CN115681426A - Step-transmission double-planetary-row transmission and speed change method thereof - Google Patents
Step-transmission double-planetary-row transmission and speed change method thereof Download PDFInfo
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- CN115681426A CN115681426A CN202110848472.2A CN202110848472A CN115681426A CN 115681426 A CN115681426 A CN 115681426A CN 202110848472 A CN202110848472 A CN 202110848472A CN 115681426 A CN115681426 A CN 115681426A
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Abstract
The invention discloses a step-transmission double-planet-row transmission, belonging to the technical field of stepless transmissions and comprising a first planet row and a second 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 first planet carrier on the first planet row is connected with a second gear ring on the second planet row, one side of the first planet row is connected with a first driving piece through a first input shaft, the same side of the second planet row is connected with a second driving piece through a second input shaft and a transmission shaft, a connector of the first gear ring and the second planet carrier is provided with a one-way stopper, and one side of the first planet carrier is connected with an output part. The step-transmission double-planet-row speed changer is characterized in that the first driving piece and the second driving piece are arranged on the same side of the stepless speed change mechanism, and the output part is arranged on the other side of the stepless speed change mechanism, so that the input position and the output position can be better separated, and the probability that the input end and the output part can interfere with each other is reduced.
Description
Technical Field
The invention relates to the technical field of automobile transmissions, in particular to a step-transmission double-planetary-row transmission 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, the AMT is applied to heavy vehicles, in order to expand the transmission ratio range, a great number of gears need to be set, the gear shifting process is slow, the operation is complex, and a lot of large vehicle drivers are reluctant to step on a 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 stepped transmission double-planetary-row transmission and a speed change method thereof.
The technical scheme of the invention is that the stepped transmission double-planet-row transmission comprises a first planet row and a second 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 first planet carrier on the first planet row is connected with a second gear ring on the second planet row, one side of the first planet row is connected with a first driving piece through a first input shaft, the same side of the second planet row is connected with a second driving piece through a second input shaft and a transmission shaft, one end of the first input shaft is connected with the first driving piece, the other end of the first input shaft penetrates through a transmission gear B, the transmission shaft and a second sun gear to be connected with a first sun gear, a one-way stopper is arranged on a connecting body of the first gear ring and the second planet carrier, and one side of the first planet carrier is connected with an output component.
As a further description of the present invention, a transmission stage is disposed between the first input shaft and the transmission shaft, the transmission stage includes a transmission gear a and a transmission gear B, one end of the second input shaft is connected to the second driving member, the other end of the second input shaft is connected to the transmission gear a, the transmission gear a and the transmission gear B are engaged through external teeth, the transmission gear B is connected to one end of the transmission shaft, and the other end of the transmission shaft is connected to a second sun gear on the second planet row.
As a further description of the present invention, the first planet row includes a first sun gear, a plurality of first planet gears are engaged with external teeth of the first sun gear, the first planet gears are connected to the first planet carrier, the first planet gears are engaged with the first ring gear, and first internal teeth are disposed on an inner wall of the first ring gear.
As a further description of the present invention, a plurality of second planet gears are engaged with the outer teeth of the second sun gear, the second planet gears are connected to the second planet carrier, the second planet gears are engaged with the second ring gear, and the inner wall of the second ring gear is provided with second inner teeth.
As a further explanation of the present invention, the one-way stopper is for limiting the rotational directions of the first ring gear and the second carrier; the one-way stopper makes the rotational direction of the first ring gear and the second carrier coincide with only the steering of the first driver.
The invention also provides a speed change method based on the step-by-step transmission double-planet-row speed changer, wherein a second driving piece and a 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 gear ring is connected with the second planet carrier, so that the rotating speeds of the first gear ring and the second planet carrier are the same; the first planet carrier, the second gear ring and the output component are connected, so that the rotating speeds of the first planet carrier, the second gear ring 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 present invention, the speed changing method performs speed changing in different manners according to different working conditions of the vehicle, and specifically includes:
and a state A: when the vehicle starts, the first driving piece and the second driving piece simultaneously drive the first planet row and the second planet row to work, the first sun gear rotates in the forward direction, and the second sun gear rotates in the reverse direction; the first sun gear can be controlled by the first driving part according to actual needs, and the rotating speed of the second sun gear can be controlled by the second driving part according to actual needs to easily finish maintaining, transition and switching, so that the whole process is continuous and smooth, and no power interruption exists;
and a state B: when the vehicle runs in an accelerating mode, the first driving piece and the second driving piece accelerate simultaneously, when the rotating speed of the first driving piece is about to exceed a high-efficiency area, the rotating speed of the first driving piece stops increasing, the rotating speed of the second driving piece is reduced, the second driving piece controls the second sun gear to gradually reduce from reverse rotation to 0, and then the rotating speed of the second sun gear is in the same direction as the rotating speed of the first sun gear; when the vehicle reaches the maximum speed, the steering directions of the first sun gear and the second sun gear are the same, and the first sun gear driven by the first driving piece and the second sun gear driven by the second driving piece both reach the maximum rotating speed;
according to the current working condition, the first driving piece and the second driving piece are respectively accelerated, decelerated or kept at rotating speeds, so that the first driving piece and the second driving piece can work in respective high-efficiency areas for a long time, and the energy-saving effect is realized;
and C, state C: when the vehicle is reversed, the first driving piece drives the first sun gear to rotate reversely, and the second driving piece drives the second sun gear to rotate forwardly.
As a further explanation of the invention, the state A comprises that the first driving part drives the first sun gear to rotate, and the rotating speed of the first sun gear is N 1 The first gear ring has a tendency of reverse rotation, and the one-way stopper acts to limit the reverse rotation of the first gear ring at a rotation speed N 3 =0, the first rowThe rotational speed of the planet carrier being N 2 The rotational speed of the output member is equal to the rotational speed of the first carrier by N 2 In the process, the first sun gear is input, the first gear ring is fixed, and the first planet carrier is decelerated and torque-increased to output;
the second driving piece drives the second sun gear to rotate, the rotating speed direction of the second sun gear is reverse, the second planet carrier has a tendency of reverse rotation, the second planet carrier is connected with the first gear ring, the one-way stopper limits the reverse rotation of the second planet carrier, and the rotating speed of the second planet carrier is N 3 =0, the rotation speed of the second gear ring is N 2 The rotating speed of the second sun gear is calculated to be N through a vector diagram 4 The transmission ratio of the transmission stage is i, so that the rotating speed of the second driving element is N 4 In the process, the second sun gear is input, the second planet carrier is fixed, and the second gear ring is decelerated and torque-increased to output;
the power of the first driving piece is output through the first planet carrier, the power of the second driving piece is output through the second gear ring, the power of the first driving piece and the power of the second driving piece are coupled together and output, the working principle of the first planet row and the working principle of the second planet row are the processes of reducing speed and increasing torque, and therefore the output torque can be increased.
As a further explanation of the invention, the speed N at which the first drive drives the first sun gear in state B is 1 Increasing the rotational speed N of the first carrier 2 Increasing the rotational speed N at which the second drive drives the second sun gear 4 Increase the rotational speed N of the second ring gear 2 Increasing; the rotational speed of the output member also increases;
when the rotating speed of the first driving piece is about to exceed the high-efficiency area, stopping increasing the rotating speed of the first driving piece, reducing the rotating speed of the second driving piece, driving the second sun gear to gradually reduce from reverse rotation to 0, and enabling the rotating speed N of the second sun gear to be equal to the rotating speed N of the second sun gear 4 Lowered to 0 because the one-way stopper limits only said firstThe gear ring and the second planet carrier can not reversely rotate, and the forward acceleration of the first gear ring and the second planet carrier is not limited, so that the rotating speed N of the second gear ring 2 Continuing to increase, the rotational speed of the output member will also continue to increase;
the second driving piece drives the second sun gear to start positive rotation, and when the rotating speed of the second sun gear is the same as that of the first sun gear, the rotating speed of the first sun gear is equal to that of the second sun gear, namely N 1 ＝N 4 The speed of rotation of the first ring gear is equal to the speed of rotation of the first carrier, i.e. N 3 ＝N 2 The rotational speed of the second ring gear is equal to the rotational speed of the second planet carrier, so N 1 ＝N 3 ＝N 2 ＝N 4 And the same as the rotational speed of the output member.
As a further explanation of the present invention, in the state C, the rotation speed of the first driving member driving the first sun gear is N 1 The direction of rotation is reverse, the first gear ring has a forward rotation tendency, a one-way retainer is acted at the moment to limit the forward rotation of the first gear ring, and the rotating speed of the first gear ring is N 3 =0, the rotational speed of the first carrier being N 2 The rotational speed of the output member is equal to the rotational speed of the first carrier by N 2 In the process, the first sun gear is input, the first gear ring is fixed, and the first planet carrier is decelerated and torque-increased to output;
the second driving piece drives the second sun gear to rotate, the rotating speed direction of the second sun gear is positive, the second planet carrier has a positive rotating trend, the second planet carrier is connected with the first gear ring, the one-way stopper limits the positive rotation of the second planet carrier, and the rotating speed of the second planet carrier is N 3 =0, the rotation speed of the second ring gear is N 2 The rotating speed of the second sun wheel is calculated to be N through a vector diagram 4 The rotating speed of the second driving piece is N 4 In the process, the second sun gear is input, the second planet carrier is fixed, and the second gear ring is decelerated and torque-increased to output;
the power of the first driving piece is output through the first planet carrier, the power of the second driving piece is output through the second gear ring, the power of the first driving piece and the power of the second driving piece are coupled together and output, the working principle of the first planet row and the working principle of the second planet row are the processes of reducing speed and increasing torque, and therefore the output torque can be increased.
The invention provides a step-transmission double-planetary-row speed changer and a speed change method thereof.A driving piece is arranged on the same side of a first sun gear and a second sun gear, the rotating speed and the steering of the driving piece are adjusted, and the stepless speed change of an output part is realized through the matching of the first planetary row, the second planetary row and a one-way retainer. The transmission stage is arranged between the second input shaft and the transmission shaft, and the transmission stage achieves the purpose of changing the size of 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 by the transmission ratio provided by the transmission stage on the premise of achieving the same using effect.
Drawings
FIG. 1 is a diagrammatic illustration of a stepped transmission double planetary transmission according to an embodiment of the present invention;
FIG. 2 is a diagram of a first planetary row rotation speed vector provided by 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 speed vector diagram for the first and second planetary rows of the combination of FIGS. 1 and 2 provided by an embodiment of the present invention;
FIG. 5 is a diagram of a rotation speed vector provided by the embodiment of the invention under a starting condition 1;
FIG. 6 is a rotation speed vector diagram provided by the embodiment of the invention under a starting condition 2;
FIG. 7 is a rotation speed vector diagram provided by the embodiment of the invention under the condition that the rotation speed control of the first driving element and the second driving element is inaccurate or the control fails under the starting working condition;
FIG. 8 is a diagram of a rotation speed vector provided by an embodiment of the present invention under an acceleration/deceleration condition 1;
FIG. 9 is a diagram of a rotation speed vector provided by the embodiment of the present invention under an acceleration/deceleration condition 2;
FIG. 10 is a rotation speed vector diagram provided by the embodiment of the invention under a reversing condition;
FIG. 11 is a diagram of a speed vector provided by an embodiment of the present invention with the first drive member disabled and the second drive member operating normally;
FIG. 12 is a speed vector diagram provided by an embodiment of the present invention with the second drive member disabled and the first drive member operating normally;
FIG. 13 is a graphical representation of rotational speeds provided by embodiments of the present invention during launch and acceleration of the first sun gear, the second sun gear, and the output member.
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-one-way stopper, 4-first input shaft, 5-second input shaft, 6-output member, 7-transmission stage, 701-transmission gear a, 702-transmission gear B, 8-transmission shaft.
Detailed Description
Firstly, the purpose that the embodiment of the invention is reported by us 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, the AMT is applied to heavy vehicles, in order to expand the transmission ratio range, a great number of gears need to be set, the gear shifting process is slow, the operation is complex, and a lot of reasons that drivers of large vehicles are reluctant to step on brakes are caused; the AMT gear shifting process depends on a complex control strategy, so that the accurate gear shifting time is difficult to master, and the problems of high energy consumption and low efficiency exist; the AMT transmission has the existing problems of complex structure, high manufacturing cost, difficult maintenance and the like, so that the step transmission double-planetary-row transmission is provided.
Referring to fig. 1, a step-gear double planetary transmission includes a first planetary gear set 1, a second planetary gear set 2, a first ring gear 103 of the first planetary gear set 1 connected to a second carrier 202 of the second planetary gear set 2, a first carrier 102 of the first planetary gear set 1 connected to a second ring gear 203 of the second planetary gear set 2, a first driving member connected to one side of the first planetary gear set 1 via a first input shaft 4, a second driving member connected to the same side of the second planetary gear set 2 via a transmission shaft 8 and a second input shaft 5, a first input shaft 4 connected to the first driving member at one end and connected to the first sun gear 101 at the other end via a transmission gear B702, the transmission shaft 8 and a second sun gear 201, a one-way stopper 3 provided on a connection body of the first ring gear 103 and the second carrier 202, and an output member 6 connected to one side of the first carrier 102.
Referring to fig. 1, a transmission stage 7 is arranged between the second input shaft 5 and the transmission shaft 8, the transmission stage 7 includes a transmission gear a701 and a transmission gear B702, one end of the second input shaft 5 is connected to the second driving member, the other end of the second input shaft is connected to the transmission gear a701, the transmission gear a701 and the transmission gear B702 are engaged through external teeth, the transmission gear B702 is connected to one end of the transmission shaft 8, and the other end of the transmission shaft 8 is connected to the second sun gear 201 of the second planetary row 2.
Referring to fig. 1, the first planetary row 1 includes a first sun gear 101, a plurality of first planet gears are engaged with external teeth of the first sun gear 101, the first planet gears are connected to a first planet carrier 102, the first planet gears are engaged with a first ring gear 103, and first internal teeth are arranged on an inner wall of the first ring gear 103.
Referring to fig. 1, a plurality of second planet wheels are engaged with the outer teeth of the second sun wheel 201, the second planet wheels are connected to the second planet carrier 202, a second ring gear 203 is engaged with the second planet wheels, and second inner teeth are arranged on the inner wall of the second ring gear 203.
Referring to fig. 1, the one-way stopper 3 serves to limit the rotational directions of the first ring gear 103 and the second carrier 202; the one-way stopper 3 makes the rotational direction of the first ring gear 103 and the second carrier 202 coincide with only the steering of the first driver.
In the following, a method of changing speed based on a step-drive double planetary transmission will be described with reference to specific configurations of embodiments of the present invention.
Referring to fig. 1, the rotation speed of the first driving member is in direct proportion to the rotation speed of the first sun gear 101; the rotation speed of the second driving member is the same as that of the second sun gear 201; the rotation speed of the first ring gear 103 is the same as the rotation speed of the second carrier 202; the rotational speed of the first planet carrier 102, the rotational speed of the second ring gear 203 and the rotational speed of the output member 6 are all the same.
In order to better illustrate the shifting effect of the present invention achieved by its own structure, the following needs to further explain the shifting method.
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.
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 (ii) a 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 rotating speed of the first driving piece driving the first sun gear 101 is set to be N 1 ；
The rotating speed of the second driving piece driving the second sun gear 201 is set to be N 4 ；
The rotation speed of the first ring gear 103 and the rotation speed of the second carrier 202 are set to N 3 ；
The rotational speeds of the first carrier 102, the second ring gear 203 and the output member 6 are all set to be N 2 ；
According to the planetary gearThe rotating speed vector calculation method of (1) obtains a rotating speed vector diagram 2 of the first planet row 1 1 Is the rotational speed of the first sun gear 101, N 2 Is the rotational speed of the first carrier 102, N 3 Is the rotational speed of the first ring gear 103. N is a radical of 1 、N 2 、N 3 The length of (d) represents the magnitude of the rotation speed, the arrow direction represents the rotation speed direction, and the arrow direction represents the rotation speed as positive. Set L 2 /L 1 = (first sun gear 101 teeth number Z) 1 ) /(number of teeth Z of first ring gear 103) 2 )。
A rotating speed vector diagram 3 of the second planet row 2 is obtained according to a rotating speed vector calculation method of the planet gear 4 Is the rotational speed, N, of the second sun gear 201 3 Is the rotational speed, N, of the second planet carrier 202 2 Is the rotational speed of the second ring gear 203. N is a radical of hydrogen 2 、N 3 、N 4 The length of (b) represents the magnitude of the rotation speed, the arrow direction represents the rotation speed direction, and the arrow direction represents the rotation speed being positive. Set L 2 /L 3 = (number of second sun gear 201 teeth Z) 3 ) /(number of teeth Z of second ring gear 203) 4 )。
Combining FIG. 2 and FIG. 3 into FIG. 4 1 Is the rotational speed of the first sun gear 101; n is a radical of 4 Is the rotational speed of the second sun gear 201; n is a radical of hydrogen 2 Is the rotational speed of the first carrier 102 and the second ring gear 203, i.e., the rotational speed of the output member 6; n is a radical of hydrogen 3 The rotation speed of the first ring gear 103 and the second carrier 202; fig. 4 shows the overall arrangement, the speed N of the first sun gear 101 1 Determining the rotational speed N of the second sun gear 201 4 Determining the rotational speed N of the output member 6 2 And is also uniquely determined.
The rotational speed N of the output member 6 can be achieved by controlling the rotational speed of the first drive element and the rotational speed of the second drive element by regulation 2 Is continuously varied.
When starting, the first driving piece drives the first sun gear 101 at the rotating speed of N 1 The second driving member drives the second sun gear 201 at a speed N 4 。
1) Starting condition 1
As shown in FIG. 5, the rotational speed N of the first sun gear 101 is set 1 And the rotational speed N of the second sun gear 201 4 Is [ Z ] of 3 ×(Z 1 +Z 2 )]/(Z 1 ×Z 4 ) The rotation speed of the first ring gear 103 and the rotation speed N of the second carrier 202 3 Always 0, the rotation speed N of the first sun gear 101 driven by the first driving member 1 And the rotation speed N of the second driving member driving the second sun gear 201 4 Is gradually increased to output a rotation speed N 2 Gradually increased, and the steering direction is positive.
2) Starting condition 2
As shown in fig. 6, when the first sun gear 101 rotates at a speed N 1 And the rotational speed N of the second sun gear 201 4 Is greater than [ Z ] 3 ×(Z 1 +Z 2 )]/(Z 1 ×Z 4 ) While following the rotational speed N of the first sun gear 101 1 And the rotational speed N of the second sun gear 201 4 Is gradually increased to output a rotation speed N 2 Gradually increasing, turning to the positive direction, the rotating speed of the first gear ring 103 and the rotating speed N of the second planet carrier 202 3 Gradually increasing and turning to the positive direction.
The starting working condition 1 and the starting working condition 2 are normal working conditions in the starting process, any one of the two working conditions or the switching time of the two working conditions is adopted, the maintaining, the transition and the switching can be easily completed by controlling the rotating speeds of the first driving piece and the second driving piece according to actual needs, the whole process is continuous and smooth, and no power interruption exists.
As shown in fig. 7, if the control of the rotational speeds of the first and second driving members is inaccurate or fails, the rotational speed N of the first sun gear 101 occurs 1 And the rotational speed N of the second sun gear 201 4 Is less than [ Z ] 3 ×(Z 1 +Z 2 )]/(Z 1 ×Z 4 ) The rotational speed N of the output member 6 2 In order to prevent the reverse rotation as shown in fig. 6, which may occur when the vehicle suddenly moves backward and is highly liable to cause a serious accident, it is not reasonable to provide the one-way stopper 3 on the connecting body of the first ring gear 103 and the second carrier 202 to limit the rotation speed N of the first ring gear 103 and the second carrier 202 3 The direction of the rotation speed of (2) can only be a forward direction, but can not be a reverse direction. This ensures the rotational speed N of the output part 6 2 Is always positive. When in useRotational speed N of the second sun gear 201 4 When the speed is too fast, only the first driving piece and the second driving piece can be dragged mutually, and the output rotating speed N can not appear 2 Is negative. The one-way stopper 3 does not restrict the forward rotation of the first ring gear 103 and the second carrier 202, so the rotation speed N of the first ring gear 103 and the second carrier 202 in the starting condition 2 3 The positive direction is possible without causing the first and second drive members to drag against each other.
Therefore, when starting, the rotation speed N1 of the first sun gear 101 is controlled by the first driving member and the rotation speed N of the second sun gear 201 is controlled by the second driving member 4 The rotational speed N of the first sun gear 101 is set 1 And the rotational speed N of the second sun gear 201 4 Is greater than or equal to [ Z ] 3 ×(Z 1 +Z 2 )]/(Z 1 ×Z 4 ). For the first planet row 1, the input is carried out by the first sun gear 101, the output is carried out by the first planet carrier 102, and the working process is a speed-reducing and torque-increasing process; for the second planet row 2, the input is from the second sun gear 201, the output is from the second ring gear 203, and the working process is also the process of speed reduction and torque increase. And because the first planet carrier 102 and the second ring gear 203 are connected together, the power of the first driving element and the power of the second driving element are coupled together through the first planet row 1 and the second planet row 2, and the speed reduction and torque increase output is carried out.
The acceleration and deceleration process drives the second sun wheel 201 according to the rotation speed N of the second driving member 4 The steering is divided into two working conditions.
1) Working condition 1
As shown in fig. 8, 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 4 The direction of rotation is reversed. Controlling the rotational speed N of the first sun gear 101 1 And the rotational speed N of the second sun gear 201 4 The rotational speed N of the first sun gear 101 is set 1 And the rotational speed N of the second sun gear 201 4 Is greater than or equal to [ Z ] 3 ×(Z 1 +Z 2 )]/(Z 1 ×Z 4 ). By controlling the speed of rotation N of the first sun gear 101 1 And rotation of the second sun gear 201Speed N 4 The rotating speed N of the output part 6 can be realized by the rotating speed of (3) and the increasing and decreasing speed 2 Gradually increasing or gradually decreasing, the direction is positive.
2) Working condition 2
As shown in fig. 9, 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 4 The direction of rotation is the forward direction. By controlling the speed of rotation N of the first sun gear 101 1 And the rotational speed N of the second sun gear 201 4 The output rotating speed N can be realized by the size of the speed and the speed increasing and decreasing degree 2 Gradually increasing or decreasing, the direction is positive. Under the working condition, when the rotating speed of the first driving piece and the rotating speed of the second driving piece reach the maximum rotating speed, the rotating speed N is output 2 A maximum is also reached, at which time the vehicle reaches a maximum speed. If the first driving member drives the first sun gear 101 at a rotational speed N1 and the second driving member drives the second sun gear 201 at a rotational speed N 4 Is the same, then the output speed N is 2 The same is true for the maximum value that can be reached, in which case the transmission ratio is 1.
As shown in fig. 8 and 9, when the acceleration and deceleration are performed according to the above-described operating condition 1 and operating condition 2, the output rotation speed N can be adjusted by adjusting the rotation speed of the second driving element while maintaining the rotation speed of the first driving element unchanged 2 The rotating speed of the second driving element can be kept unchanged, and the output rotating speed N can be adjusted by adjusting the rotating speed of the first driving element 2 The size of (2). At the speed N of the output member 6 2 In the process of acceleration or deceleration, the first driving part and the second driving part can set the acceleration, deceleration and maintaining rotating speed of the first driving part and the second driving part according to the current working condition according to different respective high-efficiency areas. Therefore, the first driving part and the second driving part can work in respective high-efficiency areas for a long time, and the energy-saving effect is improved.
As shown in FIG. 10, during reverse, the first driving member drives the first sun gear 101 at a rotation speed N 1 The direction of rotation is reverse, and the second driving member drives the second sun gear 201 at a speed N 4 The direction of rotation is the forward direction. ControlThe rotational speed of the first driving member and the rotational speed of the second driving member are controlled so that the rotational speed N of the first sun gear 101 1 And the rotational speed N of the second sun gear 201 4 Is greater than or equal to [ Z ] 3 ×(Z 1 +Z 2 )]/(Z 1 ×Z 4 ). The output rotating speed N can be realized by controlling the rotating speed of the first driving part and the rotating speed of the second driving part and increasing and decreasing the speed 2 Gradually increasing or decreasing, the direction of rotation is reversed. Preventing the rotational speed N of the output member 6 if the rotational speed control of the first and second drive members is inaccurate or fails 2 When the normal rotation occurs, the one-way stopper 3 at the connecting body of the first ring gear 103 and the second carrier 202 is switched to limit the rotation speed N of the first ring gear 103 and the second carrier 202 3 The direction of the rotation speed of (2) can only be reverse direction, but can not be forward direction.
Besides the normal working condition, an abnormal working condition needs supplementary explanation, which is specifically as follows:
as shown in fig. 11, when the first driving member fails due to a fault, the second driving member can continue to drive the vehicle. The first driving member is disabled, and the second driving member drives the second sun gear 201 at a rotating speed N 4 When the direction of rotation is reversed, the first ring gear 103 and the second carrier 202 tend to rotate in reverse, and the reverse rotation is restricted by the one-way stopper 3, and the rotation speed N of the first ring gear 103 and the second carrier 202 is equal to or higher than the rotation speed N of the first ring gear 103 and the second carrier 202 3 0, rotational speed N of the output member 6 2 For positive rotation, the second drive element is powered via a gear stage 7 and the second planetary gear set 2 at a fixed gear ratio i x (Z) 4 /Z 3 ) And (5) reducing and increasing torque output.
As shown in fig. 12, when the second driving member fails due to a failure, the first driving member can continue to drive the vehicle. The second driving member is disabled, and the first driving member drives the first sun gear 101 at a rotating speed N 1 When the direction of rotation is in the forward direction, the first ring gear 103 and the second carrier 202 tend to rotate in the reverse direction, and the reverse rotation is restricted by the one-way stopper 3, the rotation speed N of the first ring gear 103 and the second carrier 202 is reduced 3 0, rotational speed N of the output member 6 2 For positive rotation, the power of the first driving member passes through the first planetary gear set 1 at a fixed transmission ratio [ (Z) 1 +Z 2 )/Z 1 ]And (5) reducing and increasing torque output.
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.
Finally, a continuous and complete description of the starting and accelerating processes of the first driving member and the second driving member is provided as follows:
as shown in fig. 13, curve 1 represents the time-dependent speed of rotation of the first sun gear 101 driven by the first driver, curve 2 represents the time-dependent speed of rotation of the second sun gear 201 driven by the second driver, and curve 3 represents the time-dependent speed of rotation of the output member 6. In the starting stage, the first driving piece drives the first sun gear 101 to rotate at a gradually increased speed, and the rotation direction is positive; the second driving element drives the second sun gear 201 to rotate at a gradually increasing speed, and the rotation direction is reverse; the rotating speed of the output part is synchronously increased, and the rotation direction is positive; the transmission ratio is the biggest this moment, and first driving piece and second driving piece all are the speed reduction and increase the torsion output, and the vehicle is with the big moment of torsion of low-speed start. In the acceleration stage, the first driving part drives the rotation speed of the first sun gear 101 to continue acceleration, and the rotation speed is kept unchanged after reaching a certain rotation speed; the second driving element drives the rotation speed of the second sun gear 201 to accelerate reversely, then to decelerate to 0, and finally to accelerate forwardly; the rotating speed of the output component is always accelerated in the positive direction, the transmission ratio is gradually reduced in the process, and the rotating speed of the output component is continuously and steplessly changed.
In the highest speed stage, the rotation speed of the first driving member and the second driving member reaches the highest rotation speed, the rotation speed of the output member also reaches the highest rotation speed, and fig. 13 shows the rotation speed N of the first sun gear 101 driven by the first driving member 1 And the rotational speed N at which the second driving member drives the second sun gear 201 4 Since the maximum value of (2) is the same, the rotation speed of the output member is the same as the maximum rotation speed of the first sun gear 101 and the second sun gear 201, the gear ratio is 1, and the vehicle speed is the highest.
The step transmission double-planetary-row transmission and the speed change method thereof provided by the embodiment of the invention have the following advantages:
1. the step transmission double-planet-row transmission 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 stepped transmission double-planetary-row transmission can realize that the output part 6 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 climbing, and the large torque can also meet the requirements of more people on vehicle use, so that the audience area of the product is larger.
3. The step transmission double-planetary-row transmission can realize the stepless change of the output rotating speed, so that the driving piece at the input end can work in a high-efficiency working 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 step transmission double-planetary-row transmission 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 first driving part and the second driving part are coupled together in a power manner 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 step-transmission double-planetary-row transmission has high transmission rate, the motor with lower power and lower rotating speed can be selected as the driving piece under the same working condition, and compared with a high-power battery, the low-power battery can better prevent the battery from overheating, and the use safety of the battery is indirectly improved through the embodiment of the invention.
8. The step-transmission double-planet-row transmission provided by the embodiment of the invention has the advantages that the first driving piece and the second driving piece are arranged on the same side of the stepless speed change mechanism, the output part is arranged on the other side of the stepless speed change mechanism, the input position and the output position can be better separated, the probability that the input end and the output part interfere with each other is reduced, the utilization rate of space can be greatly improved by the design, and the whole power equipment is more reasonable in arrangement and space occupancy rate.
9. The step transmission double-planetary-row transmission provided by the embodiment of the invention is provided with the transmission stage between the second input shaft and the transmission shaft, 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 transmission ratio provided by the transmission stage 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 (10)
1. A stepped transmission double planetary gear set transmission, characterized by comprising a first planetary gear set (1) and a second planetary gear set (2), wherein a first ring gear (103) on the first planetary gear set (1) is connected with a second planet carrier (202) on the second planetary gear set (2), a first planet carrier (102) on the first planetary gear set (1) is connected with a second ring gear (203) on the second planetary gear set (2), one side of the first planetary gear set (1) is connected with a first driving part through a first input shaft (4), the same side of the second planetary gear set (2) is connected with a second driving part through a transmission shaft (8) and a second input shaft (5), one end of the first input shaft (4) is connected with the first driving part, the other end of the first input shaft passes through a transmission gear B (702), the transmission shaft (8) and a second sun gear (201) to be connected with a first sun gear (101), a one-way stopper (3) is arranged on the connection body of the first ring gear (103) and the second planet carrier (202), and one side of the first planet carrier (102) is connected with an output member (6).
2. A step-gear double planetary transmission according to claim 1, characterized in that a transmission stage (7) is arranged between the second input shaft (5) and the transmission shaft (8), the transmission stage (7) comprises a transmission gear a (701) and a transmission gear B (702), one end of the second input shaft (5) is connected to the second driving member, the other end is connected to the transmission gear a (701), the transmission gear a (701) and the transmission gear B (702) are engaged by external teeth, the transmission gear B (702) is connected to one end of the transmission shaft (8), and the other end of the transmission shaft (8) is connected to the second sun gear (201) on the second planetary row (2).
3. A step-gear double planetary transmission according to claim 1, wherein the first planetary gear (1) comprises a first sun gear (101), a plurality of first planet gears are engaged on the outer teeth of the first sun gear (101), the first planet gears are connected to the first carrier (102), the first planet gears are engaged with the first ring gear (103), and first inner teeth are provided on the inner wall of the first ring gear (103).
4. A step-gear double row transmission according to claim 1, characterised in that the second planetary row (2) comprises a second sun wheel (201), which second sun wheel (201) is externally toothed with a number of second planet wheels, which second planet wheels are connected to the second planet carrier (202), which second planet wheels are in engagement with the second ring gear (203), which second ring gear (203) is internally toothed with a second internal toothing.
5. A step-geared double planetary transmission according to claim 1, characterized in that the one-way stopper (3) is used to limit the direction of rotation of the first ring gear (103) and second carrier (202); the one-way stopper (3) makes the rotational direction of the first ring gear (103) and the second carrier (202) coincide with only the steering of the first sun gear (101).
6. A method of transmission based on a step-gear double planetary transmission, characterized in that a second drive member and a second sun gear (201) are connected via a second input shaft (5) such that the rotational speed of the second drive member and the rotational speed of the second sun gear (201) are the same; the first gear ring (103) is connected with the second planet carrier (202), so that the rotating speeds of the first gear ring (103) and the second planet carrier (202) are the same; the first planet carrier (102), the second gear ring (203) and the output component (6) are connected, so that the rotating speeds of the first planet carrier (102), the second gear ring (203) and the output component (6) 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 (6) is achieved, in which process the speed ratio is correspondingly changed.
7. The method of claim 6, wherein the step-variable transmission is configured to perform different speed changes according to different operating conditions of the vehicle, and comprises:
and a state A: when the vehicle starts, the first driving piece and the second driving piece simultaneously drive the first planet row (1) and the second planet row (2) to work, the first sun gear (101) rotates in the positive direction, and the second sun gear (201) rotates in the reverse direction; the first sun gear (101) can be controlled by the first driving piece and the second sun gear (201) can be controlled by the second driving piece according to actual needs to easily maintain, transition and switch, and the whole process is continuous and smooth without power interruption;
and a state B: when the vehicle runs in an accelerating mode, the first driving element and the second driving element accelerate simultaneously, when the rotating speed of the first driving element is about to exceed a high-efficiency area, the rotating speed of the first driving element is stopped to be increased, the rotating speed of the second driving element is reduced, the second driving element controls the second sun gear (201) to be gradually reduced from reverse rotation to 0, and then the rotating speed of the second sun gear (201) is started to be in the same direction as the rotating speed of the first sun gear (101); when the vehicle reaches the maximum speed, the first sun gear (101) and the second sun gear (201) are in the same steering direction, and the first sun gear (101) driven by the first driving piece and the second sun gear (201) driven by the second driving piece both reach the maximum rotating speed;
according to the current working condition, the first driving piece and the second driving piece are respectively accelerated, decelerated or kept at rotating speeds, so that the first driving piece and the second driving piece can work in respective high-efficiency areas for a long time, and the energy-saving effect is realized;
and C, state C: when backing, first driving piece drive first sun gear (101) reverse rotation, second driving piece drive second sun gear (201) forward rotation.
8. Method for governing a step-gear double planetary transmission according to claim 7, wherein state A comprises the first drive element driving the first sun wheel (101) in rotation, the first sun wheel (101) having a speed of rotation N 1 The first gear ring (103) has a tendency of rotating in the reverse direction, the one-way stopper (3) acts to limit the reverse rotation of the first gear ring (103), and the rotation speed of the first gear ring (103) is N 3 =0, the rotational speed of the first carrier (102) being N 2 The rotational speed of the output member (6) is equal to the rotational speed of the first carrier (102) by N 2 In the course of this process, the temperature of the molten steel is controlled,the first sun gear (101) is used for inputting, the first gear ring (103) is fixed, and the first planet carrier (102) is used for reducing speed and increasing torque for outputting;
the second driving piece drives the second sun gear (201) to rotate, the rotating speed direction of the second sun gear (201) is reverse, the second planet carrier (202) has a tendency of reverse rotation, the second planet carrier (202) is connected with the first gear ring (103), the unidirectional stopper (3) limits the reverse rotation of the second planet carrier (202), and the rotating speed of the second planet carrier (202) is N 3 =0, the rotation speed of the second ring gear (203) is N 2 The rotating speed of the second sun wheel (201) is calculated to be N through a vector diagram 4 The transmission ratio of the transmission stage is i, so that the rotating speed of the second driving element is N 4 Xi, in the process, the second sun gear (201) is input, the second planet carrier (202) is fixed, and the second ring gear (203) is decelerated and torque-increased to output;
the power of the first driving piece is output through the first planet carrier (102), the power of the second driving piece is output through the second gear ring (203), the powers of the first driving piece and the second driving piece are coupled together and output, the working principle of the first planet row (1) and the working principle of the second planet row (2) are the processes of speed reduction and torque increase, and therefore the output torque can be increased.
9. Method of regulating the speed of a step-gear double planetary transmission according to claim 7, characterized in that the speed N at which the first drive drives the first sun gear (101) in state B is the rotational speed 1 Increasing the rotational speed N of the first planet carrier (102) 2 Increasing the rotational speed N at which the second drive drives the second sun gear (201) 4 Increasing the rotational speed N of the second ring gear (203) 2 Increasing; the rotational speed of the output member (6) is also increased;
when the rotating speed of the first driving member is about to exceed the high-efficiency area, the rotating speed of the first driving member is stopped to be increased, the rotating speed of the second driving member is reduced, the second driving member drives the second sun gear (201) to be gradually reduced from reverse rotation to 0, and the second driving member drives the second sun gear to rotateRotational speed N of the two sun gears (201) 4 Is reduced to 0, and the rotating speed N of the second gear ring (203) is reduced to 0 because the one-way stopper (3) only limits the first gear ring (103) and the second planet carrier (202) not to be capable of reversely rotating and limits the forward acceleration of the first gear ring (103) and the second planet carrier (202) 2 The rotating speed of the output component (6) is increased continuously;
the second driving part drives the second sun gear (201) to start forward rotation, and when the rotating speed of the second sun gear (201) is the same as that of the first sun gear (101), the rotating speed of the first sun gear (101) is equal to that of the second sun gear (201), namely N 1 ＝N 4 The rotational speed of the first ring gear (103) is equal to the rotational speed of the first carrier (102), i.e. N 3 ＝N 2 The rotational speed of the second ring gear (203) is equal to the rotational speed of the second planet carrier (202), so N 1 ＝N 3 ＝N 2 ＝N 4 And the same as the rotational speed of the output member (6).
10. Method of regulating the speed of a step-gear double planetary transmission according to claim 7, wherein the first driving member drives the first sun gear (101) in state C at a speed N 1 When the direction of rotation is reverse, the first gear ring (103) has a forward rotation tendency, a one-way stopper (3) is acted to limit the forward rotation of the first gear ring (103), and the rotation speed of the first gear ring (103) is N 3 =0, the rotational speed of the first carrier (102) being N 2 The rotational speed of the output member (6) is equal to the rotational speed of the first planet carrier (102) by N 2 In the process, the first sun gear (101) is input, the first gear ring (103) is fixed, and the first planet carrier (102) is subjected to speed reduction and torque increase output;
the second driving piece drives the second sun gear (201) to rotate, the rotating speed direction of the second sun gear (201) is positive, the second planet carrier (202) tends to rotate positively, the second planet carrier (202) is connected with the first gear ring (103), and the one-way stopper (3) limits the positive rotation of the second planet carrier (202), so thatThe rotating speed of the second planet carrier (202) is N 3 =0, the rotation speed of the second ring gear (203) is N 2 The rotating speed of the second sun wheel (201) is calculated to be N through a vector diagram 4 The rotating speed of the second driving piece is N 4 Xi, in the process, the second sun gear (201) is input, the second planet carrier (202) is fixed, and the second ring gear (203) is decelerated and torque-increased to output;
the power of the first driving piece is output through the first planet carrier (102), the power of the second driving piece is output through the second gear ring (203), the powers of the first driving piece and the second driving piece are coupled together to be output, the working principle of the first planet row (1) and the working principle of the second planet row (2) are the speed reduction and torque increase processes, and therefore the output torque can also be increased.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202110848472.2A CN115681426A (en) | 2021-07-27 | 2021-07-27 | Step-transmission double-planetary-row transmission and speed change method thereof |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202110848472.2A CN115681426A (en) | 2021-07-27 | 2021-07-27 | Step-transmission double-planetary-row transmission and speed change method thereof |
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| CN115681426A true CN115681426A (en) | 2023-02-03 |
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| CN202110848472.2A Pending CN115681426A (en) | 2021-07-27 | 2021-07-27 | Step-transmission double-planetary-row transmission and speed change method thereof |
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| CN (1) | CN115681426A (en) |
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