CN115727105A - Unilateral-staged-transmission three-planet-row stepless speed change mechanism and speed change method thereof - Google Patents
Unilateral-staged-transmission three-planet-row stepless speed change mechanism and speed change method thereof Download PDFInfo
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- CN115727105A CN115727105A CN202110996661.4A CN202110996661A CN115727105A CN 115727105 A CN115727105 A CN 115727105A CN 202110996661 A CN202110996661 A CN 202110996661A CN 115727105 A CN115727105 A CN 115727105A
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Abstract
The invention discloses a unilateral stepped transmission three-planet-row stepless speed change mechanism and a speed change method thereof, belonging to the technical field of stepless speed changers. The transmission stage is arranged between the first input shaft and the transmission shaft of the stepless speed change mechanism, and the transmission stage achieves the purpose of changing the transmission ratio between the second driving piece and the second sun gear by changing the gear ratio of the transmission gear A and the transmission gear B, so that the power selection range of the second driving piece is widened.
Description
Technical Field
The invention relates to the technical field of continuously variable transmissions, in particular to a unilateral stepped transmission three-planet-row 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, 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 three-planet-row stepless speed change mechanism with single-side stepped transmission and a speed change method thereof.
The technical scheme of the invention is that the unilateral stepped transmission three-planetary-row stepless speed change mechanism comprises a first planetary row, a second planetary row, a third planetary row and a transmission stage, wherein the transmission stage comprises a transmission gear A and a transmission gear B, the transmission gear A is meshed with the transmission gear B through external teeth, a first gear ring on the first planetary row is connected with a second planet carrier on the second planetary row, the second planet carrier is connected with a third sun gear on the third planetary row through a connecting shaft, a first planet 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, the one-way stopper is arranged on the connecting bodies of the first planet carrier, the second gear ring and the third gear ring, the third planet carrier on the third planet row is connected with an output part, a transmission shaft connected with a second sun gear on the second planet row penetrates through the second planet carrier, the connecting shaft, the third sun gear, the third planet carrier and the output part and is connected with the transmission gear B, a first input shaft connected with a first sun gear on the first planet row penetrates through the second sun gear, the transmission shaft and the transmission gear B and is connected with a first driving piece, and the transmission gear A is connected with a second driving piece through a second input shaft.
As a further explanation of the present invention, the external teeth of the first sun gear engage with a first planet gear, the first planet gear is mounted on the first planet carrier, and the first planet gear engages with the inner ring 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 teeth 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 teeth of the third gear ring.
As a further explanation of the present invention, the one-way stopper serves to limit 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 of the second sun gear driven by the second driver.
The invention also provides a speed change method of the three-planet-row stepless speed change mechanism based on unilateral stepped transmission, 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 second sun gear are connected through a second input shaft, a transmission stage and a transmission shaft, so that the rotating speed of the second driving piece and the rotating speed of the second sun gear form a transmission proportional relation of the transmission stage; 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 rotating speeds of the first gear ring, the second planet carrier and the third sun gear are the same; the output part is connected with the third planet carrier, so that the rotating speeds of the third planet carrier and the output part are the same; the stepless continuous change of the rotating speed of the output part is realized by adjusting and controlling the rotating speed of the first driving part and the rotating speed of the second driving part, and the speed ratio is correspondingly changed in the process.
As a further explanation of the invention, it is assumed that: the rotating speed of the first driving piece and the rotating speed of the first sun gear are N 1 The rotation speed of the second sun gear is N 2 The transmission ratio of the transmission stage is i, and the rotating speed of the second driving piece is N 2 Xi, the rotation speeds of the first gear ring, the second planet carrier and the third sun gear are N 3 The rotation speed of the first planet carrier, the second gear ring and the third gear ring is N 4 And the third planet carrier and the output member rotate at a speed 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 ring gear is Z 6 When said N is 1 、N 2 、N 3 、N 4 And N 5 When any two values in the vector diagram are determined, the other three values can be calculated through the proportional relation of line segments in the vector diagram; regulating and controlling the rotational speed N of the first sun gear by driving the first driving member and the second driving member 1 And the rotational speed N of the second sun gear 2 The rotational speed N of the output member can be realized 5 Continuous stepless variation of (2); controlling the rotational speed N of the first sun gear by regulation 1 And the rotational speed N of the second sun gear 2 The output states of the output means are made to include state a, state B, state C, state D, and state E.
As a further explanation of the present invention, in the state a, the rotation speed at which the first driving member drives the first sun gear is N 1 The direction of rotation is reverse; the rotating speed of the second driving piece driving the second sun gear is N 2 The steering direction is positive; rotational speed N of the second sun gear 2 And the rotational speed N of the first sun gear 1 Is equal to [ Z ] 1 ×(Z 3 +Z 4 )]/(Z 2 ×Z 3 ) A rotation speed N of the first carrier, the second ring gear and the third ring gear 4 Is 0, the rotational speed N of the output member 5 The direction of rotation of (c) is the forward direction.
As a further explanation of the present invention, in the state B, the rotation speed at which the first driving member drives the first sun gear is N 1 The direction of rotation is reverse; the rotating speed of the second driving piece driving the second sun gear is N 2 The steering direction is positive; rotational speed N of the second sun gear 2 And the rotational speed N of the first sun gear 1 Is greater than [ Z ] 1 ×(Z 3 +Z 4 )]/(Z 2 ×Z 3 ) A rotation speed N of the first carrier, the second ring gear and the third ring gear 4 Is a forward direction, the rotational speed N of the output member 5 The direction of rotation of (c) is the forward direction.
As a further explanation of the present invention, in the state C, the rotation speed at which the first driving member drives the first sun gear is N 1 The direction of rotation is reverse; the rotating speed of the second driving piece driving the second sun gear is N 2 The steering direction is positive; rotational speed N of the second sun gear 2 And the rotational speed N of the first sun gear 1 Is less than [ Z ] 1 ×(Z 3 +Z 4 )]/(Z 2 ×Z 3 ) A rotation speed N of the first carrier, the second ring gear and the third ring gear 4 Is reversed, the rotational speed N of the output member 5 May be forward or reverse, and in order to prevent this, a one-way stopper is provided on the connected body of the first carrier, the second ring gear and the third ring gear to limit the rotation speed N of the first carrier, the second ring gear and the third ring gear 4 The rotation direction of the output component can only be a forward direction and can not be a reverse direction, so that the rotation speed N of the output component is ensured 5 The steering of (c) is always positive.
As a further explanation of the invention, in state D the rotational speed N at which the first drive drives the first sun gear 1 Is 0; the rotating speed of the second driving piece driving the second sun gear is N 2 The steering direction is positive; rotational speed N of the first carrier, the second gear ring and the third gear ring 4 Is a forward direction, the rotational speed N of the output member 5 The direction of rotation of (c) is the forward direction.
As a further explanation of the invention, in state E the rotational speed N at which the first drive drives the first sun gear 1 And the rotating speed N of the second driving piece driving the second sun wheel 2 The steering directions are all positive directions; rotational speed N of the first carrier, the second gear ring and the third gear ring 4 And said N 1 And said N 2 The steering directions are all positive directions; rotational speed N of the output member 5 And said N 1 、N 2 And N 4 Are the same in size, and the steering is positive.
As a further explanation of the invention, the rotational speed of the second drive member is N when the first drive member fails 2 Xi, the direction of rotation is reverse, and the rotation speed of the second sun wheel is N 2 The rotation speed N of the first carrier, the second ring gear and the third ring gear is in the forward direction 4 There is a tendency of reverse rotation, in which a one-way stopper limits reverse rotation thereof to a rotational speed N of the first carrier, the second ring gear and the third ring gear 4 Is 0, the rotational speed N of the output member 5 The power of the second driving piece is output by the transmission system, the second planet row and the third planet row in a speed reduction and torque increase way with the transmission ratio of i x [ (Z) 3 +Z 4 )×(Z 5 +Z 6 )]/(Z 3 ×Z 5 )。
As a further description of the invention, when the second driving element fails, the first driving element drives the first sun gear at a speed N 1 In the reverse direction, the rotational speed N of the first carrier, the second ring gear and the third ring gear 4 There is a tendency of reverse rotation, in which a one-way stopper limits reverse rotation thereof to a rotational speed N of the first carrier, the second ring gear and the third ring gear 4 Is 0, the rotational speed N of the output member 5 In a forward direction, the firstThe power of a driving piece is output through the first planet row and the third planet row in a speed reduction and torque increase mode, and the transmission ratio is [ Z ] 2 ×(Z 5 +Z 6 )]/(Z 1 ×Z 5 )。
The invention provides a unilateral step-drive three-planet-row stepless speed change mechanism and a speed change method thereof, which change the transmission ratio between an input end and an output end by adjusting the rotating speeds of a first driving piece and a second driving piece and matching the first planet row, the second planet row, a third planet row and a one-way retainer, thereby realizing the stepless speed change of the output end. In addition, the connecting ends of the first driving piece, the second driving piece and the output part are all arranged at one end of the stepless speed change mechanism, so that the input and the output of power are all arranged at one end of the stepless speed change mechanism, the utilization rate of a space can be greatly improved by the design, and the whole power equipment is more reasonable in arrangement and space utilization rate.
Drawings
FIG. 1 is a schematic view of a single-side stepped transmission three-planetary-row continuously variable transmission mechanism provided by an embodiment of the invention;
FIG. 2 is a speed vector diagram for a first planetary gear set in accordance with an embodiment of the present invention;
FIG. 3 is a speed vector diagram for a second planetary row as provided by an embodiment of the present invention;
FIG. 4 is a third planetary row tachometric vector diagram provided in accordance with an embodiment of the present invention;
FIG. 5 is a rotation speed vector diagram provided by the embodiment of the present invention and combining FIG. 2, FIG. 3 and FIG. 4;
FIG. 6 shows the rotational speeds N of the first carrier, the second ring gear and the third ring gear according to the embodiment of the present invention 4 A rotation speed vector diagram when the rotation speed vector diagram is 0;
FIG. 7 shows the rotational speeds N of the first carrier, the second ring gear and the third ring gear according to the embodiment of the present invention 4 A rotation speed vector diagram when less than 0;
FIG. 8 shows the first driver speed N according to an embodiment of the present invention 1 A rotation speed vector diagram when the rotation speed vector diagram is 0;
FIG. 9 is a speed vector diagram illustrating the same speed of the first sun gear and the second sun gear according to an embodiment of the present invention;
FIG. 10 shows the rotational speed N of the first sun gear and the second sun gear according to the embodiment of the present invention 1 And N 2 The steering is a rotating speed vector diagram in the positive direction at the same time;
FIG. 11 shows the rotational speeds N of the first carrier, the second ring gear and the third ring gear under the reverse operating condition provided by the embodiment of the invention 4 A rotation speed vector diagram when the rotation speed vector diagram is 0;
FIG. 12 shows the rotational speeds N of the first carrier, the second ring gear and the third ring gear under the reverse operating condition provided by the embodiment of the invention 4 A rotation speed vector diagram when less than 0;
FIG. 13 shows the rotational speed N of the second sun gear driven by the second driving member when the first driving member fails according to an embodiment of the present invention 2 A rotating speed vector diagram when the steering direction is the forward direction;
FIG. 14 shows the rotational speed N of the first drive member when the second drive member fails according to an embodiment of the present invention 1 And the rotating speed vector diagram when the steering is in the reverse direction.
Reference numerals are as follows:
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-transmission stage, 401-transmission gear a, 402-transmission gear B, 5-one-way stopper, 6-first input shaft, 7-second input shaft, 8-connecting shaft, 9-output member, 10-transmission shaft.
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 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 has the existing problems of complex structure, high manufacturing cost, difficult maintenance and the like, so that a three-planetary-row stepless speed change mechanism with unilateral graded transmission 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 single-side stepped transmission three-planetary-row continuously variable transmission mechanism comprises a first planetary row 1, a second planetary row 2, a third planetary row 3 and a transmission stage 4, wherein the transmission stage 4 comprises a transmission gear a401 and a transmission gear B402, the transmission gear a401 and the transmission gear B402 are meshed through external teeth, a first ring gear 103 on the first planetary row 1 is connected with a second planet carrier 202 on the second planetary row 2, the second planet 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 8, the first planet carrier 102 on the first planetary row 1 is connected with a second ring gear 203 on the second planetary row 2 and a third ring gear 303 on the third planetary row 3, a connecting body of the first planet carrier 102, the second ring gear 203 and the third ring gear 303 is provided with a one-way stopper 5, the third planet carrier 302 on the third planetary row 3 is connected with an output member 9, a transmission shaft 10 connected with the second sun gear 201 on the second planetary row 2 passes through the connecting shaft 202, the third ring gear 301, the third sun gear 302 and the third ring gear 303, the third sun gear 302 is connected with a first planet carrier 2, a driving member 1 is connected with a first planet carrier input driving member 101 and a driving member 101 connected with a first planetary input of the first planetary row 2, a driving member 101, and a driving member 4 connected with a driving member of the first planetary row 2.
Referring to fig. 1, a first sun gear 101 is engaged with first planet gears on outer teeth, the first planet gears are mounted on a first planet carrier 102, and the first planet gears are engaged with inner ring teeth of a first ring gear 103; a second planet wheel is meshed with the outer teeth of the second sun gear 201, is arranged on a second planet carrier 202, and is meshed with the inner ring teeth of a second ring gear 203; the third sun gear 301 is engaged with third planets on its outer teeth, which are mounted on a third carrier 302, and engaged with inner ring teeth of a third ring gear 303.
Referring to fig. 1, the one-way stopper 5 serves to limit the rotational directions of the first carrier 102, the second ring gear 203, and the third ring gear 303, and the one-way stopper 5 makes the rotational directions of the first carrier 102, the second ring gear 203, and the third ring gear 303 coincide with only the turning direction of the second sun gear.
In the following, we need to describe a speed change method of a three-planetary-row stepless speed change mechanism based on single-side stepped transmission by combining with the specific structure of the embodiment of the present invention.
According to the basic principle of the planetary gear, the rotating speeds of three members, namely a sun gear, a ring gear and a planet carrier, of any two members 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 components, namely the sun gear, the ring gear and the planet carrier, is the same, and the rotation speed of the other component 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 N 1 (ii) a The rotation speed of the second driving member is set to N 2 Xi, the rotational speed of the second sun gear 201 is N 2 (ii) a The rotation speeds of the first ring gear 103, the second carrier 202, and the third sun gear 301 are the same, and N is set 3 (ii) a The rotation 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 (ii) a The third carrier 302 and the output member 9 have the same rotational speed, and are set to N 5 (ii) a The number of teeth of the first sun gear 101 is set to Z 1 The number of teeth of the first ring gear 103 is Z 2 The number of teeth of the second sun gear 201 is Z 3 The number of teeth of the second ring gear 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 。
A rotation speed vector diagram of the first planetary row 1 is obtained according to a rotation speed vector calculation method of the planetary gear, as shown in fig. 2. N is a radical of 1 Is the rotational speed of the first sun gear 101, N 3 Is the rotational speed of the first ring gear 103, N 4 Is the rotational speed of the first carrier 102. N is a radical of 1 、N 3 、N 4 The length of (d) represents the magnitude of the rotation speed, the arrow direction represents the rotation speed direction, the arrow direction represents the rotation speed as a forward direction, and the arrow direction represents the rotation speed as a reverse direction. Set L 2 /L 3 ＝Z 1 /Z 2 。
A rotation speed vector diagram of the second planetary row 2 is obtained according to the rotation speed vector calculation method of the planetary gears, as shown in fig. 3. N is a radical of 2 Is the rotational speed, N, of the second sun gear 201 4 Is the rotational speed, N, of the second ring gear 203 3 Is the rotational speed of the second carrier 202. N is a radical of 2 、N 3 、N 4 The length of (d) represents the magnitude of the rotation speed, the arrow direction represents the rotation speed direction, the arrow direction represents the rotation speed as a forward direction, and the arrow direction represents the rotation speed as a reverse direction. Set L 2 /L 1 ＝Z 3 /Z 4 。
A rotation speed vector diagram of the third planetary row 3 is obtained according to the rotation speed vector calculation method of the planetary gears, as shown in fig. 4. N is a radical of 3 Is the rotational speed, N, of the third sun gear 301 4 Is the rotational speed of the third ring gear 303, N 5 Is the rotational speed of the third carrier 302. N is a radical of 3 、N 4 、N 5 The length of (d) represents the magnitude of the rotation speed, the arrow direction represents the rotation speed direction, the arrow direction represents the rotation speed as a forward direction, and the arrow direction represents the rotation speed as a reverse direction. Set L 5 /L 4 ＝Z 5 /Z 6 。
In FIGS. 2, 3 and 4, L 1 、L 2 、L 3 、L 4 、L 5 Only the corresponding proportional relationship needs to be satisfied, L 1 、L 2 、L 3 、L 4 、L 5 Does not affect the calculation of N 1 、N 2 、N 3 、N 4 、N 5 The size of (2). FIG. 5 can be obtained by combining FIG. 2, FIG. 3 and FIG. 4, let L 2 ＝L 4 +L 5 。
See FIG. 5,N 1 Is the rotational speed of the first sun gear 101, i.e. the rotational speed of the first drive member; n is a radical of 2 Is the rotational speed of the second sun gear 201; n is a radical of 3 Is the first gear ring103. The rotational speed of the second carrier 202 and the third sun gear 301; n is a radical of 4 Is the rotational speed of the first carrier 102, the second ring gear 203, and the third ring gear 303; n is a radical of 5 Is the rotational speed of the third planet carrier 302 and the output member 9.
N 1 、N 2 、N 3 、N 4 And N 5 Any two values are determined, and the other three values can be calculated through the proportional relation of line segments in the vector diagram. I.e. the rotational speed N of the first sun gear 101 1 Determining the rotational speed N of the second sun gear 201 2 Determining the rotational speed N of the output member 9 5 And is also uniquely determined. Regulating and controlling the rotational speed N of the first sun gear 101 by means of the first drive element and the second drive element 1 And the rotational speed N of the second sun gear 201 2 The rotational speed N of the output member 9 can be realized 5 Continuously stepless variation of (a).
The speed change principle of the three-planetary-row stepless speed change mechanism with single-side stepped transmission according to the embodiment of the invention is described below by combining specific working conditions.
1. Starting condition
Referring to fig. 5 and 6, at the time of starting, the first driving member drives the first sun gear 101 at the rotating speed N 1 The direction of rotation is reverse; the second driving member drives the second sun gear 201 at a rotating speed N 2 The direction of rotation is the forward direction. The two driving members are simultaneously started to accelerate, and the rotating speed N of the second sun gear 201 is controlled 2 And the rotational speed N of the first sun gear 101 1 Is always greater than (as in FIG. 5) or equal to (as in FIG. 6) [ Z ] 1 ×(Z 3 +Z 4 )]/(Z 2 ×Z 3 ) Control of the rotational speed N of the output member 9 is achieved 5 Gradually accelerate from 0 and turn to the positive direction. Under the working condition, the transmission ratio is maximum, 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
The acceleration and deceleration may be in accordance with the speed N of the first drive member 1 The steering is divided into three cases, which specifically comprise:
1) Situation one
Referring to fig. 5 and 6, firstThe rotating speed of the driving piece driving the first sun gear 101 is N 1 The direction of rotation is reverse, and the second driving member drives the second sun gear 201 at a speed N 2 The direction of rotation is the forward direction. By controlling the speed of rotation N of the second sun gear 201 2 And the rotational speed N of the first sun gear 101 1 Always greater than or equal to [ Z ] 1 ×(Z 3 +Z 4 )]/(Z 2 ×Z 3 ). The rotational speed N of the first sun gear 101 is controlled by the first and second drive elements 1 And the rotational speed N of the second sun gear 201 2 The degree of increase or decrease of (2) can control the rotation speed N of the output member 9 5 The steering direction is the forward direction, so that the vehicle can accelerate or decelerate to run forwards.
2) Situation two
Referring to fig. 8, the first driving member drives the first sun gear 101 at a rotation speed N 1 The magnitude is gradually reduced to 0, and the rotating speed of the second driving piece driving the second sun wheel 201 is N 2 The rotation direction is forward direction by controlling the rotation speed N of the first sun gear 101 1 Is 0 and the rotational speed N of the second sun gear 201 2 The speed of increase and decrease of the speed can realize the output rotating speed N 5 The steering direction is the forward direction, so that the vehicle can accelerate or decelerate to run forwards.
3) Situation three
Referring to fig. 10, the first driving member drives the first sun gear 101 at a rotation speed N 1 The rotation direction is positive, and the second driving member drives the second sun gear 201 at the rotation speed N 2 The direction of rotation is the forward direction. The rotational speed N of the first sun gear 101 is controlled by the first and second drive elements 1 And the rotational speed N of the second sun gear 201 2 The speed of increase and decrease of the speed can realize the output rotating speed N 5 The steering direction is the forward direction, so that the vehicle can accelerate or decelerate to run forwards.
Alternatively, the method of acceleration and deceleration may be adjusted by maintaining the speed N of the first drive member 1 Without change, by adjusting the speed N of the second drive member 2 By the size of xi to regulate the speed N of the output member 9 5 The size of (d); the rotating speed N of the second driving member can be maintained 2 X i isBy adjusting the speed N of the first drive member 1 To adjust the rotational speed N of the output member 9 5 The size of (2). When the rotational speed N of the output member 9 is realized 5 In 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. 9 and 10, the first driving member drives the first sun gear 101 at a rotation speed N 1 The rotation direction is positive, and the second driving member drives the second sun gear 201 at the rotation speed N 2 The direction of rotation is the forward direction. When the rotation speed N of the first sun gear 101 1 And the rotational speed N of the second sun gear 201 2 The rotational speed N of the output member 9 when all reach the maximum rotational speed 5 The maximum speed is also reached, at which time the vehicle speed reaches the maximum vehicle speed. If the rotational speed N of the first sun gear 101 1 And the rotational speed N of the second sun gear 201 2 Is the same, the rotational speed N of the output member 9 5 The maximum rotational speed that can be achieved and the maximum rotational speed N of the first sun gear 101 and the second sun gear 201 1 、N 2 Also, the gear ratio is 1.
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. 7, the rotation speed N when the first driving member drives the first sun gear 101 1 Is reversed, the second driving member drives the rotational speed N of the second sun gear 201 2 The steering of (1) is a forward direction, and the vehicle runs in a starting stage or a medium-low speed stage. If the control of the rotating speeds of the first driving member and the second driving member is inaccurate or fails, the rotating speed N of the second sun gear 201 occurs 2 And the rotational speed N of the first sun gear 101 1 Is less than [ Z ] 1 ×(Z 3 +Z 4 )]/(Z 2 ×Z 3 ) At this time, as shown in FIG. 7, the rotational speed N of the output member 9 5 Can turn toThe reverse condition can occur, and at the moment, the vehicle suddenly runs backwards, so that serious accidents are easy to happen. To prevent this from happening, limiting the speed of rotation N of the first planet carrier 102, the second ring gear 203 and the third ring gear 303 is achieved by providing a one-way stop 5 on the connection body of the first planet carrier 102, the second ring gear 203 and the third ring gear 303 4 The 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 9 5 The direction of turning of (1) is always positive. Therefore, when the dangerous condition occurs, the rotation speed N of the first carrier 102, the second ring gear 203 and the third ring gear 303 is limited due to the one-way stopper 5 4 The rotation direction of the driving member (1) can only be a forward direction and can not be a reverse direction, at the moment, the two driving members can be mutually dragged, and the rotation speed N2 of the second sun gear 201 and the rotation speed N of the first sun gear 101 are 1 Will always be equal to [ Z ] 1 ×(Z 3 +Z 4 )]/(Z 2 ×Z 3 ). Rotational speed N of the first carrier 102, the second ring gear 203 and the third ring gear 303 4 Equal to 0, the rotation speed N5 of the output member 9 can be steered only in the forward direction, so that a reverse travel does not suddenly occur.
4. Working condition of backing car
Referring to fig. 11 and 12, when the vehicle is reversed, the first driving member drives the first sun gear 101 at a rotation speed N 1 The rotation direction is positive, and the second driving member drives the second sun gear 201 at the rotation speed N 2 The direction of rotation is reversed. The two driving members are simultaneously started to accelerate, and the rotating speed N of the second sun gear 201 is controlled 2 And the rotational speed N of the first sun gear 101 1 Is always greater than (as in FIG. 12) or equal to (as in FIG. 11) [ Z ] 1 ×(Z 3 +Z 4 )]/(Z 2 ×Z 3 ) Control of the rotational speed N of the output member 9 is achieved 5 Gradually accelerate from 0 and turn to reverse. If the control of the rotating speeds of the first driving member and the second driving member is inaccurate or fails, the rotating speed N of the second sun gear 201 occurs 2 And the rotational speed N of the first sun gear 101 1 Is less than [ Z ] 1 ×(Z 3 +Z 4 )]/(Z 2 ×Z 3 ) The rotational speed N of the output member 9 5 The steering may be in a forward direction, in which case the vehicle suddenly travels forwardSerious accidents are easy to happen. In order to prevent this, the rotation speed N of the first carrier 102, the second ring gear 203 and the third ring gear 303 is limited by providing a one-way stopper 5 on the connecting body of the first carrier 102, the second ring gear 203 and the third ring gear 303 4 The direction of rotation of (1) can only be reverse direction, but not forward direction. This ensures the rotational speed N of the output member 9 5 The direction of rotation of (c) is always reversed.
In addition to the above normal working conditions and dangerous working conditions, some emergency working conditions need to be dealt with, and the embodiments of the invention take the same into consideration and solve the problem.
Example (c): referring to FIG. 13, when the first driver fails, the second driver has a speed N 2 Xi, forward direction, speed N of the first carrier 102, the second ring gear 203 and the third ring gear 303 4 There is a tendency of reverse rotation in which the one-way stopper 5 restricts reverse rotation to rotate the rotational speed N of the first carrier 102, the second ring gear 203, and the third ring gear 303 4 0, rotational speed N of the output member 9 5 The power of the second driving piece is output by the transmission stage, the second planet row 2 and the third planet row 3 in a speed reduction and torque increase way with the transmission ratio of i x [ (Z) 3 +Z 4 )×(Z 5 +Z 6 )/Z 3 ×Z 5 ]So that the vehicle can continue to accelerate or decelerate forward.
Referring to FIG. 14, when the second driver fails, the first driver has a speed of N 1 The rotation speed N of the first carrier 102, the second ring gear 203 and the third ring gear 303 is reversed 4 There is a tendency of reverse rotation, in which the one-way stopper 5 restricts the reverse rotation to rotate the rotational speed N of the first carrier 102, the second ring gear 203 and the third ring gear 303 4 0, rotational speed N of the output member 9 5 The power of the first driving piece is output through the first planet row 1 and the third planet row 3 in a speed reduction and torque increase mode in the positive direction, and the transmission ratio is [ Z ] 2 ×(Z 5 +Z 6 )]/(Z 1 ×Z 5 ) So that the vehicle can continue to accelerate or decelerate forward.
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 embodiment of the invention provides a unilateral stepped transmission three-planet-row stepless speed change mechanism and a speed change method thereof, which have the following advantages:
1. the unilateral-graded-transmission three-planet-row 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 unilateral stepped transmission three-planet-row stepless speed change mechanism can realize that the output end has large torque from low speed to high speed, the vehicle has the capability of quickly accelerating starting when driving by outputting the large torque, the large torque can climb a larger slope when climbing, the large torque can also meet the requirements of more people, and the vehicle using area of the product is larger.
3. The unilateral-graded-transmission three-planet-row stepless speed change mechanism can realize stepless continuous change of output rotating speed, the driving piece at 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 unilateral-graded-transmission three-planet-row 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 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 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 unilateral stepped transmission three-planet-row stepless speed change mechanism has high transmission rate, a motor with lower power and lower rotating speed can be selected as a 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 unilateral stepped transmission three-planet-row stepless speed change mechanism adopts three-planet-row transmission, increases the transmission ratio, further increases the torque, can be applied to heavy trucks such as trucks, muck trucks and buses with larger loads, and further widens the application range of the embodiment of the invention.
9. According to the unilateral-graded-transmission three-planet-row stepless speed change mechanism, the connecting ends of the first driving piece, the second driving piece and the output part 9 are all arranged at one end of the stepless speed change mechanism, so that power is input and output at one end of the stepless speed change mechanism, the design can greatly improve the space utilization rate, and the whole power equipment is more reasonable in arrangement and space utilization rate.
10. The single-side stepped transmission three-planet-row stepless speed change mechanism provided by the embodiment of the invention is characterized in that the transmission stage 4 is arranged between the second input shaft 7 and the transmission shaft 10, and the transmission stage 4 achieves the purpose of changing the transmission ratio between the second driving piece and the second sun gear 201 by changing the gear ratio of the transmission gear A401 and the transmission gear B402, so that the transmission ratio provided by the transmission stage 4 widens the power selection range of the second driving piece on the premise of achieving the same use effect.
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 unilateral stepped transmission three-planet-row stepless speed change mechanism is characterized by comprising a first planet row (1), a second planet row (2), a third planet row (3) and a transmission stage (4), wherein the transmission stage (4) comprises a transmission gear A (401) and a transmission gear B (402), the transmission gear A (401) and the transmission gear B (402) are meshed through external teeth, a first gear ring (103) on the first planet row (1) is connected with a second planet carrier (202) on the second planet row (2), the second planet carrier (202) is connected with a third sun gear (301) on the third planet row (3) through a connecting shaft (8), a first planet carrier (102) on the first planet row (1) is connected with a second gear ring (203) on the second planet row (2) and a third gear ring (303) on the third planet row (3), the first planet carrier (102), the second gear ring (203) and the third gear ring (303) on the third planet row (3) are connected, a unidirectional output connector (9) of the third planet carrier (201) penetrates through a second planet carrier (2), and a second planet carrier (2) output connector (9) on the third planet carrier (2) is connected with a second planet carrier (201) output connector (9), the connecting shaft (8), the third sun gear (301), the third planet carrier (302) and the output component (9) are connected with the transmission gear B (402), a first input shaft (6) connected with a first sun gear (101) on the first planet row (1) penetrates through the second sun gear (201), the transmission shaft (10) and the transmission gear B (402) to be connected with a first driving piece, and the transmission gear A (401) is connected with a second driving piece through a second input shaft (7).
2. The single-sided step-geared three-planetary-row continuously variable transmission according to claim 1, wherein the first sun gear (101) is engaged with a first planetary gear on external teeth, the first planetary gear is mounted on the first carrier (102), and the first planetary gear is engaged with internal ring teeth of the first ring gear (103);
the second sun gear (201) is meshed with a second planet gear on external teeth, the second planet gear is arranged on the second planet carrier (202), and the second planet gear is meshed with internal ring teeth of the second ring gear (203);
and a third planet wheel is meshed with the external teeth of the third sun gear (301), is arranged on the third planet carrier (302), and is meshed with the inner ring teeth of the third gear ring (303).
3. The single-sided step-geared three planetary gear set continuously variable transmission according to claim 1, wherein the one-way stopper (5) is configured to limit the rotational directions of the first carrier (102), the second ring gear (203), and the third ring gear (303), and the one-way stopper (5) makes the rotational directions of the first carrier (102), the second ring gear (203), and the third ring gear (303) coincide with only the steering of the second sun gear (201) to which the second drive is connected.
4. A speed change method of a three-planetary-row stepless speed change mechanism based on single-side stepped transmission is characterized in that a first driving piece and a first sun gear (101) are connected through a first input shaft (6), so that the rotating speed of the first driving piece is the same as that of the first sun gear (101); the second driving piece is connected with the second sun gear (201) through a second input shaft (7), a transmission stage (4) and a transmission shaft (10), so that the rotating speed of the second driving piece and the rotating speed of the second sun gear (201) form a transmission proportional relation of the transmission stage (4); the first planet carrier (102), the second gear ring (203) and the third gear ring (303) are connected, so that the rotating speeds of the first planet carrier (102), the second gear ring (203) and the third gear ring (303) are the same; a first gear ring (103), a second planet carrier (202) and a 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 (9) is connected with the third planet carrier (302), so that the rotating speeds of the third planet carrier (302) and the output component (9) are the same; the rotational speed of the first drive element and the rotational speed of the second drive element are controlled in a regulated manner, so that a continuously variable change of the rotational speed of the output element (9) is achieved, in which process the speed ratio is correspondingly changed.
5. The speed change method of a three planetary gear set continuously variable transmission mechanism based on one-sided step transmission according to claim 4, characterized in that: the rotating speed of the first driving part and the rotating speed of the first sun gear (101) are N 1 The rotation speed of the second sun gear (201) is N 2 The transmission ratio of the transmission stage (4) is i, and the rotating speed of the second driving piece is N 2 Xi, the rotation speed of the first ring gear (103), the second planet carrier (202) and the third sun gear (301) is N 3 The rotational speeds of the first carrier (102), the second ring gear (203) and the third ring gear (303) are N 4 The third planet carrier (302) and the output member (9) have a rotational speed N 5 The number of teeth of the first sun gear (101) is Z 1 The number of teeth of the first ring gear (103) is Z 2 The number of teeth of the second sun gear (201) is Z 3 The number of teeth of the second ring gear (203) is Z 4 The number of teeth of the third sun gear (301) is Z 5 The number of teeth of the third gear ring (303) is Z 6 When said N is 1 、N 2 、N 3 、N 4 And N 5 When any two values in the vector diagram are determined, the other three values can be calculated through the proportional relation of line segments in the vector diagram; regulating and controlling the rotational speed N of the first sun gear (101) by driving the first and second drive elements 1 And the rotational speed N of the second sun gear (201) 2 The rotational speed N of the output member (9) can be realized 5 Continuous stepless variation of (2); controlling the rotational speed N of the first sun gear (101) by regulation 1 And the rotational speed N of the second sun gear (201) 2 The 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 method for changing the speed of a three planetary gear set continuously variable transmission mechanism according to claim 5, wherein in the state A, the first driving member drives the first sun gear (101) at a speed N 1 The direction of rotation is reverse; the second driving piece drives the second sun gear (201) to rotate at a speed of N 2 The steering direction is positive; rotational speed N of the second sun gear (201) 2 And the rotational speed N of the first sun gear (101) 1 Is equal to [ Z ] 1 ×(Z 3 +Z 4 )]/(Z 2 ×Z 3 ) A rotational speed N of the first carrier (102), the second ring gear (203) and the third ring gear (303) 4 Is 0, the rotational speed N of the output member (9) 5 The direction of rotation of (c) is the forward direction.
7. The method for changing the speed of a three planetary gear set continuously variable transmission mechanism according to claim 5, wherein in state B, the first driving member drives the first sun gear (101) at a speed N 1 The direction of rotation is reverse; the second driving piece drives the second sun gear (201) to rotate at a speed of N 2 The steering direction is positive; rotational speed N of the second sun gear (201) 2 And the rotational speed N of the first sun gear (101) 1 Is greater than [ Z1X (Z3 + Z4) ]](Z2 xZ 3), the rotational speed N of the first carrier (102), the second ring gear (203) and the third ring gear (303) 4 Is a forward direction, the rotational speed N of the output member (9) 5 The direction of rotation of (c) is the forward direction.
8. The method for changing the speed of a three planetary gear set continuously variable transmission mechanism according to claim 5, wherein in the state C, the first driving member drives the first sun gear (101) at a speed N 1 The direction of rotation is reverse; the second driving piece drives the second sun gear (201) to rotate at a speed of N 2 The steering direction is positive; rotational speed N of the second sun gear (201) 2 And the first sun gear (1)01 Rotational speed N of 1 Is less than [ Z ] 1 ×(Z 3 +Z 4 )]/(Z 2 ×Z 3 ) A rotational speed N of the first carrier (102), the second ring gear (203) and the third ring gear (303) 4 Is reversed, the rotational speed N of the output member (9) 5 In order to prevent the situation from happening, a one-way stopper (5) is arranged on the connecting body of the first planet carrier (102), the second gear ring (203) and the third gear ring (303) to limit the rotating speed N of the first planet carrier (102), the second gear ring (203) and the third gear ring (303) 4 Can only be in a forward direction but not in a reverse direction, thus ensuring the rotating speed N of the output part (9) 5 The steering of (c) is always positive.
9. The method for changing the speed of a three planetary gear set continuously variable transmission mechanism according to claim 5, wherein in state D, the first driver drives the first sun gear (101) at a speed N 1 Is 0; the second driving piece drives the second sun gear (201) at a rotating speed N 2 The steering direction is positive; a rotational speed N of the first carrier (102), the second ring gear (203) and the third ring gear (303) 4 Is a forward direction, the rotational speed N of the output member (9) 5 The direction of rotation of (c) is the forward direction.
10. The method for changing the speed of a three planetary gear set continuously variable transmission mechanism according to claim 5, wherein in state E the first driver drives the first sun gear (101) at a speed N 1 And a rotational speed N at which the second drive drives the second sun gear (201) 2 The steering directions are all positive directions; a rotational speed N of the first carrier (102), the second ring gear (203) and the third ring gear (303) 4 And said N 1 And said N 2 The steering directions are all positive directions; rotational speed N of the output member (9) 5 And said N 1 、N 2 And N 4 Are the same in size, and the steering is positive.
11. The method of claim 5, wherein the second driver has a speed N when the first driver fails 2 Xi, the direction of rotation is reverse, the rotational speed of the second sun gear (201) is N 2 The rotation speed N of the first carrier (102), the second ring gear (203) and the third ring gear (303) in the forward direction 4 The reverse rotation trend is existed, the reverse rotation of the first planet carrier (102), the second gear ring (203) and the third gear ring (303) is limited by a one-way stopper (5) at the time, and the rotating speed N of the first planet carrier, the second gear ring (203) and the third gear ring (303) is enabled to be 4 0, the rotational speed N of the output member (9) 5 The power of the second driving piece is output in a speed reducing and torque increasing mode through the transmission stage (4), the second planet row (2) and the third planet row (3) in a forward direction, and the transmission ratio is i x [ (Z) 3 +Z 4 )×(Z 5 +Z 6 )]/(Z 3 ×Z 5 )。
12. The method for changing the speed of a three planetary gear set continuously variable transmission mechanism according to claim 5, wherein when the second driving element fails, the first driving element drives the first sun gear (101) at a speed N 1 In the opposite direction, the rotational speed N of the first carrier (102), the second ring gear (203) and the third ring gear (303) 4 The reverse rotation trend is existed, the reverse rotation of the first planet carrier (102), the second gear ring (203) and the third gear ring (303) is limited by a one-way stopper (5) at the time, and the rotating speed N of the first planet carrier, the second gear ring (203) and the third gear ring (303) is enabled to be 4 Is 0, the rotational speed N of the output member (9) 5 The power of the first driving piece is output in a speed reducing and torque increasing way through the first planet row (1) and the third planet row (3) in a transmission ratio of Z 2 ×(Z 5 +Z 6 )]/(Z 1 ×Z 5 )。
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| CN202110996661.4A CN115727105A (en) | 2021-08-27 | 2021-08-27 | Unilateral-staged-transmission three-planet-row stepless speed change mechanism and speed change method thereof |
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