CN215806120U - Single-side step-by-step transmission four-planet-row stepless speed change mechanism - Google Patents
Single-side step-by-step transmission four-planet-row stepless speed change mechanism Download PDFInfo
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- CN215806120U CN215806120U CN202122301676.2U CN202122301676U CN215806120U CN 215806120 U CN215806120 U CN 215806120U CN 202122301676 U CN202122301676 U CN 202122301676U CN 215806120 U CN215806120 U CN 215806120U
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Abstract
The utility model discloses a unilateral-stage-transmission 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 third sun gear on the third 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, and an output component is connected onto the fourth planet carrier. A transmission stage is additionally arranged between a first planet row and a first driving piece of the unilateral-stage-transmission four-planet-row stepless speed change mechanism, 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 unilateral graded 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 four-planet-row stepless speed change mechanism with single-side stepped transmission.
The technical scheme of the utility model is that the single-side stepped transmission 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 third sun gear on the third 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 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 fourth sun gear on the fourth 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, the third sun gear passes in proper order through the transmission shaft the third planet carrier the second connecting axle the fourth sun gear the fourth planet carrier with output element with drive gear A connects, drive gear B is connected with the second driving piece through the second input shaft, the first sun gear on the first planet row passes in proper order through first input shaft first connecting shaft the second sun gear the third sun gear the transmission shaft with drive gear A is connected with the first driving piece.
As a further explanation of the present invention, the first connecting shaft, the second sun gear, the third planet carrier, the second connecting shaft, the fourth sun gear, the fourth planet carrier, the output member, 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 unilateral stage transmission four-planet-row stepless speed change mechanism provided by the utility model changes the transmission ratio between the input end and the output end by adjusting the rotating speed of the first driving piece and the second driving piece and matching the first planet row, the second planet row, the third planet row, the fourth planet row and the one-way stopper, thereby realizing the stepless speed change of the output end. In addition, the single-side step-drive four-planet-row stepless speed change mechanism is provided with a 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 third 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.
Drawings
FIG. 1 is a schematic diagram of a single-side stepped drive four-planetary-row continuously variable transmission mechanism provided by an embodiment of the utility model;
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 gear2The ratio of (a) to (b) is equal to 1 and the rotation speed vector diagram is when the rotation directions are all positive;
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 gear2The 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 sun gear according to an embodiment of the present invention1The rotational speed N of the third sun gear is adjusted without change2Vector of rotation in magnitudeA measurement chart;
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 for a forward direction of rotation of the first drive member in the event of a failure of the second drive member in accordance with 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-planet-row stepless speed change mechanism with unilateral graded transmission 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, a single-side stepped transmission four-planetary-row stepless speed change mechanism comprises a first planetary row 1, a second planetary row 2, a third planetary row 3 and a fourth planetary row 4, wherein a third sun gear 301 on the third planetary row 3 is connected with a transmission stage 5, the transmission stage 5 comprises a transmission gear A501 and a transmission gear B502, the transmission gear A501 and the transmission gear B502 are meshed 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, the third planet carrier 302 on the third planetary row 3 is connected with a fourth sun gear 401 on the fourth planetary row 4 through a second connecting shaft 9, the fourth planet carrier 402 on the fourth planetary row 4 is connected with an output component 10, the first planet carrier 102 on the first planetary row 1, the second planet row 2, the third planet carrier 3 and the fourth planet carrier 3 on the fourth planet 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 same-rotation-speed connector, a one-way stopper 11 is arranged on the same-rotation-speed connector, the third sun gear 301 on the third planet row 3 sequentially passes through the third planet carrier 302, the second connecting shaft 9, the fourth sun gear 401, the fourth planet carrier 402 and the output part 10 through the transmission shaft 12 to be connected with the transmission gear a501, the transmission gear B502 is connected with the second driving member through the second input shaft 7, and the first sun gear 101 on the first planet row 1 sequentially passes through the first connecting shaft 8, the second sun gear 201, the third sun gear 301, the transmission shaft 12 and the transmission gear a501 through the first input shaft 6 to be connected with the first 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 first connecting shaft 8, the second sun gear 201, the third sun gear 301, the third planet carrier 302, the second connecting shaft 9, the fourth sun gear 401, the fourth planet carrier 402, the output part 10, the transmission shaft 12 and the transmission gear a501 are all in a through hollow structure. 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 describe the speed change method of the four-planetary-row continuously variable transmission mechanism based on single-side stepped transmission by combining the specific structure of the embodiment of the present invention.
According to the basic principle of the planetary gear, when the rotating speeds of any two members 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 third sun gear 301 is N2The gear ratio of the gear stage 5 is i and the rotational speed of the second drive element is N2Xi; 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 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 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 element2Xi is determined, the rotational speed N of the output member 10 is then6And is also uniquely determined. By adjusting the speed N of the first drive member1And the rotational speed N of the second drive member2X i to control the rotational 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).
The speed change principle of the four-planetary-row stepless speed change mechanism with single-side stepped transmission according to the embodiment of the utility model is described below with reference to specific working 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 member1The rotational speed N of the third sun gear 301 is regulated via the second drive element without change2To 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 part 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 reduced1Rotational 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. Highest vehicleSpeed 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 part1And the rotational speed N of the second drive member2X i is set. Therefore, only the second 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 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 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 four-planet-row stepless speed change mechanism with unilateral grading transmission provided by the embodiment of the utility model has the following advantages:
1. the four-planet-row stepless speed change mechanism with the unilateral hierarchical 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 four-planet-row stepless speed change mechanism with unilateral hierarchical transmission can realize that the output end has large torque from low speed to high speed, the vehicle has the capability of quick acceleration starting when driving by outputting the large torque, the large torque can climb larger gradient when climbing the vehicle, and the large torque can also meet the requirement of more people, so that the vehicle using area of the product is larger.
3. The unilateral-graded-transmission 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 four-planet-row stepless speed change mechanism with unilateral hierarchical 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 the 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 unilateral-stage-transmission four-planet-row stepless speed change mechanism has high transmission rate, a motor with lower power and lower rotating speed can be selected as a 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 four-planetary-row stepless speed change mechanism adopting the unilateral stepped transmission of the embodiment of the utility model adopts four-planetary-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. According to the unilateral-graded-transmission four-planet-row stepless speed change mechanism, the connecting ends of the first driving piece, the second driving piece and the output part are all arranged at one end of the stepless speed change mechanism, so that power is input and output at one end of the stepless speed change mechanism, the first input shaft penetrates through the second input shaft and the second driving piece and is connected with the first driving piece, the design can greatly improve the utilization rate of space, and the whole power equipment is more reasonable in arrangement and space utilization rate.
10. The four-planet-row stepless speed change mechanism with single-side stepped 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 third 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 (3)
1. The single-side stepped transmission four-planet-row stepless speed change 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 third sun gear (301) on the third planet row (3) 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 planet row (1) is connected with a second sun gear (201) on the second planet row (2) through a first connecting shaft (8), 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), and the third planet carrier (302) is connected with a fourth sun gear (401) on the fourth planet row (4) through a second connecting shaft (9) Then, 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 all connected to a connector with the same rotating speed, a one-way stopper (11) is arranged on the connector with the same rotating speed, the third sun gear (301) sequentially passes through the third planet carrier (302), the second connecting shaft (9), the fourth sun gear (401), the fourth planet carrier (402) and the output component (10) through a transmission shaft (12) and is connected with the transmission gear a (501), and the transmission gear B (502) is connected with a second driving component through a second input shaft (7), the first sun gear (101) on the first planet row (1) sequentially penetrates through the first connecting shaft (8), the second sun gear (201), the third sun gear (301), the transmission shaft (12) and the transmission gear A (501) through the first input shaft (6) and is connected with the first driving piece.
2. The single-side stepped transmission four-planetary-row continuously variable transmission mechanism according to claim 1, wherein the first connecting shaft (8), the second sun gear (201), the third sun gear (301), the third planet carrier (302), the second connecting shaft (9), the fourth sun gear (401), the fourth planet carrier (402), the output part (10), the transmission shaft (12) and the transmission gear A (501) are all of a through hollow structure.
3. The single-sided step-geared four-planetary-row continuously variable transmission mechanism according to claim 2, wherein the one-way stopper (11) 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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| Application Number | Priority Date | Filing Date | Title |
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| CN202122301676.2U CN215806120U (en) | 2021-09-23 | 2021-09-23 | Single-side step-by-step transmission four-planet-row stepless speed change mechanism |
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| Application Number | Priority Date | Filing Date | Title |
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| CN202122301676.2U CN215806120U (en) | 2021-09-23 | 2021-09-23 | Single-side step-by-step transmission four-planet-row stepless speed change mechanism |
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| CN215806120U true CN215806120U (en) | 2022-02-11 |
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| CN202122301676.2U Active CN215806120U (en) | 2021-09-23 | 2021-09-23 | Single-side step-by-step transmission four-planet-row stepless speed change mechanism |
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2021
- 2021-09-23 CN CN202122301676.2U patent/CN215806120U/en active Active
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