Auxiliary transmission, main transmission and vehicle

Abstract

The invention relates to an auxiliary transmission, a main transmission and a vehicle, the auxiliary transmission comprises an intermediate shaft, one end of the intermediate shaft is in spline connection with an output shaft, and the outer wall of the other end of the intermediate shaft is sleeved with a second input gear; the planetary gear shaft is arranged on the outer wall of the intermediate shaft in a sleeving mode, one end of the planetary gear shaft is meshed with a planet carrier assembly, and the outer wall of the other end of the planetary gear shaft is sleeved with a first input gear; one end of the synchronizer assembly is in spline connection with the output shaft, the other end of the synchronizer assembly is in spline connection with the planet carrier assembly, and the synchronizer assembly is used for power connection or power disconnection of the planet carrier assembly and the intermediate shaft. The problems that a planetary gear assembly (a planetary gear shaft and a planetary carrier assembly) of a traditional auxiliary transmission is always in a running state, abrasion of a planetary gear is accelerated, the service life is shortened, the transmission efficiency is reduced, and frequent maintenance and replacement of parts are needed when the traditional auxiliary transmission works in a speed reduction output mode or a direct output mode can be solved.

Description

Technical Field

[0001] The present application relates to the field of auxiliary transmissions, and in particular to an auxiliary transmission, a main transmission and a vehicle. Background Art

[0002] Auxiliary transmission is an additional transmission attached to the main transmission. Its function is to increase the number of transmission gears and expand the transmission ratio range. It is mostly used in heavy-duty vehicles. Auxiliary transmission is used for heavy-duty vehicles with large changes in empty and full-load mass, complex operating conditions, especially diesel engine torque changes slowly, poor adaptability, and the need to expand the transmission ratio range and increase the number of gears to meet the power and economy requirements under various operating conditions. In order to avoid making the structure of the transmission too complicated and facilitate serialization, it is often combined with a four-speed or five-speed transmission and a two-, three-, or four-speed auxiliary transmission. The auxiliary transmission can be installed before or after the transmission. The front auxiliary transmission is mostly composed of a pair of gears to form an overdrive gear instead of the constant meshing transmission gear of the transmission. It has a compact structure and is easy to change. The rear auxiliary transmission can be composed of two pairs of gears or planetary gear mechanisms. The transmission ratio is relatively large. The rear position can reduce the size and load of the transmission and is a common type; the front and rear equal placement scheme can obtain more gears.

[0003] In the related art, when the auxiliary transmission is performing deceleration output or direct output, its planetary gear assembly is always in operation. Continuous operation will accelerate the wear of the planetary gears, shorten their service life, and increase the internal friction of the planetary gear assembly, thereby reducing the transmission efficiency. Due to the increased wear, more frequent maintenance and replacement of parts are required, which increases maintenance costs. Summary of the invention

[0004] The present application provides a sub-transmission, a main transmission and a vehicle, which can avoid the problem that the planetary gear assembly (planetary gear shaft and planetary carrier assembly) of the traditional sub-transmission is always in operation regardless of whether it is working in deceleration output or direct output, which will accelerate the wear of the planetary gears, shorten their service life, reduce transmission efficiency, require more frequent maintenance and replacement of parts, and increase maintenance costs.

[0005] In a first aspect, an embodiment of the present application provides a sub-transmission, comprising:

[0006] An intermediate shaft, one end of which is spline-connected to the output shaft, and the other end of which is sleeved with a second input gear on its outer wall;

[0007] A planetary gear shaft, wherein the planetary gear shaft is sleeved on the outer wall of the intermediate shaft, one end of the planetary gear shaft is meshed with a planet carrier assembly, and the outer wall of the other end thereof is sleeved with a first input gear;

[0008] A synchronizer assembly, one end of which is spline-connected to the output shaft, and the other end of which is spline-connected to the planetary carrier assembly, and the synchronizer assembly is used for power connection or power disconnection between the planetary carrier assembly and the intermediate shaft.

[0009] In combination with the first aspect, in one implementation, the synchronizer assembly includes:

[0010] A gear seat, the inner wall of which is spline-connected to the outer wall of the output shaft;

[0011] A cone ring, the cone ring is coaxially arranged with the gear seat, and the inner wall of the cone ring is spline-connected with the outer wall of one end of the planet carrier assembly;

[0012] The sliding sleeve is sleeved on the outer wall of the gear seat and the cone ring and is spline-connected with the gear seat. The sliding sleeve can move radially and is spline-connected with the cone ring.

[0013] In combination with the first aspect, in one embodiment, an elastic telescopic member is embedded and installed in the outer wall of the tooth seat, one end of the elastic telescopic member faces the axis of the tooth seat, and the other end of the elastic telescopic member is arranged in an arc surface;

[0014] An arc groove is provided on the inner side wall of the sliding sleeve, and the other end of the elastic telescopic member moves into the arc groove due to its own elastic force. When the sliding sleeve moves radially and connects with the cone ring spline, the other end of the elastic telescopic member moves out of the arc groove.

[0015] In combination with the first aspect, in one embodiment, an outer wall of the gear seat is provided with a mounting groove;

[0016] The elastic expansion member comprises:

[0017] A support column protrusion, one end of which is arranged in the installation groove, and the other end surface of which is arranged in an arc surface and is adapted to the arc groove;

[0018] A spring is sleeved with the outer wall of the support column protrusion, and two ends of the spring are against the support column protrusion and the installation groove.

[0019] In combination with the first aspect, in one embodiment, the other end side wall of the elastic telescopic member is provided with a protrusion;

[0020] The outer wall of the gear seat is clamped and fixed to the clamping ring, and the end surface of the clamping ring is in contact with the protruding portion, which is used to prevent the elastic telescopic member from deviating along the telescopic direction.

[0021] In combination with the first aspect, in one embodiment, a first notch is formed on the side wall of the gear seat, a protrusion is formed on the side wall of the clamping ring, and the protrusion is located in the first notch;

[0022] A second notch is formed on the inner side wall of the sliding sleeve, and a limiting block is provided on the second notch. When projected in the radial direction, the first notch is located inside the second notch, and the limiting block is located inside the first notch.

[0023] When the sliding sleeve moves radially toward the gear seat, the first notch moves into the second notch until the limiting block abuts against the protruding portion, so as to limit the sliding sleeve from further radial movement.

[0024] In combination with the first aspect, in one implementation, the synchronizer assembly further includes:

[0025] A linear motor, a shift fork being fixed to the translation end of the linear motor;

[0026] The outer wall of the sliding sleeve is provided with a sliding groove, and one end of the shift fork is arranged in the sliding groove;

[0027] The linear motor can drive the shift fork to move linearly, so as to drive the sliding sleeve to move radially.

[0028] In combination with the first aspect, in one embodiment, the planet carrier assembly includes a planet carrier, the planet carrier is rotatably mounted with a plurality of planetary gears along its circumferential direction, the plurality of planetary gears are meshed with one end of the planetary gear shaft, and the outer walls of the plurality of planetary gears are meshed with the same gear ring;

[0029] The auxiliary transmission also includes:

[0030] The rear housing, the synchronizer assembly and the output shaft are assembled in the rear housing. The inner side wall of the rear housing is provided with a first internal spline, and the first internal spline is assembled and fixed with the outer ring spline of the gear ring.

[0031] In a second aspect, an embodiment of the present application provides a main transmission, which includes a sub-transmission as described in some of the above embodiments, and the output end of the main transmission can be switched to engage with the first input gear or the second input gear.

[0032] In a third aspect, an embodiment of the present application provides a vehicle comprising a main transmission as described above.

[0033] The beneficial effects brought by the technical solution provided in the embodiments of the present application include:

[0034] Deceleration output route: when the first input gear is subjected to force (the source of force is the main transmission gear meshing with it), torque begins to be transmitted, and the force is transmitted from the first input gear to the planetary gear shaft, planetary carrier assembly, synchronizer assembly and output shaft in sequence to complete the deceleration output. At this time, the synchronizer assembly is in meshing state, so that the planetary carrier assembly and the output shaft are connected in power; direct output route: when the second input gear is subjected to force, torque begins to be transmitted, and the force is transmitted from the second input gear to the intermediate shaft and output shaft in sequence to complete the direct output. At this time, the synchronizer assembly is in neutral state, so that the planetary carrier assembly and the output shaft are disconnected in power. This avoids the problem that the planetary gear assembly (planetary gear shaft and planetary carrier assembly) of the traditional auxiliary transmission is always in operation regardless of the deceleration output or direct output, which will accelerate the wear of the planetary gears, shorten their service life, reduce transmission efficiency, require more frequent maintenance and replacement of parts, and increase maintenance costs. BRIEF DESCRIPTION OF THE DRAWINGS

[0035] In order to more clearly illustrate the technical solutions in the embodiments of the present application, the drawings required for use in the description of the embodiments will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present application. For ordinary technicians in this field, other drawings can be obtained based on these drawings without creative work.

[0036] Figure 1 is a schematic cross-sectional structural diagram of the auxiliary transmission;

[0037] Figure 2 It is a schematic diagram of the three-dimensional structure of the planet carrier assembly from the first perspective;

[0038] Figure 3 It is a schematic diagram of the three-dimensional structure of the planet carrier assembly from a second viewing angle;

[0039] Figure 4 is a schematic diagram of the side structure of the planet carrier assembly;

[0040] Figure 5 is a schematic diagram of the three-dimensional structure of the rear shell;

[0041] Figure 6 is a schematic cross-sectional view of the synchronizer assembly in a neutral state;

[0042] Figure 7 is a schematic cross-sectional view of the synchronizer assembly in a meshing synchronous state;

[0043] Figure 8 Schematic diagram of the three-dimensional structure of the sliding sleeve;

[0044] Fig. 9 Schematic diagram of the three-dimensional structure of the clasp;

[0045] Fig.10It is a schematic diagram of the three-dimensional structure of the support column protrusion;

[0046] Fig.11 Schematic diagram of the three-dimensional structure of the gear seat;

[0047] Fig.12 It is a three-dimensional structural schematic diagram of the gear seat being assembled on the sliding sleeve;

[0048] Fig.13 It is a schematic diagram of the three-dimensional structure before the planet carrier and the cone ring are assembled;

[0049] Fig.14 It is a schematic diagram of the three-dimensional structure after the planet carrier and the cone ring are assembled;

[0050] Fig.15 Schematic diagram of the three-dimensional structure of the output shaft;

[0051] Fig.16 is a schematic diagram of the three-dimensional structure of the planetary gear shaft;

[0052] Fig.17 is a schematic diagram of the three-dimensional structure of the intermediate shaft;

[0053] Fig.18 A schematic diagram of the speed reduction output route of the auxiliary transmission;

[0054] Fig.19 Schematic diagram of the direct output route of the auxiliary transmission.

[0055] In the figure:

[0056] 1. Linear motor; 2. Control shaft; 3. First race; 4. Fixed pin; 5. Second race;

[0057] 6. rear housing; 61. first internal spline; 62. motor assembly end surface;

[0058] 7. Shift fork;

[0059] 8. Synchronizer assembly; 81. Gear seat; 811. Clamping groove; 812. First notch; 82. Conical ring; 821. Second internal spline; 822. First external spline; 83. Support column convex block; 84. Sliding sleeve; 841. Stop block; 842. Arc groove; 843. Second notch; 85. Clamping ring; 851. Protrusion; 86. Spring;

[0060] 9. Locking nut; 10. Flange; 11. Target wheel; 12. First bearing;

[0061] 13. output shaft; 131. second external spline; 132. third external spline; 133. third internal spline; 134. first bearing assembly surface; 135. second bearing assembly surface;

[0062] 14. Second bearing; 15. Ring gear;

[0063] 16. Planet carrier assembly; 161. Planetary gear; 162. Double needle roller shaft; 163. Planetary gear revolving shaft; 164. Planet carrier; 1641. Bearing assembly surface three; 1642. Fourth external spline; 1643. Bearing assembly surface four;

[0064] 17. The third bearing;

[0065] 18. Planetary gear shaft; 181. Sun gear; 182. Fifth external spline; 183. Bearing assembly surface five; 184. Bearing assembly surface six;

[0066] 19. Fourth bearing; 20. First input gear; 21. Fifth bearing; 22. Second input gear;

[0067] 23. Intermediate shaft; 231. Sixth external spline; 232. Seventh external spline; 233. Bearing assembly surface seven;

[0068] 24. Sixth bearing. DETAILED DESCRIPTION

[0069] In order to enable those skilled in the art to better understand the solution of the present application, the technical solution in the embodiments of the present application will be clearly and completely described below in conjunction with the drawings in the embodiments of the present application. Obviously, the described embodiments are only part of the embodiments of the present application, not all of the embodiments. Based on the embodiments in the present application, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of this application.

[0070] The embodiments of the present application provide a sub-transmission, a main transmission and a vehicle, which can avoid the problem that the planetary gear assembly (planetary gear shaft and planetary carrier assembly) of the traditional sub-transmission is always in operation regardless of whether it is working in deceleration output or direct output, which will accelerate the wear of the planetary gears, shorten their service life, reduce transmission efficiency, require more frequent maintenance and replacement of parts, and increase maintenance costs.

[0071] First, as Fig.18 and Fig.19As shown, an embodiment of the present application provides a sub-transmission, which includes: an intermediate shaft 23, one end of which is spline-connected to the output shaft 13, and the outer wall of the other end thereof is sleeved with a second input gear 22; a planetary gear shaft 18, the planetary gear shaft 18 is sleeved on the outer wall of the intermediate shaft 23, one end of the planetary gear shaft 18 is meshed with a planetary carrier assembly 16, and the outer wall of the other end thereof is sleeved with a first input gear 20; a synchronizer assembly 8, one end of the synchronizer assembly 8 is spline-connected to the output shaft 13, and the other end is spline-connected to the planetary carrier assembly 16, and the synchronizer assembly 8 is used for power connection or power disconnection between the planetary carrier assembly 16 and the intermediate shaft 23.

[0072] Exemplarily, the right end of the intermediate shaft 23 is spline-connected to the left end of the output shaft 13, and the outer wall of the intermediate shaft 23 is sleeved with a planetary gear shaft 18. The intermediate shaft 23 and the planetary gear shaft 18 rotate independently without interfering with each other. The left end of the intermediate shaft 23 is sleeved with a second input gear 22, and the left end of the planetary gear shaft 18 is sleeved with a first input gear 20. The main transmission can choose to use the second input gear 22 or the first input gear 20 as the power input point. The right end of the planetary gear shaft 18 is meshed with the planetary carrier assembly 16, and the right end of the planetary carrier assembly 16 and the output shaft 13 are both spline-connected to the synchronizer assembly 8. The synchronizer assembly 8 can realize power connection or disconnection within itself, thereby realizing power connection or disconnection between the right end of the planetary carrier assembly 16 and the output shaft 13.

[0073] Specifically, the deceleration output route: when the first input gear 20 is subjected to force (the source of force is the main transmission gear meshed with it), the torque begins to be transmitted, and the force is transmitted from the first input gear 20 to the planetary gear shaft 18, the planetary carrier assembly 16, the synchronizer assembly 8 and the output shaft 13 in sequence, completing the deceleration output. At this time, the synchronizer assembly 8 is in a meshing state, so that the planetary carrier assembly 16 and the output shaft 13 are connected in power; the direct output route: when the second input gear 22 is subjected to force, the torque begins to be transmitted, and the force is transmitted from the second input gear 22 to the intermediate shaft 23 and the output shaft 13 in sequence, completing the direct output. At this time, the synchronizer assembly 8 is in a neutral state, so that the planetary carrier assembly 16 and the output shaft 13 are disconnected in power. This avoids the problem that the planetary gear assembly (planetary gear shaft 18 and planetary carrier assembly 16) of the traditional auxiliary transmission is always in operation regardless of the deceleration output or direct output, which will accelerate the wear of the planetary gears, shorten their service life, reduce transmission efficiency, require more frequent maintenance and replacement of parts, and increase maintenance costs.

[0074] In combination with the first aspect, in one embodiment, Figure 6 and Figure 7As shown, the synchronizer assembly 8 includes: a gear seat 81, the inner wall of which is spline-connected to the outer wall of the output shaft 13; a cone ring 82, which is coaxially arranged with the gear seat 81, and the inner wall of which is spline-connected to the outer wall of one end of the planetary carrier assembly 16; a sleeve 84, which is sleeved on the outer walls of the gear seat 81 and the cone ring 82, and is spline-connected to the gear seat 81, and the sleeve 84 can move radially and is spline-connected to the cone ring 82.

[0075] Exemplarily, the synchronizer assembly 8 includes a sleeve 84 and a tooth seat 81 and a cone ring 82 disposed in the sleeve 84, as shown in FIG. Fig.13 and Fig.14 The interior of the cone ring 82 is connected to the fourth external spline of the outer wall of the right end of the planetary carrier assembly 16 through the second internal spline 821. Fig.13 and Figure 7 The outer portion of the cone ring 82 is connected to the inner spline of the sleeve 84 through the first outer spline 822. Fig.11 and Fig.15 The internal spline of the gear seat 81 is spline-connected with the third external spline 132 of the output shaft 13. Figure 6 When the sleeve 84 is on the right side, that is, the sleeve 84 is in meshing connection with the gear holder 81, but is disconnected from the cone ring 82. At this time, the synchronizer assembly 8 is in neutral, and the power disconnection between the planet carrier assembly 16 and the output shaft 13 is achieved. For details, refer to Figure 7 The sliding sleeve 84 can move to the left and be in meshing connection with the cone ring 82. At this time, the synchronizer assembly 8 is in meshing state, realizing power transmission between the planet carrier assembly 16 and the output shaft 13.

[0076] In combination with the first aspect, in one embodiment, Figure 6 , Figure 7 , Fig.10 , Fig.11 and Fig.12 An elastic telescopic part is embedded in the outer wall of the tooth seat 81, one end of the elastic telescopic part faces the axis of the tooth seat 81, and the other end of the elastic telescopic part is arranged in an arc surface; an arc groove 842 is opened on the inner wall of the sliding sleeve 84, and the other end of the elastic telescopic part moves into the arc groove 842 due to its own elastic force. When the sliding sleeve 84 moves radially and is spline-connected with the conical ring 82, the other end of the elastic telescopic part moves out of the arc groove 842.

[0077] Exemplary, specific reference Figure 7In the cross-sectional view shown in FIG. 1 , the upper and lower top walls of the tooth seat 81 are embedded with elastic members, which are perpendicular to the side walls and point to the center of the tooth seat 81. The elastic force of the elastic member causes the end of the elastic member away from the tooth seat 81 to abut against the inner wall of the sliding sleeve 84. For details, refer to FIG. Figure 6 As shown in the cross-sectional view, when the sleeve 84 moves to the right, its elastic member will be stuck in the arc groove 842 under its own elastic force, so that the sleeve 84 moves to the right and ensures that the synchronizer assembly 8 is completely disconnected. The elastic member mainly plays a positioning and supporting role, ensuring that the synchronizer assembly can remain stable during operation and correctly cooperate with other components to help achieve synchronous meshing of gears, thereby shortening the shifting time and preventing gear impact before synchronization. Figure 7 As shown, when the sliding sleeve 84 moves to the left, its elastic telescopic part will move out of the arc groove 842 under its own elastic force. The other end of the elastic telescopic part is set in an arc surface and with the cooperation of the arc groove 842, the sliding sleeve 84 can be smoothly moved to prevent jamming. The outer diameter of the cone ring 82 gradually increases from left to right. At this time, after the arc groove 842 and the outer wall of the cone ring 82 are engaged in place, the subsequent sliding sleeve 84 can be prevented from continuing to move to the left and affecting the power connection state.

[0078] In combination with the first aspect, in one embodiment, Fig.10 and Fig.11 As shown, the outer wall of the tooth seat 81 is provided with a mounting groove; the elastic telescopic member includes: a support column protrusion 83, one end of the support column protrusion 83 is arranged in the mounting groove, and the other end face thereof is arranged in an arc surface and is adapted to the arc groove 842; a spring 86, the spring 86 is sleeved on the outer wall of the support column protrusion 83, and the two ends of the spring 86 are against the support column protrusion 83 and the mounting groove.

[0079] Exemplarily, the outer wall of the gear holder 81 is provided with four mounting grooves along its circumferential direction, and elastic telescopic parts are arranged in the mounting grooves, and the elastic telescopic parts include a support column protrusion 83, one end of the support column protrusion 83 is installed in the mounting groove through a spring 86, and the other end thereof is matched with the arc groove 842. When the sliding sleeve 84 moves to shift gears, the cooperation of the support column protrusion 83 and the spring 86 ensures that the sliding sleeve 84 shifts into place.

[0080] In combination with the first aspect, in one embodiment, Figure 6 , Figure 7 and Fig. 9 As shown, the other end side wall of the elastic telescopic member is provided with a protrusion; the outer wall of the tooth seat 81 is engaged and fixed to the clamping ring 85, and the end face of the clamping ring 85 is in contact with the protrusion, which is used to prevent the elastic telescopic member from shifting along the telescopic direction.

[0081] Exemplarily, because the support column protrusion 83 is at least partially located outside the mounting groove, during the movement and shifting of the sliding sleeve 84, the sliding sleeve 84 will drive the support column protrusion 83 to radially deviate, so that the support column protrusion 83 is no longer perpendicular to the outer wall of the gear seat 81. At this time, the outer wall of the gear seat 81 is sleeved with a retaining ring 85, and the side wall of the retaining ring 85 will contact the protrusion of the support column protrusion 83, limiting the radial deviation of the support column protrusion 83 in the direction close to the retaining ring 85. The protrusion of the support column protrusion 83 can be specifically referred to Fig.10 The support column protrusion 83 is divided into three parts. The first part is the support column at the bottom end. The second part is the protrusion fixed to the top of the support column. The top surface of the protrusion is set in an arc surface to facilitate the adaptation of the arc groove 842. The third part is a protrusion integrally formed with the right side of the protrusion. The protrusion contacts the retaining ring 85 to prevent the support column protrusion 83 from radially deviating in the direction close to the retaining ring 85.

[0082] In combination with the first aspect, in one embodiment, Figure 6 , Figure 7 , Figure 8 , Fig. 9 , Fig.11 and Fig.12 As shown, the side wall of the tooth seat 81 is provided with a first notch 812, the side wall of the retaining ring 85 is provided with a protrusion 851, and the protrusion 851 is located in the first notch 812; the inner side wall of the sliding sleeve 84 is provided with a second notch 843, the second notch 843 is provided with a limiting block 841, and projected in the radial direction, the first notch 812 is located in the second notch 843, and the limiting block 841 is located in the first notch 812; when the sliding sleeve 84 moves radially close to the tooth seat 81, the first notch 812 moves into the second notch 843 until the limiting block 841 abuts against the protrusion 851 to limit the sliding sleeve 84 from continuing to move radially.

[0083] For example, Fig.11 As shown, the end surface of the gear holder 81 is provided with a slot 811, and the snap ring 85 is fixed in the slot 811. The outer wall of the gear holder 81 is provided with four first notches 812, and the snap ring 85 is provided with four protrusions 851 ( Fig.11 Only one protrusion 851 is shown in the figure, and the sliding sleeve 84 is provided with four second notches 843 correspondingly. Fig.12 As shown, after the protrusion 851 is inserted into the slot 811, the protrusion 851 is located in the first notch 812. When the sleeve 84 moves right to the neutral position, the end face of the limit block 841 contacts the protrusion 851, and the sleeve 84 cannot move any further, thereby preventing the sleeve 84 from moving to the right beyond the neutral position when the synchronizer assembly 8 is in neutral, i.e., an anti-overrun design.

[0084] In combination with the first aspect, in one embodiment, Figure 1 As shown, the synchronizer assembly 8 also includes: a linear motor 1, a shift fork 7 is fixed to the translation end of the linear motor; a slide groove is provided on the outer wall of the slide sleeve 84, and one end of the shift fork 7 is arranged in the slide groove; the linear motor 1 can drive the shift fork 7 to move linearly, so as to drive the slide sleeve 84 to move radially.

[0085] For example, the linear motor 1 is mounted on the top of the rear housing 6, and its translation end can drive the shift fork 7 to move left and right. Figure 1 and Figure 6 One end of the shift fork 7 is arranged in the slide groove of the sliding sleeve 84 to drive the sliding sleeve 84 to move left and right to perform the shift operation.

[0086] In combination with the first aspect, in one embodiment, Figure 2 , Figure 3 , Figure 4 and Figure 5 As shown, the planetary carrier assembly 16 includes a planetary carrier 164, and the planetary carrier 164 is rotatably installed with multiple planetary gears 161 along its own circumferential direction. The multiple planetary gears 161 are meshed with one end of the planetary gear shaft 18, and the outer walls of the multiple planetary gears 161 are meshed with the same ring gear 15; the auxiliary transmission also includes: a rear housing 6, the synchronizer assembly 8 and the output shaft 13 are assembled in the rear housing 6, and the inner side wall of the rear housing 6 is provided with a first internal spline 61, and the first internal spline 61 is assembled and fixed with the outer ring spline of the ring gear 15.

[0087] Exemplarily, the planetary carrier assembly 16 is meshed with the first internal spline 61 of the inner wall of the rear shell 6 through the ring gear 15, which can improve the stability of the operation of the planetary carrier assembly 16 and avoid the planetary carrier assembly 16 meshing with the rear shell 6 after long-term use, affecting the service life of the rear shell 6.

[0088] In summary, specifically, Figure 1 As shown, the auxiliary transmission includes a linear motor 1, an operating shaft 2, a first race 3, a fixing pin 4, a second race 5 and a shift fork 7. Figure 5As shown, the linear motor 1 is installed at the motor assembly end face 62 of the rear housing 6, wherein the auxiliary transmission also includes a front housing (not shown in the figure) assembled and connected to the rear housing 6, and is sleeved on the outer walls of the third bearing 17, the planetary gear shaft 18, the fourth bearing 19, the first input gear 20, the fifth bearing 21, the second input gear 22, the intermediate shaft 23 and the sixth bearing 24. The operating shaft 2 is fixed at the motor assembly end face 62 through the first seat ring 3 and the second seat ring 5. The shift fork 7 is slidably connected to the outer wall of the operating shaft 2, and the outer wall of the shift fork 7 is provided with a receiving groove, which is used for the moving end of the linear motor 1 to move into it, so that the linear movement of the linear motor 1 drives the linear movement of the shift fork 7, and one end of the shift fork 7 moves into the sliding groove of the sliding sleeve 84, thereby driving the radial movement of the sliding sleeve 84.

[0089] Among them, the locking nut 9, the flange 10, the target wheel 11 and the first bearing 12 are used for the stable installation of the output shaft 13 in the rear housing 6. The third bearing 17 is used for the stable installation between the planet carrier assembly 16 and the front housing, the fourth bearing 19 is used for the stable installation between the planetary gear shaft 18 and the front housing, the fifth bearing 21 is used for the stable installation between the intermediate shaft 23 and the planetary gear shaft 18, and the sixth bearing 24 is used for the stable installation between the intermediate shaft 23 and the front housing.

[0090] Among them, Figure 4 and Figure 5 As shown, the outer ring spline of the gear ring 15 is assembled and fixed on the first inner spline 61 of the rear housing 6, as shown in FIG. Figure 3 As shown, the planetary gear revolving shaft 163 is fixed on the planetary carrier 164. Figure 4 As shown, the double needle roller shaft 162 is sleeved on the planetary gear revolving shaft 163, and the planetary gear 161 is sleeved on the double needle roller shaft 162 and can rotate freely. One end of the tooth surface of the planetary gear 161 is connected to the sun gear 181 (see Figure 4 ) tooth surface, and the other end is in contact with the inner ring tooth surface of the gear ring 15, such as Figure 1 and Figure 2 As shown, the third bearing 17 is assembled on the bearing assembly surface 1641, and the fourth external spline 1642 is assembled and fixed with the second internal spline 821 of the cone ring 82 (see Fig.13 and Fig.14 ), the inner wall of the bearing assembly surface 4 1643 is assembled with the second bearing 14 (see Figure 1 and Figure 3 ).

[0091] Among them, see Figure 1 and Fig.15The second external spline 131 is connected, matched and fixed with the internal spline of the flange 10, the third external spline 132 is connected, matched and fixed with the internal spline of the gear seat 81, and the third internal spline 133 is connected, matched and fixed with the sixth external spline 231 of the intermediate shaft 23. The second bearing 14 is mounted on the first bearing assembly surface 134, and the first bearing 12 is mounted on the second bearing assembly surface 135.

[0092] Among them, see Figure 1 and Fig.16 The sun gear 181 of the planetary gear shaft 18 meshes with the planetary gear 161 , the fifth external spline 182 is connected and fixed to the internal spline of the first input gear 20 , the fifth bearing 21 is assembled on the bearing assembly surface 5 183 , and the fourth bearing 19 is assembled on the bearing assembly surface 6 184 .

[0093] Among them, see Figure 1 and Fig.17 The sixth external spline 231 of the intermediate shaft 23 is connected and fixed to the third internal spline 133 of the output shaft 13 , the seventh external spline 232 is connected, matched and fixed to the internal spline of the second input gear 22 , and the sixth bearing 24 is assembled on the bearing assembly surface 233 .

[0094] In a second aspect, an embodiment of the present application provides a main transmission including a sub-transmission as described in some of the above embodiments, wherein the output end of the main transmission can be switched to engage with the first input gear 20 or the second input gear 22 .

[0095] In a third aspect, an embodiment of the present application provides a vehicle, which includes a main transmission as mentioned above.

[0096] In the description of the present application, it should be noted that the terms "upper", "lower", etc. indicate orientations or positional relationships based on the orientations or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the present application and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as a limitation on the present application. Unless otherwise clearly specified and limited, the terms "installed", "connected", and "connected" should be understood in a broad sense, for example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be a direct connection, or it can be an indirect connection through an intermediate medium, or it can be a connection between the two elements. For those of ordinary skill in the art, the specific meanings of the above terms in the present application can be understood according to the specific circumstances.

[0097] It should be noted that, in this application, relational terms such as "first" and "second" are only used to distinguish one entity or operation from another entity or operation, and do not necessarily require or imply any such actual relationship or order between these entities or operations. Moreover, the terms "include", "comprise" or any other variants thereof are intended to cover non-exclusive inclusion, so that a process, method, article or device including a series of elements includes not only those elements, but also other elements not explicitly listed, or also includes elements inherent to such process, method, article or device. In the absence of further restrictions, the elements defined by the sentence "comprise a ..." do not exclude the presence of other identical elements in the process, method, article or device including the elements.

[0098] The above description is only a specific implementation of the present application, so that those skilled in the art can understand or implement the present application. Various modifications to these embodiments will be apparent to those skilled in the art, and the general principles defined herein can be implemented in other embodiments without departing from the spirit or scope of the present application. Therefore, the present application will not be limited to the embodiments shown herein, but will conform to the widest range consistent with the principles and novel features applied for herein.

Claims

1. A sub-transmission, It is characterized in that It includes: An intermediate shaft (23), one end of which is spline-connected to the output shaft (13), and the other end of which is sleeved on an outer wall with a second input gear (22); A planetary gear shaft (18), wherein the planetary gear shaft (18) is sleeved on the outer wall of the intermediate shaft (23), one end of the planetary gear shaft (18) is meshed with a planet carrier assembly (16), and the outer wall of the other end of the planetary gear shaft (18) is sleeved with a first input gear (20); A synchronizer assembly (8), one end of which is spline-connected to the output shaft (13), and the other end of which is spline-connected to the planetary carrier assembly (16), and the synchronizer assembly (8) is used for power connection or power disconnection between the planetary carrier assembly (16) and the intermediate shaft (23).

2. The auxiliary transmission as claimed in claim 1, It is characterized in that The synchronizer assembly (8) comprises: A gear seat (81), the inner wall of the gear seat (81) being spline-connected to the outer wall of the output shaft (13); A cone ring (82), the cone ring (82) and the gear seat (81) are coaxially arranged, and the inner wall of the cone ring (82) is spline-connected to the outer wall of one end of the planet carrier assembly (16); A sliding sleeve (84) is sleeved on the outer walls of the tooth seat (81) and the cone ring (82) and is spline-connected to the tooth seat (81). The sliding sleeve (84) is radially movable and spline-connected to the cone ring (82).

3. The auxiliary transmission as claimed in claim 2, It is characterized in that An elastic telescopic member is embedded and installed on the outer wall of the tooth seat (81), one end of the elastic telescopic member faces the axis of the tooth seat (81), and the other end of the elastic telescopic member is arranged in an arc surface; The inner wall of the sliding sleeve (84) is provided with an arc groove (842), and the other end of the elastic telescopic member moves into the arc groove (842) due to its own elastic force. When the sliding sleeve (84) moves radially to be spline-connected with the conical ring (82), the other end of the elastic telescopic member moves out of the arc groove (842).

4. The auxiliary transmission as claimed in claim 3, It is characterized in that The outer wall of the gear seat (81) is provided with a mounting groove; The elastic expansion member comprises: A support column protrusion (83), one end of which is disposed in the mounting groove, and the other end surface of which is disposed in an arc shape and is adapted to the arc groove (842); A spring (86), wherein the spring (86) is sleeved on the outer wall of the support column protrusion (83), and two ends of the spring (86) abut against the support column protrusion (83) and the installation groove.

5. The auxiliary transmission as claimed in claim 3, It is characterized in that The other end side wall of the elastic telescopic member is provided with a protrusion; The outer wall of the tooth seat (81) is clamped and fixed to the clamping ring (85), and the end surface of the clamping ring (85) is in contact with the protruding portion, which is used to prevent the elastic telescopic member from deviating along the telescopic direction.

6. The auxiliary transmission as claimed in claim 5, It is characterized in that A first notch (812) is formed on the side wall of the tooth seat (81), a protrusion (851) is formed on the side wall of the snap ring (85), and the protrusion (851) is located in the first notch (812); The inner side wall of the sliding sleeve (84) is provided with a second notch (843), and the second notch (843) is provided with a limiting block (841). When projected in the radial direction, the first notch (812) is located in the second notch (843), and the limiting block (841) is located in the first notch (812); When the sliding sleeve (84) moves radially toward the tooth seat (81), the first notch (812) moves into the second notch (843) until the limit block (841) abuts against the protruding portion (851), thereby limiting the sliding sleeve (84) from continuing to move radially.

7. The auxiliary transmission as claimed in claim 3, It is characterized in that The synchronizer assembly (8) further comprises: A linear motor (1), wherein a shift fork (7) is fixed to the translation end of the linear motor; The outer wall of the sliding sleeve (84) is provided with a sliding groove, and one end of the shift fork (7) is arranged in the sliding groove; The linear motor (1) can drive the shift fork (7) to move linearly, thereby driving the sliding sleeve (84) to move radially.

8. The auxiliary transmission as claimed in claim 1, It is characterized in that The planet carrier assembly (16) comprises a planet carrier (164), wherein the planet carrier (164) is rotatably mounted with a plurality of planetary gears (161) along its own circumferential direction, wherein the plurality of planetary gears (161) are meshed with one end of the planetary gear shaft (18), and the outer walls of the plurality of planetary gears (161) are meshed with the same gear ring (15); The auxiliary transmission also includes: The rear housing (6), the synchronizer assembly (8) and the output shaft (13) are assembled in the rear housing (6); the inner side wall of the rear housing (6) is provided with a first internal spline (61); the first internal spline (61) is assembled and fixed with the outer ring spline of the gear ring (15).

9. A main transmission, It is characterized in that It comprises the auxiliary transmission as claimed in any one of claims 1 to 8, and the output end of the main transmission can be switched to mesh with the first input gear (20) or the second input gear (22).

10. A vehicle, It is characterized in that It comprises a main transmission as claimed in claim 9.

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