阅读说明：本技术 电动车辆的动力传动系统 (Power transmission system of electric vehicle ) 是由 段诚武 姚健 于 2018-08-31 设计创作，主要内容包括：一种车辆的动力传动系统包括壳体、电动发电机单元、变矩器、第一轴和第二轴、第一齿轮组和第二齿轮组以及扭矩传递机构。电动发电机单元包括输出构件。变矩器包括泵和涡轮。泵与电动发电机单元的输出构件连接以便共同旋转。第一轴由动力传动系统壳体可旋转地支撑,并且与变矩器的涡轮连接以便共同旋转。第二轴由动力传动系统壳体可旋转地支撑,并且平行于第一轴设置。输出齿轮连接到第二轴以便共同旋转。(A powertrain system of a vehicle includes a housing, a motor generator unit, a torque converter, first and second shafts, first and second gear sets, and a torque transmitting mechanism. The motor generator unit includes an output member. The torque converter includes a pump and a turbine. The pump is connected for common rotation with an output member of the motor generator unit. The first shaft is rotatably supported by the driveline housing and is connected for common rotation with a turbine of the torque converter. The second shaft is rotatably supported by the driveline housing and is disposed parallel to the first shaft. The output gear is connected for common rotation to the second shaft.)

1. A vehicle driveline, the driveline comprising:

a drivetrain housing;

a motor generator unit including an output member;

a torque converter including a pump and a turbine, and wherein the pump is connected for common rotation with an output member of the motor generator unit;

a first shaft rotatably supported by the driveline housing, and wherein the first shaft is connected for common rotation with a turbine of the torque converter;

a second shaft rotatably supported by the driveline housing and disposed parallel to the first shaft, and wherein an output gear is connected to the second shaft for common rotation;

a first gear set including a first gear and a second gear, and wherein the first gear is rotatably supported by the first shaft and the second gear is connected for common rotation with the second shaft;

a second gear set including a third gear and a fourth gear, and wherein the third gear is rotatably supported by the first shaft and the fourth gear is connected for common rotation with the second shaft, an

A torque-transmitting mechanism that selectively transmits torque from the first shaft to the second shaft; and is

Wherein the powertrain is selectively actuated to provide one of a first forward drive gear ratio and a reverse drive gear ratio.

2. The drivetrain of claim 1, wherein the torque-transmitting mechanism selectively connects a first gear of the first gear set to the first shaft for common rotation.

3. The drivetrain of claim 1, wherein the torque-transmitting mechanism selectively connects a third gear of the second gear set to the first shaft for common rotation.

4. The drivetrain of claim 2, further comprising a transfer member disposed about the first and second gears of the first gear set to transfer torque from the first gear to the second gear.

5. The drivetrain of claim 4, wherein the conveyance member is one of a chain and a belt.

6. The drivetrain of claim 1, wherein the torque-transmitting mechanism is one of a synchronizer, a dog clutch, and a friction clutch.

7. The drivetrain of claim 1, wherein the first gear set further comprises a planetary gear set including a sun gear, a ring gear, a plurality of planet gears that mesh with the sun gear and the ring gear, respectively, and a planet carrier member that rotatably supports the planet gears, and wherein the sun gear is connected for common rotation with a pump of the torque converter and the planet carrier member is connected for common rotation with the first gear of the first gear set.

8. The drivetrain of claim 7, wherein the torque-transmitting mechanism selectively connects the ring gear of the planetary gear set to the housing.

9. The drivetrain of claim 8, wherein a third gear of the second gear set is coplanar with a fourth gear of the second gear set, and the third gear is connected for common rotation with the first shaft.

10. The drivetrain of claim 9, wherein the torque transmitting mechanism is a dog clutch.

Technical Field

The present disclosure relates generally to a powertrain system of a vehicle, and more particularly to a transmission of a vehicle having a motor generator unit as a primary torque source.

Background

Modern Electric Vehicles (EVs) are becoming increasingly popular due to advances in many vehicle performance attributes. However, a major obstacle to the increasing popularity of EVs includes the distance that an EV can travel after being charged once. While there are many characteristics that help increase the range of an EV, improving certain characteristics may adversely affect the performance of an EV in other areas. Sometimes tradeoffs are made to meet customer expectations. For example, when a driver operates a treadmill with a powerful engine, they understand that the engine may make a loud sound when traveling at the highest speed. Furthermore, if the driver wants to make a quick pass through a turn, they may accept that potholes and bumps in the road may be perceived more than a cruising vehicle that is comfortable to drive.

Therefore, when the mileage of the extended EV is prioritized, other attributes are also affected. For example, sizing a Motor Generator Unit (MGU) may provide an opportunity to travel the same distance using less battery power. However, other attributes, such as drivability, startability, and mobility, may not meet the customer's expectations.

Accordingly, there is a need in the art for an improved EV having superior performance while exceeding current range capacity and increasing affordability by reducing costs.

Disclosure of Invention

The present disclosure includes a vehicle powertrain. The transmission system includes a housing, a motor generator unit, a torque converter, first and second shafts, first and second gear sets, and a torque transmitting mechanism. The motor generator unit includes an output member. The torque converter includes a pump and a turbine. The pump is connected for common rotation with an output member of the motor generator unit. The first shaft is rotatably supported by the driveline housing and is connected for common rotation with a turbine of the torque converter. The second shaft is rotatably supported by the driveline housing and is disposed parallel to the first shaft. The output gear is connected for common rotation to the second shaft.

The first gear set includes a first gear rotatably supported by the first shaft and a second gear connected for common rotation with the second shaft. The second gear set has a third gear rotatably supported by the first shaft and a fourth gear connected for common rotation with the second shaft. The torque-transmitting mechanism selectively transmits torque from the first shaft to the second shaft. The powertrain is selectively actuated to provide one of a first forward drive gear ratio and a reverse drive gear ratio.

In one example of the present disclosure, a torque-transmitting mechanism selectively connects a first gear of a first gear set to a first shaft for common rotation.

In another example of the present disclosure, a torque-transmitting mechanism selectively connects the third gear of the second gear set to the first shaft for common rotation.

In another example of the present disclosure, a transfer member is disposed about the first and second gears of the first gear set for transferring torque from the first gear to the second gear.

In another example of the present disclosure, the conveying member is one of a chain and a belt.

In another example of the present disclosure, the torque transmitting mechanism is one of a synchronizer and a dog clutch.

In another example of the present disclosure, the first gear set further includes a planetary gear set including a sun gear, a ring gear, and a plurality of planet gears meshing with the sun gear and the ring gear, respectively. The planet gear carrier member rotatably supports the planet gears. The sun gear is connected for common rotation with the pump of the torque converter, and the planet carrier member is connected for common rotation with the first gear of the first gear set.

In another example of the present disclosure, a torque-transmitting mechanism selectively connects the ring gear of the planetary gear set to the housing.

In another example of the present disclosure, the third gear of the second gear set is coplanar with the fourth gear of the second gear set, the third gear being connected for common rotation with the first shaft.

In another example of the present disclosure, the torque transmitting mechanism is a dog clutch.

In another example of the present disclosure, the powertrain is selectively actuated to provide an initial forward launch mode, a second forward launch mode, and a reverse launch mode. The initial forward start mode includes engaging the dog clutch when the motor generator unit is operating in a forward rotational direction. The second forward launch mode includes disengaging the dog clutch when the motor generator unit is operating in the forward rotational direction. The reverse launch mode includes engaging the dog clutch when the motor generator unit is operating in a reverse rotational direction.

The above features and advantages and other features and advantages of the present disclosure will become apparent from the following detailed description when taken in conjunction with the accompanying drawings.

Drawings

The drawings described herein are for illustration purposes only and are not intended to limit the scope of the present disclosure in any way.

FIG. 1 is a schematic illustration of a powertrain system of an electric vehicle according to the principles of the present disclosure;

FIG. 2 is a schematic diagram of a powertrain system of an electric vehicle according to the principles of the present disclosure;

FIGS. 3A and 3B are graphs comparing motor torque to motor speed and resulting vehicle performance in accordance with the principles of the present disclosure;

FIG. 4 is a vehicle speed profile of various examples of a powertrain system according to the principles of the present disclosure; and

FIG. 5 is a graphical representation of torque measurements at various components of a powertrain system according to the principles of the present disclosure.

Detailed Description

Referring to the drawings, wherein like reference numbers refer to like components, in fig. 1 and 2, an example of a vehicle powertrain is shown and will now be described. The powertrain in fig. 1 is designated by reference numeral 10 and includes a Motor Generator Unit (MGU)12, a torque converter 14, a first shaft 16, a second shaft 18, a synchronizer 20, a first co-planar gear set 22, a second co-planar gear set 24, and a transmitting member 26. More specifically, the MGU 12 is an electric motor that provides torque to the output shaft 28 by converting stored electrical power into rotating mechanical torque. However, other types of motors or engines are contemplated for use with powertrain system 10 without departing from the present disclosure. For example, an internal combustion engine may be employed to provide torque to other portions of the powertrain.

The torque converter 14 includes a turbine 30, a stator 32, and a pump 34. The turbine 30 is connected for common rotation with the first shaft 16. The pump 34 is connected for common rotation with the output shaft 28 of the MGU 12. The stator 32 is disposed between the turbine 30 and the pump 34 and provides a mechanism for multiplying the torque from the turbine 30 to the pump 34.

The first and second co-planar gear sets 22, 24 each include two gears. The first gear 36 of the first co-planar gear set 22 is rotatably supported by the first shaft 16. The second gear 38 of the first co-planar gear set 22 is connected for common rotation with the second shaft 18. The transfer member 26 is connected for common rotation with a first gear 36 and a second gear 38, respectively, of the first co-planar gear set 22. The transfer member 26 may be a chain or belt or some other means for maintaining torque transfer from the first gear 36 to the second gear 38 of the first co-planar gear set 22 while maintaining the same rotational direction.

The first gear 40 of the second co-planar gear set 24 is also rotatably supported by the first shaft 16. The second gear 42 of the second co-planar gear set 24 is connected for common rotation with the second shaft 18. The first gear 40 and the second gear 42 of the second co-planar gear set 24 are disposed in meshing arrangement with one another. In this manner, torque is transferred from the first gear 40 to the second gear 42 of the second co-planar gear set 24, wherein the direction of rotation between the first gear 40 and the second gear 42 is changed.

The second shaft 18 includes an output gear 44, the output gear 44 being connected to the second shaft 18 for common rotation. The output gear 44 meshes with a ring gear 60 of a differential 62, providing a torque path to the drive wheels 64 of the vehicle.

The synchronizer 20 includes internal splines that engage splines on the first shaft 16 to provide for common rotation between the synchronizer 20 and the first shaft 16 while maintaining relative axial movement. Thus, by sliding on the first shaft 16, the synchronizer 20 is selectively manipulated into one of three positions. When the synchronizer 20 is disposed in the first or neutral position, the first shaft 16 is free to rotate relative to the first gears 36, 40 of the first and second co-planar gear sets 22, 24. In the second or forward position, synchronizer 20 slides along first shaft 16 to mesh for common rotation with first gear 40 of second co-planar gear set 24. In this manner, the first gear 40 rotates in unison with the synchronizer 20 and the first shaft 16, respectively.

In the third or reverse position, the synchronizer 20 slides along the first shaft 16 to mesh with the first gear 36 of the first co-planar gear set 22 for common rotation. Similar to the second position, the third position provides for common rotation between the first gear 36 of the first co-planar gear set 22 and the first shaft 16. However, because the first gear 36 is coupled to the second gear 38 through the transfer member 26 rather than through meshing gears, the second gear 38, as well as the second shaft 18, the output gear 44, and the differential 62 rotate in opposite directions. In this manner, a reverse gear ratio is achieved that maintains the same rotational direction of the MGU 12. The resulting benefits include maintaining torque multiplication of the torque converter 14 while providing reverse direction on the drive wheels 64.

Turning now to fig. 2, another example of the present disclosure is shown and will now be described. The powertrain in FIG. 2, which includes MGU 112, torque converter 114, first shaft 116, second shaft 118, torque-transmitting mechanism 120, co-planar gear set 122, and planetary gear set 124, is designated by reference numeral 100. More specifically, the MGU 112 is an electric motor that provides torque to the output member 128 by converting stored electric power to rotating mechanical torque.

The torque converter 114 includes a turbine 130, a stator 132, and a pump 134. The turbine 130 is connected for common rotation with the first shaft 116. The pump 134 is connected for common rotation with the output member 128 of the MGU 112. The stator 132 is disposed between the turbine 130 and the pump 134 and provides a mechanism for multiplying the torque from the turbine 130 to the pump 134.

The co-planar gear set 122 includes a first gear 136 and a second gear 138. The first gear 136 of the co-planar gear set 122 is connected for common rotation with the first shaft 116. The second gear 138 of the co-planar gear set 122 is connected for common rotation with the second shaft 118.

The planetary gear set 124 includes a sun gear member 140, a ring gear member 142, and a planet gear carrier member 144, the planet gear carrier member 144 rotatably supporting a set of planet gears 146 (only two of which are shown). The planet gears 146 are each configured to intermesh with both the sun gear member 140 and the ring gear member 142. The sun gear member 140 is connected for common rotation with the pump 134 of the torque converter 114. The ring gear member 142 is selectively connectable to a housing 150 of the powertrain through the torque-transmitting mechanism 120. The type of torque-transmitting mechanism 120 employed in this example is a dog clutch 120, which is selectively operated by the powertrain controller. However, alternative torque-transmitting mechanisms may be employed without departing from the scope of the present disclosure. For example, torque-transmitting mechanism 120 may be a clutch or brake having interleaved clutch plates that are selectively activated by a powertrain controller via hydraulic pistons. The planet carrier member 144 includes a splined outer periphery 148 that meshes with a second co-planar gear 152, the second co-planar gear 152 being connected for common rotation with the second shaft 118. In the alternative to accomplish the same purpose, the planet carrier member 144 is connected for common rotation with the first gear 154 of the second co-planar gear set 156. The second co-planar gear set 156 includes a second co-planar gear 152, the second co-planar gear 152 meshing with the first gear 154 and connected for common rotation with the second shaft 118.

The second shaft 118 includes an output gear 158, the output gear 158 being connected to the second shaft 118 for common rotation. The output gear 158 meshes with an annular or input gear 160 of a differential 162, providing a torque path to the drive wheels 164 of the vehicle.

Operation of the powertrain 100 includes three phases or functional modes. In a first or initial forward launch mode, the torque-transmitting mechanism 120 is engaged and the driveline launches the vehicle in a forward direction. Since the pump 134 and turbine 130 are not hydraulically coupled at start-up, power flows from the pump 134 through the sun gear member 140 of the planetary gear set 124. Because the ring gear member 142 is held by the torque-transmitting mechanism 120, the planet gears 146 rotate relative to the sun gear member 140 and the ring gear member 142. The planet carrier member 144 rotates at a speed ratio (speed ratio) that is less than that of the sun gear member 140, and therefore less than the output member 128 of the MGU 112. Power flows through the planet carrier member 144 to the co-planar gear 152 of the second shaft 118 and to the output gear 158 and the differential 162. The purpose of the first mode is to immediately transmit a low speed, high torque power flow from the MGU 112 to the drive wheels 164.

The second or secondary forward launch mode includes disengaging the torque-transmitting mechanism 120 while continuing to launch the vehicle forward. As the speed of the turbine 130 increases and is coupled with the pump 134 of the torque converter 114, the power flow path includes the torque converter 114, the first shaft 116, the first gear 136 of the co-planar gear set 122, the second gear 138 of the co-planar gear set 122, and the second shaft 118. Since the power flow is through the torque converter, if torque-transmitting mechanism 120 is of the dog clutch type, it will automatically unload and disengage. If additional control is required of the torque-transmitting mechanism 120, such as a hydraulic brake or clutch, disengagement would require hydraulic or electrical signals to be accomplished.

The third or reverse launch mode includes launching the vehicle in reverse at a lower gear ratio. With the torque-transmitting mechanism 120 engaging and braking the ring gear member 142 of the planetary gear set 124, the MGU 112 is energized in the opposite direction, and the power flow includes the pump 134 of the torque converter 114, the sun gear member 140 of the planetary gear set 124, the planet gear carrier member 144 of the planetary gear set 124, the splined outer periphery 148 of the planet gear carrier member 144, the co-planar gears 152, and the second shaft 118. Since the ring gear member 142 is held, the planet carrier member 144 rotates at a lower speed than the sun gear member 140, but carries a higher torque.

Turning now to fig. 3A, 3B, 4 and 5, graphs depicting the performance of a vehicle having the powertrain system 100 of the present disclosure are shown and will now be described. Fig. 3A is a graph 200 illustrating the amount of torque 202 available at a particular motor speed 204. The data includes a baseline MGU 206 and a reduced-size MGU 208. As can be seen, the baseline MGU 206 has more torque at lower motor speeds 210, however, the reduced sized MGU208 has higher torque at higher motor speeds 212. Thus, while the benefits of utilizing a reduced-size MGU208 may be realized at higher motor speeds 212, performance degradation at lower motor speeds 210 requires additional solutions. FIG. 3B is a graph 228 illustrating the performance of an electric vehicle in a staged reverse maneuver. The y-axis 214 depicts the speed in kph at vehicle start-up at a reverse 25% staging. The x-axis 216 depicts the time (seconds) required to reach a particular speed. In the data provided, the baseline MGU 206 requires 2.5 seconds to achieve 10kph 220, while the reduced-size MGU208 requires 7.2 seconds to achieve 10 kph. 218 indicates a larger reduction in the MGU size, which results in almost twice the time required to reach 10kph, 13 seconds.

The graph 230 shown in FIG. 4 depicts launch performance for three different powertrain configurations. The y-axis 232 is the firing rate in kph, while the x-axis 234 is the time in seconds. As can be seen, the baseline MGU 206 performs up to about 4 seconds less than other powertrain configurations. In particular, the first data includes the performance of the reduced-size MGU208 (in this example, 25% motor reduction) and the reduced-size MGU 222 having the powertrain 100 configured in fig. 2.

The graph 270 shown in fig. 5 depicts the torque output of the powertrain in three configurations. The y-axis 272 is torque and the x-axis 274 is time in seconds from start-up. The second data series 276 is generated by the torque of the pump 134 of the torque converter 114. The third data series 278 is generated by the torque of the turbine 130. The fourth data series 280 is generated from the torque of the planetary gear set 124 having the configuration shown in FIG. 2. As shown, the torque multiplication from the pump 134 to the planet carrier member 144 increases significantly.

While examples have been described in detail, those familiar with the art to which this disclosure relates will recognize various alternative designs and examples for practicing the disclosed methods within the scope of the appended claims.