Multi-stage planetary gear and internal transmission comprising same

Abstract

A multi-stage planetary gear and an internal transmission comprising same. The multi-stage planetary gear comprises a gear main body. The gear main body is formed by means of a mold forming process and is composed of three or more stages of gears, which are integrally formed by means of sequential coaxial arrangement from the smallest diameter to the largest diameter. The gears comprise a smallest gear at the front, a largest gear at the back, and one or more intermediate gears located between the smallest gear and the largest gear. The smallest gear and the intermediate gear have the same number of teeth but different tooth modules. The gear main body is integrally formed by means of the mold forming process, which makes production and processing quick and convenient, reduces costs, and provides excellent strength, excellent transmission strength, and a long service life.

Description

A multi-connected planetary gear and an inner transmission comprising the same

[0001] The present application claims priority to Chinese Patent Application No. 202411256307.8, filed on September 9, 2024, entitled “A Multi-connected Planetary Gear and an Inner Transmission”, Chinese Patent Application No. 202411256931.8, filed on September 9, 2024, entitled “A Clutch Seat and an Inner Transmission”, Chinese Patent Application No. 202411256586.8, filed on September 9, 2024, entitled “A Transmission Positioning Support Ring, Mandrel and Inner Transmission”, Chinese Patent Application No. 202422203331.7, filed on September 9, 2024, entitled “A Gear Shifting Mechanism and an Inner Transmission”, and Chinese Patent Application No. 202422203156.1, filed on September 9, 2024, entitled “A Pawl Control Ring, Gear Shifting Mechanism and Inner Transmission”, all of which are incorporated herein by reference in their entirety. TECHNICAL FIELD

[0002] The present application relates to the technical field of inner transmissions, and in particular to a multi-connected planetary gear and an inner transmission comprising the same. BACKGROUND

[0003] The multi-connected planetary gear of the inner transmission bears an important transmission function: when the inner transmission is shifted to different gears, the corresponding different sun gears are locked. When an external force drives the input to rotate, the planetary carrier is rotated, and the corresponding gear on the multi-connected planetary gear is rotated around the locked sun gear, thereby driving the entire multi-connected planetary gear to rotate, and the inner ring gear engaged with the multi-connected planetary gear also rotates, thereby driving the output to rotate. It should be particularly noted that the gear engaged with the inner ring gear is one of the gears on the multi-connected planetary gear, and therefore the gear on the multi-connected planetary gear needs to bear the load frequently.

[0004] However, the gears of each stage of the conventional multi-connected planetary gear of the inner transmission are not the same in number, and are produced by cutting machining, which is time-consuming and tedious, and the gear engaged with the inner ring gear is particularly prone to long-term damage, and the service life of the entire multi-connected planetary gear is short.

[0005] Therefore, it is necessary to propose a new multi-connected planetary gear and an inner transmission to solve the above problems, and to solve the problems of time-consuming and tedious production of the conventional multi-connected planetary gear of the inner transmission, the gear engaged with the inner ring gear being particularly prone to damage, and the service life of the entire multi-connected planetary gear being short. SUMMARY

[0006] Therefore, the present application aims to provide a multi-connection planetary gear and an internal gear transmission containing the same, so as to solve the problems of time-consuming and complicated production mode of conventional internal gear transmission multi-connection planetary gear, easy damage of gears meshing with the internal gear ring, and short service life of the whole multi-connection planetary gear.

[0007] To solve the above technical problems, the technical scheme used by the present application is:

[0008] In one aspect, the multi-connection planetary gear of the present application comprises a gear main body, which is composed of three or more gears by a mold forming process, and is integrally formed in the order of coaxial arrangement from small to large gear diameters; the gear comprises a smallest gear arranged at the front, a largest gear arranged at the rear, and one or more middle gears arranged between the smallest gear and the largest gear; the smallest gear and the middle gears have the same number of teeth but different gear module.

[0009] Preferably, the gear teeth of the smallest gear and the middle gears are aligned with each other.

[0010] Preferably, the third gear or more gears from the smallest gear to the largest gear have twice the number of teeth of the adjacent front gear.

[0011] Preferably, the smallest gear has the same shape as the middle gears.

[0012] Preferably, the gear module of the smallest gear and the middle gears increases in the order from large to small.

[0013] Preferably, the gear main body is a multi-connection spur gear.

[0014] Preferably, the gear further comprises a largest gear arranged at the rear of the middle gears, and the largest gear has more teeth than the remaining gears.

[0015] Further preferably, the gear teeth of the largest gear are aligned with the gear teeth of the front gears at every interval.

[0016] In another aspect, the internal gear transmission of the present application comprises the above multi-connection planetary gear.

[0017] Preferably, the internal gear transmission further comprises an internal gear ring, which meshes with the largest middle gear.

[0018] Preferably, the internal gear transmission is further provided with a clutch structure, which comprises an inner ring and an outer ring sleeved outside the inner ring, a clutch is arranged between the inner ring and the outer ring, the outer ring can be fixed relative to the inner ring or unidirectionally rotate around a rotation axis, and the clutch comprises a retainer and a return elastic member.

[0019] The clutch structure further comprises a support ring, which is arranged at one end of the inner ring inside, and is fixed relative to the inner ring, and a return elastic member is arranged between the support ring and the retainer for returning the retainer.

[0020] Further preferably, the retainer is provided with a boss, one end of the inner ring is provided with a clearance opening penetrating the outer side and the inner side of the inner ring, and the boss penetrates the clearance opening to the inside of the inner ring; one end of the return elastic member is fixed on the boss, and the other end of the return elastic member is fixed on the support ring.

[0021] More preferably, the support ring is provided with a notch penetrating the inner side and the outer side of the support ring, and the boss penetrates the notch.

[0022] More preferably, one side of the notch is provided with a stop block shielding the outer side of the boss.

[0023] More preferably, the inner side of the support ring is provided with an inwardly extending fixing block, the fixing block and the boss are each provided with a through hole, and the two ends of the return elastic member are respectively fixed on the through holes.

[0024] More preferably, the inner side of the support ring is provided with a stop edge for blocking the bearing from moving away from the inner ring in the axial direction.

[0025] More preferably, the inner side of the inner ring is provided with a recess, and the outer side of the support ring is provided with a clamping block clamped in the recess.

[0026] More preferably, the clutch further comprises a plurality of first rollers, the outer side of the inner ring is provided with a plurality of grooves matching the side surfaces of the first rollers, and the clutch is provided with an opening penetrating the clutch for accommodating the rollers; when the inner ring and the outer ring rotate relative to each other, the first rollers always rotate in the grooves.

[0027] More preferably, the clutch further comprises a plurality of second rollers, and the outer side of the inner ring is provided with a plurality of slopes corresponding to the positions of the second rollers; the retainer is distributed with a plurality of roller grooves for accommodating the second rollers, and the first rollers and the second rollers are in the same plane.

[0028] Preferably, the inner transmission comprises a mandrel, the mandrel comprises a radial slot and an axial slot, the radial slot extends along the radial direction of the mandrel on the surface of the mandrel, and the axial slot extends along the axial direction of the mandrel on the surface of the mandrel.

[0029] The inner transmission further comprises a positioning support ring, which comprises a support ring sleeved on the mandrel, the inner wall of the support ring is provided with a fixed positioning protrusion for preventing the support ring from moving axially, and the inner wall of the support ring is further provided with a positioning boss for preventing the support ring from rotating radially; the positioning protrusion is embedded in the radial slot on the mandrel; and the positioning boss is located in the axial slot on the mandrel.

[0030] Further preferably, the positioning support ring further comprises an elastic member, which is arranged in the axial slot and is used for preventing the positioning protrusion from being withdrawn from the radial slot by rotation.

[0031] More preferably, the positioning protrusion comprises a first positioning protrusion, and the first positioning protrusion is fixedly connected with the positioning boss.

[0032] More preferably, the positioning protrusion further comprises a second positioning protrusion, and a gap is left between the first positioning protrusion and the second positioning protrusion, and the gap allows the elastic member to pass through.

[0033] Further preferably, the elastic member is provided with a plug pin extending into the radial slot.

[0034] Further preferably, the plug pin extends into an adjacent radial slot of the radial slot in which the positioning protrusion is located.

[0035] Further preferably, the support ring is provided with a clearance groove on both sides for avoiding the pawl.

[0036] Preferably, the inner transmission comprises a mandrel and a pawl, and the inner transmission is provided with a shifting mechanism, the shifting mechanism comprises a pawl control ring and a first pawl seat sleeved on the mandrel, the pawl control ring is provided with an opening slot for controlling the pawl to open or retract, the first pawl seat is provided with a pawl slot for accommodating the pawl, the first pawl seat is installed at the end of the pawl control ring, and the pawl control ring can rotate around an axis relative to the first pawl seat.

[0037] Further preferably, the pawl slot comprises a locking segment for accommodating the pawl locking portion, and the position of the locking segment is staggered with the position of the outer teeth of the sun gear.

[0038] Further preferably, the pawl control ring and the first pawl seat are sleeved on the mandrel, respectively.

[0039] Further preferably, the opening slot is arranged on the inside of the pawl control ring.

[0040] Further preferably, the inner transmission further comprises a positioning key arranged in a key cavity on the mandrel, and the inner wall of the first pawl seat is provided with a key groove allowing the positioning key to pass through.

[0041] Further preferably, the first pawl seat is provided with a boss extending into the inside of the pawl control ring.

[0042] Further preferably, the first pawl seat is provided with a radial through hole near one side of the pawl control ring for accommodating the control part of the pawl.

[0043] Further preferably, the pawl control ring comprises a first control ring and a second control ring, the first control ring and the second control ring are arranged on the mandrel in axial direction, the first control ring is provided with a lever near one side of the second control ring, and the second control ring is provided with a lever slot for allowing the lever to be inserted.

[0044] Further preferably, the inner wall of the second control ring is provided with a protruding strip extending inwardly, and the protruding strip is provided with a lever slot extending through in axial direction.

[0045] Further preferably, the pawl control ring comprises a connecting rod and a control part on the connecting rod, the control part is provided with an opening slot for controlling the opening and closing of the pawl, the control part rotates with the connecting rod rotating around the mandrel, and the connecting rod comprises a front connecting rod segment and a rear connecting rod segment, the distance between the rear connecting rod segment and the center line of the rotation axis is smaller than the distance between the front connecting rod segment and the center line of the rotation axis.

[0046] Further preferably, the control part comprises a front control part and a rear control part, the front control part is arranged on the front connecting rod segment, and the rear control part is arranged on the rear connecting rod segment.

[0047] Further preferably, the rear control part is arranged at the end of the rear connecting rod segment.

[0048] Further preferably, the connecting rod is attached to the mandrel.

[0049] Further preferably, the outer side of the connecting between the rear connecting rod segment and the front connecting rod segment is provided with a recessed first step for avoiding the smallest sun gear.

[0050] Further preferably, the outer side of the connecting between the rear connecting rod segment and the front connecting rod segment is provided with a recessed second step, and the distance between the second step and the center line of the rotation axis is greater than the distance between the first step and the center line of the rotation axis.

[0051] Further preferably, the inner side of the connecting between the rear connecting rod segment and the front connecting rod segment is provided with a retracted part extending towards the mandrel, and the rear connecting rod segment extends in axial direction from the retracted part.

[0052] Alternatively, the front connecting rod segment and the rear connecting rod segment are parallel.

[0053] Further preferably, the shaft is provided with a second pawl seat for accommodating the pawl.

[0054] The beneficial effects of the present application relative to the prior art mainly include:

[0055] The present application can be molded by a mold forming process to arrange the gear bodies in a three-stage or more than three-stage gear in a coaxial manner in order from small to large gear diameters, the smallest gear has the same number of teeth as the middle gear but different tooth modules, and the production and processing are suitable for mold forming, which is convenient, fast and low in cost. The extrusion molding can obtain good strength, and during installation, the largest middle gear can be engaged with the inner gear ring of the inner variator, and since the largest middle gear has relatively large gear teeth, good transmission strength can be provided, and the service life is long.

[0056] The beneficial effects of the present application relative to the prior art mainly include:

[0057] The present application fixes the support ring and the inner ring by arranging the support ring at one end of the inner ring, and the support ring is fixed relative to the inner ring, and a return elastic member is arranged between the support ring and the retainer for retainer return, the retainer, the inner ring and the support ring are arranged from outside to inside in sequence, and the return elastic member is located inside the inner ring between the retainer and the support ring, and the overall structure reduces the axial length of the inner variator;

[0058] The positioning protrusions are embedded in the radial grooves on the mandrel, and the positioning bosses are located in the axial grooves on the mandrel, so that the support ring is fixed on the mandrel, the structure and assembly method are simple, the sun gear can stably rotate after being sleeved on the support ring, and the problems of the traditional clutch, such as easy rotation deviation of the support ring, poor stability, friction and collision between the sun gear and the pawl and the planetary gear, unsmooth shifting process and short service life, are solved. BRIEF DESCRIPTION OF DRAWINGS

[0059] The above and other objects, features and advantages of the present application will become more clearly understood from the following detailed description taken in conjunction with the accompanying drawings, in which:

[0060] Fig. 1 is a perspective view of an inner variator according to an embodiment of the present application;

[0061] Fig. 2 is a sectional view of the inner variator according to the embodiment of the present application;

[0062] Fig. 3 is a schematic diagram of a combined structure of a multi-connected planetary gear and a sun gear according to an embodiment of the present application;

[0063] Fig. 4 is a perspective view of a multi-connected planetary gear according to an embodiment of the present application;

[0064] Fig. 5 is a front view of a multi-connected planetary gear according to an embodiment of the present application;

[0065] Fig. 6 is a schematic diagram of a clutch structure according to an embodiment of the present application;

[0066] Fig. 7 is an exploded view of a clutch structure according to an embodiment of the present application;

[0067] Fig. 8 is a sectional view of a clutch structure according to an embodiment of the present application, when an inner ring and an outer ring relatively rotate;

[0068] Fig. 9 is a sectional view of a clutch structure according to an embodiment of the present application, when an inner ring and an outer ring are relatively fixed;

[0069] Fig. 10 is a schematic diagram of an inner ring according to an embodiment of the present application;

[0070] Fig. 11 is a schematic diagram of a retainer according to an embodiment of the present application;

[0071] Fig. 12 is a schematic diagram of a support ring according to an embodiment of the present application;

[0072] Fig. 13 is a schematic diagram of a combined structure of a support ring, an elastic member and a mandrel according to an embodiment of the present application;

[0073] Fig. 14 is an exploded view of a support ring, an elastic member and a mandrel according to an embodiment of the present application;

[0074] Fig. 15 is a schematic diagram of a combined structure of a support ring, an elastic member and a mandrel according to an embodiment of the present application, from another perspective;

[0075] Fig. 16 is a schematic diagram of a combined structure of a support ring, an elastic member, a mandrel, a pawl and a pawl control ring according to an embodiment of the present application;

[0076] Fig. 17 is a schematic diagram of a support ring according to an embodiment of the present application;

[0077] Fig. 18 is a schematic diagram of an elastic member according to an embodiment of the present application;

[0078] Fig. 19 is a schematic diagram of a combined structure of a pawl control ring, a pawl seat, a pawl and a mandrel according to an embodiment of the present application;

[0079] Fig. 20 is an exploded view of a pawl control ring, a pawl seat, a pawl and a mandrel according to an embodiment of the present application;

[0080] Fig. 21 is a schematic view of a combination structure of a second control ring, a pawl seat and a pawl according to an embodiment of the present application;

[0081] Fig. 22 is an exploded view of a combination structure of a second control ring, a pawl seat and a pawl according to an embodiment of the present application;

[0082] Fig. 23 is a schematic view of a combination structure of a second control ring, a pawl seat and a pawl according to an embodiment of the present application from another perspective;

[0083] Fig. 24 is an exploded view of a combination structure of a second control ring, a pawl seat and a pawl according to an embodiment of the present application from another perspective;

[0084] Fig. 25 is a sectional view of an inner transmission according to an embodiment of the present application;

[0085] Fig. 26 is an enlarged view of A in Fig. 25;

[0086] Fig. 27 is a perspective view of a shift mechanism according to an embodiment of the present application;

[0087] Fig. 28 is an exploded view of a shift mechanism according to an embodiment of the present application;

[0088] Fig. 29 is a perspective view of a pawl control ring according to an embodiment of the present application;

[0089] Fig. 30 is a side view of a pawl control ring according to an embodiment of the present application;

[0090] 100-spindle; 200-pawl, 210-locking portion, 220-pawl control portion; 300-gear body, 310-gear, 311-smallest gear, 312-middle gear, 313-largest gear; 400-pawl control ring, 411-first control ring, 412-second control ring, 413-pull lever, 414-rod groove, 415-ridge; 410-control portion, 416-front control portion, 417-rear control portion; 420-link, 421-link front section, 422-link rear section, 423-first step, 424-second step, 425-retraction portion, 426-connection portion; 500-shifting assembly, 520-sun gear, 530-planetary gear, 540-input, 550-carrier, 560-clutch, 570-inner ring gear, 580-output, 590-bearing; 1-inner ring, 10-recess, 11-clearance, 12-recess, 13-groove, 14-slope; 2-outer ring; 3-support ring, 30-bump, 31-gap, 32-stop block, 33-fixed block, 34-stop edge, 35-clamping block; 4-retainer, 41-boss, 42-step, 43-opening, 44-roller groove; 5-return elastic member, 50-through hole; 6-first roller, 7-second roller; 8-support ring, 110-clearance groove, 120-radial groove, 130-axial groove; 9-positioning bump, 91-first positioning bump, 92-second positioning bump; 15-positioning boss; 16-elastic member, 161-latch; 20-opening groove, 21-key groove, 22-boss, 23-clearance, 24-pawl groove; 40-second pawl seat, 50-first pawl seat, 60-positioning key. DETAILED DESCRIPTION

[0091] The technical solutions of the present application will be further described in detail below in combination with the drawings and specific embodiments, so that those skilled in the art can better understand the present application and implement it. However, the embodiments are not intended to limit the present application. In the embodiments, it should be understood that the terms "longitudinal", "transverse", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer" and the like indicate the orientation or positional relationship shown in the drawings, and are only used for the purpose of describing the present application, and do not indicate or imply that the devices or elements referred to must have a particular orientation, be constructed and operated in a particular orientation, and therefore cannot be understood as limiting the present application.

[0092] It is to be understood that when a component is referred to as being "connected" to another component, it can be directly connected to the other component, or intervening components can be present. The terms "mounting", "one end", "the other end" and the like are used herein for the purpose of explanation only.

[0093] Referring to Figs. 1 to 5, a multiple planetary gear comprises a gear body 300 which is composed of three or more gears 310 by a mold forming process, and is integrally formed in the order of the gear diameters from small to large. The gear 1 comprises a smallest gear 311 at the front, a largest gear 313 at the rear, and one or more intermediate gears 312 between the smallest gear 311 and the largest gear 313. The smallest gear 311 and the intermediate gears 312 have the same number of teeth but different tooth modules.

[0094] The multiple planetary gear of the embodiment is suitable for mold forming, and is convenient, fast and low in cost. The extrusion forming has good strength. During installation, the largest intermediate gear 312 is engaged with the inner ring gear 570 of the inner transmission. Since the largest intermediate gear 312 has large teeth, good transmission strength is provided, and the service life is long.

[0095] Specifically, during use, the shift assembly 500 is operated to drive the pawl control ring to control the opening and closing of the pawls 200 on the core shaft 100. When the pawls 200 are closed, the sun gears 520 and the multiple planetary gears are free to rotate. When the input member 540 inputs torque, the torque is first transmitted to the planet carrier 550, and then the clutch 560 is engaged to synchronize the rotation of the planet carrier 550 and the inner ring gear 570. The torque of the planet carrier 550 is transmitted to the inner ring gear 570, and then output to the wheels through the output member 580. At this time, the inner transmission does not change speed through the planetary gear mechanism.

[0096] When the pawls 200 are open, one of the sun gears 520 is locked. When the input member 540 inputs torque, the torque is first transmitted to the planet carrier 550, and then the planet carrier 550 rotates to drive the multiple planetary gears to rotate. One of the sun gears 520 is engaged with the multiple planetary gears, and the largest intermediate gear 312 is engaged with the inner ring gear 570. Since the largest intermediate gear 312 has large teeth, good transmission strength is provided, and the service life is long. Since the rotation speed of the inner ring gear 570 is higher than that of the planet carrier 550, the clutch 560 is separated, and the torque of the inner ring gear 570 is output to the wheels through the output member 580. At this time, the inner transmission changes speed through the planetary gear mechanism.

[0097] The teeth of the smallest gear 311 are aligned with the teeth of the middle gear 312. This facilitates the integrated molding process.

[0098] The third gear or more than three gears, from the smallest gear to the largest gear, have twice the number of teeth of the adjacent previous gear. This facilitates the design of the number of teeth.

[0099] The smallest gear 311 has the same shape as the middle gear 312.

[0100] The gear modulus of the smallest gear 311 and the middle gear 312 increases from large to small. This ensures that the largest middle gear 312 can obtain high strength.

[0101] The gear body 300 is a multi-connected spur gear. This facilitates the integrated molding process.

[0102] The gear 310 also includes a largest gear 313 located behind the middle gear 312, which has more teeth than the rest of the gears 310. This allows the corresponding smallest sun gear 520 to be made smaller, and because the largest middle gear 312 engages with the inner ring gear 570, the largest gear 313 can protrude outside the edge of the inner ring gear 570, making it more compact.

[0103] The teeth of the largest gear 313 are aligned with the teeth of the gear 310 in front of it at intervals. This facilitates the integrated molding process.

[0104] In addition, an inner transmission is also provided, which includes the above-mentioned multi-connected planetary gear.

[0105] In a preferred embodiment, the inner transmission also includes an inner ring gear 570 that engages with the largest middle gear 312.

[0106] In another preferred embodiment, as shown in FIGS. 6-12, the inner transmission is also provided with a clutch structure, which includes an inner ring 1 and an outer ring 2 sleeved outside the inner ring 1, a clutch 560 is arranged between the inner ring 1 and the outer ring 2, the outer ring 2 can be fixed relative to the inner ring 1 or unidirectionally rotate around the rotation axis, the clutch 560 includes a retainer 4 and a return spring 5, the clutch structure also includes a support ring 3, which is arranged at one end of the inner ring 1, the support ring 3 is fixed relative to the inner ring 1, and the return spring 5 is arranged between the support ring 3 and the retainer 4 for returning the retainer 4. The retainer 4, the inner ring 1, and the support ring 3 are arranged from outside to inside in sequence, and the return spring 5 is located between the retainer and the support ring, which reduces the axial length of the inner transmission.

[0107] Preferably, the support ring 3 and the inner ring 1 are interlocked by a protrusion 30 and a recess 10 to prevent the support ring 3 from rotating around the axis and moving towards the inner ring.

[0108] In use, the bearing 590 is sleeved in the support ring 3, and the bearing 590 indirectly supports the inner ring 1 through the support ring 3. Since the support ring 3 and the inner ring 1 are mutually embedded through the protrusion 30 and the notch 10, the support ring 3 can be prevented from rotating around the axis direction and moving the inner ring 1 towards the inner ring direction. The inner ring 1 is more stable during rotation and will not deviate, and the rotation is smooth.

[0109] Specifically, in the first gear, the pawl on the mandrel 100 is retracted, and the corresponding sun gear 520 and planetary gear 530 are free to rotate. When the input member 540 inputs the torque, it first passes through the inner ring 1, and the rotation speed of the inner ring 1 is higher than that of the outer ring 2. Then the clutch 560 is engaged, so that the rotation speed of the inner ring 1 is synchronized with that of the outer ring 2. The torque of the inner ring 1 is transmitted to the outer ring 2, and then output to the wheel through the output member 580. At this time, the inner transmission does not change speed through the planetary gear mechanism.

[0110] In other gears, one of the sun gears 520 is locked. When the input member 540 inputs the torque, it first passes through the inner ring 1, and the inner ring 1 rotates to drive the planetary gear 530 to rotate. One of the sun gears 520 is engaged with the planetary gear 530, so that the rotation speed of the outer ring 2 is higher than that of the inner ring 1. At this time, the clutch 560 is separated, so that the torque of the outer ring 2 is output to the wheel through the output member 580. At this time, the inner transmission changes speed through the planetary gear mechanism.

[0111] Preferably, the notch 10 is arranged on the edge of the inner ring 1, and the protrusion 30 is arranged on the side of the support ring 3 away from the inner ring 1.

[0112] The clutch 560 includes a retainer 4 and a return spring 5. The retainer 4 is provided with a boss 41, and the inner ring 1 is provided with a clearance 11 penetrating the inner and outer sides of the inner ring 1. The boss 41 penetrates the clearance 11 to the inside of the inner ring 1. One end of the return spring 5 is fixed on the boss 41, and the other end of the return spring 5 is fixed on the support ring 3. The clearance 11 can allow the boss 41 to penetrate into the inner ring 1 to hide the boss 41, and can provide rotation space for the boss 41 when the retainer 4 rotates relative to the inner ring. The return spring 5 provides a pre-tightening force for the clutch 560 to avoid the clutch 560 from being out of working condition. Preferably, the return spring 5 is a tension spring.

[0113] The support ring 3 is provided with a gap 31 penetrating the inner and outer sides of the support ring 3, and the boss 41 penetrates the gap 31. The gap 31 can further provide rotation space for the boss 41 when the retainer 4 rotates relative to the inner ring.

[0114] One side of the gap 31 is provided with a block 32 shielding the outer side of the boss 41. The block 32 can further hide the return spring 5, and can isolate the return spring 5 and other components from each other without interfering with each other.

[0115] The boss 41 is provided with a step 42 for avoiding the block 32. The step 42 can further provide the boss 41 with a rotating space when the retainer 4 rotates relative to the inner ring.

[0116] The inner side of the support ring 3 is provided with an inwardly extending fixing block 33. The fixing block 33 and the boss 41 are each provided with a through hole 50. The two ends of the return elastic member 5 are fixed on the through holes 50 respectively. The through hole 50 can provide a fixing position for the tension spring.

[0117] The inner side of the support ring 3 is provided with a stop edge 34 for blocking the bearing from moving away from the inner ring 1 in the axial direction. The stop edge 34 can block the bearing from moving away from the inner ring 1 in the axial direction, so that the position of the components is more stable, and the shift and vibration collision is avoided, and the rotation smoothness and service life are improved.

[0118] The inner side of the inner ring 1 is provided with a recess 12, and the outer side of the support ring 3 is provided with a clamping block 35 clamped in the recess 12. In this way, the axial relative movement between the inner ring 1 and the support ring 3 can be further avoided, and the relative position is more stable.

[0119] The clutch 560 further comprises a plurality of first rollers 6. The outer side of the inner ring 1 is provided with a plurality of grooves 13 matching the side surfaces of the first rollers 6. The clutch 560 is provided with an opening 43 penetrating the clutch 560 for accommodating the rollers. When the inner ring 1 and the outer ring 2 rotate relative to each other, the first rollers 6 always rotate in the grooves 13. The first rollers 6 and the grooves 13 form a bearing, which does not interfere with the clutching action of the clutch 560. In this way, the clutch and the bearing can be integrated, the axial space of the inner transmission is saved, and it is not necessary to be designed into two rows. The bearing part can make the concentricity between the clutch, the inner ring 1 and the outer ring 2 higher.

[0120] The clutch 560 further comprises a plurality of second rollers 7, a plurality of slopes 14 corresponding to the positions of the second rollers 7 on the outer side of the inner ring 1, and a plurality of roller grooves 44 accommodating the second rollers 7 on the retainer 4. When the rotational speed of the inner ring 1 is higher than that of the outer ring 2, the second rollers 7 move towards the slopes 14, so that the second rollers 7 are pressed by the slopes 14 and the outer ring 2, so that the torque is transmitted from the inner ring 1 to the outer ring 2 through the second rollers 7, and the outer ring 2 rotates at the same speed as the inner ring 1.

[0121] The first rollers 6 and the second rollers 7 are in the same plane. In this way, the axial space of the inner transmission can be further saved.

[0122] In the transmission structure, the inner ring 1 is a planet carrier, and the outer ring 2 is an inner ring gear.

[0123] The embodiment of the present application sets the support ring at one end of the inner ring, and fixes the support ring and the inner ring, so that the support ring is fixed relative to the inner ring, and sets the return elastic member between the support ring and the retainer for the return of the retainer, and the retainer, the inner ring and the support ring are arranged from outside to inside, and the return elastic member is located inside the inner ring between the retainer and the support ring, so that the overall structure reduces the axial length of the inner transmission.

[0124] In another preferred embodiment, as shown in Figs. 13 to 18, the inner transmission comprises a mandrel 100, the mandrel 100 comprises radial grooves 120 and axial grooves 130, the radial grooves 120 extend along the mandrel 100 radially on the surface of the mandrel 100, and the axial grooves 130 extend along the mandrel 100 axially on the surface of the mandrel 100;

[0125] The inner transmission further comprises a positioning support ring, the positioning support ring comprises a support ring 8 sleeved on the mandrel 100, the inner wall of the support ring 8 is provided with fixed positioning protrusions 9 for preventing the support ring 8 from moving axially, and the inner wall of the support ring 8 is further provided with a positioning boss 15 for preventing the support ring 8 from rotating radially; the positioning protrusions 9 are embedded in the radial grooves 120 on the mandrel 100; the positioning boss 15 is located in the axial groove 130 on the mandrel 100, and the support ring 8 is thereby fixed on the mandrel 100, and the structure and assembly method are simple, and the sun gear 520 can stably rotate after being sleeved on the support ring 8.

[0126] The present application sets the fixed positioning protrusions 9 for preventing the support ring 8 from moving axially on the inner wall of the support ring, and further sets the positioning boss 15 for preventing the support ring 8 from rotating radially on the inner wall of the support ring, embeds the positioning protrusions 9 in the radial grooves 120 on the mandrel 100, and locates the positioning boss 15 in the axial groove 130 on the mandrel 100, so as to fix the support ring 8 on the mandrel 100, and the structure and assembly method are simple, and the sun gear 520 can stably rotate after being sleeved on the support ring 8, thereby solving the problems of the traditional clutch, such as easy rotation and deviation of the support ring, poor stability, friction and collision between the sun gear and the pawl and the planetary gear, unsmooth transmission process and short service life.

[0127] Specifically, in use, the shift assembly 500 is operated to drive the pawl control ring 400 to control the opening and closing of the pawl 200 on the mandrel 100. When the pawl 200 is retracted, the sun gear 520 and the planetary gear 530 are free to rotate, the support ring 8 supports the sun gear 520, and the sun gear 520 rotates smoothly in a stable position. When the input member 540 inputs the torque, it first passes through the planet carrier 550, the rotation speed of the planet carrier 550 is higher than that of the inner ring 570, then the clutch 560 is engaged to synchronize the rotation speed of the planet carrier 550 and the inner ring 570, the torque of the planet carrier 550 is transmitted to the inner ring 570, and the inner ring 570 outputs the torque to the wheels through the output member 580. At this time, the inner transmission does not pass through the planetary gear mechanism for transmission.

[0128] When the pawl 200 is opened, one of the sun gears 520 is locked, and when the input member 540 inputs torque, the torque first passes through the planet carrier 550, and the planet carrier 550 rotates to drive the planet gears 530 to rotate, one of the sun gears 520 meshes with the planet gears 530, the support ring 8 supports the sun gear 520, the sun gear 520 rotates smoothly in a stable position, the combination and transmission between the sun gear 520, the pawl 200 and the planet gears 530 are more smooth, the rotation speed of the inner ring gear 570 is higher than that of the planet carrier 550, at this time, the clutch 560 is separated, and the torque of the inner ring gear 570 is output to the wheels through the output member 580. At this time, the inner transmission is speed-changed through the planet gear mechanism.

[0129] Further comprising an elastic member 16 arranged in the axial groove 130, used to prevent the positioning block 9 from being rotated out of the radial groove 120. The elastic member 16 can apply pressure to the positioning boss 15 and the inner wall of the axial groove 130 away from the positioning boss 15, so that the positioning boss 15 is pressed against the inner wall of the axial groove 130, further preventing the positioning block 9 from being rotated out of the radial groove 120, thereby further fixing the position of the support ring 8; at the same time, the support ring 8 and the inner wall of the axial groove 130 jointly define the position of the elastic member 16, preventing the elastic member 16 from rotating radially.

[0130] The positioning block 9 comprises a first positioning block 91 fixedly connected with the positioning boss 15. In this way, the first positioning block 91 can be embedded in the radial groove 120 close to the positioning boss 15.

[0131] The positioning block 9 further comprises a second positioning block 92, and a gap is left between the first positioning block 91 and the second positioning block 92, allowing the elastic member 16 to pass through. In this way, the radial grooves 120 on both sides of the axial groove 130 can be respectively embedded with the first positioning block 91 and the second positioning block 92.

[0132] Preferably, the radial groove in which the second positioning block 92 is located has a groove seat that can pass through the gap, facilitating the installation of the support ring 8 on the mandrel 100.

[0133] The elastic member 16 is provided with a plug 161 extending into the radial groove. In this way, the axial movement of the elastic member 16 can be prevented, further preventing the positioning block 9 from being rotated out of the radial groove 120, thereby further fixing the position of the support ring 8.

[0134] The plug 161 extends into an adjacent radial groove 120 located at the radial groove in which the positioning block 9 is located. In this way, an embedding space can be provided for the positioning block 9 to be embedded in the radial groove 120, and the installation of the elastic member is facilitated.

[0135] The support ring 8 is provided with a gap slot 110 on both sides to avoid the pawl 200, so that the support ring 8 can provide a support space for the sun gear 520 and an activity space for the pawl 200, thereby reducing the axial space of the inner transmission, and the groove seat where the radial groove 120 is located can also support the support ring 8.

[0136] In another preferred embodiment, as shown in FIGS. 19 to 24, the inner transmission comprises a mandrel 100, a pawl 200, and a shifting mechanism, wherein the shifting mechanism comprises a pawl control ring 400 and a first pawl seat 50 sleeved on the mandrel 100, the pawl control ring 400 is provided with an opening slot 20 for controlling the opening or closing of the pawl 200, the first pawl seat 50 is provided with a pawl slot 24 for accommodating the pawl 200, the first pawl seat 50 is installed at the end of the pawl control ring 400, and the pawl control ring 400 can rotate relative to the first pawl seat 50 around an axis. The independent first pawl seat 50 at the end can provide an installation position for the pawl control ring 400, so that the pawl control ring 400 can not only control the pawl 200, but also support the smallest sun gear 520, and the sun gear 520 does not need to wrap the pawl 200, the first pawl seat 50, and the pawl control ring 400 at the same radial position at the same time, so that the sun gear 520 can obtain a smaller size, the corresponding planetary gear 530 can obtain a larger space, the gear shifting range can be larger, the radial space of the entire inner transmission can be smaller, the demand for smaller and more gear shifting can be met, and the mandrel 100 also does not need to be reduced in diameter, and the strength and safety are still guaranteed.

[0137] Specifically, in use, the shifting assembly 500 is operated to drive the pawl control ring 400 to control the opening and closing of the pawl 200 on the mandrel 100. When the pawl 200 is closed, the sun gear 520 and the planetary gear 530 rotate freely, and at this time, the pawl control ring 400 also supports the sun gear 520. When the input member 540 inputs a torque, the torque first passes through the planet carrier 550, the rotation speed of the planet carrier 550 is higher than that of the inner ring 570, then the clutch 560 is engaged, the rotation speed of the planet carrier 420 is synchronized with that of the inner ring 570, the torque of the planet carrier 550 is transmitted to the inner ring 570, and the inner ring 570 outputs the torque to the wheels through the output member 580. At this time, the inner transmission does not shift through the planetary gear mechanism.

[0138] When the pawl control ring 400 controls the pawl 200 to open, the sun gear 520 is locked, and at this time, the pawl control ring 400 also supports the sun gear 520. When the input member 540 inputs a torque, the torque first passes through the planet carrier 550, the planet carrier 550 rotates to drive the planetary gear 530 to rotate, the sun gear 520 meshes with the planetary gear 530, the rotation speed of the inner ring 570 is higher than that of the planet carrier 550, at this time, the clutch 560 is separated, the torque of the inner ring 570 is output to the wheels through the output member 580. At this time, the inner transmission shifts through the planetary gear mechanism.

[0139] The pawl slot 24 includes a locking section that accommodates the locking portion 210 of the pawl 200, and the position of the locking section is staggered with the position of the outer teeth of the sun gear. This can further ensure that the position of the outer teeth of the sun gear 520 does not need to be left out to wrap the pawl 200, and only other positions of the sun gear 520 need to be wrapped, so that the sun gear 520 can obtain a smaller radial dimension.

[0140] The pawl control ring 400 and the first pawl seat 50 are respectively sleeved on the mandrel 100.

[0141] The open slot 20 is arranged on the inner side of the pawl control ring 400, so that the outer surface of the pawl control ring 400 is smooth, and the sun gear 520 can be conveniently supported.

[0142] The positioning key 60 arranged in the key cavity on the mandrel 100, and the inner wall of the first pawl seat 50 is provided with a key groove 21 allowing the positioning key 60 to pass through. This can prevent the first pawl seat 50 from rotating radially, and the pawl 200 can be stably installed.

[0143] The first pawl seat 50 is provided with a boss 22 extending into the interior of the pawl control ring 400. The boss 22 can improve the concentricity of the first pawl seat 50 and the pawl control ring 400, the rotation is more stable, and the rotation angle of the pawl control ring 400 is limited to avoid unnecessary control due to excessive rotation.

[0144] The side of the first pawl seat 50 close to the pawl control ring 400 is provided with a radial through gap 23 for accommodating the control claw portion 220 of the pawl 200. This can make the first pawl seat 50 and the components more closely integrated, improve the integration, and facilitate miniaturization.

[0145] The pawl control ring 400 includes a first control ring 411 and a second control ring 412, the first control ring 411 and the second control ring 412 are sleeved on the mandrel 100 and arranged in the axial direction of the mandrel 100, the side of the first control ring 411 close to the second control ring 412 is provided with a lever 413, and the second control ring 412 is provided with a lever groove 414 allowing the lever 413 to be inserted. This can allow the second control ring 412 controlling the smallest sun gear 520 to be manufactured and installed separately, facilitating production and installation.

[0146] The inner wall of the second control ring 412 is provided with an inwardly extending protrusion 415, and the protrusion 415 is provided with a lever groove 414 penetrating in the axial direction. The protrusion 415 can cooperate with the boss 22 to limit the rotation amplitude, and also form the lever groove 414.

[0147] In a further preferred embodiment, as shown in FIGS. 25 to 30, the pawl control ring comprises a connecting rod 420 and a control portion 410 on the connecting rod 420, the control portion 410 is provided with an opening slot 20 for controlling the opening and closing of the pawl 200, the control portion 410 rotates with the connecting rod 420 rotating around the core shaft 100, the connecting rod 420 comprises a connecting rod front section 421 and a connecting rod rear section 422, the distance between the connecting rod rear section 422 and the center line of the rotation shaft is smaller than the distance between the connecting rod front section 421 and the center line of the rotation shaft. By dividing the connecting rod 420 into the connecting rod front section 421 and the connecting rod rear section 422, and setting the distance between the connecting rod rear section 422 and the center line of the rotation shaft to be smaller than the distance between the connecting rod front section 421 and the center line of the rotation shaft, space is left for the sun gear 520 at the end, especially the smallest sun gear, so as to realize the miniaturization of the sun gear 520, and the space of the corresponding planetary gear 530 and the number of gear shifting stages are relatively increased, the radial space occupied by the entire inner transmission is reduced, the demand for smaller and more stages of shifting is met, and the problem that the traditional pawl control ring has a straight connecting rod, which causes the sun gear, especially the smallest sun gear, to be unable to be miniaturized, the space of the corresponding planetary gear to be limited, the number of gear shifting stages to be limited, the entire inner transmission to occupy a larger radial space, and the demand for smaller and more stages of shifting to be met is solved.

[0148] Specifically, in use, the shifting assembly 500 is connected with the connecting portion 426 on the pawl control ring, the shifting assembly 500 is operated to drive the connecting rod 420 of the pawl control ring, the control portion 410 rotates with the connecting rod 420 rotating around the core shaft 100, and the opening slot 20 controls the opening and closing of the pawl 200 on the core shaft 100. The distance between the connecting rod rear section 422 and the center line of the rotation shaft is smaller than the distance between the connecting rod front section 421 and the center line of the rotation shaft, the control portion 410 on the connecting rod rear section 422 is close to the center line of the rotation shaft, the sun gear 520 at this position can be set to be smaller, and the radial distance difference between the connecting rod front section 421 and the connecting rod rear section 422 forms a force arm, the control of the pawl 200 at the connecting rod rear section 422 is more labor-saving.

[0149] When the pawl 200 is retracted, the sun gear 520 and the planetary gear 530 are free to rotate. After the input member 540 inputs torque, the torque first passes through the planet carrier 550, the rotation speed of the planet carrier 550 is higher than that of the inner ring gear 570, then the clutch 560 is engaged, the rotation speed of the planet carrier 550 is synchronized with that of the inner ring gear 570, the torque of the planet carrier 550 is transmitted to the inner ring gear 570, and the inner ring gear 570 outputs the torque to the wheels through the output member 580. At this time, the inner transmission does not shift through the planetary gear mechanism.

[0150] When the pawl control ring controls the pawl 200 to open, the sun gear 520 is locked. When the input member 540 inputs torque, the torque first passes through the planet carrier 550, the planet carrier 550 rotates to drive the planet gear 530 to rotate, the sun gear 520 meshes with the planet gear 530, so that the rotation speed of the inner ring gear 570 is higher than that of the planet carrier 550, at this time the clutch 560 is separated, so that the torque of the inner ring gear 570 is output to the wheel through the output member 580. At this time, the inner transmission is speed-changed through the planetary gear mechanism.

[0151] The control part 410 includes a front control part 416 and a rear control part 417, the front control part 416 is arranged on the front section 421 of the connecting rod, and the rear control part 417 is arranged on the rear section 422 of the connecting rod. In this way, different control parts are arranged in front and back, different sizes of sun gears 520 can be flexibly arranged, and more gear shifting stages can be arranged.

[0152] The rear control part 417 is arranged at the end of the rear section 422 of the connecting rod. In this way, the control of the smallest sun gear 520 can be realized at the end of the connecting rod 420, and the connecting rod 420 is fully utilized.

[0153] The connecting rod 420 is attached to the mandrel 100. In this way, the space occupied in the radial direction can be smaller.

[0154] The outer side of the connecting part between the rear section 422 and the front section 421 of the connecting rod is provided with a recessed first step 423 for avoiding the smallest sun gear 520. In this way, the connecting rod 420 occupies smaller space, and the space occupied in the radial direction can be further smaller.

[0155] The outer side of the connecting part between the rear section 422 and the front section 421 of the connecting rod is provided with a recessed second step 424, and the distance between the second step 424 and the center line of the rotating shaft is greater than the distance between the first step 423 and the center line of the rotating shaft. In this way, more sun gears 520 can be avoided.

[0156] The inner side of the connecting part between the rear section 422 and the front section 421 of the connecting rod is provided with an inwardly recessed part 425 extending towards the mandrel 100, so that the rear section 422 of the connecting rod extends along the axis direction from the inwardly recessed part 425. The inwardly recessed part 425 can be attached to the part of the mandrel 100 that is reduced in the radial direction, and the space occupied in the radial direction can be further smaller.

[0157] The front section 421 and the rear section 422 of the connecting rod are parallel, so that the connecting rod 420 can be more attached to the mandrel 100, and the inner ring of the sun gear 520 can be flat and stable. The mandrel 100 is provided with a second pawl seat 40 for accommodating the pawl 200.

[0158] In this specification, unless otherwise explicitly specified and limited, a first feature is "on", "above", or "under" a second feature can mean that the first and second features are directly in contact, or that the first and second features are indirectly in contact through an intermediate medium. Also, the first feature "over", "above", and "on top of" the second feature can mean that the first feature is directly above or obliquely above the second feature, or simply means that the first feature is horizontally higher than the second feature. The first feature "under", "below", and "underneath" the second feature can mean that the first feature is directly below or obliquely below the second feature, or simply means that the first feature is horizontally lower than the second feature.

[0159] In the description of the specification, the description of the terms "preferred embodiment", "further embodiment", "other embodiment", or "specific example" and the like means that the specific features, structures, materials or characteristics described in connection with the embodiment or example are included in at least one embodiment or example of the present application. In the specification, the illustrative description of the above terms does not necessarily refer to the same embodiment or example. Also, the specific features, structures, materials or characteristics described can be combined in any appropriate manner in any one or more embodiments or examples. Furthermore, the person skilled in the art can combine and combine the different embodiments or examples described in the specification and the features of the different embodiments or examples, without contradiction.

[0160] Although the embodiments of the present application have been shown and described above, it is understood that the above-described embodiments are exemplary and are not to be construed as limiting the present application, and those skilled in the art can make changes, modifications, replacements and variations to the above-described embodiments within the scope of the present application.

Claims

1. A multi-row planetary gear comprising a gear body composed of three or more gears by a die forming process, and the gears are sequentially arranged in the same axis from small to large in gear diameter, characterized in that: The gear comprises a minimum gear arranged at the front, a maximum gear arranged at the rear, and one or more intermediate gears arranged between the minimum gear and the maximum gear, the minimum gear and the intermediate gears have the same number of teeth but different tooth modules.

2. The multi-row planetary gear according to claim 1, characterized in that: The teeth of the minimum gear and the teeth of the intermediate gears are aligned with each other.

3. A multi-row planetary gear according to claim 1 or 2, characterized in that: The third gear or the third or more gears from the minimum gear to the maximum gear have twice the number of teeth of the adjacent front gear.

4. The multi-row planetary gear according to claim 1, characterized in that: The minimum gear has the same shape as the intermediate gears.

5. The multi-row planetary gear according to claim 1, characterized in that: The gear modules of the minimum gear and the intermediate gears increase from large to small.

6. The multi-row planetary gear according to claim 1, characterized in that: The gear body is a multi-connected spur gear.

7. The multi-row planetary gear according to claim 1, characterized in that: The gear further comprises a maximum gear arranged at the rear of the intermediate gears, the maximum gear has more teeth than the other gears.

8. The multi-row planetary gear according to claim 7, characterized in that: The teeth of the maximum gear are aligned with the teeth of the front gears at every interval.

9. A transfer case characterized by: The multi-connected planetary gear comprises any one of claims 1 to 8.

10. The powershift transmission according to claim 9, characterized in that: The inner gear ring is engaged with the maximum intermediate gear.

11. The range extender according to claim 9, characterized in that: The inner transmission further comprises a clutch structure, the clutch structure comprises an inner ring and an outer ring sleeved outside the inner ring, a clutch is arranged between the inner ring and the outer ring, the outer ring is fixed relative to the inner ring or rotates unidirectionally around a rotation axis, the clutch comprises a retainer and a return spring; The clutch structure further comprises a support ring, the support ring is arranged at one end inside the inner ring, the support ring is fixed relative to the inner ring, and a return spring is arranged between the support ring and the retainer for returning the retainer.

12. The powershift transmission according to claim 11, characterized in that: The retainer is provided with a boss, one end of the inner ring is provided with a clearance opening penetrating the inner ring outside and inside, the boss penetrates the clearance opening to the inside of the inner ring, one end of the return spring is fixed on the boss, and the other end of the return spring is fixed on the support ring.

13. The powershift transmission according to claim 12, characterized in that: The support ring is provided with a notch penetrating the inside and outside of the support ring, and the boss penetrates the notch.

14. The powershift transmission according to claim 13, characterized in that: One side of the notch is provided with a stop block shielding the outside of the boss.

15. The powershift transmission of claim 12, characterized by: The inside of the support ring is provided with a fixed block extending inwardly, the fixed block and the boss are respectively provided with through holes, and the two ends of the return spring are respectively fixed on the through holes.

16. The powershift transmission of claim 12, characterized by: The inside of the support ring is provided with a stop edge for blocking the bearing from moving away from the inner ring in the axial direction.

17. The powershift transmission of claim 12, characterized by: The inside of the inner ring is provided with a recess, and the outside of the support ring is provided with a clamping block clamped in the recess.

18. The powershift transmission according to any one of claims 12 to 17, characterized in that: The clutch further comprises a plurality of first rollers, the outside of the inner ring is provided with a plurality of grooves matching the side surfaces of the first rollers, and the clutch is provided with an opening penetrating the clutch for accommodating the rollers.

19. The range extender according to claim 18, characterized in that: The clutch further comprises a plurality of second rollers and a plurality of slopes on the outside of the inner ring corresponding to the positions of the second rollers, the retainer is distributed with a plurality of roller grooves for accommodating the second rollers, and the first rollers and the second rollers are in the same plane.

20. The internal gearbox according to claim 9 or 10, comprising a mandrel, characterized in that: The mandrel comprises a radial groove and an axial groove, the radial groove extends along the radial direction of the mandrel on the surface of the mandrel, and the axial groove extends along the axial direction of the mandrel on the surface of the mandrel. The inner transmission further comprises a positioning support ring, which comprises a support ring sleeved on the mandrel, the inner wall of the support ring is provided with a fixed positioning protrusion preventing the support ring from moving axially, and the inner wall of the support ring is further provided with a positioning boss preventing the support ring from rotating radially; the positioning protrusion is embedded in the radial groove on the mandrel; and the positioning boss is located in the axial groove on the mandrel.

21. The range extender according to claim 20, characterized in that: Further comprising an elastic member, which is arranged in the axial groove and is used to prevent the positioning protrusion from being withdrawn from the radial groove by rotation.

22. The powershift transmission of claim 21, characterized by: The positioning protrusion comprises a first positioning protrusion, which is fixedly connected with the positioning boss.

23. The range extender of claim 22, characterized in that: The positioning protrusion further comprises a second positioning protrusion, and a gap is left between the first positioning protrusion and the second positioning protrusion, which allows the elastic member to pass through.

24. The internal transmission of claim 22, wherein: The elastic member is provided with a plug extending into the radial groove.

25. The step-gearbox according to claim 24, characterized in that: The plug extends into an adjacent radial groove located in the radial groove where the positioning protrusion is located.

26. The internal transmission of claim 20, characterized in that: The support ring is provided with a clearance groove on both sides to avoid the pawl.

27. The internal transmission according to claim 9 or 10, comprising a spindle and a pawl, characterized in that: The inner transmission is provided with a shifting mechanism, which comprises a pawl control ring and a first pawl seat sleeved on the mandrel, the pawl control ring is provided with an opening groove for controlling the pawl to open or retract, the first pawl seat is provided with a pawl groove accommodating the pawl, the first pawl seat is installed at the end of the pawl control ring, and the pawl control ring can rotate around the axis relative to the first pawl seat.

28. The internal transmission of claim 27, wherein: The pawl groove comprises a locking segment accommodating the pawl locking part, and the position of the locking segment is staggered with the position of the outer teeth of the sun gear.

29. The internal transmission of claim 27, wherein: The pawl control ring and the first pawl seat are respectively sleeved on the mandrel.

30. The internal transmission of claim 27, wherein: The opening groove is arranged on the inside of the pawl control ring.

31. The internal transmission of claim 27, wherein: Further comprising a positioning key arranged in the key cavity on the mandrel, and the inner wall of the first pawl seat is provided with a key groove allowing the positioning key to pass through.

32. The internal transmission of claim 27, wherein: The first pawl seat is provided with a boss extending into the inside of the pawl control ring.

33. The internal transmission of claim 27, wherein: The side of the first pawl seat close to the pawl control ring is provided with a clearance opening penetrating in the radial direction, which is used to accommodate the control claw part of the pawl.

34. The internal transmission of claim 27, wherein: The pawl control ring comprises a first control ring and a second control ring, which are sleeved on the mandrel and arranged in the axial direction of the mandrel, the side of the first control ring close to the second control ring is provided with a lever, and the second control ring is provided with a lever groove allowing the lever to be inserted.

35. The step transmission according to claim 34, characterized in that: The inner wall of the second control ring is provided with an inwardly extending protrusion, and the protrusion is provided with a lever groove penetrating in the axial direction.

36. The internal transmission of claim 27, characterized in that: The pawl control ring comprises a connecting rod and a control part on the connecting rod, the control part is provided with an opening groove for controlling the opening and closing of the pawl, the control part rotates with the connecting rod rotating around the mandrel, and the connecting rod comprises a front connecting rod segment and a rear connecting rod segment, and the distance between the connecting rod rear segment and the center line of the rotating shaft is smaller than the distance between the connecting rod front segment and the center line of the rotating shaft.

37. The step transmission according to claim 36, characterized in that: The control part comprises a front control part and a rear control part, the front control part is arranged on the connecting rod front segment, and the rear control part is arranged on the connecting rod rear segment.

38. The internal transmission of claim 37, wherein: The rear control part is arranged at the end of the connecting rod rear segment.

39. The internal transmission of claim 36, wherein: The connecting rod is fitted with the mandrel.

40. The internal transmission of claim 36, characterized in that: An outer side of a connecting position of the rear section of the connecting rod and the front section of the connecting rod is provided with a recessed first step, and the first step is used for avoiding the smallest sun gear.

41. The internal transmission of claim 40, wherein: An outer side of a connecting position of the rear section of the connecting rod and the front section of the connecting rod is provided with a recessed second step, and a distance of the second step from a center line of the rotating shaft is greater than a distance of the first step from the center line of the rotating shaft.

42. The internal transmission of claim 36, characterized in that: An inner side of a connecting position of the rear section of the connecting rod and the front section of the connecting rod is provided with a retracted part extending towards the mandrel, and the rear section of the connecting rod extends along an axial direction from the retracted part. Or, the front section of the connecting rod and the rear section of the connecting rod are parallel.

43. The internal transmission of claim 27, characterized in that: The mandrel is provided with a second pawl seat accommodating the pawl.

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