CN115681428A - Dual-drive coupling stepless speed change mechanism and speed change method thereof - Google Patents
Dual-drive coupling stepless speed change mechanism and speed change method thereof Download PDFInfo
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- CN115681428A CN115681428A CN202110848487.9A CN202110848487A CN115681428A CN 115681428 A CN115681428 A CN 115681428A CN 202110848487 A CN202110848487 A CN 202110848487A CN 115681428 A CN115681428 A CN 115681428A
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Abstract
The invention discloses a dual-drive coupling stepless speed change mechanism, which belongs to the technical field of a stepless speed changer and comprises a first planet row, a second planet row and a one-way stopper, wherein a first gear ring is connected with a second planet carrier, the first planet carrier is connected with a second gear ring, 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, the first driving piece is arranged on one side of the second driving piece, the second planet row is arranged on the other side of the second driving piece, and the one-way stopper is arranged on a connecting body of the first gear ring and the second planet carrier. The dual-drive coupling stepless speed change mechanism 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, so that the input position and the output position are 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 a continuously variable transmission, in particular to a dual-drive coupling continuously variable transmission mechanism and a transmission method thereof.
Background
With the higher and higher requirements of the society on environmental protection, the electric vehicle technology becomes the mainstream research direction of each large vehicle enterprise. At present, the electric vehicle mostly adopts a speed reducer with a fixed speed ratio, although the speed reducer with a large speed ratio can be selected to meet the power requirement when the vehicle starts and climbs, the large speed ratio limits the vehicle to be incapable of reaching a high maximum speed, and the reason that the maximum speed of the electric vehicle is generally lower than the maximum speed of a fuel vehicle on the market is also provided. In order to take account of the highest speed and the climbing capability of a vehicle, a plurality of vehicle enterprises begin to install AMT transmissions on electric vehicles, but the AMT transmissions belong to step-by-step speed change in principle, and have the problems of gear shifting, gear shifting and power interruption in the prior art; the transmission ratio range of the AMT is limited by gear setting and is applied to heavy vehicles, in order to expand the transmission ratio range, a large number of gears need to be set, the gear shifting process is slow, the operation is complex, and a lot of drivers of large vehicles are reluctant to step on the brake; the AMT gear shifting process depends on a complex control strategy, the accurate gear shifting time is difficult to master, and the problems of high energy consumption and low efficiency exist; the AMT transmission has the disadvantages of complex structure, high manufacturing cost and difficult maintenance.
Disclosure of Invention
The invention aims to solve the problems and designs a double-drive coupling stepless speed change mechanism and a speed change method thereof.
The technical scheme of the invention is that the dual-drive coupling stepless speed change mechanism comprises a first planet row, a second planet row and a one-way stopper, wherein the first planet row is provided with a first sun gear, a first planet carrier and a first gear ring, the second planet row is provided with a second sun gear, a second planet carrier and a second gear ring, the first gear ring is connected with the second planet carrier, the first planet carrier is connected with the second gear ring, 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, the first driving piece is arranged on one side of the second driving piece, the second planet row is arranged on the other side of the second driving piece, the connector of the first gear ring and the second planet carrier is provided with the one-way stopper, and one side of the first planet carrier is connected with an output component.
As a further description of the present invention, one end of the second input shaft is connected to the second driving element, and the other end is connected to the second sun gear; one end of the first input shaft is connected with the first driving part, and the other end of the first input shaft penetrates through the second driving part, the second input shaft and the second sun gear to be connected with the first sun gear.
As a further description of the present invention, the first sun gear is engaged with a first planet gear, the first planet gear is mounted on the first planet carrier, the first planet gear is engaged with the first ring gear, and the inner wall of the first ring gear is provided with first internal teeth.
As a further explanation of the present invention, the second sun gear is engaged with a second planetary gear, the second planetary gear is mounted on the second planetary carrier, the second planetary gear is engaged with the second gear ring, and the inner wall of the second gear ring is provided with first internal teeth.
As a further explanation of the present invention, the one-way stopper is for limiting the rotational direction 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 dual-drive coupling stepless speed change mechanism, wherein a first driving piece and a first sun gear are connected through a first input shaft, so that the rotating speed of the first driving piece is the same as that of the first sun gear; the second driving piece and the second sun gear are connected through a second input shaft, so that the rotating speed of the second driving piece is the same as that of the second sun gear; the rotating speeds of the first gear ring and the second planet carrier are the same; the rotating speeds of the first planet carrier, the second gear ring and the output part are the same; the rotating speed of the first driving part and the rotating speed of the second driving part are adjusted and controlled, stepless continuous change of the rotating speed of the output part is achieved, and in the process, the speed ratio can be correspondingly changed.
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 work simultaneously, and the rotating speed direction is opposite; the first driving part rotates in a forward direction, and the second driving part rotates in a reverse direction; the maintenance, transition and switching can be easily finished by controlling the rotating speed of the first driving part and the second driving part according to actual requirements, 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 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 then the rotating speed of the second driving piece and the rotating speed of the first driving piece start to be in the same direction; when the vehicle reaches the maximum speed, the steering directions of the first driving piece and the second driving piece are the same, and the first driving piece and the second driving piece 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, the rotational speed of first driving piece is the reversal, the rotational speed of second driving piece is forward.
As a further explanation of the invention, the rotational speed of the first drive member in state A is N 1 So that the rotation 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 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 member drives the second sun gear to rotate, soThe rotating speed direction of the second sun gear is reverse, the second planet carrier has a tendency of reverse rotation, and the second planet carrier is connected with the first gear ring, wherein 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 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.
As a further elaboration of the invention, the speed N of the first sun gear in state B is 1 Increasing the rotational speed N of the first carrier 2 Increasing the rotation speed of the second driving member and the rotation speed N of 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 Lowered to 0, the rotational speed N of the second ring gear since the one-way stopper restricts only the first ring gear and the second carrier from being reversed and does not restrict the first ring gear and the second carrier from being accelerated in the forward direction 2 And when the rotation speed of the output component is increased continuously, the second planet carrier starts to rotate forwards at the rotation speed of N 3 ；
The second driving member starts to rotate forwards, and when the rotation speed of the second driving member and the rotation of the first driving member are equalWhen the speeds are the same, the rotating speed of the first sun gear is equal to the rotating speed 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 planet 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 elaboration of the invention, the rotational speed of the first drive member in state C is N 1 The direction of rotation is reverse, and the rotational speed of the second drive member is N 4 The steering direction is positive, the first gear ring has the tendency of positive rotation, the one-way retainer acts at the moment to limit the positive 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 gear 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 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 dual-drive coupling stepless speed change mechanism 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 a first planet row, a second planet row and a one-way retainer.
Drawings
FIG. 1 is a schematic structural diagram of a dual-drive coupled continuously variable 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 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 of the combination of FIGS. 1 and 2 provided by an embodiment of the present invention;
FIG. 5 is a rotation speed vector diagram 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 speed vector diagram 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 graph of rotational speed provided by an embodiment of the present invention during launch and acceleration of the first driver, the second driver 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 brake, 4-first input shaft, 5-second input shaft, 6-output member.
Detailed Description
Firstly, the purpose of the invention is explained, and the invention aims to solve the problems of gear shifting pause and power interruption existing in the AMT; 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, 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 a dual-drive coupling stepless speed change mechanism is provided to solve the existing problems.
Referring to fig. 1, a double-drive coupling continuously variable transmission mechanism includes a first planet row 1, a second planet row 2 and a one-way stopper 3, where the first planet row 1 is provided with a first sun gear 101, a first planet carrier 102 and a first ring gear 103, the second planet row 2 is provided with a second sun gear 201, a second planet carrier 202 and a second ring gear 203, the first ring gear 103 is connected with the second planet carrier 202, the first planet carrier 102 is connected with the second ring gear 203, one side of the first planet row 1 is connected with a first driving member through a first input shaft 4, one side of the second planet row 2 is connected with a second driving member through a second input shaft 5, the first side is installed on one side of the second driving member, the second planet row 2 is installed on the other side of the second driving member, the connecting body of the first ring gear 103 and the second planet carrier 202 is provided with the one-way stopper 3, and one side of the first planet carrier 102 is connected with an output member 6.
Referring to fig. 1, one end of the second input shaft is connected to the second driving member, and the other end is connected to the second sun gear; one end of the first input shaft is connected with the first driving piece, and the other end of the first input shaft penetrates through the second driving piece, the second input shaft and the second sun gear to be connected with the first sun gear.
Referring to fig. 1, a first sun gear 101 is engaged with a first planetary gear, the first planetary gear is mounted on a first carrier 102, the first planetary gear is engaged with a first ring gear 103, and first internal teeth are provided on an inner wall of the first ring gear 103.
Referring to fig. 1, a second planet gear is engaged with the second sun gear 201, the second planet gear is mounted on the second planet carrier 202, the second planet gear is engaged with the second ring gear 203, and the inner wall of the second ring gear 203 is provided with first inner teeth.
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, we need to describe a speed change method based on an electric vehicle stepless speed change mechanism by combining with the specific structure of the invention.
According to the basic principle of the planetary gear, the rotating speeds of any two of three members, namely a sun gear, a ring gear and a planet carrier, 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 rotational speed of the first driving member and the rotational speed of the first sun gear 101 are set to N 1 ；
The rotational speed of the second driving member and the rotational speed of the second sun gear 201 are 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 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 (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 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 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 )。
FIG. 4 is a combination of FIG. 2 and FIG. 3 1 Is the rotational speed of the first sun gear 101 and the first driver; n is a radical of hydrogen 4 Is the rotational speed of the second sun gear 201 and the second drive; 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 3 The rotation speed of the first ring gear 103 and the second carrier 202; from the figure4 the speed N of the entire mechanism, the first drive element 1 Determining the rotational speed N of the second drive element 4 Determining the rotational speed N of the output member 6 2 And is also uniquely determined.
Controlling the speed N of the first drive member by regulation 1 And the rotational speed N of the second drive member 4 The rotational speed N of the output member 6 can be realized 2 Is continuously varied.
When starting, the rotating speed of the first driving piece is N 1 The direction of rotation is forward, and the rotation speed of the second driving member is N 4 The direction of rotation is reversed.
1) Starting condition 1
As shown in FIG. 5, the rotation speed N of the first driving member is set 1 And the rotational speed N of the second drive member 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 Is always 0, and the rotating speed N of the first driving part is changed 1 And the rotational speed N of the second drive member 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 driving member rotates at a speed N 1 And the rotational speed N of the second drive member 4 Is greater than [ Z ] 3 ×(Z 1 +Z 2 )]/(Z 1 ×Z 4 ) While following the rotation speed N of the first driving member 1 And the rotational speed N of the second drive member 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 maintenance, the transition and the switching can be easily completed by controlling the rotating speeds of the first driving part and the second driving part according to actual needs, the whole process is continuous and smooth, and no power interruption exists.
If the rotational speed of the first and second drivers is not controlled, as shown in FIG. 7Accuracy or control failure, when the rotational speed N of the first drive member occurs 1 And the rotational speed N of the second drive member 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. This ensures the rotational speed N of the output part 6 2 Is always in the forward direction. When the rotational speed N of the second driving member 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 rotating speed N1 of the first driving piece and the rotating speed N of the second driving piece are controlled 4 Make the rotational speed N of the first driving member 1 And the rotational speed N of the second drive member 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 being in accordance with the rotational speed N of the second drive member 4 The steering is divided into two working conditions.
1) Working condition 1
As shown in FIG. 8, the first driving member rotates at a speed N 1 The direction of rotation is forward, and the rotation speed of the second driving member is N 4 The direction of rotation is reversed. Controlling the speed N of the first drive member 1 And the rotational speed N of the second drive member 4 Make the rotational speed N of the first driving member 1 And the rotational speed N of the second drive member 4 Is greater than or equal to [ Z ] 3 ×(Z 1 +Z 2 )]/(Z 1 ×Z 4 ). By controlling the speed N of the first drive member 1 And the rotational speed N of the second drive member 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 rotates at a speed N 1 The direction of rotation is positive, and the rotational speed of the second driving member is N 4 The direction of rotation is also positive. By controlling the speed N of the first drive member 1 And the rotational speed N of the second drive member 4 The output rotating speed N can be realized by the rotating speed of the speed-increasing and speed-reducing device 2 Gradually increasing or decreasing, the direction of rotation is positive. Under the working condition, the rotating speed N of the first driving part 1 And the rotational speed N of the second drive member 4 When the rotating speed reaches 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 rotational speed N of the first drive member 1 And the rotational speed N of the second drive member 4 Are the same, then the output speed N is 2 The same is true for the maximum value that can be reached, which is a transmission ratio of 1.
As shown in fig. 8 and 9, when acceleration and deceleration are performed according to the above-described operating condition 1 and operating condition 2, the rotation speed N of the first driving element can be maintained 1 Without change, by adjusting the speed N of the second drive member 4 To adjust the output speed N 2 Can also maintain the rotating speed of the second driving piece to be N 4 Without change, by adjusting the rotation speed of the first driving member to N 1 To adjust the output speed N 2 The size of (2).
At the moment of realizing the rotation speed of the output member 6N 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 rotates at a speed N in reverse 1 The direction of rotation being reversed and the rotational speed of the second drive member being N 4 The direction of rotation is the forward direction. Controlling the rotational speed N of the first drive member 1 And the rotational speed N of the second drive member 4 Make the rotational speed N of the first driving member 1 And the rotational speed N of the second drive member 4 Is greater than or equal to [ Z ] 3 ×(Z 1 +Z 2 )]/(Z 1 ×Z 4 ). By controlling the speed N of the first drive member 1 And the rotational speed N of the second drive member 4 The rotating speed and the speed increasing and decreasing degree of the rotating speed can realize the output of the rotating speed N 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 (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 rotating speed of the second driving member is 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 one-way stopper 3 restricts the reverse rotation, 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 failed, and the rotating speed of the first driving member is 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 Is 0, the rotational speed N of the output terminal 6 2 For forward rotation, the power of the first driving member passes through the first planetary row 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 first driver speed over time, curve 2 represents the second driver speed over time, and curve 3 represents the output speed over time. In the starting stage, the rotating speed of the first driving piece is gradually increased, and the steering direction is positive; the rotating speed of the second driving piece is gradually increased, and the rotating direction is reverse; the rotating speed of the output end is synchronously increased, and the rotating 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 rotating speed of the first driving part is continuously accelerated, and the rotating speed is kept unchanged after the rotating speed reaches a certain rotating speed; the rotating speed of the second driving piece is accelerated reversely, then is reduced to 0, and finally is accelerated forwards; the rotating speed of the output end is always accelerated in the positive direction, the transmission ratio is gradually reduced in the process, and the rotating speed of the output end is continuously and steplessly changed. In the highest speed stage, the rotating speeds of the first driving piece and the second driving piece reach the highest rotating speed, and the rotating speed of the output end also reaches the highest rotating speed; in the highest vehicle speed stage, the rotation speeds of the first driving element and the second driving element both reach the highest rotation speed, and the rotation speed of the output member also reaches the highest rotation speed, and fig. 13 shows the case where the highest rotation speeds of the first driving element and the second driving element are the same, so that the rotation speed of the output member is also the same as the highest rotation speeds of the first driving element and the second driving element, the transmission ratio is 1, and the vehicle speed reaches the highest. The starting and accelerating application conditions of other different forms are not listed.
The dual-drive coupling stepless speed change mechanism and the speed change method thereof provided by the embodiment of the invention have the following advantages:
1. the dual-drive coupling stepless speed change mechanism provided by the embodiment of the invention has no power interruption in the speed regulation process, runs quietly and stably, has better vehicle using experience when a user uses a vehicle, can greatly meet the requirements of customers in sense, and lays a good foundation for popularization and use of the product.
2. The dual-drive coupling stepless speed change mechanism can realize that the output part 6 has large torque from low speed to high speed, and the vehicle has the capability of quickly accelerating starting by outputting the large torque when driving, the large torque can climb larger gradient when climbing the slope, and the large torque can also meet the vehicle demand of more people, so that the audience area of the product is larger.
3. The dual-drive coupling stepless speed change mechanism can realize stepless continuous change of output rotating speed, the driving piece at the input end can work in a high-efficiency interval for a long time, the working efficiency is improved, the effect of saving more energy can be achieved in the aspect of energy use, and more contributions can be made in the aspect of energy saving.
4. The dual-drive coupling stepless speed change mechanism provided by the embodiment of the invention has the advantages that the speed regulation is simple and convenient, and the stepless continuous change of the output rotating speed can be realized only by controlling the rotating speeds of the first driving part and the second driving part, 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 means of the other driving part and drive the vehicle to a maintenance site in time, the occurrence of a trailer calling event is avoided, and the vehicle using experience of the vehicle owner is better taken care of.
6. Compared with the traditional driving mode of a single driving part, the product provided by the embodiment of the invention not only can be driven by adopting the double driving parts, but also can be matched with the driving part with smaller volume and lower rotating speed, the driving part with small volume is more beneficial to the arrangement design of the driving part in the vehicle body, the aesthetic design of the appearance of the vehicle body at the later stage is more convenient, and the cost can be saved by using the smaller driving part.
7. The dual-drive coupling stepless speed change mechanism 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 battery with low power can better prevent the battery from overheating, and the use safety of the battery is indirectly improved through the embodiment of the invention.
8. The dual-drive coupling stepless speed change mechanism 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, and the first input shaft passes through the second input shaft and the second driving piece to be connected with the first driving piece.
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 double-drive-coupling continuously variable transmission mechanism is characterized by comprising a first planet row (1), a second planet row (2) and a one-way stopper (3), wherein a first sun gear (101), a first planet carrier (102) and a first gear ring (103) are arranged on the first planet row (1), a second sun gear (201), a second planet carrier (202) and a second gear ring (203) are arranged on the second planet row (2), the first gear ring (103) is connected with the second planet carrier (202), the first planet carrier (102) is connected with the second gear ring (203), one side of the first planet row (1) is connected with a first driving piece through 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), the first driving piece is installed on one side of the second driving piece, the other side of the second planet row (2) is arranged on the other side of the second driving piece, the first gear ring (103) and the second planet carrier (202) are provided with a one-way stopper (6), and an output component of the planet carrier (102) is connected with the first stopper (3).
2. The dual-drive coupling continuously variable transmission mechanism according to claim 1, wherein the second input shaft (5) is hollow tubular, one end of the second input shaft (5) is connected to the second driving member, and the other end is connected to the second sun gear (201); one end of the first input shaft (4) is connected with the first driving part, and the other end of the first input shaft passes through the second driving part, the second input shaft (5) and the second sun gear (201) to be connected with the first sun gear (101).
3. A dual drive coupling continuously variable transmission according to claim 1, wherein a first planet wheel is engaged with the first sun gear (101), the first planet wheel is mounted on the first carrier (102), the first planet wheel is engaged with the first ring gear (103), and first internal teeth are provided on an inner wall of the first ring gear (103).
4. A dual drive coupling continuously variable transmission according to claim 1, wherein said second sun gear (201) is engaged with a second planetary gear, said second planetary gear is mounted on said second planet carrier (202), said second planetary gear is engaged with said second ring gear (203), and said second ring gear (203) has a first internal tooth disposed on its inner wall.
5. A dual drive coupling continuously variable transmission mechanism according to claim 1, wherein said one-way stopper (3) is used to limit the rotational direction of said 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 driver.
6. A speed change method based on a dual-drive coupling stepless speed change mechanism is characterized in that a first driving piece and a first sun gear (101) are connected through a first input shaft (4), so that the rotating speed of the first driving piece is the same as that of the first sun gear (101); the second driving piece and the second sun gear (201) are connected through a second input shaft (5), so that the rotating speed of the second driving piece is the same as that of the second sun gear (201); the rotating speeds of the first gear ring (103) and the second planet carrier (202) are the same; the rotating speeds of the first planet carrier (102), the second gear ring (203) and the output component (6) are the same; the stepless continuous change of the rotating speed of the output component (6) 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.
7. The speed change method of the dual-drive coupling continuously variable transmission mechanism according to claim 6, wherein the speed change method performs speed change in different modes according to different working conditions of a vehicle, and specifically comprises the following steps:
and a state A: when the vehicle starts, the first driving piece and the second driving piece work simultaneously, and the rotating speed direction is opposite; the first driving piece rotates in the forward direction, and the second driving piece rotates in the reverse direction; the maintenance, transition and switching can be easily finished 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 is interrupted;
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 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 to 0 from reverse rotation, and then the rotating speed of the second driving piece is in the same direction as the rotating speed of the first driving piece; when the vehicle reaches the maximum speed, the steering directions of the first driving piece and the second driving piece are the same, and the first driving piece and 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, the rotational speed of first driving piece is the reversal, the rotational speed of second driving piece is forward.
8. The method according to claim 7, wherein the speed of the first driving member in state A is N 1 So that the rotational speed of the first sun gear (101) is 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 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 the tendency of reverse rotation, and the second planet carrier (202) and the second sun gear (201) rotate in the same directionThe first ring gear (103) is connected, wherein a one-way stopper (3) limits the reverse rotation of the second planet carrier (202), and the rotation 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.
9. The method for shifting a dual drive-coupled continuously variable transmission according to claim 7, wherein the rotation speed N of the first sun gear (101) in the state B is N 1 Increasing the rotational speed N of the first planet carrier (102) 2 Increasing the rotational speed of the second drive, increasing the rotational speed N of 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 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, gradually reducing the rotating speed of the second driving piece from reverse rotation to 0, and enabling the rotating speed N of the second sun gear (201) to be equal to or lower than the high-efficiency area 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 limits the first ring gear (103) and the second planet carrier (202) not to be accelerated in the forward direction 2 The rotation speed of the output component (6) is increased continuously, the second planet carrier (202) starts to rotate forwards, and the rotation speed is N 3 ；
The second driving member starts to rotate forwards, and when the rotating speed of the second driving member is the same as that of the first driving member, 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 the first driver has a speed N in state C 1 The direction of rotation is reverse, and the rotational speed of the second drive member is N 4 When the direction of rotation is positive, the first gear ring (103) has the tendency of rotating in the positive direction, the one-way stopper (3) acts to limit the positive 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 decelerated and torque-increased to 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), the one-way stopper (3) limits the positive 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 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 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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| CN113483066A (en) * | 2021-07-27 | 2021-10-08 | 苏州擎驰传动有限公司 | Single-side input and output continuously variable transmission and speed change method thereof |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113483066A (en) * | 2021-07-27 | 2021-10-08 | 苏州擎驰传动有限公司 | Single-side input and output continuously variable transmission and speed change method thereof |
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