JP2013023011A - Power transmission device for hybrid vehicle - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a compact oil pump which can be driven even during engine stop, in a power transmission device for a hybrid vehicle.SOLUTION: The oil pump 24 is driven by rotation of any of an engine 14 and a driving wheel 40. Even if the engine 14 is stopped, the oil pump 24 can be driven by rotation of a first pump driving shaft 114 connected to the driving wheel 40. The oil pump 24 is arranged on the same axis as the first pump driving shaft 114, a second pump driving shaft 118 and a planetary gear device 22, thereby preventing increase in space for arranging the oil pump 24. No gear is required for transmitting power when the oil pump 24 exists on a different shaft, thereby achieving the compact oil pump 24 with a simple structure.

Description

  The present invention relates to a power transmission device for a hybrid vehicle, and more particularly to a structure of an oil pump provided in the power transmission device.

  2. Description of the Related Art A hybrid vehicle power transmission device (hereinafter, power transmission device) including a planetary gear device that distributes engine power to an electric motor and drive wheels is well known. In such a power transmission device, conventionally, each lubricating part in the power transmission device is lubricated by the lubricating oil discharged from an oil pump driven by the engine. However, if the motor running mode in which the engine is stopped and the vehicle is driven by the electric motor continues for a long time, the oil pump is not driven, so that the lubricating oil is not supplied for a long time, resulting in a shortage of lubricating oil.

  On the other hand, in the hybrid vehicle disclosed in Patent Document 1, the second gear connected to the first gear 47 connected to the drive wheels via the first one-way clutch 45 and connected to the engine. 49 is provided with an oil pump 35 connected via a second one-way clutch 46. The oil pump 35 configured as described above is driven by the fast-rotating gear of the first gear 47 and the second gear 49, and thus is connected to the drive wheels even when the engine is stopped. As the oil pump 35 is driven by the first gear 47, the lubricating oil can be supplied.

JP 2000-335263 A

  By the way, the oil pump 35 of Patent Document 1 is arranged on a different axis from the planetary gear 6 (planetary gear device), the engine 2 and the first electric circuit means 3 (electric motor). When the oil pump 35 is arranged on another shaft in this way, a space for arranging the oil pump 35 on another shaft becomes large, and there is a problem that the power transmission device is enlarged to secure the space. there were. In addition, there is a problem in that the structure is complicated because a gear for connecting the engine and driving wheels and the oil pump is required.

  The present invention has been made in the background of the above circumstances, and the object thereof is a power transmission device for a hybrid vehicle including a planetary gear device that distributes engine power to an electric motor and drive wheels. An object of the present invention is to provide an oil pump that can be driven even when the engine is stopped and that is compact.

  To achieve the above object, the gist of the invention according to claim 1 is that: (a) a first rotating element, a second rotating element, and a third rotating respectively connected to the engine, the electric motor, and the drive wheel; A power transmission device for a hybrid vehicle having an element and having a planetary gear device that distributes the power of the engine to an electric motor and drive wheels, and (b) connected to the third rotating element, and the planetary gear device A first pump drive shaft that rotates about the same axis as the first pump drive shaft, and (c) a second pump drive shaft that is coupled to the first rotation element and rotates about the first pump drive shaft and the coaxial center; The first pump drive shaft, the second pump drive shaft, and the planetary gear device are arranged coaxially, and the first pump drive shaft and the second pump drive shaft respectively have a first one-way clutch and a second one-way clutch. Connected through a clutch An oil pump which are characterized in that it comprises (e).

  In this way, since the oil pump is driven by the rotation of either the engine or the drive wheel, the oil pump is driven by the rotation of the first pump drive shaft connected to the drive wheel even when the engine is stopped. Can be driven. In addition, since the oil pump is arranged coaxially with the first pump drive shaft, the second pump drive shaft, and the planetary gear device, the space for arranging the oil pump does not increase, and the oil pump is on another shaft. In this case, the gear for transmitting the power, etc., which is necessary in the case of the above, can be eliminated, so that the oil pump can be configured compactly with a simple structure.

  Preferably, the planetary gear device and the electric motor are separated by a partition wall that is a non-rotating member, and the partition wall is used as a constituent member of the oil pump. In this way, since the oil pump is disposed in the partition wall that partitions the electric motor and the planetary gear device, the axial distance between the oil pump and the planetary gear device is reduced, and the oil pump and the planetary gear device are The lengths in the axial direction of the first pump drive shaft and the second pump drive shaft connecting the two are shortened. Further, since the partition wall is used as a constituent member of the oil pump, the number of parts of the oil pump can be reduced by one.

  Preferably, the outer diameter of the oil pump is smaller than the outer diameter of the rotor of the electric motor. If it does in this way, when arranging an oil pump, a part of space formed between a rotor and a partition can be used, and the axial length of a power transmission device can be shortened.

1 is a skeleton diagram for explaining a power transmission device for a hybrid vehicle to which the present invention is applied. 2 is a cross-sectional view showing a range corresponding to a portion A (dashed line) of FIG. 1 including an oil pump in the power transmission device of FIG. 1. It is an enlarged view of the one-way clutch shown in FIG.

  Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. In the following embodiments, the drawings are appropriately simplified or modified, and the dimensional ratios, shapes, and the like of the respective parts are not necessarily drawn accurately.

  FIG. 1 is a skeleton diagram for explaining a hybrid vehicle power transmission device 10 (hereinafter referred to as “power transmission device 10”) to which the present invention is applied.

  In FIG. 1, a power transmission device 10 is interposed between an engine 14 which is an internal combustion engine such as a gasoline engine or a diesel engine and a drive wheel 40, and a driving force from the engine 14 is applied to the drive wheel 40. A transaxle to transmit. The power transmission device 10 has a transaxle (T / A) case 12 (hereinafter referred to as “case 12”) as a non-rotating member attached to the vehicle body. In the case 12, the first axis RC1 is provided. A damper 16 operatively connected to an output shaft (for example, a crankshaft) of the engine 14 in order from the engine 14 side, and an input shaft connected to the engine 14 via the damper 16 and driven to rotate by the engine 14 18, a first drive gear 20 as an output rotating member supported so as to be rotatable relative to the input shaft 18 on the outer peripheral side of the input shaft 18, a planetary gear device 22 functioning as a power distribution mechanism, an oil pump 24, and A first electric motor M1 is provided. The first electric motor M1 corresponds to the electric motor of the present invention.

  Further, the power transmission device 10 has a first driven gear 26, a first counter gear device 28, and a first driven gear 26 that mesh with the first drive gear 20 on a second axis RC2 parallel to the first axis RC1. A second drive gear (differential drive gear) 30, a second counter gear device 32, and a second drive gear 30 connected via a first counter gear device 28 via a second counter gear device 32. Two electric motors M2 are provided. Further, the power transmission device 10 includes a differential gear device (final reduction gear) having a second driven gear (diffractive driven gear) 34 that meshes with the second drive gear 30 on a third axis RC3 parallel to the second axis RC2. 36, a pair of left and right axles 38 which are output shafts of the differential gear device 36, and a pair of left and right drive wheels 40 connected to the pair of left and right axles 38. Thus, the power transmission device 10 is a multi-shaft transaxle in which the first electric motor M1 and the second electric motor are arranged on different axes.

  The power transmission device 10 is placed in front of a front wheel drive, that is, an FF (front engine / front drive) type vehicle 6 and is preferably used for driving the drive wheels 40, for example. In the power transmission device 10, the power of the engine 14 is transmitted to the planetary gear device 22 via the damper 16 and the input shaft 18. Then, by controlling the first electric motor M1, the power of the engine 14 is appropriately distributed to the first electric motor M1 and the first drive gear 20 by the planetary gear device 22 which is a power distribution mechanism. The power distributed to the first drive gear 20 sequentially passes through the first drive gear 20, the first driven gear 26, the first counter gear device 28, the second drive gear 30, the differential gear device 36, the pair of axles 38, and the like. Via the pair of drive wheels 40. Further, regenerative control by the first electric motor M1 is executed by the power distributed to the first electric motor M1. Further, when the motor is running (engine stopped), the power output from the second electric motor M2 sequentially passes through the second counter gear device 32, the second drive gear 30, the differential gear device 36, the pair of axles 38, and the like. Via the pair of drive wheels 40.

  The damper 16 is a damper used in a general vehicle, and is interposed between the engine 14 and the input shaft 18. The damper 16 transmits torque from one of the engine 14 and the input shaft 18 to the other and the engine. 14 absorbs pulsation caused by torque fluctuations and the like.

  The first counter gear device 28 includes a first countershaft 42 that is parallel to the second axis RC2, a first gear 44 that is coaxially connected to the first driven gear 26, and a first gear 44 that meshes with the first gear 44. A second gear 46 connected to the countershaft 42, a third gear 48 connected to the first countershaft 42 and rotating integrally with the second gear 46, meshed with the third gear 48, and the second drive gear 30. A fourth gear 50 connected coaxially therewith is provided. The first counter gear device 28 thus configured decelerates the rotation from the first driven gear 26 and transmits it to the second drive gear 30.

  The second counter gear device 32 includes a second countershaft 52 parallel to the second axis RC2, a fifth gear 54 coaxially connected to the second electric motor M2, and a second gear meshing with the fifth gear 54. A sixth gear 56 connected to the countershaft 52, a seventh gear 58 connected to the second countershaft 52 and rotating integrally with the sixth gear 56, meshed with the seventh gear 58, and the second drive gear 30. An eighth gear 60 connected coaxially thereto is also provided. The second counter gear device 32 configured in this manner decelerates the rotation from the second electric motor M <b> 2 and transmits it to the second drive gear 30.

  FIG. 2 is a cross-sectional view showing a range corresponding to part A (dashed line) of FIG. 1 including the oil pump 24 in the power transmission device 10 of FIG. As shown in FIG. 2, on the outer peripheral side of the input shaft 18 that rotates around the first axis RC1, a planetary gear device 22 that functions as a power distribution mechanism is arranged with the first axis RC1 as the center of rotation. Further, on the opposite side of the planetary gear device 22 in the axial direction from the engine 14, a first electric motor M1 is disposed around the first axis RC1 with a partition wall 70 as a non-rotating member to be described later.

  The case 12 of the present embodiment includes a first case member 12a that mainly accommodates the planetary gear unit 22 and a second case member 12b that mainly accommodates the first electric motor M1. The members (12a, 12b) are integrally fastened by bolts 72.

  The planetary gear device 22 includes a sun gear S1, a pinion gear P1, a carrier CA1 that supports the pinion gear P1 so as to rotate and revolve, and a ring gear R1 that meshes with the sun gear S1 via the pinion gear P1. The carrier CA1 corresponds to the first rotating element of the present invention, the sun gear S1 corresponds to the second rotating element of the present invention, and the ring gear R1 corresponds to the third rotating element of the present invention.

  The sun gear S1 is formed in a cylindrical shape and is rotatably supported around the first axis RC1. On the outer peripheral side of the sun gear S1, outer peripheral teeth that mesh with the pinion gear P1 are formed. The sun gear S1 is rotated integrally with the rotor shaft 86 by being spline-fitted to a rotor shaft 86 described later of the first electric motor M1.

  The carrier CA1 is rotated together with the input shaft 18 by being connected to the flange portion 18a extending in the radial direction from the input shaft 18. The carrier CA1 holds a plurality of carrier pins 74 in the circumferential direction, and a pinion gear P1 is supported on the outer periphery of the carrier pin 74 so as to be capable of rotating.

  The ring gear R1 has inner peripheral teeth that mesh with the pinion gear P1 on the inner peripheral side, and further, a first drive gear 20 and a parking gear 76 are formed on the outer peripheral side. Thus, the ring gear R1 is a composite gear member in which the first drive gear 20 and the parking gear are integrally formed as well as the inner peripheral teeth that mesh with the pinion gear P1. The ring gear R1 is rotatably supported on the case 12 by bearings 78a and 78b arranged at both ends on the inner peripheral side.

  The first electric motor M1 includes a stator 80, coil ends 82 disposed at both ends of the stator 80 in the axial direction, a rotor 84 disposed on the inner peripheral side of the stator 80, and a rotor shaft connected to the inner peripheral end of the rotor 84. 86.

  The stator 80 is formed in an annular shape by laminating a plurality of disc steel plates, and is fixed to the case 12 (second case member 12b) by a bolt 88 so as not to rotate. The rotor 84 is disposed on the inner peripheral side of the stator 80 with a slight gap therebetween. The rotor 84 is formed in an annular shape by laminating a plurality of disc steel plates, and a rotor shaft 86 is connected to the inner peripheral end of the rotor 84. The rotor shaft 86 is rotatably supported at both ends via bearings 90 and the like. Accordingly, the rotation of the first electric motor M1 is transmitted from the rotor shaft 86 to the sun gear S1 of the planetary gear device 22.

  A partition wall 70 is formed so as to partition the first electric motor M <b> 1 and the planetary gear device 22. The partition wall 70 is a non-rotating member having a disk shape extending from the outer peripheral wall of the second case member 12b toward the inner periphery toward the first axis RC1. Therefore, the planetary gear device 22 and the first electric motor M1 are separated by the partition wall 70.

  In the present embodiment, the partition wall 70 is provided with an oil pump 24 for pumping up lubricating oil stored in an oil pan (not shown) and supplying it to the planetary gear unit 22 and the like. Specifically, the partition wall 70 is used as a part of a member constituting the oil pump 24. The oil pump 24 is a known gear pump, and includes a drive gear 94, a driven gear 96, a partition wall 70, and a disc-shaped pump cover 98.

  An annular space is formed in the inner peripheral portion of the partition wall 70, and the drive gear 94 and the driven gear 96 of the oil pump 24 are accommodated in this space. That is, the partition wall 70 functions as a part of the pump body for housing the drive gear 94 and the driven gear 96.

  The pump cover 98 is fastened to the partition wall 70 by the bolt 100, so that the drive gear 94 and the driven gear 96 are sealed in the space of the partition wall 70. The outer peripheral teeth of the drive gear 94 and the inner peripheral teeth of the driven gear 96 are meshed with each other. When the drive gear 94 rotates, lubricating oil sucked up from an oil pan (not shown) is discharged to the pump cover 98. It is discharged to the oil passage 102.

  The discharged lubricating oil passes through the radial oil passage 104 formed in the rotor shaft 86 and the first radial oil passage 106 formed in the input shaft 18 and enters the inner peripheral side of the input shaft 18. It is supplied to the lubricating oil supply oil passage 108 parallel to the formed first axis RC1. Further, the lubricating oil flowing through the lubricating oil supply oil passage 108 passes through the second radial oil passage 110 and the third radial oil passage 112 by the centrifugal force when the input shaft 18 rotates, and the planetary gear device 22 and each of the planetary gear devices 22. Supplied to bearings and the like.

  Here, rotation is transmitted to the drive gear 94 of this embodiment from either the carrier CA1 or the ring gear R1 of the planetary gear unit 22. The drive gear 94 (oil pump 24) is connected to the first pump drive shaft 114 connected to the ring gear R1 (the third rotating element of the present invention) via a known first one-way clutch 116, and the carrier It is connected to a second pump drive shaft 118 connected to CA1 (the first rotating element of the present invention) via a known second one-way clutch 117. The ring gear R1 (third rotating element) includes the first drive gear 20, the first driven gear 26, the first counter gear device 28, the second drive gear 30, the second drive gear 30, the differential gear device 36, and a pair. The first pump drive shaft 114 is also connected to the drive wheel 40 in the same manner. Further, since the carrier CA1 (first rotating element) is connected to the engine 14 via the input shaft 18, the damper device 16, and the like, the second pump drive shaft 118 is also connected to the engine 14 in the same manner. The first one-way clutch 116 corresponds to the first one-way clutch of the present invention, and the second one-way clutch 117 corresponds to the second one-way clutch of the present invention.

  The first pump drive shaft 114 includes a cylindrical portion 114a that can rotate about the first axis RC1 and a disc portion 114b that extends in the radial direction from the end on the planetary gear device 22 side in the axial direction of the cylindrical portion 114a. ing. Outer peripheral teeth are formed at the outer peripheral end of the disc portion 114b, and the outer peripheral teeth are engaged with the inner peripheral teeth of the ring gear R1. Accordingly, the first pump drive shaft 114 is rotated together with the ring gear R1. Further, an outer peripheral end portion on the first electric motor M1 side in the axial direction of the cylindrical portion 114a is connected to an inner peripheral surface of the first one-way clutch 116.

  The second pump drive shaft 118 is disposed on the inner peripheral side of the first pump drive shaft 114 and has a cylindrical shape that can rotate around the first axis RC1. The end of the planetary gear unit 22 in the axial direction of the second pump drive shaft 118 is connected to the carrier CA1. In the present embodiment, the second pump drive shaft 118 and the carrier CA1 are integrally formed. Further, the outer peripheral end of the first electric motor M1 in the axial direction of the second pump drive shaft 118 is connected to the inner peripheral surface of the second one-way clutch 117. A thrust bearing 119 is interposed between the first pump drive shaft 114 and the second pump drive shaft 118, and these are supported so as to be relatively rotatable.

  FIG. 3 is an enlarged view of the first one-way clutch 116 and the second one-way clutch 117. As shown in FIG. 3, the first one-way clutch 116 is inserted between the drive gear 94 of the oil pump 24 and the first pump drive shaft 114, and the second one-way clutch 117 is connected to the drive gear 94 and the second pump. It is inserted between the drive shaft 118. The first one-way clutch 116 includes a first sprag 120 interposed between the first pump drive shaft 114 and the drive gear 94. The second one-way clutch 117 includes a second sprag 122 that is interposed between the second pump drive shaft 118 and the drive gear 94. In the present embodiment, the drive gear 94 also serves as the outer ring of the one-way clutch, and the first pump drive shaft 114 and the second pump drive shaft 118 also serve as the inner ring of the one-way clutch.

  In this embodiment, the first one-way clutch 116 and the second one-way clutch 117 have an integral structure. Specifically, a first sprag 120, a second sprag 122, a spacer 124 interposed between the first sprag 120 and the second sprag 122 in the axial direction, the first sprag 120, the second sprag 122, And an annular plate-like cage 126 that holds the spacer 124, and is configured as one member.

  A plurality of the first sprags 120 and the second sprags 122 are arranged in the circumferential direction, and are held by the cage 126 at equal angular intervals in the circumferential direction. In addition, the spacer 124 is interposed between the first sprag 120 and the second sprag 122, so that the axial interval between the first sprag 120 and the second sprag 122 is maintained at a constant value. .

  The first one-way clutch 116 (first sprag 120) connects the first pump drive shaft 114 and the drive gear 94 when the first pump drive shaft 114 rotates in the forward rotation direction corresponding to the vehicle forward direction. . On the other hand, at the time of reverse rotation or when the rotation of the drive gear 94 is faster than the rotation of the first pump drive shaft 114, these are idled so that the first pump drive shaft 114 and the drive gear 94 are disconnected.

  Further, the second saddle-way clutch 117 (second sprag 122) has a second pump drive shaft 118, a drive gear 94, and the like when the second pump drive shaft 118 rotates in the forward rotation direction corresponding to the vehicle forward direction. Connect. On the other hand, during reverse rotation or when the rotation of the drive gear 94 is faster than the rotation of the second pump drive shaft 118, these are idled so that the second pump drive shaft 118 and the drive gear 94 are disconnected. There are many specific shapes of the first sprags 120 and the second sprags 122, for example, but they are well known and will not be described.

  By providing the first sprag 120 and the second sprag 122 in this way, the first one-way clutch 116 and the second one-way clutch 117 have a fast rotation among the first pump drive shaft 114 and the second pump drive shaft 118. The side member and the drive gear 94 are connected. For example, when the rotation of the first pump drive shaft 114 is faster than the second pump drive shaft 118, the first pump drive shaft 114 and the drive gear 94 are connected by the first sprag 120. At this time, since the rotation of the drive gear 94 is faster than the rotation of the second pump drive shaft 118, the second pump drive shaft 118 and the drive gear 94 are idle.

  When the rotation of the second pump drive shaft 118 is faster than that of the first pump drive shaft 114, the second pump drive shaft 118 and the drive gear 94 are connected by the second sprag 120. At this time, since the rotation of the drive gear 94 is faster than the rotation of the first pump drive shaft 114, the first pump drive shaft 114 and the drive gear 94 are in an idling state. From the above, if either one of the first pump drive shaft 114 and the second pump drive shaft 118 is rotating in the forward rotation direction, the drive gear 94 is driven.

  Returning to FIG. 2, in the present embodiment, the outer diameter r1 of the oil pump 24 is designed to be smaller than the outer diameter r2 of the rotor 84 of the first electric motor M1. In the present embodiment, the outer diameter r1 of the oil pump 24 is defined as the outer diameter r1 of the driven gear 96. When the oil pump 24 is configured in this way, when the oil pump 24 is arranged, a part of the space formed on the inner peripheral side of the coil end 82 of the first electric motor M1 can be used. The oil pump 24 can be approached in the axial direction. The oil pump 24 of the present embodiment is provided for supplying lubricating oil and does not generate a large capacity and high pressure hydraulic pressure, so that the oil pump 24 can be made small.

  Further, the oil pump 24 of the present embodiment is disposed coaxially with the first pump drive shaft 114, the second pump drive shaft 118, and the planetary gear device 22. When the oil pump 24 is arranged at such a position, the connection configuration between the oil pump 24 and the first pump drive shaft and the second pump drive shaft 118 becomes simple, and the oil pump 24 can be configured compactly. For example, when the oil pump is disposed on a separate shaft, a gear or the like for transmitting power to the oil pump disposed on the separate shaft is required. Moreover, since it becomes necessary to extend the non-rotating member etc. for accommodating the gear of an oil pump, the space which arrange | positions an oil pump will enlarge. On the other hand, in the oil pump 24 of the present embodiment, the above problem does not occur because the oil pump 24 is arranged on the same axis. Moreover, since the partition wall 70 conventionally formed is used as a constituent member (pump body) of the oil pump 24, the number of parts of the oil pump 24 is further reduced.

  The lubrication of the power transmission device 10 configured as described above will be described. During forward travel by the engine 14, the first pump drive shaft 114 rotates in the same rotation as the engine 14 via the input shaft 18 and the carrier CA 1 of the planetary gear device 22. Further, since the ring gear R1 of the planetary gear device 22 also rotates, the second pump drive shaft 118 also rotates in the same manner. Accordingly, the drive gear 94 is driven by a member of the first pump drive shaft 114 and the second pump drive shaft 118 that rotates faster, so that the lubricating oil is supplied from the oil pump 24. For example, when the second pump drive shaft 118 rotates faster than the first pump drive shaft 114 during low-speed traveling, the second pump drive shaft 118 and the drive gear 94 are connected by the second one-way clutch 117, and the engine The drive gear 94 is driven by the rotation from the 14 side. Further, for example, when the rotation of the first pump drive shaft 114 becomes faster than the second pump drive shaft 118 during high speed traveling, the second one-way clutch 117 is switched to the idling state, while the first one-way clutch 116 causes the first pump drive shaft 114 to rotate. 114 and the drive gear 94 are connected, and the drive gear 94 is driven by rotation from the drive wheel 40 side.

  Further, when the engine 14 is stopped and the second electric motor M2 travels forward (motor travel), the engine 14 is in a non-rotating state, so that the second pump drive shaft 118 is similarly in a rotation stopped state. However, when the second electric motor M2 rotates, the ring gear R1 rotates via the second counter gear device 32, the first counter gear device 28, the first driven gear 26, and the first drive gear 20, so that the first pump drive shaft 114 is rotated. Rotates. Accordingly, the driven gear 94 is driven by the first pump drive shaft 114, and the oil pump 24 is driven. Therefore, even if the motor travels for a long time, the power transmission device 10 can be lubricated.

  As described above, according to the present embodiment, the oil pump 24 is driven by the rotation of either the engine 14 or the drive wheels 40, so that the oil pump 24 is connected to the drive wheels 40 even when the engine 14 is stopped. The oil pump 24 can be driven by the rotation of the first pump drive shaft 114. Further, since the oil pump 24 is arranged coaxially with the first pump drive shaft 114, the second pump drive shaft 118, and the planetary gear device 22, the space for arranging the oil pump 24 does not increase, and the oil pump 24 Since the gear and the like for transmitting power required when the pump 24 is on another axis can be eliminated, the oil pump 24 can be configured compactly with a simple structure.

  Further, according to the present embodiment, the planetary gear device 22 and the first electric motor M1 are separated by the partition wall 70 that is a non-rotating member, and the partition wall 70 is used as a constituent member of the oil pump 24. In this way, since the oil pump 24 is disposed on the partition wall 70 that partitions the first electric motor M1 and the planetary gear device 22, the axial distance between the oil pump 24 and the planetary gear device 22 is close. Thus, the axial lengths of the first pump drive shaft 114 and the second pump drive shaft 18 connecting the oil pump 24 and the planetary gear device 22 are shortened. Further, since the partition wall 70 is used as a constituent member (pump body) of the oil pump 24, the number of parts of the oil pump 24 can be reduced by one.

  Further, according to the present embodiment, the outer diameter r1 of the oil pump 24 is smaller than the outer diameter r2 of the rotor 84 of the first electric motor M1. In this way, when the oil pump 24 is disposed, a part of the space formed between the rotor 84 and the partition wall 70 can be used, and the axial length of the power transmission device 10 can be shortened.

  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, in the above-described embodiment, the carrier CA1 and the second pump drive shaft 118 are integrally formed, but the carrier CA1 and the second pump drive shaft 118 are formed separately, for example, spline fitting or welding. It may be configured to be connected by.

  In the above-described embodiment, the carrier CA1 of the planetary gear unit 22 is connected to the engine 14, the sun gear S1 is connected to the first electric motor M1, and the ring gear R1 is connected to the drive wheels 40. For example, the carrier CA1 may be connected to the drive wheel, the sun gear S1 may be connected to the engine, and the ring gear R1 may be connected to the electric motor.

  In the above-described embodiment, the one-way clutch 116 is a sprag type, but a roller-type one-way clutch may be used. In the above-described embodiment, the one-way clutch 116 is of a type that integrally includes the first sprag 120 and the second sprag 122, but the first one-way clutch that includes the first sprag 120, and A configuration in which the two one-way clutches of the second one-way clutch composed of the second sprags 122 are separately provided may be employed.

  In the above-described embodiment, the oil pump 24 is a gear pump. However, other types of oil pumps such as a vane pump may be used within a consistent range.

  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.

10: Power transmission device for hybrid vehicle 14: Engine 22: Planetary gear device)
24: oil pump 40: drive wheel 70: partition wall 84: rotor 114: first pump drive shaft 116: first one-way clutch (first one-way clutch)
117: Second one-way clutch (second one-way clutch)
118: Second pump drive shaft CA1: Carrier (first rotating element)
S1: Sun gear (second rotating element)
R1: Ring gear (third rotating element)
M1: 1st electric motor (electric motor)

Claims (3)

A planetary gear device having a first rotating element, a second rotating element, and a third rotating element coupled to an engine, an electric motor, and a driving wheel, respectively, and distributing power of the engine to the electric motor and the driving wheel A hybrid vehicle power transmission device comprising:
A first pump drive shaft coupled to the third rotating element and rotating about a coaxial axis with the planetary gear device;
A second pump drive shaft coupled to the first rotating element and rotating about a coaxial axis with the first pump drive shaft;
The first pump drive shaft, the second pump drive shaft, and the planetary gear device are arranged coaxially, and the first pump drive shaft and the second pump drive shaft are respectively provided with a first one-way clutch and a second one. An oil pump connected via a directional clutch,
A power transmission device for a hybrid vehicle, comprising: The planetary gear device and the electric motor are separated by a partition wall that is a non-rotating member,
The power transmission device for a hybrid vehicle according to claim 1, wherein the partition wall is used as a constituent member of the oil pump.   The power transmission device for a hybrid vehicle according to claim 2, wherein an outer diameter of the oil pump is smaller than an outer diameter of a rotor of the electric motor.

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