JP6519340B2 - Torque vectoring device - Google Patents

Description

  The present invention relates to a torque vectoring device.

  BACKGROUND ART Conventionally, as disclosed in Patent Document 1, a torque vectoring device has been proposed which distributes drive torque output to left and right drive wheels by motor torque. The torque vectoring device includes a first planetary gear mechanism serving as a differential mechanism, a second planetary gear mechanism serving as a torque distribution mechanism, a third planetary gear mechanism, and a motor generator. .

WO 2014/008896 A1 Publication

  In the torque vectoring device disclosed in Patent Document 1, a first connecting member that connects a sun gear of a first planetary gear mechanism and a ring gear of a second planetary gear mechanism, a carrier of the first planetary gear mechanism, and a third planetary gear mechanism And a second connecting member that connects with the ring gear of the second gear is disposed between the first planetary gear mechanism and the second planetary gear mechanism. For this reason, the dimension of the axial direction of the drive device for vehicles was large.

  The present invention has been made to solve the above-described problems, and provides a torque vectoring device capable of reducing the axial dimension.

  In order to solve the above problems, the invention of the torque vectoring device according to claim 1 has a first planetary gear mechanism, a second planetary gear mechanism, a third planetary gear mechanism, and a motor, and is outputted from a drive source. A torque vectoring device that variably distributes the torque to the left and right drive wheels, wherein the first planetary gear mechanism includes a first sun gear provided non-rotatably, and a plurality of first A planetary gear, a plurality of first planetary gears rotatably supported, a first carrier on which one of the drive wheels is rotatably connected, and a first ring gear engaged with the plurality of first planetary gears; The second planetary gear mechanism rotatably supports a second sun gear, a plurality of second planetary gears meshing with the second sun gear, and the plurality of second planetary gears, and the other drive wheel A second carrier rotatably connected and a second ring gear engaged with the plurality of second planetary gears and connected to the first ring gear, wherein the third planetary gear mechanism is coaxial with the plurality of second planetary gears A plurality of third planetary gears integrally formed with the plurality of second planetary gears and rotatably supported on the second carrier, and meshed with the plurality of third planetary gears, and a torque output from the drive source And a third ring gear to which is input, and the motor is rotatably connected to the second sun gear.

  According to the torque vectoring device configured as described above, connecting members for connecting the respective elements of the respective planetary gear mechanisms are unnecessary between the respective planetary gear mechanisms. Therefore, the axial dimension of the torque vectoring device can be reduced.

BRIEF DESCRIPTION OF THE DRAWINGS It is explanatory drawing of the drive device for vehicles by which the torque vectoring apparatus which concerns on this embodiment was mounted. It is a velocity diagram of a torque vectoring device.

(Drive for vehicle)
The vehicle drive device 100 of the vehicle V on which the torque vectoring device 10 of the present embodiment is mounted will be described below using FIG. 1. The vehicle drive device 100 includes an engine 1, a transmission 2, an output gear 3, and a torque vectoring device 10. The vehicle V includes drive wheels 21L and 21R and drive shafts 22L and 21R.

  The engine 1 (drive source) is a known internal combustion engine that outputs an engine torque using a hydrocarbon such as gasoline or light oil as a fuel. The transmission 2 has an input shaft 2a and an output shaft 2b. The transmission 2 decelerates or accelerates the engine torque input from the engine 1 via the input shaft 2a at a transmission ratio obtained by dividing the rotational speed of the input shaft 2a by the rotational speed of the output shaft 2b. An output gear 3 is provided on the output shaft 2b. The transmission 2 includes both a manual transmission and an automatic transmission. The automatic transmission includes a torque converter type automatic transmission equipped with a torque converter and a plurality of planetary gear mechanisms, a continuously variable automatic transmission (CVT), an automated manual transmission (AMT), a dual clutch transmission (DCT) Etc. are included.

(Torque vectoring device)
The torque vectoring device 10 variably distributes the engine torque output from the transmission 2 (output gear 3) to the left and right drive wheels 21L and 21R, and absorbs the rotational speed difference between the left and right drive wheels 21L and 21R. It is The torque vectoring device 10 includes a first planetary gear mechanism 11, a second planetary gear mechanism 12, a third planetary gear mechanism 13, a motor generator 14 (motor), an inverter device 15, a battery 16, and a control unit 17. There is. The first planetary gear mechanism 11, the second planetary gear mechanism 12, and the third planetary gear mechanism 13 are coaxially provided in series in the axial direction.

  The first planetary gear mechanism 11 includes a first sun gear S1, a plurality of first planetary gears P1, a first carrier C1, and a first ring gear R1. The first sun gear S1 is fixed to a housing 10a of the torque vectoring device 10. That is, the first sun gear S1 is provided non-rotatably. The plurality of first planetary gears P1 are provided on the outer peripheral side of the first sun gear S1 in mesh with the first sun gear S1.

  The first carrier C1 supports the plurality of first planetary gears P1 rotatably (automatically). The first carrier C1 is rotationally connected to the left drive wheel 21L via the left drive shaft 22L. That is, the first carrier C1 integrally rotates with the left drive wheel 21L. The first ring gear R1 is ring-shaped, and the first ring gear R1 is provided on the outer peripheral side of the plurality of first planetary gears P1. A first inner gear R11 is formed on the inner peripheral side of the first ring gear R1. The first inner gear R11 meshes with a plurality of first planetary gears P1.

  The second planetary gear mechanism 12 is provided adjacent to the first planetary gear mechanism 11. The second planetary gear mechanism 12 is composed of a second sun gear S2, a plurality of second planetary gears P2, a second carrier C2, and a second ring gear R2. The plurality of second planetary gears P2 are provided on the outer peripheral side of the second sun gear S2 in mesh with the second sun gear S2.

  The second carrier C2 rotatably and rotatably supports the plurality of second planetary gears P2. The second carrier C2 is rotationally connected to the right drive wheel 21R via the right drive shaft 22R. That is, the second carrier C2 rotates integrally with the right drive wheel 21R. The second ring gear R2 has a ring shape, and is provided on the outer peripheral side of the plurality of second planetary gears P2. A second inner gear R21 is formed on the inner peripheral side of the second ring gear R2. The second inner gear R21 meshes with the plurality of second planetary gears P2. The first ring gear R1 and the second ring gear R2 are connected by a first connecting member 10b.

Note that the number of teeth _{Z S1} of the first sun gear S1, the number of teeth _{Z S2} of the second sun gear S2 is equal. Further, the number of teeth _{Z P1} of the first planetary gears P1, the number of teeth _{Z P2} of the second planetary gears P2, is equal. Furthermore, the number of teeth _{Z R11} of the first inner gear R11, the number of teeth _{Z R21} of the second inner gear R21 is equal.

The third planetary gear mechanism 13 (third gear mechanism) is provided adjacent to the second planetary gear mechanism 12. The third planetary gear mechanism 13 is configured of a plurality of third planetary gears P3, a second carrier C2, and a third ring gear R3. The second planetary gear P2 and the third planetary gear P3 are common planetary gears coaxially and integrally provided. The gear diameter of the second planetary gear P2 is larger than the gear diameter of the third planetary gear P3. The number of teeth _{Z P2} of the second planetary gear P2 is made larger than the number of teeth _{Z P3} of the third planetary gear P3. The second carrier C2 supports the plurality of third planetary gears P3 rotatably (automatically). The third ring gear R3 is ring-shaped, and is provided on the outer peripheral side of the plurality of third planetary gears P3. A third inner gear R31 is formed on the inner peripheral side of the third ring gear R3, and a third outer gear R32 is formed on the outer peripheral side. The number of teeth _{Z R32} of the third outer gear R32 is made larger than the number of teeth _{Z R31} of the third inner gear R31. The third inner gear R31 meshes with the plurality of third planetary gears P3. The third outer gear R32 meshes with the output gear 3.

  The motor generator 14 comprises a rotor 14a and a stator 14b. The rotor 14a is rotatably provided. The rotor 14a is rotationally connected to the second sun gear S2 and integrally rotates with the second sun gear S2. The stator 14 b is non-rotatably provided on the outer peripheral side of the rotor 14 a. The battery 16 is a secondary battery that stores electric power, and supplies power to the stator 14 b of the motor generator 14 via the inverter device 15. The inverter device 15 boosts the voltage of the power supplied from the battery 16 based on the command from the control unit 17 and supplies it to the stator 14 b of the motor generator 14 to drive the motor generator 14. Further, inverter device 15 steps down the current generated by motor generator 14 based on the command from control unit 17 to charge battery 16.

(Description of velocity diagram)
Next, a velocity diagram of the torque vectoring device 10 will be described with reference to FIG. In FIG. 2, the vertical axis is the rotational speed of each element. The region above 0 shown in FIG. 2 is a positive rotation, and the region below 0 is a negative rotation. Since the first sun gear S1 is connected to the housing 10a, it does not rotate. The second sun gear S2 rotationally connected to the motor generator 14 is capable of positive rotation or negative rotation. Each symbol in FIG. 2 is as follows.
Z _s1 : Number of teeth of first sun gear Z _s2 : Number of teeth of second sun gear Z _R11 : Number of teeth of first inner gear R11 _R21 : Number of teeth of second inner gear R21 Z _R31 : Teeth of third inner gear R31 Number Z _p2 : Number of teeth of second planetary gear P2 Z _p3 : Number of teeth of third planetary gear P3 Tm: Motor torque Te input to second sun gear S2: Engine torque Tlv input to third ring gear R3: Left drive wheel Left drive torque Trv input to 21L: Right drive torque input to right drive wheel 21R

  When the vehicle V is traveling straight, the rotational speed of the second sun gear S2 is zero, and no external torque is input to the motor generator 14, and neither driving nor power generation is performed. When the vehicle V is turning, regardless of when going straight, in the case where the driving torque difference is given to the left and right driving wheels 21L, 21R, the motor in the direction in which the second sun gear S2 rotates forward or backward. The generator 14 outputs a motor torque Tm. Then, the right drive torque Trv input to the right drive wheel 21R rotationally connected to the second carrier C2 and the right drive torque Tlv input to the left drive wheel 21L rotationally connected to the first carrier C1 change. Do. When the vehicle V is turning, as shown in FIG. 2, the inclination of the first straight line L1 representing the relationship between the respective elements on the right side of the ring gears R1 and R2 and the rotational speed changes, and When the inclination changes, the inclination of the first straight line L1 and the second straight line L2 connected by the ring gears R1 and R2 (a straight line representing the relationship between the elements on the left side of the ring gears R1 and R2 in FIG. 2 and the rotational speed) Changes.

(Effect of this embodiment)
As apparent from the above description, the torque vectoring device 10 has the first planetary gear mechanism 11, the second planetary gear mechanism 12, the third planetary gear mechanism 13, and the motor generator 14, and the engine 1 (drive source Is variably distributed to the left and right driving wheels 21L and 21R. The first planetary gear mechanism 11 rotatably supports a first sun gear S1 provided non-rotatably, a plurality of first planetary gears P1 meshing with the first sun gear S1, and a plurality of first planetary gears P1. A first carrier C1 in which one drive wheel 21L is rotationally connected and a first ring gear R1 meshing with a plurality of first planetary gears P1 are provided. The second planetary gear mechanism 12 rotatably supports a second sun gear S2, a plurality of second planetary gears P2 meshing with the second sun gear S2, and a plurality of second planetary gears P2, and the other drive wheel 21R A second carrier C2 rotationally connected and a second ring gear R2 engaged with the plurality of second planetary gears P2 and connected to the first ring gear R1 are provided. The third planetary gear mechanism 13 is integrally formed with the plurality of second planetary gears P2 coaxially with the plurality of second planetary gears P2, and rotatably supported by the second carrier C2 with the plurality of third planetary gears P3. And a third ring gear R3 engaged with the plurality of third planetary gears P3 and to which the engine torque output from the engine 1 (drive source) is input. The motor generator 14 is rotatably connected to the second sun gear S2.

  According to the torque vectoring device configured as described above, connecting members for connecting the respective elements of the planetary gear mechanisms 11 to 13 are unnecessary among the planetary gear mechanisms 11 to 13. Therefore, the dimension of the torque vectoring device 10 in the axial direction can be reduced, and the mountability of the torque vectoring device 10 on the vehicle V becomes good.

The drive torque difference ΔT1 input to the left and right drive wheels 21L and 21R by the torque vectoring device 10 of the present embodiment is expressed by the following equation (1).
ΔT1 = 2 (1 + Z _R / Z _S ) Tm (1)
ΔT1: Drive torque difference input to the left and right drive wheels 21L, 21R Z _R : Number of teeth of the first inner gear R11 and the second inner gear R21 Z _S : Number of teeth of the first sun gear S1 and the second sun gear S2 Tm: Motor torque input to second sun gear S2

On the other hand, the drive torque difference ΔT2 input to the left and right drive wheels by the torque vectoring device disclosed in WO 2014/008896 A1 is expressed by the following equation (2).
ΔT2 = 2 (Z _R / Z _S ) Tm (2)
ΔT2: Drive torque difference input to the left and right drive wheels Z _R : Number of teeth of ring gear Z _S : Number of teeth of sun gear Tm: Motor torque In the torque vectoring device disclosed in WO 2014/008896 A1, Since two connecting members for connecting the respective elements of each planetary gear mechanism are provided on the outer peripheral side of the planetary gear mechanism, the enlargement of the ring gear is hindered.

  Thus, the drive torque difference ΔT1 of the torque vectoring device 10 of the present embodiment is larger than the drive torque difference ΔT2 of the torque vectoring device disclosed in WO 2014/008896 A1. Therefore, torque vectoring device 10 of the present embodiment can generate a larger drive torque difference ΔT1, or motor generator 14 can be miniaturized.

  The gear diameter of the plurality of second planetary gears P2 is larger than the gear diameter of the plurality of third planetary gears P3. The effects of this will be described below. If the gear diameter of the second planetary gear P2 and the gear diameter of the third planetary gear P3 are the same, the engine torque Te is applied to the first ring gear R1 and the second ring gear R2 in the velocity diagram shown in FIG. It can be regarded as being in the input state. Then, when the vehicle V goes straight, the motor generator 14 needs to control so that the second sun gear S2 does not rotate, which not only makes the control of the motor generator 14 complicated but also causes extra energy in the motor generator 14 Is consumed. On the other hand, in the torque vectoring device 10 of the present embodiment, the gear diameter of the plurality of second planetary gears P2 is larger than the gear diameter of the plurality of third planetary gears P3, so when the vehicle V goes straight, Torque is not input from the outside, and there is no need to control the motor generator 14.

(Another embodiment)
In the embodiment described above, the drive source that outputs the drive torque to the ring gear 31 is the engine 1. However, the drive source for outputting the drive torque to the ring gear 31 may be a motor generator. Further, instead of the motor generator or the motor generator 14, a motor without a power generation function may be used.

  In the embodiment described above, the left drive wheel 21L, which is one drive wheel, is rotationally connected to the first carrier C1 via the left drive shaft 22L, and the other drive wheel is linked to the second carrier C2 via the right drive shaft 22R. A certain right drive wheel 21R is rotationally connected. However, the right drive wheel 21R which is one drive wheel is rotatably connected to the first carrier C1 via the right drive shaft 22R, and the left drive wheel which is the other drive wheel via the left drive shaft 22L to the second carrier C2. An embodiment in which 21 L is rotationally connected may be used.

  DESCRIPTION OF SYMBOLS 10 ... Torque vectoring apparatus, 11 ... 1st planetary gear mechanism, 12 ... 2nd planetary gear mechanism, 13 ... 3rd planetary gear mechanism, S1 ... 1st sun gear, P1 ... 1st planetary gear, C1 ... 1st carrier, R1 ... first ring gear, S2 ... first sun gear, P2 ... second planetary gear, C2 ... second carrier, R2 ... second ring gear, P3 ... third planetary gear, R3 ... third ring gear, 14 ... motor generator (motor)

Claims (2)

A torque vectoring device having a first planetary gear mechanism, a second planetary gear mechanism, a third planetary gear mechanism, and a motor, and variably distributing torque output from a drive source to left and right drive wheels,
The first planetary gear mechanism is
A first sun gear provided non-rotatable,
A plurality of first planetary gears meshing with the first sun gear;
A first carrier rotatably supporting the plurality of first planetary gears, and one of the drive wheels being rotationally connected;
A first ring gear meshing with the plurality of first planetary gears;
The second planetary gear mechanism is
With the second sun gear,
A plurality of second planetary gears meshing with the second sun gear;
A second carrier rotatably rotatably supporting the plurality of second planetary gears, and the other drive wheel being rotationally connected;
And a second ring gear engaged with the plurality of second planetary gears and connected to the first ring gear.
The third planetary gear mechanism is
A plurality of third planetary gears coaxially formed with the plurality of second planetary gears and integrally formed with the plurality of second planetary gears and rotatably supported on the second carrier;
And a third ring gear engaged with the plurality of third planetary gears and to which a torque output from the drive source is input.
The torque vectoring device, wherein the motor is rotationally connected to the second sun gear.   The torque vectoring device according to claim 1, wherein a gear diameter of the plurality of second planetary gears is larger than a gear diameter of the plurality of third planetary gears.

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