CN215763131U - Four-star row stepless speed change mechanism with classified input - Google Patents
Four-star row stepless speed change mechanism with classified input Download PDFInfo
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- CN215763131U CN215763131U CN202122301572.1U CN202122301572U CN215763131U CN 215763131 U CN215763131 U CN 215763131U CN 202122301572 U CN202122301572 U CN 202122301572U CN 215763131 U CN215763131 U CN 215763131U
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Abstract
The utility model discloses a step-input four-planet-row stepless speed change mechanism, which belongs to the technical field of stepless speed change devices and comprises a first planet row, a second planet row, a third planet row and a fourth planet row, wherein a first sun gear on the first planet row is connected with a transmission stage, the transmission stage comprises a transmission gear A and a transmission gear B, 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, a fourth planet carrier on the fourth planet row is connected with an output component, and one side of a rotating speed connector is provided with a one-way stopper. The transmission stage is additionally arranged between the first planet row of the four-planet-row stepless speed change mechanism and the first driving piece, and the transmission ratio provided by the transmission stage widens the power selection range of the first driving piece.
Description
Technical Field
The utility model relates to the technical field of continuously variable transmissions, in particular to a four-planet-row continuously variable transmission mechanism with classified input.
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 four-planet-row stepless speed change mechanism with graded input.
The technical scheme of the utility model is that the 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 sun gear on the first planet row is connected with a transmission stage, the transmission stage comprises a transmission gear A and a transmission gear B, the transmission gear A is meshed with the transmission gear B through external teeth, 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, a fourth planet carrier on the fourth planet row is connected with an output component, and the first planet carrier on the first planet row is connected with a first sun gear on the second planet row through a second connecting shaft, The second planet carrier on the second planet row, the third ring gear on the third planet row with the fourth ring gear on the fourth planet row all connects on the connector with the rotational speed, be provided with one-way stopper on the connector with the rotational speed, first sun gear on the first planet row pass through the transmission shaft with drive gear A connects, drive gear B is connected with first driving piece through first input shaft, third sun gear on the third planet row passes in proper order through the second input shaft second sun gear first connecting shaft first sun gear the transmission shaft with drive gear A is connected with the second driving piece.
As a further explanation of the present invention, the second sun gear, the first connecting shaft, the first sun gear, the transmission shaft, and the transmission gear a 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 utility model provides a step-input four-planet-row stepless speed change mechanism, which changes the transmission ratio between an input end and an output end by adjusting the rotating speed of a first driving piece and a second driving piece and matching the first planet row, the second planet row, a third planet row, a fourth planet row and a one-way stopper, thereby realizing the stepless speed change of the output end. In addition, the step-input four-planet-row stepless speed change mechanism is provided with a transmission stage between the first input shaft and the transmission shaft, and the transmission stage achieves the purpose of changing the transmission ratio between the first driving piece and the first sun gear by changing the gear ratio of the transmission gear A and the transmission gear B, so that the transmission ratio provided by the transmission stage widens the power selection range of the first driving piece on the premise of achieving the same use effect.
Drawings
FIG. 1 is a schematic diagram of a stepped input four-planetary-row continuously variable transmission provided by 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 sun gear according to the embodiment of the present invention1And the rotational speed N of the third sun gear2When 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 sun gear according to an embodiment of the present invention1And the rotational speed N of the third sun gear2When the ratio of the rotation speed to the rotation speed is larger than P, the rotation speed vector diagram is obtained;
FIG. 6 shows the rotational speed N of the first sun gear according to an embodiment of the present invention1And the rotational speed N of the second sun gear2A rotation speed vector diagram when the ratio of (1) is equal to 1;
FIG. 7 shows the rotational speed N of the first sun gear according to an embodiment of the present invention1And the rotational speed N of the second sun gear2A rotation speed vector diagram with the ratio of (1) to (2);
FIG. 8 shows the rotational speed N of the first sun gear according to an embodiment of the present invention1The rotational speed N of the third sun gear is adjusted without change2A large-hour rotating speed vector diagram;
FIG. 9 shows the rotational speed N of the third sun gear according to the embodiment of the present invention2The rotating speed N of the first sun gear is adjusted without changing1A large-hour rotating speed vector diagram;
FIG. 10 is a speed vector diagram illustrating the forward direction of rotation of the third sun gear when the first drive member is disabled according to an embodiment of the present invention;
FIG. 11 is a speed vector diagram illustrating the forward direction of rotation of the first sun gear when the second drive member is disabled, according to an embodiment of the present invention;
FIG. 12 shows the rotational speed N of the first sun gear according to an embodiment of the present invention1And the rotational speed N of the third sun gear2Is 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-transmission stage, 501-transmission gear a, 502-transmission gear B, 6-first input shaft, 7-second input shaft, 8-first connection shaft, 9-second connection shaft, 10-output member, 11-one-way stopper, 12-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 a four-planetary-row stepless speed change mechanism with classified input 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 stepped input four planetary row continuously variable transmission mechanism according to 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 sun gear 101 of the first planetary row 1 is connected to a transmission stage 5, the transmission stage 5 includes a transmission gear a501 and a transmission gear B502, the transmission gear a501 and the transmission gear B502 are engaged by external teeth, a first ring gear 103 of the first planetary row 1 is connected to a second sun gear 201 of the second planetary row 2 through a first connection shaft 8, a second ring gear 203 of the second planetary row 2 is connected to a third carrier 302 of the third planetary row 3, a third carrier 302 of the third planetary row 3 is connected to a fourth sun gear 401 of the fourth planetary row 4 through a second connection shaft 9, a fourth carrier 402 of the fourth planetary row 4 is connected to an output member 10, a first carrier 102 of the first planetary row 1, a second carrier 102 of the third planetary row 3, and a fourth carrier 4 of the fourth planetary row 4, The second planet carrier 202 on the second planet row 2, the third gear ring 303 on the third planet row 3 and the fourth gear ring 403 on the fourth planet row 4 are all connected to a connector with the same rotating speed, one side of the connector with the same rotating speed is provided with a one-way stopper 11, the first sun gear 101 on the first planet row 1 is connected with the transmission gear a501 through the transmission shaft 12, the transmission gear B502 is connected with the first driving member through the first input shaft 6, and the third sun gear 301 on the third planet row 3 sequentially passes through the second sun gear 201, the first connecting shaft 8, the first sun gear 101, the transmission shaft 12 and the transmission gear a501 through the second input shaft 7 to be connected with the second driving member.
Referring to fig. 1, the first planetary row 1 includes a first sun gear 101, a first carrier 102, and a first ring gear 103, the second planetary row 2 includes a second sun gear 201, a second carrier 202, and a second ring gear 203, the third planetary row 3 includes a third sun gear 301, a third carrier 302, and a third ring gear 303, and the fourth planetary row 4 includes a fourth sun gear 401, a fourth carrier 402, and a fourth ring gear 403. In practical application, the second sun gear 201, the first connecting shaft 8, the first sun gear 101, the transmission shaft 12 and the transmission gear a501 are all designed to be hollow through. The one-way stopper 11 is used to limit the rotational direction 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 explain the speed change method of the four-planetary-row continuously variable transmission mechanism based on the stepped input in combination with 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.
So the rotation speed of the first sun gear 101 is N1The gear ratio of the gear stage 5 is i and the rotational speed of the first drive element is N1Xi; 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 10 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. Namely the first driveRotational speed N of moving part1X i determination, rotational speed N of the second drive member2Determining the rotational speed N of the output part 106And is also uniquely determined. By adjusting the speed N of the first drive member1Xi and the rotational speed N of the second drive member2To control the rotation speed N of the first sun gear 1011And the rotational speed N of the third sun gear 3012Control of the rotational speed N of the output member 10 can be achieved6Continuously stepless variation of (a).
Next, the speed change principle of the four-planetary-row stepless speed change mechanism input in stages according to the embodiment of the present invention will be described with reference to specific operating conditions.
1. Starting condition
Referring to fig. 3, when starting, the engine is started to accelerate, and the first driving member and the second driving member control the rotation speed N of the first sun gear 101 in terms of rotation direction1And the rotational speed N of the third sun gear 3012Both in the forward direction, and controls the rotational speed N of the first sun gear 101 in terms of rotational speed1And the rotational speed N of the third sun gear 3012Is equal to P. The rotational speed N of the output member 106Gradually 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, during acceleration and deceleration, the first driving member and the second driving member control the first sun gear 101 and the third sun gear 301 to rotate in both forward directions, and control the rotation speed N of the first sun gear 101 in rotation speed1And the rotational speed N of the third sun gear 3012Is less than P. The first driving member and the second driving member control the rotating speed N of the first sun gear 1011And the rotational speed N of the third sun gear 3012By the magnitude of (2) and the speed of increase/decrease, the number of revolutions N of the output member 10 can be realized6The steering direction is the forward direction, so that the vehicle can accelerate or decelerate to run forwards.
In addition, as shown in fig. 8, the speed regulation method for acceleration and deceleration may be to maintain the rotation speed N of the first sun gear 101 through the first driving member1Without change, the third sun is regulated by the second driveRotational speed N of the wheel 3012To adjust the rotational speed N of the output member 106The size of (d); as shown in fig. 9, the rotational speed N of the third sun gear 301 may be maintained by the second driver2The rotational speed N of the first sun gear 101 is regulated via the first drive element without change1To adjust the rotational speed N of the output member 106The size of (2). Therefore, the rotating speed N of the output component 10 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 rotation speed N of the first sun gear 101 is controlled by the first driving member and the second driving member1And the rotational speed N of the third sun gear 3012Is equal in magnitude, is in the forward direction, and reaches the maximum rotation speed, the rotation speed N of the output member 106And the rotational speed N of the first sun gear 1011And the rotational speed N of the third sun gear 3012And 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 reduced1Xi, rotational speed N of the first sun gear 1011And also relatively decreases, the second driving member maintains the rotating speed N of the third sun gear 3012The rotation speed N of the output member 10 is set so that the maximum rotation speed is constant6The rise was continued. The maximum vehicle speed is determined by the rotational speed N of the output member 106Is determined by the magnitude of (1), the rotational speed N of the output member 106Can be controlled by controlling the rotating speed N of the first driving part1Xi and 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, when the control of the rotational speeds of the first and second drivers is inaccurate or fails, the rotational speed N of the first sun gear 101 occurs1And the rotational speed N of the third sun gear 3012Is greater than P, and the first sun gear 101 and the third sun gear 301 are both rotating in the forward direction, resulting in the rotation speed N of the output member 106In order to prevent the occurrence of a serious accident in which the vehicle suddenly runs in reverse, a reverse rotation may occur, in which 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 by providing a one-way stopper 11 on the same-rotational-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 commonly connected3The 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 part 106The direction of turning of (1) is always positive. Therefore, when the dangerous condition occurs, 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 limited due to the one-way stopper 113The rotation direction of the first sun gear 101 can only be a forward direction, but not a reverse direction, at the moment, the first driving piece and the second driving piece can be dragged mutually, and the rotating speed N of the first sun gear 1011And the rotational speed N of the third sun gear 3012Is 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, so that the rotational speed N of the output member 106The 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, the first driving member and the second driving member control the first sun gear 101 and the third sun gear 301 to be in opposite directions in terms of steering, and control the rotating speed N of the first sun gear 101 in terms of rotating speed1And the rotational speed N of the third sun gear 3012Is equal to P. The rotational speed N of the output member 106Gradually accelerates and turns to the reverse direction. Under the working conditionThe power of the first driving piece and the power of the second driving piece are coupled together, and the speed and the torque are reduced and increased to output, so that the vehicle can accelerate and move backwards.
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 driving member fails, the second driving member drives the third sun gear 301 at a rotation 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 11 restricts reverse rotation to rotate the first carrier 102, the second carrier 202, the third ring gear 303, and the fourth ring gear 403 at the rotational speed N30, rotational speed N of the output member 106The 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 driving member fails, the first driving member drives the first sun gear 101 at a rotation speed 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 of reverse rotation in which the one-way stopper 11 restricts the reverse rotation to rotate the rotation speed N of the first carrier 102, the second carrier 202, the third ring gear 303, and the fourth ring gear 40330, rotational speed N of the output member 106The 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 step-input four-planet-row stepless speed change mechanism provided by the embodiment of the utility model has the following advantages:
1. the four-star-row stepless speed change mechanism with classified input 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 four-star-row stepless speed change mechanism with hierarchical input provided by the embodiment of the utility model can realize that the output end has large torque from low speed to high speed, the vehicle has the capability of quickly accelerating starting when driving by outputting the large torque, the large torque can climb a larger slope when climbing, the large torque can also meet the vehicle using requirements of more people, and the audience area of the product is larger.
3. The step-input 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 step-input 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 step-input four-star-row stepless speed change mechanism has high-efficiency transmission rate, and under the same working condition, the motor with lower power and lower rotating speed can be selected as the driving piece, so that 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-input 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 and passenger cars with larger loads, and further widens the application range of the embodiment of the utility model.
9. The connection ends of the input end and the output end of the step-input four-planet-row stepless speed change mechanism are respectively arranged at the two ends of the step-input four-planet-row stepless speed change mechanism, so that the condition that the input end and the output end can be influenced mutually 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 stepless speed change mechanism for the four planetary rows with the classified input is characterized by comprising a first planetary row (1), a second planetary row (2), a third planetary row (3) and a fourth planetary row (4), wherein a first sun gear (101) on the first planetary row (1) is connected with a transmission stage (5), the transmission stage (5) comprises a transmission gear A (501) and a transmission gear B (502), the transmission gear A (501) is meshed with the transmission gear B (502) through external teeth, a first gear ring (103) on the first planetary row (1) is connected with a second sun gear (201) on the second planetary row (2) through a first connecting shaft (8), a second gear ring (203) on the second planetary row (2) is connected with a third planet carrier (302) on the third planetary row (3), and the third planet carrier (302) on the third planetary row (3) is connected with a third planet carrier (302) on the fourth planetary row (4) through a second connecting shaft (9) The four sun gears (401) are connected, an output component (10) is connected to a fourth planet carrier (402) on the fourth planet row (4), a first planet carrier (102) on the first planet row (1), a second planet carrier (202) on the second planet row (2), a third gear ring (303) on the third planet row (3) and a fourth gear ring (403) on the fourth planet row (4) are connected to a connector with the same rotating speed, a one-way stopper (11) is arranged on the connector with the same rotating speed, a first sun gear (101) on the first planet row (1) is connected with a transmission gear A (501) through a transmission shaft (12), a transmission gear B (502) is connected with a first driving piece through a first input shaft (6), and a third sun gear (301) on the third planet row (3) sequentially penetrates through a second sun gear (201) and a second input shaft (7), The first connecting shaft (8), the first sun gear (101), the transmission shaft (12) and the transmission gear A (501) are connected with a second driving piece.
2. The step-input four-planetary-row continuously variable transmission mechanism according to claim 1, wherein the second sun gear (201), the first connecting shaft (8), the first sun gear (101), the transmission shaft (12) and the transmission gear a (501) are all of a through hollow structure.
3. The stepwise input four-planetary-row continuously variable transmission mechanism according to claim 2, wherein the one-way stopper (11) is for limiting a rotational direction of the first carrier (102), the second carrier (202), the third ring gear (303), and the fourth ring gear (403).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202122301572.1U CN215763131U (en) | 2021-09-23 | 2021-09-23 | Four-star row stepless speed change mechanism with classified input |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202122301572.1U CN215763131U (en) | 2021-09-23 | 2021-09-23 | Four-star row stepless speed change mechanism with classified input |
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| CN215763131U true CN215763131U (en) | 2022-02-08 |
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| CN202122301572.1U Active CN215763131U (en) | 2021-09-23 | 2021-09-23 | Four-star row stepless speed change mechanism with classified input |
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2021
- 2021-09-23 CN CN202122301572.1U patent/CN215763131U/en active Active
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