CN215567701U - Three-planetary-row stepless speed change mechanism with classified input - Google Patents
Three-planetary-row stepless speed change mechanism with classified input Download PDFInfo
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- CN215567701U CN215567701U CN202122046848.6U CN202122046848U CN215567701U CN 215567701 U CN215567701 U CN 215567701U CN 202122046848 U CN202122046848 U CN 202122046848U CN 215567701 U CN215567701 U CN 215567701U
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Abstract
The utility model discloses a three-planetary-row stepless speed change mechanism with classified input, which belongs to the technical field of stepless speed change devices and 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 and the transmission gear B are meshed through external teeth, a first gear ring on the first planetary row is connected with a second planetary frame on the second planetary row, a second planetary frame on the second planetary row is connected with a third sun gear on the third planetary row through a connecting shaft, and a first planetary frame 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. The transmission stage is arranged between the first input shaft and the transmission shaft of the three-planetary-row stepless speed change mechanism with the step input function, 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 power selection range of the first driving piece is widened.
Description
Technical Field
The utility model relates to the technical field of continuously variable transmissions, in particular to a three-planetary-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 three-planetary-row stepless speed change mechanism with graded input.
The technical scheme of the utility model is that the stepless speed change mechanism of the three planetary rows with classified input 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, the first sun gear on the first planet row is connected with a transmission gear B through a transmission shaft, a second input shaft connected with a second sun gear on the second planet row penetrates through the first sun gear, the transmission shaft and the transmission gear B to be connected with a second driving piece, and a transmission gear A on the transmission stage is connected with a first driving piece through a first 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 driver.
The stepless speed change mechanism for the three planetary rows with the graded input, provided by the utility model, has the advantages of high transmission efficiency, large output torque, no power interruption, simple and reliable structure, low manufacturing cost, easiness in maintenance, simplicity and convenience in speed regulation and the like. In addition, the connecting ends of the first driving piece and the second driving piece are arranged on the same side of the stepless speed change mechanism, and the connecting end of the output part is arranged on the other side of the stepless speed change mechanism, so that the input position and the output position can be better separated, the probability that the input end and the output part interfere with each other is reduced, the utilization rate of space can be greatly improved through the design, and the whole power equipment is more reasonable in arrangement and space occupancy rate.
Drawings
FIG. 1 is a schematic diagram of a stepped input three planetary row continuously variable transmission mechanism provided by an embodiment of the present invention;
FIG. 2 is a speed vector diagram for a first planetary gear set in accordance with an embodiment of the present invention;
FIG. 3 is a speed vector diagram for a second planetary row as provided by an embodiment of the present invention;
FIG. 4 is a 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 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 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 invention2The steering of (1) is a rotating speed vector diagram when the steering is positive;
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 invention1Is a rotation speed vector diagram 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 has the existing problems of complex structure, high manufacturing cost, difficult maintenance and the like, so a three-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, a three-planetary-row continuously variable transmission mechanism with stepped input 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, the third planet carrier 302 on the third planet row 3 is connected with an output member 9, the first sun gear 101 on the first planet row 1 is connected with a transmission gear B402 through a transmission shaft 10, the second input shaft 7 connected with the second sun gear 201 on the second planet row 2 passes through the first sun gear 101, the transmission shaft 10 and the transmission gear B402 to be connected with a second driving member, and the transmission gear a401 on the transmission stage 4 is connected with the first driving member through a first input shaft 6.
Referring to fig. 1, the first sun gear 101 is engaged with a first planetary gear on its outer teeth, the first planetary gear is mounted on the first carrier 102, and the first planetary gear is engaged with the inner ring teeth of the first ring gear 103; the outer teeth of the second sun gear 201 are engaged with second planet gears which are mounted on the second planet carrier 202, and the second planet gears are engaged with the inner teeth of the second ring gear 203; and the outer teeth of the third sun gear 301 are engaged with third planet gears, the third planet gears are arranged on the third planet carrier 302, and the third planet gears are engaged with the inner ring teeth of the third gear ring 303.
Referring to fig. 1, the one-way stopper 5 is used to limit the rotation direction of the first carrier 102, the second ring gear 203 and the third ring gear 303, and the one-way stopper 5 makes the rotation direction of the first carrier 102, the second ring gear 203 and the third ring gear 303 coincide with the steering of the second driver only.
In the following, we need to describe a gear shifting method of a three-planetary-row continuously variable transmission mechanism based on stepped input in combination 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 second driving member is the same as the rotational speed of the second sun gear 201, and is set to N2(ii) a The rotation speed of the first driving member is set to N1Xi, the rotational speed of the first sun gear 101 is N1(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). Therefore, FIG. 5 can be obtained by combining FIG. 2, FIG. 3 and FIG. 4, let L2＝L4+L5。
See FIG. 5, N2Is the rotational speed of the second sun gear 201, i.e., the rotational speed of the second driving member; n is a radical of1Is the rotational speed of the first sun gear 101; 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 ofOne numerical value is determined, and the other three numerical 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 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 rotational speed N of the output member 9 can be realized5Continuously stepless variation of (a).
The gear shifting principle of the three-planetary-row stepless speed change mechanism with stepped input 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, and the second driving member drives the second sun gear 201 at a 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 of rotation N of the first sun gear1The 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 controlled5The steering direction is the forward direction, so that the vehicle can accelerate or decelerate to run forwards.
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 member1X i is constant by adjusting the speed N of the second drive member2To adjust the rotational speed N of the output member 95The size of (d); the rotating speed N of the second driving member can be maintained2Without change, by adjusting the speed N of the first drive member1By the size of xi to regulate the 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 piece and the second driving piece can be different according to respective high-efficiency working areas, and the control system controls the first driving piece according to the current working conditionAcceleration, deceleration and maintenance of rotational speed of the first and second drive members. 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, 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. 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 rotation direction of the first sun gear 201 is positive, and when the vehicle runs in a starting stage or a middle and low speed stage, if the rotation speed control of the first driving piece and the second driving piece is inaccurate or fails, the rotation 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 suddenly runs 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 the first sun gear 201 can only be forward direction, but not reverse direction, at the moment, the two driving pieces can be dragged mutually, and the rotating speed N of the second sun gear 2012And 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, rotational speed N of the output member 95The steering of (2) can only be in the forward direction, so that the reverse driving cannot happen 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 being only in the reverse directionAnd cannot be in the 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 fails, the rotation speed of the second driving member is N2The rotation speed N of the first carrier 102, the second ring gear 203, and the third ring gear 303 in the forward direction4There is a tendency of reverse rotation, in which the one-way stopper 5 limits reverse rotation thereof, and the rotational speed N of the first carrier 102, the second ring gear 203, and the third ring gear 303 is made to be equal to or lower than the rotational speed N40, the rotational speed N of the output member 95The power of the second driving piece is output through the second planet row 2 and the third planet row 3 in a speed reduction and torque increase way with the transmission ratio of [ (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 driving member fails, the first driving member drives the first sun gear at a rotation speed N1The direction of rotation is reversed, the rotational 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 limits the reverse rotation to the rotation speed N of the first carrier 102, the second ring gear 203 and the third ring gear 30340, the rotational speed N of the output member 95The power of the first driving piece is output through the transmission stage, the first planetary row 1 and the third planetary row 3 in a speed reduction and torque increase mode in a forward direction, and the transmission ratio is i x [ 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-planet-row stepless speed change mechanism with the hierarchical input function provided by the embodiment of the utility model has the following advantages:
1. the three-star-row stepless speed change mechanism with the hierarchical input function provided by the embodiment of the utility model has no power interruption in the speed regulation process, runs quietly and stably, has better car using experience when a user uses a car, can greatly meet the customer demand in sense, and lays a good foundation for popularization and use of the product.
2. The three-planetary-row stepless speed change mechanism with the hierarchical input function 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 larger gradient when climbing the slope, and the large torque can also meet the vehicle using requirements of more people, so that the audience area of the product is larger.
3. The three-planetary-row stepless speed change mechanism with the hierarchical input function can realize the stepless continuous change of the 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 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 three-planetary-row stepless speed change mechanism with the classified input function has high transmission rate, the motor with lower power and lower rotating speed can be selected as the driving piece under the same working condition, and compared with a high-power battery, the low-power battery can better prevent the battery from overheating, and the use safety of the battery is indirectly improved through the embodiment of the utility model.
8. The three-planetary-row stepless speed change mechanism with the classified input function in the embodiment of the utility model adopts three-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. The three-planet-row stepless speed change mechanism with the hierarchical input function of the embodiment of the utility model has the advantages that the first driving piece and the second driving piece are arranged on the same side of the stepless speed change mechanism, the output part 9 is arranged on the other side of the stepless speed change mechanism, so that the input position and the output position can be better separated, the probability that the input end and the output part 9 interfere with each other is reduced, the utilization rate of space can be greatly improved by the design, and the whole power equipment is more reasonable in arrangement and space occupancy rate.
10. The step-input three-planetary-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 first input shaft 6 and the transmission shaft 10, and the transmission stage 4 achieves the purpose of changing the transmission ratio between the first driving piece and the first sun gear 101 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 first 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 three-planetary-row stepless speed change mechanism with classified input is characterized by comprising 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 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 planetary row (1) is connected with a second planetary carrier (202) on the second planetary row (2), the second planetary carrier (202) is connected with a third sun gear (301) on the third planetary row (3) through a connecting shaft (8), a first planetary carrier (102) on the first planetary row (1) is connected with a second gear ring (203) on the second planetary row (2) and a third gear ring (303) on the third planetary row (3), one-way stoppers (5) are arranged on connecting bodies of the first planet carrier (102), the second gear ring (203) and the third gear ring (303), a third planet carrier (302) on the third planet row (3) is connected with an output component (9), a first sun gear (101) on the first planet row (1) is connected with a transmission gear B (402) through a transmission shaft (10), a second input shaft (7) connected with a second sun gear (201) on the second planet row (2) penetrates through the first sun gear (101), the transmission shaft (10) and the transmission gear B (402) to be connected with a second driving piece, and a transmission gear A (401) on the transmission stage (4) is connected with a first driving piece through a first input shaft (6).
2. A stepped input three planetary gear set continuously variable transmission according to claim 1, wherein the first sun gear (101) is externally toothed to engage a first planet gear, which is mounted on the first carrier (102) and which is engaged on the inner ring gear 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. A stepped input three planetary gear set continuously variable transmission mechanism according to claim 1, wherein said one-way stopper (5) is for limiting a rotational direction of said first carrier (102), said second ring gear (203) and said third ring gear (303), said one-way stopper (5) making the rotational direction of said first carrier (102), said second ring gear (203) and said third ring gear (303) coincide with only a steering of said second driver.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202122046848.6U CN215567701U (en) | 2021-08-27 | 2021-08-27 | Three-planetary-row stepless speed change mechanism with classified input |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202122046848.6U CN215567701U (en) | 2021-08-27 | 2021-08-27 | Three-planetary-row stepless speed change mechanism with classified input |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN215567701U true CN215567701U (en) | 2022-01-18 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202122046848.6U Active CN215567701U (en) | 2021-08-27 | 2021-08-27 | Three-planetary-row stepless speed change mechanism with classified input |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN215567701U (en) |
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2021
- 2021-08-27 CN CN202122046848.6U patent/CN215567701U/en active Active
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