor.
[0037] To address the related technical problems, this application provides an intermediate shaft assembly, see [link to relevant documentation]. Figures 1 to 3 , Figure 1 This is a schematic diagram of an embodiment of the intermediate shaft assembly provided in this application. Figure 2 yes Figure 1 The diagram shows the disassembled structure of the intermediate shaft assembly. Figure 3 yes Figure 2A schematic diagram of one embodiment of the driven large gear is shown.
[0038] The intermediate shaft assembly 10 includes an intermediate driven shaft 100 and a driven large gear 200. The intermediate driven shaft 100 includes a connecting shaft section 110 and a plurality of mating key teeth 112. The connecting shaft section 110 has a first mating surface 111 on its outer side in the radial direction, and the plurality of mating key teeth 112 are spaced apart on the first mating surface 111 in the circumferential direction of the connecting shaft section 110. The driven large gear 200 includes a sleeve 210 and a mating sleeve 220. 0 is sequentially sleeved onto the connecting shaft section 110 in the axial direction. The inner sidewall of the sleeve 210 serves as the second mating surface 211. The second mating surface 211 is matched and connected with part of the first mating surface 111. The fitting sleeve 220 is connected to the end of the sleeve 210 near the fitting key 112. The end face of the fitting sleeve 220 away from the sleeve 210 is provided with a plurality of fitting keyways 221 at intervals in the circumferential direction. Each fitting key 112 is fitted into a fitting keyway 221.
[0039] The intermediate driven shaft 100 includes a connecting shaft section 110 and a plurality of mating key teeth 112. The connecting shaft section 110 may be a solid round shaft. The connecting shaft section 110 is only a small segment of the intermediate driven shaft 100. The outer wall surface of the connecting shaft section 110 is a first mating surface 111. The plurality of mating key teeth 112 are spaced apart on the connecting shaft section 110 along the circumferential direction. Specifically, the mating key teeth 112 may be located near the end position of the connecting shaft section 110, so that when the mating key teeth 112 are connected with other structures, the axial dimension of the connecting shaft section 110 can be reduced, the size of the gearbox can be reduced, and the weight can be reduced.
[0040] The driven large gear 200 is sleeved on the connecting shaft section 110. Specifically, the driven large gear 200 includes a sleeve 210 and a fitting sleeve 220, which are arranged adjacent to each other. The sleeve 210 is connected to the end of the fitting sleeve 220 away from the fitting key 112. Both the sleeve 210 and the fitting sleeve 220 are sleeved on the connecting shaft section 110. The inner wall surface of the sleeve 210 is used as the second mating surface 211, which is connected to a portion of the first mating surface 111. The sleeve 210 is rotatably connected to the connecting shaft section 110 by an interference fit, so that the connecting shaft section 110 can drive the sleeve 210 to rotate. The outer side of the sleeve 210 may be provided with a large external spline, which is used for drive connection with the input shaft of the transmission or the output shaft of the transmission. The fitting sleeve 220 has multiple fitting keyways 221 on its end face away from the sleeve 210. The number of fitting keyways 221 corresponds to the number of fitting key teeth 112. The multiple fitting keyways 221 are spaced apart in the circumferential direction on the end face of the fitting sleeve 220 away from the sleeve 210. The fitting keyways 221 penetrate the inner wall of the fitting sleeve 220 in the radial direction toward the connecting shaft segment 110, so that the fitting key teeth 112 can be embedded in the fitting keyways 221 in the axial direction. A keyway protrusion 222 is formed between two fitting keyways 221. The keyway protrusion 222 protrudes from the end face of the fitting sleeve 220 toward the fitting key teeth 112. The inner wall of the keyway protrusion 222 is a fourth mating surface, which is correspondingly connected to the first mating surface 111 between the fitting key teeth 112. The fitting sleeve 220 is rotatably connected to the connecting shaft segment 110 through two methods: the engagement of the fitting key teeth 112 and the fitting keyway 221; and the engagement of the first mating surface 111 and the fourth mating surface. This allows the driven large gear 200 to be rotatably connected to the connecting shaft segment 110 via the sleeve 210 and the fitting sleeve 220.
[0041] Compared to machining the internal spline on the second mating surface 211 of the sleeve 210, machining the fitting groove on the end face of the fitting sleeve 220 is a simpler, more practical, and more manufacturable method. Furthermore, the sidewalls and bottom wall of the fitting groove are perpendicular, resulting in a simpler structure that is easier to machine.
[0042] The fitting bushing 220 and the sleeve bushing 210 can be integrally formed to ensure a high connection strength between them. The intermediate shaft assembly 10 may include a plurality of driven large gears 200, each of which may have the same or different radial dimensions. The plurality of driven large gears 200 are spaced apart in the axial direction on the intermediate driven shaft 100 to achieve multiple different gear adjustments.
[0043] Through the above embodiments, the driven large gear 200 is rotatably connected to the intermediate driven shaft 100 by matching the sleeve 210 with the connecting shaft section 110, and by matching the keyway 221 provided on one end face of the sleeve 220 with the key teeth 112. This reduces the interference fit between the intermediate driven shaft 100 and the driven large gear 200, and also reduces the risk of relative slippage between the two.
[0044] See Figure 4 and Figure 5 , Figure 4 yes Figure 1 The cross-sectional view of the intermediate shaft assembly shown along the AA direction. Figure 5 yes Figure 4 An enlarged structural schematic diagram of the section shown within the dashed box.
[0045] In some embodiments, the keyway 221 penetrates the inner wall of the fitting sleeve 220 in the radial direction to form a keyway protrusion 222. The keyway protrusion 222 has arc-shaped chamfers 2221 on both sides near the end of the connecting shaft segment 110. Each fitting key tooth 112 includes an arc-shaped mating surface 1121, and each arc-shaped mating surface 1121 matches the corresponding arc-shaped chamfer 2221. Multiple fitting keyways 221 are spaced apart on the end face of one end of the fitting sleeve 220 in the circumferential direction, and each fitting keyway 221 penetrates the inner wall of the fitting sleeve 220 in the radial direction, thereby forming a keyway protrusion 222 between two adjacent fitting keyways 221. Conversely, the fitting sleeve 220 also has multiple keyway protrusions 222 spaced apart in the circumferential direction, and the fitting keyway 221 is formed by the spaced-apart keyway protrusions 222. The keyway protrusion 222 has arc-shaped chamfers 2221 on both sides near the end of the connecting shaft section 110. This can be understood as the keyway protrusion 222 having an arc-shaped surface at the connection point between the fourth mating surface near the connecting shaft section 110 in the radial direction and the two side surfaces in the circumferential direction, so as to transition adjacent surfaces with an arc. The mating key tooth 112 has arc-shaped mating surfaces 1121 on both sides in the circumferential direction. Specifically, the arc-shaped mating surfaces 1121 are located at both ends of the connection point between the mating key tooth 112 and the first mating surface 111 in the circumferential direction. When the mating key tooth 112 and the mating keyway 221 are mated, the arc-shaped mating surfaces 1121 and the arc-shaped chamfers 2221 are matched. When the connecting shaft segment 110 is rotatably connected by the mating connection of the mating key teeth 112 and the mating keyway 221, the mating key teeth 112 and the mating keyway 221 will be subjected to shear force in the circumferential direction. An arc-shaped chamfer 2221 is provided at the end of the mating keyway 221 to connect with the arc-shaped mating surface 1121 of the mating key teeth 112. The stress distributed at the corresponding positions by the arc-shaped mating surface 1121 and the arc-shaped chamfer 2221 can reduce the risk of damage to the mating key teeth 112 and the mating keyway 221. This can also reduce the risk of damage to other components of the intermediate shaft assembly 10 due to debris falling from the damaged mating key teeth 112 or the mating keyway 221.
[0046] In some embodiments, the extension lines of the sidewalls of each mating key tooth 112 and each mating keyway 221 converge at the axis of the intermediate driven shaft 100. The mating keyways 221 are spaced apart in the circumferential direction at the end face of the mating sleeve 220 away from the sleeve 210, and the extension lines of the two sidewalls of the mating keyways 221 in the circumferential direction converge at the axis of the intermediate driven shaft 100. The mating key teeth 112 are mated and connected to the mating keyways 221, and the extension lines of the two sidewalls of the mating key teeth 112 in the circumferential direction also converge at the axis of the intermediate driven shaft 100. This ensures that the coplanarity of the side surfaces of the mating key teeth 112 and the mating keyway 221 is perpendicular to the tangent in the circumferential direction, thereby making the stress on the side surfaces of the mating key teeth 112 and the corresponding side surfaces of the mating keyway 221 uniform during mating. This further reduces the risk of damage to the mating keyway 221 and the mating key teeth 112 due to uneven stress.
[0047] In some embodiments, the keyway 221 penetrates the outer wall of the fitting sleeve 220 in the radial direction. In addition to penetrating the inner wall of the fitting sleeve 220 in the radial direction, the keyway 221 also penetrates the outer wall of the fitting sleeve 220, forming a through groove at the end of the fitting sleeve 220 that penetrates the opposing inner and outer walls of the fitting sleeve 220. This simplifies the machining of the fitting groove in the driven gear 200 and improves manufacturability.
[0048] In some embodiments, the key teeth 112 are interference-fitted with the keyway 221. With the second mating surface 211 and part of the first mating surface 111 interference-fitted, the key teeth 112 are also interference-fitted with the keyway 221, thereby improving the matching degree between the key teeth 112 and the keyway 221 and reducing the risk of relative displacement of the key teeth 112 within the keyway 221. Furthermore, the keyway 221 penetrates the opposing inner and outer walls of the mating sleeve 220, which reduces the volume of the keyway protrusion 222. During the press-fitting process of the key teeth 112 into the keyway 221, the deformation of the keyway protrusion 222 is reduced, lowering the risk of uneven centrifugal force in different parts of the intermediate shaft assembly 10 during rotation due to uneven deformation, and improving the rotational stability of the intermediate shaft assembly 10.
[0049] See Figure 6 , Figure 6 yes Figure 3 The diagram shows a cross-sectional view of the driven large gear along the BB direction.
[0050] In some embodiments, the ratio of the axial dimension of the keyway 221 to the total axial dimension of the sleeve 210 and the fitting sleeve 220 is 0.1 to 0.3. The axial dimension of the keyway 221 can be understood as the depth of the keyway 221, and the total axial dimension of the sleeve 210 and the fitting sleeve 220 can be understood as the total length of the sleeve 210 and the fitting sleeve 220. Figure 6 As shown in the figure, L1 represents the axial dimension of the keyway 221, and L2 represents the total axial dimension of the sleeve 210 and the fitting sleeve 220. The ratio of the axial dimension of the keyway 221 to the total axial dimension of the sleeve 210 and the fitting sleeve 220 is in the range of 0.1 to 0.3, that is, the depth of the keyway 221 is between 0.1 and 0.3 times the total length of the sleeve 210 and the fitting sleeve 220. This allows the keyway 221 to effectively bear the torque of the intermediate shaft assembly 10 and reduces the risk of deformation or breakage of the keyway 221 due to excessive depth.
[0051] The ratio of the axial dimension of the keyway 221 to the total axial dimension of the sleeve 210 and the fitting sleeve 220 can be 0.1, 0.15, 0.2, 0.25 or 0.3, or a range of any two of the above values, such as 0.1 to 0.2 or 0.2 to 0.3.
[0052] See Figure 7 and Figure 8 , Figure 7 yes Figure 2 The diagram shows a structural schematic of one embodiment of the intermediate driven shaft. Figure 8 yes Figure 7 The cross-sectional view of the intermediate driven shaft along the CC direction is shown.
[0053] In some embodiments, the ratio of the radial dimension of the mating key 112 relative to the first mating surface 111 to the dimension of the first mating surface 111 of the connecting shaft segment 110 is 0.1 to 0.3. The radial dimension of the mating key 112 relative to the first mating surface 111 can be understood as the distance from the mating key 112 to the axis in the radial direction minus the perpendicular distance from the first mating surface 111 to the axis; in other words, it is the height of the mating key 112 located on the first mating surface 111. The radial dimension of the first mating surface 111 of the connecting shaft segment 110 can be understood as the perpendicular distance from the first mating surface 111 to the axis; in other words, it is the radial dimension of the outer wall of the connecting shaft segment 110. Figure 7As shown in the figure, L3 represents the radial dimension of the mating key 112 relative to the first mating surface 111, and L4 represents the dimension of the first mating surface 111 of the connecting shaft segment 110. The ratio of the radial dimension of the mating key 112 relative to the first mating surface 111 to the dimension of the first mating surface 111 of the connecting shaft segment 110 is in the range of 0.1 to 0.3. That is to say, the height of the mating key 112 is between 0.1 and 0.3 times the radial dimension of the outer wall of the connecting shaft segment 110. This enables the mating key 112 to effectively bear the torque of the intermediate shaft assembly 10 and reduces the risk of deformation or breakage of the mating key 112 due to excessive height.
[0054] The ratio of the radial dimension of the mating key 112 relative to the first mating surface 111 to the dimension of the first mating surface 111 of the connecting shaft segment 110 can be 0.1, 0.15, 0.2, 0.25 or 0.3, or a range of any two of the above values, such as 0.1 to 0.2 or 0.2 to 0.3.
[0055] In some embodiments, the intermediate driven shaft 100 includes a small spline shaft segment 120, which includes a main shaft segment 121 and a small external spline segment 122. The main shaft segment 121 is connected to the end of the connecting shaft segment 110 away from the sleeve 210, and the small external spline segment 122 is sleeved on the main shaft segment 121. Each engaging key tooth 112 is connected to the end of the connecting shaft segment 110 away from the sleeve 210. The intermediate driven shaft 100 includes the small spline shaft segment 120, which is connected to the end of the connecting shaft segment 110 away from the driven large gear 200. The small spline shaft segment 120 can be used for drive connection with the input shaft or output shaft of the transmission to achieve different gears. The radial dimension of the small spline shaft segment 120 is larger than that of the connecting shaft segment 110. The end of the mating key 112 away from the mating sleeve 220 is connected to one end of the small spline shaft segment 120, thereby increasing the fixed connection area between the mating key 112 and the intermediate shaft assembly 10, improving the connection strength of the mating key 112, increasing the load torque capacity of the mating key 112, and reducing the risk of breakage of the mating key 112. The small spline shaft segment 120 can be integrally set with the connecting shaft segment 110. The structure of the small spline shaft segment 120 is simple, and the intermediate shaft assembly 10 with the small spline shaft segment 120 can be directly machined by lathe to improve the connection strength between the small spline shaft segment 120 and the connecting shaft segment 110. The purpose of describing the two separately is to facilitate better understanding. Of course, the small spline shaft segment 120 and the connecting shaft segment 110 can also be connected together by welding. Specifically, the small spline shaft segment includes a main shaft segment 121 and a small external spline segment 122. The main shaft segment 121 is connected to the end of the connecting shaft segment 110 away from the driven large gear 200. The small external spline segment 122 is connected to the outer side of the main shaft segment 121 in the radial direction. The mating key 112 is connected to the end of the main shaft segment 121 near the driven large gear 200. This increases the fixed connection area between the mating key 112 and the intermediate shaft assembly 10, improves the connection strength of the mating key 112, increases the load torque capacity of the mating key 112, and reduces the risk of breakage of the mating key 112. The radial dimension of the main shaft section 121 can be greater than or equal to the radial dimension of the mating key 112. That is to say, the height of the mating key 112 relative to the first mating surface 111 is less than the height of the main shaft section 121 relative to the first mating surface 111. In other words, the height of the small external spline 122 in the radial direction is greater than the height of the mating key 112. Therefore, when the mating key 112 is connected to the main shaft section 121, the interference of the mating key 112 on the small external spline 122 can be reduced.
[0056] In summary, the driven large gear 200 is rotatably connected to the intermediate driven shaft 100 by matching the sleeve 210 with the connecting shaft section 110, and by matching the keyway 221 provided on one end face of the sleeve 220 with the key teeth 112. This reduces the interference fit between the intermediate driven shaft 100 and the driven large gear 200, and also reduces the risk of relative slippage between the two.
[0057] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of this application, and not to limit them. Although this application has been described in detail with reference to the foregoing embodiments, those skilled in the art should understand that modifications can still be made to the technical solutions described in the foregoing embodiments, or equivalent substitutions can be made to some or all of the technical features therein. These modifications or substitutions do not cause the essence of the corresponding technical solutions to deviate from the scope of the technical solutions of the embodiments of this application, and they should all be covered within the scope of the claims and specification of this application. In particular, as long as there is no structural conflict, the various technical features mentioned in the embodiments can be combined in any way. This application is not limited to the specific embodiments disclosed herein, but includes all technical solutions falling within the scope of the claims.
Claims
1. An intermediate shaft assembly, characterized in that, The intermediate shaft assembly includes: The intermediate driven shaft includes a connecting shaft segment and a plurality of mating key teeth. The connecting shaft segment has a first mating surface on its outer side in the radial direction, and the plurality of mating key teeth are spaced apart on the first mating surface in the circumferential direction of the connecting shaft segment. The driven large gear includes a sleeve and a fitting sleeve. The sleeve and the fitting sleeve are sequentially fitted onto the connecting shaft section in the axial direction. The inner sidewall of the sleeve serves as a second mating surface, which is matched and connected with a portion of the first mating surface. The fitting sleeve is connected to the end of the sleeve near the fitting key. The end face of the fitting sleeve away from the sleeve is provided with a plurality of fitting keyways at intervals in the circumferential direction. Each fitting key is fitted into one fitting keyway.
2. The intermediate shaft assembly according to claim 1, characterized in that, The keyway penetrates the inner wall of the fitting sleeve in the radial direction to form a keyway protrusion. The two sides of the keyway protrusion are provided with arc-shaped chamfers near the end of the connecting shaft section. Each fitting key tooth includes an arc-shaped matching surface, and each arc-shaped matching surface matches the corresponding arc-shaped chamfer.
3. The intermediate shaft assembly according to claim 2, characterized in that, The extension lines of the sidewalls of each of the mating key teeth and each of the mating keyways converge at the axis of the intermediate driven shaft.
4. The intermediate shaft assembly according to claim 3, characterized in that, The fitting keyway extends through the outer wall of the fitting bushing in the radial direction.
5. The intermediate shaft assembly according to claim 1, characterized in that, The interlocking key teeth and the interlocking keyway are interference-fitted.
6. The intermediate shaft assembly according to claim 1, characterized in that, The ratio of the dimension of the fitting keyway in the axial direction to the total dimension of the sleeve and the fitting sleeve in the axial direction is 0.1 to 0.
3.
7. The intermediate shaft assembly according to claim 1, characterized in that, The ratio of the dimension of the mating key tooth relative to the first mating surface in the radial direction to the dimension of the first mating surface of the connecting shaft segment is 0.1 to 0.
3.
8. The intermediate shaft assembly according to claim 1, characterized in that, The intermediate driven shaft includes a small spline shaft section, which includes a main shaft section and a small external spline section. The main shaft section is connected to the end of the connecting shaft section away from the sleeve, and the small external spline section is sleeved on the main shaft section. The end of each of the mating key teeth away from the sleeve is connected to the main shaft section.
9. A transmission, characterized in that, The transmission includes an intermediate shaft assembly as described in any one of claims 1 to 8.
10. A vehicle, characterized in that, The vehicle includes the transmission as described in claim 9.