CN115681427A - Single-side stepped transmission input double-planetary-row transmission and speed changing method thereof - Google Patents
Single-side stepped transmission input double-planetary-row transmission and speed changing method thereof Download PDFInfo
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- CN115681427A CN115681427A CN202110848474.1A CN202110848474A CN115681427A CN 115681427 A CN115681427 A CN 115681427A CN 202110848474 A CN202110848474 A CN 202110848474A CN 115681427 A CN115681427 A CN 115681427A
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Abstract
The invention discloses a single-side stepped transmission input double-planet-row speed changer, which belongs to the technical field of stepless speed changers and 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, a first planet carrier on the first planet row is connected with a second gear ring on the second planet row, one side of the second planet row is connected with a second driving piece through a second input shaft, the same side of the first planet row is connected with the first driving piece through a first input shaft and a transmission shaft, and a connecting body of the first gear ring and the second planet carrier is provided with a one-way stopper. The single-side stepped transmission input double-planetary-row transmission is provided with the transmission stage between the first input shaft and the transmission shaft, and the transmission stage achieves the purpose of changing the transmission ratio between the first driving piece and the first 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 first driving piece is widened.
Description
Technical Field
The invention relates to the technical field of automobile transmissions, in particular to a single-side stepped transmission input double-planet-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 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-planetary-row transmission with single-side stepped transmission input and a speed changing method thereof.
The technical scheme of the invention is that the single-side stepped transmission input 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, a 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 transmission shaft and a first input shaft, the same side of the second planet row is connected with a second driving piece through a second input shaft, one end of the second input shaft is connected with the second driving piece, the other end of the second input shaft penetrates through a transmission gear B, the transmission shaft and a first sun gear to be connected with a second 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 first input shaft is connected to the first driving member, the other end of the first 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 passes through an output component and is connected to a first sun gear on the first 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, the second planet row includes a second sun gear, a plurality of second planet gears are meshed with external teeth of the second sun gear, the second planet gears are connected to the second planet carrier, the second planet gears are meshed with the second ring gear, and second internal teeth are arranged on an inner wall of the second ring gear.
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 sun gear.
The invention also provides a speed change method of the double-planetary-row speed changer based on unilateral stepped transmission input, 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 piece and the second sun gear can be controlled by the second driving piece according to actual needs to easily finish maintaining, transition and switching, 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 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 elaboration of the invention, state A comprises a transmission ratio i of the transmission stage, the first driving member drives the first sun gear to rotate, and the first sun gear has a rotational speed N 1 The rotating speed of the first driving part is N 1 Xi, said first ring gear having a reverse rotationA trend that the one-way stopper is activated to restrict the reverse rotation of the first ring gear at a rotation speed 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 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 ring gear is N 2 The rotating speed of the second sun wheel is calculated to be N through a vector diagram 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, and reducing the rotating speed of the second driving piece, wherein the rotating speed of the second driving piece is gradually reduced from reverse rotation to 0, and the rotating speed N of the second sun gear is 4 Is reduced to 0 becauseThe one-way stopper only limits the first ring gear and the second planet carrier not to be reversely rotated but not limits the first ring gear and the second planet carrier to be positively accelerated, so the rotating speed N of the second ring gear 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 to rotate positively, 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 And the direction of rotation is reverse, the first gear ring tends to rotate in forward direction, the one-way retainer acts 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 ring gear is reducedRapidly increasing torque 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 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 and the working principle of the second planet row are the processes of speed reduction and torque increase, and therefore the output torque is increased.
The invention provides a single-side step-drive input double-planetary-row speed changer and a speed changing 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 first input shaft and the transmission shaft, and the transmission stage achieves the purpose of changing the size of the transmission ratio between the first driving piece and the first 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 first 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 schematic structural diagram of a single-side stepped input double planetary transmission according to 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 speed vector diagram for the first and second planetary rows incorporating 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 the 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:
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 of the embodiment of the invention is explained, and the problem that the AMT has gear shifting pause and power interruption in the nature is solved; the transmission ratio range of the AMT is limited by gear setting and is applied to heavy vehicles, in order to expand the transmission ratio range, a large number of gears need to be set, the gear shifting process is slow, the operation is complex, and a large number of reasons that drivers of large vehicles do not want to step on the brake are caused; the AMT gear shifting process depends on a complex control strategy, so that the accurate gear shifting time is difficult to master, and the problems of high energy consumption and low efficiency exist; the AMT has the existing problems of complex structure, high manufacturing cost, difficult maintenance and the like, so that the double-planetary-row transmission with single-side stepped transmission input is provided.
Referring to fig. 1, a single-side stepped transmission input double planetary gear transmission includes a first planetary gear set 1 and a second planetary gear set 2, a first ring gear 103 of the first planetary gear set 1 is connected to a second carrier 202 of the second planetary gear set 2, a first carrier 102 of the first planetary gear set 1 is connected to a second ring gear 203 of the second planetary gear set 2, one side of the first planetary gear set 1 is connected to a first driving member through a transmission shaft 8 and a first input shaft 4, the same side of the second planetary gear set 2 is connected to a second driving member through a second input shaft 5, one end of the second input shaft 5 is connected to the second driving member, the other end of the second input shaft 5 is connected to a second sun gear 201 through a transmission gear B702, the transmission shaft 8 and a first sun gear 101, a one-way stopper 3 is disposed on a connecting body of the first ring gear 103 and the second carrier 202, and one side of the first carrier 102 is connected to an output member 6.
Referring to fig. 1, a transmission stage 7 is arranged between the first input shaft 4 and the transmission shaft 8, the transmission stage 7 includes a transmission gear a701 and a transmission gear B702, one end of the first input shaft is connected to the first driving member, the other end of the first 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 passes through the output member 6 and is connected to the first sun gear 101 on the first planetary row 1.
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, the second planetary row 2 includes a second sun gear 201, a plurality of second planetary gears are engaged with external teeth of the second sun gear (201), the second planetary gears are connected to a second planetary carrier 202, a second ring gear 203 is engaged with the second planetary gears, and second internal teeth are disposed on an 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 sun gear 101.
In the following, a method for changing a double planetary transmission based on a single-side stepped transmission input will be described with reference to specific configurations of embodiments of the present invention.
Referring to fig. 1, the rotational speed of the first driving member is proportional to the rotational 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 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 by its own structure, the following needs to 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 member driving the second sun gear 201 is set to 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 first carrier 102, the second ring gear 203 and the output member 6 are all set to rotate at N 2 ；
Obtaining a rotating speed vector diagram 2,N of the first planet row 1 according to a rotating speed vector calculation method of the planet gear 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 )。
Obtaining a rotating speed vector diagram 3,N of the second planet row 2 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 2 、N 3 、N 4 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 3 = (second sun gear 201 teeth number Z) 3 ) (number of teeth Z of second ring gear 203) 4 )。
Combining FIG. 2 and FIG. 3 to obtain FIG. 4,N 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 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 speeds 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 part 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 increasing and turning to the positive direction.
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 increased, and the steering direction is positive.
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 (1) can only be a forward direction, but cannot be a reverse direction. Thus ensuring the transfusionRotational speed N of the output member 6 2 Is always positive. When the rotational 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 A positive orientation is possible without causing the first and second drivers 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. Since the first carrier 102 and the second ring gear 203 are connected together, the power of the first driver and the power of the second driver are coupled together through the first planetary gear set 1 and the second planetary gear set 2, and the speed reduction and torque increase output is performed.
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, the second driving member drives the second sun gear 201 at a 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 controlling101 speed N of the first sun gear 1 And the rotational speed N of the second sun gear 201 4 By the magnitude and the speed increasing and decreasing degree of (2), the rotating speed N of the output member 6 can be realized 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 degree of increasing and decreasing the speed 2 Gradually increasing or decreasing, the direction of rotation 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 Are 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 performing acceleration and deceleration according to the above-mentioned operating condition 1 and operating condition 2, the output rotation speed N can be adjusted by adjusting the rotation speed of the second driving member while maintaining the rotation speed of the first driving member 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, the first driving member drives the first sun gear 101 at a speed N when the vehicle is in reverse 1 The direction of rotation is reversed, and the second driving member drives the secondThe rotation speed of the sun gear 201 is N 4 The direction of rotation is the forward direction. The rotation speed of the first driving member and the rotation speed of the second driving member are controlled so that the rotation 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 control 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 (1) 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 failed, 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 power of the second drive member is passed through the second planetary row 2 at a fixed transmission ratio (Z) 4 /Z 3 ) And (5) speed reduction and torque increase output.
As shown in fig. 12, when the second driving member fails due to a fault, 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 forward rotation, the first drive member is powered via the gear stage 7 and the first drive memberPlanet row 1, with fixed gear ratio i x [ (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 rotation speed of the second sun gear 201 driven by the second driving element is gradually increased, 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 element drives the rotation speed of the first sun gear 101 to continue acceleration, and the rotation speed is kept unchanged after the rotation speed reaches 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 rotation speed N of the second driving member driving 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 embodiment of the invention provides a single-side stepped transmission input double-planetary-row transmission and a speed change method thereof, which have the following advantages:
1. the double-planet-row transmission with the unilateral graded transmission input, provided by the embodiment of the invention, has no power interruption in the speed regulation process, is quiet and stable in operation, has better car using experience when a user uses a car, can greatly meet the customer demand in sense, and lays a good foundation for popularization and use of the product.
2. The double-planetary-row transmission with the unilateral stepped transmission input in the embodiment of the invention can realize that the output part 6 has large torque from low speed to high speed, and the vehicle has the capability of quick acceleration starting by outputting the large torque when driving, the large torque can climb a larger slope when climbing, and the large torque can also meet the requirements of more people, so that the audience of the product is larger.
3. The single-side stepped transmission input double-planetary-row transmission can realize stepless continuous change of output rotating speed, the input end driving piece can work in a high-efficiency interval for a long time, the working efficiency is improved, the effect of saving energy can be achieved, and more contribution can be made in the aspect of energy saving.
4. The single-side stepped transmission input 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 the 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 single-side stepped transmission input double-planet-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 single-side stepped transmission input double-planetary-row transmission provided by the embodiment of the invention has the advantages that the first driving piece, the second driving piece and the output part are arranged on the same side of the stepless speed change mechanism, so that the input and the output of energy are arranged at one end of the stepless speed change mechanism, the design can greatly improve the utilization rate of space, and the whole power equipment is more reasonable in arrangement and space utilization rate.
9. The single-side stepped transmission input double-planetary-row transmission provided by the embodiment of the invention is provided with the transmission stage between the first input shaft and the transmission shaft, and the transmission stage achieves the purpose of changing the transmission ratio between the first driving piece and the first 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 first 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 single-side stepped transmission input double-planet-row transmission is characterized by comprising a first planet row (1) and a second planet row (2), wherein 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), 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), one side of the first planet row (1) is connected with a first driving piece through a transmission shaft (8) and a first input shaft (4), the same side of the second planet row (2) is connected with a second driving piece through a second input shaft (5), one end of the second input shaft (5) is connected with the second driving piece, the other end of the second planet row is connected with a second sun wheel (201) through a transmission gear B (702), a transmission shaft (8) and a first sun wheel (101), a connecting body of the first ring gear (103) and the second planet carrier (202) is provided with a one-way stopper (3), and one side of the planet carrier (102) is connected with an output stopper (6).
2. The single-sided step drive input double planetary transmission according to claim 1, wherein a transmission stage (7) is disposed between the first input shaft (4) 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 first input shaft (4) is connected to the first driving member, the other end of the first input shaft 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) passes through an output member (6) and is connected to the first sun gear (101) of the first planetary row (1).
3. A single-side stepped input double planetary transmission according to claim 1, wherein said first planetary row (1) comprises a first sun gear (101), a plurality of first planet gears are engaged on external teeth of said first sun gear (101), said first planet gears are connected to said first carrier (102), said first planet gears are engaged with said first ring gear (103), and said first ring gear (103) is provided with first internal teeth on its inner wall.
4. The single-sided step-gear input double planetary transmission according to claim 1, wherein the second planetary gear set (2) includes a second sun gear (201), a plurality of second planetary gears are engaged with external teeth of the second sun gear (201), the second planetary gears are connected to the second planet carrier (202), the second planetary gears are engaged with the second ring gear (203), and second internal teeth are provided on an inner wall of the second ring gear (203).
5. The single-sided step-geared input double planetary transmission according to claim 1, characterized in that the one-way stopper (3) is used to limit the rotational direction 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 changing speed in a double planetary transmission based on single-side stepped transmission input, characterized in that a second driving member and a second sun gear (201) are connected by a second input shaft (5) such that the rotational speed of the second driving member is the same as the rotational speed of the second sun gear (201); 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 part (6) are connected, so that the rotating speeds of the first planet carrier (102), the second gear ring (203) and the output part (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 for controlling the speed of a single-side stepped transmission input double planetary gear transmission according to claim 6, wherein the speed change method is used for carrying out speed change in different modes according to different working conditions of a vehicle, and comprises the following steps:
and a state A: when the vehicle starts, the first driving piece and the second driving piece simultaneously drive the first planetary row (1) and the second planetary row (2) to work, the first sun gear (101) rotates in the forward 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 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. The method of claim 7, wherein the state A comprises a transmission ratio of i for the gear stage, the first drive member drives the first sun gear (101) to rotate, and the first sun gear (101) rotates at a speed N 1 The rotating speed of the first driving part is N 1 Xi, the first ring gear (103) having a tendency to rotate in the reverse directionWhen the one-way stopper (3) acts to restrict the first ring gear (103) from rotating in the reverse direction, the rotation speed of the first ring gear (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 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 reverse, the second planet carrier (202) has a tendency of reverse rotation, and the second planet carrier (202) is connected with the first gear ring (103), wherein the reverse rotation of the second planet carrier (202) is limited by a one-way stopper (3), 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 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. The method of speed governing in a single-sided step-gear input double planetary transmission according to claim 7, wherein the speed N at which the first drive drives the first sun gear (101) in state B is 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 said first step isWhen the rotating speed of a driving piece is about to exceed the high-efficiency area, the rotating speed of the first driving piece stops increasing, the rotating speed of the second driving piece is reduced, the rotating speed of the second driving piece is gradually reduced from reverse rotation to 0, and the rotating speed N of the second sun gear (201) is reduced 4 Lowered to 0, the rotational speed N of the second ring gear (203) is reduced because the one-way stopper (3) limits only the first ring gear (103) and the second planet carrier (202) not to be reversed and does not limit the first ring gear (103) and the second planet carrier (202) to be accelerated in the forward direction 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. The method of claim 7, wherein said state C in which said first drive member drives said first sun gear (202) at a speed N 1 When the direction of rotation is reverse, the first gear ring (103) has a tendency of rotating in the forward direction, the one-way stopper (3) acts to limit the forward rotation of the first gear ring (103), and the rotating 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 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 wheel (201) to rotate, and the second sun wheelThe rotating speed direction of the wheel (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), the positive rotation of the second planet carrier (202) is limited by the one-way stopper (3), 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 rotating speed of the second driving piece is N 4 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.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202110848474.1A CN115681427A (en) | 2021-07-27 | 2021-07-27 | Single-side stepped transmission input double-planetary-row transmission and speed changing method thereof |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202110848474.1A CN115681427A (en) | 2021-07-27 | 2021-07-27 | Single-side stepped transmission input double-planetary-row transmission and speed changing method thereof |
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| Publication Number | Publication Date |
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| CN115681427A true CN115681427A (en) | 2023-02-03 |
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| CN202110848474.1A Pending CN115681427A (en) | 2021-07-27 | 2021-07-27 | Single-side stepped transmission input double-planetary-row transmission and speed changing method thereof |
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| CN (1) | CN115681427A (en) |
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