CN215720576U - Single-side step-by-step transmission three-planet-row stepless speed change mechanism - Google Patents
Single-side step-by-step transmission three-planet-row stepless speed change mechanism Download PDFInfo
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- CN215720576U CN215720576U CN202122044800.1U CN202122044800U CN215720576U CN 215720576 U CN215720576 U CN 215720576U CN 202122044800 U CN202122044800 U CN 202122044800U CN 215720576 U CN215720576 U CN 215720576U
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Abstract
The utility model discloses a unilateral stepped transmission three-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 transmission stage, wherein the transmission stage comprises a transmission gear A and a transmission gear B, the transmission gear A and the transmission gear B are meshed through external teeth, a first gear ring on the first planet row is connected with a second planet carrier on the second planet row, a second planet carrier on the second planet row is connected with a third sun gear on the third planet row through a connecting shaft, and a first planet carrier on the first planet row is connected with a second gear ring on the second planet row and a third gear ring on the third planet row. The transmission stage is arranged between the first input shaft and the transmission shaft of the stepless speed change mechanism, and the transmission stage achieves the purpose of changing the transmission ratio between the second driving piece and the second sun gear by changing the gear ratio of the transmission gear A and the transmission gear B, so that the power selection range of the second driving piece is widened.
Description
Technical Field
The utility model relates to the technical field of continuously variable transmissions, in particular to a three-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 three-planet-row stepless speed change mechanism with single-side stepped transmission.
The technical scheme of the utility model is that the unilateral stepped transmission three-planetary-row stepless speed change mechanism comprises a first planetary row, a second planetary row, a third planetary row and a transmission stage, wherein 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 planetary row is connected with a second planet carrier on the second planetary row, the second planet carrier is connected with a third sun gear on the third planetary row through a connecting shaft, a first planet carrier on the first planetary row is connected with a second gear ring on the second planetary row and a third gear ring on the third planetary row, a connecting body of the first planet carrier, the second gear ring and the third gear ring is provided with a one-way stopper, and the third planet carrier on the third planetary row is connected with an output component, and a transmission shaft connected with a second sun gear on the second planet row penetrates through the second planet carrier, the connecting shaft, the third sun gear, the third planet carrier and the output component to be connected with the transmission gear B, a first input shaft connected with a first sun gear on the first planet row penetrates through the second sun gear, the transmission shaft and the transmission gear B to be connected with a first driving piece, and the transmission gear A is connected with a second driving piece through a second input shaft.
As a further explanation of the present invention, the external teeth of the first sun gear engage with a first planet gear, the first planet gear is mounted on the first planet carrier, and the first planet gear engages with the inner ring teeth of the first ring gear;
the outer teeth of the second sun gear are meshed with a second planet gear, the second planet gear is arranged on the second planet carrier, and the second planet gear is meshed with the inner ring teeth of the second gear ring;
and the outer teeth of the third sun gear are engaged with a third planet gear, the third planet gear is arranged on the third planet carrier, and the third planet gear is engaged with the inner ring teeth of the third gear ring.
As a further explanation of the present invention, the one-way stopper serves to limit the rotational directions of the first carrier, the second ring gear, and the third ring gear, and the one-way stopper makes the rotational directions of the first carrier, the second ring gear, and the third ring gear coincide with only the steering of the second sun gear driven by the second driver.
The unilateral stepped transmission three-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 and the one-way retainer, thereby realizing the stepless speed change of the output end. In addition, 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 the input and the output of power are all arranged at one end of the stepless speed change mechanism, the utilization rate of a space can be greatly improved by the design, and the whole power equipment is more reasonable in arrangement and space utilization rate.
Drawings
FIG. 1 is a schematic diagram of a single-side stepped transmission three-planetary-row continuously variable transmission mechanism provided by an embodiment of the utility model;
FIG. 2 is a speed vector diagram for a first planetary gear set in accordance with an embodiment of the present invention;
FIG. 3 is a speed vector diagram for a second planetary row as provided by an embodiment of the present invention;
FIG. 4 is a third planetary row tachometric vector diagram provided in accordance with an embodiment of the present invention;
FIG. 5 is a rotation speed vector diagram provided by the embodiment of the present invention and combining FIG. 2, FIG. 3 and FIG. 4;
FIG. 6 shows the rotational speeds N of the first carrier, the second ring gear and the third ring gear according to the embodiment of the present invention4A rotation speed vector diagram when the rotation speed vector diagram is 0;
FIG. 7 shows the rotational speeds N of the first carrier, the second ring gear and the third ring gear according to the embodiment of the present invention4A rotation speed vector diagram when less than 0;
FIG. 8 shows the first driver speed N according to an embodiment of the present invention1A rotation speed vector diagram when the rotation speed vector diagram is 0;
FIG. 9 is a speed vector diagram illustrating the same speed of the first sun gear and the second sun gear according to an embodiment of the present invention;
FIG. 10 shows the rotational speed N of the first sun gear and the second sun gear according to the embodiment of the present invention1And N2The steering is a rotating speed vector diagram in the positive direction at the same time;
FIG. 11 shows the rotational speeds N of the first carrier, the second ring gear and the third ring gear under the reverse operating condition provided by the embodiment of the utility model4A rotation speed vector diagram when the rotation speed vector diagram is 0;
FIG. 12 shows the rotation of the first carrier, the second ring gear and the third ring gear under the reverse operating condition provided by the embodiment of the utility modelSpeed N4A rotation speed vector diagram when less than 0;
FIG. 13 shows the rotational speed N of the second sun gear driven by the second driving member when the first driving member fails according to an embodiment of the present invention2A rotating speed vector diagram when the steering direction is the forward direction;
FIG. 14 shows the rotational speed N of the first driving member when the second driving member fails according to an embodiment of the present invention1And the rotating speed vector diagram when the steering is in the reverse direction.
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-transmission stage, 401-transmission gear a, 402-transmission gear B, 5-one-way stopper, 6-first input shaft, 7-second input shaft, 8-connecting shaft, 9-output member, 10-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 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 existing problems of complex structure, high manufacturing cost, difficult maintenance and the like, so that a unilateral stepped transmission three-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, a single-side stepped transmission three-planetary-row continuously variable transmission mechanism comprises a first planetary row 1, a second planetary row 2, a third planetary row 3 and a transmission stage 4, wherein the transmission stage 4 comprises a transmission gear a401 and a transmission gear B402, the transmission gear a401 and the transmission gear B402 are meshed through external teeth, a first ring gear 103 on the first planetary row 1 is connected with a second planet carrier 202 on the second planetary row 2, the second planet carrier 202 on the second planetary row 2 is connected with a third sun gear 301 on the third planetary row 3 through a connecting shaft 8, a first planet carrier 102 on the first planetary row 1 is connected with a second ring gear 203 on the second planetary row 2 and a third ring gear 303 on the third planetary row 3, a connecting body of the first planet carrier 102, the second ring gear 203 and the third ring gear 303 is provided with a one-way stopper 5, a third planet carrier 302 on the third planetary row 3 is connected with an output component 9, a transmission shaft 10 connected with a second sun gear 201 on the second planetary row 2 passes through the second planet carrier 202, the connecting shaft 8, the third sun gear 301, the third planet carrier 302 and the output component 9 to be connected with a transmission gear B402, a first input shaft 6 connected with a first sun gear 101 on the first planetary row 1 passes through the second sun gear 201, the transmission shaft 10 and the transmission gear B402 to be connected with a first driving member, and a transmission gear a401 on the transmission stage 4 is connected with a second driving member through a second input shaft 7.
Referring to fig. 1, a first sun gear 101 is engaged with first planet gears on outer teeth, the first planet gears are mounted on a first planet carrier 102, and the first planet gears are engaged with inner ring teeth of a first ring gear 103; a second planet wheel is meshed with the outer teeth of the second sun gear 201, is arranged on a second planet carrier 202, and is meshed with the inner ring teeth of a second ring gear 203; the third sun gear 301 is engaged with third planetary gears on its outer teeth, which are mounted on a third carrier 302, and engaged with inner ring teeth of a third ring gear 303.
Referring to fig. 1, the one-way stopper 5 serves to limit the rotational directions of the first carrier 102, the second ring gear 203, and the third ring gear 303, and the one-way stopper 5 makes the rotational directions of the first carrier 102, the second ring gear 203, and the third ring gear 303 coincide with only the turning direction of the second sun gear.
In the following, we need to describe a speed change method of a three-planetary-row stepless speed change mechanism based on single-side stepped transmission by combining with the specific structure of the embodiment of the present invention.
According to the basic principle of the planetary gear, the rotating speeds of three members, namely a sun gear, a ring gear and a planet carrier, of any two members are determined, the rotating speed of the other member is also determined, and the rotating speed relations of the members are in corresponding proportion according to the number of teeth of the sun gear and the number of teeth of the ring gear.
According to the basic principle of the planetary gear, the rotation speed of any two of the three components, namely the sun gear, the ring gear and the planet carrier, is the same, and the rotation speed of the other component 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 rotation speed of the second driving member is set to N2Xi, the rotational speed of the second sun gear 201 is N2(ii) a The rotation speeds of the first ring gear 103, the second carrier 202, and the third sun gear 301 are the same, and N is set3(ii) a The rotation speeds of the first carrier 102, the second ring gear 203, and the third ring gear 303 are the same, and are set to N4(ii) a The third carrier 302 and the output member 9 have the same rotational speed, and are set to N5(ii) a The number of teeth of the first sun gear 101 is set to Z1The number of teeth of the first ring gear 103 is Z2The number of teeth of the second sun gear 201 is Z3The number of teeth of the second ring gear 203 is Z4The number of teeth of the third sun gear 301 is Z5The number of teeth of the third ring gear 303 is Z6。
A rotation speed vector diagram of the first planetary row 1 is obtained according to a rotation speed vector calculation method of the planetary gear, as shown in fig. 2. N is a radical of1Is the rotational speed of the first sun gear 101, N3Is the rotational speed of the first ring gear 103, N4Is the rotational speed of the first carrier 102. N is a radical of1、N3、N4The length of (d) represents the magnitude of the rotation speed, the arrow direction represents the rotation speed direction, the arrow direction represents the rotation speed as a forward direction, and the arrow direction represents the rotation speed as a reverse direction. Set L2/L3＝Z1/Z2。
A rotation speed vector diagram of the second planetary line 2 is obtained according to a rotation speed vector calculation method of the planetary gears, as shown in fig. 3. N is a radical of2Is the rotational speed, N, of the second sun gear 2014Is the rotational speed, N, of the second ring gear 2033Is the rotational speed of the second carrier 202. N is a radical of2、N3、N4The length of (d) represents the magnitude of the rotation speed, the arrow direction represents the rotation speed direction, the arrow direction represents the rotation speed as a forward direction, and the arrow direction represents the rotation speed as a reverse direction. Set L2/L1＝Z3/Z4。
A rotation speed vector diagram of the third planetary row 3 is obtained according to the rotation speed vector calculation method of the planetary gears, as shown in fig. 4. N is a radical of3Is the rotational speed of the third sun gear 301, N4Is the rotational speed of the third ring gear 303, N5Is the rotational speed of the third carrier 302. N is a radical of3、N4、N5The length of (d) represents the magnitude of the rotation speed, the arrow direction represents the rotation speed direction, the arrow direction represents the rotation speed as a forward direction, and the arrow direction represents the rotation speed as a reverse direction. Set L5/L4＝Z5/Z6。
In FIGS. 2, 3 and 4, L1、L2、L3、L4、L5Only the corresponding proportional relationship needs to be satisfied, L1、L2、L3、L4、L5Does not affect the calculation of N1、N2、N3、N4、N5The size of (2). FIG. 5 can be obtained by combining FIG. 2, FIG. 3 and FIG. 4, let L2＝L4+L5。
See FIG. 5, N1Is the rotational speed of the first sun gear 101, i.e. the rotational speed of the first drive member; n is a radical of2Is the rotational speed of the second sun gear 201; n is a radical of3Is the rotational speed of the first ring gear 103, the second carrier 202, and the third sun gear 301; n is a radical of4Is the rotational speed of the first carrier 102, the second ring gear 203 and the third ring gear 303; n is a radical of5Is the rotational speed of the third planet carrier 302 and the output member 9.
N1、N2、N3、N4And N5Any two values are determined, and the other three values can be calculated through the proportional relation of line segments in the vector diagram. I.e. the rotational speed N of the first sun gear 1011Determining the rotational speed N of the second sun gear 2012Determining the rotational speed N of the output member 95And is also uniquely determined. The first gear is adjusted and controlled by the first driving piece and the second driving pieceRotational speed N of the sun gear 1011And the rotational speed N of the second sun gear 2012The rotational speed N of the output member 9 can be realized5Continuously stepless variation of (a).
The speed change principle of the three-planetary-row stepless speed change mechanism with single-side stepped transmission according to the embodiment of the utility model is described below by combining specific working conditions.
1. Starting condition
Referring to fig. 5 and 6, at the time of starting, the first driving member drives the first sun gear 101 at the rotating speed N1The direction of rotation is reverse; the second driving member drives the second sun gear 201 at a rotating speed N2The direction of rotation is the forward direction. The two driving members are simultaneously started to accelerate, and the rotating speed N of the second sun gear 201 is controlled2And the rotational speed N of the first sun gear 1011Is always greater than (as in FIG. 5) or equal to (as in FIG. 6) [ Z ]1×(Z3+Z4)]/(Z2×Z3) Control of the rotational speed N of the output member 9 is achieved5The acceleration is gradually increased from 0, and the direction is changed to the positive direction. Under the working condition, the transmission ratio is maximum, 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
The acceleration and deceleration may be in accordance with the speed N of the first drive member1The steering is divided into three cases, which specifically comprise:
1) situation one
Referring to fig. 5 and 6, the first driving member drives the first sun gear 101 at a rotation speed N1The direction of rotation is reverse, and the second driving member drives the second sun gear 201 at a speed N2The direction of rotation is the forward direction. By controlling the speed of rotation N of the second sun gear 2012And the rotational speed N of the first sun gear 1011Always greater than or equal to [ Z ]1×(Z3+Z4)]/(Z2×Z3). The rotational speed N of the first sun gear 101 is controlled by the first and second drive elements1And the rotational speed N of the second sun gear 2012By increasing or decreasing the speed, the rotational speed N of the output member 9 can be controlled5Gradually increasing or decreasing, turning to the forward direction, accelerating the vehicleOr to decelerate forward.
2) Situation two
Referring to fig. 8, the first driving member drives the first sun gear 101 at a rotation speed N1The magnitude is gradually reduced to 0, and the rotating speed of the second driving piece driving the second sun wheel 201 is N2The rotation direction is forward direction by controlling the rotation speed N of the first sun gear 1011Is 0 and the rotational speed N of the second sun gear 2012The speed of increase and decrease of the speed can realize the output rotating speed N5The steering direction is the forward direction, so that the vehicle can accelerate or decelerate to run forwards.
3) Situation three
Referring to fig. 10, the first driving member drives the first sun gear 101 at a rotation speed N1The rotation direction is positive, and the second driving member drives the second sun gear 201 at the rotation speed N2The direction of rotation is the forward direction. The rotational speed N of the first sun gear 101 is controlled by the first and second drive elements1And the rotational speed N of the second sun gear 2012The speed of increase and decrease of the speed can realize the output rotating speed N5The steering direction is the forward direction, so that the vehicle can accelerate or decelerate to run forwards.
Alternatively, 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 member2By the size of xi to regulate the speed N of the output member 95The size of (d); the rotating speed N of the second driving member can be maintained2Xi is unchanged by adjusting the rotational speed N of the first drive member1To adjust the rotational speed N of the output member 95The size of (2). When the rotational speed N of the output member 9 is realized5In 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. 9 and 10, firstThe rotating speed of the driving piece driving the first sun gear 101 is N1The rotation direction is positive, and the second driving member drives the second sun gear 201 at the rotation speed N2The direction of rotation is the forward direction. When the rotation speed N of the first sun gear 1011And the rotational speed N of the second sun gear 2012The rotational speed N of the output member 9 when all reach the maximum rotational speed5The maximum speed is also reached, at which time the vehicle speed reaches the maximum vehicle speed. If the rotational speed N of the first sun gear 1011And the rotational speed N of the second sun gear 2012Is the same, the rotational speed N of the output member 95The maximum rotational speed that can be achieved and the maximum rotational speed N of the first sun gear 101 and the second sun gear 2011、N2Also, the gear ratio is 1.
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. 7, the rotation speed N when the first driving member drives the first sun gear 1011Is reversed, the second driving member drives the rotational speed N of the second sun gear 2012The steering of (1) is a forward direction, and the vehicle runs in a starting stage or a medium-low speed stage. If the control of the rotating speeds of the first driving member and the second driving member is inaccurate or fails, the rotating speed N of the second sun gear 201 occurs2And the rotational speed N of the first sun gear 1011Is less than [ Z ]1×(Z3+Z4)]/(Z2×Z3) At this time, as shown in FIG. 7, the rotational speed N of the output member 95The steering of the vehicle can be in a reverse direction, and the vehicle can suddenly run backwards, so that serious accidents are easy to happen. To prevent this from happening, limiting the speed of rotation N of the first planet carrier 102, the second ring gear 203 and the third ring gear 303 is achieved by providing a one-way stop 5 on the connection body of the first planet carrier 102, the second ring gear 203 and the third ring gear 3034The 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 95The 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 ring gear 203 and the third ring gear 303 is limited due to the one-way stopper 54The direction of rotation of (1) can only be forward direction, but not reverse direction, at this timeThe two driving elements drag each other, the rotational speed N2 of the second sun gear 201 and the rotational speed N of the first sun gear 1011Will always be equal to [ Z ]1×(Z3+Z4)]/(Z2×Z3). Rotational speed N of the first carrier 102, the second ring gear 203 and the third ring gear 3034Equal to 0, the rotation speed N5 of the output member 9 can be steered only in the forward direction, so that a reverse driving situation does not occur suddenly.
4. Working condition of backing car
Referring to fig. 11 and 12, when the vehicle is reversed, the first driving member drives the first sun gear 101 at a rotation speed N1The rotation direction is positive, and the second driving member drives the second sun gear 201 at the rotation speed N2The direction of rotation is reversed. The two driving members are simultaneously started to accelerate, and the rotating speed N of the second sun gear 201 is controlled2And the rotational speed N of the first sun gear 1011Is always greater than (as in FIG. 12) or equal to (as in FIG. 11) [ Z ]1×(Z3+Z4)]/(Z2×Z3) Control of the rotational speed N of the output member 9 is achieved5Gradually accelerate from 0 and turn to reverse. If the control of the rotating speeds of the first driving member and the second driving member is inaccurate or fails, the rotating speed N of the second sun gear 201 occurs2And the rotational speed N of the first sun gear 1011Is less than [ Z ]1×(Z3+Z4)]/(Z2×Z3) The rotational speed N of the output member 95The steering may be in a forward direction, and at this time, the vehicle suddenly runs forward, so that a serious accident is easy to happen. To prevent this from happening, limiting the speed of rotation N of the first planet carrier 102, the second ring gear 203 and the third ring gear 303 is achieved by providing a one-way stop 5 on the connection body of the first planet carrier 102, the second ring gear 203 and the third ring gear 3034The direction of rotation of (1) can only be reverse direction, but not forward direction. This ensures the rotational speed N of the output member 95The direction of rotation of (c) is always reversed.
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. 13, when the first driving member is drivenWhen the failure occurs, the rotating speed of the second driving piece is N2Xi, forward direction, speed N of the first carrier 102, the second ring gear 203 and the third ring gear 3034There is a tendency of reverse rotation in which the one-way stopper 5 restricts reverse rotation to rotate the first carrier 102, the second ring gear 203, and the third ring gear 303 at the rotational speed N40, rotational speed N of the output member 95The power of the second driving piece is output through the transmission stage, the second planet row 2 and the third planet row 3 in a speed reduction and torque increase mode in the positive direction, and the transmission ratio is i x [ (Z)3+Z4)×(Z5+Z6)/Z3×Z5]So that the vehicle can continue to accelerate or decelerate forward.
Referring to FIG. 14, when the second driver fails, the first driver has a speed of N1The rotation speed N of the first carrier 102, the second ring gear 203 and the third ring gear 303 is reversed4There is a tendency of reverse rotation, in which the one-way stopper 5 restricts the reverse rotation to rotate the rotational speed N of the first carrier 102, the second ring gear 203 and the third ring gear 30340, rotational speed N of the output member 95The power of the first driving piece is output through the first planet row 1 and the third planet row 3 in a speed reduction and torque increase mode in the positive direction, and the transmission ratio is [ Z ]2×(Z5+Z6)]/(Z1×Z5) So that the vehicle can continue to accelerate or decelerate forward.
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 three-planetary-row stepless speed change mechanism with single-side stepped transmission provided by the embodiment of the utility model has the following advantages:
1. the unilateral-graded-transmission three-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 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 unilateral stepped transmission three-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 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 requirements of more people, and the vehicle using area of the product is larger.
3. The unilateral-graded-transmission three-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 unilateral-graded-transmission three-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 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 stepped transmission three-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 unilateral stepped transmission three-planet-row stepless speed change mechanism adopts three-planet-row transmission, increases the transmission ratio, further increases the torque, can be applied to heavy trucks such as trucks, muck trucks and buses with larger loads, and further widens the application range of the embodiment of the utility model.
9. According to the unilateral-graded-transmission three-planet-row stepless speed change mechanism, the connecting ends of the first driving piece, the second driving piece and the output part 9 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 design can greatly improve the space utilization rate, and the whole power equipment is more reasonable in arrangement and space utilization rate.
10. The single-side stepped transmission three-planet-row stepless speed change mechanism provided by the embodiment of the utility model is characterized in that the transmission stage 4 is arranged between the second input shaft 7 and the transmission shaft 10, and the transmission stage 4 achieves the purpose of changing the transmission ratio between the second driving piece and the second sun gear 201 by changing the gear ratio of the transmission gear A401 and the transmission gear B402, so that the transmission ratio provided by the transmission stage 4 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. A single-side stepped transmission three-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 transmission stage (4), wherein the transmission stage (4) comprises a transmission gear A (401) and a transmission gear B (402), the transmission gear A (401) and the transmission gear B (402) are meshed through external teeth, a first gear ring (103) on the first planet row (1) is connected with a second planet carrier (202) on the second planet row (2), the second planet carrier (202) is connected with a third sun gear (301) on the third planet row (3) through a connecting shaft (8), a first planet carrier (102) on the first planet row (1) is connected with a second gear ring (203) on the second planet row (2) and a third gear ring (303) on the third planet row (3), a one-way stopper (5) is arranged on a connecting body of the first planet carrier (102), the second gear ring (203) and the third gear ring (303), the third planet carrier (302) on the third planet row (3) is connected with an output part (9), a transmission shaft (10) connected with a second sun gear (201) on the second planet row (2) passes through the second planet carrier (202), the connecting shaft (8), the third sun gear (301), the third planet carrier (302) and the output component (9) and is connected with the transmission gear B (402), a first input shaft (6) connected with a first sun gear (101) on the first planet row (1) passes through the second sun gear (201), the transmission shaft (10) and the transmission gear B (402) to be connected with a first driving piece, the transmission gear A (401) is connected with a second driving piece through a second input shaft (7).
2. The single-sided step-drive three-planetary-row continuously variable transmission according to claim 1, wherein the first sun gear (101) is engaged with a first planetary gear on external teeth, the first planetary gear is mounted on the first carrier (102), and the first planetary gear is engaged with inner ring teeth of the first ring gear (103);
the second sun gear (201) is meshed with a second planet gear on external teeth, the second planet gear is arranged on the second planet carrier (202), and the second planet gear is meshed with internal ring teeth of the second ring gear (203);
and a third planet wheel is meshed with the external teeth of the third sun gear (301), is arranged on the third planet carrier (302), and is meshed with the inner ring teeth of the third gear ring (303).
3. The single-sided step-geared three planetary gear set continuously variable transmission according to claim 1, wherein the one-way stopper (5) is configured to limit the rotational directions of the first carrier (102), the second ring gear (203), and the third ring gear (303), and the one-way stopper (5) makes the rotational directions of the first carrier (102), the second ring gear (203), and the third ring gear (303) coincide with the steering of only the second sun gear (201) to which the second drive is connected.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202122044800.1U CN215720576U (en) | 2021-08-27 | 2021-08-27 | Single-side step-by-step transmission three-planet-row stepless speed change mechanism |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202122044800.1U CN215720576U (en) | 2021-08-27 | 2021-08-27 | Single-side step-by-step transmission three-planet-row stepless speed change mechanism |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN215720576U true CN215720576U (en) | 2022-02-01 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202122044800.1U Active CN215720576U (en) | 2021-08-27 | 2021-08-27 | Single-side step-by-step transmission three-planet-row stepless speed change mechanism |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN215720576U (en) |
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2021
- 2021-08-27 CN CN202122044800.1U patent/CN215720576U/en active Active
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