CN212455381U

CN212455381U - Bidirectional spiral direction-changing speed-changing device

Info

Publication number: CN212455381U
Application number: CN202021186151.8U
Authority: CN
Inventors: 杨勇
Original assignee: Individual
Current assignee: Individual
Priority date: 2020-06-24
Filing date: 2020-06-24
Publication date: 2021-02-02
Anticipated expiration: 2030-06-24

Abstract

A bidirectional spiral direction-changing and speed-changing device belongs to the field of electric vehicles, the number of intermediate gears between a power gear and high and low speed gear-changing teeth is different by one, the high and low speed gear-changing teeth smoothly rotate on a gear-changing shaft, the circumferential directions of opposite side surfaces of the high and low speed gear-changing teeth are respectively provided with an array arc slotted hole and an annular array bevel edge groove, the other side surface of the low speed gear-changing teeth is provided with a groove which is the same as the annular array bevel edge groove on the high speed gear-changing teeth, a direction-changing mechanism is arranged between the high and low speed gear-changing teeth, the gear shifting shaft on the outer side of the gear shifting device is provided with a low-gear clutch mechanism, the lateral surface of the outer side of the low-speed gear shifting tooth is provided with a low-gear shifting deflector rod, and the gear shifting shaft is also integrally provided with a gear shifting output tooth.

Description

Bidirectional spiral direction-changing speed-changing device

Technical Field

The utility model relates to a diversion speed change gear, in particular to two-way spiral diversion speed change gear belongs to the electric motor car field.

Background

Electric tricycles are already a popular vehicle, are seen everywhere in cities and rural areas where roads are flat, and in recent years, with the development of electric vehicles, the electric tricycles have been developed to hills and even mountainous areas, which benefit mainly from the gear shifting of the electric vehicles. The output of the direct current motor of the electro-tricycle is close to an oblique line, and the electro-tricycle is characterized in that the driving torque is small at a high speed and is large at a low speed. When the rotating speed of the motor is changed, the efficiency is also changed, the efficiency curve of the motor is like a peak contour line of a dome, the highest position is close to the rated rotating speed, and when the speed is equal to zero, the efficiency is also equal to zero. That is to say: the motor has two working condition points in the running process, and when the vehicle needs to output large torque, the advancing speed can be reduced, so that the condition is suitable for driving under the conditions of climbing and high load by utilizing the low-speed gear of the vehicle; when a large torque is not required, high speed operation can be utilized in high gear, in which case constant power is output, often for flat roads or light load conditions. The gear shifting is similar to that of a traditional engine vehicle, however, the traditional engine gear shifting structure cannot be directly matched with the electric vehicle, and therefore, a transmission of the electric vehicle running under a two-gear or multi-gear working condition needs to be developed.

The motor of the three-wheeled electric vehicle has a wide working range, relatively speaking, under the condition of medium and low rotating speed, the torque of the motor is very sufficient, and the working efficiency is relatively high. The two-stage transmission has the function of enabling the motor to work in a high-efficiency rotating speed range as much as possible, so that the effects of reducing loss, improving endurance mileage and the like are achieved.

Currently, a two-stage transmission has been used in a three-wheeled electric vehicle, and the two-stage transmission is used in a method of changing the running speed of the vehicle by forcibly engaging different speed change gears in a stopped state, and fig. 10 is a schematic view of the overall structure of a shift mechanism in the prior art. In the traditional two-stage transmission, power is transmitted to a first shift input tooth 21a by a power tooth 20, a second shift input tooth 21b is arranged coaxially with the first shift input tooth 21a, a high-speed shift tooth 22a and a low-speed shift tooth 22b are respectively meshed on the first shift input tooth 21a and the second shift input tooth 21b, the diameter of the high-speed shift tooth 22a is smaller than that of the low-speed shift tooth 22b, and finally, the result of forward high-speed operation and reverse low-speed operation is obtained, the high-speed shift tooth 22a and the low-speed shift tooth 22b slide and rotate on the same shift shaft 24, the shift shaft 24 between the high-speed shift tooth 22a and the low-speed shift tooth 22b is axially connected with a shift ring 26 through an external spline 29a, the periphery of the shift ring 26 is of a concave structure, a shifting fork is arranged in the concave structure, and drives the shift ring 26 to axially slide between the high-speed shift tooth 22a and the low-speed shift tooth 22b, a first shift link 27a and a second shift link 27b are respectively fixed to both sides of the shift ring 26, respectively corresponding to a first shift connection hole 28a and a second shift connection hole 28b provided on both side surfaces of the high-speed shift tooth 22a and the low-speed shift tooth 22b, when the shift ring 26 is axially adjacent to the high-speed shift tooth 22a or the low-speed shift tooth 22b, the shift link one 27a or the shift link two 27b is inserted into the shift coupling hole one 28a or the shift coupling hole two 28b, the first shift link 27a or the second shift link 27b is interlocked with the high-speed shift tooth 22a or the low-speed shift tooth 22b, transmits power to the shift shaft 24 through the external spline 29a, the gear output 23, which is fixedly connected to the gear shaft 24, transmits power again to the differential input teeth 25, which in turn transmit power through the internal differential to the two half-shafts 30, so that the wheels arranged at the ends of the half-shafts 30 are driven in rotation.

Fig. 11 is a schematic end view of a prior art ball type one-way clutch. In the figure, a ball 33 for clutch is arranged between an inner ring 31 and an outer ring 30, like the bearing inner ring and the shaft, the inner ring 31 is arranged on a central shaft 32 in an interference manner, when the central shaft 32 rotates clockwise, the inner ring 31 and the outer ring 30 are locked, the inner ring 31 and the outer ring 30 are in an interlocking state, the inner ring 31 and the outer ring 30 move synchronously with the central shaft 32, when the central shaft 32 rotates anticlockwise, the inner ring 31 and the outer ring 30 are locked and separated, the inner ring 31 and the outer ring 30 are in a free state and lose interlocking with each other, and although the inner ring 31 and the central shaft 32 do synchronous circular motion, the outer ring 30 does not move synchronously with the inner ring 31.

In the above-described structure of fig. 10, there are drawbacks in that: because the low-speed gear shifting tooth 22a or the high-speed gear shifting tooth 22b rotates, the first gear shifting connecting rod 27a or the second gear shifting connecting rod 27b is not easy to insert into the first gear shifting connecting hole 28 a-or the second gear shifting connecting hole 28b arranged on the side surface of the high-speed gear shifting tooth 22a or the low-speed gear shifting tooth 22b along the axial direction, when the rotating speed of the electric vehicle is not reduced, not only can great impact be brought, but also the rotating direction is vertical to the axial gear shifting mechanism, sometimes the gear shifting teeth can be damaged, the situations of component replacement and vehicle maintenance can be frequently brought, and great inconvenience can be brought to users. In addition, this structure merely switches between different speeds, and cannot switch between different speeds when moving forward.

How to achieve gear shifting can not bring impact or gear damage, and can realize that the motor rotates at different speeds in the forward direction and outputs low speed in the reverse direction, which is a matter that technicians of the three-wheel electric vehicle are always concerned about, and is also an important subject existing in an electric tricycle and even an electric vehicle.

Disclosure of Invention

Can bring the impact problem among the switching speed to prior art, do not have the problem of different speeds on the same direction of advance, the utility model provides a two-way spiral diversion speed change gear, the direction of cut-in when its purpose changes the gear shift reduces the impact of bringing when shifting, changes the rotation direction through the positive and negative commentaries on classics of motor, realizes the different speeds that advance at a high speed and the low-speed backs, reaches high-speed and low-speed operation according to heavy burden and road condition in the direction of advance.

The technical scheme of the utility model is that: a bidirectional spiral direction-changing and speed-changing device comprises a power tooth, a high-speed gear tooth and a low-speed gear tooth, wherein the diameter of the high-speed gear tooth is smaller than that of the low-speed gear tooth, n and n +1 gears are respectively arranged between the power tooth and the high-speed gear tooth and between the power tooth and the low-speed gear tooth, the high-speed gear tooth and the low-speed gear tooth circumferentially and smoothly rotate on an external spline of a gear-changing shaft, the different diameters of opposite side surfaces of the high-speed gear tooth and the low-speed gear tooth are circumferentially provided with an array arc-shaped slotted hole and an annular array bevel edge groove respectively, the other side surface of the low-speed gear tooth is provided with a low-speed annular array bevel edge groove which is the same as the annular array bevel edge groove on the high-speed gear tooth, a direction-changing mechanism is arranged between the high-speed gear tooth and the low-speed gear tooth, a low-gear clutch mechanism is arranged on a gear shaft outside the low-speed gear tooth, and a low-speed gear, the gear shifting shaft is also integrally provided with gear shifting output teeth which are meshed with the input teeth of the differential mechanism;

further, the direction changing mechanism comprises a spline sleeve meshed with an external spline of the shift shaft and a spiral spline sleeve meshed with the periphery of the spline sleeve, a shift ring is arranged on the periphery of the spiral spline sleeve, a plurality of ratchets with inclined teeth at two ends opposite to each other are respectively arranged at two ends of the spiral spline sleeve, an annular damping spring with an annular handle is circumferentially arranged in the middle of the periphery of the spiral spline sleeve, the annular damping spring is radially connected with the shift ring through an annular handle, shift rods are axially arranged at two ends of the shift ring, two ends of each shift rod are opposite to the array arc-shaped slotted holes, the ratchets at two ends of the spiral spline sleeve are opposite to the annular array bevel edge grooves, after the spiral spline sleeve axially moves, the shift rods at one side are matched with the opposite array arc-shaped slotted holes, and the ratchets at one side are matched;

further, the low-gear clutch mechanism comprises a low-gear spline sleeve engaged with an external spline of the gear shifting shaft and a low-gear spiral spline sleeve engaged with the periphery of the low-gear spline sleeve, one side of the low-gear spiral spline sleeve facing to the low-speed gear shifting teeth is provided with a one-way ratchet, the one-way ratchet is arranged opposite to and matched with a bevel edge groove of the low-gear annular array, the periphery of the low-gear spiral spline sleeve is provided with a one-way clutch locked in the advancing direction, a low-gear annular damping spring groove is arranged on a low-gear outer ring of the one-way clutch, a low-gear annular damping spring with a low-gear ring handle is arranged in the low-gear annular damping spring groove, and the spiral structure of the low-gear spiral spline sleeve is;

furthermore, the power teeth are engaged with an intermediate idler wheel, the intermediate idler wheel is simultaneously engaged and output to the high-speed gear shifting teeth and the duplex input teeth on the duplex shaft, and the duplex output teeth on the duplex shaft are engaged with the low-speed gear shifting teeth;

furthermore, a spline sleeve is meshed on an external spline of the gear shifting shaft, an external spiral spline is arranged on the periphery of the spline sleeve, a spiral spline sleeve is meshed on the periphery of the external spiral spline, and the length of the spiral spline sleeve in the axial direction is smaller than that of the spline sleeve in the axial direction;

furthermore, the inclined edges of the annular array inclined edge grooves on the end surfaces of the high-speed gear shifting tooth and the low-speed gear shifting tooth are opposite and are consistent with the inclined teeth of the plurality of ratchet teeth in the upward inclining direction in the axial direction, and the radial width of the annular array inclined edge grooves is larger than or equal to the radial thickness of the plurality of ratchet teeth;

furthermore, the linear length of the deflector rod in the circumferential direction of the shift shaft is smaller than the chord length of the array arc-shaped slotted hole, and the thickness of the deflector rod in the radial direction of the shift shaft is smaller than or equal to the width of the array arc-shaped slotted hole in the radial direction of the shift shaft;

furthermore, an annular groove is circumferentially arranged in the middle of the periphery of the spiral spline housing, an annular damping spring with an annular handle is arranged in the groove, and the elastic force of the annular damping spring is positioned in the radial direction of the periphery of the spiral spline housing towards the axis;

furthermore, the direction of the ring handle of the annular damping spring with the ring handle is positioned in the radial direction of the gear shifting shaft, the length of the ring handle is smaller than the outer diameter of the gear shifting ring, and the ring handle and any one of the shift levers synchronously rotate in the circumferential direction;

furthermore, the inner circumference of the gear shifting ring and the outer circumference of the spiral spline sleeve are arranged in a rotating and smooth mode, an annular convex part is arranged on the outer circumference of the gear shifting ring, a shifting fork matched with the annular convex part is arranged on the outer circumference of the annular convex part, and the shifting fork is used for shifting the gear shifting ring to move in the axial direction of the gear shifting shaft.

The utility model discloses a beneficial effect who has is: the intermediate gear is arranged between the power gear and the high-speed gear shifting gear, and the intermediate gear and the duplex gear are arranged between the power gear and the low-speed gear shifting gear, so that the rotating speeds of the high-speed gear shifting gear and the low-speed gear shifting gear are changed and the rotating directions of the high-speed gear shifting gear and the low-speed gear shifting gear are opposite after the power is transmitted to the high-speed gear shifting gear and the low-speed gear shifting gear due to the difference of n intermediate gears and n +1 intermediate gears, and the forward and backward at different speeds can be realized; the high-speed gear shift tooth or the high-speed gear shift tooth and the gear shift ring rotate at the same part by arranging a shifting fork at the periphery of the gear shift ring, further enabling the shifting rod arranged at the end face of the gear shift ring to move along one side in the axial direction, enabling the shifting rod to be inserted into an array arc-shaped slotted hole arranged at the opposite side face of the high-speed gear shift tooth or the high-speed gear shift tooth, further enabling the annular damping spring with the annular handle to rotate by the gear shift ring, enabling the annular handle of the annular damping spring to be synchronously connected with the gear shift ring, and enabling the gear shift ring to be synchronously connected with the damping spring under the action of radial elasticity towards the axis after the gear shift ring and the damping spring are synchronous, the spiral spline sleeve is driven to move axially along the spiral spline in circumferential rotation at the periphery of the spline sleeve, so that the end part of the spiral spline sleeve is arranged in a manner that the ratchet enters the bevel edge groove along the bevel edge of the bevel edge groove, power on the high-speed gear shifting tooth or the high-speed gear shifting tooth is transmitted to the spiral spline sleeve, under the condition, the power is transmitted to the gear shifting shaft through the internal spline of the spline sleeve, the shifted power is output from the gear shifting output shaft, the output speed of the ratchet of the spiral spline sleeve close to the high-speed gear shifting tooth is high, the output speed is low when close to one side of the low-speed gear shifting shaft, because the bevel edges of the annular array bevel edge grooves on the end surfaces of the high-speed gear shifting tooth and the low-speed gear shifting tooth are opposite and are consistent with the bevel edges of the plurality of ratchet teeth in the axial tilt direction, and the radial width of the annular array bevel edge groove is more than or equal to the radial, the arrangement of the bevel edge and the bevel teeth not only can enable the ratchet teeth to enter the bevel edge groove in the rotation process and reduce the impact between the ratchet teeth and the bevel edge groove, but also can enable the rotation directions of the low gear or the high gear to be opposite due to the fact that the bevel edges of the annular array bevel edge groove on the end faces of the high-speed gear shifting tooth and the low-speed gear shifting tooth are opposite, and can realize different speeds of forward high-speed operation and backward low-speed operation; the length of the spiral spline sleeve in the axial direction is smaller than that of the spline sleeve in the axial direction, and the spiral spline sleeve moves axially on the periphery of the spline sleeve, so that the movement switching between the high-speed gear shifting teeth and the low-speed gear shifting teeth can be realized through the forward and reverse rotation of the driving motor, and the switching between the high speed and the low speed and the change of the rotation direction are realized; the low-gear clutch mechanism is arranged on the gear shifting shaft outside the low-speed gear shifting teeth, so that a low gear can be added in the forward direction, and particularly, the low-gear spline sleeve meshed with the external spline of the gear shifting shaft and the low-gear spiral spline sleeve meshed with the periphery of the low-gear spline sleeve can drive the gear shifting shaft to rotate simultaneously when the low-gear spiral spline sleeve rotates; the one-way ratchet is arranged on one side of the low-gear spiral spline sleeve facing to the low-speed gear shifting tooth, the one-way ratchet is arranged opposite to and matched with the low-gear annular array bevel edge groove, when the low-speed gear shifting tooth rotates towards the advancing direction, the low-speed gear shifting rod on the low-speed gear shifting sleeve drives the low-gear annular damping spring, the low-gear annular damping spring drives the low-gear outer ring of the low-gear one-way clutch to rotate, the low-gear outer ring of the low-gear one-way clutch is in a locking state between the low-gear inner ring and the low-gear outer ring during forward rotation, the low-gear inner ring and the one-way ratchet of the low-gear spiral spline sleeve are driven to move towards the outer side of the low-speed gear shifting tooth, the one-way ratchet enters the low-gear annular array bevel edge groove of the low-speed gear shifting tooth, finally, the power output of the low-speed gear shifting tooth is realized, the low-speed output in the, High torque operation at high load.

Utilize the utility model discloses can change the direction of cutting into when shifting, reduce the impact of bringing when shifting, can change the rotation direction through the positive reverse rotation of motor, the fast different speeds that gos forward and the low-speed backs can also realize the operation of two speeds of high-low fender, can satisfy the traveling under different road conditions, not equidimension load situation.

Drawings

Fig. 1 is a schematic view of the overall structure of the high-gear speed-changing tooth side of the present invention.

Fig. 2 is a schematic view of the side overall structure of the low-gear clutch mechanism.

Fig. 3 is an exploded view of the shift mechanism of the present invention.

Fig. 4 is a schematic view of the inside structure of the high-speed shift tooth.

FIG. 5 is an inside view of the low shift tooth.

FIG. 6 is an outboard schematic view of the low gear shift tooth.

FIG. 7 is an exploded view of the helical spline housing and shift shaft.

Fig. 8 is an exploded view of the low clutch mechanism on the outer periphery of the shift shaft.

FIG. 9 is a schematic view of a partial combination of the low range clutch mechanism.

Fig. 10 is a schematic view of the overall structure of a prior art shift mechanism.

FIG. 11 is a schematic diagram of an end face structure of a ball type one-way clutch in the prior art

Description of reference numerals: 10-middle idler shaft, 10 a-middle idler, 11-double coupling, 11 a-double input tooth, 11 b-double output tooth, 12-low gear clutch mechanism, 13-spiral spline housing, 13 a-external spiral spline, 13 b-internal spiral spline, 14-annular damping spring, 14 a-annular groove, 14 b-annular handle, 15 a-ratchet I, 15 b-ratchet II, 16 a-bevel edge groove I, 16 b-bevel edge groove II, 16 c-low gear annular array bevel edge groove 17a, 17 b-bevel edge II, 17 c-low gear bevel edge, 18 a-arc slotted hole I, 18 b-arc slotted hole II, 19-deflector rod, 19 a-deflector rod I, 19 b-deflector rod II, 19 c-low gear shift deflector rod, 20-power teeth, 21 a-gear shifting input teeth I, 21 b-gear shifting input teeth II, 22 a-high gear shifting teeth, 22 b-low gear shifting teeth, 23-gear shifting output teeth, 24-gear shifting shaft, 25-differential input teeth, 26-gear shifting ring, 26 a-gear shifting ring I, 26 b-gear shifting ring II, 27 a-gear shifting connecting rod I, 27b gear shifting connecting rod II, 28a gear shifting connecting hole I, 28 b-gear shifting connecting hole II, 29-spline housing, 29 a-external spline, 29 b-internal spline, 30-external ring, 31-internal ring, 32-central shaft, 33-ball, 121-low gear annular damping spring, 121 a-low gear ring handle, 122-low gear external ring, 123-low gear internal ring, 124-low gear spiral spline housing, 124 a-one-way ratchet, 125-low gear ball, 126-low gear internal helical spline, 127-low gear external helical spline, 128-low gear spline sleeve, 129-low gear internal spline and 130-low gear external ring gear.

Detailed Description

The following describes the embodiments of the present invention in detail with reference to the accompanying drawings.

The technical scheme of the utility model a two-way spiral diversion speed change gear, figure 1 is the utility model discloses the overall structure schematic diagram, figure 2 of high fender variable speed flank are the utility model discloses low fender clutch mechanism side overall structure schematic diagram, figure 3 the utility model discloses well shift mechanism's explosion chart. The bidirectional spiral speed change and direction change device comprises a power tooth 20, a high-speed shift tooth 22a and a low-speed shift tooth 22b, the diameter of the high-speed shift tooth 22a is smaller than that of the low-speed shift tooth 22b, n and n +1 gears are respectively arranged between the power tooth 20 and the high-speed shift tooth 22a and between the power tooth 22b and the low-speed shift tooth 22b, the high-speed shift tooth 22a and the low-speed shift tooth 22b circumferentially and smoothly rotate on an external spline 29a of a shift shaft 24, fig. 4 is an internal structural schematic diagram of the high-speed shift tooth 22a, fig. 5 is an internal structural schematic diagram of the low-speed shift tooth 22b, fig. 6 is an external structural schematic diagram of the low-speed shift tooth, arc-shaped slotted holes 18a and arc-shaped slotted holes 18b are respectively arranged on opposite side surfaces of the high-speed shift tooth 22a and the low-speed shift tooth 22b, an annular array bevel edge array groove 16a and an annular bevel edge array groove 16b are also respectively arranged on opposite side surfaces of the high-speed shift tooth 22a and the annular array groove 16a and the second side groove 16b is arranged in the circumferential direction of the high-speed shift tooth 22a and the low-speed shift tooth 22b with different radiuses, a direction changing mechanism is arranged between the high-speed shift tooth 22a and the low-speed shift tooth 22b, a low-gear annular array bevel edge groove 16c is arranged on the other side surface of the low-speed shift tooth 22b, one side of the low-gear annular array bevel edge groove 16c is a low-gear bevel edge 17c and is the same as the annular array bevel edge groove 16a on the high-speed shift tooth 22a, a direction changing mechanism is arranged between the high-speed shift tooth 22a and the low-speed shift tooth 22b, a low-gear clutch mechanism 12 is arranged on a shift shaft 24 outside the low-speed shift tooth 22b, a low-gear shift lever 19c is arranged on the side surface outside the low-speed shift tooth 22b, a shift output tooth 23 is further integrally arranged on the shift shaft 24, and the shift output tooth 23 is meshed with a differential input tooth 25.

The direction changing mechanism comprises a spline sleeve 29 engaged with an external spline 29a of the shift shaft 24, an internal spline 29b arranged on the inner circumference of the spline sleeve 29, an external helical spline 13a arranged on the outer circumference of the spline sleeve 29, a helical spline sleeve 13 engaged with the outer circumference of the spline sleeve 29, an internal helical spline 13b arranged on the inner circumference of the helical spline sleeve 13, a shift ring 26 arranged on the outer circumference of the helical spline sleeve 13, a first ratchet 15a and a second ratchet 15b with opposite inclined teeth at two ends arranged at two ends of the helical spline sleeve 13 respectively, wherein the first ratchet 15a and the second ratchet 15b both comprise a plurality of ratchets, an annular damping spring 14 with an annular handle arranged on the middle circumference of the outer circumference of the helical spline sleeve 13, the annular handle 14b of the annular damping spring 14 is radially connected with the shift ring 26 to realize synchronous rotation, a plurality of shift rods 19 are circumferentially arranged on two ends of the shift ring 26 in an array manner, the shift rods 19 are parallel to each other, and the length directions of the shift rods 19 are consistent with, two ends of a plurality of deflector rods 19 are respectively arranged opposite to the first array arc-shaped slotted hole 18a and the second array arc-shaped slotted hole 18b on the end surfaces of the high-speed shift tooth 22a and the low-speed shift tooth 22b, the end parts of the plurality of deflector rods 19 can enter the first array arc-shaped slotted hole 18a and the second array arc-shaped slotted hole 18b, a plurality of ratchets of the first ratchet 15a and the second ratchet 15b on two ends of the spiral spline sleeve 13 are respectively arranged opposite to the first annular array bevel edge groove 16a and the second annular array bevel edge groove 16b on the end surfaces of the high-speed shift tooth 22a and the low-speed shift tooth 22b, and can be engaged with each other through axial movement, a shift output tooth 23 is also integrally arranged on the shift shaft 24, and the shift output tooth 23 is engaged with the differential input.

Fig. 7 is an exploded schematic view of the helical spline housing and the shift shaft, and referring to fig. 1-2, the power tooth 20 is engaged with an intermediate idler 10a, the intermediate idler 10a is disposed on the intermediate idler shaft 10, the intermediate idler 10a is simultaneously engaged and output to the high-speed shift tooth 22a and the duplex input tooth, the duplex shaft 11 is simultaneously disposed with the duplex input tooth 11a and the duplex output tooth 11b, and the duplex output tooth 11b on the duplex shaft is engaged with the low-speed shift tooth 22 b.

Fig. 8 is an exploded view of the low clutch mechanism on the outer periphery of the shift shaft, and fig. 9 is a partial combination view of the low clutch mechanism. The low-gear clutch mechanism 12 comprises a low-gear spline housing 128 engaged with an external spline 29a of the shift shaft 24, a low-gear internal spline 129 arranged on the inner periphery of the low-gear spline housing 128, the low-gear internal spline 129 matched with the external spline 29a, a low-gear external helical spline 127 arranged on the outer periphery of the low-gear spline housing 128, a low-gear helical spline housing 124 engaged with the outer periphery of the low-gear spline housing 128, a low-gear internal helical spline 126 arranged on the inner periphery of the low-gear helical spline housing 124, a one-way ratchet 124a arranged on the low-gear helical spline housing 124 facing one side of the low-gear shift teeth 22b, a one-way ratchet 124a arranged opposite to and engaged with the low-gear annular array bevel edge groove 16c, a low-gear one-way clutch locked in the forward direction arranged on the outer periphery of the low-gear helical spline housing 124, a low-gear annular damping spring groove 121 arranged on the low-gear outer ring 122 of the low-gear one-way clutch, and a, 125 is a low-gear ball disposed at a position of a gap outside the low-gear inner ring 123, and a low-gear ring 130 is disposed outside the low-gear outer ring 122, and the helical structure of the low-gear helical spline housing 124 is the same as that of the helical spline housing 13.

In the present embodiment, the low-stage inner ring 123 is disposed on the outer periphery of the low-stage helical spline housing 124, and both are integrated, or the low-stage inner ring 123 may be disposed on the outer periphery of the low-stage helical spline housing 124 by interference coupling of both of the separate bodies.

Referring to fig. 3, a spiral spline housing 13 engaged with the outer periphery of a spline housing 29, an inner periphery of the spiral spline housing 13 is provided with an inner spiral spline 13b, the outer periphery of the inner spiral spline 13b is of a smooth structure except for an annular groove 14a at the middle position, a shift ring 26 is sleeved on the outer periphery of the spiral spline housing 13, two ends of the spiral spline housing 13 are respectively provided with a plurality of ratchets with opposite inclined teeth at two ends, specifically, a first ratchet 15a and a second ratchet 15b, an annular array inclined edge groove 16a of the first ratchet 15a facing one side of a high-speed shift tooth 22a, an annular array inclined edge groove 16b of the second ratchet 15b facing one side of a low-speed shift tooth 22b, an annular damping spring 14 with a ring handle 14b is arranged in the annular groove 14a in the middle periphery of the outer periphery of the spiral spline housing 13, two ends of the shift ring 26 are respectively provided with a plurality of shift levers 19a and two shift levers 19b in an array manner, and two ends of the shift levers 19a and two levers are respectively connected with the high-speed shift tooth The first slotted hole 18a and the second arc-shaped slotted hole 18b are correspondingly arranged, a plurality of ratchets of the first ratchet 15a and the second ratchet 15b at two ends of the spiral spline sleeve 13 are correspondingly arranged with a first annular array bevel edge groove 16a and a second annular array bevel edge groove 16b on the end faces of the high-speed gear shifting tooth 22a and the low-speed gear shifting tooth 22b respectively, a gear shifting output tooth 23 is further integrally arranged on the gear shifting shaft 24, and the gear shifting output tooth 23 is meshed with the differential input tooth.

The shift shaft 24 is provided with a spline housing 29 engaged with an external spline 29a, an external helical spline 13a is arranged on the outer periphery of the spline housing 29, a helical spline housing 13 is engaged with the outer periphery of the external helical spline 13a, an internal helical spline 13b is arranged on the inner periphery of the helical spline housing 13, and the axial length of the helical spline housing 13 is smaller than that of the spline housing 29.

Referring to fig. 3, a linear distance of the first shift lever 19a and the second shift lever 19b in the circumferential direction of the shift shaft 24 is smaller than a chord length of the first arc-shaped slot 18a and the second arc-shaped slot 18b, and a thickness of the first shift lever 19a and the second shift lever 19b in the radial direction of the shift shaft 24 is smaller than or equal to a width of the first arc-shaped slot 18a and the second arc-shaped slot 18b in the radial direction of the shift shaft 24.

An annular groove 14a is formed in the middle of the periphery of the spiral spline sleeve 13 in the circumferential direction, an annular damping spring 14 with an annular handle 14b is arranged in the groove, the elastic force of the annular damping spring 14 is clamping force, and the clamping force is located in the radial direction of the periphery of the spiral spline sleeve 13 towards the axis. The annular damping spring 14 is radially connected to a shift ring 26 on the outer periphery of the spiral spline housing 13 by a shank 14b of the annular damping spring 14, and rotates in synchronization with the shift ring.

In this embodiment, the direction of the annular handle 14b of the annular damping spring 14 is located in the radial direction of the shift shaft 24, the length of the annular handle 14b is smaller than the outer diameter of the shift ring 26, the annular handle 14b and the corresponding shift lever 19 rotate synchronously in the circumferential direction, when the shift ring 26 rotates, the shift lever 19 shifts the annular handle 14b to further drive the spiral spline housing 13 to rotate and move circumferentially, and when the spiral spline housing 13 moves axially, the end ratchet can enter the annular array bevel edge groove one 16a or the annular array bevel edge groove two 16b arranged on the inner side of the high-speed shift tooth 22a or the low-speed shift tooth 22b, so as to transmit the power of the high-speed shift tooth 22a or the low-speed shift tooth 22b to the spiral spline housing 13, and then to the shift housing 29, and further transmit the power to the shift shaft 24 for output.

The inner periphery of the shift ring 26 and the outer periphery of the spiral spline sleeve 13 are arranged in a smooth rotating mode, an annular convex portion is arranged on the outer periphery of the shift ring 26, a shifting fork matched with the annular convex portion is arranged on the outer periphery of the annular convex portion, the shifting fork shifts the shift ring 26 to move in the axial direction of the shift shaft 24, the shift ring 26 can drive the shifting rod 19 to further drive the annular damping spring 14 and the spiral spline sleeve 13 to move in the axial direction.

In this embodiment, the shift ring 26 is divided into two shift rings 26a and 26b along the vertical center, wherein the shift ring 26a is close to the inner side of the high-speed shift tooth 22a, the shift ring 26b is close to the inner side of the low-speed shift tooth 22b, the shift rods 19 connected into a whole are arranged between the shift ring 26a and the shift ring 26b in an array manner in the circumferential direction, the middle diameter of each shift rod 19 is larger than the diameters of the shift rods 19a and 19b on both sides, the middle large-diameter portion is arranged between the shift ring 26a and the shift ring 26b and axially supports the shift ring 26a and the shift ring 26b on both sides, the shift rods 19a and 19b extend to both sides through a plurality of holes which are formed in the circumferential direction of the shift ring 26a and the shift ring 26b and are equal to the diameters of the shift rods 19a and 19b, and the shift rods 18a and 18b which are respectively facing the inner side of the high-speed shift tooth array and the inner side of the low-speed shift tooth 22a, and the shift ring 22b are respectively arranged in an array manner The second slot hole 18 b.

After the shifting fork shifts the first shift ring 26a and the second shift ring 26b axially, the first shift rod 19a or the second shift rod 19b can enter the first array arc-shaped slot 18a inside the high-speed shift tooth 22a or the second array arc-shaped slot 18b inside the low-speed shift tooth 22b, after entering, the high-speed shift tooth 22a or the low-speed shift tooth 22b can drive a plurality of shift rods 19 to rotate simultaneously, one of the shift rods 19 can shift the ring handle 14b of the annular damping spring 14, the annular damping spring 14 drives the annular damping spring 14 to drive the spiral spline sleeve 13 to rotate, the ratchets at the end part of the spiral spline sleeve 13 can drive the spline sleeve 29 and even the shift shaft 24 to rotate, and power is output. At this time, the entire shift mechanism rotates in synchronization with the high-speed shift tooth 22a or the low-speed shift tooth 22 b.

In this embodiment, after a plurality of shift levers 19 are arranged, the shift ring one 26a and the shift ring two 26b on both sides are welded into a whole, the shift levers 19, the shift ring one 26a and the shift ring two 26b are integrated into a whole, when the shift fork is shifted into the integrated shift ring 26, the shift levers 19 are driven to move axially, the shift levers 19a and the shift levers 19b on both sides of the shift lever 19 enter the arc-shaped slot one 18a or the arc-shaped slot two 18b inside the high-speed shift tooth 22a or the low-speed shift tooth 22b corresponding to the shift levers, and the annular damping spring 14 and the helical spline housing 13 are driven to move during the axial movement of the shift ring 26a, so that the ratchet tooth one 15a or the ratchet tooth two 15b at the end of the helical spline housing 13 enters the annular array groove one 16a or the annular array groove two 16b along the bevel edge one 17a or the bevel edge 17b of the annular array groove 16b, the high-speed shift tooth 22a or the low-speed shift tooth 22b rotates to rotate the shift shaft 24, and the power is output to the shift output tooth 23. The first inclined edge 17a or the second inclined edge 17b is in the same inclination direction with the first ratchet tooth 15a or the second ratchet tooth 15b, and the first inclined edge and the second inclined edge are in contact with each other along the spiral direction, so that direct impact in the prior art can be relieved, and inclined teeth can enter the inclined edge groove along the inclined edge.

In the present embodiment, the plurality of shift levers 19 are provided to keep the shift rings one 26a and two 26b parallel.

When the shifting rod 19 enters one side of the high-speed shifting tooth 22a, the first array bevel edge groove 16a on the side of the high-speed shifting tooth 22b is meshed with the first ratchet tooth 15a, the first ratchet tooth 15, the spiral spline sleeve 13, the spline sleeve 29 and the shifting shaft 24 are sequentially driven to rotate, high-speed rotation is carried out, and power is output from the power output tooth 23 integrated with the shifting shaft 24.

When the shift fork moves to one side of the low-speed gear shifting tooth 22b in the advancing direction under the condition that the gear shifting clutch mechanism is not arranged, the two array bevel edge grooves 16b on the side of the low-speed gear shifting tooth 22b are in smooth connection with the first ratchet teeth 15b, and are in an overrunning state, and power is not transmitted between the two arrays bevel edge grooves.

When the shift fork moves to one side of the low-speed shift tooth 22b in the forward direction under the condition that the shift clutch mechanism is arranged outside the low-speed shift tooth 22b, the low-speed shift lever 19c thereon sequentially drives the low-gear ring handle 121a and the low-gear annular damping spring 121 to rotate due to the rotation of the low-speed shift tooth 22b, the low-gear annular damping spring 121 drives the low-gear outer ring 122 to rotate under the elastic force action in the radial direction towards the axial center, the low-gear outer ring 122 simultaneously locks the low-gear inner ring 123 to rotate when rotating, and further sequentially drives the low-gear ratchet helical spline housing 124 and the one-way ratchet 124a to rotate, the one-way ratchet 124a moves axially along the shift shaft 24 set while rotating, the one-way ratchet 124a enters the low-gear array bevel edge groove 16c arranged outside the low-speed shift tooth 22b to be engaged with each other, and sequentially drives the low-gear helical spline housing 124, the low-gear spline housing 128 and the shift shaft 24 to rotate, the low-gear power output is realized, and simultaneously, the low-gear one-way clutch also synchronously rotates, the friction resistance between the low-gear annular damping spring 121 and the low-gear outer ring 123 is avoided, and finally the low-speed output of the friction-free low-speed gear shifting tooth 22b in the forward direction is achieved.

Thus, there are two outputs, high and low, and two speeds in the forward direction, and a low reverse speed output in the reverse direction.

The utility model has the advantages that: by arranging the middle idle gear 10a between the power gear 20 and the high-speed gear shifting tooth 22a and arranging the middle idle gear 10a and the duplex gear between the power gear 20 and the low-speed gear shifting tooth 22b, the power is transmitted to the high-speed gear shifting tooth 22a and the low-speed gear shifting tooth 22a due to the fact that the number of gears before reaching the high-speed gear shifting tooth 22a and the low-speed gear shifting tooth 22a is different by one, so that the rotating speed and the rotating direction are changed, and advancing and backing at different speeds can be achieved; the high-speed gear shifting tooth 22a and the low-speed gear shifting tooth 22a are smoothly rotated on the external spline 29a of the gear shifting shaft 24 along the circumferential direction, so that the rotating speed and the rotating direction can be changed and then transmitted to the input gear 25 of the differential mechanism through the gear shifting mechanism arranged on the gear shifting shaft 24 between the high-speed gear shifting tooth and the low-speed gear shifting tooth, and finally transmitted to the differential mechanism; the shifting fork is arranged on the periphery of the shift ring 26, the shift ring 26 can be shifted to the high-speed shift tooth 22a or the low-speed shift tooth 22b, the shifting rod 19 arranged on the end face of the shift ring 26 can further move to one side along the axial direction, the first shifting rod 19a or the second shifting rod 19b at two ends of the shifting rod 19 are inserted into the first arc-shaped slot 18a or the second arc-shaped slot 18b arranged on the opposite side face of the high-speed shift tooth 22a or the low-speed shift tooth 22b, the high-speed shift tooth 22a or the low-speed shift tooth 22b and the shift ring 26 rotate in the same part, the annular damping spring 14 with the ring handle 14b is further driven by the shift ring 26 to rotate, the damping spring drives the spiral ratchet sleeve 13 to rotate in the circumferential direction along the spiral spline on the periphery of the spline sleeve 29 under the action of radial elastic force towards the axial center, and the end part of the spiral spline sleeve 13 is arranged on the first ratchet sleeve 15a or the second ratchet tooth 15b along the first annular array first groove 16a or the annular array inclined edge second groove 16b 17a or the second inclined edge 17b enters the first annular array inclined edge groove 16a or the second annular array inclined edge groove 16b, the power on the high-speed shift tooth 22a or the low-speed shift tooth 22b is transmitted to the spiral spline housing 13, in this case, the power is transmitted to the shift shaft 24 through the internal spline 29b of the spline housing 29, the shifted power is output from the shift shaft, the high rotating speed is output by the first ratchet tooth 15a of the spiral spline housing 13 close to the high-speed shift tooth 22a, the low rotating speed is output by the second ratchet tooth 15b of the spiral spline housing 13 close to the side of the low-speed shift shaft 24, and the low speed is output because the inclined angles of the first annular array inclined edge groove 16a and the second inclined edge 17b of the second annular array inclined edge groove 16b on the end surfaces of the high-speed shift tooth 22a and the low-speed shift tooth 22b are opposite to each other and are respectively consistent with the inclined angles of the plurality of inclined teeth of the first ratchet tooth 15a and the second inclined edge 15b in the axial direction, the radial width of the annular array bevel edge groove I16 a and the annular array bevel edge groove II 16b is more than or equal to the radial thickness of a plurality of ratchets, the arrangement of the bevel edge I17 a, the bevel edge II 17b, the ratchet teeth I15 a and the ratchet teeth II 15b not only can enable the ratchet teeth to enter the annular array bevel edge groove I16 a and the annular array bevel edge groove II 16b in the rotation process and reduce the impact between the ratchet teeth, but also can enable the rotation directions of a low gear or a high gear to be opposite because the diameter of the high-speed gear tooth 22a is smaller than that of the low-speed gear tooth and the diameter of the annular array bevel edge groove II 16b is opposite, and can realize the forward high-speed operation and the backward low-speed operation; by making the length of the helical spline housing 13 in the axial direction smaller than that of the spline housing 29 in the axial direction, since the helical spline housing 13 makes axial movement on the outer periphery of the spline housing 29, the movement switching between the high-speed operation of the high-speed shift teeth 22a and the low-speed operation of the low-speed shift teeth 22b can be realized by the forward and reverse rotation of the driving motor, thereby realizing the switching between the high speed and the low speed and the change of the rotation direction; by arranging the low-gear clutch mechanism on the gear shift shaft 24 outside the low-speed gear shift teeth 22b, a low gear can be added in the forward direction, particularly a low-gear spline sleeve 128 meshed with the external spline 29a of the gear shift shaft 24 and a low-gear helical spline sleeve 124 meshed with the periphery of the low-gear spline sleeve 128 can drive the gear shift shaft 24 to rotate simultaneously when the low-gear helical spline sleeve 124 rotates; by arranging the annular one-way ratchet 124a on the low-gear helical spline housing 124 toward the low-gear annular array bevel edge groove 16c, and arranging the one-way ratchet 124a opposite to and matching with the low-gear annular array bevel edge groove 16c, when the low-gear helical spline housing 22b rotates in the forward direction, the low-gear shift lever 19c on the low-gear shift lever toggles the low-gear ring handle 121a to further drive the low-gear annular damping spring 121 to rotate, the low-gear annular damping spring 121 drives the low-gear outer ring 122 of the low-gear one-way clutch to rotate, the low-gear outer ring 122 of the low-gear one-way clutch is in a locking state between the low-gear inner ring 123 and the low-gear outer ring 122 in the forward direction, so as to drive the low-gear inner ring 123 and the one-way ratchet 124a of the low-gear helical spline housing 124 to move in the direction of the low-gear helical spline 22b, so that the low-gear teeth 22b of the one-way ratchet 124a enter the low, finally, the low-speed output in the forward state is realized on the shift shaft 24 which realizes the power output of the low-speed shift tooth 22b, and the low-speed shift function is added on the basis of only high speed originally, so that the high-torque operation under the conditions of climbing and high load can be coped with.

Claims

1. The utility model provides a two-way spiral diversion speed change gear, includes power tooth, high-speed gear tooth and low-speed gear tooth, and high-speed gear tooth diameter is less than low-speed gear tooth, its characterized in that: the transmission gear is characterized in that n and n +1 gears are respectively arranged between the power gear and the high-speed gear shifting tooth and the low-speed gear shifting tooth, the high-speed gear shifting tooth and the low-speed gear shifting tooth circumferentially and smoothly rotate on an external spline of a gear shifting shaft, the opposite sides of the high-speed gear shifting tooth and the low-speed gear shifting tooth circumferentially and respectively are provided with an array arc-shaped slotted hole and an annular array bevel edge groove in the circumferential direction of different diameters, the other side of the low-speed gear shifting tooth is provided with a low-gear annular array bevel edge groove which is the same as the annular array bevel edge groove on the high-speed gear shifting tooth, a reversing mechanism is arranged between the high-speed gear shifting tooth and the low-speed gear shifting tooth, a low-gear clutch mechanism is arranged on the gear shifting shaft outside the low-speed gear shifting tooth, a low-gear shifting lever is arranged on the side of the outer side of the low-speed gear shifting tooth, a gear shifting output tooth.

2. A bidirectional spiral direction-changing and speed-changing device as claimed in claim 1, wherein: the direction changing mechanism comprises a spline sleeve meshed with an external spline of the shift shaft and a spiral spline sleeve meshed with the periphery of the spline sleeve, a shift ring is arranged on the periphery of the spiral spline sleeve, a plurality of ratchets with inclined teeth at two ends opposite to each other are respectively arranged at two ends of the spiral spline sleeve, an annular damping spring with an annular handle is circumferentially arranged in the middle of the periphery of the spiral spline sleeve, the annular handle of the annular damping spring is radially connected with the shift ring, shift rods are axially arranged at two ends of the shift ring, two ends of each shift rod are opposite to the arc-shaped array groove holes, ratchets at two ends of the spiral spline sleeve are opposite to the annular array inclined edge grooves, after the spiral spline sleeve axially moves, the shift rods at one side are matched with the opposite arc-shaped array groove holes, and the ratchets at one side are matched.

3. A bidirectional spiral direction-changing and speed-changing device as claimed in claim 1, wherein: the low-gear clutch mechanism comprises a low-gear spline sleeve meshed with an external spline of the gear shifting shaft and a low-gear spiral spline sleeve meshed with the periphery of the low-gear spline sleeve, wherein one-way ratchets are arranged on the low-gear spiral spline sleeve towards one side of the low-speed gear shifting teeth, the one-way ratchets are arranged opposite to the bevel edge grooves of the low-gear annular array and are matched with each other, a one-way clutch locked in the advancing direction is arranged on the periphery of the low-gear spiral spline sleeve, a low-gear annular damping spring groove is formed in the low-gear outer ring of the one-way clutch, a low-gear annular damping spring with a low-gear ring handle is arranged in the low-gear annular damping spring, and the spiral structure of the low.

4. A bidirectional spiral direction-changing and speed-changing device as claimed in claim 1, wherein: the power teeth are engaged with a middle idle gear, the middle idle gear is simultaneously engaged and output to the high-speed gear shifting teeth and the duplex input teeth on the duplex shaft, and the duplex output teeth on the duplex shaft are engaged with the low-speed gear shifting teeth.

5. A bidirectional spiral direction-changing and speed-changing device as claimed in claim 2, wherein: the external spline of the gear shifting shaft is engaged with a spline housing, an external helical spline is arranged on the periphery of the spline housing, a helical spline housing is engaged on the periphery of the external helical spline, and the length of the helical spline housing in the axial direction is smaller than that of the spline housing in the axial direction.

6. A bidirectional spiral direction-changing and speed-changing device as claimed in claim 1, wherein: the inclined edges of the annular array inclined edge grooves on the end surfaces of the high-speed gear shifting teeth and the low-speed gear shifting teeth are opposite and are consistent with the inclined teeth of the ratchet teeth in the inclined direction in the axial direction,

the width of the annular array bevel groove in the radial direction is greater than or equal to the thickness of the plurality of ratchet teeth in the radial direction.

7. A bidirectional spiral direction-changing and speed-changing device as claimed in claim 1, wherein: the linear length of the shifting lever in the circumferential direction of the shifting shaft is smaller than the chord length of the array arc-shaped slotted hole, and the thickness of the shifting lever in the radial direction of the shifting shaft is smaller than or equal to the width of the array arc-shaped slotted hole in the radial direction of the shifting shaft.

8. A bidirectional spiral direction-changing and speed-changing device as claimed in claim 2, wherein: an annular groove is formed in the middle of the periphery of the spiral spline sleeve in the circumferential direction, an annular damping spring with an annular handle is arranged in the groove, and the elastic force of the annular damping spring is located in the radial direction of the periphery of the spiral spline sleeve towards the axis.

9. A bidirectional spiral direction-changing and speed-changing device as claimed in claim 2, wherein: the direction of the annular damping spring with the annular handle is located in the radial direction of the gear shifting shaft, the length of the annular handle is smaller than the outer diameter of the gear shifting ring, and the annular handle and any one of the shifting levers synchronously rotate in the circumferential direction.

10. A bidirectional spiral direction-changing and speed-changing device as claimed in claim 2, wherein: the inner periphery of the gear shifting ring and the outer periphery of the spiral spline sleeve are arranged in a rotating and smooth mode, an annular convex portion is arranged on the outer periphery of the gear shifting ring, a shifting fork matched with the annular convex portion is arranged on the outer periphery of the annular convex portion, and the shifting fork is used for shifting the gear shifting ring to move in the axial direction of the gear shifting shaft.