Power transmission mechanism

Abstract

To obtain a torque vectoring function while suppressing the complication of the control of a motor generator.SOLUTION: A power transmission mechanism 14 includes: a first one-way clutch 32a having a first inner ring part 150a interlocked with a first pinion gear 58a, and a first outer ring part 152a engaged with an internal gear 100, and switchable in the adaptability of the transmission of torque following a rotation direction of the first outer ring part 152a with respect to the first inner ring part 150a; and a second one-way clutch 32b having a second inner ring part 150b interlocked with a second pinion gear 58b, and a second outer ring part 152b engaged with the internal gear 100, and switchable in the adaptability of the transmission of the torque following a rotation direction of the second outer ring part 152b with respect to the second inner ring part 150b.SELECTED DRAWING: Figure 2

Description

[Technical field]

[0001] The present invention relates to a power transmission mechanism that transmits power from a drive source to wheels. [Background technology]

[0002] In vehicles such as hybrid electric vehicles, for example, the rotating shaft of a motor serving as a drive source is connected to an input shaft of a differential mechanism, and the output shaft of the differential mechanism is connected to wheels (for example, Patent Document 1). (For example, Patent Document 1). [Prior art documents] [Patent documents]

[0003] [Patent Document 1] Japanese Patent Application Publication No. 09-298802 Summary of the Invention [Problem to be solved by the invention]

[0004] When providing a torque vectoring function to a power transmission mechanism that transmits the power of a drive source to wheels, it is possible to provide a motor generator on each of a right output shaft connected to a right wheel and a left output shaft connected to a left wheel. However, this configuration increases the number of motor generators, and the installation space for the motor generators becomes large. For this reason, it is desirable to realize the torque vectoring function while reducing the number of motor generators.

[0005] Therefore, it is conceivable to connect one motor generator to the differential mechanism and realize the torque vectoring function with one motor generator. However, depending on the connection mode of the motor generator to the differential mechanism, the relationship between the increase / decrease in the turning angle due to the torque vectoring function and the rotation direction of the motor generator may be reversed depending on the turning direction. This makes the control of the motor generator when executing the torque vectoring function complicated.

[0006] Therefore, an object of the present invention is to provide a power transmission mechanism that is capable of realizing a torque vectoring function while suppressing the complication of the control of the motor generator. [Means for solving the problem]

[0007] In order to solve the above problems, the power transmission mechanism of the present invention includes a first pinion gear meshed with a first sun gear connected to a first output shaft, a second pinion gear meshed with a second sun gear connected to a second output shaft and meshed with the first pinion gear, a differential case connected to an input shaft and supporting the first pinion gear and the second pinion gear so as to be revolvable around the axes of the first output shaft and the second output shaft and to be rotatable about its own axis, an internal gear rotatable around the axes of the first output shaft and the second output shaft, and an internal gear. The motor generator is connected to the turn gear, a first one-way clutch having a first inner ring portion that interlocks with the first pinion gear and a first outer ring portion that meshes with the internal gear, and capable of switching whether or not torque can be transmitted depending on the rotation direction of the first outer ring portion relative to the first inner ring portion, and a second one-way clutch having a second inner ring portion that interlocks with the second pinion gear and a second outer ring portion that meshes with the internal gear, and capable of switching whether or not torque can be transmitted depending on the rotation direction of the second outer ring portion relative to the second inner ring portion.

[0008] In addition, the first one-way clutch and the second one-way clutch may be arranged so that the rotation direction of the first outer ring portion relative to the first inner ring portion, through which torque can be transmitted, and the rotation direction of the second outer ring portion relative to the second inner ring portion, through which torque can be transmitted, are the same.

[0009] The differential may further include an electronically controlled clutch having first and second clutch plates facing each other, the first clutch plate connected to a differential case, and the second clutch plate connected to an internal gear, which allows differential movement of the first output shaft and the second output shaft by the first pinion gear and the second pinion gear when the first clutch plate and the second clutch plate are in an open state, and which limits the differential depending on the engagement between the first clutch plate and the second clutch plate. Effect of the Invention

[0010] According to the present invention, it is possible to realize a torque vectoring function while suppressing the control of the motor generator from becoming complicated. [Brief description of the drawings]

[0011] [Figure 1] FIG. 1 is a schematic diagram showing the configuration of a vehicle. [Diagram 2] FIG. 2 is a schematic diagram showing the configuration of the power transmission mechanism. [Diagram 3] FIG. 3 is a perspective view showing an example of a double pinion. [Figure 4] FIG. 4 is a diagram illustrating the differential function. [Diagram 5] FIG. 5 is a diagram for explaining the differential limiting function when the left wheel spins. [Figure 6] FIG. 6 is a diagram for explaining the differential limiting function when the right wheel spins. [Figure 7] FIG. 7 is a diagram illustrating the motor drive function. [Figure 8] FIG. 8 is a diagram illustrating the regenerative function. [Figure 9] FIG. 9 is a diagram illustrating an example of the torque vectoring function. [Figure 10] FIG. 10 is a diagram illustrating another example of the torque vectoring function. [Figure 11] FIG. 11 is a diagram illustrating an example of a power transmission mechanism of a comparative example. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0012] Hereinafter, an embodiment of the present invention will be described in detail with reference to the accompanying drawings. The dimensions, materials, and other specific numerical values ​​shown in the embodiment are merely examples for facilitating understanding of the invention, and do not limit the present invention unless otherwise specified. In this specification and drawings, elements having substantially the same functions and configurations are given the same reference numerals to avoid repeated explanations, and elements not directly related to the present invention are not shown.

[0013] 1 is a schematic diagram showing the configuration of a vehicle 1. The vehicle 1 includes a drive source 10, a transmission 12, power transmission mechanisms 14a, 14b, front wheels 16a, and rear wheels 16b.

[0014] The vehicle 1 is an electric vehicle provided with a motor as the driving source 10. The vehicle 1 may be an engine vehicle provided with an engine as the driving source 10. The vehicle 1 may also be a hybrid electric vehicle provided with an engine and a motor in parallel as the driving source 10. The driving source 10 generates torque by consuming, for example, power from a battery (not shown).

[0015] An output shaft of the driving source 10 is connected to the transmission 12. The transmission 12 is, for example, a continuously variable transmission. The transmission 12 is connected to a front wheel 16a through a power transmission mechanism 14a. The power transmission mechanism 14a transmits the torque (power) of the driving source 10 provided through the transmission 12 to the front wheel 16a. The transmission 12 is also connected to a rear wheel 16b through a power transmission mechanism 14b. The power transmission mechanism 14b transmits the torque (power) of the driving source 10 provided through the transmission 12 to the rear wheel 16b.

[0016] Hereinafter, the power transmission mechanism 14a and the power transmission mechanism 14b may be collectively referred to as the power transmission mechanism 14. The power transmission mechanism 14 will be described in detail later. Furthermore, the front wheel 16a and the rear wheel 16b may be collectively referred to as the wheels 16.

[0017] Fig. 2 is a schematic diagram showing the configuration of the power transmission mechanism 14. The power transmission mechanism 14 in Fig. 2 is, for example, an example of a rear-side power transmission mechanism 14b. Note that the front-side power transmission mechanism 14a is similar to the rear-side power transmission mechanism 14b.

[0018] The power transmission mechanism 14 includes an input shaft 20, a planetary mechanism 22, a first output shaft 24, a second output shaft 26, a clutch case 28, an electronically controlled clutch 30, a first one-way clutch 32a, a second one-way clutch 32b, and a motor generator 34.

[0019] The input shaft 20 is, for example, a drive pinion shaft. The input shaft 20 is connected to the transmission 12 via, for example, a propeller shaft. The torque of the drive source 10 is input to the input shaft 20. A bevel gear 40 (bevel gear) is formed at the tip of the input shaft 20. The bevel gear 40 is meshed with a bevel gear 42. The rotating shaft of the bevel gear 42 is connected to the rotating shaft of a reduction gear 44. The reduction gear 44 is linked to the planetary mechanism 22.

[0020] The planetary mechanism 22 includes a helical gear 50, a differential case 52, a first sun gear 54, a second sun gear 56, a first pinion gear 58a, and a second pinion gear 58b.

[0021] The helical gear 50 is meshed with the reduction gear 44. The differential case 52 is formed in a hollow cylindrical shape. One axial end of the differential case 52 is fixed to a surface on one side (e.g., the right side) of the helical gear 50. The other axial end of the differential case 52 is closed by a bottom surface of the differential case 52.

[0022] Differential case 52 is connected to input shaft 20 via helical gear 50, reduction gear 44, and bevel gears 40 and 42. Differential case 52 rotates integrally with helical gear 50. Differential case 52 accommodates a first sun gear 54, a second sun gear 56, a first pinion gear 58a, and a second pinion gear 58b.

[0023] The first sun gear 54 and the second sun gear 56 are arranged parallel to the helical gear 50 and opposed to each other with a gap therebetween. The first sun gear 54 is connected to the first output shaft 24. The first output shaft 24 extends rightward through the differential case 52. The right wheel 16 is connected to the first output shaft 24. The second sun gear 56 is connected to the second output shaft 26. The second output shaft 26 extends leftward through the helical gear 50. The left wheel 16 is connected to the second output shaft 26. The first output shaft 24 and the second output shaft 26 are arranged on the same straight line. That is, the central axes of the helical gear 50, the differential case 52, the first sun gear 54, the first output shaft 24, the second sun gear 56, and the second output shaft 26 overlap with each other.

[0024] The first pinion gear 58a meshes with the first sun gear 54. A first pinion shaft 60a is connected to the center of the first pinion gear 58a. The first pinion shaft 60a is rotatably supported by the helical gear 50 and the differential case 52. In other words, the first pinion gear 58a is capable of revolving around the axis of the first output shaft 24 (in other words, along the periphery of the first sun gear 54) and is supported to be rotatable around the central axis of the first pinion gear 58a.

[0025] The second pinion gear 58b is meshed with the second sun gear 56. A second pinion shaft 60b is connected to the center of the second pinion gear 58b. The second pinion shaft 60b is rotatably supported by the helical gear 50 and the differential case 52. In other words, the second pinion gear 58b is capable of revolving around the axis of the second output shaft 26 (in other words, along the periphery of the second sun gear 56) and is supported to be rotatable around the central axis of the second pinion gear 58b.

[0026] The second pinion gear 58b meshes with the second sun gear 56 and also with the first pinion gear 58a. The second pinion gear 58b rotates in a direction opposite to the rotation direction of the first pinion gear 58a in response to the rotation of the first pinion gear 58a. In other words, the first pinion gear 58a and the second pinion gear 58b form a so-called double pinion.

[0027] 3 is a perspective view showing an example of a double pinion. For example, the first sun gear 54 and the second sun gear 56 have the same diameter and number of teeth. The first pinion gear 58a is composed of a first piece 58a1 and a second piece 58a2. The first piece 58a1 and the second piece 58a2 have the same diameter and number of teeth and are connected by a first pinion shaft 60a. The first piece 58a1 is meshed with the first sun gear 54. The position of the second piece 58a2 is shifted in the axial direction with respect to the first sun gear 54 and the second sun gear 56.

[0028] The second pinion gear 58b has the same diameter and number of teeth as the first pinion gear 58a (in other words, the first piece 58a1 and the second piece 58a2). The second pinion gear 58b meshes with the second sun gear 56. The second pinion gear 58b is axially longer than the second sun gear 56, and meshes with the second piece 58a2.

[0029] For example, when the first output shaft 24 rotates relatively in the counterclockwise direction, the first sun gear 54 rotates counterclockwise in conjunction with the first output shaft 24. Then, the first piece 58a1 meshed with the first sun gear 54 rotates clockwise. In this case, the second piece 58a2 connected to the first piece 58a1 by the first pinion shaft 60a rotates clockwise in conjunction with the first piece 58a1. The second pinion gear 58b meshed with the second piece 58a2 rotates counterclockwise, which is the opposite direction to the rotation direction of the second piece 58a2. Then, the second sun gear 56 meshed with the second pinion gear 58b rotates clockwise. Then, the second output shaft 26 rotates in the clockwise direction, which is the opposite direction to the first output shaft 24, in conjunction with the second sun gear 56.

[0030] In this way, first pinion gear 58a and second pinion gear 58b function as differential element 58 capable of differentially rotating first output shaft 24 and second output shaft 26. Note that the double pinion is not limited to the specific example given above, and can be designed as appropriate.

[0031] Returning to Fig. 2, the clutch case 28 is formed in a roughly cylindrical shape. The clutch case 28 is provided on the outside of the differential case 52 so as to cover the differential case 52. The central axis of the clutch case 28 overlaps with the central axis of the first output shaft 24. The clutch case 28 is rotatable around the axis of the first output shaft 24.

[0032] The electronically controlled clutch 30 includes a plurality of first clutch plates 70, a plurality of second clutch plates 72, a ball cam 74, and a clutch actuation motor 76. Hereinafter, the first clutch plates 70 and the second clutch plates 72 may be collectively referred to simply as clutch plates.

[0033] The clutch plates are formed in an annular plate shape. The differential case 52 is inserted inside the clutch plates. In other words, the clutch plates are located on the outer periphery of the differential case 52 and extend in the radial direction of the differential case 52. The central axis of the clutch plates overlaps with the central axis of the first output shaft 24.

[0034] The first clutch plate 70 is connected to a member different from the differential element 58 in the planetary mechanism 22, specifically, to the differential case 52. The first clutch plate 70 is connected to the differential case 52 so as to be slidable in the axial direction (i.e., the axial direction of the first output shaft 24). For example, a spline extending in the axial direction is formed on the outer circumferential surface of the differential case 52, and the first clutch plate 70 is slidable by having its inner circumferential edge connected to the spline of the differential case 52. The outer circumferential edge of the first clutch plate 70 is separated from the clutch case 28.

[0035] The second clutch plate 72 is connected to the clutch case 28. The second clutch plate 72 is connected to the clutch case 28 so as to be slidable in the axial direction of the clutch case 28 (i.e., the axial direction of the first output shaft 24). For example, a spline extending in the axial direction is formed on the inner peripheral surface of the clutch case 28, and the second clutch plate 72 is slidable by having an outer peripheral edge connected to the spline on the inner peripheral surface of the clutch case 28. The inner peripheral edge of the second clutch plate 72 is separated from the differential case 52.

[0036] The multiple first clutch plates 70 are stacked in the axial direction. The first clutch plates 70 and the second clutch plates 72 are alternately stacked and disposed such that each of the multiple second clutch plates 72 sandwiches a first clutch plate 70 therebetween.

[0037] The ball cam 74 is provided on one side in the stacking direction of the clutch plates. Specifically, the ball cam 74 is provided on the helical gear 50 side (i.e., the left side in FIG. 2) with respect to the clutch plates. The ball cam 74 includes a pressure plate 80, a cam 82, and a ball 84.

[0038] The pressure plate 80 is disposed to the left of the leftmost surface of the clutch plate. The cam 82 is disposed to the left of the pressure plate 80 and facing the pressure plate 80. A recess is formed in each of the facing surfaces of the cam 82 and the pressure plate 80. The ball 84 is accommodated in the recess of the cam 82 and the pressure plate 80, and is sandwiched between the cam 82 and the pressure plate 80. The cam 82 is fixed to a housing 86 that houses, for example, the clutch case 28, etc.

[0039] The clutch actuating motor 76 is connected to a reduction gear 90. The reduction gear 90 is meshed with a reduction gear 92. The rotation shaft of the reduction gear 92 is connected to the rotation shaft of a reduction gear 94. The reduction gear 94 is meshed with teeth provided on the outer circumferential surface of the pressure plate 80. The clutch actuating motor 76 is capable of rotating the pressure plate 80 through the reduction gears 90, 92, and 94.

[0040] If the rotational angle of the clutch actuation motor 76 is taken as the initial position, there is no deviation in the rotational direction of the pressure plate 80 relative to the cam 82. When the pressure plate 80 is not misaligned in the rotational direction, the pressure plate 80 is positioned closer to the cam 82 and does not press the clutch plates. In this state, the surfaces of the clutch plates are separated and the electronically controlled clutch 30 is disengaged. When the electronically controlled clutch 30 is in the disengaged state, the differential case 52 and the clutch case 28 can rotate independently of each other (in other words, individually).

[0041] On the other hand, when the rotation angle of the clutch actuation motor 76 is increased from the initial position, a deviation in the rotational direction occurs in the pressure plate 80 relative to the cam 82. When the pressure plate 80 deviates in the rotational direction, the balls 84 move so as to overcome the recesses in the cam 82 and the pressure plate 80, and the pressure plate 80 is pushed toward the clutch plate by an amount corresponding to the rotational angle.

[0042] As a result, the pressure plate 80 presses against the clutch plates, the surfaces of the clutch plates come into contact with each other, and frictional force is generated between the clutch plates. This frictional force engages the electronically controlled clutch 30 (specifically, the first clutch plate 70 and the second clutch plate 72). In this way, the clutch actuation motor 76 controls the rotation angle, and as a result, the engagement force of the electronically controlled clutch 30 can be controlled. Furthermore, when the electronically controlled clutch 30 is fully engaged, the differential case 52 and the clutch case 28 are mutually constrained and rotate as a unit.

[0043] An internal gear 100 (internal gear) is formed on the inner circumferential surface of the clutch case 28. The internal gear 100 is disposed to the right of the rightmost surface of the clutch plate. The internal gear 100 is located on the opposite side of the differential case 52 from the helical gear 50 (the right side in FIG. 2). The internal gear 100 is connected to the second clutch plate 72 through the clutch case 28. The internal gear 100 is connected to the motor generator 34 through the clutch case 28, as will be described later. The internal gear 100 is rotatable integrally with the clutch case 28 around the axes of the first output shaft 24 and the second output shaft 26.

[0044] An external gear 110 (external gear) is formed on the outer circumferential surface of the clutch case 28. The external gear 110 is located at the end of the clutch case 28 opposite to the helical gear 50. The external gear 110 is integral with the clutch case 28 and is rotatable around the axis of the first output shaft 24.

[0045] The motor generator 34 is, for example, a synchronous motor or an induction motor. The motor generator 34 is provided separately (i.e., independently) from the drive source 10 that inputs torque to the input shaft 20 of the planetary mechanism 22. The motor generator 34 is connected to a battery via an inverter (not shown). The motor generator 34 can consume power from the battery to rotate the rotating shaft 120. The motor generator 34 can also generate power (i.e., generate electricity) in response to the rotation of the rotating shaft 120. The power generated by the motor generator 34 is regenerated in the battery.

[0046] An external gear 122 is formed on the tip of a rotating shaft 120 of the motor generator 34. The external gear 122 is meshed with a reduction gear 124. The rotating shaft of the reduction gear 124 is connected to a reduction gear 126. The reduction gear 126 is meshed with the external gear 110 of the clutch case 28.

[0047] The motor generator 34 is connected to the clutch case 28 via a rotating shaft 120, an external gear 122, reduction gears 124 and 126, and an external gear 110. The motor generator 34 is connected to the internal gear 100 via the clutch case 28.

[0048] The first one-way clutch 32a is disposed between the differential case 52 and the clutch case 28. The first one-way clutch 32a has a first inner ring portion 150a, a first outer ring portion 152a, and a first intermediate portion 154a.

[0049] The first inner ring portion 150a is formed in a cylindrical shape. The first pinion shaft 60a is connected to the center of the first inner ring portion 150a. Therefore, the first inner ring portion 150a rotates integrally with the first pinion gear 58a in conjunction with the first pinion gear 58a. The first outer ring portion 152a is formed in an annular shape whose inner diameter is larger than the outer diameter of the first inner ring portion 150a. The first inner ring portion 150a is located inside the first outer ring portion 152a and is arranged concentrically with the first outer ring portion 152a. Teeth are formed on the outer peripheral surface of the first outer ring portion 152a. The teeth on the outer peripheral surface of the first outer ring portion 152a are engaged with the internal gear 100. The first intermediate portion 154a is arranged between the first inner ring portion 150a and the first outer ring portion 152a.

[0050] The first one-way clutch 32a can switch between transmitting and not transmitting torque according to the rotation direction of the first outer ring portion 152a relative to the first inner ring portion 150a. For example, when the first outer ring portion 152a rotates in one circumferential direction relative to the first inner ring portion 150a, the torque is transmitted between the first inner ring portion 150a and the first outer ring portion 152a through the first intermediate portion 154a. On the other hand, when the first outer ring portion 152a rotates in the other circumferential direction relative to the first inner ring portion 150a, the transmission of torque through the first intermediate portion 154a is interrupted, and the first outer ring portion 152a rotates freely relative to the first inner ring portion 150a.

[0051] The second one-way clutch 32b is disposed between the differential case 52 and the clutch case 28. The second one-way clutch 32b has a second inner ring portion 150b, a second outer ring portion 152b, and a second intermediate portion 154b.

[0052] The second inner ring portion 150b is formed in a cylindrical shape. The second pinion shaft 60b is connected to the center of the second inner ring portion 150b. Therefore, the second inner ring portion 150b rotates integrally with the second pinion gear 58b in conjunction with the second pinion gear 58b. The second outer ring portion 152b is formed in an annular shape whose inner diameter is larger than the outer diameter of the second inner ring portion 150b. The second inner ring portion 150b is located inside the second outer ring portion 152b and is arranged concentrically with the second outer ring portion 152b. Teeth are formed on the outer peripheral surface of the second outer ring portion 152b. The teeth on the outer peripheral surface of the second outer ring portion 152b are engaged with the internal gear 100. The second intermediate portion 154b is arranged between the second inner ring portion 150b and the second outer ring portion 152b.

[0053] The second one-way clutch 32b can switch between transmitting and not transmitting torque according to the rotation direction of the second outer ring portion 152b relative to the second inner ring portion 150b. For example, when the second outer ring portion 152b rotates in one circumferential direction relative to the second inner ring portion 150b, the torque is transmitted between the second inner ring portion 150b and the second outer ring portion 152b through the second intermediate portion 154b. On the other hand, when the second outer ring portion 152b rotates in the other circumferential direction relative to the second inner ring portion 150b, the transmission of torque through the second intermediate portion 154b is interrupted, and the second outer ring portion 152b rotates freely relative to the second inner ring portion 150b.

[0054] The first one-way clutch 32a and the second one-way clutch 32b are arranged so that the rotation direction of the first outer ring portion 152a relative to the first inner ring portion 150a, through which torque can be transmitted, and the rotation direction of the second outer ring portion 152b relative to the second inner ring portion 150b, through which torque can be transmitted, are the same. For example, assume that the first one-way clutch 32a and the second one-way clutch 32b are viewed from the motor generator 34 side. At this time, the first one-way clutch 32a allows the transmission of torque if the rotation direction of the first outer ring portion 152a is clockwise relative to the first inner ring portion 150a, and the second one-way clutch 32b allows the transmission of torque if the rotation direction of the second outer ring portion 152b is clockwise relative to the second inner ring portion 150b.

[0055] When the electronically controlled clutch 30 is released, the differential case 52 and the clutch case 28 can rotate independently as described above. In this case, when the first pinion gear 58a rotates, the first inner ring portion 150a of the first one-way clutch 32a rotates in conjunction with the first pinion gear 58a. The rotation direction of the first inner ring portion 150a is the same as the rotation direction of the first pinion gear 58a. At this time, if the rotation direction of the first outer ring portion 152a relative to the first inner ring portion 150a due to the rotation of the first inner ring portion 150a is a direction that allows the transmission of torque (for example, clockwise), the first outer ring portion 152a rotates integrally with the first inner ring portion 150a, causing the internal gear 100 to rotate.

[0056] When the first pinion gear 58a rotates, the second pinion gear 58b rotates in the opposite direction to the first pinion gear 58a. When the second pinion gear 58b rotates, the second inner ring portion 150b of the second one-way clutch 32b rotates in conjunction with the first pinion gear 58b. The rotation direction of the second inner ring portion 150b is the same as the rotation direction of the second pinion gear 58b and is opposite to the rotation direction of the first inner ring portion 150a. In other words, when the first inner ring portion 150a rotates in a direction that allows the transmission of torque, the second inner ring portion 150b rotates in a direction that blocks the transmission of torque. Then, the second outer ring portion 152b rotates freely independent of the second inner ring portion 150b and does not contribute to the rotation of the internal gear 100. The second outer ring portion 152b rotates freely on its axis and does not impede the rotation of the internal gear 100 by the first outer ring portion 152a.

[0057] In addition, when the electronically controlled clutch 30 is released, if the rotation direction of the second pinion gear 58b and the second inner ring portion 150b is a direction that allows the transmission of torque, the second outer ring portion 152b rotates integrally with the second inner ring portion 150b, causing the internal gear 100 to rotate. At this time, the first pinion gear 58a and the first inner ring portion 150a rotate in the opposite direction to the second pinion gear 58b and the second inner ring portion 150b. Since the rotation direction of the first inner ring portion 150a is a direction that blocks the transmission of torque, the first outer ring portion 152a rotates freely independent of the first inner ring portion 150a and does not contribute to the rotation of the internal gear 100. Note that the first outer ring portion 152a does not hinder the rotation of the internal gear 100 by the second outer ring portion 152b by rotating freely.

[0058] In contrast, when the electronically controlled clutch 30 is engaged, the clutch case 28 and the differential case 52 rotate together as described above. In this case, the revolution speed of the first pinion gear 58a and the second pinion gear 58b coincides with the revolution speed of the internal gear 100. As a result, the first pinion gear 58a, the first inner ring portion 150a, and the first outer ring portion 152a cannot rotate about the axis of the first pinion gear 58a. Similarly, the second pinion gear 58b, the second inner ring portion 150b, and the second outer ring portion 152b cannot rotate about the axis of the second pinion gear 58b.

[0059] In this way, the electronically controlled clutch 30 limits the rotation of the first pinion gear 58a and the second pinion gear 58b through the first one-way clutch 32a and the second one-way clutch 32b in response to engagement between the first clutch plate 70 and the second clutch plate 72. When the rotation of the first pinion gear 58a and the second pinion gear 58b is limited, the differential between the first output shaft 24 and the second output shaft is consequently limited.

[0060] The power transmission mechanism 14 has a differential function, a differential limiting function (so-called limited slip differential (LSD)) function, a motor drive function, a regenerative function, and a torque vectoring function.

[0061] The differential function is a function that allows differential motion between the first output shaft 24 and the second output shaft 26. The differential limiting function is a function that limits differential motion between the first output shaft 24 and the second output shaft 26. The motor drive function is a function that can output equal torque to each of the first output shaft 24 and the second output shaft 26 in accordance with the rotation of the motor generator 34. The regenerative function is a function that causes the motor generator 34 to generate electricity in accordance with the torque applied to the first output shaft 24 or the second output shaft 26. The torque vectoring function is a function that can output different torques to each of the first output shaft 24 and the second output shaft 26 in accordance with the rotation of the motor generator 34.

[0062] The power transmission mechanism 14 can switch between a differential function, a differential limiting function, a motor drive function, a regenerative function, and a torque vectoring function depending on whether the clutch plates of the electronically controlled clutch 30 are released or engaged. Each function will be described in detail below.

[0063] 4 is a diagram for explaining the differential function. When the differential function is realized (hereinafter, referred to as during differential function), the electronic control clutch 30 is released. Also, during the differential function, the motor generator 34 is stopped.

[0064] As shown by a dashed arrow A10 in Fig. 4, the torque of the driving source 10 is input to the input shaft 20. The torque of the driving source 10 is transmitted from the input shaft 20 to the helical gear 50. As shown by a dashed arrow A12, the torque of the driving source 10 is output to the first output shaft 24 through the first pinion shaft 60a, the first pinion gear 58a, and the first sun gear 54. In parallel with this, the torque of the driving source 10 is output to the second output shaft 26 through the second pinion shaft 60b, the second pinion gear 58b, and the second sun gear 56, as shown by a dashed arrow A14. In this way, the torque of the driving source 10 is output to the first output shaft 24 and the second output shaft 26, respectively.

[0065] For example, when the vehicle 1 turns, a difference in rotation speed occurs between the left and right wheels 16, i.e., the first output shaft 24 and the second output shaft 26. During the differential function, the first pinion gear 58a and the second pinion gear 58b rotate on their own axes, thereby allowing the difference in rotation speed between the first output shaft 24 and the second output shaft 26.

[0066] Here, when one of the left and right wheels 16 spins, the rotation speed of the spinning wheel 16 becomes higher than the rotation speed of the non-spinning wheel 16. This causes the torque transmitted to the non-spinning wheel 16 to decrease, which may reduce the stability of the vehicle 1. Therefore, a differential limiting function is implemented to prevent the difference in rotation speed between the left and right wheels 16 from becoming too large.

[0067] 5 is a diagram for explaining the differential limiting function when the left wheel 16 spins. When the differential limiting function is realized (hereinafter, referred to as during differential limiting), the electronically controlled clutch 30 is engaged. Note that during the differential limiting function, the magnitude of the fastening force of the electronically controlled clutch 30 (i.e., the magnitude of the differential limiting torque) can be controlled to an arbitrary magnitude. Also, during the differential limiting function, the motor generator 34 is stopped.

[0068] When electronically controlled clutch 30 is engaged, clutch case 28 is constrained to differential case 52 as described above, and rotation of first pinion gear 58a and second pinion gear 58b is restricted through internal gear 100, the first one-way clutch, and the second one-way clutch. This restricts a decrease in the rotation speed of right wheel 16 that is not spinning through first sun gear 54 and first output shaft 24.

[0069] In addition, by limiting the rotation of the first pinion gear 58a and the second pinion gear 58b, the torque of the driving source 10 (dashed arrow A10) is output to the first output shaft 24 (dashed arrow A12), and unnecessary output to the second output shaft 26 is prevented.

[0070] 6 is a diagram for explaining the differential limiting function when the right wheel 16 spins. When the right wheel 16 spins, the electronically controlled clutch 30 is engaged to realize the differential limiting function, in the same way as when the left wheel 16 spins.

[0071] When electronically controlled clutch 30 is engaged, the rotation of first pinion gear 58a and second pinion gear 58b is restricted, thereby suppressing a decrease in the rotation speed of non-spinning left wheel 16 through second sun gear 56 and second output shaft 26. In addition, by restricting the rotation of first pinion gear 58a and second pinion gear 58b, the torque (broken arrow A10) of drive source 10 is output to second output shaft 26 (broken arrow A14), suppressing unnecessary output to first output shaft 24.

[0072] In this way, when the differential limiting function is realized, it is possible to suppress a decrease in the torque transmitted to the non-spinning wheels 16. As a result, it is possible to suppress a decrease in the stability of the vehicle 1.

[0073] 7 is a diagram for explaining the motor drive function. When the motor drive function is realized (hereinafter, referred to as during motor drive function), the electronically controlled clutch 30 is engaged. Also, during the motor drive function, the motor generator 34 operates as a motor. The motor generator 34 rotates the rotating shaft 120 so that the rotation direction of the clutch case 28 coincides with the rotation direction of the differential case 52.

[0074] In the motor drive function, the torque of the drive source 10 is output to the first output shaft 24 and the second output shaft 26, similarly to the differential function. In the motor drive function, in addition to the torque of the drive source 10, the torque of the motor generator 34 is also output to the first output shaft 24 and the second output shaft 26.

[0075] Specifically, the torque of the motor generator 34 is transmitted to the clutch case 28 as indicated by the two-dot chain arrow A20. Because the electronically controlled clutch 30 is engaged, the torque of the motor generator 34 is transmitted to the differential case 52 and the helical gear 50 through the clutch plates.

[0076] As indicated by a two-dot chain line arrow A22, the torque of motor generator 34 is output to first output shaft 24 through first pinion shaft 60a, first pinion gear 58a, and first sun gear 54. In parallel with this, the torque of motor generator 34 is output to second output shaft 26 through second pinion shaft 60b, second pinion gear 58b, and second sun gear 56, as indicated by a two-dot chain line arrow A24.

[0077] For example, it is assumed that the torque of the driving source 10 is output in the forward rotation direction from the first output shaft 24 and the second output shaft 26 as indicated by the arrows B24 and B26. The forward rotation direction indicates a rotation direction that moves the vehicle 1 forward or accelerates the vehicle 1. In this state, it is further assumed that the motor generator 34 outputs torque in the forward rotation direction.

[0078] During the motor drive function, the first pinion gear 58a and the second pinion gear 58b revolve together with the differential case 52 and the clutch case 28. As a result, the forward torque of the motor generator 34 is output equally to each of the first output shaft 24 and the second output shaft 26. In other words, the rotation direction of the first output shaft 24 by the motor generator 34 (arrow C24) and the rotation direction of the second output shaft 26 by the motor generator 34 (arrow C26) are the same. Furthermore, in each of the first output shaft 24 and the second output shaft 26, the rotation direction by the torque of the drive source 10 and the rotation direction by the torque of the motor generator 34 are the same.

[0079] The torque in the forward rotation direction of the driving source 10 (arrow B24) and the torque in the forward rotation direction of the motor generator 34 (arrow C24) are added together in the first output shaft 24. Since the torques in the same directions are added together, the torque output from the first output shaft 24 becomes higher than the torque of the driving source 10.

[0080] In the second output shaft 26, the torque in the forward rotation direction of the driving source 10 (arrow B26) and the torque in the forward rotation direction of the motor generator 34 (arrow C26) are added together. Since the torques in the same directions are added together, the torque output from the second output shaft 26 is also higher than the torque of the driving source 10. As a result, during the motor drive function, the acceleration of the vehicle 1 can be assisted by the torque of the motor generator 34 in addition to the torque of the driving source 10.

[0081] However, during the motor drive function, since the electronically controlled clutch 30 is engaged, the first pinion gear 58a and the second pinion gear 58b cannot rotate, and the differential function of the first output shaft 24 and the second output shaft 26 does not work.

[0082] 8 is a diagram for explaining the regenerative function. When the regenerative function is realized (hereinafter, referred to as during regenerative function), the electronic control clutch 30 is engaged. Also, during the regenerative function, the motor generator 34 operates as a generator.

[0083] The regenerative function is realized, for example, when the vehicle 1 decelerates. When the vehicle 1 decelerates, the torque of the driving source 10 is not transmitted to the wheels 16, and a torque in the reverse direction according to the rotation of the wheels 16 is applied to the first output shaft 24 and the second output shaft 26. The reverse direction indicates a rotation direction that moves the vehicle 1 backward or a rotation direction that decelerates the vehicle 1.

[0084] The torque of the wheels 16 applied to the first output shaft 24 is transmitted to the helical gear 50 and the differential case 52 through the first sun gear 54, the first pinion gear 58a, and the first pinion shaft 60a, as shown by a dashed double-dashed line arrow A32. Meanwhile, the torque of the wheels 16 applied to the second output shaft 26 is transmitted to the helical gear 50 and the differential case 52 through the second sun gear 56, the second pinion gear 58b, and the second pinion shaft 60b, as shown by a dashed double-dashed line arrow A34.

[0085] Because the electronically controlled clutch 30 is engaged, the torque of the wheels 16 is transmitted to the clutch case 28 through the clutch plate. At this time, the torque of the wheels 16 rotates the clutch case 28 so that the rotation direction of the clutch case 28 coincides with the rotation direction of the differential case 52. The torque of the wheels 16 is then transmitted to the rotating shaft 120, causing the rotating shaft 120 to rotate in the reverse direction. This causes the motor generator 34 to generate electricity, which is then regenerated into the battery.

[0086] However, during the regenerative function, since the electronically controlled clutch 30 is engaged, the first pinion gear 58a and the second pinion gear 58b cannot rotate, and the differential function of the first output shaft 24 and the second output shaft 26 does not work.

[0087] 9 is a diagram illustrating an example of the torque vectoring function. When the torque vectoring function is realized (hereinafter, referred to as during the torque vectoring function), the electronically controlled clutch 30 is released. Furthermore, during the torque vectoring function, the motor generator 34 operates as a motor. The motor generator 34 may rotate the rotating shaft 120 in any direction, regardless of the rotation direction of the differential case 52.

[0088] During the torque vectoring function, the torque of the driving source 10 is output to the first output shaft 24 and the second output shaft 26, similar to the differential function. During the torque vectoring function, in addition to the torque of the driving source 10, the torque of the motor generator 34 is also output to the first output shaft 24 and the second output shaft 26.

[0089] FIG. 9 shows a case where the motor generator 34 generates torque in the forward direction when the vehicle 1 is turning right. When the vehicle 1 is turning right, the relative rotation speed of the first output shaft 24 on the right side is decelerated as shown by an arrow B44 by the differential function. Also, the relative rotation speed of the second output shaft 26 on the left side is increased as shown by an arrow B46. In this case, the first pinion gear 58a and the first inner ring portion 150a rotate in the clockwise direction when viewed from the motor generator 34 side. The second pinion gear 58b and the second inner ring portion 150b rotate in the counterclockwise direction when viewed from the motor generator 34 side. When the motor generator 34 rotates in the forward direction when the vehicle 1 is turning right, the internal gear 100 is given a torque from the motor generator 34 that rotates the internal gear 100 in the clockwise direction.

[0090] A torque is applied to the first outer ring portion 152a through the internal gear 100 to rotate the first outer ring portion 152a clockwise. When a torque is applied to the first outer ring portion 152a to further rotate clockwise in a state in which the first inner ring portion 150a rotates clockwise, the first one-way clutch 32a transmits the torque of the motor generator 34 to the first pinion gear 58a as indicated by the two-dot chain arrow A40. As a result, in addition to the clockwise rotation caused by the differential function, the first pinion gear 58a is provided with a torque from the motor generator 34 in a direction to increase the clockwise rotation speed. That is, the first pinion gear 58a is provided with a torque that increases the differential. The torque of the motor generator 34 is transmitted from the first pinion gear 58a through the first sun gear 54 to the first output shaft 24 as indicated by the two-dot chain arrow A42. In addition to the torque of the driving source 10, a torque that further decelerates the first output shaft 24 is superimposed on the right-side first output shaft 24 by the motor generator 34 as indicated by an arrow C44.

[0091] Furthermore, a torque that rotates the second outer ring portion 152b clockwise is applied to the second outer ring portion 152b through the internal gear 100. When a torque that rotates the second outer ring portion 152b clockwise is applied in a situation in which the second inner ring portion 150b rotates counterclockwise, the second one-way clutch 32b cuts off the transmission of torque from the motor generator 34.

[0092] However, since the second pinion gear 58b is meshed with the first pinion gear 58a, the torque of the motor generator 34 is applied to the second pinion gear 58b through the first pinion gear 58a. In addition to the counterclockwise rotation due to the differential function, the second pinion gear 58b is applied with a torque in a direction to increase the counterclockwise rotation speed from the motor generator 34 through the first pinion gear 58a. That is, the second pinion gear 58b is applied with a torque that increases the differential. The torque of the motor generator 34 is transmitted from the second pinion gear 58b through the second sun gear 56 to the second output shaft 26, as shown by the two-dot chain arrow A44. Then, in addition to the torque of the drive source 10, the left second output shaft 26 is superimposed with a torque that further increases the speed of the second output shaft 26 by the motor generator 34, as shown by the arrow C46.

[0093] In this way, when the vehicle 1 is turning right, rotating the motor generator 34 in the forward direction causes a torque that increases the differential to be superimposed on the first output shaft 24 and the second output shaft 26, making it possible to further increase the right turning angle.

[0094] Furthermore, when the vehicle 1 is turning right, rotating the motor generator 34 in the reverse direction causes a torque that reduces the differential to be superimposed on the first output shaft 24 and the second output shaft 26, making it possible to reduce the right turning angle.

[0095] Fig. 10 is a diagram for explaining another example of the torque vectoring function, which illustrates a case in which the motor generator 34 generates torque in the forward rotation direction when the vehicle 1 is turning left.

[0096] When the vehicle 1 is turning left, the relative rotation speed of the first output shaft 24 on the right side is increased by the differential function as shown by the arrow B54. Meanwhile, the relative rotation speed of the second output shaft 26 on the left side is decreased as shown by the arrow B56. In this case, the first pinion gear 58a and the first inner ring portion 150a rotate in the counterclockwise direction as viewed from the motor generator 34 side. The second pinion gear 58b and the second inner ring portion 150b rotate in the clockwise direction as viewed from the motor generator 34 side. When the vehicle 1 is turning left, if the motor generator 34 rotates in the normal direction, the internal gear 100 is provided with a torque from the motor generator 34 that rotates the internal gear 100 in the clockwise direction.

[0097] A torque is applied to the second outer ring portion 152b through the internal gear 100 to rotate the second outer ring portion 152b clockwise. When a torque is applied to the second outer ring portion 152b to further rotate clockwise in a state in which the second inner ring portion 150b rotates clockwise, the second one-way clutch 32b transmits the torque of the motor generator 34 to the second pinion gear 58b as indicated by a two-dot chain arrow A50. As a result, in addition to the clockwise rotation caused by the differential function, the second pinion gear 58b is provided with a torque from the motor generator 34 in a direction to increase the clockwise rotation speed. That is, the second pinion gear 58b is provided with a torque that increases the differential. The torque of the motor generator 34 is transmitted from the second pinion gear 58b through the second sun gear 56 to the second output shaft 26 as indicated by a two-dot chain arrow A54. In addition to the torque of the driving source 10, a torque that further decelerates the second output shaft 26 on the left side is superimposed by the motor generator 34 as shown by an arrow C56.

[0098] Furthermore, a torque that rotates the first outer ring portion 152a in a clockwise direction is applied to the first outer ring portion 152a through the internal gear 100. When a torque that rotates the first outer ring portion 152a in a clockwise direction is applied in a situation in which the first inner ring portion 150a rotates in a counterclockwise direction, the first one-way clutch 32a cuts off the transmission of the torque of the motor generator 34.

[0099] However, since the first pinion gear 58a is meshed with the second pinion gear 58b, the torque of the motor generator 34 is applied to the first pinion gear 58a through the second pinion gear 58b. In addition to the counterclockwise rotation caused by the differential function, the first pinion gear 58a is applied with a torque in a direction that increases the counterclockwise rotation from the motor generator 34 through the second pinion gear 58b. That is, the first pinion gear 58a is applied with a torque that increases the differential. The torque of the motor generator 34 is transmitted from the second pinion gear 58b through the second sun gear 56 to the second output shaft 26, as shown by the two-dot chain arrow A52. Then, in addition to the torque of the drive source 10, the right-side first output shaft 24 is superimposed with a torque that further increases the speed of the first output shaft 24 by the motor generator 34, as shown by the arrow C54.

[0100] In this way, when the vehicle 1 is turning left, rotating the motor generator 34 in the forward direction causes a torque that increases the differential to be superimposed on the first output shaft 24 and the second output shaft 26, making it possible to further increase the left turning angle.

[0101] Furthermore, when the vehicle 1 is turning left, rotating the motor generator 34 in the reverse direction causes a torque that reduces the differential to be superimposed on the first output shaft 24 and the second output shaft 26, making it possible to reduce the left turning angle.

[0102] 11 is a diagram showing an example of a power transmission mechanism 214 of a comparative example. The power transmission mechanism 214 of this comparative example differs from the power transmission mechanism 14 of the present embodiment in that the first one-way clutch 32a and the second one-way clutch 32b are eliminated and a spur gear 232 (spur gear) is included. The spur gear 232 is connected to the first pinion shaft 60a and meshes with the internal gear 100.

[0103] In the power transmission mechanism 214 of the comparative example, when the motor generator 34 is rotated in the normal direction in a situation where the vehicle 1 is turning right, the right turning angle can be increased. However, in the power transmission mechanism 214 of the comparative example, when the motor generator 34 is rotated in the normal direction in a situation where the vehicle 1 is turning left, the left turning angle is decreased. In other words, in the power transmission mechanism 214 of the comparative example, when the vehicle 1 is turning left, in order to increase the left turning angle, it is necessary to rotate the motor generator 34 in the reverse direction. Thus, in the power transmission mechanism 214 of the comparative example, the rotation direction of the motor generator 34 for increasing the absolute value of the turning angle is opposite depending on the turning direction. For this reason, in the power transmission mechanism 214 of the comparative example, the rotation control of the motor generator 34 during traveling becomes complicated.

[0104] In contrast, in the power transmission mechanism 14 of this embodiment, when the motor generator 34 is rotated in the forward direction while turning right, the right turning angle increases, and when the motor generator 34 is rotated in the forward direction while turning left, the left turning angle increases. In other words, in the power transmission mechanism 14 of this embodiment, the absolute value of the turning angle can be increased by rotating the motor generator 34 in the forward direction regardless of the turning direction.

[0105] Therefore, in the power transmission mechanism 14 of this embodiment, it is possible to realize the torque vectoring function while suppressing the control of the motor generator 34 from becoming complicated, as compared to the comparative example described above.

[0106] Also, for example, when the vehicle 1 is passing through a curve, the transmission of torque to the road surface during the curve becomes insufficient, causing the turning angle to become smaller than the steering angle. In such a case, the torque vectoring function is executed in the vehicle 1, and the motor generator 34 is rotated in the forward direction so as to increase the turning angle. Then, on a straight line at the exit of the curve, the function is switched from the torque vectoring function to the motor drive function to assist acceleration.

[0107] In the power transmission mechanism 214 of the comparative example, to increase the turning angle when turning left using the torque vectoring function, the motor generator 34 is rotated in the reverse direction. On the other hand, to assist the acceleration of the vehicle 1 using the motor drive function, the motor generator 34 is rotated in the forward direction. In other words, in the power transmission mechanism 214 of the comparative example, when switching from the torque vectoring function to the motor drive function for turning left, it is necessary to reverse the rotation direction of the motor generator 34. For this reason, in the power transmission mechanism 214 of the comparative example, there is a risk that the operation of switching from the torque vectoring function to the motor drive function at the exit of a curve will become complicated.

[0108] In contrast, in the power transmission mechanism 14 of this embodiment, to increase the turning angle using the torque vectoring function, the motor generator 34 is rotated in the forward direction regardless of the turning direction. Also, when assisting the acceleration of the vehicle 1 using the motor drive function, the motor generator 34 is rotated in the forward direction. In other words, in the power transmission mechanism 14 of this embodiment, when switching from the torque vectoring function to the motor drive function, it is not necessary to reverse the rotation direction of the motor generator 34. Therefore, in the power transmission mechanism 14 of this embodiment, it is possible to prevent the operation of switching from the torque vectoring function to the motor drive function from becoming complicated.

[0109] Furthermore, in the power transmission mechanism 14 of this embodiment, a differential function or a torque vectoring function can be realized by disengaging the electronically controlled clutch 30, and a differential limiting function, a motor drive function, or a regenerative function can be realized by engaging the electronically controlled clutch 30. In the power transmission mechanism 14 of this embodiment, the differential function or the torque vectoring function can be switched between the differential limiting function, the motor drive function, or the regenerative function by the electronically controlled clutch 30. Therefore, in the power transmission mechanism 14 of this embodiment, many functions can be realized with a simple configuration, and each function can be easily switched.

[0110] Although the embodiment of the present invention has been described above with reference to the attached drawings, it goes without saying that the present invention is not limited to such an embodiment. It is clear that a person skilled in the art can think of various modified or altered examples within the scope of the claims, and it is understood that such examples also naturally belong to the technical scope of the present invention.

[0111] For example, the power transmission mechanism 14 may be applied to a rear differential device, a front differential device, or a center differential device. [Explanation of symbols]

[0112] 14, 14a, 14b Power transmission mechanism 20 Input shaft 24 First output shaft 26 Second output shaft 30 Electronically controlled clutch 32a First one-way clutch 32b Second one-way clutch 34 Motor generator 52 Differential case 54 1st sun gear 56 Second sun gear 58a 1st pinion gear 58b 2nd pinion gear 70 First clutch plate 72 No. 2 clutch plate 100 Internal Gear 150a First inner ring 152a First outer ring 150b Second inner ring 152b Second outer ring

Claims

1. a first pinion gear meshed with a first sun gear connected to a first output shaft; a second pinion gear meshed with a second sun gear connected to a second output shaft and meshed with the first pinion gear; a differential case connected to an input shaft and supporting the first pinion gear and the second pinion gear so as to be revolvable around the axes of the first output shaft and the second output shaft and to be rotatable about their own axes; an internal gear rotatable around an axis of the first output shaft and the second output shaft; a motor generator connected to the internal gear; a first one-way clutch having a first inner ring portion that is interlocked with the first pinion gear and a first outer ring portion that is meshed with the internal gear, the first one-way clutch being capable of switching between enabling and disabling transmission of torque in accordance with a rotation direction of the first outer ring portion relative to the first inner ring portion; a second one-way clutch having a second inner ring portion that is interlocked with the second pinion gear and a second outer ring portion that is meshed with the internal gear, the second one-way clutch being capable of switching between enabling and disabling transmission of torque in accordance with a rotation direction of the second outer ring portion relative to the second inner ring portion; A power transmission mechanism comprising:

2. The power transmission mechanism of claim 1, wherein the first one-way clutch and the second one-way clutch are arranged so that the rotation direction of the first outer ring portion relative to the first inner ring portion, through which torque can be transmitted, and the rotation direction of the second outer ring portion relative to the second inner ring portion, through which torque can be transmitted, are the same.

3. 3. The power transmission mechanism according to claim 1 or 2, further comprising an electronically controlled clutch having a first clutch plate and a second clutch plate opposed to each other, the first clutch plate being connected to the differential case and the second clutch plate being connected to the internal gear, the electronically controlled clutch allowing differential movement of the first output shaft and the second output shaft by the first pinion gear and the second pinion gear when the first clutch plate and the second clutch plate are in an open state, and limiting the differential depending on engagement between the first clutch plate and the second clutch plate.

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