CN215763091U - Mixed-action three-planet-row stepless speed change mechanism - Google Patents
Mixed-action three-planet-row stepless speed change mechanism Download PDFInfo
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- CN215763091U CN215763091U CN202122046841.4U CN202122046841U CN215763091U CN 215763091 U CN215763091 U CN 215763091U CN 202122046841 U CN202122046841 U CN 202122046841U CN 215763091 U CN215763091 U CN 215763091U
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Abstract
The utility model discloses a hybrid three-planet-row stepless speed change mechanism, which belongs to the technical field of stepless speed change devices and comprises a first planet row, a second planet row and a third planet row, wherein a first gear ring on the first planet row is connected with a second planet carrier on the second planet row, the second planet carrier 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; a one-way clutch F is arranged between the shell and a connecting body of the first planet carrier, the second gear ring and the third gear ring; a clutch is arranged between the first connecting shaft and the second connecting shaft. The engine and the second motor in the hybrid three-planetary-row stepless speed change mechanism perform power sectional input, so that the power of the engine can be kept in a working efficient area of the engine all the time, the energy consumption and the emission are reduced, the fuel economy is improved, and the endurance mileage is further improved.
Description
Technical Field
The utility model relates to the technical field of continuously variable transmissions, in particular to a hybrid three-planetary-row continuously variable transmission mechanism.
Background
With the popularization of new energy automobiles, China has become the largest new energy automobile market all over the world, and a hybrid electric vehicle is a vehicle type which adopts traditional fuel and is matched with a motor or an engine to improve low-speed power output and fuel consumption.
At present, most of hybrid power automatic speed change systems are driven by matching a single motor with an engine, and have the disadvantages of low comprehensive efficiency, high energy consumption, poor climbing and the like, so that the application and popularization of new energy electric automobiles are restricted. In order to reach the speed of 0-120 km per hour, only a small part of the high-efficiency working area is occupied if the speed of the vehicle is changed by motor speed regulation, and energy consumption is very high when complex road conditions are met. If the motor works with large torque for a long time, the service life of the motor and other aspects are affected. Therefore, it is necessary to design an automatic transmission of a hybrid power system, which makes the vehicle have stronger dynamic property and high-speed cruising ability and makes the dynamic property and the economical efficiency of the whole vehicle more step by step.
SUMMERY OF THE UTILITY MODEL
The utility model aims to solve the problems and designs a hybrid three-planetary-row stepless speed change mechanism.
The technical scheme of the utility model is that the hybrid three-planetary-row stepless speed change mechanism comprises a first planetary row, a second planetary row and a third planetary row, wherein a first gear ring on the first planetary row is connected with a second planetary carrier on the second planetary row, the second planetary carrier is connected with a third sun gear on the third planetary row through a connecting shaft, and a first planetary 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 one-way clutch F is arranged between a connecting body of the first planet carrier, the second gear ring and the third gear ring and the shell; the planetary gear set is characterized in that an output component is connected to a third planet carrier on the third planet row, a first sun gear on the first planet row is connected with a first motor through a first input shaft, a second input shaft connected with a second sun gear on the second planet row penetrates through the first sun gear, the first input shaft and the first motor and is connected with a second motor, the second motor is connected with an engine through a second connecting shaft and a first connecting shaft, and a clutch C is arranged between the first connecting shaft and the second connecting 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;
the outer teeth of the third sun gear are meshed with a third planet gear, the third planet gear is installed on the third planet carrier, and the third planet gear is meshed with the inner ring teeth of the third gear ring;
the first sun gear, the first input shaft and the first motor are all in a penetrating hollow structure.
As a further explanation of the present invention, the one-way clutch F is for restricting the rotational directions of the first carrier, the second ring gear, and the third ring gear, and the one-way clutch F 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 motor or the engine.
According to the hybrid three-planetary-row stepless speed change mechanism provided by the utility model, the transmission ratio between the input end and the output end is changed by adjusting the rotating speeds of the first motor and the second motor, or adjusting the rotating speeds of the first motor and the engine, and matching the first planetary row, the second planetary row, the third planetary row and the one-way clutch, so that stepless speed change of the output end is realized, the engine and the second motor of the mechanism carry out sectional input of power, the power of the engine can be kept in the working efficient area of the engine all the time, the energy consumption and the emission are reduced, the fuel economy is increased, and the endurance mileage is further improved.
Drawings
FIG. 1 is a schematic diagram of a hybrid three-planetary-row continuously variable transmission mechanism provided by an embodiment of the utility model;
FIG. 2 is a speed vector diagram of a first, second, and third planetary gear set provided by an embodiment of the present invention;
FIG. 3 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 the rotation speed vector diagram when P;
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 second 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 invention1A rotation speed vector diagram when the rotation speed vector diagram is 0;
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 same rotating speed vector diagram;
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 gear2When the ratio of (A) is greater than P, the rotating speed vector diagram is obtained;
FIG. 8 is a rotation speed vector diagram at a starting stage in the electric-only mode according to the embodiment of the present invention;
FIG. 9 is a rotation speed vector diagram at a low speed stage in the pure electric mode according to an embodiment of the present invention;
FIG. 10 is a rotation speed vector diagram of a middle/high speed stage in a hybrid mode according to an embodiment of the present invention;
FIG. 11 is a rotation speed vector diagram of the highest vehicle speed stage in the hybrid mode according to an embodiment of the present invention;
FIG. 12 is a rotation speed vector diagram under the safety protection condition provided by the embodiment of the utility model;
FIG. 13 is a rotation speed vector diagram under a reverse operating condition provided by the embodiment of the utility model;
FIG. 14 is a rotation speed vector diagram under the condition of single-motor driving of the first motor according to the embodiment of the present invention;
FIG. 15 is a rotation speed vector diagram under the condition of single driving of the second motor according to the embodiment of the present invention;
FIG. 16 is a speed vector diagram for engine-only driving in accordance with an embodiment of the present invention.
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-one-way clutch F, 5-first connecting shaft, 6-clutch C, 7-second connecting shaft, 8-first input shaft, 9-second input shaft, 10-third connecting shaft, 11-output member.
Detailed Description
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 hybrid three-planetary-row continuously variable transmission mechanism comprises a first planetary row 1, a second planetary row 2 and a third planetary row 3, wherein a first gear ring 103 on the first planetary row 1 is connected with a second gear carrier 202 on the second planetary row 2, the second gear carrier 202 is connected with a third sun gear 301 on the third planetary row 3 through a connecting shaft, and a first gear 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; a one-way clutch F4 is provided between the housing and the connecting body of the first carrier 102, the second ring gear 203, and the third ring gear 303; the third carrier 302 of the third planetary row 3 is connected with an output component 11, the first sun gear 101 of the first planetary row 1 is connected with a first motor through a first input shaft 8, the second input shaft 9 connected with the second sun gear 201 of the second planetary row 2 passes through the first sun gear 101, the first input shaft 8 and the first motor to be connected with a second motor, the second motor is connected with an engine through a second connecting shaft 7 and the first connecting shaft 5, and a clutch C6 is arranged between the first connecting shaft 5 and the second connecting 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 outer teeth of the third sun gear 301 are engaged with third planet gears, the third planet gears are arranged on a third planet carrier 302, and the third planet gears are engaged with the inner ring teeth of a third gear ring 303;
the first sun gear 101, the first input shaft 8 and the first motor are all in a through hollow structure.
Referring to fig. 1, the one-way clutch F4 is used to restrict the rotational direction of the first carrier 102, the second ring gear 203, and the third ring gear 303, and the one-way clutch F4 makes the rotational direction of the first carrier 102, the second ring gear 203, and the third ring gear 303 coincide with the steering of only the second motor or the engine.
In the following, a speed change method based on a hybrid three-planetary-row continuously variable transmission mechanism will be described with reference to specific structures of embodiments 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. Setting: the first sun gear 101 has a rotational speed N1The rotation speed of the second sun gear 201 is N2The rotation speed of the first ring gear 103, the second carrier 202, and the third sun gear 301 is N3The rotation speed of the first carrier 102, the second ring gear 203 and the third ring gear 303 is N4The third planet carrier 302 and the output member 11 rotate at a speed N5。
In the electric-only mode, the clutch C6 is disengaged, and the first motor drives the first sun gear 101 at a speed N1(ii) a The second motor drives the second sun gear 201 at a speed of N2; by controlling the speed of rotation N of the first sun gear 1011And the rotational speed of the second sun gear 201N2The size and direction and the speed increasing and decreasing degree of the output part 11 to realize the rotating speed N of the output part 115Is continuously varied.
In the hybrid mode, the clutch C6 is engaged, the engine is engaged, the second electric machine is not engaged, and the first electric machine drives the first sun gear 101 at a speed N1The engine drives the second sun gear 201 at a speed N2The rotor of the second motor is driven by the engine to idle; maintaining the rotational speed N of the engine2In the most efficient rotation speed interval, the rotation speed N of the first motor driving the first sun gear 101 is controlled1The size and direction and the speed increasing and decreasing degree of the output part 11 to realize the rotating speed N of the output part 115Is continuously varied.
Referring to fig. 2, a rotation speed vector diagram of the first planetary row 1, the second planetary row 2 and the third planetary row 3 is obtained according to a rotation speed vector calculation method of the planetary gear, as shown in fig. 2, the first ring gear 103, the second planet carrier 202 and the third sun gear 301 are connected together with the same rotation speed N3(ii) a The first planet carrier 102, the second ring gear 203 and the third ring gear 303 are connected together with the same rotational speed N4. The length of the line segment in the figure represents the rotating speed, the arrow direction represents the rotating speed direction, and the arrow direction is defined as the forward direction upwards and the arrow direction downwards is defined as the reverse direction.
The speed vector diagrams of the first planetary row 1, the second planetary row 2 and the third planetary row 3 are combined together to obtain a diagram 3, and when N is shown in the diagram 3, the speed vector diagram is combined1、N2、N3、N4And N5When any two numerical values in the vector diagram are determined, the other three numerical values can be obtained through proportional relation calculation of line segments in the vector diagram; wherein the rotational speed N when the first planet carrier 102, the second ring gear 203 and the third ring gear 303 rotate4When 0, the rotational speed N of the first sun gear 101 is set1And the rotational speed N of the second sun gear 2012The ratio of (A) to (B) is P. The output states of the output member 11 include a state a, a state B, a state C, a state D, and a state E by adjusting and controlling the rotation speeds of the first motor, the second motor, and the engine.
Referring to fig. 3, in state a, the rotational speeds of the first carrier 102, the second ring gear 203, and the third ring gear 303N4Is 0, the first motor drives the first sun gear 101 at a rotation speed N1The reverse direction is the reverse direction, the clutch C6 is controlled to be disengaged or engaged, and the second motor or engine drives the second sun gear 201 at the speed N2The direction of rotation is forward, and the rotational speed N of the first sun gear 101 is1And the rotational speed N of the second sun gear 2012Is P, such that the rotational speed N of the output member 115The steering is positive, the vehicle accelerates and runs forwards, and the transmission ratio in the state is maximum.
Referring to fig. 4, in state B, the rotational speed N of the first carrier 102, the second ring gear 203 and the third ring gear 3034The rotation direction is not 0, the rotation direction is positive, and the rotation speed of the first motor driving the first sun gear 101 is N1The reverse direction is the reverse direction, the clutch C6 is controlled to be disengaged or engaged, and the second motor or engine drives the second sun gear 201 at the speed N2The direction of rotation is forward, and the rotational speed N of the first sun gear 101 is1And the rotational speed N of the second sun gear 2012Is less than P, so that the rotational speed N of the output member 115The steering direction of (1) is the forward direction, and the vehicle accelerates to run forwards.
Referring to fig. 5, in state C, the first motor drives the rotational speed N of the first sun gear 1011Gradually reduced from reverse rotation to 0, the clutch C6 is controlled to be disengaged or engaged, and the second motor or engine drives the second sun gear 201 at the speed N2The rotation direction is positive, and the rotation speed N of the output member 11 is set5And increasing, turning to the forward direction, and accelerating the vehicle to run forwards.
Referring to fig. 6, in state D, the first motor drives the rotational speed N of the first sun gear 1011Gradually increasing from 0, turning to the positive direction, controlling the clutch C6 to be disengaged or engaged, and driving the second sun gear 201 by the second motor or engine at the speed N2The rotation direction is positive, and the rotation speed N of the output member 11 is set5The rotation speed N of the first sun gear 101 is increased, the steering direction is positive, and the vehicle is accelerated and driven forward1And the rotational speed N of the second sun gear 2012The same applies to the gear ratio of 1.
Referring to fig. 7, in state E, the first motor drives the first sun gear 101 at a rotation speed N1The reverse direction is the reverse direction, the clutch C6 is controlled to be disengaged or engaged, and the second motor or engine drives the second sun gear 201 at the speed N2The rotation speed N of the first sun gear 101 is the forward rotation speed1And the rotational speed N of the second sun gear 2012Is greater than P, the rotational speed N of the first planet carrier 102, the second ring gear 203 and the third ring gear 3034Is reversed, the rotational speed N of the output member 11 is set5To prevent the reverse, a one-way clutch F4 is provided on the connecting body of the first carrier 102, the second ring gear 203, and the third ring gear 303 to limit the rotational speed N of the first carrier 102, the second ring gear 203, and the third ring gear 3034Can only be in the forward direction but not in the reverse direction, thus ensuring the rotating speed N of the output part 115The steering of the vehicle is always positive, so that the vehicle always runs forwards.
A preferred power split scheme in which embodiments of the present invention can handle all operating conditions is described next.
1. Starting condition
Referring to fig. 8, the starting stage adopts a pure electric mode, the clutch C6 is controlled to be disengaged, the first motor and the second motor are started to accelerate simultaneously, and the first motor drives the rotating speed N of the first sun gear 1011Is reversed, the second motor drives the rotational speed N of the second sun gear 2012Is in the forward direction, the rotational speed N of the first sun gear 101 is set1And the rotational speed N of the second sun gear 2012Is equal to P, such that the rotational speed N of the output member 115The speed is gradually increased, the steering direction is the forward direction, and the vehicle accelerates and runs forwards. Under the working condition, the power of the first motor and the power of the second motor are coupled together, the speed is reduced, the torque is increased, and the engine does not participate in the work under the working condition.
2. Low speed operating mode
Referring to fig. 9, the low-speed stage adopts a pure electric mode, the clutch C6 is controlled to be separated, the first motor and the second motor work simultaneously, and the first motor worksRotational speed N of the first sun gear 1011Is reversed, the second motor drives the rotational speed N of the second sun gear 2012Is in the forward direction, the rotational speed N of the first sun gear 101 is set1And the rotational speed N of the second sun gear 2012Is equal to or less than P by adjusting the first motor speed N1And a second motor speed N2The magnitude and the acceleration/deceleration degree of (2) to realize the rotation speed N of the output member 115The steering is positive. Under the working condition, the power of the first motor and the power of the second motor are coupled together, the speed is reduced, the torque is increased, and the engine does not participate in the work under the working condition.
3. Medium and high speed working condition
Referring to fig. 10, the medium-high speed stage adopts a hybrid mode, the clutch C6 is controlled to be engaged, the first motor and the engine work, and the engine drives the rotation speed N of the second sun gear 2012The rotation speed N of the first motor driving the first sun gear 101 is the forward direction, the rotation speed of the engine is always maintained near the high-efficiency rotation speed, and the rotation speed N is the forward direction1The rotation direction is decelerated from the reverse direction to 0 and then accelerated from the forward direction to the rotation speed N of the second sun gear 2012The same applies to the rotational speed N of the output member 115Gradually accelerates and turns to the positive direction. In this condition, the rotation speed of the engine is always maintained near the high-efficiency rotation speed, and the rotation speed N of the first sun gear 101 is adjusted by the first motor1The magnitude, direction and acceleration/deceleration degree of the output member 11, the rotation speed N of the output member 11 can be realized5The steering is positive. Under the working condition, the power of the first motor and the power of the engine are coupled together for output, and the engine always works in a high-efficiency area in the acceleration and deceleration process, so that the energy consumption and the emission are reduced, the fuel economy is improved, and the endurance mileage is further improved.
Maximum vehicle speed condition
Referring to FIG. 11, the highest vehicle speed phase is in the hybrid mode with clutch C6 engaged, the first electric machine and the engine operating, and the engine driving the secondRotational speed N of sun gear 2012The rotation speed of the engine is always maintained near the high-efficiency rotation speed, the rotation speed N of the first sun gear 101 is continued to be the positive direction through the first motor1To achieve the rotational speed N of the output member 115To achieve higher vehicle speeds. Under the working condition, because the rotating speed of the engine is always in a high-efficiency area and is accelerated only by the first motor, the energy consumption and the emission are reduced, the fuel economy is improved, and the endurance mileage is further improved.
5. Safety protection operating mode
Referring to fig. 12, the rotation speed N of the first motor-driven first sun gear 1011Is reverse, the rotational speed N of the second sun gear 201 driven by the second electric machine or engine2If the rotational speed N of the first sun gear 101 is positive1And the rotational speed N of the second sun gear 2012Control is inaccurate or control fails, the rotational speed N of the first sun gear 101 may occur1And the rotational speed N of the second sun gear 2012Is greater than P, the rotational speed N of the output member 115In order to prevent the occurrence of a situation that the steering direction is reversed, and the vehicle suddenly runs backwards, a serious accident is very likely to happen, a one-way clutch F4 is arranged on the connecting body of the first planet carrier 102, the second ring gear 203 and the third ring gear 303 to limit the rotating speed N of the first planet carrier 102, the second ring gear 203 and the third ring gear 3034Can only be in the forward direction but not in the reverse direction, thus ensuring the rotating speed N of the output part 115The steering of (2) is always positive, so that the vehicle can only drive forwards.
6. Working condition of backing car
Referring to fig. 13, the reverse operation condition is similar to the starting operation condition stage, the pure electric mode is adopted during the reverse operation, the clutch C6 is controlled to be separated, the first motor and the second motor are started and accelerated simultaneously, and the first motor drives the rotating speed N of the first sun gear 1011Is in the forward direction, the second motor drives the rotational speed N of the second sun gear 2012Is reversed, the rotational speed N of the first sun gear 101 is set1And the rotational speed N of the second sun gear 2012Is equal to P, so that the output is equal toRotational speed N of the output member 115Gradually increasing, turning negative, and accelerating the vehicle backward. If the first motor and the second motor rotate at the speed N of the first sun gear 1011And the rotational speed N of the second sun gear 2012Control is inaccurate or control fails, the rotational speed N of the first sun gear 101 may occur1And the rotational speed N of the second sun gear 2012Is greater than P, the rotational speed N of the output member 115In order to prevent the occurrence of a situation that the vehicle is suddenly driven forward and a serious accident is easily caused, a one-way clutch F4 is provided on a connecting body of the first carrier 102, the second ring gear 203 and the third ring gear 303 to limit the rotating speed N of the first 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 part 115The steering of (2) is always in reverse direction, so that the vehicle can only drive backwards.
7. Emergency operating mode
1) Referring to fig. 14, when the second motor and the engine stop operating, the first motor drives the first sun gear 101 at a rotation speed N1The reverse direction is the reverse direction, and the clutch C6 is disengaged, and the rotational speed N of the first carrier 102, the second ring gear 203, and the third ring gear 303 is equal to or higher than the rotational speed N4The one-way clutch F4 may limit the reverse rotation of the first carrier 102, the second ring gear 203 and the third ring gear 303 to make the rotation 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 115The steering of the first motor is always positive, the vehicle can continuously run forwards, and the power of the first motor is output in a speed reduction and torque increase mode through the first planet row 1 and the third planet row 3;
2) referring to fig. 15, when the first motor and the engine stop operating, the second motor drives the second sun gear 201 at a rotation speed N2The steering is in the forward direction, and the clutch C6 is disengaged, at which time the rotational speed N of the first carrier 102, the second ring gear 203, and the third ring gear 3034The one-way clutch F4 may restrict the first carrier 102, the second ring gear 203, and the third ring gear 303 from rotating in reverse, and may cause the first carrier 102, the second ring gear 203, and the third ring gear 303 to rotate in reverseRotational speed N of third ring gear 30340, rotational speed N of the output member 115The steering of the second motor is always positive, the vehicle can continuously run forwards, and the power of the second motor is output in a speed reduction and torque increase mode through the second planetary row 2 and the third planetary row 3;
3) referring to fig. 16, when the first and second motors stop operating, the engine drives the second sun gear 201 at a rotational speed N2The steering is in the forward direction, and the clutch C6 is engaged, at which time the rotational speed N of the first carrier 102, the second ring gear 203, and the third ring gear 3034The one-way clutch F4 may limit the reverse rotation of the first carrier 102, the second ring gear 203 and the third ring gear 303 to make the rotation 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 115The vehicle can continue to run forwards, and the power of the engine is output in a speed reduction and torque increase mode through the second planetary row 2 and the third planetary row 3.
8. Energy recovery regime
When the vehicle is braked in the running process of the vehicle, the first motor drags to work under the inertia speed of the vehicle, and at the moment, the first motor is used as a generator to convert the recovered energy into electric energy to be stored in the battery.
The hybrid three-planet-row stepless speed change mechanism provided by the embodiment of the utility model has the following advantages:
1. the hybrid three-planetary-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 hybrid three-planet-row stepless speed change mechanism can realize that the output end has large torque from low speed to high speed, and the vehicle has the capability of quickly accelerating starting by outputting the large torque when driving, and the large torque can climb larger gradient when climbing the slope, and the large torque can also meet the requirements of more people for using the vehicle, so that the audience area of the product is larger.
3. The hybrid three-planetary-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. According to the embodiment of the utility model, the power of the first motor and the power of the second motor are coupled together to drive the vehicle to run, or the power of the first motor and the power of the engine are coupled together to drive the vehicle to run, when any one or two of the first motor, the second motor and the engine fails, the other one or two of the first motor, the second motor and the engine can drive the vehicle to run, so that the reliability of the use of the vehicle is greatly increased, and even if one or two driving parts fails when a vehicle owner uses the vehicle, the vehicle owner can drive the vehicle by depending on the remaining one or two driving parts and drive the vehicle to a maintenance place in time, so that the occurrence of a trailer calling event is avoided, and the vehicle using experience of the vehicle owner is better taken care of.
5. The hybrid three-planetary-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.
6. The hybrid three-planetary-row stepless speed change mechanism provided by 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.
7. When the vehicle reaches the working condition of medium and high speed, the hybrid three-planetary-row stepless speed change mechanism provided by the embodiment of the utility model replaces the second motor by the engine to transmit power, so that the power of the engine can be kept in the working efficient area of the engine all the time, the energy consumption and the emission are reduced, the fuel economy is increased, and the endurance mileage is further improved.
8. When the hybrid three-planetary-row stepless speed change mechanism provided by the embodiment of the utility model is used for braking a vehicle, the first motor is dragged to work at the inertia speed of the vehicle, and at the moment, the first motor is used as a generator, so that the recovered energy is converted into electric energy to be stored in a battery, and the utilization rate of the energy is improved.
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 hybrid three-planetary-row continuously variable transmission mechanism is characterized by comprising a first planetary row (1), a second planetary row (2) and a third planetary row (3), wherein a first gear ring (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) is connected with a third sun gear (301) on the third planetary row (3) through a connecting shaft, and a first planet 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); a one-way clutch F (4) is arranged between a connecting body of the first planet carrier (102), the second gear ring (203) and the third gear ring (303) and a shell; be connected with output member (11) on third planet carrier (302) on third planet row (3), first sun gear (101) on first planet row (1) are connected with first motor through first input shaft (8), second input shaft (9) that second sun gear (201) on second planet row (2) are connected pass first sun gear (101), first input shaft (8) and first motor are connected with the second motor, the engine is connected through second connecting axle (7) and first connecting axle (5) to the second motor, be provided with clutch C (6) between first connecting axle (5) and second connecting axle (7).
2. Hybrid three planetary gear set continuously variable transmission according to claim 1, characterized in that the first sun gear (101) is engaged on its external teeth with a first planet wheel, which is mounted on the first planet carrier (102) and is engaged on the internal 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);
the outer teeth of the third sun gear (301) are meshed with a third planet gear, the third planet gear is installed on the third planet carrier (302), and the third planet gear is meshed with the inner ring teeth of the third gear ring (303);
the first sun gear (101), the first input shaft (8) and the first motor are all in a penetrating hollow structure.
3. A hybrid three planetary gear set continuously variable transmission mechanism according to claim 1, wherein the one-way clutch F (4) is used to restrict the rotational directions of the first carrier (102), the second ring gear (203), and the third ring gear (303), and the one-way clutch F (4) causes the rotational directions of the first carrier (102), the second ring gear (203), and the third ring gear (303) to coincide with only the steering of the second motor or the engine.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202122046841.4U CN215763091U (en) | 2021-08-27 | 2021-08-27 | Mixed-action three-planet-row stepless speed change mechanism |
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