CN216078165U - Step-transmission double-planetary-row transmission - Google Patents
Step-transmission double-planetary-row transmission Download PDFInfo
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- CN216078165U CN216078165U CN202121713126.5U CN202121713126U CN216078165U CN 216078165 U CN216078165 U CN 216078165U CN 202121713126 U CN202121713126 U CN 202121713126U CN 216078165 U CN216078165 U CN 216078165U
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Abstract
The utility model discloses a step transmission 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, the first planet carrier on the first planet row is connected with a second gear ring on the second planet row, one side of the first planet row is connected with a first driving piece through a first input shaft, the same side of the second planet row is connected with a second driving piece through a second input shaft and a transmission shaft, a connector of the first gear ring and the second planet carrier is provided with a one-way stopper, and one side of the first planet carrier is connected with an output part. The step-transmission double-planet-row speed changer is characterized in that the first driving piece and the second driving piece are arranged on the same side of the stepless speed change mechanism, and the output part is arranged on the other side of the stepless speed change mechanism, so that the input position and the output position can be better separated, and the probability that the input end and the output part can interfere with each other is reduced.
Description
Technical Field
The utility model relates to the technical field of automobile transmissions, in particular to a stepped transmission double-planetary-row transmission.
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.
SUMMERY OF THE UTILITY MODEL
The utility model aims to solve the problems and designs a stepped transmission double-planetary-row transmission.
The technical scheme of the utility model is that the stepped transmission double-planet-row transmission comprises a first planet row and a second planet row, wherein a first gear ring on the first planet row is connected with a second planet carrier on the second planet row, the first planet carrier on the first planet row is connected with a second gear ring on the second planet row, one side of the first planet row is connected with a first driving piece through a first input shaft, the same side of the second planet row is connected with a second driving piece through a second input shaft and a transmission shaft, one end of the first input shaft is connected with the first driving piece, the other end of the first input shaft penetrates through a transmission gear B, the transmission shaft and a second sun gear to be connected with a first sun gear, a one-way stopper is arranged on a connecting body of the first gear ring and the second planet carrier, and one side of the first planet carrier is connected with an output component.
As a further description of the present invention, a transmission stage is disposed between the first input shaft and the transmission shaft, the transmission stage includes a transmission gear a and a transmission gear B, one end of the second input shaft is connected to the second driving member, the other end of the second input shaft is connected to the transmission gear a, the transmission gear a and the transmission gear B are engaged through external teeth, the transmission gear B is connected to one end of the transmission shaft, and the other end of the transmission shaft is connected to a second sun gear on the second planet row.
As a further description of the present invention, the first planetary row includes a first sun gear, a plurality of first planetary gears are engaged with external teeth of the first sun gear, the first planetary gears are connected to the first carrier, the first planetary gears are engaged with the first ring gear, and first internal teeth are disposed on an inner wall of the first ring gear.
As a further description of the present invention, a plurality of second planet gears are engaged with the outer teeth of the second sun gear, the second planet gears are connected to the second planet carrier, the second planet gears are engaged with the second ring gear, and the inner wall of the second ring gear is provided with second inner teeth.
As a further explanation of the present invention, the one-way stopper is for limiting the rotational directions of the first ring gear and the second carrier; the one-way stopper makes the rotational direction of the first ring gear and the second carrier coincide with only the steering of the first driver.
The utility model provides a step-transmission double-planet-row speed changer and a speed change method thereof, wherein 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 direction of the driving piece are adjusted, and the stepless speed change of an output part is realized through the matching of the first planet row, the second planet row and a one-way retainer, the mechanism has the advantages of high transmission efficiency, large output torque, no power interruption, simple and reliable structure, low manufacturing cost, easy maintenance, simple and convenient speed regulation and the like, in addition, 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 speed change mechanism, so that the positions of power input and output can be better separated, the probability that the input end and the output part can generate mutual interference is reduced, and the design can greatly improve the utilization rate of space, the whole power equipment is more reasonable in arrangement and space occupancy rate. The transmission stage is arranged between the second input shaft and the transmission shaft, and the transmission stage achieves the purpose of changing the size of the transmission ratio between the second driving piece and the second sun gear by changing the gear ratio of the transmission gear A and the transmission gear B, so that the power selection range of the second driving piece is widened by the transmission ratio provided by the transmission stage on the premise of achieving the same using effect.
Drawings
FIG. 1 is a schematic illustration of a step-drive, 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 speed vector diagram for a second planetary row as provided by an embodiment of the present invention;
FIG. 4 is a speed vector diagram for the first and second planetary rows incorporating 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 utility model under a starting condition 1;
FIG. 6 is a rotation speed vector diagram provided by the embodiment of the utility model under a starting condition 2;
FIG. 7 is a rotation speed vector diagram provided by the embodiment of the utility model 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 utility model 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 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 utility model 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 transmission has the existing problems of complex structure, high manufacturing cost, difficult maintenance and the like, so that the step transmission double-planetary-row transmission is provided.
Referring to fig. 1, a step-gear double planetary transmission includes a first planetary gear set 1, a second planetary gear set 2, a first ring gear 103 of the first planetary gear set 1 connected to a second carrier 202 of the second planetary gear set 2, a first carrier 102 of the first planetary gear set 1 connected to a second ring gear 203 of the second planetary gear set 2, a first driving member connected to one side of the first planetary gear set 1 via a first input shaft 4, a second driving member connected to the same side of the second planetary gear set 2 via a transmission shaft 8 and a second input shaft 5, a first input shaft 4 connected to the first driving member at one end and connected to the first sun gear 101 at the other end via a transmission gear B702, the transmission shaft 8 and a second sun gear 201, a one-way stopper 3 provided on a connection body of the first ring gear 103 and the second carrier 202, the first carrier 102 is connected at one side to the output member 6.
Referring to fig. 1, a transmission stage 7 is arranged between the second input shaft and the transmission shaft 8, the transmission stage 7 includes a transmission gear a701 and a transmission gear B702, one end of the second input shaft 5 is connected to the second driving member, the other end of the second input shaft is connected to the transmission gear a701, the transmission gear a701 and the transmission gear B702 are engaged through external teeth, the transmission gear B702 is connected to one end of the transmission shaft 8, and the other end of the transmission shaft 8 is connected to the second sun gear 201 of the second planetary row 2.
Referring to fig. 1, the first planetary row 1 includes a first sun gear 101, a plurality of first planet gears are engaged with external teeth of the first sun gear 101, the first planet gears are connected to a first planet carrier 102, the first planet gears are engaged with a first ring gear 103, and first internal teeth are arranged on an inner wall of the first ring gear 103.
Referring to fig. 1, a plurality of second planet wheels are engaged with the outer teeth of the second sun wheel 201, the second planet wheels are connected to the second planet carrier 202, a second ring gear 203 is engaged with the second planet wheels, and second inner teeth are arranged on the inner wall of the second ring gear 203.
Referring to fig. 1, the one-way stopper 3 serves to limit the rotational directions of the first ring gear 103 and the second carrier 202; the one-way stopper 3 makes the rotational direction of the first ring gear 103 and the second carrier 202 coincide with only the steering of the first driver.
In the following, a method of changing speed based on a step-drive double planetary transmission will be described with reference to specific configurations of embodiments of the present invention.
Referring to fig. 1, the rotation speed of the first driving member is in direct proportion to the rotation speed of the first sun gear 101; the rotation speed of the second driving member is the same as that of the second sun gear 201; the rotation speed of the first ring gear 103 is the same as the rotation speed of the second carrier 202; the rotational speed of the first carrier 102, the rotational speed of the second ring gear 203 and the rotational speed of the output member 6 are all the same.
In order to better illustrate the shifting effect of the present invention achieved by its own structure, the following needs to 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 Z1The number of teeth of the first ring gear 103 is Z2(ii) a The number of teeth of the second sun gear 201 is Z3The number of teeth of the second ring gear 203 is Z4。
The rotating speed of the first driving piece driving the first sun gear 101 is set to be N1；
The rotating speed of the second driving member driving the second sun gear 201 is set to N4；
The rotation speed of the first ring gear 103 and the rotation speed of the second carrier 202 are set to N3；
The rotational speeds of the first carrier 102, the second ring gear 203 and the output member 6 are all set to be N2；
Obtaining a rotation speed vector diagram 2, N of a first planet row 1 according to a rotation speed vector calculation method of the planet gear1Is the rotational speed of the first sun gear 101, N2Is the rotational speed of the first carrier 102, N3Is the rotational speed of the first ring gear 103. N is a radical of1、N2、N3The 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 L2/L1═ first sun gear 101 tooth number Z1) /(number of teeth Z of first ring gear 103)2)。
Obtaining a rotation speed vector diagram 3, N of the second planet row 2 according to a rotation speed vector calculation method of the planet gear4Is the rotational speed, N, of the second sun gear 2013Is the rotational speed, N, of the second planet carrier 2022Is the rotational speed of the second ring gear 203. N is a radical of2、N3、N4The 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 L2/L3(number of teeth Z of second sun gear 201)3) /(second ring gear 203 number of teeth Z4)。
Combining FIG. 2 and FIG. 3 into FIG. 4, N1Is the rotational speed of the first sun gear 101; n is a radical of4Is the rotational speed of the second sun gear 201; n is a radical of2Is 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 of3The 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 1011Determining the rotational speed N of the second sun gear 2014Determining the rotational speed N of the output part 62And 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 regulation2Is continuously varied.
When starting, the first driving piece drives the first sun gear 101 at the rotating speed of N1The second driving member drives the second sun gear 201 at a speed N4。
1) Starting mode 1
As shown in FIG. 5, the rotational speed N of the first sun gear 101 is set1And the rotational speed N of the second sun gear 2014Is [ Z ] of3X(Z1+Z2)]/(Z1×Z4) The rotation speed of the first ring gear 103 and the rotation speed N of the second carrier 2023Always 0, the rotation speed N of the first sun gear 101 driven by the first driving member1And the rotational speed N at which the second driving member drives the second sun gear 2014Is gradually increased to output a rotation speed N2Gradually increased, and the steering direction is positive.
2) Starting mode 2
As shown in fig. 6, when the first sun gear 101 rotates at a speed N1And the rotational speed N of the second sun gear 2014Is greater than [ Z ]3×(Z1+Z2)]/(Z1×Z4) While following the rotational speed N of the first sun gear 1011And the rotational speed N of the second sun gear 2014Is gradually increased to output a rotation speed N2Gradually 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 2023Gradually 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 occurs1And the rotational speed N of the second sun gear 2014Is less than [ Z ]3×(Z1+Z2)]/(Z1×Z4) The rotational speed N of the output member 62In 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 2023The 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 62Is always positive. When the rotation speed N of the second sun gear 2014When 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 appear2Is 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 23A positive orientation is possible without causing the first and second drivers to drag against each other.
Therefore, at the time of starting, the rotation speed N1 of the first sun gear 101 is controlled by the first driver and the rotation speed N of the second sun gear 201 is controlled by the second driver4The rotational speed N of the first sun gear 101 is set1And rotation of the second sun gear 201Speed N4Is greater than or equal to [ Z ]3×(Z1+Z2)]/(Z1×Z4). For the first planet row 1, the input is carried out by the first sun gear 101, the output is carried out by the first planet carrier 102, and the working process is a speed-reducing and torque-increasing process; for the second planet row 2, the input is from the second sun gear 201, the output is from the second ring gear 203, and the working process is also the process of speed reduction and torque increase. And because the first planet carrier 102 and the second ring gear 203 are connected together, the power of the first driving element and the power of the second driving element are coupled together through the first planet row 1 and the second planet row 2, and the speed reduction and torque increase output is carried out.
The acceleration and deceleration process drives the second sun wheel 201 according to the rotation speed N of the second driving member4The 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 N1The rotation direction is positive, and the second driving member drives the second sun gear 201 at the rotation speed N4The direction of rotation is reversed. Controlling the rotational speed N of the first sun gear 1011And the rotational speed N of the second sun gear 2014The rotational speed N of the first sun gear 101 is set1And the rotational speed N of the second sun gear 2014Is greater than or equal to [ Z ]3×(Z1+Z2)]/(Z1×Z4). By controlling the speed of rotation N of the first sun gear 1011And the rotational speed N of the second sun gear 2014The rotating speed N of the output part 6 can be realized by the rotating speed of (3) and the increasing and decreasing speed2Gradually 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 N1The rotation direction is positive, and the second driving member drives the second sun gear 201 at the rotation speed N4The direction of rotation is the forward direction. By controlling the speed of rotation N of the first sun gear 1011And the rotational speed N of the second sun gear 2014The output rotating speed N can be realized by the size of the speed and the speed degree of increasing and decreasing the speed2Gradually increasing or decreasing, the direction is positive. In this operating mode, the rotational speed of the first drive element and the secondWhen the rotating speeds of the two driving pieces reach the maximum rotating speed, the rotating speed N is output2A maximum is also reached, at which time the vehicle reaches a maximum speed. If the rotational speed N1 of the first sun gear 101 driven by the first drive element and the rotational speed N of the second sun gear 201 driven by the second drive element are equal4Is the same, then the output speed N is2The 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 unchanged2The 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 element2The size of (2). At the speed N of the output member 62In the process of acceleration or deceleration, the first driving part and the second driving part can set the acceleration, deceleration and maintaining rotating speed of the first driving part and the second driving part according to the current working condition according to different respective high-efficiency areas. Therefore, the first driving part and the second driving part can work in respective high-efficiency areas for a long time, and the energy-saving effect is improved.
As shown in FIG. 10, during reverse, the first driving member drives the first sun gear 101 at a rotation speed N1The direction of rotation is reverse, and the second driving member drives the second sun gear 201 at a speed N4The 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 1011And the rotational speed N of the second sun gear 2014Is greater than or equal to [ Z ]3×(Z1+Z2)]/(Z1×Z4). 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 speed2Gradually 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 fails2When the forward 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 restrict the first ring gear 103 and the second ring gear 103Rotational speed N of the two planetary carriers 2023The 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 disabled, and the second driving member drives the second sun gear 201 at a rotating speed N4When 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 20230, rotational speed N of the output member 62For forward rotation, the second drive member is powered through the gear stage 7 and the second planetary row 2 at a fixed gear ratio i × (Z)4/Z3) And (5) reducing and increasing torque output.
As shown in fig. 12, when the second driving member fails due to a failure, the first driving member can continue to drive the vehicle. The second driving member is disabled, and the first driving member drives the first sun gear 101 at a rotating speed N1When 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 reduced30, rotational speed N of the output member 62For forward rotation, the power of the first driving member passes through the first planetary row 1 at a fixed transmission ratio [ (Z)1+Z2)/Z1]And (5) reducing and increasing torque output.
Therefore, when one driving part fails, the other driving part can still drive the vehicle to run, and although the dynamic property is reduced, the vehicle can run to a maintenance place or a safety place by means of the one driving part, so that the reliability of the vehicle can be greatly improved.
Finally, a continuous and complete description of the starting and accelerating processes of the first driving member and the second driving member is provided as follows:
as shown in fig. 13, curve 1 represents the time-dependent speed of rotation of the first sun gear 101 driven by the first driver, curve 2 represents the time-dependent speed of rotation of the second sun gear 201 driven by the second driver, and curve 3 represents the time-dependent speed of rotation of the output member 6. In the starting stage, the first driving piece drives the first sun gear 101 to rotate at a gradually increased speed, and the rotation direction is positive; the second driving element drives the second sun gear 201 to rotate at a gradually increasing speed, and the rotation direction is reverse; the rotating speed of the output part is synchronously increased, and the rotation direction is positive; the transmission ratio is the biggest this moment, and first driving piece and second driving piece all are the speed reduction and increase the torsion output, and the vehicle is with the big moment of torsion of low-speed start. In the acceleration stage, the first driving 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 member1And the rotational speed N at which the second driving member drives the second sun gear 2014Since the maximum value of (2) is the same, the rotation speed of the output member is the same as the maximum rotation speed of the first sun gear 101 and the second sun gear 201, the gear ratio is 1, and the vehicle speed is the highest.
The step transmission double-planetary-row speed changer provided by the embodiment of the utility model has the following advantages:
1. the step transmission double-planet-row transmission provided by the embodiment of the utility model has no power interruption in the speed regulation process, runs quietly and stably, has better vehicle using experience when a user uses a vehicle, can greatly meet the requirements of customers in sense, and lays a good foundation for popularization and use of the product.
2. The stepped transmission double-planetary-row transmission can realize that the output part 6 has large torque from low speed to high speed, the vehicle has the capability of quickly accelerating to start when driving by outputting the large torque, the large torque can climb a larger slope when climbing, and the large torque can also meet the requirements of more people on vehicle use, so that the audience area of the product is larger.
3. The step transmission double-planetary-row transmission can realize the stepless change of the output rotating speed, so that the driving piece at the input end can work in a high-efficiency working interval for a long time, the working efficiency is improved, the effect of saving more energy can be achieved in the aspect of energy use, and more contribution can be made in the aspect of energy saving.
4. The step transmission double-planetary-row transmission provided by the embodiment of the utility model has the advantages that the speed regulation is simple and convenient, and the stepless continuous change of the output rotating speed can be realized only by controlling the rotating speeds of the first driving piece and the second driving piece, so that the requirement of a vehicle on a control system is reduced, the popularization and application range of the product is wider, and the popularization and popularity of the product are ensured to a certain extent.
5. According to the embodiment of the utility model, 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 utility model not only can be driven by adopting the double driving parts, but also can be matched with the driving part with smaller volume and lower rotating speed, the driving part with small volume is more beneficial to the arrangement design of the driving part in the vehicle body, the aesthetic design of the appearance of the vehicle body at the later stage is more convenient, and the cost can be saved by using the smaller driving part.
7. The step-transmission double-planetary-row transmission has high transmission rate, the motor with lower power and lower rotating speed can be selected as the driving piece under the same working condition, and compared with a high-power battery, the low-power battery can better prevent the battery from overheating, and the use safety of the battery is indirectly improved through the embodiment of the utility model.
8. The step transmission double-planetary-row transmission provided by the embodiment of the utility model has the advantages that the first driving piece and the second driving piece are arranged on the same side of the stepless speed change mechanism, the output part is arranged on the other side of the stepless speed change mechanism, the input position and the output position can be better separated, the probability that the input end and the output part interfere with each other is reduced, the utilization rate of space can be greatly improved by the design, and the whole power equipment is more reasonable in arrangement and space occupancy rate.
9. The step transmission double-planetary-row transmission provided by the embodiment of the utility model is provided with the transmission stage between the second input shaft and the transmission shaft, and the transmission stage achieves the purpose of changing the transmission ratio between the second driving piece and the second sun gear by changing the gear ratio of the transmission gear A and the transmission gear B, so that the transmission ratio provided by the transmission stage widens the power selection range of the second driving piece on the premise of achieving the same use effect.
The technical solutions described above only represent the preferred technical solutions of the present invention, and some possible modifications to some parts of the technical solutions by those skilled in the art all represent the principles of the present invention, and fall within the protection scope of the present invention.
Claims (5)
1. A stepped transmission double-planet-row transmission is characterized by comprising a first planet row (1) and a second planet row (2), wherein a first gear ring (103) on the first planet row (1) is connected with a second gear ring (202) on the second planet row (2), a first planet carrier (102) on the first planet row (1) is connected with a second gear ring (203) on the second planet row (2), 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 transmission shaft (8) and a second input shaft (5), one end of the first input shaft (4) is connected with the first driving piece, and the other end of the first input shaft penetrates through the transmission gear B (702), the transmission shaft (8) and the interior of a second sun gear (201) to be connected with a first sun gear (101), a one-way stopper (3) is arranged on a connecting body of the first ring gear (103) and the second planet carrier (202), and one side of the first planet carrier (102) is connected with an output component (6).
2. A step-gear double planetary transmission according to claim 1, characterized in that a transmission stage (7) is arranged between the second input shaft (5) and the transmission shaft (8), the transmission stage (7) comprises a transmission gear a (701) and a transmission gear B (702), one end of the second input shaft (5) is connected to the second driving member, the other end is connected to the transmission gear a (701), the transmission gear a (701) and the transmission gear B (702) are engaged by external teeth, the transmission gear B (702) is connected to one end of the transmission shaft (8), and the other end of the transmission shaft (8) is connected to the second sun gear (201) on the second planetary row (2).
3. A step-gear double planetary transmission according to claim 1, wherein the first planetary gear (1) comprises a first sun gear (101), a plurality of first planet gears are engaged on the outer teeth of the first sun gear (101), the first planet gears are connected to the first carrier (102), the first planet gears are engaged with the first ring gear (103), and first inner teeth are provided on the inner wall of the first ring gear (103).
4. A step-gear double row transmission according to claim 1, characterised in that the second planetary row (2) comprises a second sun wheel (201), which second sun wheel (201) is externally toothed with a number of second planet wheels, which second planet wheels are connected to the second planet carrier (202), which second planet wheels are in engagement with the second ring gear (203), which second ring gear (203) is internally toothed with a second internal toothing.
5. A step-geared double planetary transmission according to claim 1, characterized in that the one-way stopper (3) is used to limit the direction of rotation of the first ring gear (103) and second carrier (202); the one-way stopper (3) makes the rotational direction of the first ring gear (103) and the second carrier (202) coincide with only the steering of the first sun gear (101).
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202121713126.5U CN216078165U (en) | 2021-07-27 | 2021-07-27 | Step-transmission double-planetary-row transmission |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202121713126.5U CN216078165U (en) | 2021-07-27 | 2021-07-27 | Step-transmission double-planetary-row transmission |
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| CN216078165U true CN216078165U (en) | 2022-03-18 |
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| CN202121713126.5U Active CN216078165U (en) | 2021-07-27 | 2021-07-27 | Step-transmission double-planetary-row transmission |
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