CN113685513A - Stepless speed change mechanism and speed change method thereof - Google Patents
Stepless speed change mechanism and speed change method thereof Download PDFInfo
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- CN113685513A CN113685513A CN202111113615.1A CN202111113615A CN113685513A CN 113685513 A CN113685513 A CN 113685513A CN 202111113615 A CN202111113615 A CN 202111113615A CN 113685513 A CN113685513 A CN 113685513A
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
- F16H3/70—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
- F16H3/72—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with a secondary drive, e.g. regulating motor, in order to vary speed continuously
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
- F16H3/72—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with a secondary drive, e.g. regulating motor, in order to vary speed continuously
- F16H3/724—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with a secondary drive, e.g. regulating motor, in order to vary speed continuously using external powered electric machines
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
- F16H3/76—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with an orbital gear having teeth formed or arranged for obtaining multiple gear ratios, e.g. nearly infinitely variable
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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
- F16H35/00—Gearings or mechanisms with other special functional features
- F16H2035/005—Gearings or mechanisms preventing back-driving
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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
- F16H61/12—Detecting malfunction or potential malfunction, e.g. fail safe; Circumventing or fixing failures
- F16H2061/1244—Keeping the current state
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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
- F16H61/12—Detecting malfunction or potential malfunction, e.g. fail safe; Circumventing or fixing failures
- F16H2061/1256—Detecting malfunction or potential malfunction, e.g. fail safe; Circumventing or fixing failures characterised by the parts or units where malfunctioning was assumed or detected
- F16H2061/1288—Detecting malfunction or potential malfunction, e.g. fail safe; Circumventing or fixing failures characterised by the parts or units where malfunctioning was assumed or detected the failing part is an actuator
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/0021—Transmissions for multiple ratios specially adapted for electric vehicles
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
- F16H2200/2012—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with four sets of orbital gears
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- Engineering & Computer Science (AREA)
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- Mechanical Engineering (AREA)
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Abstract
The invention discloses a continuously variable transmission mechanism, which belongs to the technical field of continuously variable transmissions and comprises a first planet row, a second planet row, a third planet row and a fourth planet row, wherein a first gear ring on the first planet row is connected with a second sun gear on the second planet row through a first connecting shaft, a second gear ring on the second planet row is connected with a third planet carrier on the third planet row, the third planet carrier on the third planet row is connected with a fourth sun gear on the fourth planet row through a second connecting shaft, an output component is connected on the fourth planet carrier on the fourth planet row, and one side of a connector with the same rotating speed is provided with a one-way stopper. The invention also discloses a speed change method of the stepless speed change mechanism. The stepless speed change mechanism of the invention realizes stepless speed change of the output end, and has the advantages of high transmission efficiency, large output torque, no power interruption, simple and reliable structure, low manufacturing cost, easy maintenance, simple and convenient speed regulation and the like.
Description
Technical Field
The invention relates to the technical field of continuously variable transmissions, in particular to a continuously variable transmission mechanism and a speed change method thereof.
Background
With the higher and higher requirements of the society on environmental protection, the electric vehicle technology becomes the mainstream research direction of each large vehicle enterprise. At present, the electric vehicle mostly adopts a speed reducer with a fixed speed ratio, although the speed reducer with a large speed ratio can be selected to meet the power requirement when the vehicle starts and climbs, the large speed ratio limits the vehicle to be incapable of reaching a high maximum speed, and the reason that the maximum speed of the electric vehicle is generally lower than the maximum speed of a fuel vehicle on the market is also provided. In order to take account of the highest speed and the climbing capability of a vehicle, a plurality of vehicle enterprises begin to install AMT transmissions on electric vehicles, but the AMT transmissions belong to step-by-step speed change in principle, and have the problems of gear shifting, gear shifting and power interruption in the prior art; the transmission ratio range of the AMT is limited by gear setting and is applied to heavy vehicles, in order to expand the transmission ratio range, a large number of gears need to be set, the gear shifting process is slow, the operation is complex, and a lot of drivers of large vehicles are reluctant to step on the brake; the AMT gear shifting process depends on a complex control strategy, so that the accurate gear shifting time is difficult to master, and the problems of high energy consumption and low efficiency exist; the AMT transmission has the disadvantages of complex structure, high manufacturing cost and difficult maintenance.
Disclosure of Invention
The invention aims to solve the problems and designs a stepless speed change mechanism and a speed change method thereof.
The technical solution of the present invention to achieve the above object is a continuously variable transmission mechanism including a first planetary row, a second planetary row, a third planetary row and a fourth planetary row, wherein a first ring gear on the first planetary row is connected to a second sun gear on the second planetary row via a first connecting shaft, a second ring gear on the second planetary row is connected to a third carrier on the third planetary row, a third carrier on the third planetary row is connected to a fourth sun gear on the fourth planetary row via a second connecting shaft, an output member is connected to a fourth carrier on the fourth planetary row, a first carrier on the first planetary row, a second carrier on the second planetary row, a third ring gear on the third planetary row and a fourth ring gear on the fourth planetary row are all connected to a common rotation speed connector, and a one-way stopper is provided on the common rotation speed connector, the first sun gear on the first planet row is connected with the first driving piece through a first input shaft, and the third sun gear on the third planet row penetrates through the third planet carrier, the second connecting shaft, the fourth sun gear, the fourth planet carrier and the output part through a second input shaft and is connected with the second driving piece.
As a further explanation of the present invention, the third planet carrier, the second connecting shaft, the fourth sun gear, the fourth planet carrier, and the output member are all hollow penetrating structures.
As a further explanation of the present invention, the one-way stopper serves to limit the rotational directions of the first carrier, the second carrier, the third ring gear, and the fourth ring gear.
The invention also provides a speed change method based on the stepless speed change mechanism, wherein a first driving piece and a first sun gear are connected through a first input shaft, so that the rotating speed of the first driving piece is the same as that of the first sun gear; the second driving piece and the third sun gear are connected through a second input shaft, so that the rotating speed of the second driving piece is the same as that of the third sun gear; the first planet carrier, the second planet carrier, the third gear ring and the fourth gear ring are all connected to a connector with the same rotating speed, so that the rotating speeds of the first planet carrier, the second planet carrier, the third gear ring and the fourth gear ring are the same; the first gear ring and the second sun gear are connected through a first connecting shaft, so that the rotating speed of the first gear ring is the same as that of the second sun gear; the second gear ring is connected with a third planet carrier, and the third planet carrier is connected with a fourth sun gear through a second connecting shaft, so that the rotating speed of the second gear ring, the rotating speed of the third planet carrier and the rotating speed of the fourth sun gear are the same; the fourth planet carrier is connected with the output component, so that the rotating speed of the fourth planet carrier is the same as that of the output component.
As a further explanation of the invention, it is assumed that: the rotating speed of the first driving part and the rotating speed of the first sun gear are N1The rotating speed of the second driving piece and the rotating speed of the third sun wheel are N2Said first planet carrierThe rotating speeds of the second planet carrier, the third gear ring and the fourth gear ring are N3The rotation speed of the first gear ring and the rotation speed of the second sun gear are N4The rotation speed of the second gear ring, the third planet carrier and the fourth sun gear is N5The fourth planet carrier and the output member rotate at a speed N6(ii) a When said N is1、N2、N3、N4、N5、N6When any two values are determined, the other four values can be calculated through the proportional relation of line segments in the vector diagram, and the rotating speed N of the first driving piece is adjusted and controlled1And the rotational speed N of the second drive member2The rotational speed N of the output member can be realized6In which the rotational speed N of the first carrier, the second carrier, the third ring gear and the fourth ring gear is caused to vary continuously, wherein3When the rotation speed is 0, the rotation speed N of the first driving part is set1And the rotational speed N of the second drive member2The ratio of (A) to (B) is P; controlling the rotation speed N of the first driving part by adjusting1And the rotational speed N of the second drive member2The output states of the output means are made to include a state a, a state B, a state C, a state D, and a state E.
As a further explanation of the present invention, in the state a, the rotation speeds N of the first carrier, the second carrier, the third ring gear, and the fourth ring gear3Is 0, the rotating speed N of the first driving part1And the rotational speed N of the second drive member2Is P, the steering is positive, so that the rotating speed N of the output part6The steering of (1) is in the forward direction, and the transmission ratio is in the maximum state.
As a further explanation of the present invention, in the state B, the rotation speeds N of the first carrier, the second carrier, the third ring gear, and the fourth ring gear3The rotation speed N of the first driving part is not 0 and the steering direction is the positive direction1And the rotational speed N of the second drive member2Is less than P, the rotation directions are positive directions, so that the rotating speed N of the output part is6The direction of rotation of (c) is the forward direction.
As a further explanation of the present invention, in the state C, the rotation speeds N of the first carrier, the second carrier, the third ring gear, and the fourth ring gear3The rotation speed N of the first driving part is not 0 and the reverse direction is adopted1And the rotational speed N of the second drive member2Is greater than P, the rotation direction is positive, and the rotation speed N of the output part is the same6In order to avoid a rotational speed N of said output member6Is arranged on the same rotational speed connecting body connected with the first planet carrier, the second planet carrier, the third gear ring and the fourth gear ring, and a one-way stopper is arranged on the same rotational speed connecting body connected with the first planet carrier, the second planet carrier, the third gear ring and the fourth gear ring and used for limiting the rotational speed N of the first planet carrier, the second planet carrier, the third gear ring and the fourth gear ring3Can only be in a forward direction but not in a reverse direction, so that the rotating speed N of the output part is enabled6The direction of turning of (1) is always positive.
As a further elaboration of the invention, in state D the rotational speed N of the first drive element1And the rotational speed N of the second drive member2Is 1, the rotation direction is positive, so that the rotating speed N of the output part is6And the rotating speed N of the first driving part1And the rotational speed N of the second drive member2Is equal in size, the steering is positive, and the transmission ratio is 1.
As a further elaboration of the invention, in state E the rotational speed N of the first drive element is1And the rotational speed N of the second drive member2Is less than 1, the rotation directions are positive directions, so that the rotating speed N of the output part is6Is greater than the rotating speed N of the first driving part1And the rotational speed N of the second drive member2The direction of rotation is the forward direction.
As a further explanation of the invention, the rotational speed of the second drive member is N when the first drive member fails2And the rotation speed N of the first planet carrier, the second planet carrier, the third gear ring and the fourth gear ring is positive3There is a tendency of reverse rotation, in which the one-way stopper restricts the reverse rotation to make the first oneRotational speed N of a planet carrier, the second planet carrier, the third gear ring and the fourth gear ring3Is 0, the rotational speed N of the output member6And the power of the second driving piece is output through the third planetary row and the fourth planetary row in a speed reduction and torque increase mode in the forward direction.
As a further explanation of the invention, the rotational speed of the first drive member is N when the second drive member fails1And the rotation speed N of the first planet carrier, the second planet carrier, the third gear ring and the fourth gear ring is positive3There is a tendency of reverse rotation, in which a one-way stopper limits the reverse rotation to a rotation speed N of the first carrier, the second carrier, the third ring gear and the fourth ring gear3Is 0, the rotational speed N of the output member6The power of the first driving piece is output through the first planet row, the second planet row and the fourth planet row in a speed reduction and torque increase mode in a forward direction.
The stepless speed change mechanism and the speed change method thereof provided by the invention change the transmission ratio between the input end and the output end by adjusting the rotating speed of the first driving piece and the second driving piece and matching the first planet row, the second planet row, the third planet row, the fourth planet row and the one-way retainer, and realize the stepless speed change of the output end. In addition, the connecting ends of the first driving piece and the second driving piece of the stepless speed change mechanism are respectively arranged at the two ends of the stepless speed change mechanism, so that the input mode of the two input ends is split-end input, the probability that the two input ends can influence each other during operation is reduced, and the integral failure rate is further reduced.
Drawings
FIG. 1 is a schematic view of a continuously variable transmission provided in accordance with an embodiment of the present invention;
FIG. 2 is a tachometric vector diagram for a first, second, third, and fourth planetary gear set in accordance with an embodiment of the present invention;
FIG. 3 is a speed vector diagram for combining a first planetary row, a second planetary row, a third planetary row and a fourth planetary row according to an embodiment of the present invention;
FIG. 4 shows the rotational speed N of the first driving member according to an embodiment of the present invention1And the rotational speed N of the second drive member2When the ratio of (A) to (B) is less than P, a rotating speed vector diagram;
FIG. 5 shows the rotational speed N of the first driving member according to an embodiment of the present invention1And the rotational speed N of the second drive member2When the ratio of the rotation speed to the rotation speed is larger than P, the rotation speed vector diagram is obtained;
FIG. 6 shows the rotational speed N of the first driving member according to an embodiment of the present invention1And the rotational speed N of the second drive member2A rotation speed vector diagram when the ratio of (1) is equal to 1;
FIG. 7 shows the rotational speed N of the first driving member according to an embodiment of the present invention1And the rotational speed N of the second drive member2The ratio of (a) to (b) is less than 1, and the rotation directions are all positive rotation speed vector diagrams;
FIG. 8 shows the rotational speed N of the first driving member according to an embodiment of the present invention1The rotational speed N of the second drive member is adjusted without change2A large-hour rotating speed vector diagram;
FIG. 9 shows the rotational speed N of the second driving member according to an embodiment of the present invention2The rotating speed N of the first driving part is adjusted without changing1A large-hour rotating speed vector diagram;
FIG. 10 shows the rotational speed N of the second drive member when the first drive member fails according to an embodiment of the present invention2A rotating speed vector diagram when the steering direction is the forward direction;
FIG. 11 shows the rotational speed N of the first drive member when the second drive member fails according to an embodiment of the present invention1A rotating speed vector diagram when the steering direction is the forward direction;
FIG. 12 shows the rotational speed N of the first driving member according to an embodiment of the present invention1And the rotational speed N of the second drive member2Is equal to P and the steering is reversed.
Reference numerals:
1-first planet row, 101-first sun gear, 102-first planet carrier, 103-first ring gear, 2-second planet row, 201-second sun gear, 202-second planet carrier, 203-second ring gear, 3-third planet row, 301-third sun gear, 302-third planet carrier, 303-third ring gear, 4-fourth planet row, 401-fourth sun gear, 402-fourth planet carrier, 403-fourth ring gear, 5-first input shaft, 6-second input shaft, 7-first connecting shaft, 8-second connecting shaft, 9-output member, 10-one-way stopper.
Detailed Description
Firstly, the purpose of the embodiment of the invention is explained, and the problem that the AMT has gear shifting pause and power interruption in the nature is solved; the transmission ratio range of the AMT is limited by gear setting and is applied to heavy vehicles, in order to expand the transmission ratio range, a large number of gears need to be set, the gear shifting process is slow, the operation is complex, and a large number of reasons that drivers of large vehicles do not want to step on the brake are caused; the AMT gear shifting process depends on a complex control strategy, so that the accurate gear shifting time is difficult to master, and the problems of high energy consumption and low efficiency exist; the AMT transmission has the existing problems of complex structure, high manufacturing cost, difficult maintenance and the like, so a stepless speed change mechanism is provided to solve the existing problems.
The following describes embodiments of the present invention with reference to the accompanying drawings, and first introduces specific structures of the embodiments of the present invention.
Referring to fig. 1, a continuously variable transmission mechanism according to an embodiment of the present invention includes a first planetary row 1, a second planetary row 2, a third planetary row 3, and a fourth planetary row 4, a first ring gear 103 of the first planetary row 1 is connected to a second sun gear 201 of the second planetary row 2 through a first connecting shaft 7, a second ring gear 203 of the second planetary row 2 is connected to a third carrier 302 of the third planetary row 3, the third carrier 302 of the third planetary row 3 is connected to a fourth sun gear 401 of the fourth planetary row 4 through a second connecting shaft 8, an output member 9 is connected to a fourth carrier 402 of the fourth planetary row 4, a first carrier 102 of the first planetary row 1, a second carrier 202 of the second planetary row 2, a third ring gear 303 of the third planetary row 3, and a fourth ring gear 403 of the fourth planetary row 4 are connected to a same rotational speed connector, a one-way stopper 10 is provided on the same rotational speed connector, the first sun gear 101 of the first planetary row 1 is connected to the first drive via a first input shaft 5, and the third sun gear 301 of the third planetary row 3 is connected to the second drive via a second input shaft 6 via a third planetary carrier 302, a second connecting shaft 8, a fourth sun gear 401, a fourth planetary carrier 402 and an output element 9.
Referring to fig. 1, the first planetary row 1 includes a first sun gear 101, a first planet gear, and a first ring gear 103, the second planetary row 2 includes a second sun gear 201, a second planet carrier 202, and a second ring gear 203, the third planetary row 3 includes a third sun gear 301, a third planet carrier 302, and a third ring gear 303, and the fourth planetary row 4 includes a fourth sun gear 401, a fourth planet carrier 402, and a fourth ring gear 403. In practical application, the third planet carrier 302, the second connecting shaft 8, the fourth sun gear 401, the fourth planet carrier 402 and the output component 9 are all designed to be hollow through structures. The one-way stopper 10 serves to limit the rotational directions of the first carrier 102, the second carrier 202, the third ring gear 303, and the fourth ring gear 403.
Next, a shift speed method based on a continuously variable transmission mechanism will be described with reference to specific configurations of embodiments of the present invention.
According to the basic principle of the planetary gear, if the rotating speeds of any two of the three members of the sun gear, the ring gear and the planet carrier are determined, the rotating speed of the other member is also determined, and the rotating speed relations of the members are in corresponding proportion according to the number of teeth of the sun gear and the number of teeth of the ring gear.
According to the basic principle of the planetary gear, the rotation speed of any two of the three members of the sun gear, the ring gear and the planet carrier is the same, and the rotation speed of the other member is also the same.
Therefore, the rotational speed of the first driving member is the same as the rotational speed of the first sun gear 101, and is set to N1(ii) a The rotational speed of the second driver is the same as the rotational speed of the third sun gear 301, and is set to N2(ii) a The rotation speeds of the first carrier 102, the second carrier 202, the third ring gear 303, and the fourth ring gear 403 are the same, and are set to N3(ii) a The first ring gear 103 and the second sun gear 201 have the same rotational speed, and are set to N4(ii) a The rotation speeds of the second ring gear 203, the third carrier 302, and the fourth sun gear 401 are the same, and are set to N5(ii) a Fourth planet carrier 402 and outputThe rotation speed of the member 9 is the same and is set to N6。
A rotation speed vector diagram of the first planetary row 1, the second planetary row 2, the third planetary row 3 and the fourth planetary row 4 is obtained according to a rotation speed vector calculation method of the planetary gear, as shown in fig. 2. The length of the line segment in fig. 2 represents the magnitude of the rotation speed, the arrow direction represents the rotation speed direction, and the arrow direction is defined as a forward direction turning direction upward and a reverse direction turning direction downward.
The rotating speed vector diagrams of the first planetary row 1, the second planetary row 2, the third planetary row 3 and the fourth planetary row 4 are combined to obtain a rotating speed vector diagram as shown in fig. 3.
See FIG. 3, when N is1、N2、N3、N4、N5And N6When any two values are determined, the other four values can be calculated through the proportional relation of line segments in the vector diagram. I.e. the rotational speed N of the first drive member1Determining the rotational speed N of the second drive element2Determining the rotational speed N of the output member 96And is also uniquely determined. Controlling the speed N of the first drive member by regulation1And the rotational speed N of the second drive member2The rotational speed N of the output member 9 can be realized6Continuously stepless variation of (a).
Next, the shifting principle of the continuously variable transmission mechanism according to the embodiment of the present invention will be described with reference to specific operating conditions.
1. Starting condition
Referring to fig. 3, when starting, the first driving piece and the second driving piece are started to accelerate, and the rotating speed N of the first driving piece is controlled in the aspect of steering1And the rotational speed N of the second drive member2Both in forward direction, controlling the speed N of the first drive member in terms of speed1And the rotational speed N of the second drive member2Is equal to P. The rotational speed N of the output member 96Gradually accelerates and turns to the positive direction. Under the working condition, the power of the first driving piece and the power of the second driving piece are coupled together, and the vehicle is decelerated and torque-increased to output, so that the vehicle can accelerate to move forwards.
2. Acceleration and deceleration conditions
Referring to FIG. 4, the speed N of the first drive member is controlled in terms of steering during acceleration and deceleration1And a firstRotational speed N of the two drive elements2Both in forward direction, controlling the speed N of the first drive member in terms of speed1And the rotational speed N of the second drive member2Is less than P. By controlling the speed N of the first drive member1And the rotational speed N of the second drive member2By the magnitude and the speed of increase and decrease, the number of rotations N of the output member 9 can be realized6The steering direction is the forward direction, so that the vehicle can accelerate or decelerate to run forwards.
Alternatively, as shown in FIG. 8, the method of acceleration and deceleration may be adjusted by maintaining the speed N of the first drive member1Without change, by adjusting the speed N of the second drive member2To adjust the rotational speed N of the output member 96The size of (d); as shown in FIG. 9, the rotational speed N of the second driving member may be maintained2Without change, by adjusting the speed N of the first drive member1To adjust the rotational speed N of the output member 96The size of (2). Therefore, the rotating speed N of the output part 9 is realized6In the process of acceleration or deceleration, the first driving part and the second driving part can be different according to respective efficient working areas, and the control system controls the acceleration, deceleration and rotation speed maintenance of the first driving part and the second driving part according to the current working condition. Therefore, the first driving part and the second driving part can work in respective high-efficiency working areas for a long time, and the energy-saving effect is achieved.
3. Maximum vehicle speed condition
Referring to fig. 6, the rotational speed N of the first driver is controlled1And the rotational speed N of the second drive member2Is equal in magnitude, is in the forward direction, and reaches the maximum rotation speed, the rotation speed N of the output member 96And the rotating speed N of the first driving member1And the rotational speed N of the second drive member2And equally, the vehicle may be set to reach the maximum vehicle speed in this state.
Referring to fig. 7, if the vehicle is required to reach a higher vehicle speed in the state where the above-described maximum vehicle speed is reached, the rotational speed N of the first drive member may be reduced1Maintaining the rotation speed of the second driving member at the highest rotation speed to make the rotation speed N of the output member 9 constant6The rise was continued. The maximum speed of the vehicle is determined by the speed of rotation of the output member 9N6Is determined by the magnitude of (1), the rotational speed N of the output member 96Can be determined by the rotational speed N of the first drive element1And the rotational speed N of the second drive member2To make the setting. Therefore, only the first driving part with lower rotating speed is selected, the very high output rotating speed can be realized, and the power requirement on the driving part is further reduced.
Aiming at the starting working condition and the acceleration and deceleration working condition, a dangerous working condition needs to be considered to avoid.
Example (c): referring to fig. 5, the speed N of the first drive member occurs when the speed control of the first and second drive members is inaccurate or fails1And the rotational speed N of the second drive member2Is greater than P, and the rotating speed N of the first driving member1And the rotational speed N of the second drive member2Is all in the forward direction, the rotational speed N of the output member 9 is set6In order to prevent the occurrence of a serious accident in which the vehicle suddenly runs in reverse, which may occur when the vehicle suddenly runs in reverse, by providing the one-way stopper 10 on the same-speed connection body to which the first carrier 102, the second carrier 202, the third ring gear 303 and the fourth ring gear 403 are connected, the rotation speed N of the first carrier 102, the second carrier 202, the third ring gear 303 and the fourth ring gear 403 is limited3The direction of rotation of (1) can only be a forward direction, but cannot be a reverse direction. This ensures the rotational speed N of the output member 96The direction of turning of (1) is always positive. Therefore, when the dangerous condition occurs, the rotational speed N of the first carrier 102, the second carrier 202, the third ring gear 303 and the fourth ring gear 403 is limited due to the one-way stopper 103The steering can only be in a forward direction and can not be in a reverse direction, at the moment, the two driving pieces can be mutually dragged, and the rotating speed N of the first driving piece1And the rotational speed N of the second drive member2Is always equal to P, the rotational speed N of the first planet carrier 102, the second planet carrier 202, the third ring gear 303 and the fourth ring gear 4033Equal to 0, rotational speed N of the output member 96The steering of (2) can only be in the forward direction, so that the vehicle does not suddenly run in reverse.
4. Working condition of backing car
Referring to fig. 12, when the vehicle is reversed, the first driving member and the second driving member are started to accelerate, and the rotating speed N of the first driving member is controlled in terms of steering1And the rotational speed N of the second drive member2Both in opposite directions, the speed N of the first drive member being controlled in relation to the speed1And the rotational speed N of the second drive member2Is equal to P. The rotational speed N of the output member 96Gradually accelerates and turns to the reverse direction. Under the working condition, the power of the first driving piece and the power of the second driving piece are coupled together, and the vehicle is decelerated and torque-increased to output, so that the vehicle can accelerate and retreat to run.
Except for the normal working condition and the dangerous working condition, some emergency working conditions need to be dealt with, and the embodiment of the invention takes the emergency working conditions into consideration and solves the problem.
Example (c): referring to FIG. 10, when the first driver fails, the second driver has a speed N2The rotational speed N of the first carrier 102, the second carrier 202, the third ring gear 303, and the fourth ring gear 403 in the forward direction3There is a tendency of reverse rotation in which the one-way stopper 10 restricts reverse rotation thereof so that the rotation speed N of the first carrier 102, the second carrier 202, the third ring gear 303, and the fourth ring gear 403 is made to be the rotation speed N30, rotational speed N of the output member 96The power of the second driving element is output through the third planetary row 3 and the fourth planetary row 4 in a speed reduction and torque increase mode in the forward direction, and the vehicle can continue to accelerate or decelerate to run forwards.
Referring to FIG. 11, when the second driver fails, the first driver has a speed of N1The rotational speed N of the first carrier 102, the second carrier 202, the third ring gear 303, and the fourth ring gear 403 in the forward direction3There is a tendency of reverse rotation in which the one-way stopper 10 restricts the reverse rotation thereof so that the rotation speed N of the first carrier 102, the second carrier 202, the third ring gear 303, and the fourth ring gear 403 is made to be the rotation speed N30, rotational speed N of the output member 96The power of the first driving element is output through the first planet row 1, the second planet row 2 and the fourth planet row 4 in a speed reduction and torque increase mode in the forward direction, so that the vehicle can continue to accelerate or decelerate and run forwards.
Therefore, when one driving part fails, the other driving part can still drive the vehicle to run, and although the dynamic property is reduced, the vehicle can run to a maintenance place or a safety place by means of the one driving part, so that the reliability of the vehicle can be greatly improved.
The stepless speed change mechanism and the speed change method thereof provided by the embodiment of the invention have the following advantages:
1. the stepless speed change mechanism provided by the embodiment of the invention has no power interruption in the speed regulation process, runs quietly and stably, has better vehicle using experience when a user uses a vehicle, can greatly meet the requirements of customers in sense, and lays a good foundation for popularization and use of the product.
2. The stepless speed change mechanism provided by the embodiment of the invention can realize that the output end has large torque from low speed to high speed, the vehicle has the capability of quickly accelerating to start when driving by outputting the large torque, the large torque can climb a larger slope when the vehicle climbs, and the large torque can also meet the vehicle using requirements of more people, so that the audience area of the product is larger.
3. The stepless speed change mechanism of the embodiment of the invention can realize stepless continuous change of the output rotating speed, the driving piece of the input end can work in a high-efficiency interval for a long time, the working efficiency is improved, the effect of saving more energy can be achieved in the aspect of energy use, and more contribution can be made in the aspect of energy saving.
4. The stepless speed change mechanism provided by the embodiment of the invention has the advantages that the speed regulation is simple and convenient, and the stepless continuous change of the output rotating speed can be realized only by controlling the rotating speeds of the first driving piece and the second driving piece, so that the requirement of a vehicle on a control system is reduced, the popularization and application range of the product is wider, and the popularization and popularity of the product are ensured to a certain extent.
5. According to the embodiment of the invention, the power of the first driving part and the power of the second driving part are coupled together to drive the vehicle to run, when one driving part fails, the other driving part can still continue to drive the vehicle to run, so that when a vehicle owner uses the vehicle, even if one driving part fails, the vehicle owner can drive the vehicle by the other driving part and drive the vehicle to a maintenance place in time, the occurrence of a trailer calling event is avoided, and the vehicle using experience of the vehicle owner is better taken care of.
6. Compared with the traditional driving mode of a single driving part, the product provided by the embodiment of the invention not only can be driven by adopting the double driving parts, but also can be matched with the driving part with smaller volume and lower rotating speed, the driving part with small volume is more beneficial to the arrangement design of the driving part in the vehicle body, the aesthetic design of the appearance of the vehicle body at the later stage is more convenient, and the cost can be saved by using the smaller driving part.
7. The stepless speed change mechanism has high-efficiency transmission rate, the motor with lower power and lower rotating speed can be selected as the driving piece under the same working condition, and compared with a high-power battery, the low-power battery can better prevent the battery from overheating, and the use safety of the battery is indirectly improved through the embodiment of the invention.
8. The stepless speed change mechanism of the embodiment of the invention adopts four-planet-row transmission, increases the transmission ratio, further increases the torque, can be applied to heavy trucks such as trucks, muck trucks, buses and the like with larger loads, and further widens the application range of the embodiment of the invention.
9. The connecting ends of the first driving piece and the second driving piece of the stepless speed change mechanism are respectively arranged at the two ends of the stepless speed change mechanism, so that the input mode of the two input ends is split-end input, the probability that the two input ends can influence each other during operation is reduced, and the integral failure rate is further reduced.
The technical solutions described above only represent the preferred technical solutions of the present invention, and some possible modifications to some parts of the technical solutions by those skilled in the art all represent the principles of the present invention, and fall within the protection scope of the present invention.
Claims (12)
1. A continuously variable transmission mechanism is characterized by comprising a first planet row (1), a second planet row (2), a third planet row (3) and a fourth planet row (4), wherein a first gear ring (103) on the first planet row (1) is connected with a second sun gear (201) on the second planet row (2) through a first connecting shaft (7), a second gear ring (203) on the second planet row (2) is connected with a third planet carrier (302) on the third planet row (3), the third planet carrier (302) on the third planet row (3) is connected with a fourth sun gear (401) on the fourth planet row (4) through a second connecting shaft (8), an output component (9) is connected with a fourth planet carrier (402) on the fourth planet row (4), and the first planet carrier (102) on the first planet row (1) is connected with a first sun gear (201) on the second planet row (2), The second planet carrier (202) on the second planet row (2), the third gear ring (303) on the third planet row (3) and the fourth gear ring (403) on the fourth planet row (4) are all connected to a same rotating speed connector, a one-way stopper (10) is arranged on the same rotating speed connector, the first sun gear (101) on the first planet row (1) is connected with the first driving piece through a first input shaft (5), and the third sun gear (301) on the third planet row (3) penetrates through the third planet carrier (302), the second connecting shaft (8), the fourth sun gear (401), the fourth planet carrier (402) and the output part (9) through a second input shaft (6).
2. Continuously variable transmission according to claim 1, characterized in that the third planet carrier (302), the second connecting shaft (8), the fourth sun gear (401), the fourth planet carrier (402) and the output member (9) are all hollow through structures.
3. The continuously variable transmission mechanism according to claim 2, wherein the one-way stopper (10) is for limiting the rotational directions of the first carrier (102), the second carrier (202), the third ring gear (303), and the fourth ring gear (403).
4. A method of shifting gears based on a continuously variable transmission, characterized in that a first driver and a first sun gear (101) are connected by a first input shaft (5) such that the rotational speed of the first driver and the rotational speed of the first sun gear (101) are the same; the second driving piece is connected with the third sun gear (301) through a second input shaft (6), so that the rotating speed of the second driving piece is the same as that of the third sun gear (301); a first planet carrier (102), a second planet carrier (202), a third gear ring (303) and a fourth gear ring (403) are all connected to a same-rotating-speed connecting body, so that the rotating speeds of the first planet carrier (102), the second planet carrier (202), the third gear ring (303) and the fourth gear ring (403) are the same; the first gear ring (103) and the second sun gear (201) are connected through a first connecting shaft (7), so that the rotating speed of the first gear ring (103) is the same as that of the second sun gear (201); the second gear ring (203) is connected with a third planet carrier (302), the third planet carrier (302) is connected with a fourth sun gear (401) through a second connecting shaft (8), and the rotating speed of the second gear ring (203), the rotating speed of the third planet carrier (302) and the rotating speed of the fourth sun gear (401) are the same; the fourth planet carrier (402) is connected with the output component (9) so that the rotating speed of the fourth planet carrier (402) is the same as the rotating speed of the output component (9).
5. The continuously variable transmission mechanism-based speed change method according to claim 4, wherein: the rotational speed of the first driving member and the rotational speed of the first sun gear (101) are N1The rotation speed of the second driving piece and the rotation speed of the third sun wheel (301) are N2The rotation speeds of the first planet carrier (102), the second planet carrier (202), the third gear ring (303) and the fourth gear ring (403) are N3The rotation speed of the first ring gear (103) and the rotation speed of the second sun gear (201) are N4The rotational speeds of the second ring gear (203), the third planet carrier (302) and the fourth sun gear (401) are N5The fourth planet carrier (402) and the output member (9) have a rotational speed N6(ii) a When said N is1、N2、N3、N4、N5、N6When any two values are determined, the other four values can be calculated through the proportional relation of line segments in the vector diagram, and the rotating speed N of the first driving piece is adjusted and controlled1And the rotational speed N of the second drive member2The rotational speed N of the output member (9) can be realized6Wherein the first planet carrier (102), the second planet carrier (202), the first planet carrier (202) are continuously and steplessly changedRotational speed N of the third ring gear (303) and the fourth ring gear (403)3When the rotation speed is 0, the rotation speed N of the first driving part is set1And the rotational speed N of the second drive member2The ratio of (A) to (B) is P; controlling the rotation speed N of the first driving part by adjusting1And the rotational speed N of the second drive member2The output state of the output member (9) is made to include a state A, a state B, a state C, a state D and a state E.
6. The continuously variable transmission mechanism-based shifting method according to claim 5, wherein in the state A, the rotation speeds N of the first carrier (102), the second carrier (202), the third ring gear (303), and the fourth ring gear (403) are3Is 0, the rotating speed N of the first driving part1And the rotational speed N of the second drive member2Is P, the rotation direction is positive, so that the rotation speed N of the output part (9)6The steering of (1) is in the forward direction, and the transmission ratio is in the maximum state.
7. The continuously variable transmission mechanism-based shifting method according to claim 5, wherein in the state B, the rotation speeds N of the first carrier (102), the second carrier (202), the third ring gear (303), and the fourth ring gear (403) are3The rotation speed N of the first driving part is not 0 and the steering direction is the positive direction1And the rotational speed N of the second drive member2Is less than P, the rotation directions are positive directions, so that the rotating speed N of the output part (9)6The direction of rotation of (c) is the forward direction.
8. The continuously variable transmission mechanism-based shifting method according to claim 5, wherein in the state C, the rotation speeds N of the first carrier (102), the second carrier (202), the third ring gear (303), and the fourth ring gear (403) are3The rotation speed N of the first driving part is not 0 and the reverse direction is adopted1And the rotational speed N of the second drive member2Is greater than P, the rotation direction is positive, and the rotation speed N of the output part (9) is at the moment6The direction of rotation of (a) is reversed,in order to avoid the rotational speed N of the output part (9)6Is arranged on a same-rotation-speed connecting body connected with the first carrier (102), the second carrier (202), the third ring gear (303) and the fourth ring gear (403), a one-way stopper (10) is arranged on the same-rotation-speed connecting body, and the one-way stopper (10) limits the rotation speed N of the first carrier (102), the second carrier (202), the third ring gear (303) and the fourth ring gear (403)3Can only be in a forward direction but not in a reverse direction, so that the rotational speed N of the output member (9)6The direction of turning of (1) is always positive.
9. The continuously variable transmission mechanism-based shifting method according to claim 5, wherein in the state D, the rotational speed N of the first driver1And the rotational speed N of the second drive member2Is 1, the rotation directions are positive directions, so that the rotating speed N of the output part (9)6And the rotating speed N of the first driving part1And the rotational speed N of the second drive member2Is equal in size, the steering is positive, and the transmission ratio is 1.
10. The continuously variable transmission mechanism-based shifting method according to claim 5, wherein in the state E, the rotational speed N of the first driver1And the rotational speed N of the second drive member2Is less than 1, the rotation directions are positive directions, so that the rotating speed N of the output part (9)6Is greater than the rotating speed N of the first driving part1And the rotational speed N of the second drive member2The direction of rotation is the forward direction.
11. The continuously variable transmission mechanism-based shifting method according to claim 5, wherein when the first driver fails, the second driver rotates at a speed N2The rotational speed N of the first carrier (102), the second carrier (202), the third ring gear (303), and the fourth ring gear (403) in the forward direction3The reverse rotation tendency exists when the one-way stopper (10) limits the reverse rotation, so that the first planet carrier (102),The rotational speed N of the second planet carrier (202), the third ring gear (303) and the fourth ring gear (403)3Is 0, the rotational speed N of the output member (9)6The power of the second driving piece is output in a speed reduction and torque increase mode through the third planetary row (3) and the fourth planetary row (4).
12. The continuously variable transmission mechanism-based shifting method of claim 5, wherein when the second driver fails, the rotational speed of the first driver is N1The rotational speed N of the first carrier (102), the second carrier (202), the third ring gear (303), and the fourth ring gear (403) in the forward direction3The reverse rotation of the planetary gear tends to be limited by a one-way stopper (10) at the time, so that the rotating speed N of the first planet carrier (102), the second planet carrier (202), the third ring gear (303) and the fourth ring gear (403) is enabled3Is 0, the rotational speed N of the output member (9)6The power of the first driving piece is output in a speed reduction and torque increase mode through the first planet row (1), the second planet row (2) and the fourth planet row (4).
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| CN202111113615.1A CN113685513A (en) | 2021-09-23 | 2021-09-23 | Stepless speed change mechanism and speed change method thereof |
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