CN114857230A - 5-15 drive ratio push type CVT mechanical stepless speed changer for electric automobile - Google Patents
5-15 drive ratio push type CVT mechanical stepless speed changer for electric automobile Download PDFInfo
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- CN114857230A CN114857230A CN202210307810.6A CN202210307810A CN114857230A CN 114857230 A CN114857230 A CN 114857230A CN 202210307810 A CN202210307810 A CN 202210307810A CN 114857230 A CN114857230 A CN 114857230A
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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
- F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
- F16H37/12—Gearings comprising primarily toothed or friction gearing, links or levers, and cams, or members of at least two of these types
- F16H37/124—Gearings comprising primarily toothed or friction gearing, links or levers, and cams, or members of at least two of these types for interconverting rotary motion and reciprocating motion
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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
- F16H61/66—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
- F16H61/662—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 with endless flexible members
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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
- F16H61/66—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
- F16H2061/6604—Special control features generally applicable to continuously variable gearings
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- 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
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- Y02T10/60—Other road transportation technologies with climate change mitigation effect
- Y02T10/72—Electric energy management in electromobility
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Abstract
The invention discloses a 5-15 push force type CVT mechanical stepless speed changer for a new energy electric vehicle, wherein two or more driving push wheels driven by a motor are uniformly arranged around an output cone pulley, working cone surface rings at two sides of the driving push wheels are respectively in tangential contact with the output cone pulley and keep a certain radial pressure, the driving push wheels revolve around the output cone pulley but do not rotate to push the output cone pulley to rotate, the rotating speed of the output cone pulley is changed to realize stepless speed regulation by changing the radial positions of the working cone surface rings of the driving push wheels tangent to the output cone pulley, the diameter of the working cone surface rings of the driving push wheels is 1/15 of the diameter of the output cone pulley under a reasonable size, 5-15 wide-range transmission ratio change is realized through a planetary gear output mechanism, the torque is increased, the rotating speed of the motor is kept in a high-efficiency reasonable area in all working condition ranges, the power does not break and the speed regulation is stable without gear shifting pause in the speed changing process, and the rotating speed of the motor is reduced, the energy consumption is reduced, the endurance mileage is prolonged, and the high-speed cruising ability is improved.
Description
Technical Field
The invention relates to a continuously variable transmission, in particular to a CVT mechanical continuously variable transmission for a new energy electric automobile.
Background
Most of the existing electric automobiles adopt a single-stage speed reducer with a transmission ratio of about 9, adopt a double-stage speed reduction transmission with a transmission ratio of about 6 and about 10, try to adopt a multi-stage speed reduction transmission, try to adopt a steel belt or steel chain CVT mechanical stepless speed changer of a traditional fuel oil vehicle to meet various working condition requirements of the vehicle, and adopt two motors with different modes and respectively match with the single-stage speed reducers with different speed ratios to meet the high and low speed requirements of the vehicle.
In addition, although the single-stage reducer is used for matching the motor with various working conditions, the motor can meet the requirements of most common working conditions under the conditions of large current, high rotating speed and high energy consumption. Although the two motors with different modes can better match working conditions, the two motors with different modes are only in a reasonable efficiency region under partial working conditions, the difference range of the transmission ratios of all gears of the two-stage and multi-stage transmissions is large, and gear shifting setback is inevitably generated no matter what gear shifting mode is adopted. Electric vehicles using a conventional fuel vehicle CVT continuously variable transmission: "because the steel belt or steel chain type CVT continuously variable transmission applied to the fuel vehicle has a transmission ratio range generally between 0.5 and 5, the steel belt or steel chain type CVT continuously variable transmission which is redesigned to be matched with the electric vehicle can only have a partial transmission ratio range to adapt to partial working condition requirements of the motor due to the limitation of the structure and the size of the steel belt or steel chain type CVT continuously variable transmission".
Disclosure of Invention
The problem that after a new energy electric vehicle is provided with a single-stage double-stage or multi-stage speed reducer, a traditional CVT (continuously variable transmission) or two motors with different modes, the rotating speed of the motor can not be kept in a reasonable high-efficiency area in most working conditions is solved, the size and the power of the motor and a controller which are provided with fewer stages of the speed reducer are correspondingly larger, the power consumption is larger, the driving mileage is shortened, and the like, and the problems of gear shifting pause and frustration of the double-stage multi-stage speed reducer are also solved. In view of the above, the invention provides a thrust type CVT mechanical continuously variable transmission with a transmission ratio range of 5 to 15, which is specially applied to new energy electric vehicles, aiming at the characteristics of electric vehicle motors, and meets the requirements of various working conditions in a full speed range.
The technical scheme adopted by the invention for solving the technical problems is as follows: two or more driving push wheels (the chamfers processed at the left and right ends of the driving push wheels are working conical surface rings) driven by an input shaft connected with a motor are uniformly arranged around an output conical wheel, the working conical surface rings at the two ends of the driving push wheels are respectively in tangential contact with the left and right working conical wheels of the output conical wheel and keep a certain radial pressure, the driving push wheels do circular motion around the output conical wheel, but the driving push wheels do not rotate and only can revolve around the output conical wheel and push the output conical wheel to rotate, the left and right working conical wheels of the output conical wheel can be close to or separated from each other, the driving push wheels can be close to or far away from the axis of the output conical wheel, when the driving push wheels are close to the axis of the output conical wheel to a limit position, the two working conical wheels of the output conical wheel are matched with the driving push wheels to separate left and right, the driving push wheels are in a high-speed gear position and in a low-speed gear position, otherwise, and the gears can be changed at any position between a high-low gear, namely, the radial position of the working conical surface ring of the driving push wheel tangent with the output conical wheel is changed to change the output rotating speed, and finally, the effective stepless transmission with the transmission ratio range of 5-15 is realized through the planetary gear output mechanism.
The working principle of the device will be described with reference to fig. 1, 2 and 3. in fig. 1 and 2, a circle with a circle center O is a driven wheel, the diameter of the large driven wheel is 2 times of that of the small driven wheel, the arc length between two adjacent points on the circumference of the large driven wheel is equal to the arc length between two adjacent points on the circumference of the small driven wheel, and the length of the arc length is equal to that of the driven wheel
In the figure 1, the driving push block which moves along a straight line is symmetrically arranged on the circumference of the driven wheel, the driving push block is in tangential contact with the driven wheel and pushes the driven wheel to rotate, just as if a pen is twisted by two hands to rotate, the driving push block moves along the AB distance in the figure 1 to push the large driven wheel to rotate by the arc length between 1 and 2, namely, 1/16 circumference arc length, the corresponding rotation circumference angle is 360 degrees/16 degrees to 22.5 degrees, in the figure 1, the diameter of the small driven wheel is 1/2 degrees of the large driven wheel, so the circumference is 1/2 degrees, and because the arc lengths of two adjacent points on the circumferences of the large driven wheel and the small driven wheel are equal, namely, the arc lengths of two adjacent points on the circumferences of the large driven wheel and the small driven wheel are equal, so that the circumference of the large driven wheel and the small driven wheel are 1/2 degrees
And is
So that the same driving push block moves AB distance to push the small driven wheel to rotate over 1 and 1 on the driving push blockThe arc length between 2, namely 1/8 circumference arc length, the corresponding rotation circumference angle is 360 °/8 ═ 45 °, so when the condition of the driving push block is not changed, the output rotation speed of the driven wheel can be changed by changing the size of the driven wheel, in fig. 2, the driving push block which moves linearly is changed into the driving push wheel which moves circularly and does not rotate, the driven wheel can rotate continuously, when the diameter of the driven wheel is changed randomly, the output rotation speed can be changed steplessly, in the upper diagram of fig. 2, the driving push wheel rotates 90 ° around the driven wheel and drives the driven wheel to rotate 90 ° +22.5 ° + 112.5 ° under the action of resultant force F, in the lower diagram of fig. 2, the driving push wheel rotates 90 ° around the driven wheel and drives the driven wheel to rotate 90 ° +45 ° + 135 ° under the action of resultant force F, from which it can be seen that when the driving push wheel revolves 90 ° to push the driven wheel to rotate, the driven wheel together pass through a common angle of 90 °, by driven wheels outside the common angle
Corresponding angles 22.5 ° and 45 °, that is, the difference between the rotation angle of the driven wheel and the revolution angle of the driving push wheel, are the rotation angles required as in fig. 1, and if a continuous rotation angle is required, the planetary gear output mechanism shown in fig. 3 is required to be matched, in fig. 3 a): the diameters of the reference circles of the number of teeth of the sun gear, the planet gears and the ring gear in the 3 planet rows are respectively the same, the ring gear 8 (connected with the driving push wheel) and the ring gear 9 (connected with the driven wheel) drive the planet carrier 6 to revolve around the sun gear 7 and the sun gear 10 through the planet gears 2 and 1 respectively, as can be seen from fig. 2, when the driving push wheel pushes the driven wheel to rotate, the driving push wheel and the driven wheel all rotate together through a common angle, the angle around which the driven wheel outside the common angle passes through is the required rotation angle, that is, the difference value of the rotation speed of the ring gear 9 being greater than that of the ring gear 8 is the required rotation angle, and because the sun gear 7 is fixed, the ring gear 8 only controls the planet carrier to rotate, the difference value of the rotation speed of the ring gear 9 being greater than that of the ring gear 8 also drives the sun gear 10 to rotate reversely through the planet gears 1, and then through the sun gear 4, The planet wheel 3 and the ring gear 5 output the difference in positive direction. The combination of fig. 2, 3a) forms a complete thrust continuously variable transmission.
The above-described push-type CVT mechanical continuously variable transmission includes: the input part consists of an input shaft, a right driving disc sleeved on the input shaft and fixedly connected with the input shaft, and a left driving disc sleeved on a central fixed control gear sleeve, wherein the left driving disc and the right driving disc are fixedly connected through two ends of at least two intermediate idler shafts; the driving push wheel part is formed by fixedly connecting a push wheel shaft and a push wheel gear sleeved on the push wheel shaft and is arranged between a left driving disc and a right driving disc, chamfers are processed at two ends of the push wheel shaft to form a working conical surface ring, two ends of the push wheel shaft are inserted into arc-shaped guide notches of the left driving disc and the right driving disc and can move along the notches, and the driving discs drive the driving push wheel to revolve around the output conical wheel and push the output conical wheel to rotate; the non-autorotation part of the driving push wheel is controlled to be composed of a central fixed control gear, an intermediate idle gear and a push wheel gear, wherein the intermediate idle gear is arranged on a driving disc idle gear shaft, the central fixed control gear is sleeved on an input shaft through a sleeve and is fixed on a transmission shell so as to be fixed and non-rotating, and the intermediate idle gear on the driving disc idle gear shaft limits the autorotation of the push wheel gear; the radial displacement control part of the driving push wheel consists of sector gear pieces, a circumferential gear ring and an arc bidirectional piston hydraulic cylinder with one end outputting, wherein two sector gear pieces are sleeved at two ends of a middle idler shaft and can freely rotate relative to the middle idler, round holes are arranged near the edges of the sector gear pieces and sleeved on the push wheel shaft through the round holes, the sector gear pieces are driven by the circumferential gear ring, only two sides of the circumferential gear ring are provided with gear teeth which are respectively meshed with the sector gear pieces, no teeth are arranged in the middle of the circumferential gear ring to prevent collision with the push wheel gear, a convex block is arranged inside the circumferential gear ring and connected with the front end of a piston of the hydraulic cylinder, the arc hydraulic cylinder is arranged between a left driving disc and a right driving disc and is fixedly connected with the driving discs, a cylindrical boss is arranged at the tail part of the arc piston, the hydraulic cylinder is divided into a front hydraulic working cavity and a rear hydraulic cavity, when the hydraulic cylinder works, the arc piston can drive the circumferential gear ring to rotate relative to the driving discs, meanwhile, the circumferential gear ring drives the sector gear piece to rotate, so that the driving push wheel can be driven to rotate around the intermediate idle wheel and drive the push wheel shaft to move along the arc-shaped guide notch on the driving disc, the radial displacement of the driving push wheel is realized, and the driving push wheel always keeps radial pressure on the output bevel wheel under the action of the hydraulic cylinder; the output cone pulley and the left and right cone pulley separation approach control part thereof are composed of an output cone pulley frame, a left and right cone pulley hydraulic cylinder fixedly connected with the frame, a left and right cone pulley integrated with a hydraulic cylinder piston, wherein the left and right cone pulleys integrated with the piston are also engaged with spline teeth on the hydraulic cylinder through spline teeth to limit the relative rotation of the cone pulley, the hydraulic cylinder and the frame, the hydraulic cylinder and the cone pulley on the left side are sleeved on a sleeve of a central fixed control gear, the hydraulic cylinder and the cone pulley on the right side are sleeved on an input shaft of a transmission, and the left and right hydraulic cylinders are fixedly connected into a whole through the frame, so when the hydraulic cylinder is fed with oil to work, the left and right cone pulleys approach, and when the driving push wheel approaches to the axis of the output cone pulley, the output cone pulley is pushed to be separated left and right, thereby realizing the stepless conversion between high and low gears; the planetary gear output part consists of a first output planetary row, a control planetary row and a second output planetary row, the tooth number reference circle diameters of 3 planetary rows, planetary wheels and central wheels are respectively the same, the planetary carriers of the first output planetary row and the control planetary row are shared, the central gear of the first output planetary row and the central gear of the second output planetary row are fixedly connected by a shaft penetrating through the central gear of the control planetary row, an input shaft of the transmission is connected with the gear ring of the control planetary row and drives and controls the planetary carriers to revolve around the central gear fixed on the shell through the planetary wheels, an output bevel wheel of the transmission is connected with the gear ring of the first output planetary row and also drives the planetary carrier to revolve around the central gear, the input shaft only controls the rotation of the planetary carriers because the central gear of the control planetary row is fixed, and the planetary wheels of the first output planetary row and the control planetary row only drive the planetary carriers to revolve around the central gear on the assumption that the rotation speeds of the input shaft and the output bevel wheel are the same In practice, because the rotating speed of the output bevel wheel is greater than that of the input shaft, and the central gear of the planet row is controlled to be fixed on the shell, so that the rotating speed of the planet carrier is controlled by the input shaft, the rotating speed of the output bevel wheel is greater than that of the input shaft, but the rotating speed of the planet carrier cannot be higher, the central gear of the first output planet row can only be driven by the planet wheel to rotate reversely, the reverse rotation drives the planet wheel of which the planet carrier is fixed on the shell by the central gear of the second output planet row, and then the rotating speed of the forward output of the ring gear is the difference value of the rotating speed of the output bevel wheel greater than that of the input shaft, namely the required output rotating speed.
The planetary gear output is described in particular here: as shown in FIG. 4, the transmission is mounted transversely on the vehicle, and the transmission input shaft and the planetary gear output part are arranged in parallel: the sun gears of the first and second output planetary rows are fixedly connected by a hollow shaft so that the half shafts drive the wheels through the hollow shaft, and the first output planetary row and the ring gear of the control planetary row are processed with external gears in addition to the internal gear and are driven by a gear fixed to the output cone hydraulic cylinder and a gear fixed to the input shaft, respectively, if the transmission input shaft is arranged coaxially with the planetary gear output: in this case, the planetary gear of the control planetary row needs to extend to the other side of the first output planetary row through the hollow shaft sleeved on the planet carrier, and the planetary gear of the first output planetary row is sleeved in the middle position of the hollow shaft, so that the ring gear of the control planetary row can move from the right side to the left side of the first output planetary row, and the connection of the input shaft is convenient, namely the situation shown in fig. 3 b).
The above-described transmission scheme realizes a thrust CVT mechanical continuously variable transmission. The high-pressure oil of the hydraulic cylinder can be supplied by a mechanical oil pump built in a similar traditional AT gearbox, and can also be supplied by a flexibly arranged electronic oil pump.
The invention has the beneficial effects that: the structure is simple, the driving push wheel which only revolves around the output cone pulley but does not rotate is adopted to push the output cone pulley to rotate, the radial position of the working conical surface ring of the driving push wheel which is tangent to the conical surface of the output cone pulley is changed to change the rotating speed of the output cone pulley, thereby realizing stepless speed regulation, the diameter of the working conical surface ring of the driving push wheel is 1/15 of the diameter of the output cone pulley under the volume of a transmission with normal reasonable size, and the transmission ratio change with the wide range of 5 to 15 is realized through a planetary gear output mechanism behind the driving push wheel, thereby the rotating speed of the motor of the electric automobile is kept in a high-efficiency reasonable area in all working condition ranges, thereby the battery electric energy is efficiently utilized to prolong the driving mileage of the automobile, the amplitude of the change of the output current of the battery under the conversion of various working conditions is reduced, the service lives of devices such as a battery motor controller are prolonged, and under the same automobile condition, the corresponding small-volume small-power motor and the controller can achieve the effect which can be achieved by the corresponding large-volume large-power motor, the rotating speed of the motor is greatly reduced under the high-speed state of the vehicle, the power consumption is reduced, the vehicle speed is improved, the defects that the efficiency and the torque of the motor are rapidly reduced and the noise is increased under the high rotating speed are overcome, the speed regulation process is stable, the power is not interrupted in the speed change process, and therefore gear shifting pause and pause do not exist.
Drawings
The invention is further illustrated with reference to the following figures and examples:
FIGS. 1 and 2 are schematic diagrams of the present invention;
FIG. 3 is a schematic illustration of the planetary gear output portion of the transmission;
FIG. 4 is a schematic diagram of the transmission and its connections to the electric machine and the differential;
FIG. 5 is a model of an embodiment of a transmission;
FIG. 6 is a schematic representation of the top and low gear positions of the embodiment of the transmission wherein a) is the lowest gear position and b) is the highest gear position;
FIG. 7 is a schematic diagram of the operation of the active pushwheel portion, the non-spinning portion for controlling the active pushwheel, and the radial displacement control portion of the active pushwheel of the transmission embodiment, wherein a) is the lowest gear position, and b) is the highest gear position;
FIG. 8 is a model explosion diagram of an embodiment of a transmission;
FIG. 9 is a block diagram of an output cone pulley and control cylinder of an embodiment of the transmission;
FIG. 10 is an exploded view of the input section, the driving pushwheel section, the non-spinning control section of the driving pushwheel, and the radial displacement control section of the driving pushwheel of the exemplary transmission;
FIG. 11 is an exploded view of the planetary gear output section of the transmission embodiment;
in the figure: 1. a first output planet row planet gear, 2 a control planet row planet gear, 3a second output planet row planet gear, 4 a second output planet row central gear, 5 an output gear ring, 6 a first output planet row and control planet row shared planet carrier, 7 a control planet row central gear fixed on the shell, 8 a control planet row ring gear connected with the input shaft of the speed changer, 9 a first output planet row ring gear connected with the output cone gear of the speed changer, 10 a first output planet row central gear, 11 a control planet row extension planet gear, 12 a first output planet row internal and external gear ring gear, 13 a control planet row internal and external gear ring gear, 14 a right cone gear, 15 a right cone gear hydraulic cylinder, 16 a speed changer input shaft, 17 a speed changer input shaft gear, 18 an output gear fixed with the output cone gear, 19 a right driving disk fixed with the input shaft of the speed changer, 20. the hydraulic system comprises a push wheel shaft, 21, a left driving disc, 22, a left bevel wheel, 23, a left bevel wheel hydraulic cylinder, 24, a central fixed control gear, 25, an intermediate idler wheel shaft, 26, an intermediate idler wheel, 27, a push wheel gear, 28, an output bevel wheel frame, 29, an arc-shaped bidirectional piston hydraulic cylinder, 30, a circumferential gear ring, 31, a shell partition plate, 32, a fan-shaped gear piece, 33, a circumferential gear ring lug, 34, a differential, 35, a motor and 36 spline teeth, wherein the left driving disc is sleeved on a sleeve of a central fixed control gear.
Detailed Description
[ examples ]
The push-type CVT mechanical continuously variable transmission includes: the device comprises an input part, an active push wheel part, a part for controlling the active push wheel not to rotate, a radial displacement control part of the active push wheel, an output cone pulley, a control part for controlling the separation and approach of a left cone pulley and a right cone pulley thereof, a planetary gear output part and the like 6. As shown in fig. 5, 6, 7, 8, 9, 10, and 11: the input part consists of an input shaft 16, a right driving disc 19 fixedly connected with the input shaft and a left driving disc 21 sleeved on a sleeve of a central fixed control gear 24, arc-shaped guide notches with the same number as the driving push wheels are machined on the driving discs, and the driving discs 19 and 21 are fixedly connected with two ends of an intermediate idler shaft 25; the driving push wheel part consists of a push wheel shaft 20 and a push wheel gear 27 which is sleeved on the push wheel shaft and fixedly connected with the push wheel shaft, the driving push wheel part is arranged between the driving disks 19 and 21, two ends of the push wheel shaft 20 are inserted into arc-shaped guide grooves on the driving disks, and two ends of the push wheel shaft 20 are processed with chamfers to form working conical surface rings which are in tangential contact with the output conical wheels 14 and 22 and push the output conical wheels to rotate; the part for controlling the driving push wheel not to rotate consists of a central fixed control gear 24 fixed on the shell through a sleeve, an intermediate idle gear 26 arranged on an intermediate idle gear shaft 25 and a push wheel gear 27, wherein the diameters of the tooth number reference circles of the central fixed control gear 24 and the push wheel gear 27 are the same, so that the push wheel gear 27 and the push wheel shaft 20 only rotate around the output bevel wheel in a revolution way and do not rotate; the radial displacement control part of the driving push wheel consists of sector gear pieces 32, a circumferential gear ring 30, an arc-shaped bidirectional piston hydraulic cylinder 29 with one end outputting and the like, wherein two sector gear pieces 32 are sleeved at two ends of the middle idler shaft 25 through central holes thereof and sleeved at two ends of the push wheel shaft 20 through round holes near the edge thereof, inner gear rings at two sides of the circumferential gear ring 30 are respectively meshed with the two sector gear pieces 32, the arc-shaped bidirectional piston hydraulic cylinder 29 is arranged between two driving disks 19 and 21 and is fixedly connected with the driving disks, wherein a cylindrical boss is processed at the tail part of the arc-shaped piston, the hydraulic cylinder is divided into a front hydraulic working cavity and a rear hydraulic working cavity, the output end of the piston is connected with a lug 33 inside the circumferential gear ring 30, when the hydraulic cylinder is in oil feeding work, the arc-shaped piston can drive the circumferential gear ring 30 to rotate relative to the driving disks 19 and 21, thereby driving the sector gear pieces 32 to push the push wheel shaft 20 to move along an arc-shaped guide notch on the driving disks and drive the push wheel gear 27 to rotate around the middle idler 26, the radial displacement of the driving push wheel is realized, and the hydraulic cylinder mechanism always enables the driving push wheel to keep a certain radial pressure on the output conical pulley, wherein the thickness of the push wheel gear 27 and the central fixed control gear 24 is 1/2 of the thickness of the intermediate idle gear 26, the push wheel gear and the central fixed control gear are respectively arranged on two sides of the axial center of the intermediate idle gear 26 and are meshed with the intermediate idle gear 26, the radial moving distance of the driving push wheel is increased, and the central fixed control gear 24 is prevented from colliding with the push wheel gear 27 in the highest gear; the output cone pulley and the control part for controlling the separation and approach of the left cone pulley and the right cone pulley thereof are composed of a cone pulley frame 28, left and right cone pulley hydraulic cylinders 23 and 15 fixedly connected with the cone pulley frame, left and right cone pulleys 22 and 14 integrated with a piston, wherein the cone pulley hydraulic cylinder and the output cone pulley integrated with the piston are also meshed through spline teeth 36 on the cone pulley hydraulic cylinder and combined into a piston hydraulic cylinder mechanism which can move left and right and can not rotate mutually, and the left cone pulley hydraulic cylinder 23 and the left cone pulley 22 are sleeved on a sleeve of the central fixed control gear 24, the right cone pulley hydraulic cylinder 15 and the right cone pulley 14 are sleeved on the right half part of the transmission input shaft 16, because the left and right side cone pulley hydraulic cylinders 23 and 15 are fixedly connected with the cone pulley frame 28 into a whole, therefore, when the hydraulic cylinder is in oil feeding operation, the left and right conical wheels approach, and when the push wheel shaft 20 approaches to the axes of the left and right conical wheels 22 and 14, the output conical wheels are pushed to separate left and right; the planetary gear output part consists of a first output planetary row, a second output planetary row and a control planetary row: the first output planet row consists of an internal and external gear ring 12, a planet gear 1 and a central gear 10, the control planet row consists of an internal and external gear ring 13, a planet gear 2 and a central gear 7 fixed on a shell partition plate 31, the second output planet row consists of a planet gear 3 (a planet carrier of which is fixed on the shell partition plate 31), a central gear 4 and an output gear ring 5, wherein the first output planet row and the control planet row share a planet carrier 6, the central gear 10 and the central gear 4 are fixedly connected into a whole by a hollow shaft penetrating through the central gear 7, the planet gear 2 drives and controls the planet carrier 6 to revolve around the central gear 7 fixed on the shell partition plate 31, an output gear 18 fixedly connected with an output bevel gear part drives the internal and external gear ring 12 of the first output planet row to rotate, and then the planet carrier 6 is driven by the planet gear 1 of the first output planet row to rotate and simultaneously drive the central gear 10 to reversely rotate, then the sun gear 4 and the planet gear 3 drive the output gear ring 5 to rotate in the positive direction, thereby completing power output.
The working process is as follows: the motor 35 drives the input part consisting of the input shaft 16 and the driving discs 19 and 21 to rotate → the input part drives the driving push wheel part consisting of the push wheel gear 27 and the push wheel shaft 20 to rotate around the output conical wheels 14 and 22 and push the output conical wheels 14 and 22 and the conical wheel frame 28 to rotate → the output gear 18 fixedly connected with the output conical wheel part drives the first output planet row internal and external gear ring 12 to rotate, meanwhile, the transmission input shaft gear 17 drives the control planet row internal and external gear ring 13 to rotate → the control planet row internal and external gear ring 13 is driven by the planet gear 2 and controls the planet carrier 6 to revolve around the central gear 7 fixed on the shell partition plate 31, the first output planet row internal and external gear ring 12 drives the planet gear 1 to revolve around the central gear 10 and simultaneously drives the central gear 10 to rotate in the reverse direction → the central gear 10 drives the central gear 4 to rotate synchronously → finally the central gear 4 drives the output gear ring 5 to rotate in the forward direction through the planet gear 3 to output the rotating speed. During the process, the driving discs 19 and 21 drive the intermediate idle wheel 26 to rotate around the central fixed control gear 24, so as to ensure that the central fixed control gear 24 passes through the intermediate idle wheel 26, and control the driving push wheel to not rotate, when the piston of the arc-shaped bidirectional piston hydraulic cylinder 29 with one end output extends out, the circumferential gear ring bump 33 pushes the circumferential gear ring 30 to drive the fan-shaped gear piece 32 to push the driving push wheel to approach to the input axis, and meanwhile, the push wheel shaft 20 pushes the output conical wheels 14 and 22 to separate left and right, so as to realize the conversion to a high gear, otherwise, when the conical wheel hydraulic cylinders 23 and 15 are fed with oil, the output conical wheels 14 and 22 approach to each other, and meanwhile, one end of the arc-shaped bidirectional piston hydraulic cylinder 29 is fed with oil, and one end of the driving push wheel is far away from the input axis, so as to realize the conversion to a low gear.
And under the volume of the transmission with normal reasonable size, the diameters of working conical surface rings at two ends of the push wheel shaft 20 can be 1/15 of the diameters of the output conical wheels 14 and 22, so that the transmission ratio change in a wide range of 5 to 15 is realized.
Claims (8)
1. A5-15 push force CVT mechanical stepless speed changer for an electric automobile is characterized by comprising an input part, an active push wheel part, a part for controlling the active push wheel not to rotate, a radial displacement control part of the active push wheel, an output cone pulley, a part for separating and approaching a left cone pulley and a right cone pulley of the output cone pulley, a planetary gear output part and the like 6, wherein two or more active push wheels driven by the input part connected with a motor are uniformly arranged around the output cone pulley and keep certain radial pressure on the output cone pulley all the time, working cone surface rings at two ends of the active push wheel are respectively in tangential contact with the left working cone pulley and the right working cone pulley of the output cone pulley, the active push wheel does circular motion around the output cone pulley, but the active push wheel does not rotate and can only revolve around the output cone pulley and push the output cone pulley to rotate, the active push wheel can be close to the axis of the output cone pulley to a limit position, meanwhile, the two working cone pulleys of the output cone pulley are matched with the driving push pulley to be separated to the left and right to form the highest gear position, otherwise, the driving push pulley is separated to the limit position from the edge of the output cone pulley, the two working cone pulleys of the output cone pulley are matched with the driving push pulley to be close to the left and right to form the lowest gear position, the gear can be changed at any position between the high gear position and the low gear position, namely, the output rotating speed is changed by changing the radial position of the working cone surface ring of the driving push pulley, which is tangent to the output cone pulley, the diameter of the working cone surface ring of the driving push pulley is 1/15 of the diameter of the output cone pulley under the reasonable size of the transmission, and the transmission ratio change in the range of 5-15 is realized through the output part of the planetary gear.
2. The input section of a 5-15 push-type CVT mechanical continuously variable transmission for an electric vehicle according to claim 1, characterized in that: the input shaft (16) is fixedly connected with a right driving disk (19), a left driving disk (21) is sleeved on a sleeve of a central fixed control gear (24), left and right driving disks (19) and (21) are fixedly connected through two ends of a middle idler shaft (25), and arc-shaped guide notches of driving push wheels are further processed on the left and right driving disks (19) and (21).
3. The active inference section of a 5 to 15-drive-force-type CVT mechanical continuously variable transmission for an electric vehicle according to claim 1, characterized in that: the push wheel gear (27) is sleeved on the push wheel shaft (20) and fixedly connected to form an active push wheel, the active push wheel is installed between the left driving disc (19) and the right driving disc (21), two ends of the push wheel shaft (20) are inserted into arc-shaped guide grooves of the driving discs, two ends of the push wheel shaft (20) are machined with chamfers to form working conical surface rings which are in tangential contact with the output conical wheels (14) and (22), and the output conical wheels (14) and (22) are pushed to rotate.
4. The controlled active push wheel non-rotation part of a 5-15 push-type CVT mechanical continuously variable transmission for an electric vehicle according to claim 1, characterized in that: the self-transmission of the push wheel gear (27) is controlled by a central fixed control gear (24) fixed on the shell through a sleeve through an intermediate idle wheel (26) arranged on an intermediate idle wheel shaft (25), wherein the number of teeth and the pitch circle diameter of the central fixed control gear (24) and the push wheel gear (27) are the same, and the active push wheel is ensured to revolve around the output bevel wheel only and does not rotate.
5. The active push wheel radial displacement control portion of a 5-15 push-type CVT mechanical continuously variable transmission for an electric vehicle according to claim 1, characterized in that: the hydraulic cylinder is composed of two fan-shaped gear pieces (32), a circumferential gear ring (30) and an arc-shaped bidirectional piston hydraulic cylinder (29) with one end outputting, wherein the two fan-shaped gear pieces (32) are sleeved at two ends of a middle idler shaft (25) through central holes of the fan-shaped gear pieces and sleeved at two ends of a push wheel shaft (20) through round holes near the edges of the fan-shaped gear pieces, inner gear rings at two sides of the circumferential gear ring (30) are respectively meshed with the two fan-shaped gear pieces (32), the arc-shaped bidirectional piston hydraulic cylinder (29) with one end outputting is arranged between a driving disc (19) and a driving disc (21) and fixedly connected with the driving disc, a cylindrical boss is processed at the tail part of an arc-shaped piston to divide the hydraulic cylinder into a front hydraulic working cavity and a rear hydraulic working cavity, the output end of the piston is connected with a convex block (33) inside the circumferential gear ring (30), and the arc-shaped piston can drive the circumferential gear ring (30) to rotate relative to the driving discs (19) and (21) when the hydraulic cylinder is fed with oil to work, thereby driving the fan-shaped gear piece (32) to push the push wheel shaft (20) to move along the arc-shaped guide notch on the driving disc and driving the push wheel gear (27) to rotate around the intermediate idle wheel (26), realizing the radial displacement of the driving push wheel, and enabling the driving push wheel to always keep a certain radial pressure on the output conical wheel by the hydraulic cylinder mechanism, wherein the thickness of the push wheel gear (27) and the central fixed control gear (24) is 1/2 of the thickness of the intermediate idle wheel (26), and the push wheel gear and the central fixed control gear are respectively arranged on two sides of the axial center of the intermediate idle wheel (26) to be meshed with the intermediate idle wheel (26), so as to increase the radial moving distance of the driving push wheel and prevent the central fixed control gear (24) from colliding with the push wheel gear (27) at the highest gear.
6. The output cone pulley and the left and right cone pulleys of the 5-15 push-type CVT mechanical continuously variable transmission for the electric vehicle according to claim 1 are separated from each other and approach the control portion, and the output cone pulley and the left and right cone pulleys are characterized in that: consists of a cone pulley frame (28), left and right cone pulley hydraulic cylinders (23) and (15) fixedly connected with the cone pulley frame, and left and right cone pulleys (22) and (14) integrated with a piston, wherein the cone pulley hydraulic cylinder and the output cone pulley integrated with the piston are also meshed through spline teeth (36) on the cone pulley hydraulic cylinder and combined into a piston hydraulic cylinder mechanism which can move left and right and can not rotate mutually, a left cone pulley hydraulic cylinder (23) and a left cone pulley (22) are sleeved on a sleeve of a central fixed control gear (24), a right cone pulley hydraulic cylinder (15) and a right cone pulley (14) are sleeved on the right half part of a transmission input shaft (16), because the left and right cone pulley hydraulic cylinders (23) and (15) are fixedly connected with the cone pulley frame (28) into a whole, therefore, when the hydraulic cylinder works in an oil feeding mode, the left conical wheel and the right conical wheel are close to each other, and when the push wheel shaft (20) is close to the axle centers of the left conical wheel, the right conical wheel and the left conical wheel (22) and the axle centers of the left conical wheel, the right conical wheel and the left conical wheel (14), the output conical wheels are pushed to be separated left and right.
7. The planetary gear output section of a 5 to 15 push-type CVT mechanical continuously variable transmission for an electric vehicle according to claim 1, characterized in that: the planetary gear output part consists of a first output planetary row, a second output planetary row and a control planetary row, wherein the first output planetary row consists of a gear ring (9) connected with an output cone wheel of the transmission, a planetary gear (1) and a central gear (10), the control planetary row consists of a gear ring (8) connected with an input shaft of the transmission, a planetary gear (2) and a central gear (7) fixed on the shell, the second output planetary row consists of a planetary gear (3) (the planetary carrier of which is fixed on a partition plate of the shell), a central gear (4) and an output gear ring (5), wherein the first output planetary row and the control planetary row share a planetary carrier (6), the central gear (10) and the central gear (4) of the first output planetary row and the second output planetary row are fixedly connected into a whole by a shaft penetrating through the central gear (7), and the input shaft of the transmission drives the control planetary row gear ring (8) to rotate, the planet carrier (6) is controlled to revolve around the central gear (7) fixed on the shell through the planet gear (2), the transmission output cone pulley drives the first output planet row gear ring (9) to rotate, then the planet carrier (6) is driven to rotate through the planet gear (1) and simultaneously the central gear (10) is driven to rotate in the reverse direction, and then the output gear ring (5) is driven to rotate in the forward direction through the central gear (4) and the planet gear (3), so that power output is completed.
8. A planetary gear output section as claimed in claim 7, wherein: when the transmission is mounted transversely on a vehicle and the transmission input shaft is arranged parallel to the planetary gear output, the sun gears (10) and (4) of the first and second output planetary rows are fixedly connected by a hollow shaft so that the axle shaft drives the wheel via the hollow shaft, and the first output planetary row and the ring gear of the control planetary row are provided with external gears in addition to internal gears, forming a first output planetary row internal and external toothed ring gear (12) and a control planetary row internal and external toothed ring gear (13), and are respectively driven by an output gear (18) fixed on the output bevel gear portion and a transmission input shaft gear (17) fixed on the input shaft, if the transmission input shaft and the planetary gear output portion are arranged coaxially, then the planetary gears (2) of the control planetary row are fixedly connected with the planetary gears (11) extending from the other side of the first output planetary row via the hollow shaft sleeved on the planet carrier (6), and the planetary gear (1) of the first output planetary row is sleeved at the middle position of the hollow shaft, and simultaneously, the gear ring (8) of the control planetary row moves from the right side to the left side of the first output planetary row to be meshed with the extension planetary gear (11), so that the input shaft of the transmission is conveniently connected with the gear ring (8) of the control planetary row.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202210307810.6A CN114857230A (en) | 2022-03-29 | 2022-03-29 | 5-15 drive ratio push type CVT mechanical stepless speed changer for electric automobile |
| PCT/CN2023/083920 WO2023185700A1 (en) | 2022-03-29 | 2023-03-26 | Electric vehicle thrust-type mechanical continuously variable transmission (cvt) having transmission ratio of 5-15 |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202210307810.6A CN114857230A (en) | 2022-03-29 | 2022-03-29 | 5-15 drive ratio push type CVT mechanical stepless speed changer for electric automobile |
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| Publication Number | Publication Date |
|---|---|
| CN114857230A true CN114857230A (en) | 2022-08-05 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202210307810.6A Pending CN114857230A (en) | 2022-03-29 | 2022-03-29 | 5-15 drive ratio push type CVT mechanical stepless speed changer for electric automobile |
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| Country | Link |
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| CN (1) | CN114857230A (en) |
| WO (1) | WO2023185700A1 (en) |
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| CN116404803A (en) * | 2023-06-07 | 2023-07-07 | 华侨大学 | Variable-speed variable-torque electric cylinder and engineering machinery thereof |
| WO2023185700A1 (en) * | 2022-03-29 | 2023-10-05 | 仇延鹏 | Electric vehicle thrust-type mechanical continuously variable transmission (cvt) having transmission ratio of 5-15 |
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| CN114857230A (en) * | 2022-03-29 | 2022-08-05 | 仇延鹏 | 5-15 drive ratio push type CVT mechanical stepless speed changer for electric automobile |
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| KR20100097564A (en) * | 2009-02-26 | 2010-09-03 | 유순기 | Fixed ring gear fixing device of planetary gear reducer |
| US20170102059A1 (en) * | 2013-12-31 | 2017-04-13 | Deere & Company | Multi-mode infinitely variable transmission |
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Also Published As
| Publication number | Publication date |
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| WO2023185700A1 (en) | 2023-10-05 |
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