CN111336225B - Triple planetary gear type in-wheel two-gear automatic speed change mechanism and gear shifting control method thereof - Google Patents
Triple planetary gear type in-wheel two-gear automatic speed change mechanism and gear shifting control method thereof Download PDFInfo
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- CN111336225B CN111336225B CN202010169083.2A CN202010169083A CN111336225B CN 111336225 B CN111336225 B CN 111336225B CN 202010169083 A CN202010169083 A CN 202010169083A CN 111336225 B CN111336225 B CN 111336225B
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
- F16H3/70—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/68—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for stepped gearings
- F16H61/684—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for stepped gearings without interruption of drive
- F16H61/686—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for stepped gearings without interruption of drive with orbital gears
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/0021—Transmissions for multiple ratios specially adapted for electric vehicles
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
- F16H2200/0034—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising two forward speeds
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/0082—Transmissions for multiple ratios characterised by the number of reverse speeds
- F16H2200/0086—Transmissions for multiple ratios characterised by the number of reverse speeds the gear ratios comprising two reverse speeds
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Abstract
The invention provides a triple planetary gear type in-wheel two-gear automatic speed change mechanism and a gear shifting control method thereof, wherein the speed change mechanism consists of a triple planetary gear mechanism and a pawl type overrunning clutch, in the triple planetary gear mechanism, a transmission planetary gear in the middle of a triple planetary gear is meshed and connected with the outer side of a sun gear, a first-gear planetary gear and a second-gear planetary gear at two ends of the triple planetary gear are respectively meshed with a first-gear ring and a second-gear ring, and two groups of pawl type overrunning clutches are controlled by the same control ring and are respectively coaxially and fixedly connected with the first-gear ring gear and the second-gear ring; according to the gear shifting control method, the first-gear forward movement, the second-gear forward movement, the first-gear reverse movement or the second-gear reverse movement and the neutral state are realized through the cooperation of the two groups of pawl overrunning clutches and the triple planetary gear train mechanism. The invention can realize two-gear automatic speed change in the wheel while meeting the larger transmission ratio required by the transmission in the wheel of the high-speed motor.
Description
Technical Field
The invention belongs to the technical field of electric vehicle transmission, and particularly relates to a triple planetary gear type in-wheel two-gear automatic speed change mechanism and a gear shifting control method thereof.
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 dynamics control, automatic driving and the like, and is used as a main research direction of various large vehicle enterprises and universities.
The electric automobile driving mode mainly comprises three modes of electric driving bridge type centralized driving, wheel side speed reduction driving and wheel hub motor direct driving. The electric drive bridge type driving mechanism has large volume, large weight and low working efficiency; the unsprung mass of the hub motor direct-drive type driving mechanism is larger, and the dynamic load is larger; compared with the first two driving mechanisms, the wheel-side reduction driving mechanism has excellent comprehensive performance in all aspects, and has become a main development direction of an electric automobile driving mode.
Currently, a motor for an 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 working range of the high-speed motor is wider, but the torque of the motor is very sufficient and the working efficiency is relatively higher under the condition of medium and low rotation speed. However, at high rotational speeds, the efficiency and torque of the motor drop rapidly. Therefore, the wheel side single reduction ratio mode cannot exert the performance advantage of the high-speed motor, and the two-stage transmission has the effect 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. The current motor with the peak value of 20000rpm has the required gear ratio range of about 10-20, and the prior speed change mechanism has difficulty in meeting the requirement of the larger gear ratio range.
Disclosure of Invention
Aiming at the defects in the prior art, the invention provides a triple planetary gear type in-wheel two-gear automatic speed change mechanism and a gear shifting control method thereof, which can realize in-wheel two-gear automatic speed change while meeting the larger transmission ratio required by in-wheel transmission of a high-speed motor. The technical scheme of the invention is as follows:
the gear shifting control method of the triple planetary gear type in-wheel two-gear automatic speed change mechanism is applied to the triple planetary gear type in-wheel two-gear automatic speed change mechanism, and the triple planetary gear type in-wheel two-gear automatic speed change mechanism consists of a triple planetary gear mechanism and a pawl 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 arranged on a triple planetary gear 2, the transmission planetary gear is in meshed connection with 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 arranged in a combined mode, 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 clutch is provided with two groups, and the inner rings 11 of the two groups of clutches are respectively and fixedly connected with the first gear ring 3 and the second gear ring 4 in a coaxial way;
the two groups of pawl type overrunning clutches control the corresponding pawls 13 to swing up and down through the same control ring 15 and realize first gear forward, second gear forward, first gear reverse and neutral gear by being matched with a triple planetary gear train mechanism, and 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;
the clutch inner ring 11 of the pawl type bidirectional controllable overrunning clutch is coaxially connected with the first gear ring 3 so as to realize first gear reversing;
the power output by the high-speed motor is input to a speed change mechanism through a sun gear 1, is transmitted to a transmission planetary gear in the middle of a triple planetary gear 2 through the sun gear, synchronously drives a first-gear planetary gear and a second-gear planetary gear to rotate, and under the control of a control ring 15, pawls 13 in two groups of pawl overrunning clutches are lifted or fallen to realize the transmission of power or overrunning of the pawl overrunning clutches, so that a first-gear ring 3 or a second-gear ring 4 which is respectively in spline connection with clutch inner rings 11 of the two groups of pawl overrunning clutches is relatively fixed or rotated, and in the triple planetary gear, when the first-gear ring 3 or the second-gear ring 4 is relatively fixed, the power is transmitted through the first-gear planetary gear or the second-gear planetary gear after being input through the sun gear 1, and finally is output to a hub from a second planetary carrier 6, so that the first-gear forward, the second-gear forward or the first-gear reverse is realized, and when the two groups of pawl overrunning clutches are both in two directions, the first-gear ring 3 and the second-gear ring 4 are free to rotate.
Further, the control ring 15 is provided with a plurality 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 the reverse gear pawl and the first gear pawl which are symmetrically arranged in the pawl type bidirectional controllable overrunning clutch to move reversely, the second gear control window controls the second gear pawl and the reverse gear pawl in the pawl type unidirectional controllable overrunning clutch to move in the same direction, and the installation direction of the second gear pawl is opposite to that of the reverse gear pawl.
Further, the end part of the wheel shaft of the sun wheel 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 arranged on a planetary pin shaft 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 planetary gear 2 and the side face of the first planet carrier 5 or the side face of the second planet carrier 6 in a cushioning mode.
Further, the first gear forward control process specifically includes:
when the sun gear 1 rotates positively under the drive of a motor, the sun gear 1 drives the triple planetary gear 2 to rotate reversely, a driving force for reverse rotation is applied by meshing the first-gear planetary gear at one end of the triple planetary gear 2 with the first-gear ring 3, a driving force for reverse rotation is applied by meshing the second-gear planetary gear at the other end with the second-gear ring 4, the clutch inner ring 11 of the pawl type bidirectional controllable overrunning clutch which is matched with the first-gear ring 3 and the clutch inner ring 11 of the pawl type unidirectional controllable overrunning clutch which is matched with the second-gear ring 4 have a movement tendency for reverse rotation, at the moment, the control ring 15 is controlled to rotate through the clutch control mechanism, so that the pawl type unidirectional controllable overrunning clutch is in a unidirectional power transmission state of reversing the clutch inner ring 11, at the moment, the clutch inner ring 11 of the pawl type bidirectional controllable overrunning clutch is relatively fixed with the clutch outer ring 12, namely the first-gear ring 3 is relatively fixed, the second-gear ring 4 can rotate reversely, and according to the transmission characteristics of the planetary gear train, power is input through the sun gear 1, and the first planetary gear is relatively fixed with the planetary gear carrier 6, and finally the planetary gear is driven through the planetary gear carrier 6, and the planetary gear is driven through the first planetary gear carrier 6 and the planetary gear carrier is driven by the same rotation;
The second gear forward control process specifically comprises the following steps:
when the sun gear 1 rotates positively under the drive of a motor, the sun gear 1 drives the triple planetary gear 2 to rotate reversely, a driving force for reverse rotation is applied by meshing a first-gear planetary gear at one end of the triple planetary gear 2 with a first-gear ring 3, a driving force for reverse rotation is applied by meshing a second-gear planetary gear at the other end with a second-gear ring 4, a clutch inner ring 11 of a pawl type bidirectional controllable overrunning clutch which is matched with the first-gear ring 3 and a clutch inner ring 11 of a pawl type unidirectional controllable overrunning clutch which is matched with the second-gear ring 4 have a movement tendency for reverse rotation, at the moment, the control ring 15 is controlled to rotate through a clutch control mechanism, so that the pawl type unidirectional controllable overrunning clutch is in a unidirectional power transmission state of reversing the clutch inner ring 11, at the moment, the clutch inner ring 11 of the pawl type unidirectional controllable overrunning clutch is fixed with the clutch outer ring 12 relatively, namely the second-gear ring 4 is fixed relatively, the first-gear ring 3 can rotate reversely, and according to the transmission characteristics of the planetary gear, power is input through the sun gear 1, the second planetary gear 4 is fixed relatively to the planetary gear carrier 6, and finally the planetary gear is driven through the second planetary gear carrier 6, and the planetary gear is driven by the same speed, and the planetary gear carrier is driven by the second planetary gear carrier 6;
The first-gear reversing control process specifically comprises the following steps:
when the sun gear 1 is driven by a motor to reversely rotate, the sun gear 1 drives the triple planetary gear 2 to positively rotate, a driving force for reverse rotation is applied by meshing the first-gear planetary gear at one end of the triple planetary gear 2 with the first-gear ring 3, a driving force for reverse rotation is applied by meshing the second-gear planetary gear at the other end with the second-gear ring 4, the clutch inner ring 11 of the pawl type bidirectional controllable overrunning clutch which is matched with the first-gear ring 3 and the clutch inner ring 11 of the pawl type unidirectional controllable overrunning clutch which is matched with the second-gear ring 4 have a movement tendency for forward rotation, at the moment, the control ring 15 is controlled to rotate through a clutch control mechanism, so that the pawl type bidirectional controllable overrunning clutch is in a unidirectional power transmission state of forward rotation of the clutch inner ring 11, at the moment, the clutch inner ring 11 of the pawl type bidirectional controllable overrunning clutch is relatively fixed with the clutch outer ring 12, namely the first-gear ring 3 is relatively fixed, the second-gear ring 4 can reversely freely rotate, and according to the transmission characteristics of the sun gear, the power is input through the sun gear 1, and the planetary gear is relatively fixed through the planetary gear carrier 6, and the planetary gear is finally rotated through the planetary gear carrier 6;
The control process for entering the neutral state specifically comprises the following steps:
when the sun gear 1 rotates under the driving of the engine, the sun gear 1 drives the triple planetary gear 2 to rotate, a driving force for reverse rotation is applied by meshing a first-gear planetary gear at one end of the triple planetary gear 2 with a first-gear ring 3, a driving force for reverse rotation is applied by meshing a second-gear planetary gear at the other end with a second-gear ring 4, a clutch inner ring 11 of a pawl type bidirectional controllable overrunning clutch which is matched with the first-gear ring 3 and a clutch inner ring 11 of a pawl type unidirectional controllable overrunning clutch which is matched with the second-gear ring 4 have a rotating movement trend, at the moment, a control ring 15 is controlled to rotate through a clutch control mechanism, and then the pawl type bidirectional controllable overrunning clutch and the pawl type unidirectional controllable overrunning clutch are in a bidirectional overrunning state, at the moment, the clutch inner ring 11 of the pawl type bidirectional controllable overrunning clutch and the pawl type unidirectional controllable overrunning clutch and the clutch outer ring 12 are free to rotate, at the moment, the first-gear ring 3 and the second-gear ring 4 are free to rotate, at the moment, no power is output by the planet carrier, and the speed change mechanism enters a neutral state.
Compared with the prior art, the invention has the beneficial effects that:
1. the triple planetary gear train is adopted by the triple planetary gear type in-wheel two-gear automatic speed change mechanism, so that a larger transmission ratio required by in-wheel transmission of a high-speed motor can be provided, the first-gear transmission ratio can reach 17.5, and the second-gear transmission ratio can reach 13.6 through calculation.
2. The triple planetary gear type in-wheel two-gear automatic speed change mechanism adopts the pawl type controllable one-way clutch, realizes free switching among a low-speed gear, a high-speed gear, a neutral gear and a reverse gear in the wheel, can be matched with a motor as a control executing mechanism, and can finish gear shifting in a short time.
3. According to the triple planetary gear type in-wheel two-gear automatic speed change mechanism, two sets of pawl type controllable one-way clutches are adopted to share one control ring, namely, one control ring is adopted to simultaneously control pawls at two sides of the axial direction to lift or put down, so that automatic in-wheel gear shifting is realized, the size of the speed change mechanism is greatly reduced, the radial space size of the whole set of in-wheel speed change mechanism can be controlled within 200mm, the axial space size can be controlled within 120mm, and the in-wheel arrangement space requirement is completely met.
Drawings
FIG. 1 is an axial schematic view of a triple planetary gear type in-wheel two-gear automatic transmission mechanism according to the present invention;
FIG. 2 is a cross-sectional view A-A of FIG. 1;
FIG. 3 is a schematic axial view of a pawl type bi-directional overrunning clutch in the in-wheel two-gear automatic transmission mechanism according to the present invention;
FIG. 4 is a schematic axial view of a pawl type one-way overrunning clutch in the in-wheel two-gear automatic transmission mechanism according to the present invention;
FIG. 5 is a schematic diagram of a transmission of the in-wheel two-speed automatic transmission according to the present invention;
FIG. 6 is a simplified transmission diagram of the in-wheel two-speed automatic transmission according to the present invention in a low gear position;
FIG. 7 is a simplified transmission diagram of the in-wheel two-speed automatic transmission according to the present invention in a high gear position;
FIG. 8 is a schematic illustration of an in-wheel two-speed automatic transmission according to the present invention in neutral position;
in the figure:
the three-gear type planetary gear mechanism comprises a 1-sun gear, a 2-triple planetary gear, a 3-first gear ring, a 4-second gear ring, a 5-first planet carrier, a 6-second planet carrier, a 7-planetary gear pin shaft, an 8-needle bearing, a 9-deep groove ball bearing, a 10-copper gasket, an 11-clutch inner ring, a 12-clutch outer ring, a 13-pawl, a 14-return spring, a 15-control ring and a 16-top ring.
Detailed Description
For a clear and complete description of the technical scheme and the specific working process thereof, the following specific embodiments of the invention are provided with reference to the accompanying drawings in the specification:
The invention discloses a triple planetary gear type in-wheel two-gear automatic speed change mechanism, which comprises: the three-way planetary gear mechanism is characterized in that a coaxial transmission planetary gear, a first-gear planetary gear and a second-gear planetary gear are respectively integrated on the three-way planetary gear in the three-way planetary gear mechanism, 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 two groups of pawl type overrunning clutches are respectively connected with the first-gear ring and the second-gear ring through splines, locking or releasing of the inner rings of the corresponding clutches is achieved through controlling pawl lifting of the pawl type overrunning clutches on two sides, and further corresponding first-gear ring or second-gear ring is controlled to be fixed or freely rotate, and gear change of the speed change mechanism is finally achieved.
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:
three groups of triple planetary gears are uniformly distributed on the outer side of the circumference of the sun gear 1, and each group of triple planetary gears comprises a transmission planetary gear positioned at the axial middle position and a first-gear planetary gear and a second-gear planetary gear positioned on two sides of the transmission planetary gear respectively; the first-gear planetary gear is positioned at one side close to the high-speed motor, the outer circumferential gear teeth are in meshed connection with the first-gear ring 3, the second-gear planetary gear is positioned at one side close to the hub, and the outer circumferential gear teeth are in meshed connection with the second-gear ring 4; the first-gear planetary gear, the transmission planetary gear and the second-gear planetary gear are coaxially arranged, and the triple planetary gear is integrally processed; and a plurality of groups of needle bearings 8 are uniformly arranged in the inner hole of the triple planetary gear along the axial direction, and the triple planetary gear is rotatably arranged on the planetary gear pin shaft 7 through the needle 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 through matching buckling of a positioning protrusion and a positioning groove, the first planet carrier 5 and the second planet carrier 6 are fixedly connected into a whole through long bolts penetrating through the first planet carrier 5 and the second planet carrier 6, other parts of the triple planetary gear mechanism and two groups of pawl type unidirectional controllable overrunning clutches are integrated between the first planet carrier 5 and the second planet carrier 6, so that the whole speed change mechanism is more compact in structure and saves installation space.
The two ends of the planetary gear pin shaft 7 are respectively and fixedly arranged on the combined planetary carrier, wherein one end of the planetary gear pin shaft 7 is inserted into a trapezoid mounting groove on the inner end surface of the first planetary carrier 5, a copper gasket 10 is arranged on the corresponding end part of the planetary gear pin shaft 7, one end of the copper gasket 10 is contacted with the outer end surface of the corresponding first-gear planetary gear, and the other end of the copper gasket 10 is arranged in the trapezoid mounting groove on the inner end surface of the first planetary carrier 5 in a matched manner with the planetary gear pin shaft 7; the other end of the planetary gear pin shaft 7 is inserted into a trapezoid mounting groove on the inner end face of the second planetary gear frame 6, another copper gasket 10 is also mounted on the corresponding end of the planetary gear pin shaft 7, one end of the copper gasket 10 is in contact with the outer end face of the corresponding second-gear planetary gear, and the other end of the copper gasket 10 is mounted in the trapezoid mounting groove on the inner end face of the second planetary gear frame 6 in a matched manner with the planetary gear pin shaft 7; the copper gasket 10 is used for realizing axial limiting of the triple planetary gear on one hand and can effectively prevent abrasion between the triple planetary gear and the corresponding planetary carrier on the other hand.
In the triple planetary gear train mechanism, the sun gear 1 positioned in the middle of the three groups of triple planetary gears is respectively and simultaneously meshed with the transmission planetary gears of the triple planetary gears, the end part 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 high-speed motor is fixed on the outer side of the shell of the transmission mechanism; the second planet carrier 6 positioned at one side of the vehicle hub is connected with the hub through a spline, so that power output is realized; furthermore, the outer circumferential side surfaces of the first carrier 5 and the second carrier 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, the pawl overrunning clutch has two groups, which are respectively composed of a clutch inner ring 11, a clutch outer ring 12, pawls 13, a return spring 14 and a control ring 15. Wherein:
in the automatic speed change mechanism, which gear is used for realizing reverse gear is selected, the pawl type overrun clutch corresponding to the gear ring of the gear is a pawl type bidirectional controllable overrun clutch, and the pawl type overrun clutch corresponding to the gear ring of the other gear is a pawl type unidirectional controllable overrun clutch. In this embodiment, a first-gear reverse gear is adopted, so that the first-gear outer ring 3 is correspondingly installed with the pawl type bidirectional controllable overrunning clutch, and the second-gear outer ring 4 is correspondingly installed with 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 side splines of the corresponding first gear ring gear 3 and the second gear ring gear 4. The gear teeth on the outer side of the clutch inner ring 11 in the pawl type bidirectional controllable overrunning clutch are bidirectional gear teeth, so that the clamping connection of the pawl arranged in the bidirectional direction can be realized; the gear teeth on the outer side of the clutch inner ring 11 in the pawl type bidirectional controllable overrunning clutch are unidirectional gear teeth, so that the pawl can be clamped in unidirectional arrangement.
In the two groups of pawl type overrunning clutches, clutch outer rings 12 of the two groups of clutches are respectively arranged on the outer sides of corresponding clutch inner rings 11, and the two groups of clutch outer rings 12 are respectively fixed on a shell of a speed change mechanism through pins so as to realize the fixation of relative positions.
In the two groups of pawl overrunning clutches, pawl assemblies consisting of pawls 13 and return springs 14 are distributed in groups in the same direction and are arranged in annular gaps between the corresponding clutch outer ring 12 and the clutch inner ring 11, one end of each return spring 14 is arranged in a spring groove formed in the inner side of the clutch outer ring 12, the bottom of each pawl 13 is rotatably arranged in a pawl groove formed in the inner side of the clutch outer ring 12, the top of each pawl 13 is connected with the other end of each return spring 14, a shifting pin perpendicular to the side end face is arranged on the side end face of each pawl 13, and the pawls 13 positioned in the same group of clutches can synchronously swing up and down around the central axis of the bottom of each pawl under the driving of the shifting pin and the elastic force of each return spring 14 and can be matched with gear teeth on the outer side of the clutch inner ring 11 to realize clamping fixation or relative free rotation between the clutch inner ring 11 and the clutch outer ring 12;
In the pawl type bidirectional controllable overrunning clutch, a plurality of pairs of pawl assembly pairs are distributed between the clutch outer ring 12 and the clutch inner ring 11 along the circumferential direction, wherein two pawls 13 in each pair of pawl assembly pairs 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 11, so the installation direction of the reverse-gear pawl is the same as the reverse rotation direction of the clutch inner 11.
In the pawl type unidirectional controllable overrun clutch, a plurality of pawl assemblies are distributed between the clutch outer ring 12 and the clutch inner ring 11 along the circumferential direction, and the pawl assemblies in the pawl type unidirectional controllable overrun clutch are in one-to-one correspondence with the pawl assemblies in the pawl type bidirectional controllable overrun clutch. The pawl 13 in the unidirectional controllable overrunning clutch is a second-gear pawl, the installation direction of the second-gear pawl is the same as that of the first-gear pawl, the installation direction of the second-gear pawl is opposite to that of the reverse-gear pawl, namely the installation direction of the second-gear pawl is the same as that of the forward rotation of the clutch inner ring 11
The 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 the first gear forward, the second gear forward, the first gear reverse and the 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 center of the control ring 15, and when the poking pin of the pawl 13 is positioned on the low control surface, the pawl 13 is in a falling state; the high control surface is a control surface far away from the center of the control ring 15, and when the poking pin of the pawl 13 is positioned on the high control surface, the pawl 13 is in a lifting state; the transition surface is a unidirectional and smooth connection surface connected between the low control surface and the high control surface, when the poking pin of the pawl 13 moves along the transition surface from the low control surface to the high control surface, the pawl 13 is gradually lifted from a falling state, namely gradually separated from the ratchet teeth on the outer side of the clutch inner ring, when the poking pin of the pawl 13 moves to the middle position of the transition surface, the pawl 13 is just separated from the ratchet teeth on the outer side of the clutch inner ring, and as the poking pin of the pawl 13 continues to move along the transition surface to the high control surface, the pawl 13 continues to lift 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 a first gear control window, a second gear control window and a reverse gear control window respectively, wherein the reverse gear control window and the second gear control window are structurally identical, the first gear control window and the reverse gear control window are radially symmetrical relative to the control ring 15, namely, the pawl movement direction controlled by the reverse gear control window and the second gear control window is identical, and the pawl movement direction controlled by the first gear control window is opposite to the pawl movement direction controlled by the reverse gear control window and the second gear control window.
The first-gear control window and the reverse-gear control window are respectively and correspondingly arranged with the first-gear pawl and the reverse-gear pawl in the pawl type bidirectional controllable overrunning clutch in a one-to-one correspondence manner, and the second-gear control window is correspondingly arranged with the second-gear pawl in the pawl type unidirectional controllable overrunning clutch in a one-to-one correspondence manner, so that when a shifting pin of the first-gear pawl moves from a high control surface to a low control surface to gradually fall down the first-gear pawl, a shifting pin of the reverse-gear pawl and the second-gear pawl simultaneously moves from the low control surface to the high control surface to gradually lift up the reverse-gear pawl and the second-gear pawl, and otherwise, when a shifting pin of the first-gear pawl moves from the low control surface to gradually lift up the first-gear shifting pin, a shifting pin of the reverse-gear pawl and the second-gear pawl simultaneously moves from the high control surface to the low control surface to gradually fall down the reverse-gear pawl and the second-gear pawl; when the shifting 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, the first gear pawl, the second gear pawl and the reverse gear pawl are all positioned at positions which are just lifted and separated from the gear ring outside the clutch inner ring 11.
According to the structure of the two groups of pawl type overrunning clutches, when the clutch inner rings 11 in the pawl type bidirectional controllable overrunning clutches and the pawl type unidirectional controllable overrunning clutches are rotated reversely, the clutch control mechanism drives the control ring 15 to rotate by a certain angle, and under the control of the control ring 15, the first gear pawl is in a falling state, and the second gear pawl and the reverse gear pawl are in a lifting state. 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 first-gear pawl is opposite to the rotation direction of the clutch inner ring 11 at the moment, so that the clutch inner ring 11 of the pawl type bidirectional controllable overrunning clutch is clamped and fixed relatively to the clutch outer ring 12, power transmission is realized, 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 separated from the corresponding clutch inner ring 11 at the moment, namely, the clutch inner ring 11 is separated from the clutch outer ring 12, and no power is transmitted. At this time, the pawl type one-way controllable overrunning clutch installed corresponding to the second gear ring gear 4 is in a one-way overrunning state in which the clutch inner ring 11 is reversed, and the pawl type one-way controllable overrunning clutch installed corresponding to the first gear ring gear 3 is in a one-way power transmission state in which the clutch inner ring 11 is reversed.
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 clutch control mechanism drives the control ring 15 to rotate for a certain angle, and under the control of the control ring 15, the first-gear pawl is in a lifting state, and the second-gear pawl and the reverse-gear pawl are in a falling state. The second-gear pawl is mounted in the same direction as the forward rotation direction of the clutch inner ring 11, that is, in the opposite direction to the rotation direction of the clutch inner ring 11 at this time, so that the second-gear pawl is clamped with the clutch inner ring, the clutch inner ring 11 of the pawl type unidirectional controllable overrunning clutch is clamped and fixed relatively to the clutch outer ring 12, thereby realizing power transmission, and the first-gear pawl is in a lifting state, so that the first-gear pawl is separated from the corresponding clutch inner ring 11, at this time, the reverse-gear pawl is in a falling state, but the mounting direction of the reverse-gear pawl is the same as the reverse rotation direction of the clutch inner ring 11, so that the reverse-gear pawl is pressed to the side of the clutch outer ring 12 by the gear teeth on the outer side of the clutch inner ring 11 along with the reverse rotation of the clutch inner ring 11, that is not clamped with the gear teeth on the outer side of the clutch inner ring 11, so that the clutch 11 of the pawl type bidirectional controllable overrunning clutch is separated from the clutch inner ring 12 without power transmission. At this time, the pawl type bidirectional controllable overrunning clutch mounted corresponding to the first gear ring 3 is in a unidirectional overrunning state in which the clutch inner race 11 is reversed, and the pawl type unidirectional controllable overrunning clutch mounted corresponding to the second gear ring 4 is in a unidirectional power transmission state in which the clutch inner race 11 is reversed.
When the clutch inner ring 3 in the pawl type bidirectional controllable overrunning clutch and the pawl type unidirectional controllable overrunning clutch both rotate positively, the clutch control mechanism drives the control ring 15 to rotate for a certain angle, and under the control of the control ring 15, the first-gear pawl is in a lifting state, and the second-gear pawl and the reverse-gear pawl are in a falling state. The installation direction of the second-gear pawl is the same as the forward rotation direction of the clutch inner ring 11, so that although the second-gear pawl is in a falling state, the installation direction of the second-gear pawl is the same as the rotation direction of the clutch inner ring 3 at the moment, and therefore, along with the forward rotation of the clutch inner ring 11, the second-gear pawl is pressed to one side of the clutch outer ring 12 by the gear teeth on the outer side of the clutch inner ring 11, namely, the second-gear pawl is not clamped with the gear teeth on the outer side of the clutch inner ring 11, so that the clutch inner ring 11 of the pawl type unidirectional controllable overrunning clutch is separated from the clutch outer ring 12 without power transmission; at this time, the first-gear pawl is lifted, so that the first-gear pawl is not clamped with the corresponding clutch inner ring 11, and the reverse-gear pawl falls down at this time, and 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 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 mounted corresponding to the second gear ring gear 4 is in a one-way overrunning state in which the clutch inner ring 11 rotates forward, and the pawl type two-way controllable overrunning clutch mounted corresponding to the first gear ring gear 3 is in a one-way power transmission state in which the clutch inner ring 11 rotates forward.
When the clutch control mechanism drives the control ring 15 to rotate by a certain angle, under the control of the control ring 15, the shifting pins of the first gear pawl, the second gear pawl and the reverse gear pawl are all positioned in the middle position of the transition surface, 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 clutch inner ring 11, at the moment, the clutch inner ring 11 and the clutch outer ring 12 in the bidirectional controllable overrunning clutch and the pawl type unidirectional controllable overrunning clutch are both separated, and the bidirectional overrunning clutch and the pawl type unidirectional controllable overrunning clutch are both realized.
A top ring 16 is coaxially arranged between the clutch outer rings 12 of the two groups of the pawl type unidirectional controllable overrunning clutches, and the top ring 16 controls the axial installation distance between the two groups of the pawl type unidirectional controllable overrunning clutches by limiting the axial distance between the clutch outer rings 12.
As shown in fig. 2, the clutch inner rings 11 of the two groups of pawl type unidirectional controllable overrunning clutches are respectively in spline 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 meshed with the first gear planetary gear and the second gear planetary gear, and the transmission planetary gear positioned in the middle of the triple planetary gear and the sun gear 1 meshed with the transmission planetary gear are positioned between the two clutch inner rings 11, so that the clutch inner rings 11 are designed into a half-shell structure, the two clutch inner rings 11 are oppositely installed, and a cavity is formed by matching with the first gear ring 3 and the second gear ring 4, thereby being 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 rotation angle of the control ring 15.
Based on the above-mentioned three-way planetary gear type in-wheel two-gear automatic speed change mechanism, the invention also provides a gear shift control method of the three-way planetary gear type in-wheel two-gear automatic speed change mechanism, as shown in figure 5, after the high-speed motor outputs power, the power is input to the speed change mechanism by the sun gear 1, the power is transmitted to the transmission planetary gear in the middle part of the three-way 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, the pawls in the two groups of pawl overrunning clutches rise or fall, so as to realize the power transmission or overrunning of the pawl overrunning clutches, and further realize the relative fixation or rotation of the first-gear ring 3 or the second-gear ring gear 4 which are respectively connected with the clutch inner rings 11 of the two groups of pawl overrunning clutches, wherein when the ring gear is fixed, the power is input through the sun gear 1, transmitted through the first-gear planetary gear or the second-gear planetary gear, and finally output from the second planetary carrier 6 to the hub, and further realize the first-gear forward, the second-gear forward or the first-gear reverse; when the first gear ring 3 and the second gear ring 4 are both free to rotate, a neutral state is entered.
The specific control process of the gear shifting control method is as follows:
1. a first gear forward control process:
as shown in fig. 6, when the sun gear 1 is driven by the motor to rotate forward, 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 two ends of the triple planetary gear 2 apply a driving force for reverse rotation to the first-gear ring 3 and the second-gear ring 4 which are connected with the first-gear ring 3 in a spline manner respectively, the inner clutch ring 11 of the pawl type bidirectional controllable overrunning clutch and the inner clutch ring 11 of the pawl type unidirectional controllable overrunning clutch which are arranged in a manner in which the first-gear ring 3 is matched with the second-gear ring 4 have a motion trend of reverse rotation, at this moment, the pawl type unidirectional controllable overrunning clutch is in a unidirectional power transmission state of reversing the inner clutch ring 11 through the clutch control mechanism, at this moment, the inner clutch ring 11 of the pawl type bidirectional controllable overrunning clutch is relatively fixed with the outer clutch ring 12, namely the first-gear ring 3 is relatively fixed, the second-gear ring 4 can rotate reversely, power is input through the sun gear 1 according to the transmission characteristic of the planetary gear, and the first-gear ring 3 is relatively fixed with the planetary gear carrier 6, and finally the planetary gear is rotated forward through the planetary gear carrier 6, and the planetary gear is rotated forward through the planetary gear carrier 6.
2. And a second gear forward control process:
as shown in fig. 7, when the sun gear 1 is driven by the motor to rotate forward, the sun gear 1 drives the triple planetary gear 2 to rotate in reverse, the first-gear planetary gear and the second-gear planetary gear at two ends of the triple planetary gear 2 apply a driving force for reverse rotation to the first-gear ring 3 and the second-gear ring 4 which are connected with the first-gear ring 3 in a spline manner respectively, the inner clutch ring 11 of the pawl type bidirectional controllable overrunning clutch and the inner clutch ring 11 of the pawl type unidirectional controllable overrunning clutch which are arranged in a matched manner 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 power transmission state of the inner clutch ring 11, at this time, the inner clutch ring 11 of the pawl type unidirectional controllable overrunning clutch is fixed with the outer clutch ring 12 relatively, namely the second-gear ring 4 is fixed relatively, the first-gear ring 3 can rotate freely in reverse direction, and power is input through the sun gear 1 according to the transmission characteristic of the planetary gear, the second-gear ring 4 is fixed relatively to the planetary gear carrier 6, and finally the power is output through the planetary gear carrier 6 to the second planetary gear carrier, and the planetary gear carrier is rotated forward by the same direction as the planetary gear carrier 6.
3. A first gear reversing control process:
as shown in fig. 6, when the sun gear 1 rotates reversely under the drive of the motor, the sun gear 1 drives the triple planetary gear 2 to rotate positively, the first-gear planetary gear and the second-gear planetary gear at two ends of the triple planetary gear 2 apply a driving force for forward rotation to the first-gear ring 3 and the second-gear ring 4 which are connected with the first-gear planetary gear ring 3 respectively, the clutch inner ring 11 of the pawl type bidirectional controllable overrunning clutch which is mounted in cooperation with the first-gear planetary gear ring 3 and the clutch inner ring 11 of the pawl type unidirectional controllable overrunning clutch which is mounted in cooperation with the second-gear planetary gear ring 4 have a movement tendency of forward 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 power transmission state of forward rotation of the clutch inner ring 11, at this time, the clutch inner ring 11 of the pawl type bidirectional controllable overrunning clutch is fixed relatively to the clutch outer ring 12, namely the first-gear ring 3 is fixed relatively, the second-gear ring 4 can rotate freely reversely, and power is input through the sun gear 1, and then the planetary gear wheel is output relatively to the second planetary gear carrier 6 through the planetary gear carrier 6, and the planetary gear carrier is rotated relatively to the second planetary gear carrier 6, and the power is finally, and the planetary gear carrier is rotated relatively the same.
4. Entering a neutral gear control process:
as shown in fig. 8, when the sun gear 1 rotates forward or backward under the drive of the motor, the sun gear 1 drives the triple planetary gear 2 to rotate, the first-gear planetary gear and the second-gear planetary gear at two ends of the triple planetary gear 2 apply a rotational driving force to the first-gear ring 3 and the second-gear ring 4 which are connected with the first-gear planetary gear, the clutch inner ring 11 of the pawl type bidirectional controllable overrunning clutch which is matched with the first-gear planetary gear 3 and the clutch inner ring 11 of the pawl type unidirectional controllable overrunning clutch which is matched with the second-gear planetary gear 4 have rotational movement tendency, at this time, the control ring 15 rotates through the clutch control mechanism, and then the pawl type bidirectional controllable overrunning clutch and the pawl type unidirectional controllable overrunning clutch are in bidirectional overrunning states, at this time, the clutch inner ring 11 and the clutch outer ring 12 of the pawl type bidirectional controllable overrunning clutch are relatively free to rotate, at this time, the planet carrier has no power output according to the transmission characteristics of the planetary gear train, and at this time, the gear mechanism enters into a neutral state.
Claims (5)
1. The gear shifting control method of the triple planetary gear type in-wheel two-gear automatic speed change mechanism is applied to the triple planetary gear type in-wheel two-gear automatic speed change mechanism, and the triple planetary gear type in-wheel two-gear automatic speed change mechanism consists of a triple planetary gear mechanism and a pawl 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 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 meshed with a first gear ring (3) and a second gear ring (4) respectively, the triple planetary gear (2) is arranged on a planetary gear pin shaft (7) through bearings, 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 arranged in a combined mode, 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 clutch is provided with two groups, and the inner rings (11) of the two groups of clutches are respectively and fixedly connected with the first gear ring (3) and the second gear ring (4) in a coaxial way;
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, second gear forward, first gear reverse and neutral gear, and 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;
The clutch inner ring (11) of the pawl type bidirectional controllable overrunning clutch is coaxially connected with a gear ring (3) so as to realize one-gear reversing, and the clutch is characterized in that:
the power output by the high-speed motor is input to a speed change mechanism through a sun gear (1), the power is transmitted to a transmission planetary gear in the middle of a triple planetary gear (2), the first-gear planetary gear and the second-gear planetary gear are synchronously driven to rotate, pawls (13) in the two groups of pawl overrunning clutches rise or fall under the control of a control ring (15), the power transmission or overrunning of the pawl overrunning clutches is realized, further, a first-gear ring (3) or a second-gear ring (4) which are respectively in spline connection with clutch inner rings (11) of the two groups of pawl overrunning clutches are relatively fixed or rotate, in the triple planetary gear, when the first-gear ring (3) or the second-gear ring (4) is relatively fixed, the power is transmitted through the first-gear planetary gear or the second-gear planetary gear after being input through the sun gear (1), and finally output to a hub from a second planetary carrier (6), the first-gear forward, the second-gear forward or the first-gear reverse is realized, and when the two groups of pawl overrunning clutches are both in two directions overrunning, and the first-gear ring (3) and the second-gear ring (4) are in a free gear state.
2. The shift control method of a triple planetary gear type in-wheel two-speed automatic transmission mechanism according to claim 1, characterized in that:
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 the reverse gear pawl and the first gear pawl which are symmetrically arranged in the pawl type bidirectional controllable overrunning clutch to move reversely, the second gear control window controls the second gear pawl and the reverse gear pawl in the pawl type unidirectional controllable overrunning clutch to move in the same direction, and the installation direction of the second gear pawl is opposite to that of the reverse gear pawl.
3. The shift control method of a triple planetary gear type in-wheel two-speed automatic transmission mechanism according to claim 1, characterized in that:
the end part of the wheel shaft of the sun wheel (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.
4. The shift control method of a triple planetary gear type in-wheel two-speed automatic transmission mechanism according to claim 1, characterized in that:
the triple planetary gear (2) is arranged on a planetary gear pin shaft (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 side face of the second planet carrier (6) in a cushioning mode.
5. The shift control method of a triple planetary gear type in-wheel two-speed automatic transmission mechanism according to claim 4, characterized in that:
the first gear forward control process specifically comprises the following steps:
when the sun gear (1) rotates positively under the drive of a motor, the sun gear (1) drives the triple planetary gear (2) to rotate reversely, a first-gear planetary gear at one end of the triple planetary gear (2) is meshed with the first-gear ring (3) to apply a driving force for reverse rotation, a second-gear planetary gear at the other end is meshed with the second-gear ring (4) to apply a driving force for reverse rotation, a clutch inner ring (11) of a pawl type bidirectional controllable overrunning clutch which is matched with the first-gear ring (3) and a clutch inner ring (11) of the pawl type unidirectional controllable overrunning clutch which is matched with the second-gear ring (4) both have a motion trend of reverse rotation, at the moment, the rotation of the control ring (15) is controlled through a clutch control mechanism, the pawl type one-way controllable overrunning clutch is in a one-way overrunning state of the reverse rotation of the clutch inner ring (11), the pawl type two-way controllable overrunning clutch is in a one-way power transmission state of the reverse rotation of the clutch inner ring (11), at the moment, the clutch inner ring (11) and the clutch outer ring (12) of the pawl type two-way controllable overrunning clutch are relatively fixed, namely the first gear ring (3) is relatively fixed, the second gear ring (4) can rotate reversely freely, according to the transmission characteristic of the planetary gear train, after power is input through the sun gear (1), the first gear ring (3) is relatively fixed, so the power is transmitted through the first gear planetary gear of the triple planetary gear (2) and finally output through the second planetary carrier (6), the rotation direction of the second planet carrier (6) is the same as that of the sun gear (1), and the speed change mechanism realizes one-gear advancing at the moment;
The second gear forward control process specifically comprises the following steps:
when the sun gear (1) rotates positively under the drive of a motor, the sun gear (1) drives the triple planetary gear (2) to rotate reversely, a driving force for reverse rotation is applied to the first-gear planetary gear and the first-gear tooth ring (3) at one end of the triple planetary gear (2), a driving force for reverse rotation is applied to the second-gear planetary gear and the second-gear tooth ring (4) at the other end of the triple planetary gear, the clutch inner ring (11) of the pawl type unidirectional controllable overrunning clutch which is matched with the first-gear tooth ring (3) and the clutch inner ring (11) of the pawl type unidirectional controllable overrunning clutch which is matched with the second-gear tooth ring (4) have a movement tendency of reverse rotation, at the moment, the control ring (15) is controlled to rotate through the clutch control mechanism, and then the pawl type unidirectional controllable overrunning clutch is in a unidirectional power transmission state of the clutch inner ring (11), at the moment, the clutch inner ring (11) of the pawl type unidirectional controllable overrunning clutch is fixed relatively to the clutch inner ring (12), namely the second-gear ring (4) is fixed relatively, the second-gear planetary gear (4) is fixed relatively to the planetary gear wheel (2) after the planetary gear is driven relatively, the planetary gear (2) is driven relatively, the power is output relatively, the planetary gear (2) is fixed relatively, and the planetary gear (2) is driven relatively, the power is in a unidirectional power transmission state through the planetary gear (2), the rotation direction of the second planet carrier (6) is the same as that of the sun gear, and the speed change mechanism realizes second gear advancing at the moment;
The first-gear reversing control process specifically comprises the following steps:
when the sun gear (1) rotates reversely under the drive of the motor, the sun gear (1) drives the triple planetary gear (2) to rotate positively, a first-gear planetary gear at one end of the triple planetary gear (2) is meshed with the first-gear ring (3) to apply a reverse rotation driving force, a second-gear planetary gear at the other end is meshed with the second-gear ring (4) to apply a reverse rotation driving force, the clutch inner ring (11) of the pawl type bidirectional controllable overrunning clutch which is matched with the first-gear ring (3) and the clutch inner ring (11) of the pawl type unidirectional controllable overrunning clutch which is matched with the second-gear ring (4) have forward rotation movement tendencies, at the moment, the clutch control mechanism controls the control ring (15) to rotate, the pawl type bidirectional controllable overrunning clutch is in a unidirectional power transmission state of forward rotation of the clutch inner ring (11), the pawl type unidirectional controllable overrunning clutch is in a unidirectional overrunning state of forward rotation of the clutch inner ring (11), at the moment, 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 (3) is relatively fixed, the second gear ring (4) can rotate reversely and freely, after power is input through the sun gear (1) according to the transmission characteristic of the planetary gear train, the power is output through the second planetary carrier (6) after being transmitted through the first gear planetary gear of the triple planetary gear (2) due to the relative fixation of the first gear ring (3), the rotation direction of the second planet carrier (6) is the same as that of the sun gear, and the speed change mechanism realizes one-gear reversing at the moment;
The control process for entering the neutral state specifically comprises the following steps:
when the sun gear (1) rotates under the driving of the engine, the sun gear (1) drives the triple planetary gear (2) to rotate, a first-gear planetary gear at one end of the triple planetary gear (2) is meshed with the first-gear ring (3) to apply a driving force for reverse rotation, a second-gear planetary gear at the other end is meshed with the second-gear ring (4) to apply a driving force for reverse rotation, a clutch inner ring (11) of a pawl type bidirectional controllable overrunning clutch which is matched with the first-gear ring (3) and a clutch inner ring (11) of the pawl type unidirectional controllable overrunning clutch which is matched with the second-gear ring (4) are in a rotating movement trend, at the moment, the control ring (15) is controlled to rotate through a clutch control mechanism, and then the pawl type bidirectional controllable overrunning clutch and the pawl type unidirectional controllable overrunning clutch are in a bidirectional overrunning state, at the moment, the clutch inner ring (11) and the clutch outer ring (12) of the pawl type bidirectional controllable overrunning clutch are in opposite free rotation, at the moment, the first-gear ring (3) and the second-gear ring (4) are in free rotation, and no planetary gear is driven by the power transmission mechanism.
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| CN112128324A (en) * | 2020-10-10 | 2020-12-25 | 吉林大学 | In-wheel two-gear automatic transmission and power-interruption-free gear shifting control method |
| CN112413067B (en) * | 2020-11-23 | 2022-02-11 | 八方电气(苏州)股份有限公司 | Multi-gear adjusting speed change mechanism of middle-placed motor and middle-placed motor |
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