JP2009083580A - Hybrid driving device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a hybrid driving device enhancing the regenerative efficiency, reducing the size thereof, and simplifying its mechanism. <P>SOLUTION: The hybrid driving device has a toroidal section 15 which is provided with an input disk 23, an output disk 24 and a power roller 25, and receives the rotation transmitted from a drive source, performs the continuously variable transmission thereof, and outputs it; a first transmission shaft 31 which is arranged between the input disk 23 and the output shaft 33 to transmit the rotation transmitted from the drive source to an output shaft 33; a second transmission shaft 32 which is arranged between the output disk 24 and the output shaft 33 around the first transmission shaft 31, and transmits the rotation output from the toroidal section 15 to the output shaft 33; and an electromotor arranged on the second transmission shaft 32. Since the second transmission shaft 32 surrounding the first transmission shaft 31 and the electromotor are arranged, the electromotor and the output shaft 33 are coupled to each other via the toroidal part 15 during the regenerative mode. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a hybrid drive device.

  2. Description of the Related Art Conventionally, a vehicle equipped with an engine and a drive motor, that is, a hybrid vehicle, can travel by transmitting rotation generated by driving the engine and drive motor to drive wheels. Yes.

  Of the hybrid drive device that is a drive device of the hybrid type vehicle, the drive motor is disposed on the input shaft side to which rotation from the engine is input, and the output shaft side that outputs rotation toward the drive wheels In a parallel hybrid type hybrid drive apparatus in which a transmission is installed in a motor, the torque generated by the drive motor is amplified and output to the output shaft when the hybrid motor is driven by driving the drive motor. However, at the time of regeneration, the rotation transmitted from the drive wheel is transmitted to the drive motor via the transmission, so that the regeneration efficiency is lowered.

  Therefore, a hybrid drive device is provided in which the drive motor and the output shaft are connected without using a transmission during regeneration, and the drive motor and the output shaft are connected through a transmission during motor travel. . In the hybrid drive device, the transmission and the output shaft are connected via a drive motor and also connected via a counter shaft.

  Therefore, loss due to the transmission can be suppressed during regeneration, so that sufficient regenerative energy can be acquired. A particularly large effect can be obtained when the hybrid drive device is mounted on an FR type hybrid vehicle in which the load applied to the rear wheels during braking is small and the control force by the rear wheels cannot be increased.

Further, since the torque can be amplified by the transmission when the motor is running, the drive motor can be reduced in size, and the hybrid drive device can be reduced in size (see, for example, Patent Document 1).
JP 2006-168442 A

  However, in the conventional hybrid drive device, when the motor is running, the drive motor and the output shaft need to be connected via the transmission, so that the rotation that has been shifted in the transmission is transmitted to the output shaft. It is necessary to dispose a counter shaft on. Therefore, the radial dimension of the hybrid drive device is increased, the hybrid drive device is increased in size and the mountability on the hybrid vehicle is reduced, and the number of clutches is increased and the counter shaft is supported. Since a bearing is required, or a gear pair that connects the counter shaft, the input shaft, the output shaft, and the like is required, the mechanism of the hybrid drive device becomes complicated.

  The present invention solves the problems of the conventional hybrid drive device, and provides a hybrid drive device that can increase the regeneration efficiency, can be downsized, and can simplify the mechanism. Objective.

  For this purpose, the hybrid drive device of the present invention includes an input disk, an output disk, and a power roller disposed between the input disk and the output disk, and receives the rotation transmitted from the drive source. A toroidal portion that shifts and outputs in stages, a first transmission shaft that is disposed between the input disk and the output shaft, and that transmits the rotation transmitted from the drive source to the output shaft, and the first transmission A second transmission shaft that surrounds the shaft and is disposed between the output disk and the output shaft and transmits the rotation output from the toroidal portion to the output shaft; and a second transmission shaft disposed on the second transmission shaft An electric machine.

  According to the present invention, the hybrid drive device includes an input disk, an output disk, and a power roller disposed between the input disk and the output disk, and receives the rotation transmitted from the drive source. A toroidal portion that shifts and outputs in stages, a first transmission shaft that is disposed between the input disk and the output shaft, and that transmits the rotation transmitted from the drive source to the output shaft, and the first transmission A second transmission shaft that surrounds the shaft and is disposed between the output disk and the output shaft and transmits the rotation output from the toroidal portion to the output shaft; and a second transmission shaft disposed on the second transmission shaft An electric machine.

  In this case, a first transmission shaft that transmits the rotation transmitted from the drive source to the output shaft, and the first transmission shaft is disposed between the output disk and the output shaft so as to surround the first transmission shaft. The second transmission shaft that transmits the rotation output from the unit to the output shaft, and the electric machine disposed on the second transmission shaft, so that the electric machine and the output shaft are connected to the toroidal unit during regeneration. They can be connected without intervening. Therefore, regeneration efficiency can be increased.

  Further, since no loss occurs due to the toroidal part during regeneration, sufficient regeneration energy can be acquired. In particular, when mounted on an FR type hybrid vehicle in which the load applied to the rear wheels during braking is small and the braking force by the rear wheels cannot be increased, a particularly great effect can be obtained.

  Further, when the hybrid machine is driven by driving the electric machine, the torque can be amplified by the toroidal portion, so that the electric machine can be reduced in size and the hybrid drive device can be reduced in size. it can.

  In addition, it is not necessary to provide a counter shaft in order to transmit the output of the toroidal part to the output shaft when the motor is running. Therefore, the radial dimension of the hybrid drive device can be reduced, and the hybrid drive device can be miniaturized. Therefore, not only can the mountability to the hybrid vehicle be improved, but also the mechanism of the hybrid drive device can be improved. It can be simplified.

  Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. In this case, a hybrid type vehicle as a vehicle will be described.

  FIG. 1 is a conceptual diagram of a hybrid vehicle according to a first embodiment of the present invention.

  In the figure, reference numeral 11 denotes a hybrid drive device, which is connected to an engine (E / G) 13 as a drive source via a clutch CL as an engagement / disengagement device, and is not shown from the engine 13 side. A toroidal portion (variator) 15 as a transmission, a drive motor 51 as an electric machine, a forward / reverse switching device 16 and a drive mode switching device 17 are sequentially connected to the wheel side. The toroidal part 15 includes a half toroidal type and a full toroidal type toroidal part. In the present embodiment, a full toroidal type toroidal part is used.

  The clutch CL is formed by a wet multi-plate clutch, is engaged and disengaged to selectively connect the output shaft 21 of the engine 13 and the input shaft 22 of the hybrid drive device 11, and is transmitted from the engine 13 when engaged. The rotation is input to the hybrid drive device 11.

  In addition, the toroidal portion 15 shifts and outputs the input rotation continuously. For this purpose, the toroidal portion 15 is rotatably disposed and opposed to each other, and is connected to the input shaft 22 and the first transmission shaft 31, and is forward (left in the figure) and rear (in the figure). Two input disks 23 as first disks disposed on the right), and are rotatably disposed between the input disks 23 so as to face the input disks 23, and the second transmission shaft 32. An output disk 24 as a connected second disk, and two rows of power rollers 25 as intermediate rolling elements sandwiched between the input disk 23 and the output disk 24 are provided. The second transmission shaft 32 has a hollow sleeve shape, and is disposed concentrically surrounding the first transmission shaft 31.

  Each of the input disk 23 and the output disk 24 is provided with arc-shaped concave grooves a and b that constitute a part of the opposing circle, and by sandwiching each power roller 25, a double cavity having two cavities is formed. Form. Therefore, the thrust force between the input disks 23 can be canceled out. In this embodiment, since the full toroidal toroidal portion 15 is used, the tilt center of each power roller 25 is placed at the center of each cavity.

  The power roller 25 is inclined by shifting in a direction perpendicular to the central axis of the toroidal portion 15 to change the contact radius between the input disk 23 and the output disk 24. As a result, the toroidal portion 15 continuously shifts the rotation input to the input disk 23 via the input shaft 22 and outputs it from the output disk 24 to the second transmission shaft 32. In the present embodiment, when the rotational speed of the input shaft 22 is the input speed ni and the rotational speed of the second transmission shaft 32 is the output speed no, the ratio of the output speed no to the input speed ni is the speed ratio γ. Is done. When a forward rotation is input to the input disk 23, the output disk 24 is reversed and the reverse rotation is output from the output disk 24. Therefore, the speed ratio γ takes a negative value.

  The drive motor 51 includes a stator 53 attached to a motor case (not shown), and a rotor 52 that is rotatably arranged in the stator 53. A drive current (U-phase, The drive motor 51 can be driven by supplying V-phase and W-phase currents). The motor case is fixed to the case 10 of the hybrid drive device 11, and the rotor 52 is fixed to the second transmission shaft 32.

  The forward / reverse switching device 16 selectively outputs rotations in opposite directions to advance or reverse the hybrid vehicle. For this purpose, the forward / reverse switching device 16 includes a planetary gear unit 54 as a reversing mechanism for reversing rotation and a differential rotating device for reversing, and clutches Cd and Cr, and is used for reversing by the clutches Cd and Cr. The engagement element (friction engagement element) is configured. The planetary gear unit 54 includes elements of a sun gear S, pinions Pa and Pb, a ring gear R, and a carrier CR that rotatably supports the pinions Pa and Pb, and the pinions Pa and Pb constitute an integrated pinion. Then, the sun gear S and the pinion Pa are meshed, and the pinion Pb and the ring gear R are meshed. The sun gear S constitutes a first rotating element, the ring gear R constitutes a second rotating element, and the carrier CR constitutes a third rotating element.

  The sun gear S is connected to the second transmission shaft 32, the ring gear R is connected to the output shaft 33 through the clutch Cd, and the carrier CR is fixed to the case 10. The second transmission shaft 32 is connected to the output shaft 33 via a clutch Cr.

  When the clutch Cd is engaged and the clutch Cr is released in the forward / reverse switching device 16, the reverse rotation input to the sun gear S is reversed while the carrier CR is fixed, and the forward forward direction. Is output to the output shaft 33. When the clutch Cd is released and the clutch Cr is engaged, the rotation output to the second transmission shaft 32 is output as it is to the output shaft 33 as a reverse rotation for reverse travel.

  The drive mode switching device 17 includes a clutch M as an engagement element (friction engagement element) for direct coupling, and the first transmission shaft 31 is connected to the output shaft 33 via the clutch M, and accordingly Thus, the input shaft 22 and the output shaft 33 are directly connected.

  The rotation output to the output shaft 33 is transmitted to a differential device (not shown) as a differential device, and further transmitted to drive wheels (not shown).

  Next, the operation of the hybrid drive device 11 having the above configuration will be described.

  FIG. 2 is a conceptual diagram showing the operation of the hybrid drive device during forward travel in the engine travel mode according to the first embodiment of the present invention, and FIG. 3 is forward travel in the engine travel mode according to the first embodiment of the present invention. FIG. 4 is a conceptual diagram showing the operation of the hybrid drive apparatus during reverse travel of the engine travel mode in the first embodiment of the present invention, and FIG. 5 is a diagram of the present invention. FIG. 6 is a velocity diagram showing the operation of the hybrid drive device during reverse travel of the engine travel mode in the first embodiment. FIG. 6 shows the hybrid drive device during forward travel in the motor travel mode according to the first embodiment of the present invention. FIG. 7 is a velocity diagram showing the operation of the hybrid drive apparatus during forward travel in the motor travel mode according to the first embodiment of the present invention. FIG. 9 is a conceptual diagram showing the operation of the hybrid drive device during reverse travel in the motor travel mode according to the first embodiment of the present invention. FIG. 9 shows the hybrid during reverse travel in the motor travel mode according to the first embodiment of the present invention. It is a velocity diagram which shows operation | movement of a drive device. Each speed diagram represents rotational speeds of the input disk 23, the output disk 24, the sun gear S, the carrier CR, and the ring gear R. 2, 4, 6, and 8, a thick line represents a path through which torque is transmitted, and a thin line represents a path through which torque is not transmitted.

  In the present embodiment, a control unit (not shown) is provided to engage / disengage the clutches CL, Cd, Cr, M, and the clutches CL, Cd, Cr, M are hydraulic pressures (not shown) as actuators. Provide servo. Therefore, in the control unit, a solenoid signal is generated, a solenoid valve is operated by the solenoid signal, and a hydraulic pressure is supplied to each hydraulic servo, whereby each clutch CL, Cd, Cr, M is engaged, and the hydraulic servo Each of the clutches CL, Cd, Cr, and M can be released by draining the hydraulic pressure.

  In this case, a driver as an operator operates a shift lever (not shown) as an operation unit to place the hybrid drive device 11 in a neutral state, drive the engine 13, stop the drive motor 51, and drive the engine travel mode. Traveling in the motor traveling mode in which the engine 13 is stopped and the drive motor 51 is driven, traveling in the forward traveling mode by switching the forward / reverse switching device 16, and traveling in the backward traveling mode. Can do. Further, it is possible to change the gear ratio γ from the underdrive side to the overdrive side in accordance with the driver's depression of the throttle pedal.

  First, when the hybrid drive device 11 is placed in the neutral state, the clutches CL, Cd, Cr, and M are released. Therefore, the rotation from the engine 13 is not transmitted to the output shaft 33.

  Further, during forward travel in the engine travel mode, as shown in FIG. 2, the clutch CL and Cd are engaged and the clutch Cr and M are engaged while the engine 13 is driven and the drive motor 51 is not driven. To be released. In this case, the rotation of the engine 13 is input to the toroidal portion 15 at the input speed ni through the clutch CL. In the toroidal portion 15, the rotation input to the input disk 23 is transmitted to the output disk 24 in the direction of the arrow through the power roller 25, and the speed is changed (decelerated or increased) at a speed ratio γ determined by the inclination angle of the power roller 25. The speed-changed rotation is output to the second transmission shaft 32 as an output speed no and input to the forward / reverse switching device 16 as shown in FIG.

The output speed no of the toroidal portion 15 changes according to the gear ratio γ, and takes a negative value between the maximum value noH in the negative direction and the minimum value noL in the negative direction,
noH ≦ no ≦ noL
become.

In the forward / reverse switching device 16, the rotation of the output speed no output to the second transmission shaft 32 is input to the sun gear S, but the carrier CR is fixed to the case 10 and the clutch Cd is engaged. Therefore, the rotation of the output speed no is reversed in the forward / reverse switching device 16 and is output to the ring gear R and output to the output shaft 33 as the output speed NO. At this time, the output speed NO changes in proportion to the output speed no,
NO = k1 · no
Can be expressed as That is, the output speed NO takes a positive value between the maximum value NOH in the positive direction and the minimum value NOL in the positive direction,
NOL ≦ NO ≦ NOH
k1 · | noL | ≦ NO ≦ k1 · | noH |
become. K1 is a proportionality constant, where the number of teeth of the sun gear S is zs, the number of teeth of the pinion Pa is zpa, the number of teeth of the pinion Pb is zpb, and the number of teeth of the ring gear R is zr. k1 is
k1 = (zs · zpb) / (zpa · zr)
become.

  In this case, the electric machine drive processing means (not shown) of the control unit performs electric machine drive processing, reads the running conditions such as the vehicle speed and the accelerator opening and the remaining battery level, and drives the drive motor 51 according to the running conditions and the remaining battery level. Is driven (assist). In addition, a regenerative processing unit (not shown) of the control unit performs a regenerative process and regenerates electric power in the drive motor 51 when braking the hybrid drive device 11.

  Next, during reverse travel of the engine travel mode, as shown in FIG. 4, the clutch 13 is engaged and the clutch Cd, M is engaged with the engine 13 being driven and the drive motor 51 not being driven. Is released. In this case, the rotation of the engine 13 is input to the toroidal portion 15 at the input speed ni through the clutch CL, as in forward travel. In the toroidal portion 15, the rotation input to the input disk 23 is transmitted to the output disk 24 in the direction of the arrow through the power roller 25, and is shifted (decelerated or increased) at the speed ratio γ of the power roller 25. As shown in FIG. 5, the shifted rotation is output to the second transmission shaft 32 as an output speed no and input to the forward / reverse switching device 16.

The output speed no of the toroidal portion 15 changes according to the gear ratio γ, and takes a negative value between the maximum value noH in the negative direction and the minimum value noL in the negative direction,
noH ≦ no ≦ noL
become.

  In the forward / reverse switching device 16, the rotation of the output speed no output to the second transmission shaft 32 is input to the sun gear S, but the clutch Cd is released and the clutch Cr is engaged. Therefore, the rotation at the output speed no is output to the output shaft 33 as it is.

  In this case as well, the control unit reads the running conditions such as the vehicle speed and the accelerator opening and the remaining battery level, and drives the drive motor 51 in accordance with the running conditions and the remaining battery level. The controller regenerates power in the drive motor 51 when braking the hybrid drive device 11.

  Next, during forward travel in the motor travel mode, as shown in FIG. 6, the clutch M is engaged and the clutches CL, Cd, Cr are released. In this case, the rotation of the drive motor 51 is input to the toroidal portion 15 through the second transmission shaft 32 at the input speed ni. In the toroidal portion 15, the rotation input to the output disk 24 is transmitted to the input disk 23 in the direction of the arrow through the power roller 25, and the speed is changed (decelerated or increased) at a speed ratio γ determined by the inclination angle of the power roller 25. As shown in FIG. 7, the rotated rotation is output to the first transmission shaft 31 as the output speed no, and is output to the output shaft 33 as it is.

  Next, during reverse travel of the motor travel mode, as shown in FIG. 8, the clutch Cr is engaged and the clutches CL, Cd, M are released. In this case, since the clutch Cr is engaged, the rotation of the drive motor 51 is directly output to the output shaft 33 via the second transmission shaft 32 as shown in FIG.

  The forward travel in the motor travel mode can be performed by engaging the clutch Cd and releasing the clutches CL, Cr, and M. In that case, the rotation of the drive motor 51 is input to the forward / reverse switching device 16 through the second transmission shaft 32 at the input speed ni. In the forward / reverse switching device 16, the rotation of the input speed ni is input to the sun gear S. However, since the carrier CR is fixed to the case 10 and the clutch Cd is engaged, the rotation of the input speed ni is Inverted in the forward / reverse switching device 16 is output to the ring gear R and output to the output shaft 33 as the output speed NO.

  Thus, in the present embodiment, the toroidal portion 15, the drive motor 51, the forward / reverse switching device 16 and the drive mode switching device 17 are connected in order from the engine 13 to the drive wheel, and the input disk 23 and the output shaft 33 are connected. Are coupled via the clutch M, the drive motor 51 and the output shaft 33 can be coupled via the toroidal portion 15 during regeneration. Therefore, during regeneration, the rotation of the drive wheel is transmitted to the drive motor 51 without passing through the toroidal portion 15, so that the regeneration efficiency can be increased.

  And since the loss by the toroidal part 15 does not occur at the time of regeneration, sufficient regenerative energy can be acquired. In particular, when mounted on an FR type hybrid vehicle in which the load applied to the rear wheels during braking is small and the braking force by the rear wheels cannot be increased, a particularly great effect can be obtained.

  Further, since the torque can be amplified by the toroidal portion 15 during motor running, the drive motor 51 can be reduced in size, and the hybrid drive device 11 can be reduced in size.

  In addition, when the motor is running, the toroidal portion 15 and the output shaft 33 can be connected by engaging the clutch M, so a counter shaft is provided to transmit the output of the toroidal portion 15 to the output shaft 33. There is no need to do. Therefore, the radial dimension of the hybrid drive device 11 can be reduced, and the hybrid drive device 11 can be reduced in size, so that not only the mountability to the hybrid vehicle can be improved, but also the hybrid drive device 11. This mechanism can be simplified.

  Moreover, in the toroidal part 15, the rotation direction of the input disk 23 and the output disk 24 is always constant, and it is not necessary to rotate in the reverse direction, so that the position of the power roller 25 can be stabilized.

  Next, a second embodiment of the present invention will be described. In addition, about what has the same structure as 1st Embodiment, the description is given by providing the same code | symbol, and the effect of the same embodiment is used about the effect of the invention by having the same structure.

  FIG. 10 is a conceptual diagram of a hybrid vehicle according to the second embodiment of the present invention.

  In the figure, 11 is a hybrid drive device, which is connected to an engine (E / G) 13 via a clutch CL as an engagement / disengagement device, from the engine 13 side to the drive wheel side (not shown), A toroidal portion (variator) 15 as a transmission, a drive motor 51 as an electric machine, and a drive mode switching device 55 are sequentially connected.

  The drive motor 51 includes a stator 53 attached to a motor case (not shown), and a rotor 52 that is rotatably arranged in the stator 53. A drive current (U-phase, The drive motor 51 can be driven by supplying V-phase and W-phase currents). The motor case is fixed to the case 10 of the hybrid drive device 11, and the rotor 52 is fixed to the second transmission shaft 32, connected to the toroidal portion 15, and switched to the drive mode via the third transmission shaft 34. It is connected with the device 55.

  The drive mode switching device 55 includes a planetary gear unit 56 as a differential rotation device for low mode as a first mode, a planetary gear unit 57 as a differential rotation device for high mode as a second mode, and A drive mode unit 58 is provided. The drive mode unit 58 includes a low mode clutch L as a first clutch and a high mode clutch H as a second clutch. A friction engagement device).

  The planetary gear unit 56 includes elements of a sun gear S1, a pinion P1, a ring gear R1, and a carrier CR1 that rotatably supports the pinion P1. Then, the sun gear S1 and the pinion P1 are meshed, and the pinion P1 and the ring gear R1 are meshed. The sun gear S1 constitutes a first rotating element, the ring gear R1 constitutes a second rotating element, and the carrier CR1 constitutes a third rotating element.

  The sun gear S1 is connected to the second and third transmission shafts 32, 34, the ring gear R1 is connected to the first transmission shaft 31, and the carrier CR1 is connected to the drive mode unit 58 via the fourth transmission shaft 35. Connected. The fourth transmission shaft 35 is disposed coaxially with the first transmission shaft 31.

  The planetary gear unit 57 includes each element of a sun gear S2, pinions Pa2, Pb2, a ring gear R2, and a carrier CR2 that rotatably supports the pinions Pa2, Pb2. The Then, the sun gear S2 and the pinion Pb2 are meshed, and the pinion Pa2 and the ring gear R2 are meshed. The sun gear S2 constitutes a first rotating element, the ring gear R2 constitutes a second rotating element, and the carrier CR2 constitutes a third rotating element.

  The sun gear S2 is connected to the output shaft 33 via the clutch H, the ring gear R2 is connected to the third transmission shaft 34, and the carrier CR2 is fixed to the case 10. The fourth transmission shaft 35 is connected to the output shaft 33 via the clutch L.

  Next, the operation of the hybrid drive device 11 having the above configuration will be described.

  FIG. 11 is a conceptual diagram showing the operation of the hybrid drive device during forward travel in the engine travel / low mode in the second embodiment of the present invention, and FIG. 12 is the engine travel / low in the second embodiment of the present invention. FIG. 13 is a conceptual diagram showing the operation of the hybrid drive device during reverse travel of the engine travel / low mode according to the second embodiment of the present invention. FIG. 14 is a velocity diagram showing the operation of the hybrid drive device during reverse running of the engine running / low mode according to the second embodiment of the present invention, and FIG. 15 shows the engine running / running according to the second embodiment of the present invention. FIG. 16 is a conceptual diagram showing the operation of the hybrid drive device during forward travel in the high mode, and FIG. 16 is the forward travel in the engine travel / high mode in the second embodiment of the present invention. FIG. 17 is a conceptual diagram showing the operation of the hybrid drive apparatus during motor travel / low mode forward / reverse travel in the second embodiment of the present invention. 18 is a velocity diagram showing the operation of the hybrid drive device during motor travel / low mode forward / reverse travel in the second embodiment of the present invention, and FIG. 19 shows motor travel in the second embodiment of the present invention. Conceptual diagram illustrating the operation of the hybrid drive device during forward travel in the high mode, and FIG. 20 is a velocity diagram illustrating the operation of the hybrid drive device during forward travel in the motor travel and high mode according to the second embodiment of the present invention. It is. Each speed diagram represents the rotational speeds of the ring gear R1, the carrier CR1, the sun gear S2, the carrier CR2, the sun gear S1, and the ring gear R2. In FIGS. 11, 13, 15, 17 and 19, the thick line represents a path through which torque is transmitted, and the thin line represents a path through which torque is not transmitted.

  In the present embodiment, the clutch CL as the engagement / disengagement device, the low mode clutch L as the first clutch, and the high mode clutch H as the second clutch are not illustrated. A control unit is provided, and each of the clutches CL, L, and H includes a hydraulic servo (not shown) as an actuator. Therefore, in the control unit, a solenoid signal is generated, a solenoid valve is operated by the solenoid signal, and a hydraulic pressure is supplied to each hydraulic servo, whereby each clutch CL, L, H is engaged, The clutches CL, L, and H can be released by draining.

  Further, in the engine travel mode and the forward travel of the engine travel / low mode indicating the low mode, as shown in FIG. 11, in the reverse travel of the engine travel / low mode, FIG. As shown, the engine 13 as a drive source is driven, the clutch CL, L is engaged, and the clutch H is released while the drive motor 51 as an electric machine is not driven.

  As shown in FIG. 11, the rotation of the engine 13 is input to the ring gear R <b> 1 via the first transmission shaft 31. Then, the rotation of the carrier CR1 is output to the fourth transmission shaft 35 as the output speed NO and output to the output shaft 33 via the clutch L.

At this time, the output speed NO takes positive and negative values between the maximum value NOH in the positive direction and the minimum value NOL in the positive direction,
NOL ≦ NO ≦ NOH
become.

And the output speed NO is as shown in FIG.
0 <NO ≦ NOH
As shown in FIG. 14, when traveling backward,
NOL ≦ NO <0
Take the negative value of.

  In addition, as shown in FIG. 12, during forward travel, as the torque is output from the carrier CR1 in the direction of the arrow, as shown in FIG. 11, the sun gear S1, the second transmission shaft 32, the second The power is transmitted to the ring gear R1 through the output disk 24 as the first disk, the power roller 25 as the intermediate rolling element, the input disk 23 as the first disk, and the first transmission shaft 31 to perform power circulation. Further, as shown in FIG. 14, during reverse travel, as torque is input to the carrier CR1 in the direction of the arrow, as shown in FIG. 13, the ring gear R1, the first transmission shaft 31, and the input disk 23, torque is transmitted to the sun gear S1 through the power roller 25, the output disk 24, and the second transmission shaft 32, and torque circulation is performed.

  And the said control part reads driving conditions, such as a vehicle speed and an accelerator opening degree, and battery residual amount, and drives the drive motor 51 according to driving conditions and battery residual amount. The controller regenerates power in the drive motor 51 when braking the hybrid drive device 11.

  Next, in the engine traveling mode and the engine traveling / high mode forward traveling representing the high mode, as shown in FIG. 15, the engine 13 is driven and the driving motor 51 is not driven. Thus, the clutches CL and H are engaged, and the clutch L is released.

  In this case, the rotation of the engine 13 is input to the toroidal portion 15 at the input speed ni through the clutch CL. In the toroidal portion 15, the rotation input to the input disk 23 is transmitted to the output disk 24 in the direction of the arrow through the power roller 25, and the speed is changed (decelerated or increased) at a speed ratio γ determined by the inclination angle of the power roller 25. The speed-changed rotation is output to the second transmission shaft 32 as an output speed no and is input to the ring gear R2 of the planetary gear unit 57 via the third transmission shaft 34.

The output speed no of the toroidal portion 15 changes according to the transmission gear ratio γ, and as shown in FIG. 16, a negative value between a maximum value noH in the negative direction and a minimum value noL in the negative direction is obtained. Pick,
noH ≦ no ≦ noL
become.

In the planetary gear unit 57, the rotation of the output speed no is input to the ring gear R2. However, since the carrier CR2 is fixed to the case 10 and the clutch H is engaged, the rotation of the output speed no Inverted in the planetary gear unit 57, output to the sun gear S2, and output to the output shaft 33 as the output speed NO. At this time, the output speed NO changes in proportion to the output speed no, and takes a positive value between the maximum value NOH in the positive direction and the minimum value NOL in the positive direction.
NOL ≦ NO ≦ NOH
become.

  In this case, the control unit reads the running conditions such as the vehicle speed and the accelerator opening and the remaining battery level, and drives the drive motor 51 according to the running conditions and the remaining battery level. The controller regenerates power in the drive motor 51 when braking the hybrid drive device 11.

  Next, in the motor travel mode and during the forward travel and the reverse travel in the motor travel / low mode indicating the low mode, as shown in FIG. 17, the engine 13 is stopped and the drive motor is stopped. In a state where 51 is driven, the clutch L is engaged, and the clutches CL and H are released.

  In this case, the rotation of the drive motor 51 is input to the toroidal portion 15 through the second transmission shaft 32 at the input speed ni and input to the sun gear S1 through the second transmission shaft 32 at the input speed ni. The In the toroidal portion 15, the rotation input to the output disk 24 is transmitted to the input disk 23 in the direction of the arrow through the power roller 25, and a speed change (deceleration or acceleration) is performed at a speed ratio γ determined by the inclination angle of the power roller 25. ), And the speed-changed rotation is output to the first transmission shaft 31 as the output speed no and input to the ring gear R1 of the planetary gear unit 56 via the first transmission shaft 31, but the clutch H is released. Since the clutch L is engaged, the power circulation is the same as in the engine running mode.

The output speed no of the toroidal portion 15 changes according to the speed ratio γ, and as shown in FIG. 18, a negative value between the maximum value noH in the positive direction and the minimum value noL in the positive direction. Take the value,
noL ≦ no ≦ noH
become.

  As a result, the rotation of the carrier CR1 is output as the output speed NO to the fourth transmission shaft 35 and output to the output shaft 33 via the clutch L.

At this time, the output speed NO changes in proportion to the output speed no, and takes positive and negative values between the maximum value NOH in the positive direction and the minimum value NOL in the positive direction,
NOL ≦ NO ≦ NOH
become.

And the output speed NO is the forward running,
0 <NO ≦ NOH
Take the positive value of
NOL ≦ NO <0
Take the negative value of.

  Further, in the motor travel mode and the motor travel indicating the high mode and the forward travel in the high mode, the engine 13 is stopped and the drive motor 51 is driven as shown in FIG. In this state, the clutch H is engaged, and the clutches CL and L are released.

  In this case, the rotation of the drive motor 51 is input to the ring gear R2 of the planetary gear unit 57 through the third transmission shaft 34 at the input speed ni, but the carrier CR2 is fixed to the case 10 and the clutch H is engaged. Therefore, the rotation of the input speed ni is reversed in the planetary gear unit 57 and output to the sun gear S2, and is output to the output shaft 33 as the output speed NO. At this time, the output speed NO takes a positive value proportional to the input speed ni.

  Thus, in the present embodiment, the rotation of the motor is transmitted to the output shaft in the planetary gear unit 57 while reversing the direction of rotation.

  The present invention is not limited to the above embodiments, and various modifications can be made based on the gist of the present invention, and they are not excluded from the scope of the present invention.

It is a conceptual diagram of the hybrid type vehicle in the 1st Embodiment of this invention. It is a conceptual diagram which shows operation | movement of the hybrid drive device at the time of advance driving | running | working in the engine driving mode in the 1st Embodiment of this invention. It is a velocity diagram which shows operation | movement of the hybrid drive device at the time of advance driving | running | working in the engine driving mode in the 1st Embodiment of this invention. It is a conceptual diagram which shows operation | movement of the hybrid drive device at the time of reverse drive of the engine drive mode in the 1st Embodiment of this invention. It is a speed diagram which shows operation | movement of the hybrid drive device at the time of reverse driving | running | working of the engine driving mode in the 1st Embodiment of this invention. It is a conceptual diagram which shows operation | movement of the hybrid drive device at the time of advance driving | running | working in the motor driving mode in the 1st Embodiment of this invention. It is a velocity diagram which shows operation | movement of the hybrid drive device at the time of advance driving | running | working in the motor driving mode in the 1st Embodiment of this invention. It is a conceptual diagram which shows operation | movement of the hybrid drive device at the time of reverse drive of the motor drive mode in the 1st Embodiment of this invention. It is a velocity diagram which shows operation | movement of the hybrid drive device at the time of reverse drive of the motor drive mode in the 1st Embodiment of this invention. It is a conceptual diagram of the hybrid type vehicle in the 2nd Embodiment of this invention. It is a conceptual diagram which shows operation | movement of the hybrid drive device at the time of engine driving | running | working / low mode advance driving | running | working in the 2nd Embodiment of this invention. It is a velocity diagram which shows the operation | movement of the hybrid drive device at the time of the advance driving | running | working of engine driving | running | working / low mode in the 2nd Embodiment of this invention. It is a conceptual diagram which shows operation | movement of the hybrid drive device at the time of reverse drive of engine driving | running | working and low mode in the 2nd Embodiment of this invention. It is a velocity diagram which shows the operation | movement of the hybrid drive device at the time of reverse drive of engine driving | running | working / low mode in the 2nd Embodiment of this invention. It is a conceptual diagram which shows the operation | movement of the hybrid drive device at the time of the advance driving | running | working of engine driving | running | working / high mode in the 2nd Embodiment of this invention. It is a velocity diagram which shows operation | movement of the hybrid drive device at the time of engine driving | running | working and the high mode forward drive in the 2nd Embodiment of this invention. It is a conceptual diagram which shows operation | movement of the hybrid drive device at the time of motor driving | running | working / low mode advance / reverse drive in the 2nd Embodiment of this invention. It is a velocity diagram which shows operation | movement of the hybrid drive device at the time of motor driving | running | working / low mode advance / reverse drive in the 2nd Embodiment of this invention. It is a conceptual diagram which shows operation | movement of the hybrid drive device at the time of the forward driving | running | working of motor driving | running | working and high mode in the 2nd Embodiment of this invention. It is a velocity diagram which shows the operation | movement of the hybrid drive device at the time of motor driving | running | working and the high mode forward drive in the 2nd Embodiment of this invention.

Explanation of symbols

DESCRIPTION OF SYMBOLS 11 Hybrid drive device 13 Engine 15 Toroidal part 21, 33 Output shaft 23 Input disk 24 Output disk 25 Power rollers 31, 32 First and second transmission shaft 51 Drive motor 54, 56, 57 Planetary gear unit

Claims (5)

  An input disk, an output disk, and a toroidal portion that includes a power roller disposed between the input disk and the output disk, receives rotation transmitted from a drive source, and outputs a continuously variable speed; and A first transmission shaft disposed between the input disk and the output shaft and transmitting the rotation transmitted from the drive source to the output shaft, and surrounding the first transmission shaft, the output disk and the output shaft And a second transmission shaft for transmitting the rotation output from the toroidal portion to the output shaft, and an electric machine disposed on the second transmission shaft. Hybrid drive device.   The hybrid drive device according to claim 1, wherein the rotation generated by driving the electric machine is transmitted to an output shaft through the toroidal portion.   The hybrid drive device according to claim 1, wherein during regeneration, rotation from the output shaft is transmitted to the electric machine without passing through the toroidal portion.   The hybrid drive device according to claim 1, further comprising a differential rotating device disposed between the first transmission shaft and the output shaft.   The hybrid drive device according to any one of claims 1 to 4, further comprising a reversing mechanism that is disposed between the electric machine and the output shaft and selectively reverses the transmitted rotation.

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