A planetary sub-gear synchronizer structure

Abstract

The application relates to a planetary sub-gearbox synchronizer structure and belongs to the technical field of vehicle transmission gear shifting, which comprises a planetary gear system, a high-gear cone ring and a low-gear cone ring. The planetary gear system comprises a planet carrier and planet gears arranged on the planet carrier, and a planet gear ring which is in mesh with the planet gears and can slide along the axial direction of the planet gears. The high-gear cone ring is arranged at one end of the planet gears and is connected with the planet carrier. The low-gear cone ring is arranged at the other end of the planet gears and is used for being connected with a housing. Therefore, the planet gear ring of the application has the function of a synchronizer sliding sleeve, and parts such as a synchronizer tooth sleeve and a support plate are reduced, which provides conditions for reducing the volume of the planetary sub-gearbox and effectively reduces the assembly difficulty and cost. The distance from the planet gear ring to the low-gear cone ring and to the housing fixed by the low-gear cone ring is shortened, the length of the torque arm of the planet gear ring acting on the housing is shortened when resisting, the reverse torque of the planetary gear system on the housing with an indirect connection relationship is greatly reduced, and the purpose of effectively avoiding the cracking of the housing is achieved.

Description

Technical Field

[0001] This application relates to the field of vehicle transmission technology, and in particular to a planetary auxiliary gearbox synchronizer structure. Background Technology

[0002] A gearbox is a gearbox that changes the transmission ratio and direction of motion. It is located between the clutch and the central drive. Its main functions are: to change the driving force and speed of the vehicle while keeping the engine speed and torque constant (shifting gears); to allow the vehicle to move backward (reversing direction); and to allow the engine to stop without shutting off (neutral).

[0003] Existing heavy-duty multi-speed gearboxes generally employ a main gearbox plus an NGW planetary auxiliary gearbox structure to achieve a multiplication of speed ratios. The planetary auxiliary gearbox has two gears: low and high, switched by a synchronizer. In high gear, the ring gear engages with the planet carrier, and the planetary auxiliary gearbox speed ratio is 1; in low gear, the ring gear is fixed, and power is output through the sun gear, planet gears, and planet carrier. Since the speed of the planet carrier is its revolution speed, a very large reduction ratio can be obtained.

[0004] However, in existing planetary auxiliary gearbox synchronizer designs, the synchronizer and oil guide device are installed in series, resulting in a large axial length and weight. The connection between the gear sleeve, gear ring, low-gear cone ring, support plate, and housing is complex, involving multiple splines, snap rings, and bolts, resulting in numerous parts, high assembly difficulty, and high cost. At the same time, in low gear, the gear ring is indirectly connected to the housing through the synchronizer's gear sleeve, low-gear cone ring, and support plate, thus fixing it and preventing it from rotating. This results in a large torque arm length for the gear ring acting on the housing, causing the planetary gear system to apply a large reverse torque to the housing with indirect connections, which can easily lead to housing cracking. Summary of the Invention

[0005] This application provides a planetary auxiliary gearbox synchronizer structure to solve the problems of high assembly difficulty and cost of planetary auxiliary gearboxes in the prior art, and the planetary gear system applying a large reverse torque to the housing connected to the support plate, which easily leads to housing cracking.

[0006] This application provides a planetary auxiliary box synchronizer structure, including:

[0007] A planetary gear system, comprising a planet carrier and planet gears mounted on the planet carrier, and a planet gear ring that meshes with the planet gears and can slide along the planet gear axis;

[0008] The high-gear cone ring is located at one end of the planetary gear and is connected to the planetary carrier. When it is in the high gear position, the planetary ring gear meshes with the high-gear cone ring for transmission.

[0009] The low-gear cone ring, located at the other end of the planetary gear and used to connect to the housing, engages with the planetary gear ring for transmission when in low gear.

[0010] In some embodiments, a synchronizing ring is inserted into the planetary gear ring at the positions corresponding to the high-gear cone ring and the low-gear cone ring, and a pre-synchronizing component with an elastic structure is provided between the synchronizing ring and the planetary gear ring; the outer ring of the planetary gear ring is provided with a shift fork groove.

[0011] Both sides of the planetary carrier are provided with annular stepped grooves for axially limiting the synchronization ring.

[0012] In some embodiments, the planetary gear ring has pre-synchronous grooves at both ends along its inner circumference, the synchronizing ring has an annular groove along its outer circumference, and the pre-synchronizing component is an elastic retaining ring disposed in the annular groove. The elastic retaining ring is used to engage with the pre-synchronizing groove when moving to generate a pre-synchronizing frictional torque.

[0013] The pre-grooving groove is formed by milling off the end of the internal teeth on the planetary gear ring. The pre-grooving groove includes a ramp on the internal teeth and a sliding surface connecting the ramp. The elastic retaining ring is provided with a trapezoidal end that mates with the ramp and the sliding surface.

[0014] In some embodiments, the synchronizing ring has a plurality of oil holes in the inner circumference that communicate with the annular groove, and the synchronizing ring has a plurality of end face grooves at the end near the planetary carrier, with the oil holes and the end face grooves being distributed alternately.

[0015] In some embodiments, the planetary gear ring has engagement teeth at both ends of its internal teeth for matching with the low-end cone ring and the high-end cone ring, the engagement teeth being formed by milling off the ends of the internal teeth.

[0016] In some embodiments, the housing includes a middle shell connected to the low-end cone ring, and a rear shell connected to the middle shell and housing the high-end cone ring;

[0017] The planetary gear system also includes a sun gear that meshes with the planet gears and a hollow shaft fixed to the sun gear. The middle shell and the low-gear cone ring are provided with interconnected lubricating oil passages that guide the lubricating oil into the hollow shaft.

[0018] In some embodiments, the middle shell and the hollow shaft are rotatably connected by bearings, and the low-end cone ring is provided with a positioning surface for an axial positioning bearing.

[0019] In some embodiments, the planetary gear ring is provided with at least one positioning groove at both ends along its axial direction, and the planetary gear ring is provided with at least one first locking tooth at both ends along its axial direction.

[0020] The synchronization ring is provided with a positioning tooth that matches the positioning groove, and a second locking tooth that cooperates with the first locking tooth. The first locking tooth can move relative to the second locking tooth.

[0021] In some embodiments, the first locking tooth is formed by milling off the end of the internal tooth on the planetary gear ring, and forms a locking area with the end face of the planetary gear ring;

[0022] When the second locking tooth engages with the first locking tooth, it can be engaged in the locking area, and the second locking tooth can move within the locking area.

[0023] In some embodiments, the positioning groove is formed by milling off the end of the internal gear on the planetary gear ring;

[0024] The mating surfaces of the first locking tooth and the second locking tooth along the axial direction of the planetary gear ring are inclined surfaces.

[0025] The beneficial effects of the technical solution provided in this application include:

[0026] This application provides a planetary auxiliary gearbox synchronizer structure, which is a planetary gear system including a planet carrier and planetary gears disposed on the planet carrier, and a planetary gear ring that meshes with the planetary gears and can slide along the axial direction of the planetary gears; a high-gear conical ring located at one end of the planetary gears and connected to the planet carrier, wherein when in the high gear position, the planetary gear ring meshes with the high-gear conical ring for transmission; and a low-gear conical ring located at the other end of the planetary gears and used to connect to the housing, wherein when in the low gear position, the planetary gear ring meshes with the low-gear conical ring for transmission.

[0027] Therefore, the planetary gear ring of this application has the function of a synchronizer sleeve. By integrating the planetary gear ring and the planetary gear ring into one design, the synchronizer sleeve, support plate and other parts are eliminated, which can reduce the axial length and weight. The available installation space in the planetary auxiliary box is larger, which provides the conditions for reducing the volume of the planetary auxiliary box and can effectively reduce the assembly difficulty and cost.

[0028] Meanwhile, the low-gear cone ring and the high-gear cone ring are symmetrically arranged at both ends of the planetary gear ring. The low-gear cone ring is directly fixed to the housing, which optimizes the transmission path of the planetary gear ring when in a downshift, shortens the distance from the planetary gear ring to the low-gear cone ring and to the housing to which the low-gear cone ring is fixed, and shortens the torque arm of the planetary gear ring acting on the housing when in a downshift. This significantly reduces the reverse torque applied by the planetary gear system to the housing which has an indirect connection, and effectively avoids the housing cracking. Attached Figure Description

[0029] To more clearly illustrate the technical solutions in the embodiments of this application, the accompanying drawings used in the description of the embodiments will be briefly introduced below. Obviously, the accompanying 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.

[0030] Figure 1This is a schematic diagram of the structure of a planetary auxiliary box in the prior art;

[0031] Figure 2 This is a power path diagram for a planetary auxiliary box in existing technology;

[0032] Figure 3 This is a schematic diagram of the pre-synchronization state in an embodiment of this application;

[0033] Figure 4 This is a power route diagram for an embodiment of this application;

[0034] Figure 5 for Figure 3 A magnified view of a portion of the marked area I;

[0035] Figure 6 This is a schematic diagram of the synchronization ring structure according to an embodiment of this application;

[0036] Figure 7 This is a schematic diagram of the structure of the planetary gear ring according to an embodiment of this application;

[0037] Figure 8 This is a schematic diagram of the low-end cone ring structure according to an embodiment of this application;

[0038] Figure 9 This is a partial cross-sectional view of the locked state according to an embodiment of this application;

[0039] Figure 10 A partial cross-sectional view of an embodiment of this application in a low-gear configuration;

[0040] Figure 11 This is a schematic diagram of the structure in the low gear state according to an embodiment of this application.

[0041] In the picture:

[0042] 1' Shaft; 2' Sun gear; 3' Planet gear; 4' Planetary ring gear; 5' Planetary carrier; 6' Gear sleeve; 7' Rear housing; 8' Support plate; 9' Low-gear cone ring; 10' High-gear cone ring; 11' Oil guide cup; 12' Oil guide seat; 13' Middle housing;

[0043] 1. Hollow shaft; 2. Oil pipe; 3. Middle shell; 4. Plug; 5. Low-gear cone ring; 6. Synchronizing ring; 7. Planetary gear ring; 8. Planetary gear; 9. Planetary carrier; 10. Bearing; 11. High-gear cone ring; 12. Rear shell; 13. Sun gear; 14. Bolt; 15. Elastic retaining ring. Detailed Implementation

[0044] To make the objectives, technical solutions, and advantages of the embodiments of this application clearer, the technical solutions of the embodiments of this application will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of this application, not all embodiments. Based on the embodiments of this application, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of this application.

[0045] This application provides a planetary auxiliary gearbox synchronizer structure, which can solve the problems of high assembly difficulty and high cost of planetary auxiliary gearboxes in the prior art, as well as the problem that the planetary gear system will apply a large reverse torque to the housing connected to the support plate, which will easily lead to housing cracking.

[0046] See Figure 1 and 2 As shown, Figure 1 For the existing planetary auxiliary box structure, Figure 1 The power path diagram for the existing technical solution shows that power is input from shaft 1' and output to planetary carrier 5'. The auxiliary gearbox has two gears: low and high, switched by a synchronizer. In high gear, planetary ring gear 4' engages with planetary carrier 5', and the gearbox speed ratio is 1. In low gear, planetary ring gear 4' is connected to the rear housing 7' and remains stationary. Power is output through sun gear 2', planetary gears 3', and planetary carrier 5'. Since the speed of planetary carrier 5' is its revolution speed, a large reduction ratio can be obtained.

[0047] The existing planetary auxiliary gearbox synchronizer design: The synchronizers are installed in series at the rear end of the planetary carrier 5'. The gear sleeve 6' is connected to the planetary gear ring 4' via a spline and snap ring. The high-gear cone ring 10' is connected to the planetary carrier 5' via a spline, and the low-gear cone ring 9' is connected to the rear housing 7' via a support plate 8'. High and low gear switching is achieved by pulling the gear sleeve 6' to engage with the high-gear cone ring 10' and the low-gear cone ring 9' respectively. An oil guide seat 12' and an oil guide cup 11' are installed between the planetary carrier 5' and the middle housing 13' to guide pressurized lubricating oil into the central oil pipe for better lubrication of the bearings, sun gear, and synchronizer.

[0048] As can be seen from the above, the synchronizer and oil guide device are installed in series, resulting in a large axial length and heavy weight; the connection between the gear sleeve 6', planetary gear ring 4', low-gear cone ring 9', support plate 8', and housing is complex, including multiple splines, snap rings, and bolts, resulting in many parts, high assembly difficulty, and high cost; when in low gear, the torque lever arm from the planetary system to the low-gear cone ring 9' is long, and the planetary system will apply a large reverse torque to the rear housing 7', causing the rear housing 7' to be prone to cracking.

[0049] See Figures 3 to 11 As shown, this application embodiment provides a planetary auxiliary box synchronizer structure, including:

[0050] A planetary gear system, comprising a planet carrier 9 and planet gears 8 disposed on the planet carrier 9, and a planet gear ring 7 that meshes with the planet gears 8 and can slide along the axial direction of the planet gears 8;

[0051] The high-gear cone ring 11 is located at one end of the planetary gear 8 and is connected to the planetary carrier 9. When it is in the high gear, the planetary gear ring 7 meshes with the high-gear cone ring 11 for transmission.

[0052] The low-gear cone ring 5 is located at the other end of the planetary gear 8 and is used to connect to the housing. When in the low gear, the planetary gear ring 7 meshes with the low-gear cone ring 5 for transmission.

[0053] In this embodiment of the planetary auxiliary gearbox synchronizer structure, the planetary gear ring 7 integrates the function of the synchronizer sleeve. The low-gear cone ring 5 and the high-gear cone ring 11 are symmetrically arranged at both ends of the planetary gear ring 7. Specifically, when the planetary gear ring 7 slides with the shift fork to mesh with the high-gear cone ring 11, the planetary gear ring 7 and the planet carrier 9 rotate synchronously, and the speed ratio of the planetary auxiliary gearbox is 1. When the planetary gear ring 7 slides with the shift fork to mesh with the low-gear cone ring 5, the planetary gear ring 7 is fixed, and the planet carrier 9 revolves with the planetary gear 8 to achieve deceleration output.

[0054] By integrating the planetary gear ring 7 and the planetary gear ring 8 into one design, compared with the existing technology, parts such as the synchronizer sleeve 6' and support plate 8' are eliminated, which can reduce the axial assembly length and overall weight. That is, the axial structure is more compact, the required installation space is smaller, the volume of the planetary auxiliary box can be reduced, and the assembly difficulty and manufacturing cost can be effectively reduced.

[0055] Meanwhile, the low-gear cone ring 5 is directly fixed to the housing, which optimizes the transmission path of the planetary gear ring 7 when in a down-gear position. This shortens the distance from the planetary gear ring 7 to the low-gear cone ring 5 and to the housing to which the low-gear cone ring 5 is fixed, thus reducing the torque arm length of the planetary gear ring 7 acting on the housing when in a down-gear position. This significantly reduces the reverse torque applied by the planetary gear system to the housing, which has an indirect connection, and effectively prevents the housing from cracking.

[0056] In some alternative embodiments: see Figures 3 to 7 As shown, this application embodiment provides a planetary auxiliary gearbox synchronizer structure. In this planetary auxiliary gearbox synchronizer structure, a synchronizer ring 6 is inserted into the planetary gear ring 7 at the positions corresponding to the high-gear cone ring 11 and the low-gear cone ring 5, respectively. A pre-synchronization component with an elastic structure is provided between the synchronizer ring 6 and the planetary gear ring 7. The outer ring of the planetary gear ring 7 is provided with a shift fork groove 7a. Both sides of the planetary carrier 9 are provided with annular stepped grooves for axially limiting the synchronizer ring 6.

[0057] In this embodiment, the shift fork groove 7a is used to install the shift fork. The shift fork drives the planetary gear ring 7 to slide axially. The planetary gear ring 7 drives the synchronization ring 6 to move through the pre-synchronization component. The annular stepped groove on the planet carrier 9 can axially limit the synchronization ring 6. Together with the outer conical surface of the high-gear conical ring 11 and the outer conical surface of the low-gear conical ring 5, the axial movement range of the synchronization ring 6 is limited, ensuring that the synchronization ring 6 can stably perform the synchronization function.

[0058] In some alternative embodiments: see Figures 3 to 11 As shown, this application embodiment provides a planetary auxiliary gearbox synchronizer structure. The planetary auxiliary gearbox synchronizer structure has pre-synchronization grooves at both ends of the planetary gear ring 7 along its inner circumference, and the synchronization ring 6 has an annular groove 6a along its outer circumference. The pre-synchronization component is an elastic retaining ring 15 disposed in the annular groove 6a. The elastic retaining ring 15 is used to engage with the pre-synchronization groove when moving to generate a pre-synchronization friction torque.

[0059] The pre-grooving groove is formed by milling off the end of the internal tooth 7c on the planetary gear ring 7. The pre-grooving groove includes a ramp 7b located on the internal tooth 7c and a sliding surface connecting the ramp 7b. The elastic retaining ring 15 is provided with a trapezoidal end 15a that mates with the ramp 7b and the sliding surface.

[0060] The pre-synchronization component in this embodiment is an elastic retaining ring 15 disposed in the annular groove 6a. The elastic retaining ring 15 expands outward and abuts against the pre-synchronization groove. When the planetary gear ring 7 moves axially with the shift fork, under the action of friction, the planetary gear ring 7 can drive the synchronization ring 6 to move through the elastic retaining ring 15 to realize pre-synchronization action or switch between high and low gears. The ramp 7b and the elastic retaining ring 15 with trapezoidal end 15a cooperate to keep the planetary gear ring 7 in the pre-synchronization position. The sliding surface rubs and slides against the elastic retaining ring 15 to assist in switching between high and low gears.

[0061] Specifically, when the planetary gear ring 7 slides from the right side to the middle, the elastic retaining rings 15 on both sides abut against the corresponding pre-synchronization grooves, the planetary gear ring 7 disengages from the high-end cone ring 11, and the right-side synchronizing ring 6 slides to the left and abuts against the right end face of the planetary carrier 9, thereby keeping the right-side synchronizing ring 6 and the high-end cone ring 11 separated. At this time, the elastic retaining ring 15 abuts against the ramp 7b, thereby maintaining the pre-synchronization position.

[0062] At this time, the planetary gear ring 7 continues to slide to the left, and at the same time, the planetary gear ring 7 continues to move to the left. With the synchronizing ring 6 on the right side not moving, the synchronizing ring 6 on the left side can move to the left to squeeze the low-gear cone ring 5, ensuring that the planetary gear ring 7 can smoothly mesh with the low-gear cone ring 5.

[0063] Similarly, when switching to a higher gear, the planetary gear ring 7 slides to the right, and the left synchronizing ring 6 abuts against the left end face of the planetary carrier 9. The planetary gear ring 7 continues to drive the right synchronizing ring 6 to move to the right through the elastic retaining ring 15, squeezing the high-gear cone ring 11, ensuring that the planetary gear ring 7 can smoothly mesh with the high-gear cone ring 11.

[0064] In some alternative embodiments: see Figure 6 As shown, this application embodiment provides a planetary auxiliary box synchronizer structure. The inner circumference of the synchronization ring 6 of the planetary auxiliary box synchronizer structure is provided with a plurality of oil holes 6g that communicate with the annular groove 6a. The end of the synchronization ring 6 near the planet carrier 9 is provided with a plurality of end face grooves 6f, and the oil holes and end face grooves 6f are alternately distributed.

[0065] The end face groove 6f and oil hole in the embodiments of this application can enhance lubrication and reduce the slippage between the end face of the synchronizing ring 6 and the annular stepped groove on the planetary carrier 9.

[0066] In some alternative embodiments: see Figure 7 and 8 As shown, this application embodiment provides a planetary auxiliary gearbox synchronizer structure. The planetary auxiliary gearbox synchronizer structure has engagement teeth 7f at both ends of the inner teeth 7c of the planetary gear ring 7 for matching with the low-gear cone ring 5 and the high-gear cone ring 11. The engagement teeth 7f are formed by milling off the ends of the inner teeth 7c.

[0067] In this embodiment, the engagement tooth 7f is integrally formed on the planetary gear ring 7 by milling, so that the internal tooth 7c of the planetary gear ring 7 has the function of meshing and matching with the low-gear cone ring 5 and the high-gear cone ring 11, realizing high and low gear meshing transmission.

[0068] In some alternative embodiments: see Figure 3 As shown, this application embodiment provides a planetary auxiliary box synchronizer structure. The housing of the planetary auxiliary box synchronizer structure includes a middle shell 3 connected to the low-end cone ring 5, and a rear shell 12 connected to the middle shell 3 and housing the high-end cone ring 11.

[0069] The planetary gear system also includes a sun gear 13 that meshes with the planet gears 8 and a hollow shaft 1 fixed to the sun gear 13. The middle shell 3 and the low-gear cone ring 5 are provided with interconnected lubricating oil passages that guide the lubricating oil into the hollow shaft 1.

[0070] In this embodiment, the low-gear cone ring 5 is fixed on the middle shell 3, and both the high-gear cone ring 11 and the low-gear cone ring 5 are located within the installation space formed by the middle shell 3 and the rear shell 12. By adopting the installation method of this application, the axial installation length is reduced, which is beneficial to reducing the volume of the rear shell 12.

[0071] Specifically, the low-end cone ring 5 of this application integrates the function of oil guiding. In conjunction with the lubrication oil circuit on the middle shell 3, it can deliver lubricating oil to the interior of the hollow shaft 1. Compared with the prior art, the oil guide seat 12' can be reduced in the axial installation direction, thus reducing the axial installation length.

[0072] In some alternative embodiments: see Figure 3As shown, this application embodiment provides a planetary auxiliary box synchronizer structure. The middle shell 3 and the hollow shaft 1 of the planetary auxiliary box synchronizer structure are rotatably connected by a bearing 10, and the low-end cone ring 5 is provided with a positioning surface of the axial positioning bearing 10.

[0073] In this embodiment, the low-profile cone ring 5 is fixed on the middle shell 3 and abuts against the bearing 10 of the fixed hollow shaft 1. That is, the low-profile cone ring 5 integrates the function of the bearing cover. Compared with the prior art, the bearing cover can be omitted in the axial installation direction, thus reducing the axial installation length.

[0074] In some alternative embodiments: see Figures 3 to 11 As shown, this application embodiment provides a planetary auxiliary gearbox synchronizer structure. The planetary gear ring 7 of the planetary auxiliary gearbox synchronizer structure is provided with at least one positioning groove 7g at both ends along its axial direction, and at least one first locking tooth 7e at both ends along its axial direction.

[0075] The synchronization ring 6 is provided with a positioning tooth 6d that matches the positioning groove 7g, and a second locking tooth 6e that cooperates with the first locking tooth 7e. The first locking tooth 7e can move relative to the second locking tooth 6e.

[0076] The first locking tooth 7e is formed by milling off the end of the internal tooth 7c on the planetary gear ring 7, and forms a locking area with the end face of the planetary gear ring 7.

[0077] When the second locking tooth 6e engages with the first locking tooth 7e, it can be engaged in the locking area, and the second locking tooth 6e can move within the locking area.

[0078] The positioning groove 7g is formed by milling off the end of the internal tooth 7c on the planetary gear ring 7; the mating surface of the first locking tooth 7e and the second locking tooth 6e along the axial direction of the planetary gear ring 7 is an inclined surface.

[0079] In summary, the planetary auxiliary gearbox synchronizer structure of this application separates the high and low gears of the auxiliary gearbox synchronizer. The low gear cone ring 5 is arranged on the left end of the planetary carrier 9 by bolts 14, and the high gear cone ring 11 is fixed to the right end of the planetary carrier 9 by splines and retaining rings. The planetary ring gear 7 integrates the functions of the internal gear and the gear sleeve 6'. The shift fork is engaged in the shift fork slot 7a. The planetary ring gear 7 moves to the left to engage the low gear and moves to the right to engage the high gear. The synchronizing rings 6 and the elastic retaining rings 15 on both sides have the same structure and are arranged symmetrically. It should be noted that during gear shifting, the planetary ring gear 7 slides relative to the planetary gears 8, but always remains engaged with the planetary gears 8.

[0080] The low-end cone ring 5 has bolt holes 5e drilled on it and is fixed to the middle shell 3 with 6 bolts 14. It has an outer cone surface 5g and meshing teeth 5f that match the engagement teeth 7f. It also integrates the functions of a bearing cover and an oil guide seat 12'.

[0081] Specifically, the low-gear cone ring 5 functions as a bearing cover, axially limiting the bearing 10 on the hollow shaft 1;

[0082] Specifically, the low-gear cone ring 5 functions as an oil guide seat 12'. Its left end face has a groove 5a, which is forged or cast. An annular oil groove 5c is machined into the inner circle. An inclined oil hole 5b connects the groove 5a and the annular oil groove 5c. Simultaneously, oil guide holes 3a and 3b are drilled from the outside of the middle shell 3 and sealed with plugs 4 to prevent oil leakage. Pressure lubricating oil passes through the oil pipe 2, the oil guide holes 3a and 3b on the middle shell 3, the groove 5a, the inclined oil hole 5b, and the annular oil groove 5c into the oil guide cup, and then into the central oil passage. The left end face 5d of the low-gear cone ring 5 is pressed tightly against the end face of the middle shell 3 to prevent oil from leaking out of the groove 5a. It should be noted that, to meet processing requirements, multiple small-diameter inclined oil holes 5b are used. The total flow cross-sectional area of ​​these multiple small-diameter inclined oil holes 5b is not less than that of the oil pipe 2 to prevent throttling.

[0083] The inner conical surface 6c of the synchronizing ring 6 is covered with carbon cloth, which mates with the outer conical surface 5g of the low-grade conical ring 5 or the outer conical surface 11a of the high-grade conical ring 11 to achieve synchronization. Multiple second locking teeth 6e and positioning teeth 6d are evenly distributed circumferentially on the outer circumference of the synchronizing ring 6, and an annular groove 6a is used to house the retaining ring 15. To enhance lubrication, an oil hole 6g is drilled at the bottom of the retaining ring groove, and an end face groove 6f is milled at one end; these two are staggered to avoid reducing the strength of the synchronizing ring 6.

[0084] The internal teeth 7c of the planetary gear ring 7 serve the dual functions of gears and engagement splines. They are formed in a single broaching operation, with engagement teeth 7f machined on both sides, featuring chamfered and tapered corners. The outer circumference of the planetary gear ring 7 has a shift fork groove 7a for shift fork positioning. A section of one of the internal teeth 7c is milled away to obtain a positioning groove 7g, which is used to install the positioning tooth 6d of the synchronizing ring 6.

[0085] The first locking tooth 7e on the planetary gear ring 7 and the second locking tooth 6e on the synchronizing ring 6 mesh. To facilitate the machining of the inclined surface of the locking tooth, a section of adjacent internal teeth 7c can be milled off to obtain a clearance groove 7d. The internal teeth 7c have a 45° slope 7b with a height of 1.5-2mm. During pre-synchronization, the elastic retaining ring 15 is compressed to generate axial thrust. Figure 7 For layout and machining purposes, the locking teeth 7j, positioning grooves 7h, and clearance grooves 7i on the high-gear side of the planetary gear ring 7 have the same parameters as those on the low-gear side, but they need to be offset by one tooth. The positioning grooves and locking teeth are evenly arranged circumferentially, and their number is divisible by the total number of internal teeth 7c, generally 3-4.

[0086] When shifting from a high gear to a low gear, the planetary gear ring 7 moves to the left. The right elastic retaining ring 15, relying on external tension, presses against the internal gear 7c, causing the right synchronizer ring 6 to move to the left as well. This separates the inner conical surface 6c of the synchronizer ring 6 from the outer conical surface 11a of the high-gear conical ring 11. Figure 5After separation, a gap 18 is created until the right synchronizing ring 6 is blocked by the planetary carrier 9. The planetary gear ring 7 continues to move to the left, generating a leftward frictional force F on the right elastic retaining ring 15. F is simultaneously transmitted to the right synchronizing ring 6 and the planetary carrier 9. Figure 3 Since there is relative rotation between the planetary carrier 9 and the right-side synchronizing ring 6, F cannot be too large, that is, the external tension of the elastic retaining ring 15 cannot be too large. It is 100-130N on the slope 7b and 10-30N on the slope 7b. The synchronizing ring 6 is provided with an end face groove 6f to facilitate oil intake and further reduce slippage with the planetary carrier 9.

[0087] When the planetary gear ring 7 moves to the left ramp 7b and contacts the trapezoidal end 15a of the left elastic retaining ring 15, as... Figure 3 The ramp 7b generates an axial force that acts on the left elastic retaining ring 15 and the left synchronous ring 6. The synchronous ring 6 presses against the low-gear cone ring 5, and the positioning tooth 6d stops rotating after being blocked by the internal tooth 7c. Figure 9 This completes the pre-synchronization ring shifting process. The oil hole 6g introduces lubricating oil into the annular groove 6a, reducing slippage between the synchronizing ring 6 and the elastic retaining ring 15 during ring shifting.

[0088] After pre-synchronization is completed, the planetary gear ring 7 continues to move until the inclined surfaces of the second locking tooth 6e and the first locking tooth 7e slide in contact. At this time, the synchronizing ring 6 cannot move and remains in the synchronization process until synchronization is completed. The frictional torque of the synchronizing ring 6 disappears, and the first locking tooth 7e pushes the left synchronizing ring 6 back half a tooth. The first locking tooth 7e passes over the second locking tooth 6e, so that the engaging tooth 7f engages with the meshing tooth 5f, completing the gear shift. Figure 10 , Figure 11 As shown, the left elastic retaining ring 15 simultaneously crosses the ramp 7b and is fully pressed into the annular groove 6a. After engaging the low gear, ensure that there is an axial clearance between the positioning teeth 6d and 7g of the left synchronizer ring 6 to prevent interference. The positioning teeth 6d and the right engagement teeth 7f on the right synchronizer ring 6 should overlap by 3-4mm to prevent the right synchronizer ring 6 from rotating to other non-working positions. The principle of shifting to a high gear is the same as that of shifting to a low gear, and will not be described in detail here.

[0089] In the description of this application, it should be noted that the terms "upper," "lower," etc., indicating the orientation or positional relationship are based on the orientation or positional relationship shown in the accompanying drawings, and are only for the convenience of describing this application and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of this application. Unless otherwise expressly specified and limited, the terms "installed," "connected," and "linked" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; 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 between two elements. For those skilled in the art, the specific meaning of the above terms in this application can be understood according to the specific circumstances.

[0090] It should be noted that in this application, relational terms such as "first" and "second" are used merely to distinguish one entity or operation from another, and do not necessarily require or imply any such actual relationship or order between these entities or operations. Furthermore, the terms "comprising," "including," or any other variations thereof are intended to cover non-exclusive inclusion, such that a process, method, article, or apparatus that comprises a list of elements includes not only those elements but also other elements not expressly listed, or elements inherent to such a process, method, article, or apparatus. Without further limitations, an element defined by the phrase "comprising one..." does not exclude the presence of other identical elements in the process, method, article, or apparatus that includes said element.

[0091] The above description is merely a specific embodiment of this application, enabling those skilled in the art to understand or implement this application. Various modifications to these embodiments will be readily apparent to those skilled in the art, and the general principles defined herein may be implemented in other embodiments without departing from the spirit or scope of this application. Therefore, this application is not to be limited to the embodiments shown herein, but is to be accorded the widest scope consistent with the principles and novel features claimed herein.

Claims

1. A planetary auxiliary box synchronizer structure, characterized in that, include: A planetary gear system, comprising a planet carrier (9) and planet gears (8) disposed on the planet carrier (9), and a planetary gear ring (7) meshing with the planet gears (8) and capable of sliding along the axial direction of the planet gears (8). The high-gear cone ring (11) is located at one end of the planetary gear (8) and is connected to the planetary carrier (9). When it is in the high gear, the planetary gear ring (7) meshes with the high-gear cone ring (11) for transmission. The low-gear cone ring (5) is located at the other end of the planetary gear (8) and is used to connect to the housing. When in the low gear, the planetary gear ring (7) meshes with the low-gear cone ring (5) for transmission. The housing includes a middle shell (3) connected to the low-end cone ring (5) and a rear shell (12) connected to the middle shell (3) and housing the high-end cone ring (11). The planetary gear system also includes a sun gear (13) meshing with the planet gear (8) and a hollow shaft (1) fixed to the sun gear (13). The middle shell (3) and the low-gear cone ring (5) are provided with interconnected lubricating oil passages that guide the hollow shaft (1) into the interior. The middle shell (3) and the hollow shaft (1) are rotatably connected by a bearing (10), and the low-end cone ring (5) is provided with a positioning surface of the axial positioning bearing (10).

2. The planetary auxiliary box synchronizer structure as described in claim 1, characterized in that: Synchronization rings (6) are respectively inserted into the planetary gear ring (7) at the positions corresponding to the high-gear cone ring (11) and the low-gear cone ring (5). A pre-synchronization component with an elastic structure is provided between the synchronization ring (6) and the planetary gear ring (7). A shift fork groove (7a) is provided on the outer ring of the planetary gear ring (7). Both sides of the planetary carrier (9) are provided with annular stepped grooves for axially limiting the synchronization ring (6).

3. The planetary auxiliary box synchronizer structure as described in claim 2, characterized in that: The planetary gear ring (7) has pre-synchronization grooves at both ends along its inner circumference, and the synchronization ring (6) has an annular groove (6a) along its outer circumference. The pre-synchronization component is an elastic retaining ring (15) set in the annular groove. The elastic retaining ring (15) is used to engage with the pre-synchronization groove when moving to generate a pre-synchronization friction torque. The pre-synchronization groove is formed by milling off the end of the internal tooth (7c) on the planetary gear ring (7). The pre-synchronization groove includes a ramp (7b) on the internal tooth (7c) and a sliding surface connecting the ramp (7b). The elastic retaining ring (15) is provided with a trapezoidal end (15a) that cooperates with the ramp (7b) and the sliding surface.

4. The planetary auxiliary box synchronizer structure as described in claim 3, characterized in that: The inner circumference of the synchronization ring (6) is provided with a plurality of oil holes (6g) that communicate with the annular groove (6a). The end of the synchronization ring (6) near the planetary carrier (9) is provided with a plurality of end face grooves (6f). The oil holes (6g) and the end face grooves (6f) are alternately distributed.

5. The planetary auxiliary box synchronizer structure as described in claim 1, characterized in that: The planetary gear ring (7) has engagement teeth (7f) at both ends of its internal teeth (7c) for matching with the low-end cone ring (5) and the high-end cone ring (11). The engagement teeth (7f) are formed by milling off the ends of the internal teeth (7c).

6. The planetary auxiliary box synchronizer structure as described in claim 2, characterized in that: The planetary gear ring (7) is provided with at least one positioning groove (7g) at both ends along its axial direction, and the planetary gear ring (7) is provided with at least one first locking tooth (7e) at both ends along its axial direction. The synchronization ring (6) is provided with a positioning tooth (6d) that matches the positioning groove (7g) and a second locking tooth (6e) that cooperates with the first locking tooth (7e). The first locking tooth (7e) can move relative to the second locking tooth (6e).

7. The planetary auxiliary box synchronizer structure as described in claim 6, characterized in that: The first locking tooth (7e) is formed by milling off the end of the internal tooth (7c) on the planetary gear ring (7) and forms a locking area with the end face of the planetary gear ring (7); When the second locking tooth (6e) engages with the first locking tooth (7e), it can be engaged in the locking area, and the second locking tooth (6e) can move within the locking area.

8. The planetary auxiliary box synchronizer structure as described in claim 6, characterized in that: The positioning groove (7g) is formed by milling off the end of the internal teeth (7c) on the planetary gear ring (7); The engagement surface of the first locking tooth (7e) and the second locking tooth (6e) along the axial direction of the planetary gear ring (7) is an inclined surface.

Images