CN111336225A - 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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- CN111336225A CN111336225A CN202010169083.2A CN202010169083A CN111336225A CN 111336225 A CN111336225 A CN 111336225A CN 202010169083 A CN202010169083 A CN 202010169083A CN 111336225 A CN111336225 A CN 111336225A
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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 an in-wheel two-gear automatic speed change mechanism of a triple planetary gear and a gear-shifting control method thereof, wherein the speed change mechanism consists of a triple planetary gear train mechanism and pawl type overrunning clutches, in the triple planetary gear train 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 and the second gear ring; the gear shifting control method realizes the states of forward in the first gear, forward in the second gear, reverse in the first gear or the second gear and neutral gear by matching two groups of pawl type overrunning clutches and a triple planetary gear train mechanism. The invention can realize two-gear automatic speed change in the wheel while meeting the requirement of a 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, particularly relates to a triple planetary gear type in-wheel two-gear automatic speed change mechanism and a gear shift control method thereof, and aims at a high-speed wheel-side motor.
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
Aiming at the defects in the prior art, the invention provides the triple planetary gear type in-wheel two-gear automatic speed change mechanism and the gear shift control method thereof, which can realize in-wheel two-gear automatic speed change while meeting the requirement of a larger transmission ratio required by in-wheel transmission of a high-speed motor. The technical scheme of the invention is as follows by combining the attached drawings of the specification:
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 the 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 of first gear, forward of second gear, reverse of first gear or 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;
A gear shifting control method of a triple planetary gear type in-wheel two-gear automatic speed change mechanism comprises the following steps:
the output power of the high-speed motor is input to a speed change mechanism from a sun gear 1, the power is transmitted to a transmission planetary gear in the middle of a triple planetary gear 2 through the sun gear and synchronously drives a first-gear planetary gear and a second-gear planetary gear to rotate, pawls 13 in two groups of pawl type overrunning clutches rise or fall under the control of a control ring 15 to realize the transmission power or overrunning of the pawl type overrunning clutches, further realize the relative fixation or rotation of a first-gear ring 3 or a second-gear ring 4 which are respectively connected with inner rings 11 of the clutches of the two groups of pawl type overrunning clutches through splines, in the triple planetary gear train, 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 gear frame 6, further realize the forward gear of a first gear, the forward gear of a second gear, when both the first gear ring gear 3 and the second gear ring gear 4 rotate freely, the neutral state is entered.
The first-gear forward control process specifically comprises the following steps:
when the sun wheel 1 rotates forward under the drive of the motor, the sun wheel 1 drives the triple planet wheel 2 to rotate reversely, the first-gear planet wheel and the second-gear planet wheel at the two ends of the triple planet wheel 2 respectively 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, a clutch inner ring 11 of a pawl type bidirectional controllable overrunning clutch which is arranged in a matching manner with the first-gear ring 3 and a clutch inner ring 11 of a pawl type unidirectional controllable overrunning clutch which is arranged in a matching manner with the second-gear ring 4 have a movement trend for reverse rotation, at the moment, a control ring 15 is controlled to rotate by a clutch control mechanism, so that the pawl type unidirectional controllable overrunning clutch is in a unidirectional overrunning state that the clutch inner ring 11 rotates reversely, the pawl type bidirectional controllable overrunning clutch is in a unidirectional power transmission state that the clutch inner ring 11 rotates reversely, at the moment, the clutch inner ring 11 of the pawl type, 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 finally output through the second planetary carrier 6, and the rotation direction of the second planetary carrier 6 is the same as that of the sun gear 1, at this time, the speed change mechanism realizes the forward movement of the first gear;
the second-gear forward control process is specifically as follows:
when the sun wheel 1 rotates forward under the drive of the motor, the sun wheel 1 drives the triple planet wheel 2 to rotate reversely, the first-gear planet wheel and the second-gear planet wheel at the two ends of the triple planet wheel 2 respectively 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, a clutch inner ring 11 of a pawl type bidirectional controllable overrunning clutch which is arranged in a matching manner with the first-gear ring 3 and a clutch inner ring 11 of a pawl type unidirectional controllable overrunning clutch which is arranged in a matching manner with the second-gear ring 4 have a movement trend for reverse rotation, at the moment, a control ring 15 is controlled to rotate by a clutch control mechanism, so that the pawl type bidirectional controllable overrunning clutch is in a unidirectional overrunning state that the clutch inner ring 11 rotates reversely, the pawl type unidirectional controllable overrunning clutch is in a unidirectional power transmission state that the clutch inner ring 11 rotates reversely, at the moment, the clutch inner ring 11 of the pawl type, namely, the second gear ring 4 is relatively fixed, the first gear ring 3 can freely rotate reversely, 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 planet gear of the triple planet gear 2 and is finally output through the second planet carrier 6, and the rotation direction of the second planet carrier 6 is the same as that of the sun gear, at this time, the speed change mechanism realizes the forward movement of the second gear;
the first gear reverse control process specifically comprises the following steps:
when the sun wheel 1 rotates reversely under the drive of the motor, the sun wheel 1 drives the triple planet wheel 2 to rotate forwardly, the first-gear planet wheel and the second-gear planet wheel at the two ends of the triple planet wheel 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 ring 3 in a spline manner, the clutch inner ring 11 of the pawl type bidirectional controllable overrunning clutch which is arranged in cooperation with the first-gear ring 3 and the clutch inner ring 11 of the pawl type unidirectional controllable overrunning clutch which is arranged in cooperation with the second-gear ring 4 have a forward rotating movement trend, at the moment, 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, the pawl type unidirectional controllable overrunning clutch is in a unidirectional overrunning state of the 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, namely, the first gear ring gear 3 is relatively fixed, the second gear ring gear 4 can freely rotate 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 finally output through the second planetary carrier 6, and the rotation direction of the second planetary carrier 6 is the same as that of the sun gear, at this time, the speed change mechanism realizes the reverse gear of the first gear;
the control process for entering the neutral gear state specifically comprises the following steps:
when the sun wheel 1 rotates under the driving of an engine, the sun wheel 1 drives the triple planet wheel 2 to rotate, a first-gear planet wheel and a second-gear planet wheel at two ends of the triple planet wheel 2 respectively apply a rotary driving force to a first-gear ring 3 and a second-gear ring 4 which are connected with the first-gear ring 3 in a spline manner, a clutch inner ring 11 of a pawl type bidirectional controllable overrunning clutch installed in cooperation with the first-gear ring 3 and a clutch inner ring 11 of a pawl type one-way controllable overrunning clutch installed in cooperation with the second-gear ring 4 have a rotary motion trend, at the moment, a control ring 15 is controlled to rotate by a clutch control mechanism, so that the pawl type bidirectional controllable overrunning clutch and the pawl type one-way controllable overrunning clutch are in a bidirectional overrunning state, at the moment, the clutch inner rings 11 and the clutch outer rings 12 of the pawl type bidirectional controllable overrunning clutch and the pawl type one-way controllable overrunning clutch freely rotate, 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.
Compared with the prior art, the invention has the beneficial effects that:
1. the triple planetary gear type in-wheel two-gear automatic speed change mechanism adopts a triple planetary gear train, can provide a larger transmission ratio required by the in-wheel transmission of a high-speed motor, and can reach 17.5 for the first gear and 13.6 for the second gear through calculation.
2. The triple planetary gear type in-wheel two-gear automatic speed change mechanism adopts the pawl type controllable one-way clutch to realize free switching among in-wheel low-speed gear, high-speed gear, neutral gear and reverse gear, and can be matched with a motor as a control execution mechanism to finish gear shifting in a short time.
3. According to the three-linkage planetary gear type in-wheel two-gear automatic speed change mechanism, two sets of pawl type controllable one-way clutches share one control ring, namely one control ring is adopted to simultaneously control pawls on two axial sides to be lifted up or put down, in-wheel automatic gear change is achieved, 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 structural schematic view of an in-wheel two-speed automatic transmission mechanism of a triple planetary gear type according to 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 bi-directional overrunning clutch in the in-wheel two-speed automatic transmission mechanism according to the present invention;
FIG. 4 is a schematic axial structure view of a pawl type one-way overrunning clutch in the in-wheel two-speed automatic transmission according to the present invention;
FIG. 5 is a schematic transmission diagram of the in-wheel two speed automatic transmission of the present invention;
FIG. 6 is a simplified transmission diagram of the in-wheel two-speed automatic transmission mechanism of the present invention in a low speed gear position;
FIG. 7 is a simplified transmission diagram of the in-wheel two-speed automatic transmission mechanism of the present invention in a high-speed gear position;
FIG. 8 is a schematic view of the in-wheel two-speed automatic transmission 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 clearly and completely describing the technical scheme and the specific working process thereof, the specific implementation mode of the invention is as follows by combining the attached drawings of the specification:
the invention discloses a triple planetary gear type in-wheel two-gear automatic speed change mechanism, which comprises: 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:
in the automatic speed change mechanism, which gear is selected to realize reverse gear, the pawl type overrunning clutch corresponding to the gear ring of the gear is a pawl type bidirectional controllable overrunning clutch, and the pawl type overrunning clutch corresponding to the gear ring of the other gear is a pawl type unidirectional controllable overrunning clutch. In the embodiment, a first gear reverse gear is adopted, so 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.
Based on the triple planetary gear type in-wheel two-gear automatic speed change mechanism, as shown in fig. 5, after the power is output by the high-speed motor, the power is input into the speed change mechanism through 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, the 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 as to realize the relative fixation or the rotation of the first-gear ring 3 or the second-gear ring 4 which are respectively connected with the inner ring 11 of the two groups of pawl type overrunning clutches through splines, in the planetary gear train, when the gear ring is fixed, the power is input through the sun gear 1 and then is transmitted through the first-gear planetary gear or the second-gear planetary gear, finally, the output is transmitted to a hub from the second planet carrier 6, and further, the forward of the first gear, the forward of the second gear or the reverse of the first gear is realized; when both the first-gear ring gear 3 and the second-gear ring gear 4 rotate freely, the neutral state is entered.
The gear shifting control method comprises the following specific control processes:
1. the first gear forward control 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-gear forward control 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 reverse gear control process:
as shown in fig. 8, 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 control 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 (7)
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 forward of first gear, forward of second gear, reverse of first gear or second gear 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.
6. The gear shift control method of the triple planetary gear type in-wheel two-gear automatic speed change mechanism according to claim 2, characterized in that:
the output power of a high-speed motor is input to a speed change mechanism from a sun gear (1), the power is transmitted to a transmission planetary gear in the middle of a triple planetary gear (2) through the sun gear and synchronously drives a first-gear planetary gear and a second-gear planetary gear to rotate, pawls (13) in two groups of pawl type overrunning clutches rise or fall under the control of a control ring (15) to realize the transmission power or overrunning of the pawl type overrunning clutches, and further realize that a first-gear ring (3) or a second-gear ring (4) which are respectively connected with inner rings (11) of the clutches of the two groups of pawl type overrunning clutches through splines are relatively fixed or rotate, in a triple planetary gear train, when the first-gear ring (3) or the second-gear ring (4) are relatively fixed, the power is input through the sun gear (1), is transmitted through the first-gear planetary gear or the second-gear planetary gear, and is finally output from a second planetary gear carrier (6) to a, When the two groups of pawl type overrunning clutches are in bidirectional overrunning and the first gear ring (3) and the second gear ring (4) rotate freely, the two gears enter a neutral gear state.
7. The gear shift control method of the triple planetary gear type in-wheel two-gear automatic speed change mechanism according to claim 6, characterized in that:
the first-gear forward control process specifically comprises the following steps:
when the sun wheel (1) rotates forward under the drive of the motor, the sun wheel (1) drives the triple planet wheel (2) to rotate reversely, the first-gear planet wheel and the second-gear planet wheel at the two ends of the triple planet wheel (2) respectively apply a reverse rotation driving force to the first-gear ring (3) and the second-gear ring (4) which are connected with the first-gear planet wheel and the second-gear planet wheel through splines, the clutch inner ring (11) of the pawl type bidirectional controllable overrunning clutch which is installed in cooperation with the first-gear planet wheel (3) and the clutch inner ring (11) of the pawl type unidirectional controllable overrunning clutch which is installed in cooperation with the second-gear planet wheel (4) both have a reverse rotation movement trend, 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 overrunning state in which the clutch inner ring (11) rotates reversely, and the pawl type bidirectional controllable overrunning clutch is in a unidirectional power, at the moment, a clutch inner ring (11) and a clutch outer ring (12) of the pawl type bidirectional controllable overrunning clutch are relatively fixed, namely a first gear ring gear (3) is relatively fixed, a second gear ring gear (4) can reversely and freely rotate, according to the transmission characteristic of the planetary gear train, after power is input through a sun gear (1), as the first gear ring gear (3) is relatively fixed, the power is transmitted through a first gear planetary gear of a triple planetary gear (2) and finally output through a second planetary carrier (6), and the rotation direction of the second planetary carrier (6) is the same as that of the sun gear (1), at the moment, the speed change mechanism realizes first gear advancing;
the second-gear forward control process is specifically as follows:
when the sun wheel (1) rotates forward under the drive of the motor, the sun wheel (1) drives the triple planet wheel (2) to rotate reversely, the first-gear planet wheel and the second-gear planet wheel at the two ends of the triple planet wheel (2) respectively apply a reverse rotation driving force to the first-gear ring (3) and the second-gear ring (4) which are connected with the first-gear planet wheel through splines, 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) both have a motion trend of reverse rotation, at the moment, the control ring (15) is controlled to rotate through 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 the moment, a clutch inner ring (11) and a clutch outer ring (12) of the pawl type unidirectional controllable overrunning clutch are relatively fixed, namely a two-gear ring (4) is relatively fixed, a one-gear ring (3) can reversely and freely rotate, according to the transmission characteristic of a planetary gear train, after power is input through a sun gear (1), as the two-gear ring (4) is relatively fixed, the power is transmitted through a two-gear planetary gear of a triple planetary gear (2) and finally output through a second planetary carrier (6), the rotation direction of the second planetary carrier (6) is the same as that of the sun gear, and at the moment, the speed change mechanism realizes two-gear forward movement;
the first gear reverse control process specifically comprises the following steps:
when the sun wheel (1) rotates reversely under the drive of the motor, the sun wheel (1) drives the triple planet wheel (2) to rotate forwardly, the first-gear planet wheel and the second-gear planet wheel at the two ends of the triple planet wheel (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 planet wheel and the second-gear planet wheel through splines, the clutch inner ring (11) of the pawl type bidirectional controllable overrunning clutch which is installed in cooperation with the first-gear planet wheel (3) and the clutch inner ring (11) of the pawl type unidirectional controllable overrunning clutch which is installed in cooperation with the second-gear planet wheel (4) both have a forward rotating movement trend, at the moment, the control ring (15) is controlled to rotate through the clutch control mechanism, so that the pawl type bidirectional controllable overrunning clutch is in a forward rotating unidirectional power transmission state of the clutch inner ring (11), and the pawl type unidirectional controllable overrunning clutch is in a forward rotating unidirectional overrunning state, at the moment, a clutch inner ring (11) and a clutch outer ring (12) of the pawl type bidirectional controllable overrunning clutch are relatively fixed, namely a first gear ring gear (3) is relatively fixed, a second gear ring gear (4) can reversely and freely rotate, according to the transmission characteristic of the planetary gear train, after power is input through a sun gear (1), as the first gear ring gear (3) is relatively fixed, the power is transmitted through a first gear planetary gear of a triple planetary gear (2) and finally output through a second planetary carrier (6), the rotation direction of the second planetary carrier (6) is the same as that of the sun gear, and at the moment, the speed change mechanism realizes first gear reversing;
the control process for entering the neutral gear state specifically comprises the following steps:
when a sun wheel (1) rotates under the driving of an engine, the sun wheel (1) drives a triple planetary gear (2) to rotate, a first-gear planetary gear and a second-gear planetary gear at two ends of the triple planetary gear (2) respectively apply a rotating driving force to a first-gear ring (3) and a second-gear ring (4) which are in spline connection with the first-gear planetary gear and the second-gear planetary gear, a clutch inner ring (11) of a pawl type bidirectional controllable overrunning clutch installed in cooperation with the first-gear ring (3) and a clutch inner ring (11) of a pawl type unidirectional controllable overrunning clutch installed in cooperation with the second-gear ring (4) have a rotating motion trend, a control ring (15) is controlled to rotate through a clutch control mechanism at the moment, the pawl type bidirectional controllable overrunning clutch and the pawl type unidirectional controllable overrunning clutch are enabled to be in a bidirectional overrunning state, and the clutch inner ring (11) and the clutch outer ring (12) of the pawl type bidirectional controllable overrunning clutch and the pawl type unidirectional controllable overrunning clutch are enabled to rotate freely And at the moment, the first gear ring gear (3) and the second gear ring gear (4) both rotate freely, the planet carrier does not have power output according to the transmission characteristic of the planetary gear train, and the speed change mechanism enters a neutral gear state.
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| CN202010169083.2A CN111336225B (en) | 2020-03-12 | 2020-03-12 | Triple planetary gear type in-wheel two-gear automatic speed change mechanism and gear shifting control method thereof |
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| CN202010169083.2A CN111336225B (en) | 2020-03-12 | 2020-03-12 | Triple planetary gear type in-wheel two-gear automatic speed change mechanism and gear shifting control method thereof |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| 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 |
| CN112413067A (en) * | 2020-11-23 | 2021-02-26 | 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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| CN112413067A (en) * | 2020-11-23 | 2021-02-26 | 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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| Publication number | Publication date |
|---|---|
| CN111336225B (en) | 2023-11-14 |
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