CN115727107A - Dual-drive three-planet-row stepless speed change mechanism and speed change method thereof - Google Patents
Dual-drive three-planet-row stepless speed change mechanism and speed change method thereof Download PDFInfo
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- CN115727107A CN115727107A CN202110998309.4A CN202110998309A CN115727107A CN 115727107 A CN115727107 A CN 115727107A CN 202110998309 A CN202110998309 A CN 202110998309A CN 115727107 A CN115727107 A CN 115727107A
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Abstract
The invention discloses a dual-drive three-planet-row stepless speed change mechanism, which belongs to the technical field of stepless speed changers and comprises a first planet row, a second planet row and a third planet row, wherein a first gear ring on the first planet row is connected with a second planet carrier on the second planet row, the second planet carrier is connected with a third sun gear on the third planet row through a connecting shaft, a first planet carrier on the first planet row is connected with a second gear ring on the second planet row and a third gear ring on the third planet row, and a connector of the first planet carrier, the second gear ring and the third gear ring is provided with a one-way stopper. The invention also discloses a speed change method of the double-drive three-planet-row stepless speed change mechanism. The driving piece at the input end of the stepless speed change mechanism can work in a high-efficiency area all the time, stepless speed change of the output end is realized, and the mechanism has 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.
Description
Technical Field
The invention relates to the technical field of continuously variable transmissions, in particular to a dual-drive 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, so that the accurate gear shifting time is difficult to master, and the problems of high energy consumption and low efficiency exist; the AMT transmission has the disadvantages of complex structure, high manufacturing cost and difficult maintenance.
Disclosure of Invention
The invention aims to solve the problems and designs a double-drive three-planet-row stepless speed change mechanism and a speed change method thereof.
The technical scheme of the invention is that the dual-drive three-planet-row stepless speed change mechanism comprises a first planet row, a second planet row and a third planet row, wherein a first gear ring on the first planet row is connected with a second planet carrier on the second planet row, the second planet carrier is connected with a third sun gear on the third planet row through a connecting shaft, a first planet carrier on the first planet row is connected with a second gear ring on the second planet row and a third gear ring on the third planet row, a connecting body of the first planet carrier, the second gear ring and the third gear ring is provided with a one-way stopper, a third planet carrier on the third planet row is connected with an output component, a first sun gear on the first planet row is connected with a first driving piece through a first input shaft, and a second input shaft connected with a second sun gear on the second planet row penetrates through the first sun gear, the first input shaft and the first driving piece to be connected with a second driving piece.
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 engaged with a third planet gear, the third planet gear is arranged on the third planet carrier, and the third planet gear is engaged with the inner ring teeth of the third gear ring.
As a further explanation of the present invention, the one-way stopper is for limiting a rotational direction of the first carrier, the second ring gear, and the third ring gear, and the one-way stopper makes the rotational direction of the first carrier, the second ring gear, and the third ring gear coincide with only a steering direction of the second driver.
The invention also provides a speed change method based on the dual-drive three-planet-row stepless speed change mechanism, wherein a first driving piece and a first sun gear are connected through a first input shaft, so that the rotating speed of the first driving piece is the same as that of the first sun gear; the second driving piece and the second sun gear are connected through a second input shaft, so that the rotating speed of the second driving piece is the same as that of the 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 rotating 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 rotating speeds of the third planet carrier and the output component 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 part and the rotating speed of the first sun gear are N 1 The rotating speed of the second driving piece and the rotating speed of the second sun wheel are N 2 The rotation speed of the first gear ring, the second planet carrier and the third sun gear is N 3 The rotation speed of the first planet carrier, the second gear ring and the third gear ring is N 4 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; by regulating the speed N of the first drive member 1 And the rotational speed N of the second drive member 2 The rotational speed N of the output member can be realized 5 Continuous stepless variation of (2); by regulating the speed N of the first drive member 1 And the rotational speed N of the second drive member 2 The output states of the output member are made to include a state a, a state B, a state C, a state D, and a state E.
As a further elaboration of the invention, in state a the rotational speed N of the first drive element is 1 Is reversed, the rotational speed N of the second drive member 2 Is in the forward direction, the rotational speed N of the second drive member 2 And the rotational speed N of the first drive member 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 elaboration of the invention, in state B the rotational speed N of the first drive element is 1 Is reversed, the rotational speed N of the second drive 2 Is in the forward direction, the rotational speed N of the second drive member 2 And the rotational speed N of the first drive member 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 elaboration of the invention, in the state C the rotational speed N of the first drive is 1 Is reversed, the rotational speed N of the second drive 2 Is in the forward direction, the rotational speed N of the second drive member 2 And the rotational speed N of the first drive member 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 in a forward direction and a reverse direction, 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 rotational 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 direction of turning of (1) is always positive.
As a further elaboration of the invention, in state D the rotational speed N of the first drive element 1 0, the rotational speed N of the second drive member 2 Is a forward direction, the rotational 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 elaboration of the invention, in state E the rotational speed N of the first drive element is 1 And the rotational speed N of the second drive member 2 Are the same, the steering is forward, and the rotating speeds N of the first planet carrier, the second gear ring and the third gear ring are all positive 4 And said N 1 And said N 2 The rotation directions are positive directions with the same size, and the rotation speed N of the output part 5 And said N 1 、N 2 And N 4 Is the same, the steering is positive, and the transmission ratio of the state E is 1.
As a further explanation of the invention, the rotational speed of the second drive member is N when the first drive member fails 2 The rotation speed N of the first carrier, the second ring gear and the third ring gear is positive 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 through the second planet row and the third planet row in a speed reduction and torque increase mode in a positive direction, and the transmission ratio is [ (Z) 3 +Z 4 )×(Z 5 +Z 6 )]/(Z 3 ×Z 5 )。
As a further explanation of the invention, when the second driver fails, the first driver has 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 the one-way stopper restricts reverse rotation to the rotational speed N of the first carrier, the second ring gear and the third ring gear 4 0, rotational speed N of the output member 5 The power of the first driving piece is output through the first planet row and the third planet row in a speed reduction and torque increase mode in a positive rotation mode, and the transmission ratio is [ (Z) 3 +Z 4 )×(Z 5 +Z 6 )]/(Z 3 ×Z 5 )。
The invention provides a double-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 speed 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, realize the stepless speed change of the output end, and have the advantages of high transmission efficiency, large output torque, no power interruption, simple and reliable structure, low manufacturing cost, easy maintenance, simple and convenient speed regulation and the like.
Drawings
FIG. 1 is a schematic view of a dual-drive three-planetary-row continuously variable transmission mechanism provided by an embodiment of the present 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 vector diagram illustrating the rotational speed of the second planetary gear set in accordance with 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 0;
FIG. 9 is a speed vector diagram illustrating the same speed of the first and second drivers provided by an embodiment of the present invention;
FIG. 10 shows the rotational speed N of the first and second drivers according to an 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 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:
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-one-way stopper, 5-first input shaft, 6-second input shaft, 7-connecting shaft, 8-output member.
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, the accurate gear shifting time is difficult to master, and the problems of high energy consumption and low efficiency exist; the AMT transmission has the existing problems of complex structure, high manufacturing cost, difficult maintenance and the like, so a dual-drive three-planet-row stepless speed change mechanism is provided to solve the existing problems.
The following describes embodiments of the present invention with reference to the accompanying drawings, and first introduces specific structures of the embodiments of the present invention.
Referring to fig. 1, a dual-drive three-planet-row continuously variable transmission mechanism includes a first planet row 1, a second planet row 2 and a third planet row 3, a first ring gear 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 on the second planet row 2 is connected with a third sun gear 301 on the third planet row 3 through a connecting shaft 7, a first planet carrier 102 on the first planet row 1 is connected with a second ring gear 203 on the second planet row 2 and a third ring gear 303 on the third planet row 3, a one-way stopper 4 is arranged on a connecting body of the first planet carrier 102, the second ring gear 203 and the third ring gear 303, a third planet carrier 302 on the third planet row 3 is connected with an output member 8, the first sun gear 101 on the first planet row 1 is connected with a first driving member through a first input shaft 5, and a second input shaft 6 connected with a second sun gear 201 on the second planet row 2 passes through the first sun gear 101, the first input shaft 5 and the first driving member and the second driving member.
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 4 is used to limit the rotational direction 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 direction 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 driver.
In the following, we need to describe a speed change method based on a dual-drive three-planet-row stepless speed change mechanism by combining 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, if the rotating speeds 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 speeds of any two of the three components of the sun gear, the ring gear and the planet carrier are 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 rotational speed of the second driving member is the same as the rotational speed of the second sun gear 201, and is set to 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 8 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 Of the first ring gear 103Number of teeth being 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 line 2 is obtained according to a 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 hydrogen 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 (b) represents 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 actual length ofCalculating N 1 、N 2 、N 3 、N 4 、N 5 Of (c) is used. 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 hydrogen 2 Is the rotational speed of the second sun gear 201, i.e., the rotational speed of the second driving member; n is a radical of 3 Is the rotational speed of the first ring gear 103, the second carrier 202, and the third sun gear 301; n is a radical of hydrogen 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 hydrogen 5 Is the rotational speed of the third planet carrier 302 and the output member 8.
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 drive member 1 Determining the rotational speed N of the second drive element 2 Determining the rotational speed N of the output member 8 5 And is also uniquely determined. Controlling the speed N of the first drive member by regulation 1 And the rotational speed N of the second drive member 2 The rotational speed N of the output member 8 can be realized 5 Continuously stepless variation of (a).
The following describes the speed change principle of the dual-drive three-planet-row stepless speed change mechanism according to the embodiment of the invention with reference to specific working conditions.
1. Starting condition
With reference to fig. 5 and 6, the rotational speed N of the first drive member at take-off 1 The rotational speed N of the second drive member being reversed 2 The direction of rotation is the forward direction. The two driving parts are started and accelerated at the same time by controlling the rotating speed N of the second driving part 2 And the rotational speed N of the first drive member 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 8 can be achieved 5 The acceleration is gradually increased from 0, and the direction is changed to the positive direction. Under the working condition, the transmission ratio is maximum, the power of the first driving part and the power of the second driving part are coupled together, and the vehicle is decelerated and torque-increased to be output, so that the vehicle can accelerate to run 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, the rotational speed N of the first driver 1 Is reversed, the rotational speed N of the second drive member 2 The direction of rotation of (c) is the forward direction. Rotational speed N of the second drive member 2 And the rotational speed N of the first drive member 1 Always greater than or equal to [ Z ] 1 ×(Z 3 +Z 4 )]/(Z 2 ×Z 3 ). By controlling the speed N of the first drive member 1 And the rotational speed N of the second drive member 2 By increasing or decreasing the speed, the rotational speed N of the output member 8 can be controlled 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 rotational speed N of the first driver 1 Is gradually reduced to 0, the rotating speed N of the second driving part 2 The direction of rotation is forward, by controlling the speed of rotation N of the first drive member 1 Is 0 and the rotational speed N of the second driving member 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 rotational speed N of the first driver 1 Is in the forward direction, the rotational speed N of the second drive member 2 The direction of rotation of (c) is the forward direction. By controlling the speed N of the first drive member 1 And the rotational speed N of the second drive member 2 The speed increase and decrease degree of (2) can realize the output of the rotating speed N 5 The steering direction is the positive direction, so that the vehicle is accelerated or decelerated 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 To adjust the rotational speed N of the output member 8 5 The size of (d); the second drive can be maintainedRotational speed N of a member 2 Without change, by adjusting the speed N of the first drive member 1 To adjust the rotational speed N of the output member 8 5 The size of (2). At the speed N of the output member 8 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 rotational speed N of the first driver 1 Is positive, the rotational speed N of the second drive 2 The direction of rotation of (c) is the forward direction. When the rotating speed N of the first driving member 1 And the rotational speed N of the second drive member 2 At all times of maximum speed, the speed N of the output member 8 5 The maximum speed is also reached, at which time the vehicle speed reaches the maximum vehicle speed. If the rotating speed N of the first driving member 1 And the rotational speed N of the second drive member 2 Is the same, the rotational speed N of the output member 8 is then 5 The maximum speed that can be reached and the maximum speed N of the first and second drive elements 1 、N 2 Also, the gear ratio is 1.
Aiming at the starting working condition and the acceleration and deceleration working condition, the dangerous working condition needs to be avoided by considering.
Example (c): referring to FIG. 7, when the first driving member rotates at a speed N 1 Is reversed, the rotational speed N of the second drive member 2 The steering direction of the first driving part and the second driving part is positive, and when the vehicle runs in a starting stage or a middle and low speed stage, if the control of the rotating speeds of the first driving part and the second driving part is inaccurate or fails, the rotating speed N of the second driving part occurs 2 And the rotational speed N of the first drive member 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 8 5 The steering may be in a reverse direction, and at the moment, the vehicle suddenly runs backwards, so that serious accidents are easy to happen. To prevent fromTo stop this, the rotation speed N of the first planet carrier 102, the second ring gear 203 and the third ring gear 303 is limited by providing a one-way stopper 4 on the connecting 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 forward direction, but can not be reverse direction. This ensures that the rotational speed N of the output member 8 is maintained 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 4 4 The steering can only be in a forward direction and can not be in a reverse direction, at the moment, the two driving pieces can be mutually dragged, and the rotating speed N of the second driving piece 2 And the rotational speed N of the first drive member 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, rotational speed N of the output member 8 5 The steering of (2) can only be in the forward direction, so that the reverse driving cannot happen suddenly.
4. Working condition of backing car
Referring to fig. 11 and 12, the rotational speed N of the first driving member when reversing 1 Speed N of the second drive member when the steering is in the forward direction 2 The direction of rotation is reversed. The two driving parts are started and accelerated at the same time by controlling the rotating speed N of the second driving part 2 And the rotational speed N of the first drive member 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 8 can be achieved 5 Gradually accelerate from 0 and turn to reverse. If the control of the rotating speeds of the first driving part and the second driving part is inaccurate or fails, the rotating speed N of the second driving part occurs 2 And the rotational speed N of the first drive member 1 Is less than [ Z ] 1 ×(Z 3 +Z 4 )]/(Z 2 ×Z 3 ) At the speed N of the output member 8 5 The steering may be in a forward direction, and at this time, the vehicle suddenly runs forward, so that a serious accident is easy to happen. In order to prevent this, a one-way stopper is arranged on the connecting body of the first planet carrier 102, the second ring gear 203 and the third ring gear 303Actuator 4, to limit the speed N of the first planet carrier 102, the second ring gear 203 and the third ring gear 303 4 Can only be in reverse direction, but not in forward direction, thus ensuring the rotation speed N of the output member 8 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 The rotation speed N of the first carrier 102, the second ring gear 203, and the third ring gear 303, which are steered in the forward direction 4 There is a tendency of reverse rotation in which the one-way stopper 4 restricts reverse rotation thereof 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 8 5 The power of the second driving piece is output by the second planet row 2 and the third planet row 3 in a speed reduction and torque increase way with the transmission ratio of [ (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 rotates at a speed N 1 The direction of rotation is reversed, and the rotational speed N of the first carrier 102, the second ring gear 203, and the third ring gear 303 is 4 There is a tendency of reverse rotation, in which the one-way stopper 4 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 8 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, although the power is reduced, the vehicle can be driven to a maintenance place or a safe place by one driving part, and the reliability of the vehicle can be greatly improved.
The embodiment of the invention provides a dual-drive three-planet-row stepless speed change mechanism and a speed change method thereof, which have the following advantages:
1. the dual-drive 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 dual-drive 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 to start when driving by outputting the large torque, the large torque can climb a larger slope when the vehicle climbs, and the large torque can also meet the vehicle using requirements of more people, so that the audience area of the product is larger.
3. The dual-drive 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 dual-drive 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 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 dual-drive three-planet-row stepless speed change mechanism has high transmission rate, the motor with lower power and lower rotating speed can be selected as the driving element 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 dual-drive 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, buses and the like with larger load, and further widens the application range of the embodiment of the invention.
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 double-drive three-planet-row stepless speed change mechanism is characterized by comprising a first planet row (1), a second planet row (2) and a third planet row (3), a first ring gear (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 (7), a first planet carrier (102) on the first planet row (1) is connected with a second ring gear (203) on the second planet row (2) and a third ring gear (303) on the third planet row (3), a one-way stopper (4) is arranged on a connecting body of the first planet carrier (102), the second gear ring (203) and the third gear ring (303), the third planet carrier (302) on the third planet 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 element through a first input shaft (5), the second input shaft (6) connected with the second sun gear (201) on the second planet row (2) passes through the first sun gear (101), the first input shaft (5) and the first driving piece to be connected with a second driving piece.
2. The dual-drive three-planetary-row continuously variable transmission according to claim 1, wherein a first planetary gear is engaged with an external tooth of the first sun gear (101), the first planetary gear is mounted on the first carrier (102), and the first planetary gear is engaged with an internal ring tooth 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 dual drive three planetary gear continuously variable transmission according to claim 1, wherein the one-way stopper (4) is used 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 (4) makes the rotational directions of the first carrier (102), the second ring gear (203), and the third ring gear (303) coincide with the rotational direction of the second driving member only.
4. A speed change method based on a dual-drive three-planet-row stepless speed change mechanism is characterized in that a first driving piece and a first sun gear (101) are connected through a first input shaft (5), 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 and the second sun gear (201) are connected through a second input shaft (6), so that the rotating speed of the second driving piece is the same as that 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 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 part (8) is connected with the third planet carrier (302) so that the rotating speeds of the third planet carrier (302) and the output part (8) are the same; by controlling the rotational speed of the first drive element and the rotational speed of the second drive element in a regulated manner, a continuously variable change of the rotational speed of the output element (8) is achieved, in which process the speed ratio is also correspondingly changed.
5. The speed change method based on the dual-drive three-planetary-row continuously variable transmission mechanism according to claim 4, characterized by setting: the rotational speed of the first driving member and the rotational 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 wheel (201) are N 2 The rotation speed of the first gear ring (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 (8) 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 ring gear (303) is Z 6 When said N is 1 、N 2 、N 3 、N 4 And N 5 When any two values are determined, the other three values can be calculated through the proportional relation of line segments in the vector diagram; controlling the speed N of the first drive member by regulation 1 And rotation of the second driving memberSpeed N 2 The rotational speed N of the output member (8) can be realized 5 Continuous stepless variation of (2); by regulating the speed N of the first drive member 1 And the rotational speed N of the second drive member 2 The output state of the output member (8) is made to include a state A, a state B, a state C, a state D and a state E.
6. The method for shifting a dual drive three planetary gear set continuously variable transmission mechanism according to claim 5, wherein in the state A, the rotational speed N of the first driving member is 1 Is reversed, the rotational speed N of the second drive 2 The direction of rotation of said second drive member is positive, the rotational speed N of said second drive member 2 And the rotational speed N of the first drive member 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 (8) 5 The direction of rotation of (c) is the forward direction.
7. The method according to claim 5, wherein in the state B, the speed N of the first driving member is equal to or higher than the speed N of the second driving member 1 Is reversed, the rotational speed N of the second drive member 2 The direction of rotation of said second drive member is positive, the rotational speed N of said second drive member 2 And the rotational speed N of the first drive member 1 Is greater 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 The direction of rotation being forward, the speed of rotation N of the output member (8) 5 The direction of rotation of (c) is the forward direction.
8. The method of claim 5, wherein in state C, the speed N of the first driver is greater than the speed N of the second driver 1 Is reversed, the rotational speed N of the second drive member 2 Is in the forward direction, saidRotational speed N of the second drive member 2 The ratio of the rotation speed N1 of the first driving member to the rotation speed N1 of the first driving member 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 (8) 5 In order to prevent the situation from happening, a one-way stop dog (4) 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 the forward direction but not in the reverse direction, thus ensuring the rotating speed N of the output component (8) 5 The direction of turning of (1) is always positive.
9. The method according to claim 5, wherein in the state D, the rotational speed N of the first driving member is equal to or greater than the rotational speed N of the second driving member 1 Is 0, the rotational speed N of the second driving member 2 Is a forward direction, the rotational speed N of the first carrier (102), the second ring gear (203) and the third ring gear (303) being 4 Is a forward direction, the rotational speed N of the output member (8) 5 The direction of rotation of (c) is the forward direction.
10. The method according to claim 5, wherein in the state E, the speed N of the first driving member is higher than the speed N of the second driving member 1 And the rotational speed N of the second drive member 2 Are all in a forward direction, and the rotational speeds 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 same size, the rotation directions are positive, and the rotating speed N of the output part (8) 5 And said N 1 、N 2 And N 4 Is the same, the steering is positive, and the transmission ratio of the state E is 1.
11. The method of claim 5The speed change method based on the dual-drive three-planet-row stepless speed change mechanism is characterized in that when the first driving piece fails, the rotating speed of the second driving piece is N 2 The rotation speed N of the first carrier (102), the second ring gear (203), and the third ring gear (303) is positive 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 (4) 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 (8) 5 The power of the second driving piece is output through the second planet row (2) and the third planet row (3) in a speed reduction and torque increase way with the transmission ratio of [ (Z) 3 +Z 4 )×(Z 5 +Z 6 )]/(Z 3 ×Z 5 )。
12. The speed change method based on the dual-drive three-planetary-row continuously variable transmission mechanism according to claim 5, wherein when the second driving element fails, the rotating speed of the first driving element is 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 (4) 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 (8) 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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| CN202110998309.4A CN115727107A (en) | 2021-08-27 | 2021-08-27 | Dual-drive three-planet-row stepless speed change mechanism and speed change method thereof |
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| CN202110998309.4A CN115727107A (en) | 2021-08-27 | 2021-08-27 | Dual-drive three-planet-row stepless speed change mechanism and speed change method thereof |
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