CN113685514B - Three-planetary-row stepless speed change mechanism with single-side input and output and speed change method thereof - Google Patents
Three-planetary-row stepless speed change mechanism with single-side input and output and speed change method thereof Download PDFInfo
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- CN113685514B CN113685514B CN202110998305.6A CN202110998305A CN113685514B CN 113685514 B CN113685514 B CN 113685514B CN 202110998305 A CN202110998305 A CN 202110998305A CN 113685514 B CN113685514 B CN 113685514B
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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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Abstract
The invention discloses a unilateral input and output three-planetary-row stepless speed change mechanism and a speed change method thereof, belonging to the technical field of stepless speed change, and comprising a first planetary row, a second planetary row and a third planetary row, wherein a first gear ring on the first planetary row is connected with a second planetary carrier on the second planetary row, the second planetary carrier on the second planetary row is connected with a third sun gear on the third planetary row through a connecting shaft, the first planetary carrier on the first planetary row is connected with a second gear ring on the second planetary row and a third gear ring on the third planetary row, and a unidirectional stopper is arranged on a connecting body of the first planetary carrier, the second gear ring and the third gear ring. The three-planetary-row stepless speed change mechanism with single-side input and output is characterized in that the connecting ends of the first driving piece, the second driving piece and the output part are arranged at one end of the stepless speed change mechanism, so that the input and output of power are at one end of the stepless speed change mechanism, and the arrangement and space utilization rate of the whole power equipment are more reasonable.
Description
Technical Field
The invention relates to the technical field of continuously variable transmissions, in particular to a three-planetary-row continuously variable transmission mechanism with single-side input and output and a speed change method thereof.
Background
Along with the increasing requirements of society on environmental protection, the electric vehicle technology becomes the mainstream research direction of each large vehicle enterprise. At present, a fixed speed reducer is adopted in an electric vehicle, and a large speed reducer can be selected to meet the power requirement when the vehicle starts and climbs a slope, but the large speed reducer limits the vehicle to reach a higher maximum speed, which is also the reason that the maximum speed of the electric vehicle in the market is generally lower than the maximum speed of the fuel vehicle. In order to give consideration to the highest speed and climbing capacity of the vehicle, many vehicle enterprises have started to install an AMT (automated mechanical transmission) on the electric vehicle, but the AMT belongs to a step-by-step speed change in principle, and the problems of gear shifting frustration and power interruption exist in the prior art; the gear ratio range of the AMT is limited by gear setting, and the AMT is applied to a heavy vehicle, so that in order to enlarge the gear ratio range, a great number of gears are required to be set, the gear shifting process is slow, the operation is complex, and a great number of cart drivers are unwilling to step on the brakes; the gear shifting process of the AMT transmission depends on a complex control strategy, so that accurate gear shifting time is difficult to grasp, and the problems of high energy consumption and low efficiency exist; the AMT transmission has the advantages of complex structure, high manufacturing cost and difficult maintenance.
Disclosure of Invention
The invention aims to solve the problems, and designs a three-planetary-row stepless speed change mechanism with single-side input and output and a speed change method thereof.
The technical scheme of the invention for achieving the purpose is that the three-planetary-row stepless speed change mechanism comprises a first planetary row, a second planetary row and a third planetary row, wherein a first gear ring on the first planetary row is connected with a second planetary carrier on the second planetary row, the second planetary carrier on the second planetary row is connected with a third sun gear on the third planetary row through a connecting shaft, the first planetary carrier on the first planetary row is connected with a second gear ring on the second planetary row and a third gear ring on the third planetary row, unidirectional stoppers are arranged on connecting bodies of the first planetary carrier, the second gear ring and the third gear ring, a third planetary carrier on the third planetary row is connected with an output part, and a second input shaft connected with a second sun gear on the second planetary row passes through the second planetary carrier, the connecting shaft, the third sun gear, the third planetary carrier and the output part and the first input shaft and the second sun gear are connected with a first driving member.
As a further illustration of the invention, the external teeth of the first sun gear engage first planet gears, which are mounted on the first planet carrier and which engage the inner teeth of the first ring gear;
The outer teeth of the second sun gear are meshed with a second planet gear, the second planet gear is arranged on the second planet carrier, and the second planet gear is meshed with the inner ring gear of the second gear ring;
And the outer teeth of the third sun gear are meshed with a third planet gear, the third planet gear is arranged on the third planet carrier, and the third planet gear is meshed with the inner ring gear of the third gear ring.
As a further explanation of the present invention, the one-way stopper is for restricting the rotational directions of the first carrier, the second ring gear, and the third ring gear, and the one-way stopper makes the rotational directions of the first carrier, the second ring gear, and the third ring gear coincide with only the steering direction of the second driver.
The invention also provides a speed changing method of the three-planetary-row stepless speed changing mechanism based on unilateral input and output, wherein the first driving piece is connected with the first sun gear through the 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 is connected with the second sun gear through a second input shaft, so that the rotating speed of the second driving piece is the same as that of the second sun gear; the first planet carrier, the second gear ring and the third gear ring are connected, so that the rotating speeds of the first planet carrier, the second gear ring and the third gear ring are the same; the first gear ring, the second planet carrier and the third sun gear are connected, so that the rotation speeds of the first gear ring, the second planet carrier and the third sun gear are the same; the output component is connected with the third planet carrier, so that the rotation speeds of the third planet carrier and the output component are the same; by adjusting and controlling the rotation speed of the first driving member and the rotation speed of the second driving member, stepless continuous change of the rotation speed of the output member is realized, and in the process, the speed ratio is correspondingly changed.
As a further explanation of the present invention, set is: the rotational speed of the first driving member and the rotational speed of the first sun gear are N 1, the rotational speed of the second driving member and the rotational speed of the second sun gear are N 2, the rotational speeds of the first ring gear, the second planet carrier and the third sun gear are N 3, The rotational speeds of the first planet carrier, the second gear ring and the third gear ring are N 4, the rotational speeds of the third planet carrier and the output part are N 5, the number of teeth of the first sun gear is Z 1, the number of teeth of the first gear ring is Z 2, The number of teeth of the second sun gear is Z 3, the number of teeth of the second gear ring is Z 4, the number of teeth of the third sun gear is Z 5, the number of teeth of the third gear ring is Z 6, When any two values in the N 1、N2、N3、N4 and the N 5 are determined, the other three values can be calculated by the proportional relation of the line segments in the vector diagram; the continuous stepless change of the rotating speed N 5 of the output part can be realized by adjusting and controlling the rotating speed N 1 of the first driving part and the rotating speed N 2 of the second driving part; the output states of the output member include state a, state B, state C, state D, and state E by adjusting and controlling the rotational speed N 1 of the first drive member and the rotational speed N 2 of the second drive member.
As a further explanation of the present invention, in the state a, the rotation of the first driver N 1 is reversed, the rotation of the second driver N 2 is forward, the ratio of the rotation of the second driver N 2 to the rotation of the first driver N 1 is equal to [ Z 1×(Z3+Z4)]/(Z2×Z3 ], the rotation of the first carrier, the second ring gear, and the third ring gear N 4 is 0, and the rotation of the output member N 5 is forward.
As a further explanation of the present invention, in the state B, the rotation speed N 1 of the first driver is reversed, the rotation speed N 2 of the second driver is forward, the ratio of the rotation speed N 2 of the second driver and the rotation speed N 1 of the first driver is greater than [ Z 1×(Z3+Z4)]/(Z2×Z3 ], the rotation speeds N 4 of the first carrier, the second ring gear, and the third ring gear are reversed, and the rotation speed N 5 of the output member is reversed.
As a further explanation of the present invention, in the state C, the rotation of the rotation speed N 1 of the first driver is reversed, the rotation of the rotation speed N 2 of the second driver is forward, the ratio of the rotation speed N 2 of the second driver to the rotation speed N 1 of the first driver is smaller than [ Z 1×(Z3+Z4)]/(Z2×Z3 ], the rotation of the rotation speed N 4 of the first carrier, the second ring gear and the third ring gear is reversed, the rotation speed N 5 of the output member may be forward or reverse, and in order to prevent this, a one-way stopper is provided on the connection body of the first carrier, the second ring gear and the third ring gear, the rotation speed N 4 of the first carrier, the second ring gear and the third ring gear is restricted to be forward only, and not reverse, so that the rotation speed N 5 of the output member is always ensured to be forward.
As a further explanation of the present invention, in the state D, the rotation speed N 1 of the first driver is 0, the rotation speed N 2 of the second driver is turned forward, the rotation speeds N 4 of the first carrier, the second ring gear, and the third ring gear are turned forward, and the rotation speed N 5 of the output member is turned forward.
As a further explanation of the present invention, in the state E, the rotational speeds N 1 of the first driving member and the rotational speeds N 2 of the second driving member are the same, the rotational directions are all forward directions, the rotational speeds N 4 of the first carrier, the second ring gear, and the third ring gear are the same as the rotational speeds N 1 and N 2, the rotational directions are all forward directions, the rotational speeds N 5 of the output member are the same as the rotational speeds N 1、N2 and N 4, the rotational directions are all forward directions, and the gear ratio of the state E is 1.
As a further explanation of the present invention, when the first driving member fails, the rotational speed of the second driving member is N 2, the rotational speed of the first carrier, the second ring gear and the rotational speed of the third ring gear are N 4, the first carrier, the second ring gear and the third ring gear have a reverse tendency, and the unidirectional stopper restricts the reverse direction, so that the rotational speeds of the first carrier, the second ring gear and the third ring gear are N 4, the rotational speed of the output member is N 5, the power of the second driving member is reduced by the second planetary row and the third planetary row, and the transmission ratio is [ (Z 3+Z4)×(Z5+Z6)]/(Z3×Z5).
As a further explanation of the present invention, when the second driving member fails, the rotational speed of the first driving member is N 1, the direction is reverse, the rotational speeds N 4 of the first carrier, the second ring gear and the third ring gear have a tendency to reverse, and the unidirectional stopper restricts the reverse, so that the rotational speeds N 4 of the first carrier, the second ring gear and the third ring gear are 0, the rotational speed N 5 of the output member rotates in the forward direction, the power of the first driving member is reduced by the first planetary gear row and the third planetary gear row, and the transmission ratio is [ (Z 3+Z4)×(Z5+Z6)]/(Z3×Z5).
The three-planetary-row stepless speed change mechanism with single-side input and output and the speed change method thereof provided by the invention have the advantages of high transmission efficiency, large output torque, no power interruption, simple and reliable structure, low manufacturing cost, easiness in maintenance, simplicity and convenience in speed regulation and the like, and the transmission ratio between the input end and the output end is changed through the adjustment of the rotating speeds of the first driving piece and the second driving piece and the cooperation of the first planetary row, the second planetary row, the third planetary row and the unidirectional stopper. In addition, the connecting ends of the first driving piece, the second driving piece and the output part are arranged at one end of the stepless speed change mechanism, so that the input and output of power are both at one end of the stepless speed change mechanism, and the first input shaft passes through the second input shaft and the second driving piece to be connected with the first driving piece, so that the utilization rate of space can be greatly improved, and the arrangement and the space utilization rate of the whole power equipment are more reasonable.
Drawings
FIG. 1 is a schematic diagram of a three-planetary-row continuously variable transmission mechanism with single-side input and output provided by an embodiment of the invention;
FIG. 2 is a rotational speed vector diagram of a first row of satellites according to an embodiment of the present invention;
FIG. 3 is a rotational speed vector diagram of a second planetary gear set according to an embodiment of the present invention;
FIG. 4 is a rotational speed vector diagram of a third planetary gear set according to an embodiment of the present invention;
FIG. 5 is a rotational speed vector diagram incorporating FIGS. 2, 3, and 4 provided in an embodiment of the present invention;
Fig. 6 is a rotational speed vector diagram of the first carrier, the second ring gear, and the third ring gear provided in the embodiment of the present invention when the rotational speed N 4 is 0;
Fig. 7 is a rotational speed vector diagram of the first carrier, the second ring gear, and the third ring gear provided in the embodiment of the present invention when the rotational speed N 4 is less than 0;
fig. 8 is a rotation speed vector diagram of the first driving member when the rotation speed N 1 of the first driving member is 0 according to the embodiment of the present invention;
FIG. 9 is a rotational speed vector diagram of the first driving member and the second driving member according to the embodiment of the present invention when the rotational speeds of the first driving member and the second driving member are the same;
FIG. 10 is a rotational speed vector diagram of the first and second driving members when the rotational speeds N 1 and N 2 of the first and second driving members are both positive in direction;
FIG. 11 is a rotational speed vector diagram of the first carrier, the second ring gear, and the third ring gear when the rotational speeds N 4 are 0 under the reverse operating condition provided by the embodiment of the present invention;
FIG. 12 is a rotational speed vector diagram of a reverse operating mode provided by an embodiment of the present invention when rotational speeds N 4 of the first carrier, the second ring gear, and the third ring gear are less than 0;
FIG. 13 is a rotational speed vector diagram of the second driving member when the rotational speed N 2 of the second driving member is turned to the forward direction when the first driving member fails according to the embodiment of the present invention;
fig. 14 is a rotational speed vector diagram of the case where the rotational speed N 1 of the first driving member is reversed when the second driving member fails according to the embodiment of the present invention.
Reference numerals:
1-first planetary row, 101-first sun gear, 102-first planet carrier, 103-first gear ring, 2-second planetary row, 201-second sun gear, 202-second planet carrier, 203-second gear ring, 3-third planetary row, 301-third sun gear, 302-third planet carrier, 303-third gear ring, 4-one-way stop, 5-first input shaft, 6-second input shaft, 7-connecting shaft; 8-an output component.
Detailed Description
Firstly, the aim of the embodiment of the invention is to be described, and the problem that the AMT transmission has shift setbacks and power interruption is solved; the gear ratio range of the AMT is limited by gear setting, and the AMT is applied to a heavy vehicle, so that in order to enlarge the gear ratio range, a great number of gears are required to be set, the gear shifting process is slow, the operation is complex, and a great number of cart drivers are unwilling to step on the brakes; the gear shifting process of the AMT transmission depends on a complex control strategy, so that accurate gear shifting time is difficult to grasp, and the problems of high energy consumption and low efficiency exist; the AMT transmission has the advantages of complex structure, high manufacturing cost, difficult maintenance and other existing problems, so that a three-planetary-row stepless speed change mechanism with single-side input and output is provided to solve the existing problems.
The following describes embodiments of the present invention with reference to the accompanying drawings, and we first introduce a specific structure of the embodiments of the present invention.
Referring to fig. 1, a single-side input and output three-planetary-row stepless speed change mechanism comprises a first planetary row 1, a second planetary row 2 and a third planetary row 3, wherein a first gear ring 103 on the first planetary row 1 is connected with a second planetary carrier 202 on the second planetary row 2, the second planetary carrier 202 on the second planetary row 2 is connected with a third sun gear 301 on the third planetary row 3 through a connecting shaft 7, a first planetary carrier 102 on the first planetary row 1 is connected with a second gear ring 203 on the second planetary row 2 and a third gear ring 303 on the third planetary row 3, a unidirectional stopper 4 is arranged on a connecting body of the first planetary carrier 102, the second gear ring 203 and the third gear ring 303, a third planetary carrier 302 on the third planetary row 3 is connected with an output part 8, a first sun gear 101 on the first planetary row 1 is connected with a first driving member through a first input shaft 5, a second input shaft 6 connected with the second sun gear 201 on the second planetary row 2 passes through the second planetary carrier 202, the connecting shaft 7, the third planetary carrier 203 and the third planetary carrier 302 and the third sun gear member 8 pass through the first sun gear 1 and the first sun gear member 101.
Referring to fig. 1, the external teeth of the first sun gear 101 engage with first planetary gears, which are mounted on the first carrier 102, and the first planetary gears engage with the internal teeth of the first ring gear 103; the external teeth of the second sun gear 201 are engaged with second planetary gears, the second planetary gears are mounted on the second planet carrier 202, and the second planetary gears are engaged with the internal teeth of the second gear ring 203; the outer teeth of the third sun gear 301 engage third planet gears, which are mounted on a third planet carrier 302, and the third planet gears engage inner teeth of a third ring gear 303.
Referring to fig. 1, the one-way stopper 4 serves to restrict the rotational directions of the first carrier 102, the second ring gear 203, and the third ring gear 303, and the one-way stopper 4 makes the rotational directions of the first carrier 102, the second ring gear 203, and the third ring gear 303 coincide with only the rotation direction of the second driver.
The following needs to describe a speed change method of a three-planetary-row stepless speed change mechanism based on unilateral input and output by combining a specific structure of the embodiment of the invention.
According to the basic principle of the planetary gear, the rotation speed of any two components of the sun gear, the gear ring and the planet carrier is determined, the rotation speed of the other component is also determined, and the rotation speed relationship of the sun gear, the gear ring and the planet carrier is in corresponding proportional relationship according to the number of teeth of the sun gear and the number of teeth of the gear ring.
According to the basic principle of the planetary gear, the sun gear, the gear ring and the planet carrier are three components, the rotation speed of any two components is the same, and the rotation speed of the other component is the same.
The rotation speed of the first driving member is the same as the rotation speed of the first sun gear 101, and is set to be N 1; the rotation speed of the second driving member is the same as the rotation speed of the second sun gear 201, and is set to be N 2; the rotational speeds of the first ring gear 103, the second carrier 202, and the third sun gear 301 are the same, and are set to N 3; the rotational speeds of the first carrier 102, the second ring gear 203, and the third ring gear 303 are the same, and are set to N 4; the rotation speed of the third carrier 302 and the output member 8 are the same, and N 5 is set; the number of teeth of the first sun gear 101 is set to be Z 1, the number of teeth of the first ring gear 103 is set to be Z 2, the number of teeth of the second sun gear 201 is set to be Z 3, the number of teeth of the second ring gear 203 is set to be Z 4, the number of teeth of the third sun gear 301 is set to be Z 5, and the number of teeth of the third ring gear 303 is set to be Z 6.
According to the rotation speed vector calculation method of the planetary gear, a rotation speed vector diagram of the first planetary gear 1 is obtained, as shown in fig. 2. N 1 is the rotational speed of the first sun gear 101, N 3 is the rotational speed of the first ring gear 103, and N 4 is the rotational speed of the first carrier 102. The length of N 1、N3、N4 represents the rotation speed, the arrow direction represents the rotation speed direction, the arrow upward represents the rotation speed is positive, and the arrow downward represents the rotation speed is reverse. L 2/L3＝Z1/Z2 is set.
According to the rotation speed vector calculation method of the planetary gear, a rotation speed vector diagram of the second planetary gear 2 is obtained, as shown in fig. 3. N 2 is the rotational speed of the second sun gear 201, N 4 is the rotational speed of the second ring gear 203, and N 3 is the rotational speed of the second carrier 202. The length of N 2、N3、N4 represents the rotation speed, the arrow direction represents the rotation speed direction, the arrow upward represents the rotation speed is positive, and the arrow downward represents the rotation speed is reverse. L 2/L1＝Z3/Z4 is set.
According to the rotation speed vector calculation method of the planetary gear, a rotation speed vector diagram of the third planetary gear 3 is obtained, as shown in fig. 4. N 3 is the rotational speed of the third sun gear 301, N 4 is the rotational speed of the third ring gear 303, and N 5 is the rotational speed of the third carrier 302. The length of N 3、N4、N5 represents the rotation speed, the arrow direction represents the rotation speed direction, the arrow upward represents the rotation speed is positive, and the arrow downward represents the rotation speed is reverse. L 5/L4＝Z5/Z6 is set.
In fig. 2, 3 and 4, L 1、L2、L3、L4、L5 only needs to satisfy the corresponding proportional relationship, and the actual length of L 1、L2、L3、L4、L5 does not affect the size of the calculated N 1、N2、N3、N4、N5. Fig. 5 may be obtained by combining fig. 2, fig. 3, and fig. 4, and let L 2＝L4+L5 be.
See fig. 5,N 1 for the rotational speed of the first sun gear 101, i.e. the rotational speed of the first drive member; n 2 is the rotational speed of the second sun gear 201, i.e. the rotational speed of the second drive member; n 3 is the rotational speed of the first ring gear 103, the second carrier 202 and the third sun gear 301; n 4 is the rotational speed of the first carrier 102, the second ring gear 203, and the third ring gear 303; n 5 is the rotational speed of the third planet carrier 302 and the output member 8.
Any two values of N 1、N2、N3、N4 and N 5 are determined, and the other three values can be calculated through the proportional relation of the line segments in the vector diagram. I.e. the rotational speed N 1 of the first drive member and the rotational speed N 2 of the second drive member, the rotational speed N 5 of the output member 8 is also uniquely determined. By regulating and controlling the rotational speed N 1 of the first drive element and the rotational speed N 2 of the second drive element, a continuous stepless variation of the rotational speed N 5 of the output element 8 is achieved.
The speed change principle of the unilateral input and output three-planetary-row stepless speed change mechanism of the embodiment of the invention is described below by combining specific working conditions.
1. Starting condition
Referring to fig. 5 and 6, at start-up, the rotation speed N 1 of the first driving member turns in the reverse direction, and the rotation speed N 2 of the second driving member turns in the forward direction. By controlling the ratio of the rotation speed N 2 of the second driving member to the rotation speed N 1 of the first driving member to be always greater than (as shown in fig. 5) or equal to (as shown in fig. 6) [ Z 1×(Z3+Z4)]/(Z2×Z3 ], the rotation speed N 5 of the output member 8 can be controlled to gradually accelerate from 0 and turn to the forward direction. Under the working condition, the transmission ratio is maximum, and the power of the first driving piece and the power of the second driving piece are coupled together, so that the vehicle can accelerate and drive forwards due to the speed reduction and torque increase output.
2. Acceleration and deceleration conditions
The acceleration and deceleration processes can be classified into three cases according to the rotation direction of the rotation speed N 1 of the first driving member, which specifically includes:
1) Case one
Referring to fig. 5 and 6, the rotation speed N 1 of the first driving member is reversed, and the rotation speed N 2 of the second driving member is forward. The ratio of the rotational speed N 2 of the second drive member to the rotational speed N 1 of the first drive member is always greater than or equal to [ Z 1×(Z3+Z4)]/(Z2×Z3 ]. By controlling the increase or decrease of the rotation speed N 1 of the first driving element and the rotation speed N 2 of the second driving element, the gradual increase or decrease of the rotation speed N 5 of the output member 8 can be controlled, and the steering is turned to the forward direction, so that the vehicle is accelerated or decelerated and driven forward.
2) Case two
Referring to fig. 8, the rotation speed N 1 of the first driving member gradually decreases to 0, the rotation speed N 2 of the second driving member turns to forward, and by controlling the rotation speed N 1 of the first driving member to 0 and the increasing/decreasing speed of the rotation speed N 2 of the second driving member, the gradual increase or decrease of the output rotation speed N 5 can be realized, the turning is forward, and the vehicle is accelerated or decelerated to forward travel.
3) Case three
Referring to fig. 10, the rotation speed N 1 of the first driving member turns forward, and the rotation speed N 2 of the second driving member turns forward. By controlling the increasing and decreasing speed of the rotation speed N 1 of the first driving member and the rotation speed N 2 of the second driving member, the output rotation speed N 5 can be gradually increased or decreased, and the vehicle can be accelerated or decelerated to drive forward by turning to the forward direction.
In addition, the speed regulation method of acceleration and deceleration can also be to adjust the rotation speed N 5 of the output part 8 by maintaining the rotation speed N 1 of the first driving piece unchanged and adjusting the rotation speed N 2 of the second driving piece; the rotation speed N 2 of the second driving member can also be kept unchanged, and the rotation speed N 5 of the output member 8 can be adjusted by adjusting the rotation speed N 1 of the first driving member. In the process of realizing acceleration or deceleration of the rotating speed N 5 of the output component 8, the first driving piece and the second driving piece can be different according to respective high-efficiency working areas, and the control system can control the acceleration, the deceleration and the maintenance of the rotating speeds of the first driving piece and the second driving piece according to the current working condition. Therefore, the first driving piece and the second driving piece 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. 9 and 10, the rotation speed N 1 of the first driving member turns forward, and the rotation speed N 2 of the second driving member turns forward. When the rotational speed N 1 of the first drive member and the rotational speed N 2 of the second drive member both reach the maximum rotational speed, the rotational speed N 5 of the output member 8 also reaches the maximum rotational speed, at which time the vehicle speed reaches the maximum vehicle speed. If the rotational speed N 1 of the first drive member is the same as the maximum rotational speed N 2 of the second drive member, the rotational speed N 5 of the output member 8 can reach the same maximum rotational speed as the maximum rotational speeds N 1、N2 of the first drive member and the second drive member, and the transmission ratio is 1.
Aiming at the starting working condition and the acceleration and deceleration working condition, the occurrence of a dangerous working condition needs to be considered to be avoided.
Examples: referring to fig. 7, when the rotation of the first driving member is reversed and the rotation of the second driving member is forward, and the vehicle is running in the start stage or the middle-low stage, if the control of the rotation of the first driving member and the second driving member is inaccurate or the control fails, the ratio of the rotation of the second driving member N 2 and the rotation of the first driving member N 1 is smaller than Z 1×(Z3+Z4)]/(Z2×Z3), As shown in fig. 7, the steering of the rotational speed N 5 of the output member 8 may be reversed, and the vehicle suddenly runs in reverse, which is very likely to cause serious accidents. In order to prevent this, by providing the one-way stopper 4 on the connection body of the first carrier 102, the second ring gear 203, and the third ring gear 303, it is achieved that the rotational speed N 4 of the first carrier 102, the second ring gear 203, and the third ring gear 303 is restricted to be turned only in the forward direction and not in the reverse direction. This ensures that the rotational speed N 5 of the output member 8 always turns in the forward direction. Therefore, when the dangerous condition occurs, the rotation speed N 4 of the first planet carrier 102, the second gear ring 203 and the third gear ring 303 is limited by the unidirectional stopper 4 to be only forward, but not reverse, at this time, the two driving members drag each other, the ratio of the rotation speed N 2 of the second driving member to the rotation speed N 1 of the first driving member is always equal to [ Z 1×(Z3+Z4)]/(Z2×Z3), The rotational speeds N 4 of the first carrier 102, the second ring gear 203, and the third ring gear 303 are equal to 0, and the rotational speed N 5 of the output member 8 can be turned only in the forward direction, so that the reverse running does not occur suddenly.
4. Reversing working condition
Referring to fig. 11 and 12, when reversing, the rotation speed N 1 of the first driving member turns forward, and the rotation speed N 2 of the second driving member turns backward. By controlling the ratio of the rotation speed N 2 of the second driving member to the rotation speed N 1 of the first driving member to be always greater than (as shown in fig. 12) or equal to (as shown in fig. 11) [ Z 1×(Z3+Z4)]/(Z2×Z3 ], the rotation speed N 5 of the output member 8 can be controlled to gradually accelerate from 0 and turn to reverse. If the control of the rotational speeds of the first driving member and the second driving member is inaccurate or fails, when the ratio of the rotational speed N 2 of the second driving member to the rotational speed N 1 of the first driving member is smaller than [ Z 1×(Z3+Z4)]/(Z2×Z3 ], the steering of the rotational speed N 5 of the output member 8 may be in a forward direction, and the vehicle suddenly goes forward and is very easy to have serious accidents. In order to prevent this, by providing the one-way stopper 4 on the connection body of the first carrier 102, the second ring gear 203, and the third ring gear 303, it is achieved that the rotation speed N 4 of the first carrier 102, the second ring gear 203, and the third ring gear 303 is restricted to be reversed only and not to be forward, so that it is ensured that the rotation speed N 5 of the output member 8 is always reversed.
In addition to the normal and dangerous conditions described above, there are also some emergency conditions that need to be addressed, which are considered and addressed by embodiments of the present invention.
Examples: referring to fig. 13, when the first driving member fails, the rotation speed of the second driving member is N 2, the rotation direction is forward, the rotation speeds N 4 of the first planet carrier 102, the second ring gear 203 and the third ring gear 303 have a reverse rotation tendency, at this time, the unidirectional stopper 4 limits the reverse rotation, so that the rotation speeds N 4 of the first planet carrier 102, the second ring gear 203 and the third ring gear 303 are 0, the rotation speed N 5 of the output member 8 rotates forward, the power of the second driving member is output through the second planet row 2 and the third planet row 3 by means of speed reduction and torque increase, and the transmission ratio is [ (Z 3+Z4)×(Z5+Z6)]/(Z3×Z5), so that the vehicle can continue to accelerate or decelerate forward.
Referring to fig. 14, when the second driver fails, the rotation speed of the first driver is N 1, the rotation direction is reverse, the rotation speeds N 4 of the first carrier 102, the second ring gear 203 and the third ring gear 303 have a tendency to reverse, at this time, the one-way stopper 4 restricts the reverse rotation thereof, so that the rotation speeds N 4 of the first carrier 102, the second ring gear 203 and the third ring gear 303 are 0, the rotation speed N 5 of the output member 8 rotates in the forward direction, the power of the first driver is output through the first planetary gear row 1 and the third planetary gear row 3 by decelerating and increasing torque, and the transmission ratio is [ Z 2×(Z5+Z6)]/(Z1×Z5 ], so that the vehicle can continue to accelerate or decelerate forward.
Therefore, when one driving piece fails, the other driving piece can still drive the vehicle to run, and the power performance is reduced, but the vehicle can be run to a maintenance site or a safety site by means of one driving piece, so that the reliability of the vehicle can be greatly improved.
The three-planetary-row stepless speed change mechanism with single-side input and output and the speed change method thereof provided by the embodiment of the invention have the following advantages:
1. The three-planetary-row stepless speed change mechanism with single-side input and output has no power interruption in the speed regulation process, is quiet and stable in operation, has better experience of using the vehicle when a user uses the vehicle, can greatly meet the requirements of the user in sense, and lays a very good foundation for popularization and use of the product.
2. The three-planetary-row stepless speed change mechanism with single-side input and output can realize that the output end has large torque from low speed to high speed, the vehicle has the capability of accelerating and starting rapidly when driving by outputting the large torque, the large torque can climb a larger gradient when climbing a slope, and the large torque can also meet the vehicle requirements of more people, so that the audience surface of the product is larger.
3. The unilateral input and output three-planetary-row stepless speed change mechanism provided by the embodiment of the invention can realize stepless continuous change of output rotating speed, the input end driving piece 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 three-planetary-row stepless speed change mechanism with single-side input and output provided by the embodiment of the invention has the advantages that the speed regulation is simple and convenient, 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 the popularity of the product are ensured to a certain extent.
5. According to the embodiment of the invention, the power of the first driving piece and the power of the second driving piece are coupled together to drive the vehicle to run, when one driving piece fails, the other driving piece can still continue to drive the vehicle to run, so that when a vehicle owner uses the vehicle, even if one driving piece fails, the vehicle owner can drive the vehicle by means of the other driving piece 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 cared.
6. Compared with the traditional driving mode of a single driving piece, the product using the embodiment of the invention not only can be driven by adopting double driving pieces, but also can select the driving piece with smaller volume and lower rotating speed for adapting, the driving piece with smaller volume is more beneficial to the arrangement design of the driving piece 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 driving piece with smaller volume.
7. The unilateral input and output three-planetary-row stepless speed change mechanism provided by the embodiment of the invention has high-efficiency transmission rate, and under the same working condition, a motor with lower power and lower rotating speed can be selected as a driving piece, so that compared with a high-power battery, the low-power battery can better prevent the overheat condition of the battery, and the use safety of the battery is indirectly improved through the embodiment of the invention.
8. The three-planetary-row stepless speed change mechanism with single-side input and output adopts three-planetary-row transmission, increases the transmission ratio, further increases the torque, and can be applied to heavy-duty trucks, earth-moving trucks, buses and the like with larger loads, thereby further widening the application range of the embodiment of the invention.
9. The three-planetary-row stepless speed change mechanism with single-side input and output is characterized in that the connecting ends of the first driving piece, the second driving piece and the output part 8 are respectively provided with one end of the stepless speed change mechanism, so that the input and output of power are both at one end of the stepless speed change mechanism, and the first input shaft 5 passes through the second input shaft 6 and the second driving piece to be connected with the first driving piece.
The above technical solution only represents the preferred technical solution of the present invention, and some changes that may be made by those skilled in the art to some parts of the technical solution represent the principles of the present invention, and the technical solution falls within the scope of the present invention.
Claims (12)
1. A three-planetary-row continuously variable transmission mechanism with single-side input and output, which is characterized by comprising a first planetary row (1), a second planetary row (2) and a third planetary row (3), wherein a first gear ring (103) on the first planetary row (1) is connected with a second planetary carrier (202) on the second planetary row (2), the second planetary carrier (202) on the second planetary row (2) is connected with a third sun gear (301) on the third planetary row (3) through a connecting shaft (7), a first planetary carrier (102) on the first planetary row (1) is connected with a second gear ring (203) on the second planetary row (2) and a third gear ring (303) on the third planetary row (3), a unidirectional stopper (4) is arranged on a connecting body of the first planetary carrier (102), the second gear ring (203) and the third gear ring (303), a third planetary carrier (302) on the third row (3) is connected with a second sun gear (302), a second planetary carrier (8) on the third planetary carrier (3) is connected with a third sun gear (301), a third planetary carrier (8) on the second planetary carrier (2) is connected with the third sun gear (201), a first input shaft (5) connected with a first sun gear (101) on the first planetary row (1) penetrates through a second sun gear (201), a second input shaft (6) and a second driving piece to be connected with the first driving piece.
2. The unilateral input/output three-planetary-row continuously variable transmission mechanism according to claim 1, wherein the external teeth of the first sun gear (101) are engaged with first planetary gears, the first planetary gears are mounted on the first planet carrier (102), and the first planetary gears are engaged with the internal teeth of the first gear ring (103);
the external teeth of the second sun gear (201) are meshed with second planetary gears, the second planetary gears are mounted on the second planet carrier (202), and the second planetary gears are meshed with the inner ring teeth of the second gear ring (203);
The external teeth of the third sun gear (301) are engaged with third planetary gears, the third planetary gears are mounted on the third planetary carrier (302), and the third planetary gears are engaged with the inner ring teeth of the third gear ring (303).
3. The single-sided input, output three-planetary-row continuously variable transmission mechanism according to claim 1, characterized in that the one-way stopper (4) is for restricting the rotational directions of the first carrier (102), the second ring gear (203), and the third ring gear (303), the one-way stopper (4) conforming the rotational directions of the first carrier (102), the second ring gear (203), and the third ring gear (303) only to the rotation direction of the second driver.
4. The speed change method of the three-planetary-row stepless speed change mechanism based on single-side input and output is characterized in that a first driving piece is connected with a first sun gear (101) through a first input shaft (5) so that the rotating speed of the first driving piece is the same as the rotating speed of the first sun gear (101); the second driving piece is connected with the second sun gear (201) through a second input shaft (6), so that the rotating speed of the second driving piece is the same as the rotating speed of the second sun gear (201); the first planet carrier (102), the second gear ring (203) and the third gear ring (303) are connected, so that the rotation speeds of the first planet carrier (102), the second gear ring (203) and the third gear ring (303) are the same; the first gear ring (103), the second planet carrier (202) and the third sun gear (301) are connected, so that the rotation speeds of the first gear ring (103), the second planet carrier (202) and the third sun gear (301) are the same; the output component (8) is connected with the third planet carrier (302) so that the rotation speeds of the third planet carrier (302) and the output component (8) are the same; by regulating and controlling the rotational speed of the first driving member and the rotational speed of the second driving member, stepless continuous change of the rotational speed of the output member (8) is achieved, and in the process, the speed ratio is correspondingly changed.
5. The speed change method of the three-planetary-row continuously variable transmission mechanism based on single-side input and output according to claim 4, wherein: the rotation speed of the first driving piece and the rotation speed of the first sun gear (101) are N 1, the rotation speed of the second driving piece and the rotation speed of the second sun gear (201) are N 2, the first gear ring (103), The rotational speed of the second planet carrier (202) and the third sun gear (301) is N 3, the rotational speed of the first planet carrier (102), the second ring gear (203) and the third ring gear (303) is N 4, the rotational speed of the third planet carrier (302) and the output member (8) is N 5, The number of teeth of the first sun gear (101) is Z 1, the number of teeth of the first gear ring (103) is Z 2, the number of teeth of the second sun gear (201) is Z 3, the number of teeth of the second gear ring (203) is Z 4, The number of teeth of the third sun gear (301) is Z 5, the number of teeth of the third ring gear (303) is Z 6, when any two values of N 1、N2、N3、N4 and N 5 are determined, the other three values can be calculated by the proportional relation of the line segments in the vector diagram; The continuous stepless change of the rotating speed N 5 of the output component (8) can be realized by adjusting and controlling the rotating speed N 1 of the first driving piece and the rotating speed N 2 of the second driving piece; the output states of the output member (8) are made to include state A, state B, state C, state D and state E by adjusting and controlling the rotational speed N 1 of the first driving member and the rotational speed N 2 of the second driving member.
6. The shifting method of the three-planetary-gear-train continuously variable transmission mechanism based on single-sided input and output according to claim 5, characterized in that in the state a, the rotation of the rotation speed N 1 of the first driver is reversed, the rotation of the rotation speed N 2 of the second driver is forward, the ratio of the rotation speed N 2 of the second driver and the rotation speed N 1 of the first driver is equal to [ Z 1×(Z3+Z4)]/(Z2×Z3 ], the rotation speeds N 4 of the first carrier (102), the second ring gear (203) and the third ring gear (303) are 0, and the rotation speed N 5 of the output member (8) is forward.
7. The shifting method of the three-planetary-gear-train continuously variable transmission mechanism based on single-sided input and output according to claim 5, characterized in that in the state B, the rotation of the rotation speed N 1 of the first driver is reversed, the rotation of the rotation speed N 2 of the second driver is forward, the ratio of the rotation speed N 2 of the second driver and the rotation speed N 1 of the first driver is larger than [ Z 1×(Z3+Z4)]/(Z2×Z3), the rotation of the rotation speed N 4 of the first carrier (102), the second ring gear (203) and the third ring gear (303) is forward, and the rotation speed N 5 of the output member (8) is forward.
8. The shifting method of the three-planetary-gear-train continuously variable transmission mechanism based on the single-sided input and output according to claim 5, characterized in that in the state C, the rotation of the rotation speed N 1 of the first driver is reversed, the rotation of the rotation speed N 2 of the second driver is forward, the ratio of the rotation speed N 2 of the second driver to the rotation speed N1 of the first driver is smaller than [ Z 1×(Z3+Z4)]/(Z2×Z3), the rotation of the rotation speed N 4 of the first carrier (102), the rotation speed N 4 of the second ring gear (203) and the rotation speed N 4 of the third ring gear (303) is reversed, the rotation of the rotation speed N 5 of the output member (8) is either forward or reverse, and in order to prevent this, a one-way stopper (4) is provided on the connecting body of the first carrier (102), the second ring gear (203) and the third ring gear (303), the rotation speed N 4 of the first carrier (102), the second ring gear (203) and the third ring gear (303) is restricted from being only forward, and thus the rotation speed N 5 of the output member is always reversed.
9. The shifting method of the three-planetary-gear-train continuously variable transmission mechanism based on single-sided input and output according to claim 5, characterized in that in the state D, the rotation speed N 1 of the first driver is 0, the rotation speed N 2 of the second driver is turned forward, the rotation speeds N 4 of the first carrier (102), the second ring gear (203) and the third ring gear (303) are turned forward, and the rotation speed N 5 of the output member (8) is turned forward.
10. The speed change method of the three planetary gear set continuously variable transmission mechanism based on single-side input and output according to claim 5, wherein in the state E, the rotational speed N 1 of the first driving member and the rotational speed N 2 of the second driving member are the same in magnitude, the steering is forward, the rotational speeds N 4 of the first carrier (102), the second ring gear (203) and the third ring gear (303) are the same in magnitude as the N 1 and the N 2, the steering is forward, the rotational speed N 5 of the output member (8) is the same in magnitude as the N 1、N2 and the N 4, the steering is forward, and the transmission ratio of the state E is 1.
11. The speed change method of the three planetary gear set continuously variable transmission mechanism based on single-side input and output according to claim 5, wherein when the first driving member fails, the rotation speed of the second driving member is N 2, the rotation speed of the second driving member turns to the forward direction, the rotation speeds N 4 of the first planet carrier (102), the second gear ring (203) and the third gear ring (303) have a reverse rotation tendency, and the unidirectional stopper (4) limits the reverse rotation, so that the rotation speeds N 4 of the first planet carrier (102), the second gear ring (203) and the third gear ring (303) are 0, the rotation speed N 5 of the output member (8) rotates forward, and the power of the second driving member is reduced and torque-increased through the second planetary gear set (2) and the third planetary gear set (3), and the transmission ratio is [ (Z 3+Z4)×(Z5+Z6)]/(Z3×Z5).
12. The speed change method of the three planetary gear set continuously variable transmission mechanism based on single-side input and output according to claim 5, wherein when the second driving member fails, the rotation speed of the first driving member is N 1, the direction is reverse, the rotation speeds N 4 of the first planet carrier (102), the second ring gear (203) and the third ring gear (303) have a reverse rotation tendency, and at the moment, the unidirectional stopper (4) limits the reverse rotation, so that the rotation speeds N 4 of the first planet carrier (102), the second ring gear (203) and the third ring gear (303) are 0, the rotation speed N 5 of the output member (8) rotates forward, and the power of the first driving member is output by reducing speed and increasing torque of the first planet carrier (1) and the third planet carrier (3), and the transmission ratio is [ Z 2×(Z5+Z6)]/(Z1×Z5).
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Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106195169A (en) * | 2016-07-08 | 2016-12-07 | 天津天海同步科技有限公司 | Planet row type buncher and there is its power assembly |
| CN109707816A (en) * | 2017-10-25 | 2019-05-03 | Zf 腓德烈斯哈芬股份公司 | The stepless drive apparatus of branched power |
Family Cites Families (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US8882627B2 (en) * | 2008-05-02 | 2014-11-11 | Daimler Ag | Electric variable transmission for hybrid electric vehicles with four forward modes and six fixed gears |
| CN103075475A (en) * | 2013-01-19 | 2013-05-01 | 龙宏元 | Planetary series stepless transmission for controlling rotating speed of controlled transmission path |
| CN104747668B (en) * | 2015-04-13 | 2016-02-24 | 南京康尼精密机械有限公司 | A kind of differential speed regulation planet gear stageless speed variator |
| CN205859092U (en) * | 2016-06-08 | 2017-01-04 | 南京农业大学 | Multisection type big-power tractor hydraulic mechanical stepless gearbox |
| CN107529592A (en) * | 2017-07-26 | 2018-01-02 | 罗灿 | Three rows 11 control speed changer |
| CN107654605B (en) * | 2017-11-10 | 2023-07-21 | 石河子大学 | Single-row compound planetary gear type multi-section hydraulic mechanical stepless transmission |
| DE102018000195B4 (en) * | 2018-01-12 | 2021-01-14 | Daimler Ag | Transmission device for a motor vehicle, in particular for a motor vehicle |
| CN110056634A (en) * | 2019-01-24 | 2019-07-26 | 南京农业大学 | Three four sections of planet row hydraulic machinery infinitely variable transmissions |
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Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106195169A (en) * | 2016-07-08 | 2016-12-07 | 天津天海同步科技有限公司 | Planet row type buncher and there is its power assembly |
| CN109707816A (en) * | 2017-10-25 | 2019-05-03 | Zf 腓德烈斯哈芬股份公司 | The stepless drive apparatus of branched power |
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