CN110030355B - Self-adaptive automatic transmission with planetary system input and double overrunning clutch main shaft output - Google Patents

Self-adaptive automatic transmission with planetary system input and double overrunning clutch main shaft output Download PDF

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Publication number
CN110030355B
CN110030355B CN201910309314.2A CN201910309314A CN110030355B CN 110030355 B CN110030355 B CN 110030355B CN 201910309314 A CN201910309314 A CN 201910309314A CN 110030355 B CN110030355 B CN 110030355B
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gear
transmission
overrunning clutch
speed
driving
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CN110030355A (en
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薛荣生
陈俊杰
邓天仪
谭志康
邱光印
王靖
邓云帆
梁品权
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Southwest University
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Southwest University
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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
    • F16H15/00—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members
    • F16H15/02—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members without members having orbital motion
    • F16H15/04—Gearings providing a continuous range of gear ratios
    • F16H15/40—Gearings providing a continuous range of gear ratios in which two members co-operative by means of balls, or rollers of uniform effective diameter, not mounted on shafts
    • 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
    • F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
    • F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
    • F16H37/021—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings toothed gearing combined with continuous variable friction gearing
    • F16H37/022—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings toothed gearing combined with continuous variable friction gearing the toothed gearing having orbital motion
    • 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
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • 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
    • F16H61/66—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 continuously variable gearings
    • F16H61/664—Friction gearings
    • 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
    • F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
    • F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
    • F16H63/30—Constructional features of the final output mechanisms
    • F16H63/32—Gear shift yokes, e.g. shift forks
    • 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
    • F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
    • F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
    • F16H63/30—Constructional features of the final output mechanisms
    • F16H63/34—Locking or disabling mechanisms
    • F16H63/3408—Locking or disabling mechanisms the locking mechanism being moved by the final actuating mechanism
    • 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
    • F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
    • F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
    • F16H63/30—Constructional features of the final output mechanisms
    • F16H63/304—Constructional features of the final output mechanisms the final output mechanisms comprising elements moved by electrical or magnetic force
    • F16H2063/305—Constructional features of the final output mechanisms the final output mechanisms comprising elements moved by electrical or magnetic force using electromagnetic solenoids
    • 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
    • F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
    • F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
    • F16H63/30—Constructional features of the final output mechanisms
    • F16H63/32—Gear shift yokes, e.g. shift forks
    • F16H2063/325—Rocker or swiveling forks, i.e. the forks are pivoted in the gear case when moving the sleeve
    • 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
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/60—Other road transportation technologies with climate change mitigation effect
    • Y02T10/72—Electric energy management in electromobility

Abstract

The invention discloses a self-adaptive automatic transmission with planetary system input and double overrunning clutch main shaft output.A driving power is input through a planetary gear system, and a speed change system comprises a low-speed gear transmission mechanism, a reverse gear transmission mechanism and a self-adaptive speed change component; the reverse gear transmission mechanism is provided with a transmission ratio I for transmitting reverse gear power from the auxiliary shaft to the main shaft, the low-speed gear transmission mechanism is provided with a transmission ratio II for transmitting low-speed gear power from the auxiliary shaft to the main shaft, and the transmission ratio I is larger than or equal to the transmission ratio II; the invention utilizes the reasonable matching of the two overrunning clutches, so that the whole structure is simple and compact, the reverse gear transmission and the low-speed and high-speed gear transmissions share a transmission line, no interference occurs, the whole performance is ensured, the adaptability is strong, the invention is smoothly and naturally matched with the self-adaptive automatic speed change mechanism, the planetary speed reduction input is adopted, the high-speed motor can be adopted as a power source, the whole efficiency is improved, and the invention is not only suitable for the field of electric vehicles, but also suitable for the field of other torque-variable mechanical transmissions.

Description

Self-adaptive automatic transmission with planetary system input and double overrunning clutch main shaft output
Technical Field
The invention relates to a motor vehicle transmission, in particular to a self-adaptive automatic transmission with planetary system input and double overrunning clutch main shaft output.
Background
The mechanical transmission system generally has complex use working conditions, needs to distribute torque to realize transmission of different loads and rotating speeds, and has complex and changeable driving environments by taking an electric vehicle as an example. In addition, the electric driving method generally adopted by the existing electric automobile is that a motor drives a fixed speed ratio, a high-efficiency reasonable interval is narrow and limited, and vicious circle is caused, so that the following problems are caused:
1. and the device can only work within the torque range of a certain working condition.
2. Under the condition of a fixed speed ratio, the rotating speed of the motor can only be increased to meet the road working condition, and the manufacturing cost of the motor is increased.
3. The motor generates heat, and the service efficiency and the service life are reduced;
4. if the requirement of the complex working condition of the electric automobile on the torque is to be met, the current and the rotating speed of the motor can only be continuously increased, the damage of heavy current discharge to the battery can only be considered, the peak power, the peak torque and the peak heavy current of the motor can only be utilized to drive the motor, and the discharge characteristic of a power battery pack is not followed completely;
5. the electric capacity of the power battery pack is rapidly reduced due to long duration of large-current discharge, the electric capacity of the power battery pack is rapidly reduced, the peak large-current discharge causes rapid temperature rise of the battery, the internal resistance of the battery cell is rapidly increased due to temperature rise, the battery is subjected to great impact and irretrievable damage is caused, the electric storage capacity and the service life of the battery cell are sharply reduced, the charging cycle times are rapidly reduced, and the problem that the endurance mileage is shorter and shorter is caused;
6. the energy recovery efficiency is low;
7. the high-speed motor acceleration and deceleration mechanism is essentially used for increasing power and torque, high-efficiency conversion cannot be realized, and the problems of rapid deterioration of the motor performance and low efficiency under rotation resistance can be caused under the working condition of low speed and heavy load; the battery, the controller, the electric appliance and the cable are damaged due to heavy current power supply and frequent heavy current impact and overload, and particularly, the battery shortens the cycle mission greatly and has poor economy;
however, the prior art has fatal defects and can not overcome by the above driving method and technical route which utilize the fixed speed ratio.
The existing automatic transmission adopts a solenoid valve and a servo motor, and realizes gear up and gear down through mechanical parts such as a synchronizer, a shifting fork, a gear ring and the like. The hydraulic control system has the advantages that the hydraulic control system is large in structural parts, power needs to be cut off, the speed of the motor instantly rises to the maximum, the driving power of the automobile disappears suddenly, the speed of the automobile drops under the action of driving resistance, the algorithm is complex, timely synchronous control is difficult to achieve, the cutting switching time is required to be short, the pause feeling is strong, the reliability is poor, and the like; there are problems of safety, comfort, reliability, etc.
In order to solve the above problems, the present inventors invented a series of cam adaptive automatic transmission devices, which can detect the driving torque-speed and the driving resistance-speed signals according to the driving resistance, so as to make the output power of the motor or engine always in the best matching state with the vehicle driving condition, and realize the balance control of the driving torque and the comprehensive driving resistance, the load of the cam adaptive automatic transmission device changes the transmission ratio with the driving force, and the cam adaptive automatic transmission device automatically shifts gears and shifts with the driving resistance without cutting off the driving force, so as to make the motor or engine always output torque at high speed in the high efficiency region; the motor vehicle can run stably in mountainous areas, hills and heavy load conditions, and the safety is improved; the friction disc is adopted to form a separation and combination structure, so that the electric vehicle has the advantage of sensitive response, is small in axial size, and well solves the problems of the electric vehicle. Although the cam self-adaptive automatic speed changing device has the advantages that the cam self-adaptive automatic speed changing device is suitable for unidirectional power transmission of electric motorcycles and electric bicycles and is not suitable for speed changers of motor vehicles and mechanical devices needing bidirectional driving due to the adoption of a mechanical automatic speed changing structure, the overall size and the structural complexity of the speed changer can be increased if a traditional reverse gear transmission mechanism is adopted, and the cam self-adaptive automatic speed changing device cannot be well fused with the cam self-adaptive automatic speed changing device.
Therefore, a reverse gear transmission mechanism with strong adaptability is added to the cam self-adaptive automatic speed change device, the device can not only self-adaptively change gears and change speed automatically under the condition that the driving force is not cut off along with the change of the driving resistance, but also solve the problem that high-efficiency roads can run forward and reversely under complex conditions under the working condition of bidirectional driving, and the device is simple and compact in arrangement, smoothly and naturally matched with the cam self-adaptive automatic speed change mechanism, reduces the manufacturing cost and ensures the stability of transmission.
Disclosure of Invention
In view of the above, the present invention provides a planetary input dual overrunning clutch main shaft output adaptive automatic transmission, and a reverse gear transmission mechanism with strong adaptability is added, the device can not only self-adaptively shift and change speed under the condition of not cutting off driving force along with the change of driving resistance, but also solve the problem of forward and reverse driving of high efficiency roads under complex conditions under the condition of bidirectional driving, and the device has the advantages of simple and compact arrangement, smooth and natural matching with a cam adaptive automatic transmission mechanism, reduced manufacturing cost and ensured transmission stability.
The invention relates to a self-adaptive automatic transmission of double overrunning clutch spindle output input by a planetary system, which comprises a spindle and a speed change system on the spindle, wherein the speed change system comprises a planetary system, a low-speed gear transmission mechanism, a reverse gear transmission mechanism and a self-adaptive speed change assembly;
the self-adaptive speed change assembly comprises a driven friction piece, a driving friction piece and a speed change elastic element;
the driving friction piece and the driven friction piece form a friction transmission pair in a way that friction surfaces are mutually matched, a speed-changing elastic element applies pretightening force for enabling the driven friction piece and the driving friction piece to be in fit transmission, the driven friction piece is in transmission fit with the main shaft through a first axial cam pair, and when the first axial cam pair outputs power through the main shaft, an axial component force opposite to the pretightening force of the speed-changing elastic element is applied to the driven friction piece; (ii) a Driving power is input to a first overrunning clutch through the planetary gear train so as to input power to the active friction piece;
the driving power is also input into the auxiliary shaft through a planetary gear train;
the low-speed transmission mechanism comprises a second overrunning clutch, and the countershaft transmits low-speed power to the driven friction piece through the second overrunning clutch;
the reverse gear transmission mechanism is arranged in a mode of transmitting reverse gear power to the driven friction piece or disconnecting the reverse gear power;
the reverse gear transmission mechanism has a transmission ratio I for transmitting reverse gear power from the auxiliary shaft to the driven friction piece, the low-speed gear transmission mechanism has a transmission ratio II for transmitting low-speed gear power from the auxiliary shaft to the driven friction piece, and the transmission ratio I is larger than or equal to the transmission ratio II;
the planetary gear train comprises an outer gear ring, a planetary gear, a planet carrier and a sun gear, wherein the outer gear ring is fixed on the box body.
Further, the second overrunning clutch and the reverse gear transmission mechanism transmit power to the driven friction piece through the second axial cam pair.
Further, the driving power is input by a sun gear and output by a planet carrier; the second axial cam pair is formed by matching a cam shaft sleeve with an end face cam and the end face cam arranged on the driven friction piece, the cam shaft sleeve is sleeved on the main shaft in a rotating matching mode, and the driven friction piece is sleeved on the main shaft through the first axial cam pair in a transmission matching mode;
the first overrunning clutch inner ring is rotationally matched with the cam shaft sleeve in an external sleeved mode, the end portion of the first overrunning clutch inner ring extends to form an extension section which is in transmission fit with the driving friction piece, and the sun wheel is rotationally matched with the extension section of the first overrunning clutch inner ring in an external sleeved mode; the planet carrier is in transmission fit with the outer ring of the first overrunning clutch and inputs power to the auxiliary shaft at the same time.
Further, the low-speed transmission mechanism also comprises a low-speed driven gear and a low-speed driving gear meshed with the low-speed driven gear, the outer ring of the second overrunning clutch is arranged in a transmission matching mode or directly forms the low-speed driven gear, and the low-speed driving gear is arranged on the auxiliary shaft in a transmission matching mode; the reverse gear transmission mechanism comprises a reverse gear driving gear and a reverse gear driven gear meshed with the reverse gear driving gear, the reverse gear driving gear can be arranged on the auxiliary shaft in an engaging or separating mode, and the reverse gear driven gear and an inner ring of the second overrunning clutch are in transmission fit with the cam shaft sleeve and are arranged on the main shaft in a rotating fit manner; the transmission ratio I is larger than the transmission ratio II.
Furthermore, the reverse gear driving gear is arranged on the auxiliary shaft in a mode that the electromagnetic gear shifting mechanism can be connected or separated, and the electromagnetic gear shifting mechanism is simultaneously used for switching power to be input in a forward and reverse rotation mode.
Further, electromagnetism gearshift includes initiative swing arm, the pivot of shifting gears, shifts the shift fork and two electromagnetism selector, two electromagnetism selector are used for driving the initiative swing arm around the axis swing of the pivot of shifting gears and drive the pivot of shifting gears around the axis of the pivot of shifting gears rotates, the pivot of shifting gears drives the shift fork of shifting gears around the axis swing is shifted and is accomplished.
Furthermore, the electromagnetic gear shifting mechanism is also provided with a positioning mechanism, the positioning mechanism comprises a positioning marble with pretightening force and arranged on the driving swing arm or a positioning component which is connected with the driving swing arm in a follow-up manner, and a positioning base arranged on the transmission box body, and a positioning pit which can be matched with the positioning marble and is jointed with or separated from the reverse gear transmission mechanism in position is arranged on the positioning base; the electromagnetic gear shifting mechanism is also provided with a position sensing assembly for detecting whether gear shifting is in place or not.
Furthermore, the speed change elastic element is a speed change disc spring, the speed change disc spring is sleeved outside the main shaft, one end of the speed change disc spring abuts against the driven friction piece through a plane bearing, and the plane bearing is a plane rolling bearing with double rows of small balls along the radial direction;
and a transmission sleeve is arranged in transmission fit with the sun wheel, is used for being matched with a motor rotor in a transmission way to input power, axially extends to form a shaft neck in a rotation fit way, and is supported in the box body, and the driving friction piece, the driven friction piece and the speed change disc spring are all positioned in a cavity between the transmission sleeve and the main shaft.
Furthermore, the second overrunning clutch and the reverse gear transmission mechanism transmit power to the second axial cam pair through a third axial cam pair so as to transmit the power to the driven friction piece, and the third axial cam pair is formed by matching an end face cam of a second cam shaft sleeve which is rotationally matched and sleeved outside the main shaft with an end face cam of one end of the cam shaft sleeve, which is opposite to the driven friction piece;
the auxiliary shaft is in transmission fit with an intermediate driven gear in transmission fit with the intermediate driving gear;
the inner ring of the second overrunning clutch extends towards the axial outer end to form a shaft sleeve which is in transmission fit with the spindle in an externally sleeved mode, the shaft sleeve is supported on the transmission box in a rotating fit mode, and the other end of the shaft sleeve is in transmission fit with the second cam shaft sleeve;
and one axial end of the outer ring of the first overrunning clutch is in transmission fit with the middle driving gear, the other end of the outer ring of the first overrunning clutch is fixedly connected to the planet carrier, and the power output end of the main shaft penetrates through and is supported on the transmission box body in a rotating fit mode.
Furthermore, the outer circle of the shaft sleeve of the second overrunning clutch is supported on the transmission box body in a rotating fit mode through a first rolling bearing; the second cam shaft sleeve is supported on a transmission box body in a rotating fit mode through a second rolling bearing, the second rolling bearing is located between the reverse gear driven gear and the middle driving gear, the middle driving gear axially extends to form a shaft neck, the shaft neck is further supported on the box body in a rotating fit mode through a fifth rolling bearing, and the middle driving gear is in rotating fit with the second rolling bearing through a first plane bearing; and the inner circle of the transmission sleeve is supported on the main shaft in a rotating fit manner through a fourth rolling bearing.
The invention has the beneficial effects that: the self-adaptive automatic transmission with planetary system input and double overrunning clutch main shaft output has all the advantages of the existing cam self-adaptive automatic transmission, such as the capability of detecting driving torque-rotating speed and driving resistance-vehicle speed signals according to the driving resistance, so that the output power of a motor and the driving condition of a vehicle are always in the best matching state, the balance control of the driving torque of the vehicle and the comprehensive driving resistance is realized, and the self-adaptive automatic gear shifting and speed changing along with the change of the driving resistance are carried out under the condition of not cutting off the driving force; the motor vehicle can be used in mountainous areas, hills and heavy load conditions, so that the motor load changes smoothly, the motor vehicle runs stably, and the safety is improved;
the mechanical self-adaptive automatic transmission has the advantages that the reverse gear structure and the low-speed gear mechanism are reasonably matched by utilizing the two overrunning clutches, the transmission ratio is reasonably set, the overall structure is simple and compact, the reverse gear transmission, the low-speed gear and the high-speed gear share a transmission route, and no interference occurs, so that the overall performance of the mechanical self-adaptive automatic transmission is ensured, the adaptability is strong, the mechanical self-adaptive automatic transmission is smoothly and naturally matched with the self-adaptive automatic speed change mechanism, the manufacturing cost is reduced, the transmission stability is ensured, the planetary speed reduction input is adopted, a high-speed motor can be used as a power source, the overall efficiency is improved, and the mechanical transmission device is not only suitable for the field of electric vehicles, but also suitable for the field of other variable torque mechanical transmissions; the planetary speed reduction input is adopted, a high-speed motor can be used as a power source, the overall efficiency is improved, and the planetary speed reduction input device is not only suitable for the field of electric vehicles, but also suitable for the field of other variable torque mechanical transmission.
Drawings
The invention is further described below with reference to the figures and examples.
FIG. 1 is a schematic axial sectional view of the present invention;
FIG. 2 is a schematic diagram of an electromagnetic shift configuration;
FIG. 3 is a cross-sectional view of the electromagnetic shifting structure;
FIG. 4 is a schematic structural view of the present invention employing a friction plate construction;
FIG. 5 is an enlarged view of the friction plate structure.
Detailed Description
Fig. 1 is a schematic axial section structure, fig. 2 is a schematic electromagnetic shift structure, and fig. 3 is a sectional electromagnetic shift structure, as shown in the drawings: the invention relates to a self-adaptive automatic transmission with planetary train input and double overrunning clutch main shaft output, which comprises a box body 20, a main shaft 1 and a speed change system on the main shaft 1, wherein the speed change system comprises a planetary train, a low-speed transmission mechanism, a reverse transmission mechanism and a self-adaptive speed change component;
the self-adaptive speed change assembly comprises a driven friction piece, a driving friction piece and a speed change elastic element;
the driving friction piece and the driven friction piece form a friction transmission pair in a way that friction surfaces are matched with each other, as shown in fig. 1, the driving friction piece 18 and the driven friction piece 2 are respectively a ring body axial inner taper sleeve and a ring body axial outer taper sleeve, the ring body axial inner taper sleeve is provided with an axial inner conical surface and sleeved on the ring body axial outer taper sleeve, the ring body axial outer taper sleeve is provided with an axial outer conical surface matched with the axial inner conical surface of the ring body axial inner taper sleeve, friction joint transmission or separation is formed through the mutually matched conical surfaces, and the description is omitted;
certainly, the friction transmission pair can also adopt a friction plate structure as shown in fig. 4 and 5, as shown in fig. 4, the active friction piece 18 'and the inner ring of the first overrunning clutch are integrally formed or in transmission fit, the active friction piece 18' is provided with an active friction plate group 18a ', the driven friction piece is provided with a driven friction plate group matched with the active friction plate 18 a', the fit structure is similar to that of the existing friction plate type clutch, but the friction plate of the structure can be detachably arranged and can be disassembled according to the integral structure so as to ensure the axial size;
the speed-changing elastic element 19 applies pretightening force for enabling the driven friction piece and the driving friction piece to be in fit transmission, the driven friction piece is in transmission fit with the main shaft 1 through a first axial cam pair, and when the first axial cam pair outputs power through the main shaft, axial component force opposite to the pretightening force of the speed-changing elastic element is applied to the driven friction piece; the first axial cam pair 27 is an axial cam (including an end cam or a spiral cam) that is engaged with each other, and when the driven friction member rotates, the first axial cam pair 27 generates two component forces in the axial direction and the circumferential direction, where the circumferential component force outputs power, and the axial component force acts on the driven friction member and is applied to the speed change elastic element, that is, the turning direction of the first axial cam pair is related to the power output rotating direction, and according to the above description, a person skilled in the art can know which turning direction of the first axial cam pair 27 can apply the axial component force in which direction on the premise of knowing the power output direction, and details thereof are omitted; (ii) a As shown in the figure, the driven friction piece 2 is sleeved on the main shaft 1 in a transmission fit manner through the first axial cam pair 27, and therefore, the first axial cam pair 27 is a spiral cam and is not described again; the driving power is input to a first overrunning clutch 4 through the planetary gear train, so that the power is input to the active friction piece, and the driving power can be realized through reasonable mechanical layout, and the details are not repeated.
The device also comprises a secondary shaft 12, and the driving power is also input into the secondary shaft 12 through a planetary gear train;
the low-speed transmission mechanism comprises a second overrunning clutch, and the countershaft transmits low-speed power to the driven friction piece through the second overrunning clutch;
the reverse transmission mechanism is provided in such a manner that the reverse power can be transmitted to the driven friction member 2 or the reverse power can be disconnected; the reverse gear transmission mechanism can be disconnected from the transmission of the driven friction piece and the auxiliary shaft 12, and the aim of the invention can be achieved;
the reverse gear transmission mechanism is provided with a transmission ratio I for transmitting reverse gear power from the auxiliary shaft 12 to the main shaft 1, the low-speed gear transmission mechanism is provided with a transmission ratio II for transmitting low-speed gear power from the auxiliary shaft 12 to the main shaft 1, and the transmission ratio I is greater than or equal to the transmission ratio II; when the reverse gear is driven, the second overrunning clutch is used for 6 overrunning, the rotating speed of the inner ring 6a (the rotating direction is the same as that of the reverse gear) is slower than that of the outer ring 6b (both the low-speed gear and the reverse gear are input by the auxiliary shaft), overrunning is formed, the reverse gear transmission mechanism smoothly drives, and otherwise, the reverse gear transmission mechanism is locked.
The planetary gear train includes an outer ring gear 31 fixed to the case 20, a pinion 30, a carrier 32, and a sun gear 29.
The axial cam pair is preferably of a cam structure with two-way output because the low-speed transmission mechanism and the reverse transmission mechanism have different transmission directions.
In this embodiment, the second overrunning clutch 6 and the reverse gear transmission mechanism both transmit power to the driven friction member 2 through the second axial cam pair 26, as shown in the figure; the second axial cam pair is preferably of a cam structure with bidirectional output, because the low-speed transmission mechanism and the reverse transmission mechanism have different transmission directions.
In the present embodiment, the driving power is input from the sun gear 30 and output from the carrier 32; the second axial cam pair 26 is formed by matching a cam shaft sleeve 16 with an end face cam and the end face cam of the driven friction piece 2, the cam shaft sleeve 16 is sleeved on the main shaft 1 in a rotating fit mode, and the driven friction piece 2 is sleeved on the main shaft 1 in a transmission fit mode through a first axial cam pair 27; the inner ring 4a of the first overrunning clutch 4 is rotationally matched with the cam shaft sleeve 22 and the end part of the inner ring is extended to form an extension section which is in transmission fit with the active friction piece 18, and the sun gear 30 is rotationally matched with the extension section of the inner ring 4a of the first overrunning clutch 4; the planet carrier 32 is in transmission fit with the outer ring 4b of the first overrunning clutch 4 and simultaneously inputs power to the auxiliary shaft 12, and the whole planetary structure is compact.
The driving power is input by the sun gear and output to the outer ring 4b of the first overrunning clutch 4 by the planet carrier, as shown in the figure, the transmission sleeve 3 is used for being matched with the rotor of the motor in a transmission way and matched with the sun gear 29 in a transmission way, as shown in the figure, a shaft neck formed by the transmission sleeve 3 externally sleeved on the sun gear can be in interference connection and in spline fit, the power input transmission is formed, and the connection rigidity is improved; the inner ring 4a of the first overrunning clutch 4 is in transmission connection with the active friction piece 18; the driving power is also input into the auxiliary shaft 12 through the outer ring of the first overrunning clutch, that is, the driving power is input in two paths, and the mode of inputting the auxiliary shaft 12 can adopt any existing mechanical transmission structure, such as gears, chains, even direct-connected transmission and the like, and is not described herein again.
In this embodiment, the low-speed transmission mechanism further includes a low-speed driven gear and a low-speed driving gear 7 engaged with the low-speed driven gear, the outer ring 6b of the second overrunning clutch 6 is arranged in a transmission matching manner or directly forms the low-speed driven gear, and the low-speed driving gear 7 is arranged on the auxiliary shaft 12 in a transmission matching manner; the reverse gear transmission mechanism comprises a reverse gear driving gear 9 and a reverse gear driven gear 8 meshed with the reverse gear driving gear 9, the reverse gear driving gear 9 can be arranged on the auxiliary shaft in an engaging (transmission) or separating (rotation) mode, the reverse gear driven gear 8 and an inner ring 6a of the second overrunning clutch 6 are in transmission fit with the cam shaft sleeve 16 and are arranged on the main shaft 1 in a rotating fit mode, and in the embodiment, the inner ring 6a of the second overrunning clutch 6 is integrally formed with the cam shaft sleeve 16; as shown in the drawings, the reverse gear driving gear 9 is disposed on the auxiliary shaft 12 in a rotationally engaged manner (needle bearing), and the engagement or disengagement of the auxiliary shaft is formed by a coupling member slidably and drivingly disposed on the auxiliary shaft, which belongs to a conventional engagement structure and is not described herein again; the transmission ratio I is larger than the transmission ratio II so as to ensure the smoothness of transmission and avoid the occurrence of locking.
In this embodiment, the reverse driving gear 9 is disposed on the auxiliary shaft 12 in a manner that the electromagnetic shift mechanism 10 can be engaged or disengaged, the electromagnetic shift mechanism is simultaneously used for switching power to input in a forward and reverse rotation manner, and when the electromagnetic shift mechanism is switched to a reverse gear, a signal is directly sent to the motor control system to control the motor to rotate reversely, so as to realize the reverse gear; the method can be realized by adopting a common signal acquisition mechanism or a switch.
In this embodiment, the electromagnetic shift mechanism includes an active swing arm 104, a shift spindle 105, a shift fork 106, and two electromagnetic shifters (an electromagnetic shifter 101 and an electromagnetic shifter 102), where the two electromagnetic shifters are configured to drive the active swing arm to swing around an axis of the shift spindle and drive the shift spindle to rotate around the axis of the shift spindle, and the shift spindle drives the shift fork to swing around the axis and complete shifting; as shown in the drawings, in this embodiment, the electromagnetic shifters 101 and 102 are arranged in parallel and respectively used for driving (or releasing) two ends of the driving swing arm, so that the driving swing arm 104 can swing around a central line, the shift shaft is in line with the central line, and is connected to the driving swing arm 104 to drive the driving swing arm to swing around the axis of the shift rotating shaft and drive the shift rotating shaft to rotate around the axis, the shift rotating shaft 105 drives the shift fork 106 to swing around the axis and drive the clutch (synchronizer) 17 to complete shifting, shifting of the clutch (synchronizer) belongs to the prior art, and is not described herein again; of course, the two electromagnetic gear shifters (the electromagnetic gear shifter 101 and the electromagnetic gear shifter 102) may be of an opposite structure, and the driving swing arm is driven to swing back and forth from two sides, so that the purpose of the invention can be achieved, and further description is omitted; the electromagnetic gear shifter is of a structure with a reciprocating push rod, when the electromagnetic gear shifter is powered on, the reciprocating push rod pushes out and pushes the driving swing arm to swing and then return immediately, and the return generally adopts a return spring structure, and the details are not repeated.
In this embodiment, the electromagnetic shift mechanism is further provided with a positioning mechanism 103, the positioning mechanism 103 includes a positioning pin 103b with pretightening force, which is arranged on the driving swing arm or on a positioning component 107 connected with the driving swing arm in a following manner, and a positioning base 103c arranged on the transmission case, and a positioning pit which is matched with the positioning pin 103b and corresponds to the reverse gear transmission mechanism in position or in separation is arranged on the positioning base 103 c; as shown in the figure, in the present embodiment, the positioning pin tumbler is disposed on the positioning component 107, the positioning component 107 is provided with a positioning hole 103a for disposing the positioning pin tumbler 103b, and a positioning spring 103d for applying a pre-tightening force to the positioning pin tumbler 103b to be outwardly positioned and matched with the positioning pit is disposed in the positioning hole; the positioning pin tumbler slides on the surface of the positioning base in the swinging process, and when the positioning pin tumbler slides to the positioning pit, the positioning pin tumbler enters the pit under the action of pretightening force to form positioning, the pit is of a smooth structure, and the positioning pin tumbler can remove the pit under certain thrust to complete a subsequent gear shifting procedure; the electromagnetic gear shifting mechanism is further provided with a position sensing assembly used for detecting whether gear shifting is in place or not, and the sensing assembly generally adopts a Hall element and magnetic steel corresponding to the Hall element.
In this embodiment, the speed-changing elastic element is a speed-changing disc spring 19, the speed-changing disc spring 19 is externally sleeved on the main shaft 1, and one end of the speed-changing disc spring abuts against the driven friction member 2 through a flat bearing 28, the flat bearing 28 is a flat rolling bearing with double rows of small balls along the radial direction, and the small ball is smaller than the ball with the same bearing capacity in the prior art; the double rows of balls are adopted, so that the parameters of the balls can be reduced under the condition that the plane bearing bears the same load, the double rows of balls have the characteristics of stable rotation, high rotating speed of the same load and strong bearing capacity, and the axial installation size can be reduced.
The transmission sleeve 3 is arranged in transmission fit with the sun gear 30, the transmission sleeve 3 is used for inputting power in transmission fit with a motor rotor, axially extends to form a shaft neck, and is supported on the box body in a rotating fit manner through a sixth rolling bearing 24, and the driving friction piece 18, the driven friction piece 2 and the speed change disc spring 19 are all positioned in a cavity between the transmission sleeve and the main shaft; the structure is compact, the integration is strong, and the arrangement of the electric vehicle is convenient; and the support cooperation through driving sleeve 3 for derailleur overall structure rigidity is stronger.
In this embodiment, the intermediate driving gear 15 is disposed in transmission fit with the outer ring 4b of the first overrunning clutch 4, as shown in the figure, the intermediate driving gear 15 forms a stepped shaft with a reduced neck, the outer ring 4b of the first overrunning clutch 4 is fixedly connected with a stepped shaft sleeve with a reduced neck, and the stepped shaft sleeve is sleeved on the stepped shaft to form transmission fit and has radial constraint capability, so as to ensure transmission and a certain supporting effect; the auxiliary shaft 12 is provided with an intermediate driven gear 14 in transmission fit with an intermediate driving gear 15;
in this embodiment, the second overrunning clutch 6 and the reverse gear transmission mechanism transmit power to the second axial cam pair 26 through a third axial cam pair 26 ', so as to transmit the power to the driven friction member 2, where the third axial cam pair 26' is formed by an end cam of a second cam shaft sleeve 25 which is rotationally fitted and sleeved on the main shaft and an end cam of one end of the cam shaft sleeve 16, which faces away from the driven friction member 2; the end facing away from the driven friction member 2 refers to the distal end compared to the driven friction member 2, such as the left end of the figure;
an intermediate driving gear 15 is in transmission fit with the outer ring 4b of the first overrunning clutch 4 and is sleeved outside the cam shaft sleeve in a rotation fit manner or the second cam shaft sleeve, and as shown in the figure, the intermediate driving gear 15 is arranged on the second cam shaft sleeve 25 in a rotation fit manner through a needle bearing 5; the auxiliary shaft 12 is provided with an intermediate driven gear 14 in transmission fit with the intermediate driving gear 5;
the inner ring 6b of the second overrunning clutch 6 extends towards the axial outer end to form a shaft sleeve which is sleeved on the main shaft 1 in a transmission fit manner, the outward direction refers to the outer side (the left end in the drawing) of the transmission, the shaft sleeve is supported on a transmission box body in a rotation fit manner, and the other end (the right end) of the shaft sleeve is in transmission fit with the second cam shaft sleeve 25;
one axial end of an outer ring 4b of the first overrunning clutch 4 is in transmission fit with the intermediate driving gear 5, the other end of the outer ring is fixedly connected to the planet carrier (in transmission), and the power output end of the main shaft 1 penetrates through and is supported on the transmission box body 20 in a rotating fit mode.
In this embodiment, the outer circle of the sleeve of the inner ring 6b of the second overrunning clutch 6 is supported on the transmission case 20 by the first rolling bearing 22 in a rotating fit manner; the second camshaft sleeve 25 is supported on the transmission case 20 in a rotating fit manner through a second rolling bearing 21, the second rolling bearing 21 is located between the reverse gear driven gear 8 and the middle driving gear 5, the middle driving gear 5 axially extends to form a shaft neck, the shaft neck is further supported on the case 20 in a rotating fit manner through a fifth rolling bearing 11, and the middle driving gear 5 and the second rolling bearing 21 are in a rotating fit manner through a first plane bearing 13 (plane rolling bearing); the inner circle of the transmission sleeve 3 is supported on the main shaft 1 through a fourth rolling bearing 23 in a rotating fit mode.
As shown in the figure, each rolling bearing supports a support rib formed on the box body, and has a reinforcing effect on the box body, the power output end of the main shaft 1 penetrates through and is supported on the transmission box body 20 through the third rolling bearing 23 in a rotating fit mode, and the transmission sleeve is supported on the main shaft 1 through the fourth rolling bearing 23 in a rotating fit mode.
In the structure of the embodiment, the power output and input section on the main shaft or/and the cam shaft sleeve is/are correspondingly and rotatably supported on the transmission box body, and in the structure, the cam shaft sleeve is sleeved on the main shaft to form a transmission and mutual support structure, so that larger torque can be transmitted without bending deformation, and the sizes of components under the condition of the same bearing capacity can be greatly reduced; aiming at each transmission bearing (power connection input and output section) part, the transmission bearing (power connection input and output section) parts are respectively supported in a transmission box body, so that a main shaft and a transmission shaft sleeve can be arranged longer, and additional bending moment generated by torque is transmitted to the box body due to the support, so that larger torque is transmitted per se, the rotating speed (the same component size) under large torque can be greatly improved, the indexes of large torque, high rotating speed and light weight are realized, the radial bearing and the shaft sleeve and the main shaft are mutually supported, the transmission has better stability and low noise under a high-speed state, compared with the prior art, the highest rotating speed for driving a motor and a high-speed reducer is more than or equal to 15000 r/min, the speed change mechanisms for efficient light-weight hub electric wheels and the like have greater advantages for energy conservation and environmental protection, and can be more suitable for pure electric vehicles taking energy conservation and environmental protection as main targets, of course, the invention is not only suitable for the field of electric vehicles, but also suitable for the field of other variable torque mechanical transmission.
In the present invention, the left and right sides of the drawings are used as the standard, and the recorded transmission connection includes all transmission connection structures in the prior art, including splines, flat keys, bolt fixed connection, etc., and is not described herein again.
The above embodiments are merely the best structures of the present invention, and do not limit the scope of the present invention; the scheme is adjusted on the connection mode, and the realization of the vision of the invention is not influenced.
The fast-gear power transmission route of the embodiment:
power → active friction element 18 → passive friction element 2 → first axial cam pair → main shaft 1 → output power;
at this time, the second overrunning clutch overruns, and the resistance transmission route is as follows: main shaft 1 → first axial cam pair → driven friction piece 2 → transmission disc spring; when the running resistance is increased to a certain value, the axial force overcomes the speed change disc spring to separate the active friction piece 18 from the driven friction piece 2, and the power is transmitted through the following route, namely a low-gear power transmission route:
power → the outer ring 4b of the first overrunning clutch 4 → the counter shaft 12 → the low-speed drive gear → the outer ring 6b of the second overrunning clutch 6 → the inner ring 6a of the second overrunning clutch → the second axial cam pair 26' → the driven friction member 2 → the first axial cam pair 26 → the driven friction member 2 → the axial cam pair 27 → the main shaft outputs power.
The low-speed power transmission route also passes through the following routes: the first axial cam pair 26 → the driven friction piece 2 → the compression speed change disc spring, which prevents the compression speed change disc spring from reciprocating compression during the low-speed gear transmission, thereby preventing the driving friction piece 18 and the driven friction piece 2 from being attached during the low-speed gear transmission.
It can be seen from the above transmission path that, when the present invention is operated, the active friction member 18 and the driven friction member 8 are tightly attached under the action of the speed change disc spring to form an automatic speed change mechanism which keeps a certain pressure, and the pressure required by the engagement of the clutch can be adjusted by increasing the axial thickness of the speed change shaft sleeve to achieve the transmission purpose, at this time, the power drives the active friction member 18, the driven friction member 2 and the main shaft 1 to make the main shaft 1 output power; the second overrunning clutch is in an overrunning state at the moment.
When the motor vehicle is started, the resistance is larger than the driving force, the resistance forces the cam shaft sleeve to rotate a certain angle in the opposite direction, and the driven friction piece 2 compresses the speed change disc spring under the action of the first axial cam pair; the driven friction piece 2 and the driving friction piece 18 are separated and synchronized, the second overrunning clutch is engaged, and the output power rotates at a low-gear speed; therefore, the low-speed starting is automatically realized, the starting time is shortened, and the starting force is reduced. Meanwhile, the speed change disc spring absorbs the motion resistance moment energy to transfer power to store potential energy for recovering the fast gear.
After the start is successful, the running resistance is reduced, when the component force is reduced to be smaller than the pressure generated by the speed change disc spring, the pressure of the speed change disc spring generated by the compression of the motion resistance is quickly released and pushed, the recovery of the close fit state of the driven friction piece 2 and the driving friction piece 18 is completed, and the low-speed gear overrunning clutch is in an overrunning state.
In the driving process, the automatic gear shifting principle is the same as the principle of automatic gear shifting along with the change of the motion resistance, gear shifting is realized under the condition of not cutting off the driving force, the whole locomotive runs stably, safety and low consumption are realized, a transmission route is simplified, and the transmission efficiency is improved.
A reverse gear transmission route:
power → the outer race 4b of the first overrunning clutch 4 → the counter shaft 12 → the reverse drive gear → the reverse driven gear → the second axial cam pair 26' → the first axial cam pair 26 → the driven friction member 2 → the axial cam pair 27 → the main shaft 1 outputs the reverse power.
At the moment, because the transmission ratio of the reverse gear is larger than the transmission ratio of the low gear and is reverse, the second overrunning clutch overruns, and because the rotation is reverse and the rotating speed of the outer ring is higher than that of the inner ring, the first overrunning clutch overruns, so that the reverse gear transmission is realized; of course, both the low-speed transmission and the reverse transmission are downshifted transmissions, which are not described in detail herein.
Finally, the above embodiments are only for illustrating the technical solutions of the present invention and not for limiting, although the present invention has been described in detail with reference to the preferred embodiments, it should be understood by those skilled in the art that modifications or equivalent substitutions may be made to the technical solutions of the present invention without departing from the spirit and scope of the technical solutions of the present invention, which should be covered in the claims of the present invention.

Claims (10)

1. A self-adaptive automatic transmission with planetary system input and double overrunning clutch main shaft output is characterized in that: the speed change system comprises a main shaft and a speed change system on the main shaft, wherein the speed change system comprises a planetary gear train, a low-speed gear transmission mechanism, a reverse gear transmission mechanism and a self-adaptive speed change assembly;
the self-adaptive speed change assembly comprises a driven friction piece, a driving friction piece and a speed change elastic element;
the driving friction piece and the driven friction piece form a friction transmission pair in a way that friction surfaces are mutually matched, a speed-changing elastic element applies pretightening force for enabling the driven friction piece and the driving friction piece to be in fit transmission, the driven friction piece is in transmission fit with the main shaft through a first axial cam pair, and when the first axial cam pair outputs power through the main shaft, the first axial cam pair applies axial component force opposite to the pretightening force of the speed-changing elastic element to the driven friction piece; driving power is input to a first overrunning clutch through the planetary gear train so as to input power to the active friction piece;
the driving power is also input into the auxiliary shaft through the planetary gear train;
the low-speed transmission mechanism comprises a second overrunning clutch, and the countershaft transmits low-speed power to the driven friction piece through the second overrunning clutch;
the reverse gear transmission mechanism is arranged in a mode of transmitting reverse gear power to the driven friction piece or disconnecting the reverse gear power;
the reverse gear transmission mechanism has a transmission ratio I for transmitting reverse gear power from the auxiliary shaft to the driven friction piece, the low-speed gear transmission mechanism has a transmission ratio II for transmitting low-speed gear power from the auxiliary shaft to the driven friction piece, and the transmission ratio I is larger than or equal to the transmission ratio II;
the planetary gear train comprises an outer gear ring, a planetary gear, a planet carrier and a sun gear, wherein the outer gear ring is fixed on the box body.
2. The planetary input, dual overrunning clutch spindle output adaptive automatic transmission of claim 1, wherein: and the second overrunning clutch and the reverse gear transmission mechanism transmit power to the driven friction piece through the second axial cam pair.
3. The planetary input, dual overrunning clutch spindle output adaptive automatic transmission of claim 2, wherein: the driving power is input by the sun gear and output by the planet carrier; the second axial cam pair is formed by matching a cam shaft sleeve with an end face cam and the end face cam arranged on the driven friction piece, the cam shaft sleeve is sleeved on the main shaft in a rotating matching mode, and the driven friction piece is sleeved on the main shaft through the first axial cam pair in a transmission matching mode;
the first overrunning clutch inner ring is rotationally matched with the cam shaft sleeve in an external sleeved mode, the end portion of the first overrunning clutch inner ring extends to form an extension section which is in transmission fit with the driving friction piece, and the sun wheel is rotationally matched with the extension section of the first overrunning clutch inner ring in an external sleeved mode; the planet carrier is in transmission fit with the outer ring of the first overrunning clutch and inputs power to the auxiliary shaft at the same time.
4. The planetary input, dual overrunning clutch spindle output adaptive automatic transmission of claim 3, wherein: the low-speed gear transmission mechanism further comprises a low-speed gear driven gear and a low-speed gear driving gear meshed with the low-speed gear driven gear, the outer ring of the second overrunning clutch is arranged in a transmission matching mode or directly forms the low-speed gear driven gear, and the low-speed gear driving gear is arranged on the auxiliary shaft in a transmission matching mode; the reverse gear transmission mechanism comprises a reverse gear driving gear and a reverse gear driven gear meshed with the reverse gear driving gear, the reverse gear driving gear can be arranged on the auxiliary shaft in an engaging or separating mode, and the reverse gear driven gear and an inner ring of the second overrunning clutch are in transmission fit with the cam shaft sleeve and are arranged on the main shaft in a rotating fit manner; the transmission ratio I is larger than the transmission ratio II.
5. The planetary input, dual overrunning clutch spindle output adaptive automatic transmission of claim 4, wherein: the reverse gear driving gear is arranged on the auxiliary shaft in a mode that the electromagnetic gear shifting mechanism can be connected or separated, and the electromagnetic gear shifting mechanism is simultaneously used for switching power to input in a positive and negative rotation mode.
6. The planetary input, dual overrunning clutch spindle output adaptive automatic transmission of claim 5, wherein: the electromagnetic gear shifting mechanism comprises an active swing arm, a gear shifting rotating shaft, a gear shifting fork and two electromagnetic gear shifters, wherein the two electromagnetic gear shifters are used for driving the active swing arm to swing around the axis of the gear shifting rotating shaft and driving the gear shifting rotating shaft to rotate around the axis of the gear shifting rotating shaft, and the gear shifting rotating shaft drives the gear shifting fork to swing around the axis and complete gear shifting.
7. The planetary input, dual overrunning clutch spindle output adaptive automatic transmission of claim 6, wherein: the electromagnetic gear shifting mechanism is also provided with a positioning mechanism, the positioning mechanism comprises a positioning marble with pretightening force and arranged on the driving swing arm or a positioning component which is connected with the driving swing arm in a follow-up manner, and a positioning base arranged on the gearbox box body, and a positioning pit which can be matched with the positioning marble and corresponds to the reverse gear transmission mechanism in position of engaging or disengaging is arranged on the positioning base; the electromagnetic gear shifting mechanism is further provided with a position sensing assembly used for detecting whether gear shifting is in place or not.
8. The planetary input, dual overrunning clutch spindle output adaptive automatic transmission of claim 3, wherein: the speed change elastic element is a speed change disc spring, the speed change disc spring is externally sleeved on the main shaft, one end of the speed change disc spring props against the driven friction piece through a plane bearing, and the plane bearing is a plane rolling bearing with double rows of small balls along the radial direction;
and a transmission sleeve is arranged in transmission fit with the sun gear, is used for inputting power in transmission fit with the motor rotor, axially extends to form a shaft neck in rotation fit with the box body, and is supported in the box body, and the driving friction piece, the driven friction piece and the speed change disc spring are all positioned in a cavity between the transmission sleeve and the main shaft.
9. The planetary input, dual overrunning clutch spindle output adaptive automatic transmission of claim 2, wherein: the second overrunning clutch and the reverse gear transmission mechanism transmit power to the second axial cam pair through a third axial cam pair so as to transmit the power to the driven friction piece, and the third axial cam pair is formed by matching an end face cam of a second cam shaft sleeve which is rotationally matched and sleeved on the main shaft with an end face cam of one end of the cam shaft sleeve, which is opposite to the driven friction piece;
the auxiliary shaft is in transmission fit with an intermediate driven gear in transmission fit with the intermediate driving gear;
the inner ring of the second overrunning clutch extends towards the axial outer end to form a shaft sleeve which is in transmission fit with the spindle in an externally sleeved mode, the shaft sleeve is supported on the transmission box body in a rotating fit mode, and the other end of the shaft sleeve is in transmission fit with the second cam shaft sleeve;
and one axial end of the outer ring of the first overrunning clutch is in transmission fit with the middle driving gear, the other end of the outer ring of the first overrunning clutch is fixedly connected to the planet carrier, and the power output end of the main shaft penetrates through and is supported on the transmission box body in a rotating fit mode.
10. The planetary input, dual overrunning clutch spindle output adaptive automatic transmission of claim 8, wherein: the outer circle of the shaft sleeve of the second overrunning clutch is supported on the transmission box body in a rotating fit mode through a first rolling bearing; the second cam shaft sleeve is supported on a transmission box body in a rotating fit mode through a second rolling bearing, the second rolling bearing is located between the reverse gear driven gear and the middle driving gear, the middle driving gear axially extends to form a shaft neck, the shaft neck is further supported on the box body in a rotating fit mode through a fifth rolling bearing, and the middle driving gear is in rotating fit with the second rolling bearing through a first plane bearing; and the inner circle of the transmission sleeve is supported on the main shaft in a rotating fit manner through a fourth rolling bearing.
CN201910309314.2A 2019-04-17 2019-04-17 Self-adaptive automatic transmission with planetary system input and double overrunning clutch main shaft output Active CN110030355B (en)

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CN110939699B (en) * 2019-12-04 2022-04-22 西南大学 Mechanical self-adaptive automatic transmission adopting multi-piece type large-torque friction clutch
CN111204407B (en) * 2019-12-31 2021-06-15 西南大学 Fixed shaft type large-load self-adaptive electric drive assembly adopting central drive form

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