CN215763092U - Dual-drive four-planet-row stepless speed change mechanism - Google Patents
Dual-drive four-planet-row stepless speed change mechanism Download PDFInfo
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- CN215763092U CN215763092U CN202122300104.2U CN202122300104U CN215763092U CN 215763092 U CN215763092 U CN 215763092U CN 202122300104 U CN202122300104 U CN 202122300104U CN 215763092 U CN215763092 U CN 215763092U
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Abstract
The utility model discloses a dual-drive four-planet-row stepless speed change mechanism, which belongs to the technical field of stepless speed changers and comprises a first planet row, a second planet row, a third planet row and a fourth planet row, wherein a first gear ring on the first planet row is connected with a second sun gear on the second planet row through a first connecting shaft, a second gear ring on the second planet row is connected with a third planet carrier on the third planet row, the third planet carrier on the third planet row is connected with a fourth sun gear on the fourth planet row through a second connecting shaft, the fourth planet carrier on the fourth planet row is connected with an output part, and one side of a connector with the rotating speed is provided with a one-way stopper. The utility model also discloses a speed change method of the dual-drive four-planet-row stepless speed change mechanism. The connecting ends of the input end and the output end of the dual-drive four-planet-row stepless speed change mechanism are respectively arranged at the two ends of the dual-drive four-planet-row stepless speed change mechanism, so that the condition that the input end and the output end can be mutually influenced when in operation is avoided, and the integral failure rate is further reduced.
Description
Technical Field
The utility model relates to the technical field of continuously variable transmissions, in particular to a dual-drive four-planet-row continuously variable transmission mechanism.
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 dual-drive four-planet-row stepless speed change mechanism.
The technical scheme of the utility model is that the dual-drive four-planet-row stepless speed change mechanism comprises a first planet row, a second planet row, a third planet row and a fourth planet row, wherein a first gear ring on the first planet row is connected with a second sun gear on the second planet row through a first connecting shaft, a second gear ring on the second planet row is connected with a third planet carrier on the third planet row, the third planet carrier on the third planet row is connected with a fourth sun gear on the fourth planet row through a second connecting shaft, an output component is connected on the fourth planet carrier on the fourth planet row, and the first planet carrier on the first planet row, the second planet carrier on the second planet row, the third gear ring on the third planet row and the fourth gear ring on the fourth planet row are all connected on a same rotating speed connecting body, the same-rotation-speed connecting body is provided with a one-way stopper, a first sun gear on the first planet row is connected with a first driving piece through a first input shaft, and a third sun gear on the third planet row penetrates through the second sun gear, the first connecting shaft, the first sun gear, the first input shaft and the first driving piece through a second input shaft and is connected with the second driving piece.
As a further description of the present invention, the second sun gear, the first connecting shaft, the first sun gear, the first input shaft, and the first driving member are all through hollow structures.
As a further explanation of the present invention, the one-way stopper serves to limit the rotational directions of the first carrier, the second carrier, the third ring gear, and the fourth ring gear.
The double-drive four-planet-row stepless speed change mechanism provided by the utility model has the advantages of high transmission efficiency, large output torque, no power interruption, simple and reliable structure, low manufacturing cost, easiness in maintenance, simplicity and convenience in speed regulation and the like. In addition, the connecting ends of the input end and the output end of the dual-drive four-planet-row stepless speed change mechanism are respectively arranged at the two ends of the dual-drive four-planet-row stepless speed change mechanism, so that the condition that the input end and the output end can be mutually influenced when in operation is avoided, and the integral failure rate is further reduced.
Drawings
FIG. 1 is a schematic diagram of a dual-drive four-planetary-row continuously variable transmission mechanism according to an embodiment of the present invention;
FIG. 2 is a tachometric vector diagram for a first, second, third, and fourth planetary gear set in accordance with an embodiment of the present invention;
FIG. 3 is a speed vector diagram for combining a first planetary row, a second planetary row, a third planetary row and a fourth planetary row according to an embodiment of the present invention;
FIG. 4 shows the rotational speed N of the first driving member according to an embodiment of the present invention1And the rotational speed N of the second drive member2When the ratio of (A) to (B) is less than P, a rotating speed vector diagram;
FIG. 5 shows the rotational speed N of the first driving member according to an embodiment of the present invention1And the rotational speed N of the second drive member2When the ratio of (A) is greater than P, the rotating speed vector diagram is obtained;
FIG. 6 shows the rotational speed N of the first driving member according to an embodiment of the present invention1And the rotational speed N of the second drive member2A rotation speed vector diagram when the ratio of (1) is equal to 1;
FIG. 7 shows the rotational speed N of the first driving member according to an embodiment of the present invention1And the rotational speed N of the second drive member2The ratio of (a) to (b) is less than 1, and the rotation directions are all positive rotation speed vector diagrams;
FIG. 8 shows the rotational speed N of the first driving member according to an embodiment of the present invention1The rotational speed N of the second drive member is adjusted without change2A large-hour rotating speed vector diagram;
FIG. 9 shows the rotational speed N of the second driving member according to an embodiment of the present invention2The rotating speed N of the first driving part is adjusted without changing1A large-hour rotating speed vector diagram;
FIG. 10 shows the rotational speed N of the second drive member when the first drive member fails according to an embodiment of the present invention2A rotating speed vector diagram when the steering direction is the forward direction;
FIG. 11 shows the rotational speed N of the first drive member when the second drive member fails according to an embodiment of the present invention1A rotating speed vector diagram when the steering direction is the forward direction;
FIG. 12 shows the rotational speed N of the first driving member according to an embodiment of the present invention1And the rotational speed N of the second drive member2Is equal to P and the steering is reversed.
Reference numerals:
1-first planet row, 101-first sun gear, 102-first planet carrier, 103-first ring gear, 2-second planet row, 201-second sun gear, 202-second planet carrier, 203-second ring gear, 3-third planet row, 301-third sun gear, 302-third planet carrier, 303-third ring gear, 4-fourth planet row, 401-fourth sun gear, 402-fourth planet carrier, 403-fourth ring gear, 5-first input shaft, 6-second input shaft, 7-first connecting shaft, 8-second connecting shaft, 9-output member, 10-one-way stopper.
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 a dual-drive four-planet-row stepless speed change mechanism is provided to solve the existing problems.
The following describes embodiments of the present invention with reference to the accompanying drawings, and first introduces specific structures of the embodiments of the present invention.
Referring to fig. 1, the dual-drive four-planetary-row continuously variable transmission provided by the embodiment of the present invention includes a first planetary row 1, a second planetary row 2, a third planetary row 3 and a fourth planetary row 4, a first ring gear 103 on the first planetary row 1 is connected to a second sun gear 201 on the second planetary row 2 through a first connecting shaft 7, a second ring gear 203 on the second planetary row 2 is connected to a third carrier 302 on the third planetary row 3, the third carrier 302 on the third planetary row 3 is connected to a fourth sun gear 401 on the fourth planetary row 4 through a second connecting shaft 8, an output member 9 is connected to a fourth carrier 402 on the fourth planetary row 4, the first carrier 102 on the first planetary row 1, the second carrier 202 on the second planetary row 2, the third ring gear 303 on the third planetary row 3 and the fourth ring gear 403 on the fourth planetary row 4 are all connected to a same rotational speed connector, the same-speed connector is provided with a one-way stopper 10, the first sun gear 101 on the first planet row 1 is connected with the first driving member through the first input shaft 5, and the third sun gear 301 on the third planet row 3 passes through the second sun gear 201, the first connecting shaft 7, the first sun gear 101, the first input shaft 5 and the first driving member through the second input shaft 6 and is connected with the second driving member.
Referring to fig. 1, the first planetary row 1 includes a first sun gear 101, a first planet gear, and a first ring gear 103, the second planetary row 2 includes a second sun gear 201, a second planet carrier 202, and a second ring gear 203, the third planetary row 3 includes a third sun gear 301, a third planet carrier 302, and a third ring gear 303, and the fourth planetary row 4 includes a fourth sun gear 401, a fourth planet carrier 402, and a fourth ring gear 403. In practical application, the second sun gear 201, the first connecting shaft 7, the first ring gear 103, the first sun gear 101, the first input shaft 5 and the first driving member are all designed to be hollow through. The one-way stopper 10 serves to limit the rotational directions of the first carrier 102, the second carrier 202, the third ring gear 303, and the fourth ring gear 403.
In the following, we need to describe a speed change method based on a dual-drive four-planetary-row stepless speed change mechanism by combining the specific structure of the embodiment of the present invention.
According to the basic principle of the planetary gear, if the rotating speeds of any two of the three members of the sun gear, the ring gear and the 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.
According to the basic principle of the planetary gear, the rotation speed of any two of the three members of the sun gear, the ring gear and the planet carrier is the same, and the rotation speed of the other member is also the same.
Therefore, the rotational speed of the first driving member is the same as the rotational speed of the first sun gear 101, and is set to N1(ii) a The rotational speed of the second driver is the same as the rotational speed of the third sun gear 301, and is set to N2(ii) a The rotation speeds of the first carrier 102, the second carrier 202, the third ring gear 303, and the fourth ring gear 403 are the same, and are set to N3(ii) a The first ring gear 103 and the second sun gear 201 have the same rotational speed, and are set to N4(ii) a The rotation speeds of the second ring gear 203, the third carrier 302, and the fourth sun gear 401 are the same, and are set to N5(ii) a The fourth carrier 402 and the output member 9 have the same rotational speed, and are set to N6。
A rotation speed vector diagram of the first planetary row 1, the second planetary row 2, the third planetary row 3 and the fourth planetary row 4 is obtained according to a rotation speed vector calculation method of the planetary gear, as shown in fig. 2. The length of the line segment in fig. 2 represents the magnitude of the rotation speed, the arrow direction represents the rotation speed direction, and the arrow direction is defined as a forward direction turning direction upward and a reverse direction turning direction downward.
The rotating speed vector diagrams of the first planetary row 1, the second planetary row 2, the third planetary row 3 and the fourth planetary row 4 are combined to obtain a rotating speed vector diagram as shown in fig. 3.
See FIG. 3, when N is1、N2、N3、N4、N5And N6When any two values are determined, the other four values can be calculated through the proportional relation of line segments in the vector diagram. I.e. the rotational speed N of the first drive member1Determining the rotational speed N of the second drive element2Determining the rotational speed N of the output member 96And is also uniquely determined. Controlling the speed N of the first drive member by regulation1And the rotational speed N of the second drive member2The rotational speed N of the output member 9 can be realized6Continuously stepless variation of (a).
Next, the speed change principle of the dual-drive four-planetary-row continuously variable transmission mechanism according to the embodiment of the utility model will be described with reference to specific operating conditions.
1. Starting condition
Referring to fig. 3, when starting, the first driving piece and the second driving piece are started to accelerate, and the rotating speed N of the first driving piece is controlled in the aspect of steering1And the rotational speed N of the second drive member2Both in forward direction, controlling the speed of rotation of the first drive member in terms of speed of rotationN1And the rotational speed N of the second drive member2Is equal to P. The rotational speed N of the output member 96Gradually accelerates and turns to the positive direction. Under the working condition, the power of the first driving piece and the power of the second driving piece are coupled together, and the vehicle is decelerated and torque-increased to output, so that the vehicle can accelerate to move forwards.
2. Acceleration and deceleration conditions
Referring to FIG. 4, the speed N of the first drive member is controlled in terms of steering during acceleration and deceleration1And the rotational speed N of the second drive member2Both in forward direction, controlling the speed N of the first drive member in terms of speed1And the rotational speed N of the second drive member2Is less than P. By controlling the speed N of the first drive member1And the rotational speed N of the second drive member2By the magnitude and the speed of increase and decrease, the number of rotations N of the output member 9 can be realized6The steering direction is the forward direction, so that the vehicle can accelerate or decelerate to run forwards.
Alternatively, as shown in FIG. 8, the method of acceleration and deceleration may be adjusted by maintaining the speed N of the first drive member1Without change, by adjusting the speed N of the second drive member2To adjust the rotational speed N of the output member 96The size of (d); as shown in FIG. 9, the rotational speed N of the second driving member may be maintained2Without change, by adjusting the speed N of the first drive member1To adjust the rotational speed N of the output member 96The size of (2). Therefore, the rotating speed N of the output part 9 is realized6In the process of acceleration or deceleration, the first driving part and the second driving part can be different according to respective efficient working areas, and the control system controls the acceleration, deceleration and rotation speed maintenance of the first driving part and the second driving part according to the current working condition. Therefore, the first driving part and the second driving part can work in respective high-efficiency working areas for a long time, and the energy-saving effect is achieved.
3. Maximum vehicle speed condition
Referring to fig. 6, the rotational speed N of the first driver is controlled1And the rotational speed N of the second drive member2Is equal in magnitude, is in the forward direction, and reaches the maximum rotation speed, the rotation speed N of the output member 96And the first driveRotational speed N of a member1And the rotational speed N of the second drive member2And equally, the vehicle may be set to reach the maximum vehicle speed in this state.
Referring to fig. 7, if the vehicle is required to reach a higher vehicle speed in the state where the above-described maximum vehicle speed is reached, the rotational speed N of the first drive member may be reduced1Maintaining the rotation speed of the second driving member at the highest rotation speed to make the rotation speed N of the output member 9 constant6The rise was continued. The maximum speed of the vehicle is determined by the speed N of the output member 96Is determined by the magnitude of (1), the rotational speed N of the output member 96Can be determined by the rotational speed N of the first drive element1And the rotational speed N of the second drive member2To make the setting. Therefore, only the first driving part with lower rotating speed is selected, the very high output rotating speed can be realized, and the power requirement on the driving part is further reduced.
Aiming at the starting working condition and the acceleration and deceleration working condition, a dangerous working condition needs to be considered to avoid.
Example (c): referring to fig. 5, the speed N of the first drive member occurs when the speed control of the first and second drive members is inaccurate or fails1And the rotational speed N of the second drive member2Is greater than P, and the rotating speed N of the first driving member1And the rotational speed N of the second drive member2When the rotation directions of the output member 9 are both positive, the rotation speed N of the output member is made to be6In order to prevent the occurrence of a serious accident in which the vehicle suddenly runs in reverse, which may occur when the vehicle suddenly runs in reverse, by providing the one-way stopper 10 on the same-speed connection body to which the first carrier 102, the second carrier 202, the third ring gear 303 and the fourth ring gear 403 are connected, the rotation speed N of the first carrier 102, the second carrier 202, the third ring gear 303 and the fourth ring gear 403 is limited3The direction of rotation of (1) can only be a forward direction, but cannot be a reverse direction. This ensures the rotational speed N of the output member 96The direction of turning of (1) is always positive. Therefore, when the dangerous condition occurs, the rotational speed N of the first carrier 102, the second carrier 202, the third ring gear 303 and the fourth ring gear 403 is limited due to the one-way stopper 103The direction of rotation of (1) can only be forward direction, but not reverse direction, at this timeThe two driving parts can be mutually dragged, and the rotating speed N of the first driving part1And the rotational speed N of the second drive member2Is always equal to P, the rotational speed N of the first planet carrier 102, the second planet carrier 202, the third ring gear 303 and the fourth ring gear 4033Equal to 0, rotational speed N of the output member 96The steering of (2) can only be in the forward direction, so that the vehicle does not suddenly run in reverse.
4. Working condition of backing car
Referring to fig. 12, when the vehicle is reversed, the first driving member and the second driving member are started to accelerate, and the rotating speed N of the first driving member is controlled in terms of steering1And the rotational speed N of the second drive member2Both in opposite directions, the speed N of the first drive member being controlled in relation to the speed1And the rotational speed N of the second drive member2Is equal to P. The rotational speed N of the output member 96Gradually accelerates and turns to the reverse direction. Under the working condition, the power of the first driving piece and the power of the second driving piece are coupled together, and the vehicle is decelerated and torque-increased to output, so that the vehicle can accelerate and retreat to run.
Except for the normal working condition and the dangerous working condition, some emergency working conditions need to be dealt with, and the embodiment of the utility model takes the emergency working conditions into consideration and solves the problem.
Example (c): referring to FIG. 10, when the first driver fails, the second driver has a speed N2The rotational speed N of the first carrier 102, the second carrier 202, the third ring gear 303, and the fourth ring gear 403 in the forward direction3There is a tendency of reverse rotation in which the one-way stopper 10 restricts reverse rotation thereof so that the rotation speed N of the first carrier 102, the second carrier 202, the third ring gear 303, and the fourth ring gear 403 is made to be the rotation speed N30, rotational speed N of the output member 96The power of the second driving element is output through the third planetary row 3 and the fourth planetary row 4 in a speed reduction and torque increase mode in the forward direction, and the vehicle can continue to accelerate or decelerate to run forwards.
Referring to FIG. 11, when the second driver fails, the first driver has a speed of N1The rotational speed N of the first carrier 102, the second carrier 202, the third ring gear 303, and the fourth ring gear 403 in the forward direction3There is a tendency to reverse, in which the one-way stopper 10 limits the reverse rotation thereof, causing the first carrier to rotate102. Rotational speed N of the second carrier 202, the third ring gear 303, and the fourth ring gear 40330, rotational speed N of the output member 96The power of the first driving element is output through the first planet row 1, the second planet row 2 and the fourth planet row 4 in a speed reduction and torque increase mode in the forward direction, so that the vehicle can continue to accelerate or decelerate and run forwards.
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.
The dual-drive four-planet-row stepless speed change mechanism provided by the embodiment of the utility model has the following advantages:
1. the dual-drive four-planet-row stepless speed change mechanism provided by the embodiment of the utility model has no power interruption in the speed regulation process, runs quietly and stably, has better car using experience when a user uses a car, can greatly meet the customer demand in sense, and lays a good foundation for popularization and use of the product.
2. The dual-drive four-planet-row stepless speed change mechanism can realize that the output end has large torque from low speed to high speed, the vehicle has the capability of quickly accelerating to start when driving by outputting the large torque, the large torque can climb a larger slope when the vehicle climbs, and the large torque can also meet the vehicle using requirements of more people, so that the audience area of the product is larger.
3. The dual-drive four-planet-row stepless speed change mechanism can realize stepless continuous change of output rotating speed, the driving piece at the input end can work in a high-efficiency interval for a long time, the working efficiency is improved, the effect of saving more energy can be achieved in the aspect of energy use, and more contribution can be made in the aspect of energy saving.
4. The dual-drive four-planet-row stepless speed change mechanism 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 power of the first driving part and the power of the second driving part are coupled together to drive the vehicle to run, when one driving part fails, the other driving part can still continue to drive the vehicle to run, so that when a vehicle owner uses the vehicle, even if one driving part fails, the vehicle owner can drive the vehicle by the other driving part and drive the vehicle to a maintenance place in time, the occurrence of a trailer calling event is avoided, and the vehicle using experience of the vehicle owner is better taken care of.
6. Compared with the traditional driving mode of a single driving part, the product provided by the embodiment of the 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 dual-drive four-planet-row stepless speed change mechanism has high transmission rate, the motor with lower power and lower rotating speed can be selected as the driving 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 dual-drive four-planet-row stepless speed change mechanism adopts four-planet-row transmission, increases the transmission ratio, further increases the torque, can be applied to heavy trucks such as trucks, muck trucks, buses and the like with larger loads, and further widens the application range of the embodiment of the utility model.
9. The connecting ends of the input end and the output end of the dual-drive four-planet-row stepless speed change mechanism are respectively arranged at the two ends of the dual-drive four-planet-row stepless speed change mechanism, so that the condition that the input end and the output end can be mutually influenced during operation is avoided, and the integral failure rate is further reduced.
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 (3)
1. The double-drive four-planet-row continuously variable transmission mechanism is characterized by comprising a first planet row (1), a second planet row (2), a third planet row (3) and a fourth planet row (4), wherein a first gear ring (103) on the first planet row (1) is connected with a second sun gear (201) on the second planet row (2) through a first connecting shaft (7), a second gear ring (203) on the second planet row (2) is connected with a third planet carrier (302) on the third planet row (3), a third planet carrier (302) on the third planet row (3) is connected with a fourth sun gear (401) on the fourth planet row (4) through a second connecting shaft (8), an output component (9) is connected with a fourth planet carrier (402) on the fourth planet row (4), and a first planet carrier (102) on the first planet row (1), Second planet carrier (202) on second planet row (2), third ring gear (303) on third planet row (3) and fourth ring gear (403) on fourth planet row (4) all connect on the connector with the rotational speed, be provided with one-way stopper (10) on the connector with the rotational speed, first sun gear (101) on first planet row (1) are connected with first driving piece through first input shaft (5), third sun gear (301) on third planet row (3) pass through second input shaft (6) second sun gear (201), first connecting shaft (7) first sun gear (101) first input shaft (5) and first driving piece are connected with the second driving piece.
2. The dual-drive four-planet-row continuously variable transmission mechanism according to claim 1, wherein the second sun gear (201), the first connecting shaft (7), the first sun gear (101), the first input shaft (5) and the first driving member are all of a through hollow structure.
3. The dual drive four planetary row continuously variable transmission according to claim 2, wherein the one-way stopper (10) is configured to limit the rotational directions of the first carrier (102), the second carrier (202), the third ring gear (303), and the fourth ring gear (403).
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| CN202122300104.2U CN215763092U (en) | 2021-09-23 | 2021-09-23 | Dual-drive four-planet-row stepless speed change mechanism |
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