CN212202999U

CN212202999U - Three-linkage planetary gear type in-wheel two-gear automatic speed change mechanism

Info

Publication number: CN212202999U
Application number: CN202020299890.1U
Authority: CN
Inventors: 高炳钊; 孟德乐; 苗丽颖; 田萌健; 岳汉奇
Original assignee: Jilin University
Current assignee: Jilin University
Priority date: 2020-03-12
Filing date: 2020-03-12
Publication date: 2020-12-22
Anticipated expiration: 2030-03-12

Abstract

The utility model provides a trigeminy planetary gear formula is two keep off automatic speed change mechanism in the wheel, speed change mechanism comprises trigeminy planetary gear mechanism and pawl formula freewheel clutch, and among the trigeminy planetary gear mechanism, the meshing of the middle transmission planetary gear of trigeminy planetary gear is connected in the sun gear outside, and a fender planet wheel at trigeminy planetary gear both ends and two keep off the ring gear respectively with one keep off the ring gear and mesh mutually, and two sets of pawl formula freewheel clutches control through same control ring and keep off the ring gear respectively and keep off the ring gear with two the ring gear is coaxial to link firmly. The utility model discloses a cooperation of two sets of pawl formula freewheel clutch and trigeminy planetary gear train mechanism realizes that one keeps off and advances, keeps off or keep off and fall back and get into the neutral gear state, when satisfying the required great drive ratio of high-speed motor in-wheel transmission, can realize taking turns two and keep off automatic transmission.

Description

Three-linkage planetary gear type in-wheel two-gear automatic speed change mechanism

Technical Field

The utility model belongs to the technical field of electric vehicle transmission, especially to high-speed round of limit motor, concretely relates to trigeminy planetary gear formula is two in-wheel keeps off automatic speed change mechanisms.

Background

Compared with the traditional fuel oil vehicle, the electric vehicle has the advantages of environmental friendliness, high energy utilization rate, simple structure, convenience in realizing rich dynamic control and automatic driving and the like, only uses a single electric energy source, and becomes the main research direction of various large vehicle enterprises and colleges.

The driving modes of the electric automobile mainly comprise electric driving bridge type centralized driving, wheel edge speed reduction driving and hub motor direct driving. The electric driving bridge type driving mechanism has large volume, heavy weight and lower working efficiency; the unsprung mass and the dynamic load of the direct-drive driving mechanism of the hub motor are large; compared with the first two driving mechanisms, the wheel reduction driving mechanism has excellent comprehensive performance in all aspects, and becomes a main development direction of the driving mode of the electric automobile.

At present, the motor for the electric automobile gradually adopts a high-speed motor. The high-speed motor has the advantages of high energy density, small mass, small volume, manufacturing material saving and the like. The high-speed motor has a wide working range, but 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. However, at high rotational speeds, the efficiency and torque of the motor can drop rapidly. Therefore, the performance advantage of the high-speed motor cannot be exerted in the form of a wheel-side single reduction ratio, and the function of the two-stage transmission is to enable 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. At present, for the motor with the peak value of about 20000rpm, the required transmission ratio range is about 10-20, and the existing speed change mechanism is difficult to meet the requirement of the larger transmission ratio range.

Disclosure of Invention

To the defect that exists among the above-mentioned prior art, the utility model provides a triple planetary gear formula is two keeps off automatic speed change mechanism in the wheel can realize taking turns two and keep off automatic speed change when satisfying the required great drive ratio of high-speed motor internal drive. With the attached drawings, the technical scheme of the utility model is as follows:

a triple planetary gear type in-wheel two-gear automatic speed change mechanism consists of a triple planetary gear system mechanism and a pawl type overrunning clutch;

in the triple planetary gear train mechanism, a first-gear planetary gear, a transmission planetary gear and a second-gear planetary gear are sequentially and respectively arranged on a triple planetary gear 2, the transmission planetary gear is meshed and connected to the outer side of a sun gear 1, the first-gear planetary gear and the second-gear planetary gear are respectively meshed with a first-gear ring 3 and a second-gear ring 4, the triple planetary gear 2 is arranged on a planetary gear pin shaft 7 through a bearing, two ends of the planetary gear pin shaft are respectively and rotatably arranged on a first planet carrier 5 and a second planet carrier 6, the first planet carrier 5 and the second planet carrier 6 are fixedly combined, and the outer sides of the first planet carrier 5 and the second planet carrier 6 are arranged on a speed change mechanism shell through;

the pawl type overrunning clutches are divided into two groups, and the inner rings 11 of the two groups of clutches are respectively and coaxially fixedly connected with the first gear ring 3 and the second gear ring 4;

the two groups of pawl type overrunning clutches control corresponding pawls 13 to swing up and down through the same control ring 15, and are matched with a triple planetary gear train mechanism to realize forward in first gear, forward in second gear, reverse in first gear or reverse in second gear and neutral gear.

Furthermore, the two groups of pawl type overrunning clutches comprise a group of pawl type bidirectional controllable overrunning clutches and a group of pawl type unidirectional controllable overrunning clutches;

and a clutch inner ring 11 of the pawl type bidirectional controllable overrunning clutch is coaxially connected with the first gear ring 3 to realize first gear reversing.

Furthermore, a plurality of groups of control window groups consisting of a first gear control window, a second gear control window and a reverse gear control window are arranged on the control ring 15, wherein the first gear control window and the reverse gear control window respectively control a first gear pawl and a reverse gear pawl which are symmetrically arranged in the pawl type bidirectional controllable overrunning clutch to move reversely, the second gear control window controls a second gear pawl and the reverse gear pawl in the pawl type unidirectional controllable overrunning clutch to move in the same direction, and the mounting direction of the second gear pawl is opposite to the mounting direction of the reverse gear pawl.

Further, the end of the wheel shaft of the sun gear 1 is connected with the output shaft of the high-speed motor through a spline to realize power input, and the second planet carrier 6 is connected with the wheel hub through a spline to realize power output.

Further, the triple planetary gear 2 is mounted on a planetary gear pin 7 through a needle bearing 8;

copper gaskets 10 are arranged at two ends of the planet wheel pin shaft 7, and the copper gaskets 10 are arranged between the end face of the triple planet gear 2 and the side face of the first planet carrier 5 or the second planet carrier 6 in a cushioning mode.

Compared with the prior art, the beneficial effects of the utility model reside in that:

1. triple planetary gear formula is two keeps off automatic speed change mechanism in the wheel adopts triple planetary gear train, can provide the required great drive ratio of high-speed motor internal transmission, keeps off drive ratio through calculating one of them and can reach 17.5, and two keep off drive ratio can reach 13.6.

2. Triple planetary gear formula in-wheel two keep off automatic speed change mechanism adopts the controllable one way clutch of pawl formula, has realized the in-wheel low-speed gear, high-speed gear, neutral gear, has reversed the free switching between the fender to can be equipped with the motor as control actuating mechanism, can accomplish in short time and shift.

3. Triple planetary gear formula is two keep off automatic speed change mechanism in wheel adopts two sets of controllable one way clutch of pawl formula to share a control ring, adopts the pawl of a control ring simultaneous control axial both sides to lift up or put down promptly, realizes taking turns automatic gearshift, has greatly reduced speed change mechanism's volume, and whole set of taking turns internal speed change mechanism radial space size is steerable within 200mm, and axial space size is steerable within 120mm, satisfies the in-wheel space requirement of arranging completely.

Drawings

Fig. 1 is an axial structural schematic diagram of a triple planetary gear type in-wheel two-gear automatic speed change mechanism of the present invention;

FIG. 2 is a cross-sectional view taken along line A-A of FIG. 1;

fig. 3 is a schematic axial structure diagram of a pawl type bidirectional overrunning clutch in the in-wheel two-gear automatic transmission mechanism of the present invention;

fig. 4 is a schematic axial structure diagram of a pawl type one-way overrunning clutch in the in-wheel two-gear automatic transmission mechanism of the present invention;

fig. 5 is a transmission schematic diagram of the in-wheel two-gear automatic transmission mechanism of the present invention;

fig. 6 is a transmission diagram of the in-wheel two-gear automatic transmission mechanism of the present invention in a low-speed gear position;

fig. 7 is a transmission diagram of the in-wheel two-gear automatic transmission mechanism of the present invention in a high-speed gear position;

fig. 8 is a schematic structural diagram of the in-wheel two-shift automatic transmission mechanism of the present invention in a neutral position;

in the figure:

1-sun gear, 2-triple planet gear, 3-first gear ring gear, 4-second gear ring gear,

5-a first planet carrier, 6-a second planet carrier, 7-a planet pin, 8-a needle bearing,

9-deep groove ball bearing, 10-copper gasket, 11-clutch inner ring, 12-clutch outer ring,

13-pawl, 14-return spring, 15-control ring, 16-top ring,

Detailed Description

For clear and complete description of the technical solution and the specific working process of the present invention, the following embodiments are provided in conjunction with the accompanying drawings of the specification:

the utility model discloses a trigeminy planetary gear formula is two fender automatic speed change mechanisms in taking turns, include: the three-gear planetary gear train mechanism comprises a three-gear planetary gear train mechanism and pawl type overrunning clutches, wherein three-gear planetary gears in the three-gear planetary gear train mechanism are respectively integrated with a coaxial transmission planetary gear, a first gear planetary gear and a second gear planetary gear, a first gear ring and a second gear ring are correspondingly meshed with the first gear planetary gear and the second gear planetary gear, the pawl type overrunning clutches are provided with two groups, inner rings of the two groups of clutches are respectively in splined connection with the first gear ring and the second gear ring, locking or releasing of corresponding inner rings of the clutches is realized by controlling lifting of pawls of pawl type overrunning clutches on two sides, and then the corresponding first gear ring or second gear ring is controlled to be fixed or freely rotated, and finally gear position change of the speed change mechanism is realized.

As shown in fig. 1 and 2, the triple planetary gear train mechanism is composed of a sun gear 1, a triple planetary gear 2, a first gear ring gear 3, a second gear ring gear 4 and a combined planet carrier. Wherein:

the three sets of triple planet gears are uniformly distributed on the outer side of the circumference of the sun gear 1, and each set of triple planet gear comprises a transmission planet gear positioned in the axial middle position and a first-gear planet gear and a second-gear planet gear which are respectively positioned on two sides of the transmission planet gear; the first-gear planet wheel is positioned on one side close to the high-speed motor, the outer circumferential gear teeth are meshed with the first-gear ring gear 3, the second-gear planet wheel is positioned on one side close to the wheel hub, and the outer circumferential gear teeth are meshed with the second-gear ring gear 4; the first-gear planet wheel, the transmission planet gear and the second-gear planet wheel are coaxially arranged, and the triple planet wheel is integrally processed; and a plurality of groups of needle roller bearings 8 are uniformly arranged in the inner hole of the triple planet wheel along the axial direction, and the triple planet wheel is rotatably arranged on a planet wheel pin shaft 7 through the needle roller bearings 8.

The combined planet carrier is formed by relatively assembling a first planet carrier 5 positioned on one side of a high-speed motor and a second planet carrier 6 positioned on one side of a hub, wherein the first planet carrier 5 and the second planet carrier 6 are positioned by matching and buckling a positioning protrusion and a positioning groove, and are fixedly connected into a whole by a long bolt penetrating through the first planet carrier 5 and the second planet carrier 6, and other parts of a triple planetary gear train mechanism and two groups of pawl type one-way controllable overrunning clutches are integrated between the first planet carrier 5 and the second planet carrier 6, so that the structure of the whole speed change mechanism is more compact, and the installation space is saved.

The two ends of the planet wheel pin shaft 7 are respectively and fixedly installed on the combined planet carrier, wherein one end of the planet wheel pin shaft 7 is inserted into the trapezoidal installation groove of the inner end face of the first planet carrier 5, a copper gasket 10 is installed on the corresponding end portion of the planet wheel pin shaft 7, one end of the copper gasket 10 is in contact with the outer end face of the corresponding first stop planet wheel, and the other end of the copper gasket 10 is installed in the trapezoidal installation groove of the inner end face of the first planet carrier 5 in a manner of being matched with the planet wheel pin shaft 7; the other end of the planet wheel pin shaft 7 is inserted into a trapezoid mounting groove in the inner end face of the second planet carrier 6, another copper gasket 10 is also mounted on the corresponding end portion of the planet wheel pin shaft 7, one end of the copper gasket 10 is in contact with the outer end face of the corresponding second planet wheel, and the other end of the copper gasket 10 is mounted in the trapezoid mounting groove in the inner end face of the second planet carrier 6 in a manner of being matched with the planet wheel pin shaft 7; the copper gasket 10 is used for realizing axial spacing of the triple planet wheel on one hand, and can effectively prevent abrasion between the triple planet wheel and the corresponding planet carrier on the other hand.

In the triple planetary gear train mechanism, a sun gear 1 positioned in the middle of three groups of triple planetary gears is respectively and simultaneously meshed with a transmission planetary gear of the triple planetary gears, the end part of a wheel shaft of the sun gear 1 is connected with an output shaft of a high-speed motor through a spline to realize power input, and the high-speed motor is fixed on the outer side of a shell of the transmission mechanism; the second planet carrier 6 positioned on one side of the vehicle hub is connected with the hub through a spline to realize power output; further, the outer circumferential side surfaces of the first and

second carriers

5 and 6 are supported and mounted on the inner wall of the housing of the transmission mechanism by deep groove ball bearings 9.

As shown in fig. 3 and 4, there are two groups of pawl type overrunning clutches, each of which is composed of a clutch inner ring 11, a clutch outer ring 12, pawls 13, a return spring 14 and a control ring 15. Wherein:

among the automatic speed change mechanism, select to realize reversing gear through which fender position, then this keeps off the pawl formula freewheel clutch that the fender position ring gear corresponds is the two-way controllable freewheel clutch of pawl formula, and another keeps off the pawl formula freewheel clutch that the gear ring gear corresponds and is the one-way controllable freewheel clutch of pawl formula. In the embodiment, a first gear reverse gear is adopted, so that the first gear outer ring 3 is installed corresponding to the pawl type bidirectional controllable overrunning clutch, and the second gear outer ring 4 is installed corresponding to the pawl type unidirectional controllable overrunning clutch.

In the two groups of pawl type overrunning clutches, two groups of clutch inner rings 11 are coaxially arranged, and the inner circumferential surfaces of the two groups of clutch inner rings 11 are respectively connected with the outer splines of the corresponding first gear ring 3 and the second gear ring 4. The gear teeth on the outer side of the inner ring 11 of the clutch in the pawl type bidirectional controllable overrunning clutch are bidirectional gear teeth, so that clamping of a bidirectional pawl can be realized; the gear teeth on the outer side of the inner ring 11 of the clutch in the pawl type bidirectional controllable overrunning clutch are unidirectional gear teeth, and clamping of a unidirectional pawl can be realized.

In the two groups of pawl type overrunning clutches, the outer rings 12 of the two groups of clutches are respectively arranged at the outer sides of the corresponding inner rings 11 of the clutches, and the outer rings 12 of the two groups of clutches are respectively fixed on a shell of the speed change mechanism through pins so as to realize the fixation of the relative positions.

In the two groups of pawl type overrunning clutches, pawl assemblies consisting of pawls 13 and return springs 14 are distributed in groups and in the same direction and are arranged in an annular gap between a corresponding clutch outer ring 12 and a corresponding clutch inner ring 11, wherein, one end of a return spring 14 is arranged in a spring groove arranged on the inner side of the outer ring 12 of the clutch, the bottom of a pawl 13 is rotatably arranged in a pawl groove arranged on the inner side of the outer ring 12 of the clutch, the top of the pawl 13 is connected with the other end of the return spring 14, a shifting pin vertical to the side end surface is arranged on the side end surface of the pawl 13, the pawls 13 in the same group of clutches can synchronously swing up and down around the central axis of the bottom of the pawl under the driving of the shifting pin and the elastic action of a return spring 14, and can realize the clamping fixation or relative free rotation between the clutch inner ring 11 and the clutch outer ring 12 by matching with the gear teeth on the outer side of the clutch inner ring 11;

in the pawl type bidirectional controllable overrunning clutch, a plurality of pairs of pawl assemblies are distributed between a clutch outer ring 12 and a clutch inner ring 11 along the circumferential direction, wherein two pawls 13 in each pair of pawl assemblies are symmetrically arranged along the radial direction of the clutch, one pawl 13 in each pair of pawl assemblies is a first-gear pawl, and the other pawl 13 is a reverse-gear pawl. The installation direction of the first-gear pawl is the same as the forward rotation direction of the clutch inner ring 11, so that the installation direction of the reverse-gear pawl is the same as the reverse rotation direction of the clutch inner ring 11.

In the pawl type one-way controllable overrunning clutch, a plurality of pawl assemblies are distributed between the outer ring 12 and the inner ring 11 of the clutch along the circumferential direction, and the pawl assemblies in the pawl type one-way controllable overrunning clutch correspond to the pawl assemblies in the pawl type two-way controllable overrunning clutch one to one. The pawl 13 in the one-way controllable overrunning clutch is a secondary pawl, the mounting direction of the secondary pawl is the same as that of a primary pawl, the mounting direction of the secondary pawl is opposite to that of a reverse pawl, namely the mounting direction of the secondary pawl is the same as that of the forward rotation of the inner ring 11 of the clutch

Two groups of pawl type overrunning clutches share one control ring 15, namely, the pawls in the two groups of pawl type overrunning clutches are simultaneously controlled to lift or fall through the same control ring 15, so that forward gear in first gear, forward gear in second gear, reverse gear in first gear and neutral gear are realized.

The control ring 15 is coaxially installed at the axial middle position of the two groups of pawl type overrunning clutches, wherein a plurality of groups of control window groups are uniformly arranged in the circumferential direction of the control ring 15, each group of control window groups consists of three control windows, and each control window consists of a low control surface, a high control surface and a transition surface connected between the low control surface and the high control surface.

The low control surface is a control surface close to the circle center of the control ring 15, and when the pin of the pawl 13 is positioned at the low control surface, the pawl 13 is in a falling state; the high control surface is a control surface far away from the circle center of the control ring 15, and when the pin of the pawl 13 is positioned at the high control surface, the pawl 13 is in a lifting state; the transition surface is a one-way and smooth connection surface connected between the low control surface and the high control surface, when the shift pin of the pawl 13 moves from the low control surface to the high control surface along the transition surface, the pawl 13 is gradually lifted from a falling state, namely is gradually separated from the ratchets on the outer side of the inner ring of the clutch, when the shift pin of the pawl 13 moves to the middle position of the transition surface, the pawl 13 is just separated from the ratchets on the outer side of the inner ring of the clutch, and the pawl 13 continues to be lifted along with the shift pin of the pawl 13 continuing to move to the high control position along the transition surface until the pawl 13 moves to the high control surface, and the pawl 13 is completely lifted.

The three control windows in each control window group are respectively a first-gear control window, a second-gear control window and a reverse-gear control window, wherein the reverse-gear control window and the second-gear control window are structurally the same, the first-gear control window and the reverse-gear control window and the structure of the second-gear control window are radially symmetrical relative to the control ring 15, namely, the pawl controlled by the first-gear control window and the second-gear control window moves in the same direction, and the pawl controlled by the first-gear control window moves in the opposite direction to the pawl controlled by the reverse-gear control window and the second-gear control window.

On the control ring 15, a first gear control window and a reverse gear control window are respectively and correspondingly installed with a first gear pawl and a reverse gear pawl in a pawl type bidirectional controllable overrunning clutch one by one, and a second gear control window is installed with a second gear pawl in a pawl type unidirectional controllable overrunning clutch one by one, so that when a pin shifting pin of the first gear pawl moves from a high control surface to a low control surface to enable the first gear pawl to gradually fall down, the reverse gear pawl and a pin shifting pin of the second gear pawl simultaneously move from the low control surface to the high control surface to enable the reverse gear pawl and the second gear pawl to gradually lift up, otherwise, when the pin shifting pin of the first gear pawl moves from the low control surface to the high control surface to enable the first gear pawl and the second gear pawl to gradually fall down, the reverse gear pawl and the second gear pawl simultaneously move from the high control surface to the low control surface; when the shift pins of the first gear pawl, the second gear pawl and the reverse gear pawl are all located at the middle positions of the transition surfaces, the first gear pawl, the second gear pawl and the reverse gear pawl are located at the positions which are just lifted and separated from the gear ring on the outer side of the clutch inner ring 11.

According to the structure of the two groups of pawl type overrunning clutches, when the inner rings 11 of the clutches in the pawl type bidirectional controllable overrunning clutch and the pawl type unidirectional controllable overrunning clutch rotate reversely, the control ring 15 is driven to rotate by a certain angle through the clutch control mechanism, the first gear pawl is in a falling state under the control of the control ring 15, and the second gear pawl and the reverse gear pawl are in a lifting state. Because the installation direction of the first-gear pawl is the same as the forward rotation direction of the clutch inner ring 11, namely the rotation direction of the clutch inner ring 11 is opposite to that of the first-gear pawl, the first-gear pawl is clamped with the clutch inner ring, the clutch inner ring 11 and the clutch outer ring 12 of the pawl type bidirectional controllable overrunning clutch are clamped and fixed relatively, and therefore power transmission is achieved, and the second-gear pawl and the reverse-gear pawl are both in a lifting state, so that the second-gear pawl and the reverse-gear pawl are both separated from the corresponding clutch inner ring 11, namely the clutch inner ring 11 is separated from the clutch outer ring 12, and no power transmission is achieved. At this time, the pawl type one-way controllable overrunning clutch installed corresponding to the second gear ring 4 is in a one-way overrunning state in which the clutch inner ring 11 rotates reversely, and the pawl type two-way controllable overrunning clutch installed corresponding to the first gear ring 3 is in a one-way power transmission state in which the clutch inner ring 11 rotates reversely.

When the clutch inner rings 11 in the pawl type bidirectional controllable overrunning clutch and the pawl type unidirectional controllable overrunning clutch rotate reversely, the control ring 15 is driven to rotate for a certain angle through the clutch control mechanism, the first-gear pawl is in a lifting state under the control of the control ring 15, and the second-gear pawl and the reverse-gear pawl are in a falling state. Because the installation direction of the two-gear pawl is the same as the positive rotation direction of the clutch inner ring 11, namely the rotation direction of the clutch inner ring 11 is opposite to the same, the two-gear pawl is clamped with the clutch inner ring, the clutch inner ring 11 and the clutch outer ring 12 of the pawl type one-way controllable overrunning clutch are clamped and fixed relatively, so that power transmission is realized, the one-gear pawl is in a lifting state, the one-gear pawl is separated from the corresponding clutch inner ring 11 at the moment, the reverse pawl is in a falling state, but because the installation direction of the reverse pawl is the same as the reverse rotation direction of the clutch inner ring 11, along with the reverse rotation of the clutch inner ring 11, the reverse pawl is pressed to one side of the clutch outer ring 12 by the gear teeth outside the clutch inner ring 11, namely the reverse pawl is not clamped with the gear teeth outside the clutch inner ring 11, so the clutch inner ring 11 and the clutch outer ring 12 of the pawl type controllable two-way overrunning clutch are separated, but no power transfer. At this time, the pawl type bidirectional controllable overrunning clutch installed corresponding to the first gear ring gear 3 is in a one-way overrunning state in which the clutch inner ring 11 rotates reversely, and the pawl type one-way controllable overrunning clutch installed corresponding to the second gear ring gear 4 is in a one-way power transmission state in which the clutch inner ring 11 rotates reversely.

When the clutch inner rings 3 in the pawl type bidirectional controllable overrunning clutch and the pawl type unidirectional controllable overrunning clutch rotate in the positive direction, the control ring 15 is driven to rotate for a certain angle through the clutch control mechanism, the first-gear pawl is in a lifting state under the control of the control ring 15, and the second-gear pawl and the reverse-gear pawl are in a falling state. Because the installation direction of the secondary pawl is the same as the forward rotation direction of the clutch inner ring 11, although the secondary pawl is in a falling state, the installation direction of the secondary pawl is the same as the rotation direction of the clutch inner ring 3 at the moment, and along with the forward rotation of the clutch inner ring 11, the secondary pawl presses the gear teeth outside the clutch inner ring 11 to one side of the clutch outer ring 12, namely the secondary pawl is not clamped with the gear teeth outside the clutch inner ring 11, so the clutch inner ring 11 of the pawl type one-way controllable overrunning clutch is separated from the clutch outer ring 12 and does not have power transmission; at the moment, the first gear pawl is lifted, so that the first gear pawl is not clamped with the corresponding clutch inner ring 11, the reverse gear pawl falls down, the installation direction of the reverse gear pawl is the same as the reverse rotation direction of the clutch inner ring 11, so that the installation direction of the reverse gear pawl is opposite to the rotation direction of the clutch inner ring 11, the reverse gear pawl is clamped with the corresponding clutch inner ring 12, and the clutch inner ring 11 and the clutch outer ring 12 of the pawl type bidirectional controllable overrunning clutch are clamped and fixed relatively, so that power transmission is realized. At this time, the pawl type one-way controllable overrunning clutch correspondingly arranged to the second gear ring 4 is in a one-way overrunning state of positive rotation of the clutch inner ring 11, and the pawl type two-way controllable overrunning clutch correspondingly arranged to the first gear ring 3 is in a one-way power transmission state of positive rotation of the clutch inner ring 11.

When the clutch control mechanism drives the control ring 15 to rotate for a certain angle, under the control of the control ring 15, the shift pins of the first-gear pawl, the second-gear pawl and the reverse-gear pawl are all positioned at the middle positions of the transition surfaces, at the moment, the first-gear pawl, the second-gear pawl and the reverse-gear pawl are all positioned at the positions which are just lifted and separated from the gear ring outside the inner ring 11 of the clutch, at the moment, the inner ring 11 and the outer ring 12 of the clutch in the bidirectional controllable overrunning clutch and the pawl type unidirectional controllable overrunning clutch are all separated, and the bidirectional controllable overrunning clutch and the pawl type unidirectional controllable overrunning clutch realize bidirectional overrunning.

And a top ring 16 is coaxially arranged between the outer rings 12 of the two groups of pawl type one-way controllable overrunning clutches, and the top ring 16 limits the axial distance between the outer rings 12 of the clutches so as to control the axial installation distance between the two groups of pawl type one-way controllable overrunning clutches.

As shown in fig. 2, the clutch inner rings 11 of the two groups of pawl type unidirectional controllable overrunning clutches are respectively in splined connection with the first gear ring 3 and the second gear ring 4, the first gear ring 3 and the second gear ring 4 are respectively engaged with the first gear planet wheel and the second gear planet wheel, the transmission planet gear positioned in the middle of the triple planet wheel and the sun gear 1 engaged with the transmission planet gear are both positioned between the two clutch inner rings 11, for reasonable arrangement, the clutch inner rings 11 are designed into a half-shell structure, the two clutch inner rings 11 are oppositely arranged, and a cavity is formed by matching the first gear ring 3 and the second gear ring 4, which is more beneficial to the arrangement of internal components.

The control mechanism of the pawl type bidirectional controllable overrunning clutch and the pawl type unidirectional controllable overrunning clutch can be driven by a motor so as to quickly and accurately control the rotating angle of the control ring 15.

As shown in fig. 5, after power is output by the high-speed motor, the power is input to the speed change mechanism from the sun gear 1, the power is transmitted to the transmission planetary gear in the middle of the triple planetary gear 2 through the sun gear, and synchronously drives the first-gear planetary gear and the second-gear planetary gear to rotate, under the control of the control ring 15, pawls in the two groups of pawl type overrunning clutches rise or fall to realize the transmission of the power or the overrunning of the pawl type overrunning clutches, so that the first-gear ring 3 or the second-gear ring 4 in spline connection with the clutch inner rings 11 of the two groups of pawl type overrunning clutches are relatively fixed or rotate, in the planetary gear train, when the ring gears are fixed, the power is transmitted through the sun gear 1, then is transmitted through the first-gear planetary gear or the second-gear planetary gear, and finally is output to the hub from the second planetary gear carrier 6, so as to realize the forward; when both the first-gear ring gear 3 and the second-gear ring gear 4 rotate freely, the neutral state is entered.

The concrete working process of speed change mechanism explains as follows:

1. the first gear advancing process:

as shown in fig. 6, when the sun gear 1 rotates forward under the driving of the motor, the sun gear 1 drives the triple planetary gear 2 to rotate reversely, the first-gear planetary gear and the second-gear planetary gear at the two ends of the triple planetary gear 2 respectively apply a driving force of reverse rotation to the first-gear ring 3 and the second-gear ring 4 which are connected with the first-gear planetary gear in a spline manner, the clutch inner ring 11 of the pawl type bidirectional controllable overrunning clutch installed in cooperation with the first-gear ring 3 and the clutch inner ring 11 of the pawl type unidirectional controllable overrunning clutch installed in cooperation with the second-gear ring 4 have a movement trend of reverse rotation, at this time, the control ring 15 is controlled to rotate by the clutch control mechanism, so that the pawl type unidirectional controllable overrunning clutch is in a unidirectional overrunning state in which the clutch inner ring 11 rotates reversely, and the pawl type bidirectional controllable overrunning clutch is in a unidirectional power transmission state in which the clutch inner, at this time, the clutch inner ring 11 and the clutch outer ring 12 of the pawl type bidirectional controllable overrunning clutch are relatively fixed, namely, the first gear ring gear 3 is relatively fixed, the second gear ring gear 4 can rotate freely in the reverse direction, and according to the transmission characteristic of the planetary gear train, after power is input through the sun gear 1, because the first gear ring gear 3 is relatively fixed, the power is transmitted through the first gear planetary gear of the triple planetary gear 2 and is finally output through the second planetary gear carrier 6, and the rotation direction of the second planetary gear carrier 6 is the same as that of the sun gear, at this time, the speed change mechanism realizes the forward of the first gear.

2. A second-stage advancing process:

as shown in fig. 7, when the sun gear 1 rotates forward under the driving of the motor, the sun gear 1 drives the triple planetary gear 2 to rotate reversely, the first-gear planetary gear and the second-gear planetary gear at the two ends of the triple planetary gear 2 respectively apply a driving force of reverse rotation to the first-gear ring 3 and the second-gear ring 4 which are connected with the first-gear planetary gear in a spline manner, the clutch inner ring 11 of the pawl type bidirectional controllable overrunning clutch installed in cooperation with the first-gear ring 3 and the clutch inner ring 11 of the pawl type unidirectional controllable overrunning clutch installed in cooperation with the second-gear ring 4 have a movement trend of reverse rotation, at this time, the control ring 15 is controlled to rotate by the clutch control mechanism, so that the pawl type bidirectional controllable overrunning clutch is in a unidirectional overrunning state in which the clutch inner ring 11 rotates reversely, and the pawl type unidirectional controllable overrunning clutch is in a unidirectional power transmission state in which the clutch inner ring, at this time, the clutch inner ring 11 and the clutch outer ring 12 of the ratchet type unidirectional controllable overrunning clutch are relatively fixed, namely the second gear ring 4 is relatively fixed, the first gear ring 3 can rotate freely in the reverse direction, and according to the transmission characteristic of the planetary gear train, after power is input through the sun gear 1, because the second gear ring 4 is relatively fixed, the power is transmitted through the second gear planetary gear of the triple planetary gear 2 and is finally output through the second planetary gear frame 6, and the rotation direction of the second planetary gear frame 6 is the same as that of the sun gear, at this time, the speed change mechanism realizes the second gear advancing.

3. A gear reversing process:

as shown in fig. 6, when the sun gear 1 rotates reversely under the driving of the motor, the sun gear 1 drives the triple planetary gear 2 to rotate forwardly, the first-gear planetary gear and the second-gear planetary gear at the two ends of the triple planetary gear 2 respectively apply a forward rotating driving force to the first-gear ring 3 and the second-gear ring 4 which are connected with the first-gear planetary gear in a spline manner, the clutch inner ring 11 of the pawl type bidirectional controllable overrunning clutch which is installed in cooperation with the first-gear ring 3 and the clutch inner ring 11 of the pawl type unidirectional controllable overrunning clutch which is installed in cooperation with the second-gear ring 4 have a forward rotating movement trend, at this time, the control ring 15 is controlled to rotate by the clutch control mechanism, so that the pawl type bidirectional controllable overrunning clutch is in a unidirectional power transmission state of the forward rotation of the clutch inner ring 11, and the pawl type unidirectional controllable overrunning clutch is in a unidirectional overrunning state of the forward rotation of, at this time, the clutch inner ring 11 and the clutch outer ring 12 of the pawl type bidirectional controllable overrunning clutch are relatively fixed, namely, the first gear ring gear 3 is relatively fixed, and the second gear ring gear 4 can freely rotate in the reverse direction, according to the transmission characteristic of the planetary gear train, after power is input through the sun gear 1, because the first gear ring gear 3 is relatively fixed, the power is transmitted through the first gear planetary gear of the triple planetary gear 2 and is finally output through the second planetary gear carrier 6, and the rotation direction of the second planetary gear carrier 6 is the same as that of the sun gear, at this time, the speed change mechanism realizes the first gear reverse.

4. Entering a neutral gear process:

as shown in fig. 8, when the sun gear 1 is driven by the motor to rotate in the forward direction or the reverse direction, the sun gear 1 drives the triple planetary gear 2 to rotate, the first-gear planetary gear and the second-gear planetary gear at the two ends of the triple planetary gear 2 respectively apply a rotary driving force to the first-gear ring 3 and the second-gear ring 4 which are connected with the first-gear planetary gear in a spline manner, the clutch inner ring 11 of the pawl type bidirectional controllable overrunning clutch installed in cooperation with the first-gear ring 3 and the clutch inner ring 11 of the pawl type unidirectional controllable overrunning clutch installed in cooperation with the second-gear ring 4 have a rotary movement trend, at this time, the control ring 15 is controlled to rotate by the clutch control mechanism, so that the pawl type bidirectional controllable overrunning clutch and the pawl type unidirectional controllable overrunning clutch are both in a bidirectional overrunning state, at this time, the clutch inner rings 11 and the clutch outer ring 12 of the pawl type bidirectional controllable overrunning clutch and the pawl type unidirectional controllable overrunning, the first gear ring gear 3 and the second gear ring gear 4 both rotate freely, and the planet carrier does not have power output according to the transmission characteristics of the planetary gear train, and the speed change mechanism enters a neutral gear state.

Claims

1. The utility model provides a triple planetary gear formula is two keeps off automatic speed change mechanism in taking turns which characterized in that:

the clutch consists of a triple planetary gear train mechanism and a pawl type overrunning clutch;

in the triple planetary gear train mechanism, a first-gear planet gear, a transmission planet gear and a second-gear planet gear are sequentially and respectively arranged on a triple planetary gear (2), the transmission planet gear is meshed and connected to the outer side of a sun gear (1), the first-gear planet gear and the second-gear planet gear are respectively meshed with a first-gear ring (3) and a second-gear ring (4), the triple planetary gear (2) is arranged on a planet gear pin shaft (7) through a bearing, two ends of the planet gear pin shaft are respectively and rotatably arranged on a first planet carrier (5) and a second planet carrier (6), the first planet carrier (5) and the second planet carrier (6) are combined and fixedly arranged, and the outer sides of the first planet carrier (5) and the second planet carrier (6) are arranged on a speed change mechanism shell through bearings;

the pawl type overrunning clutches are divided into two groups, and inner rings (11) of the two groups of clutches are respectively and coaxially fixedly connected with the first gear ring (3) and the second gear ring (4);

the two groups of pawl type overrunning clutches control corresponding pawls (13) to swing up and down through the same control ring (15), and are matched with a triple planetary gear train mechanism to realize first-gear forward movement, second-gear forward movement, first-gear reverse movement, second-gear reverse movement and neutral gear.

2. The triple planetary gear type in-wheel two-gear automatic speed change mechanism according to claim 1, wherein:

the two groups of pawl type overrunning clutches comprise a group of pawl type bidirectional controllable overrunning clutches and a group of pawl type unidirectional controllable overrunning clutches;

and a clutch inner ring (11) of the pawl type bidirectional controllable overrunning clutch is coaxially connected with the first gear ring (3) to realize first gear reversing.

3. The triple planetary gear type in-wheel two-gear automatic speed change mechanism according to claim 2, wherein:

the control ring (15) is provided with a plurality of groups of control window groups which are respectively composed of a first gear control window, a second gear control window and a reverse gear control window, wherein the first gear control window and the reverse gear control window respectively control a first gear pawl and a reverse gear pawl which are symmetrically arranged in the pawl type bidirectional controllable overrunning clutch to move reversely, the second gear control window controls a second gear pawl and the reverse gear pawl in the pawl type unidirectional controllable overrunning clutch to move in the same direction, and the mounting direction of the second gear pawl is opposite to the mounting direction of the reverse gear pawl.

4. The triple planetary gear type in-wheel two-gear automatic speed change mechanism according to claim 1, wherein:

the end part of a wheel shaft of the sun wheel (1) is connected with an output shaft of the high-speed motor through a spline to realize power input, and the second planet carrier (6) is connected with the wheel hub through the spline to realize power output.

5. The triple planetary gear type in-wheel two-gear automatic speed change mechanism according to claim 1, wherein:

the triple planetary gear (2) is arranged on a planetary gear pin shaft (7) through a needle bearing (8);

copper gaskets (10) are installed at two ends of the planet wheel pin shaft (7), and the copper gaskets (10) are installed between the end face of the triple planet gear (2) and the side face of the first planet carrier (5) or the second planet carrier (6) in a cushioning mode.