JP2005119573A - Hybrid vehicle - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a hybrid vehicle which has a power distribution unit connected to an engine and a motor and miniaturizes an electric motor to realize higher output of the engine. <P>SOLUTION: A first motor generator MG1 is connected to a power distribution unit (a second planetary gear device 14) via a reduction gear (a first planetary gear device 12), and the torque generated by the first motor generator MG1 is reduced compared with the power of an engine 6 connected to the power distribution unit in comparison with the case not provided with the reduction gear, and the first motor generator MG1 can be miniaturized. Therefore, even when the engine output is increased, the first motor generator MG1 can be relatively miniaturized. In other words, the first motor generator MG1 can be miniaturized to realize higher output of the engine 6, and favorably mounted on a vehicle. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

  The present invention relates to a hybrid vehicle including a power distribution unit connected to, for example, an engine and a motor generator, and more particularly to a technique that enables a motor generator to be miniaturized.

  For example, as in the hybrid vehicle described in Patent Document 1 or Non-Patent Document 1, the engine, two motor generators, and a power distribution unit that distributes engine power to one motor generator and an output member, The electric power generated by one of the motor generators is supplied to the other motor generator connected to the output member, so that the driving force of the other motor generator is applied to the output member together with the engine power. A hybrid vehicle having a configured power transmission device is known. Usually, in the power transmission device provided in the hybrid vehicle, the power distribution unit is composed of a set of planetary gear devices, and the three rotating elements of the planetary gear device are respectively an engine, one motor generator, and the other. The motor generator is connected to an output member to which the motor generator is connected. Also in such a hybrid vehicle, it is desired to cope with various types of engines or higher output of the engine, similarly to a vehicle using only the engine as a driving force source.

JP 2002-281607 A "Prius New Model Manual" issued on October 14, 1997, Service Department, Toyota Motor Corporation

  However, one of the three rotating elements of the planetary gear device has a rotational driving torque which is controlled by controlling the amount of power generated by one motor generator connected to the one rotating element. Since the force is changed at any time and the rotational speed is controlled, the one motor generator is used in order to cope with the higher output of the engine connected to the other of the three rotating elements. There is a possibility that mounting the power transmission device on a vehicle including a response to various engines may be disadvantageous. Such a situation was the same when an electric motor was used instead of the motor generator.

  The present invention has been made against the background of the above circumstances, and the object of the present invention is to cope with higher engine output in a hybrid vehicle including a power distribution unit coupled to an engine and an electric motor. An object of the present invention is to provide a hybrid vehicle that can reduce the size of an electric motor.

  A gist of the first invention for achieving the object is a hybrid vehicle including a power distribution unit coupled to an engine and an electric motor, wherein the electric motor is connected to the power distribution unit via a reduction gear. It is characterized by that.

  According to a second aspect of the present invention, in the hybrid vehicle of the first aspect, the electric motor is operatively connected to the power distribution unit via a first planetary gear unit, and the power distribution unit is configured by a second planetary gear unit. It is.

  A third invention is a hybrid vehicle according to the second invention, wherein the planetary gear of the first planetary gear device has a larger diameter than the planetary gear of the second planetary gear device, and is a stepped pinion integrated with each other. is there.

  According to a fourth aspect of the present invention, in the hybrid vehicle according to any one of the first to third aspects, the speed reducer and the power distribution unit are arranged in order from one end side to the other end side on the alignment chart. , A second rotating element, a third rotating element, and a fourth rotating element, the first rotating element is connected to the electric motor, the third rotating element is connected to the engine, and the fourth rotating element is an output member. It is connected to.

  According to a fifth aspect of the present invention, in the hybrid vehicle of the fourth aspect, the first sun gear of the first planetary gear device constitutes the first rotating element, and the second sun gear of the second planetary gear device comprises the second rotating element. And the first carrier of the first planetary gear device and the second carrier of the second planetary gear device are interconnected to form the third rotating element, and the second ring gear of the second planetary gear device is The fourth rotating element is configured.

  According to a sixth aspect of the invention, in the hybrid vehicle of the fourth aspect of the invention, the first sun gear of the first planetary gear unit constitutes the first rotating element, and the first carrier of the first planetary gear unit and the second planetary gear unit. And the second ring gear of the first planetary gear unit and the second carrier of the second planetary gear unit are coupled to each other to form the third rotation element. The second ring gear of the second planetary gear set constitutes the fourth rotating element.

  A seventh invention is the hybrid vehicle of the fourth invention, wherein the first ring gear of the first planetary gear device and the second ring gear of the second planetary gear device are connected to each other to constitute the first rotating element, The first carrier of the first planetary gear device and the second carrier of the second planetary gear device are connected to each other to form the second rotating element, and the first sun gear of the first planetary gear device is the third rotation. The second sun gear of the second planetary gear set constitutes the fourth rotating element.

  An eighth invention is the hybrid vehicle of the fourth invention, wherein the first sun gear of the first planetary gear device and the second sun gear of the second planetary gear device are connected to each other to constitute the first rotating element, The first carrier of the first planetary gear device and the second carrier of the second planetary gear device are connected to each other to form the second rotating element, and the first ring gear of the first planetary gear device is the third ring gear. A rotating element is configured, and the second ring gear of the second planetary gear device configures the fourth rotating element.

  According to a ninth invention, in the hybrid vehicle of the fourth invention, the first sun gear of the first planetary gear device constitutes the first rotating element, and the first carrier and the second planetary gear device of the first planetary gear device. The second sun gears are connected to each other to form the second rotating element, and the second carrier of the second planetary gear unit forms the third rotating element, and the first ring gear of the first planetary gear unit and The second ring gears of the second planetary gear device are connected to each other to constitute the fourth rotating element.

  In the hybrid vehicle according to any one of the first to ninth inventions, since the electric motor is connected to the power distribution unit via a reduction gear, the electric motor is connected to the power distribution unit without passing through the reduction gear. In other words, compared with the case where no reduction gear is provided, the torque of the motor required for the power of the engine connected to the power distribution unit, that is, the torque generated by the motor can be small. It can be configured in a small size. Therefore, even if the engine output increases, the electric motor can be configured relatively small. That is, since the electric motor can be reduced in size in order to cope with the higher output of the engine, the mounting on the vehicle is advantageous.

  Further, in the second invention, the electric motor is further operatively connected to the power distribution unit composed of the second planetary gear device via the first planetary gear device, so that the entire device is simple and compact. Composed. Further, since two sets of planetary gear units are used, a gear ratio に corresponding to the gear ratio ρ of one set of planetary gear units that can be set as two sets of planetary gear units as a whole compared to the case of using one set of planetary gear units. By setting the gear ratio ρ of each planetary gear unit, the torque generated by the electric motor can be set to be smaller.

  In the third invention, the planetary gear of the first planetary gear device has a larger diameter than the planetary gear of the second planetary gear device and is a stepped pinion integrated with each other. The whole is further reduced in size.

  According to the fourth aspect of the present invention, when the relative rotational speed of the first rotational element with respect to the rotational speed of the third rotational element is changed according to the rotational speed of the electric motor, the rotational speed of the third rotational element of the fourth rotational element is changed. The relative rotational speed with respect to is changed. In addition, since the rotation speed of the electric motor is continuously changed, the relative rotation speed of the output member with respect to the engine rotation speed is continuously changed. Therefore, the reduction gear and the power distribution unit are continuously variable transmissions. As a function. Further, since the electric motor is connected to the first rotating element, the first rotating element, the second rotating element, the third rotating element, the second rotating element, the second rotating element, the second rotating element, the second rotating element, and the like. Since the interval between the four rotating elements can be set, the electric motor can be reduced in size.

  Further, in the fifth aspect of the invention, the use of two sets of planetary gear units increases the range of gear ratios that can be set for the two sets of planetary gear units as a whole compared to the case of using one set of planetary gear units. Since a gear ratio ρ which is appropriate as a set of planetary gear devices, for example, a gear ratio 小 さ な with a smaller value can be set in a range of about “0.3 to 0.6”, the torque of the electric motor can be further increased. It can be set to be small. Further, since the planetary gear of the first planetary gear device has a larger diameter than the planetary gear of the second planetary gear device and can be integrated with each other, the entire device can be further reduced in size. .

  Further, in any of the sixth to ninth inventions, two sets of planetary gear devices are set as a whole by using two sets of planetary gear devices as compared to the case of using one set of planetary gear devices. The width of the gear ratio can be increased, and a gear ratio ρ which is appropriate as a set of planetary gear units, for example, a gear ratio ratio having a smaller value in the range of about “0.3 to 0.6” can be set. Therefore, it is possible to set the torque of the electric motor to be smaller. Further, the relative rotational speed δ of the first planetary gear constituting the first planetary gear device with respect to the first carrier or the relative rotational speed δ of the second planetary gear constituting the second planetary gear device with respect to the second carrier is reduced, The durability of the first planetary gear device or the second planetary gear device is improved. Particularly, in the sixth or seventh invention, the relative rotational speed δ is reduced as compared with the eighth or ninth invention.

  Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.

  FIG. 1 is a schematic diagram for explaining a main part of the configuration of a power transmission device 8 suitably used for a hybrid vehicle to which a power distribution device 10 according to an embodiment of the present invention is applied. 1 is a skeleton diagram of a dispensing device 10. FIG. In FIG. 1, the power transmission device 8 includes an input shaft 16 as an input member disposed on a common axis, and a first planetary gear device 12 and a second planetary gear device 14 connected to the input shaft 16. A power distribution device 10 configured as a main body, and an output gear 18 as an output member connected to the power distribution device 10 are provided. In addition, since the power transmission device 8 is configured symmetrically with respect to its axis, the lower side is omitted in the portion representing the power transmission device 8 of FIG. The same applies to each of the following embodiments. This power transmission device 8 is provided between the engine 6 as a driving force source and a pair of driving wheels 24, and is input via, for example, a damper (vibration damping device) (not shown) for suppressing rotational fluctuation and torque fluctuation. The output of the engine 6 is transmitted to the pair of drive wheels 24 through the reduction gear 20 and the pair of axles 22 which are constituted by a counter shaft, a differential gear device (final reduction gear) and the like.

  The power transmission device 8 has a function of mechanically synthesizing or distributing the power of the engine 6 input to the input shaft 16. For example, the power of the engine 6 is distributed to the power distribution device 10 by the power distribution device 10. As a motor and a generator connected to the output gear 18 and the power of the engine 6 distributed to the output gear 18 and the first motor generator MG1 functioning as a motor and a generator. The driving force by the functioning second motor generator MG2 is combined. The driving force of the second motor generator MG2 is that the electric power generated when the first motor generator MG1 is driven by the power of the engine 6 distributed to the first motor generator MG1 is supplied to the second motor via the inverter 26. This is generated when the second motor generator MG2 is driven by the generated electric power transmitted to the generator MG2. Such control is controlled by, for example, an electronic control device (not shown) provided in the hybrid vehicle, and by controlling the power generation state by the first motor generator MG1, the driving state by the second motor generator MG2, and the like. The power transmission device 8 has a function as a continuously variable transmission. Further, the control by the electronic control device is an aspect in normal traveling of the hybrid vehicle, and there are various aspects according to the traveling state of the hybrid vehicle. For example, when the vehicle is decelerating, the second motor generator MG2 is caused to function as a generator and so-called regenerative braking is performed in which power is charged to the battery 28 via the inverter 26, or second power is charged by the power charged in the battery 28. For example, control for traveling with only the driving force generated by driving motor generator MG2 is executed.

The first planetary gear device 12 constituting the power distribution device 10 functions as a speed reducer, and the second planetary gear device 14 constitutes a power distribution unit, each of which is a single pinion type planetary gear. It consists of devices. The first planetary gear unit 12 includes a first sun gear S1, a first planetary gear P1, a first carrier CA1 that supports the first planetary gear P1 so as to rotate and revolve, and a first sun gear via the first planetary gear P1. and a first ring gear R1 meshing with the S1, for example has a gear ratio [rho ₁ of about "0.3". The second planetary gear unit 14 includes a second sun gear S2 via a second sun gear S2, a second planetary gear P2, a second carrier CA2 that supports the second planetary gear P2 so as to rotate and revolve, and a second planetary gear P2. and a second ring gear R2 meshing with, for example, has a "0.53" about a gear ratio [rho _2. If the number of teeth of the first sun gear S1 is Z _S1 , the number of teeth of the first ring gear R1 is Z _R1 , the number of teeth of the second sun gear S2 is Z _S2 , and the number of teeth of the second ring gear R2 is Z _R2 , the gear ratio ρ ₁ is Z _S1 / Z _R1 , and the gear ratio ρ ₂ is Z _S2 / Z _R2 . In the present embodiment, the first planetary gear P1 has a larger diameter than the second planetary gear P2, and the first planetary gear P1 and the second planetary gear P2 are stepped pinions integrated with each other. It is a certain stepped pinion SP. Therefore, as described above, the first planetary gear device 12 has a function as a speed reducer. The first carrier CA1 and the second carrier CA2 are integral, and the first ring gear R1 and the second sun gear S2 are omitted.

  In the power distribution device 10, the first sun gear S 1 is operatively connected to the first motor generator MG 1, and the first carrier CA 1 and the second carrier CA 2 that are integral are operated to the engine 6 via the input shaft 16. The second ring gear R2 is connected to an output gear 18 as an output member. That is, the first motor generator MG1 is operatively connected to the second planetary gear unit 14 via the first planetary gear unit 12, and the second planetary gear unit 14 transmits the power of the engine 6 to the output gear 18. It has a function of distributing to the first motor generator MG1.

FIG. 2 is a collinear diagram that can represent the relative relationship between the rotational speeds of the rotating elements on the straight line in the power distribution device 10. The collinear chart of FIG. 2 is a two-dimensional coordinate indicating the relationship of the gear ratio ρ of each planetary gear device 12, 14 in the horizontal axis X direction and the relative rotational speed in the vertical axis Y direction. X1 indicates the engine rotational speed N _E which is operatively connected to the rotational speed of "1.0" that is, the input shaft 16. The four vertical lines Y1 to Y4 indicate, from the left, the first sun gear S1 corresponding to the first rotation element RE1, the second sun gear S2 corresponding to the second rotation element RE2, and the third rotation element RE3. The corresponding integrated first carrier CA1 and second carrier CA2 represent the second ring gear R2 corresponding to the fourth rotating element RE4, respectively, and their intervals are the gear ratios ρ ₁ , ρ of the planetary gear units 12, 14. It is determined according to ₂ . When the distance between the sun gear and the carrier between the ordinates of the nomograph is set to an interval corresponding to “1”, the interval between the carrier and the ring gear is set to an interval corresponding to ρ. In FIG. The interval between them is set based on the above relationship. As described above, the power distribution device 10 includes the first sun gear S1 of the first planetary gear device 12, the first carrier CA1, the first ring gear R1, the second sun gear S2 of the second planetary gear device 14, and the second carrier. CA2 and a part of second ring gear R2 are singly or connected to each other, so that in the collinear diagram, four first rotation elements RE1 and first in order from one (left) end to the other (right) end. A two-rotation element RE2, a third rotation element RE3, and a fourth rotation element RE4 are configured.

  If expressed using the collinear diagram, in the power distribution device 10 of the present embodiment, the first rotating element RE1 (S1) is operatively connected to the first motor generator MG1, and the third rotating element RE3. (CA1, CA2) are operatively connected to the engine 6 via the input shaft 16, and the fourth rotating element RE4 (R2) is connected to an output gear 18 as an output member.

As apparent from the collinear diagram of FIG. 2, the rotational speed of the fourth rotating element RE4 indicated by a circle (the rotational speed here is the horizontal axis X1 or the input shaft 16 corresponding to the third rotating element RE3 indicated by a black circle). operatively linked are the relative rotational speed with respect to the engine rotational speed N _E. hereinafter, the same in the rotational speed of the rotating element) is varied in accordance with the rotational speed of the first rotary element RE1 shown in mark △. In other words, the relative rotational speed is continuously changed with respect to the engine rotational speed N _E of the output gear 18 corresponding to the fourth rotating element RE4 in accordance with the rotational speed of the first motor generator MG1 corresponding to the first rotary element RE1 . Moreover, since the rotation speed of the first motor generator MG1 is continuously changed, the gear ratio is changed steplessly. For example, when the rotational speed of the first rotating element RE1 and zero, the rotational speed of the fourth rotating element RE4 is a so-called overdrive is accelerated relative to the engine rotational speed N _E, in this embodiment the The gear ratio is 0.83 according to the gear ratios ρ ₁ and ρ ₂ . It can be said that the rotational speed of the first motor generator MG1 corresponds to the torque (reaction force) generated by the first motor generator MG1, which is the rotational driving torque of the first motor generator MG1.

Further, the ratio (= A: B) of the interval A between the first rotation element RE1 and the third rotation element RE3 and the interval B between the third rotation element RE3 and the fourth rotation element RE4 is 1: 0.2. Thus, it can be said that the gear ratio ₁₀ (= interval B / interval A) of the power distribution device 10 as a whole is about “0.2”. Normally, considering the size of each gear constituting the set of planetary gear devices and the overall size, about 0.3 to 0.6 is appropriate, and thus the gear ratio ₁₀ is “ It is difficult to configure a value of about 0.2 "with one set of planetary gear devices, and it is possible by setting a large gear ratio range for the power distribution device 10 as a whole using two sets of planetary gear devices. It can be said that it became. The gear ratio is equivalent to the gear ratio ρ of a set of planetary gear devices.

  The rotational speed of the first motor generator MG1 is a torque (reaction force) that is a rotational driving torque of the first motor generator MG1 by controlling the power generation amount (or driving force) of the first motor generator MG1 by the electronic control unit. ) Is changed at any time to change the rotation speed. Therefore, the rotational drive torque of the first motor generator MG1 needs to be obtained in accordance with the power of the engine 6 distributed by the second planetary gear unit 14. That is, if the torque of the engine 6 is increased, a rotational drive torque corresponding to the torque can be obtained, so that the first motor generator MG1 also needs to be enlarged. However, the increase in size of the first motor generator MG1 may be disadvantageous for mounting on the vehicle in terms of space and weight. Therefore, in the power distribution device 10 of the present embodiment, the gear ratio of the entire power distribution device 10 is increased by providing the first planetary gear device 12 as a speed reducer and not providing the first planetary gear device 12. The first motor generator MG1 is connected to the first rotating element RE1 (first sun gear S1), which has the smallest torque (reaction force) that the first motor generator MG1 takes on, so that the engine 6 distributed by the second planetary gear unit 14 The torque generated by the first motor generator MG1 with respect to the power can be small. That is, since the power distribution device 10 can further reduce the size of the first motor generator MG1, it is possible to increase the output of the engine 6 and handle various engines. Note that the decrease in output due to downsizing of first motor generator MG1 can be compensated for by increasing the rotation speed of first motor generator MG1.

  Further, the power distribution device 10 is provided with the first planetary gear device 12 as a speed reducer and has two planetary gear devices, but the second planetary gear P2 of the second planetary gear device 14 as a power distribution unit is stepped. Since it can be regarded as one planetary gear device replaced with a dopinion SP, the power distribution device 10 as a whole can be configured not to increase in size even though a reduction gear is provided.

  As described above, according to the present embodiment, the first motor generator MG1 is connected to the power distribution unit (second planetary gear unit 14) via the speed reducer (first planetary gear unit 12). Compared to the case where motor generator MG1 is connected to the power distribution unit without passing through the reduction gear, that is, the case where no reduction gear is provided, the first required for the power of engine 6 connected to the power distribution unit. The torque of one motor generator MG1, that is, the torque generated by the first motor generator MG1, can be small, and the first motor generator MG1 can be made compact. Therefore, even if the engine output increases, the first motor generator MG1 can be configured relatively small. That is, since the first motor generator MG1 can be reduced in size in order to cope with the higher output of the engine 6, it is advantageous to mount it on the vehicle.

  In addition, according to the present embodiment, the first motor generator MG1 is operatively connected to the power distribution unit constituted by the second planetary gear device 14 via the first planetary gear device 12, so that the entire device is Simple and compact. Further, since two sets of planetary gear devices are used, the range of gear ratios that can be set for the two sets of planetary gear devices as a whole is larger than when one set of planetary gear devices is used. By setting ρ, the torque generated by the first motor generator MG1 can be easily set to be smaller.

  Further, according to this embodiment, the planetary gear of the first planetary gear unit 12 has a larger diameter than the planetary gear of the second planetary gear unit 14 and is a stepped pinion integrated with each other. The entire apparatus is further reduced in size.

Further, according to the present embodiment, when the relative rotational speed of the first rotational element RE1 with respect to the rotational speed of the third rotational element RE3 is changed according to the rotational speed of the first motor generator MG1, the fourth rotational element RE4 The relative rotation speed with respect to the rotation speed of the third rotation element RE3 is changed. Moreover, since the rotational speed of the first motor generator MG1 is brought continuously changed, it means that the relative rotational speed is continuously changed with respect to the engine rotational speed N _E of the output gear 18 as an output member, wherein The power distribution device 10 has a function as a continuously variable transmission. Further, since the first motor generator MG1 is connected to the first rotating element RE1, the first rotating element RE1, the torque generated by the first motor generator MG1 with respect to the output of the engine 6 can be minimized. Since the intervals between the second rotating element RE2, the third rotating element RE3, and the fourth rotating element RE4 can be set, the first motor generator MG1 can be reduced in size.

  Further, according to the present embodiment, the power distribution device 10 is obtained by using two planetary gear devices of the first planetary gear device 12 and the second planetary gear device 14 as compared with the case of using one set of planetary gear devices. The width of the gear ratio that can be set as a whole is increased, and a gear ratio ρ that is appropriate for a set of planetary gear units, for example, a smaller value as a whole of the power distribution device 10 in the range of about “0.3 to 0.6”. Can be set so that the torque of the first motor generator MG1 can be smaller. Further, since the first planetary gear P1 of the first planetary gear device 12 has a larger diameter than the second planetary gear P2 of the second planetary gear device 14 and can be a stepped pinion SP integrated with each other, The entire power distribution device 10 is further reduced in size.

  Next, another embodiment of the present invention will be described. In the following description, parts common to those in the above-described embodiment are denoted by the same reference numerals and description thereof is omitted.

  FIG. 3 is a skeleton diagram illustrating a configuration of a power distribution device 30 according to another embodiment of the present invention, and FIG. 4 is a collinear diagram thereof. The power distribution device 30 shown in FIG. 3 is applied to a power transmission device 8 that is preferably used for a hybrid vehicle in place of the power distribution device 10 shown in FIG.

In this embodiment, the first planetary gear device 32 constituting the power distribution device 30 functions as a speed reducer, and the second planetary gear device 34 constitutes a power distribution unit, each of which is a single unit. It is composed of a pinion type planetary gear device. The first planetary gear device 32 includes a first sun gear S1, a first planetary gear P1, a first carrier CA1 that supports the first planetary gear P1 so as to rotate and revolve, and a first sun gear via the first planetary gear P1. and a first ring gear R1 meshing with the S1, for example has a gear ratio [rho ₁ of about "0.429". The second planetary gear unit 34 includes a second sun gear S2 via a second sun gear S2, a second planetary gear P2, a second carrier CA2 that supports the second planetary gear P2 so as to rotate and revolve, and a second planetary gear P2. A second ring gear R2 that meshes with the second ring gear R2 and has a predetermined gear ratio ρ ₂ of, for example, about “0.333”.

  In the power distribution device 30, the first sun gear S1 is operatively connected to the first motor generator MG1, and the first ring gear R1 and the second carrier CA2 are integrally connected to each other via the input shaft 16, for example, the engine. 6, the second ring gear R2 is connected to an output member such as the output gear 18. That is, the first motor generator MG1 is operatively connected to the second planetary gear unit 34 via the first planetary gear unit 32, and the second planetary gear unit 34 uses the power of the engine 6 as the output member and the second planetary gear unit 34. It has a function of distributing to one motor generator MG1.

FIG. 4 is a collinear diagram that can represent the relative relationship of the rotational speeds of the rotating elements on a straight line in the power distribution device 30. The collinear chart of FIG. 4 shows the relationship of the gear ratio ρ of each planetary gear device 32, 34 in the horizontal axis direction, and is a two-dimensional coordinate indicating the relative rotational speed in the vertical axis direction. One horizontal line X1 is shows the rotational speed of "1.0" that is, the engine rotational speed N _E which is operatively connected to the input shaft 16. The four vertical lines Y1 to Y4 indicate, in order from the left, the first sun gear S1 corresponding to the first rotating element RE1 and the first carrier CA1 corresponding to the second rotating element RE2 and connected to each other. 2 sun gear S2 corresponding to the third rotating element RE3 and the mutually connected first ring gear R1 and the second carrier CA2, respectively, and the second ring gear R2 corresponding to the fourth rotating element RE4, respectively, and their spacing is It is determined according to the gear ratios ρ ₁ and ρ ₂ of the planetary gear devices 32 and 34, respectively.

  If expressed using the collinear diagram, in the power distribution device 30 of the present embodiment, the first rotating element RE1 (S1) is operatively connected to the first motor generator MG1, and the third rotating element RE3. (R1, CA2) is operatively connected to the engine 6 via the input shaft 16, and the fourth rotating element RE4 (R2) is connected to an output gear 18 as an output member.

As apparent from the collinear diagram of FIG. 4, the fourth rotation element RE4 corresponds to the rotation speed of the first motor generator MG1 corresponding to the first rotation element RE1 as in the embodiment shown in FIG. the relative rotational speed is continuously changed with respect to the engine rotational speed N _E of the output member e.g. output gear 18. Moreover, since the rotation speed of the first motor generator MG1 is continuously changed, the gear ratio is changed steplessly. For example, when the rotational speed of the first rotating element RE1 and zero, the rotational speed of the fourth rotating element RE4 is a so-called overdrive is accelerated relative to the engine rotational speed N _E, in this embodiment the The gear ratio is 0.90 according to the gear ratios ρ ₁ and ρ ₂ .

The ratio (= A: B) of the distance A between the first rotation element RE1 and the third rotation element RE3 and the distance B between the third rotation element RE3 and the fourth rotation element RE4 is 1: 0.1. Thus, it can be said that the gear ratio ₃₀ (= interval B / interval A) of the power distribution device 30 as a whole is about “0.1”. Normally, considering the size of each gear constituting the set of planetary gear devices and the overall size, about 0.3 to 0.6 is appropriate, and thus the gear ratio ratio ₃₀ is “ It is difficult to configure a value of about 0.1 "with one set of planetary gear devices, and it is possible by setting a large gear ratio range for the power distribution device 30 as a whole using two sets of planetary gear devices. It can be said that it became.

  In the power distribution device 30 of the present embodiment, the first planetary gear device 32 is not provided by providing the first planetary gear device 32 as a speed reducer, similarly to the power distribution device 10 in the embodiment of FIGS. Compared to the case, the gear ratio of the entire power distribution device 30 is reduced, and the first motor generator MG1 is connected to the first rotating element RE1 (first sun gear S1) with the smallest torque (reaction force). Thus, the torque generated by the first motor generator MG1 with respect to the power of the engine 6 distributed by the second planetary gear unit 34 can be reduced. That is, since the power distribution device 30 can further reduce the size of the first motor generator MG1, it is possible to increase the output of the engine 6 and cope with various engines. Note that the decrease in output due to downsizing of first motor generator MG1 can be compensated for by increasing the rotation speed of first motor generator MG1.

Further, since the power distribution device 30 cannot replace the second planetary gear P2 with the stepped pinion SP unlike the power distribution device 10, the first planetary gear device 32 is provided as a speed reducer and two planetary gears are provided. Compared with the case of replacing with the stepped pinion SP, for example, the relative rotational speed δ _{1 of} the first planetary gear P1 with respect to the first carrier CA1 or the relative speed of the second planetary gear P2 with respect to the second carrier CA2 is compared. There is an advantage that the rotational speed δ ₂ is reduced.

  As described above, according to the present embodiment, the first motor generator MG1 is connected to the power distribution unit (second planetary gear unit 34) via the speed reducer (first planetary gear unit 32). Compared to the case where motor generator MG1 is connected to the power distribution unit without passing through the reduction gear, that is, the case where no reduction gear is provided, the first required for the power of engine 6 connected to the power distribution unit. The torque of one motor generator MG1, that is, the torque generated by the first motor generator MG1, can be small, and the first motor generator MG1 can be made compact. Therefore, even if the engine output increases, the first motor generator MG1 can be configured relatively small. That is, since the first motor generator MG1 can be reduced in size in order to cope with the higher output of the engine 6, it is advantageous to mount it on the vehicle.

  In addition, according to the present embodiment, the first motor generator MG1 is operatively connected to the power distribution unit constituted by the second planetary gear device 34 via the first planetary gear device 32. Simple and compact. Further, since two sets of planetary gear devices are used, the range of gear ratios that can be set for the two sets of planetary gear devices as a whole is larger than when one set of planetary gear devices is used. By setting ρ, the torque generated by the first motor generator MG1 can be easily set to be smaller.

Further, according to the present embodiment, when the relative rotational speed of the first rotational element RE1 with respect to the rotational speed of the third rotational element RE3 is changed according to the rotational speed of the first motor generator MG1, the fourth rotational element RE4 The relative rotation speed with respect to the rotation speed of the third rotation element RE3 is changed. Moreover, since the rotational drive torque of the first motor generator MG1 is brought continuously changed, it means that the relative rotational speed is continuously changed with respect to the engine rotational speed N _E of the output gear 18 as an output member, The power distribution device 30 has a function as a continuously variable transmission. Further, since the first motor generator MG1 is connected to the first rotating element RE1, the first rotating element RE1, the torque generated by the first motor generator MG1 with respect to the output of the engine 6 can be minimized. Since the intervals between the second rotating element RE2, the third rotating element RE3, and the fourth rotating element RE4 can be set, the first motor generator MG1 can be reduced in size.

Further, according to the present embodiment, the power distribution device 30 is obtained by using two sets of planetary gear devices, that is, the first planetary gear device 32 and the second planetary gear device 34 as compared with the case of using one set of planetary gear devices. The width of the gear ratio that can be set as a whole is increased, and the gear ratio ρ that is appropriate as a set of planetary gear units, for example, a smaller value as a whole of the power distribution device 30 in the range of about “0.3 to 0.6”. Can be set so that the torque of the first motor generator MG1 can be smaller. The relative rotational speed [delta] ₁ for the first carrier CA1 of the first planetary gear _P1, or the relative rotational speed [delta] ₂ is reduced to the second carrier of the second planetary gear, the first planetary gear 32 or the second planetary gear device The durability of 34 is improved.

  FIG. 5 is a skeleton diagram illustrating the configuration of a power distribution device 40 according to another embodiment of the present invention, and FIG. 6 is a collinear diagram thereof. The power distribution device 40 shown in FIG. 5 is applied to the power transmission device 8 suitably used for a hybrid vehicle in place of the power distribution device 10 shown in FIG. 1, and the embodiment shown in FIGS. This has the same effect as the power distribution device 30.

In the present embodiment, the first planetary gear device 42 constituting the power distribution device 40 functions as a speed reducer, and the second planetary gear device 44 constitutes a power distribution unit, It is composed of a pinion type planetary gear device. The first planetary gear device 42 includes a first sun gear S1, a first planetary gear P1, a first carrier CA1 that supports the first planetary gear P1 so as to rotate and revolve, and a first sun gear via the first planetary gear P1. and a first ring gear R1 meshing with the S1, for example has a gear ratio [rho ₁ of about "0.429". The second planetary gear unit 44 includes a second sun gear S2 via a second sun gear S2, a second planetary gear P2, a second carrier CA2 that supports the second planetary gear P2 so as to rotate and revolve, and a second planetary gear P2. and a second ring gear R2 meshing with, for example, has a "0.375" approximately predetermined gear ratio [rho _2.

  In the power distribution device 40, the first ring gear R1 and the second ring gear R2 are integrally connected and operatively connected to the first motor generator MG1, and the first sun gear S1 is connected to the engine, for example, via the input shaft 16. 6, the second sun gear S2 is connected to an output member such as the output gear 18. That is, the first motor generator MG1 is operatively connected to the second planetary gear unit 44 via the first planetary gear unit 42, and the second planetary gear unit 44 uses the power of the engine 6 as the output member and the second planetary gear unit 44. It has a function of distributing to one motor generator MG1.

FIG. 6 is a collinear diagram that can represent the relative relationship of the rotational speeds of the rotating elements on a straight line in the power distribution device 40. The collinear chart of FIG. 6 is a two-dimensional coordinate indicating the relationship of the gear ratio ρ of each planetary gear unit 42, 44 in the horizontal axis direction and the relative rotational speed in the vertical axis direction. One horizontal line X1 is shows the rotational speed of "1.0" that is, the engine rotational speed N _E which is operatively connected to the input shaft 16. The four vertical lines Y1 to Y4 correspond to the first rotation element RE1 and the mutually connected first ring gear R1 and second ring gear R2 in order from the left to the second rotation element RE2. The interconnected first carrier CA1 and second carrier CA2 represent the first sun gear S1 corresponding to the third rotating element RE3 and the second sun gear S2 corresponding to the fourth rotating element RE4, respectively, and the distance between them is They are determined according to the gear ratios ρ ₁ and ρ ₂ of the planetary gear devices 42 and 44, respectively.

  If expressed using the collinear diagram, in the power distribution device 40 of the present embodiment, the first rotation element RE1 (R1, R2) is operatively connected to the first motor generator MG1, and the third rotation. The element RE3 (S1) is operatively connected to the engine 6 via the input shaft 16, and the fourth rotating element RE4 (S2) is connected to an output gear 18 as an output member.

As apparent from the collinear diagram of FIG. 6, the fourth rotation element RE4 corresponds to the rotation speed of the first motor generator MG1 corresponding to the first rotation element RE1 as in the embodiment shown in FIG. the relative rotational speed is continuously changed with respect to the engine rotational speed N _E of the output member e.g. output gear 18. Moreover, since the rotation speed of the first motor generator MG1 is continuously changed, the gear ratio is changed steplessly. For example, when the rotational speed of the first rotating element RE1 and zero, the rotational speed of the fourth rotating element RE4 is a so-called overdrive is accelerated relative to the engine rotational speed N _E, in this embodiment the The gear ratio is 0.90 according to the gear ratios ρ ₁ and ρ ₂ .

The ratio (= A: B) of the distance A between the first rotation element RE1 and the third rotation element RE3 and the distance B between the third rotation element RE3 and the fourth rotation element RE4 is 1: 0.1. Thus, it can be said that the gear ratio ₄₀ (= interval B / interval A) of the power distribution device 40 as a whole is about “0.1”. Normally, considering the size of each gear constituting the set of planetary gear devices and the overall size, about 0.3 to 0.6 is appropriate. Thus, the gear ratio ratio ₄₀ is “ It is difficult to configure a value of about 0.1 "with one set of planetary gear units, and it is possible by setting a large gear ratio range for the power distribution device 40 as a whole using two sets of planetary gear units. It can be said that it became.

  In the power distribution device 40 of the present embodiment, the first planetary gear device 42 is not provided by providing the first planetary gear device 42 as a speed reducer, like the power distribution device 10 in the embodiment of FIGS. Compared to the case, the first rotating element RE1 (the first ring gear R1 connected to each other) is made to reduce the gear ratio of the entire power distribution device 40 and minimize the torque (reaction force) that the first motor generator MG1 has. By connecting to the second ring gear R2), the torque generated by the first motor generator MG1 with respect to the power of the engine 6 distributed by the second planetary gear unit 44 can be reduced. That is, since the power distribution device 40 can further reduce the size of the first motor generator MG1, it is possible to increase the output of the engine 6 and to cope with various engines. Note that the decrease in output due to downsizing of first motor generator MG1 can be compensated for by increasing the rotation speed of first motor generator MG1.

Further, since the power distribution device 40 cannot replace the second planetary gear P2 with the stepped pinion SP unlike the power distribution device 10, the first planetary gear device 42 is provided as a speed reducer and two planetary gears are provided. Compared with the case of replacing with the stepped pinion SP, for example, the relative rotational speed δ _{1 of} the first planetary gear P1 with respect to the first carrier CA1 or the relative speed of the second planetary gear P2 with respect to the second carrier CA2 is compared. There is an advantage that the rotational speed δ ₂ is reduced.

  FIG. 7 is a skeleton diagram illustrating the configuration of a power distribution device 50 according to another embodiment of the present invention, and FIG. 8 is a collinear diagram thereof. The power distribution device 50 shown in FIG. 7 is applied to a power transmission device 8 suitably used for a hybrid vehicle in place of the power distribution device 10 shown in FIG. 1, and the embodiment shown in FIGS. This has the same effect as the power distribution device 30.

In the present embodiment, the first planetary gear device 52 constituting the power distribution device 50 functions as a speed reducer, and the second planetary gear device 54 constitutes a power distribution unit, each of which is a single gear unit. It is composed of a pinion type planetary gear device. The first planetary gear unit 52 includes a first sun gear S1, a first planetary gear P1, a first carrier CA1 that supports the first planetary gear P1 so as to rotate and revolve, and a first sun gear via the first planetary gear P1. and a first ring gear R1 meshing with the S1, for example has a gear ratio [rho ₁ of about "0.429". The second planetary gear unit 54 includes a second sun gear S2 via a second sun gear S2, a second planetary gear P2, a second carrier CA2 that supports the second planetary gear P2 so as to rotate and revolve, and a second planetary gear P2. and a second ring gear R2 meshing with, for example, has a "0.571" approximately predetermined gear ratio [rho _2.

  In the power distribution device 50, the first sun gear S1 and the second sun gear S2 are integrally connected and operatively connected to the first motor generator MG1, and the first ring gear R1 is connected to the engine, for example, via the input shaft 16. 6, the second ring gear R2 is connected to an output member such as the output gear 18. That is, the first motor generator MG1 is operatively connected to the second planetary gear unit 54 via the first planetary gear unit 52, and the second planetary gear unit 54 uses the power of the engine 6 as the output member and the second planetary gear unit 54. It has a function of distributing to one motor generator MG1.

FIG. 8 is a collinear diagram that can represent the relative relationship between the rotational speeds of the rotating elements on a straight line in the power distribution device 50. The collinear chart of FIG. 8 is a two-dimensional coordinate indicating the relationship between the gear ratios ρ of the planetary gear devices 52 and 54 in the horizontal axis direction and the relative rotational speed in the vertical axis direction. shows the rotational speed of "1.0" that is, the engine rotational speed N _E which is operatively connected to the input shaft 16. The four vertical lines Y1 to Y4 correspond to the first rotating element RE1 and the mutually connected first sun gear S1 and second sun gear S2, in order from the left, and correspond to the second rotating element RE2. The interconnected first carrier CA1 and second carrier CA2 represent the first ring gear R1 corresponding to the third rotating element RE3, and the second ring gear R2 corresponding to the fourth rotating element RE4, respectively, and their spacing is They are determined according to the gear ratios ρ ₁ and ρ ₂ of the planetary gear devices 52 and 54, respectively.

  If expressed using the collinear diagram, in the power distribution device 50 of the present embodiment, the first rotating element RE1 (S1, S2) is operatively connected to the first motor generator MG1, and the third rotation is performed. The element RE3 (R1) is operatively connected to the engine 6 via the input shaft 16, and the fourth rotating element RE4 (R2) is connected to an output gear 18 as an output member.

As apparent from the collinear diagram of FIG. 8, the fourth rotation element RE4 corresponds to the rotation speed of the first motor generator MG1 corresponding to the first rotation element RE1 as in the embodiment shown in FIG. the relative rotational speed is continuously changed with respect to the engine rotational speed N _E of the output member e.g. output gear 18. Moreover, since the rotation speed of the first motor generator MG1 is continuously changed, the gear ratio is changed steplessly. For example, when the rotational speed of the first rotating element RE1 and zero, the rotational speed of the fourth rotating element RE4 is a so-called overdrive is accelerated relative to the engine rotational speed N _E, in this embodiment the The gear ratio is 0.90 according to the gear ratios ρ ₁ and ρ ₂ .

The ratio (= A: B) of the distance A between the first rotation element RE1 and the third rotation element RE3 and the distance B between the third rotation element RE3 and the fourth rotation element RE4 is 1: 0.1. Thus, it can be said that the gear ratio ₅₀ (= interval B / interval A) of the power distribution device 50 as a whole is about “0.1”. Normally, considering the size of each gear constituting the set of planetary gear devices and the overall size, about 0.3 to 0.6 is appropriate. Thus, the gear ratio ₅₀ is “ It is difficult to configure a value of about 0.1 "with one set of planetary gear units, and it is possible by setting a large gear ratio range for the power distribution device 50 as a whole using two sets of planetary gear units. It can be said that it became.

  In the power distribution device 50 of the present embodiment, the first planetary gear device 52 is not provided by providing the first planetary gear device 52 as a speed reducer, similarly to the power distribution device 10 in the embodiment of FIGS. Compared to the case, the first rotating element RE1 (the first sun gear S1 connected to each other) is made smaller in the gear ratio of the entire power distribution device 50 and the torque (reaction force) that the first motor generator MG1 has the smallest. By connecting to the second sun gear S2), the torque generated by the first motor generator MG1 with respect to the power of the engine 6 distributed by the second planetary gear unit 54 can be reduced. That is, since the first motor generator MG1 can be further downsized in the power distribution device 50, it is possible to increase the output of the engine 6 and cope with various engines. Note that the decrease in output due to downsizing of first motor generator MG1 can be compensated for by increasing the rotation speed of first motor generator MG1.

Further, since the power distribution device 50 cannot replace the second planetary gear P2 with the stepped pinion SP unlike the power distribution device 10, the first planetary gear device 52 is provided as a speed reducer and two planetary gears are provided. Compared with the case of replacing with the stepped pinion SP, for example, the relative rotational speed δ _{1 of} the first planetary gear P1 with respect to the first carrier CA1 or the relative speed of the second planetary gear P2 with respect to the second carrier CA2 is compared. There is an advantage that the rotational speed δ ₂ is reduced.

  FIG. 9 is a skeleton diagram illustrating the configuration of a power distribution device 60 according to another embodiment of the present invention, and FIG. 10 is a collinear diagram thereof. The power distribution device 60 shown in FIG. 9 is applied to the power transmission device 8 suitably used for a hybrid vehicle in place of the power distribution device 10 shown in FIG. 1, and the embodiment shown in FIGS. This has the same effect as the power distribution device 30.

In the present embodiment, the first planetary gear device 62 constituting the power distribution device 60 functions as a speed reducer, and the second planetary gear device 64 constitutes a power distribution unit, each of which is a single unit. It is composed of a pinion type planetary gear device. The first planetary gear device 62 includes a first sun gear S1, a first planetary gear P1, a first carrier CA1 that supports the first planetary gear P1 so as to rotate and revolve, and a first sun gear via the first planetary gear P1. and a first ring gear R1 meshing with the S1, for example has a gear ratio [rho ₁ of about "0.571". The second planetary gear unit 64 includes a second sun gear S2 via a second sun gear S2, a second planetary gear P2, a second carrier CA2 that supports the second planetary gear P2 so as to rotate and revolve, and a second planetary gear P2. A second ring gear R2 that meshes with the second ring gear R2 and has a predetermined gear ratio ρ ₂ of, for example, about “0.333”.

  In the power distribution device 60, the first sun gear S1 is operatively connected to the first motor generator MG1, and the second carrier CA2 is operatively connected to the engine 6, for example, via the input shaft 16, and the first ring gear R1. And the second ring gear R2 are integrally connected to an output member such as the output gear 18. That is, the first motor generator MG1 is operatively connected to the second planetary gear unit 64 via the first planetary gear unit 62, and the second planetary gear unit 64 uses the power of the engine 6 as the output member and the second planetary gear unit 64. It has a function of distributing to one motor generator MG1.

FIG. 10 is a collinear diagram that can represent the relative relationship between the rotational speeds of the rotating elements on a straight line in the power distribution device 60. The collinear chart of FIG. 10 shows the relationship between the gear ratios ρ of the planetary gear devices 62 and 64 in the horizontal axis direction, and is a two-dimensional coordinate indicating the relative rotational speed in the vertical axis direction. shows the rotational speed of "1.0" that is, the engine rotational speed N _E which is operatively connected to the input shaft 16. The four vertical lines Y1 to Y4 indicate, in order from the left, the first sun gear S1 corresponding to the first rotating element RE1 and the first carrier CA1 corresponding to the second rotating element RE2 and connected to each other. 2 represents the sun gear S2, the second carrier CA2 corresponding to the third rotating element RE3, the first ring gear R1 and the second ring gear R2 corresponding to and connected to the fourth rotating element RE4, respectively. They are determined according to the gear ratios ρ ₁ and ρ ₂ of the planetary gear devices 62 and 64, respectively.

  If expressed using the collinear diagram, in the power distribution device 60 of the present embodiment, the first rotation element RE1 (S1) is operatively connected to the first motor generator MG1, and the third rotation element RE3. (CA2) is operatively connected to the engine 6 via an input shaft 16, and the fourth rotating element RE4 (R1, R2) is connected to an output gear 18 as an output member.

As apparent from the collinear diagram of FIG. 10, the fourth rotation element RE4 corresponds to the rotation speed of the first motor generator MG1 corresponding to the first rotation element RE1 as in the embodiment shown in FIG. the relative rotational speed is continuously changed with respect to the engine rotational speed N _E of the output member e.g. output gear 18. Moreover, since the rotation speed of the first motor generator MG1 is continuously changed, the gear ratio is changed steplessly. For example, when the rotational speed of the first rotating element RE1 and zero, the rotational speed of the fourth rotating element RE4 is a so-called overdrive is accelerated relative to the engine rotational speed N _E, in this embodiment the The gear ratio is 0.90 according to the gear ratios ρ ₁ and ρ ₂ .

The ratio (= A: B) of the distance A between the first rotation element RE1 and the third rotation element RE3 and the distance B between the third rotation element RE3 and the fourth rotation element RE4 is 1: 0.1. Thus, it can be said that the gear ratio ₆₀ (= interval B / interval A) of the power distribution device 60 as a whole is about “0.1”. Usually, considering the size of each gear constituting the set of planetary gear units and the overall size, “0.3 to 0.6” is appropriate, and thus the gear ratio ₆₀ is “ It is difficult to configure a value of about 0.1 "with one set of planetary gear units, and it is possible by setting a large gear ratio range for the power distribution device 60 as a whole using two sets of planetary gear units. It can be said that it became.

  In the power distribution device 60 of the present embodiment, the first planetary gear device 62 is not provided by providing the first planetary gear device 62 as a speed reducer, similarly to the power distribution device 10 in the embodiment of FIGS. Compared to the case, the gear ratio of the entire power distribution device 60 is reduced, and the first motor generator MG1 is connected to the first rotating element RE1 (first sun gear S1) with the smallest torque (reaction force). Thus, the torque generated by the first motor generator MG1 with respect to the power of the engine 6 distributed by the second planetary gear unit 64 can be reduced. That is, since the power distribution device 60 can further reduce the size of the first motor generator MG1, it is possible to increase the output of the engine 6 and handle various engines. Note that the decrease in output due to downsizing of first motor generator MG1 can be compensated for by increasing the rotation speed of first motor generator MG1.

Further, since the power distribution device 60 cannot replace the second planetary gear P2 with the stepped pinion SP unlike the power distribution device 10, the first planetary gear device 62 is provided as a speed reducer and two planetary gears are provided. Compared with the case of replacing with the stepped pinion SP, for example, the relative rotational speed δ _{1 of} the first planetary gear P1 with respect to the first carrier CA1 or the relative speed of the second planetary gear P2 with respect to the second carrier CA2 is compared. There is an advantage that the rotational speed δ ₂ is reduced.

  As mentioned above, although the Example of this invention was described in detail based on drawing, this invention is applied also in another aspect.

  For example, the configuration other than the power distribution device 10 shown in FIG. 1 of the above-described embodiment is an example of the power transmission path of the hybrid vehicle, and the power distribution devices 10, 30, 40, 50, and 60 are also applied to other hybrid vehicles. Can be applied.

Further, the power distribution device 30 or the power distribution device 40 of the above-described embodiment can be configured to have a relative rotational speed δ ₁ or a relative rotational speed δ ₂ smaller than that of the power distribution device 50 or the power distribution device 60. The durability of the first planetary gear device 12 or the second planetary gear device 14 is further improved.

  Further, the first motor generator MG1 and the second motor generator MG2 provided in the power transmission device 8 of the above-described embodiment may be rotating electric machines, that is, a generator only for power generation, a motor only for power running, and a generator. It may be any one having both a function and a function as an electric motor.

  The above description is only an embodiment, and the present invention can be implemented in variously modified and improved forms based on the knowledge of those skilled in the art.

FIG. 1 is a schematic diagram for explaining a main part of a configuration of a power transmission device suitably used for a hybrid vehicle to which a power distribution device according to an embodiment of the present invention is applied. FIG. It is an alignment chart explaining the action | operation of the power distribution device of the Example of FIG. It is a skeleton diagram explaining the structure of the power distribution device which is another Example of this invention, Comprising: The inside of a dashed-dotted line is a figure corresponded in the dashed-dotted line of FIG. FIG. 4 is a collinear diagram illustrating the operation of the power distribution device of the embodiment of FIG. 3, corresponding to FIG. 2. It is a skeleton diagram explaining the structure of the power distribution device which is another Example of this invention, Comprising: The inside of a dashed-dotted line is a figure corresponded in the dashed-dotted line of FIG. FIG. 6 is a collinear diagram illustrating the operation of the power distribution device of the embodiment of FIG. 5, corresponding to FIG. 2. It is a skeleton diagram explaining the structure of the power distribution device which is another Example of this invention, Comprising: The inside of a dashed-dotted line is a figure corresponded in the dashed-dotted line of FIG. FIG. 9 is a collinear diagram illustrating the operation of the power distribution device according to the embodiment of FIG. 7, corresponding to FIG. 2. It is a skeleton diagram explaining the structure of the power distribution device which is another Example of this invention, Comprising: The inside of a dashed-dotted line is a figure corresponded in the dashed-dotted line of FIG. FIG. 10 is a collinear diagram illustrating the operation of the power distribution device of the embodiment of FIG. 9, corresponding to FIG. 2.

Explanation of symbols

6: Engine 12, 32, 42, 52, 62: First planetary gear unit (reduction gear)
S1: First sun gear R1: First ring gear CA1: First carrier 14, 34, 44, 54, 64: Second planetary gear unit (power distribution unit)
S2: Second sun gear R2: Second ring gear CA2: Second carrier 18: Output gear (output member)
MG1: First motor generator (electric motor)
RE1: First rotating element RE2: Second rotating element RE3: Third rotating element RE4: Fourth rotating element SP: Stepped pinion

Claims (9)

A hybrid vehicle including a power distribution unit coupled to an engine and an electric motor,
The hybrid vehicle, wherein the electric motor is connected to the power distribution unit via a speed reducer. 2. The hybrid vehicle according to claim 1, wherein the electric motor is operatively connected to the power distribution unit via a first planetary gear unit, and the power distribution unit is configured of a second planetary gear unit. The hybrid vehicle according to claim 2, wherein the planetary gear of the first planetary gear device is a stepped pinion having a larger diameter than that of the planetary gear of the second planetary gear device and integrated with each other. The speed reducer and the power distribution unit include a first rotating element, a second rotating element, a third rotating element, and a fourth rotating element that are sequentially positioned from one end side to the other end side on the collinear diagram,
The first rotating element is coupled to the electric motor;
The third rotating element is coupled to the engine;
The hybrid vehicle according to any one of claims 1 to 3, wherein the fourth rotating element is connected to an output member. The first sun gear of the first planetary gear device constitutes the first rotating element, the second sun gear of the second planetary gear device constitutes the second rotating element, and the first carrier of the first planetary gear device. And the second carrier of the second planetary gear device is connected to each other to constitute the third rotating element, and the second ring gear of the second planetary gear device constitutes the fourth rotating element. 4 hybrid vehicles. The first sun gear of the first planetary gear device constitutes the first rotating element, and the first carrier of the first planetary gear device and the second sun gear of the second planetary gear device are connected to each other to form the second sun gear. A first ring gear of the first planetary gear set and a second carrier of the second planetary gear set are connected to each other to form the third rotary element, and the second planetary gear set of the second planetary gear set. The hybrid vehicle according to claim 4, wherein a two-ring gear constitutes the fourth rotating element. The first ring gear of the first planetary gear device and the second ring gear of the second planetary gear device are connected to each other to form the first rotating element, and the first carrier and the second planetary gear device of the first planetary gear device. The second carrier of the planetary gear unit is connected to each other to form the second rotating element, and the first sun gear of the first planetary gear unit forms the third rotating element, and the second planetary gear unit The hybrid vehicle according to claim 4, wherein the two sun gears constitute the fourth rotating element. The first sun gear of the first planetary gear device and the second sun gear of the second planetary gear device are connected to each other to form the first rotating element, and the first carrier of the first planetary gear device and the first The second carriers of the two planetary gear units are connected to each other to constitute the second rotating element, the first ring gear of the first planetary gear unit constitutes the third rotating element, and the second planetary gear unit The hybrid vehicle according to claim 4, wherein the second ring gear constitutes the fourth rotating element. The first sun gear of the first planetary gear device constitutes the first rotating element, and the first carrier of the first planetary gear device and the second sun gear of the second planetary gear device are connected to each other to form the second sun gear. A second carrier of the second planetary gear set constitutes the third rotary element, and the first ring gear of the first planetary gear set and the second ring gear of the second planetary gear set mutually The hybrid vehicle according to claim 4, wherein the hybrid vehicle is connected to constitute the fourth rotating element.

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