JP2004138122A - Carrier support structure for planetary gear device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a carrier support structure for a planetary gear device to be used for a hybrid transmission or the like in which axial direction size is reduced. <P>SOLUTION: The planetary gear device is provided with a planetary gear mechanism comprising ring gears R1 and R2, sun gears S1 and S2, a long pinion P1 engaged with the ring gear R1 and the sun gear S2, a short pinion P2 engaged with the ring gear R2 and the sun gear S1, and also engaged with the long pinion P1, and a carrier C supporting the long and short pinions P1 and P2 through a pinion rotation shaft to act as a driving force output element. The planetary gear device is further provided with an input shaft 20 disposed on the same axial line as the sun gears S1 and S2 to be a driving force input element, a clutch CL to couple the ring gear R1 with the input shaft 20 for driving, and a brake FWD/B to brake rotation of the ring gear R2. In a pinion rotation shaft support member 29 provided at one axial end part of the carrier C, a boss part is projected axially outward to a radially extended part to form an L-shaped cross section. The boss part is engaged with the input shaft 20, so that it is supported. <P>COPYRIGHT: (C)2004,JPO

Description

[0001]
TECHNICAL FIELD OF THE INVENTION
The present invention relates to a carrier support structure for a planetary gear device, and more particularly to a carrier support structure with improved space efficiency.
[0002]
[Prior art]
As the planetary gear mechanism, generally, a first ring gear and a second ring gear, a first sun gear and a second sun gear respectively coupled to mutually different rotating elements, the first ring gear and the first sun gear, A long pinion that meshes, a short pinion that meshes with the second ring gear and the second sun gear and meshes with the long pinion, and rotatably supports the long pinion and the short pinion via a pinion rotation shaft. For example, a Ravigneaux-type planetary gear mechanism is known which has a carrier as an output element of a driving force.
[0003]
In addition to this planetary gear mechanism, an input shaft which is arranged on the same axis as the first sun gear and the second sun gear and serves as an input element of driving force, and an input shaft of the first ring gear and the second ring gear A planetary gear device can be configured by including a clutch that one of the driving shafts is coupled to the input shaft and a brake that brakes the rotation of the other of the first ring gear and the second ring gear. .
[0004]
[Problems to be solved by the invention]
However, in such a planetary gear device, a support portion for the first sun gear or the second sun gear, a support portion for the carrier, and a clutch for drivingly coupling one of the first ring gear and the second ring gear to the input shaft are provided. Are arranged along the same axis, and if they are simply juxtaposed, the dimension in the axial direction becomes long, and a problem arises in that the planetary gear device cannot be compactly constructed.
[0005]
SUMMARY OF THE INVENTION It is an object of the present invention to advantageously solve the above-mentioned problems, improve space efficiency, and configure a compact planetary gear device having a short axial dimension.
[0006]
[Means for Solving the Problems]
The carrier support structure of the planetary gear device according to the present invention has the following features.
The present invention provides a first ring gear and a second ring gear, a first sun gear and a second sun gear respectively coupled to different rotating elements, and a long gear meshing with the first ring gear and the first sun gear. A pinion, a short pinion that meshes with the second ring gear and the second sun gear and meshes with the long pinion, and rotatably supports and drives the long pinion and the short pinion via a pinion rotation shaft, respectively; A planetary gear mechanism having a carrier serving as a force output element, an input shaft disposed on the same axis as the first sun gear and the second sun gear and serving as a driving force input element, A clutch drivingly coupling one of a ring gear and the second ring gear to the input shaft; A planetary gear unit comprising a brake for braking the other of the rotation of the serial first ring gear and said second ring gear to the assumption.
[0007]
According to the present invention, in the planetary gear device, the carrier has a boss portion and a radially extending portion that extends radially outward from the carrier and supports the pinion rotation shaft. The pinion rotary shaft support member has an L-shaped cross section by projecting the boss portion outward in the axial direction of the carrier with respect to the radially extending portion, and fitting the boss portion to the input shaft. The carrier is supported to form a carrier support structure.
[0008]
【The invention's effect】
According to the carrier support structure of the planetary gear device having the above-described configuration, the pinion rotation shaft support member at one axial end of the carrier extends radially outward from the boss portion and radially outward from the boss portion to support the pinion shaft. And the boss portion is formed to protrude outward in the axial direction of the carrier with respect to the radially extending portion so as to have an L-shaped cross section, so that one end of the carrier is supported by the boss portion having a sufficient width. Meanwhile, another member such as a ring gear support member can be disposed outside the carrier adjacent to the radially extending portion, thereby increasing space efficiency and forming a compact planetary gear device having a short axial dimension. can do.
[0009]
BEST MODE FOR CARRYING OUT THE INVENTION
Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. FIG. 1 illustrates a hybrid transmission for applying a carrier support structure of a planetary gear device according to the present invention, which is used as a transaxle for a front-wheel drive vehicle (FF vehicle) in the present embodiment. The configuration described below, which is useful for the following, is adopted.
[0010]
In FIG. 1, reference numeral 1 denotes a transmission case, and a Ravigneaux type planetary gear set 2 as a planetary gear mechanism is built in the transmission case 1 on the right side in the axial direction (left-right direction in the drawing) (front side near the engine ENG). On the left side of FIG. 1 (on the rear side far from the engine ENG), for example, a motor / generator set that enables the composite current two-layer motor 4 is incorporated.
The Ravigneaux type planetary gear set 2 and the composite current two-layer motor 4 are coaxially arranged on the main axis of the transmission case 1, but the countershaft 5 and the differential gear device 6, which are offset from the main axis and arranged in parallel, also change the speed. It is built into the machine case 1.
[0011]
The Ravigneaux type planetary gear set 2 is a combination of a single pinion planetary gear set 7 and a double pinion planetary gear set 8 sharing the long pinion P1. The single pinion planetary gear set 7 has a structure in which a long pinion P1 is meshed with a sun gear (first sun gear) S2 and a ring gear (first ring gear) R1, respectively. The double pinion planetary gear set 8 includes a large-diameter short pinion P2 in addition to the sun gear (second sun gear) S1, the long pinion P1, and the ring gear (second ring gear) R2. And the long pinion P1 and the ring gear R2.
Note that the Ravigneaux planetary gear set 2 has a configuration in which a total of six pinion gears, that is, three long pinions P1 and three short pinions P2 are provided.
Then, all the pinion gears P1, P2 of the planetary gear sets 7, 8 are rotatably supported by a common carrier C.
The forward brake FWD / B composed of a multi-plate brake acts to restrain the rotation of the ring gear R2 by engaging the forward brake FWD / B. The forward brake FWD / B is always engaged when the vehicle travels forward, while it is engaged when the vehicle travels backward. The fastening is released.
[0012]
The Ravigneaux-type planetary gear set 2 having the above-described configuration mainly includes five rotating members of a sun gear S1, a sun gear S2, a ring gear R1, a ring gear R2, and a carrier C, and two members among the five rotating members. Is determined, the rotational speed of the other members is determined, and a two-degree-of-freedom differential is determined.
The rotation speeds of the five rotating members are in the order of the sun gear S1, the ring gear R1, the carrier C, the ring gear R2, and the sun gear S2.
[0013]
The composite current two-layer motor 4 also includes an inner rotor 4ri and an annular outer rotor 4ro surrounding the inner rotor 4ri, supported coaxially and rotatably in the transmission case 1. The inner rotor 4ri and the outer rotor 4ro are provided. An annular stator 4s coaxially arranged in an annular space between them is fixed to the transmission case 1.
A first motor / generator MG1, which is an inner motor / generator, is constituted by the annular coil 4s and the inner rotor 4ri, and a second motor / generator MG2, which is an outer motor / generator, is constituted by the annular coil 4s and the outer rotor 4ro. Is configured.
Here, the motors / generators MG1 and MG2 are motors that output rotations in individual directions according to the supply current and at individual speeds (including stop) according to the supply current when the composite current is supplied. It functions as a generator that generates electric power according to rotation by external force when composite current is not supplied.
[0014]
The five rotating members of the Ravigneaux type planetary gear set 2 include a first motor / generator MG1 and an engine ENG as a prime mover in the order of sun gear S1, ring gear R1, carrier C, ring gear R2 and sun gear S2 in order of rotational speed. The output (Out) to the wheel drive system including the differential gear device 6, the forward brake FWD / B, and the second motor / generator MG2 are respectively coupled.
[0015]
This coupling will be described in detail below with reference to FIG. 1. In order to use the ring gear R1 as an input element to which the engine (ENG) rotation is input as described above, the ring gear R1 is connected to the engine crankshaft 9 via the clutch CL. Join.
The clutch CL here disconnects and connects the ring gear R <b> 1 and the engine crankshaft 9. By the connection and disconnection of the clutch CL, dragging of the engine torque during the electric running, which should be performed only by the motor / generator while the engine is stopped, can be prevented.
The sun gear S1 is coupled to the inner rotor 4ri of the first motor / generator MG1 via the hollow shaft 13, and the sun gear S2 is connected to the second motor / generator MG2 via the shaft 14 into which the motor / generator MG1 and the hollow shaft 13 are loosely fitted. To the outer rotor 4ro.
[0016]
In order to make the carrier C an output element for outputting rotation to the wheel drive system as described above, an output gear 16 is connected to the carrier C via a hollow shaft 15 and meshed with a counter gear 17 on the counter shaft 5. Let it. A final drive pinion 18 is separately provided integrally with the counter shaft 5 and meshes with a final drive ring gear 19 provided in the differential gear device 6.
The output rotation from the transmission reaches a differential gear device 6 via a final drive gear set composed of a final drive pinion 18 and a final drive ring gear 19, and is distributed to the tires T as left and right drive wheels by the differential gear device. Shall be.
[0017]
In the hybrid transmission having the above configuration, as described above, the motor / generators MG1 and MG2 are rotated by rotating the engine ENG in the vehicle stopped state, that is, in the stopped state of the rotation of the tire T shown in FIG. May generate electricity. When the vehicle is stopped, the Ravigneaux type planetary gear set 2 stops the revolution of the carrier C finally connected to the tire T, and the pinion gears P1 and P1 supported by the carrier C with the rotation of the sun gears S1 and S2 and the ring gear R1. P2 rotates and the ring gear R2 meshing with the pinion gear P2 also rotates.
[0018]
Therefore, in this embodiment, even in such a stopped state of the vehicle, the lubrication of the pinion gears P1 and P2 supported by the carrier C and the bearing rotatably supporting the ring gear R2 meshing with the pinion gear P2 can be sufficiently performed. In the above, the following carrier support and lubrication structure including the configuration according to the present invention is applied to the hybrid transmission.
[0019]
Here, FIG. 2 is a cross-sectional view showing the carrier support and lubrication structure applied to the hybrid transmission having the above-described configuration in an actual configuration, and FIG. 3 is a partially enlarged cross-sectional view of the actual configuration shown in FIG. In this actual configuration, an input shaft 20 as a rotating member is inserted between the shaft 14 and the engine crankshaft 9, and one end of the input shaft 20 is connected to the engine crankshaft 9, while the input shaft 20 is connected to the input shaft 20. The other end of 20 is connected to shaft 14.
[0020]
Further, in this actual configuration, it is necessary to provide a needle bearing 27 as a bearing for supporting the force in the thrust direction of the input shaft 20 near the inner peripheral end of the fixed wall 21, and the layout shown here is a compact size of the transmission. It is configured to realize the conversion.
[0021]
In this actual configuration, as shown in FIGS. 2 and 3, the upstream-side lubricating oil that allows the lubricating oil flowing from the transmission case 1 to flow radially inward to the fixed wall 21 fixed to the transmission case 1. A road 21a is provided. Further, a radially inner portion of the upstream-side lubricating oil passage 21a is provided with an axial supply oil passage 21b opening on the inner peripheral surface of the fixed wall 21 and an axial direction extending in the axial direction and opening on an end surface of the fixed wall 21. It branches to the lubricating oil passage 21c.
[0022]
The input shaft 20 has a flange 20 a facing the fixed wall 21, and is disposed closer to the center of the transmission than the fixed wall 21. An axial oil passage 20b is provided at the axis of the input shaft 20. The shaft oil passage 20b communicates with a shaft oil passage 14a provided at the shaft center of the shaft 14, and supplies oil for cooling the motor / generators MG1 and MG2 shown in FIG. 1 and lubricating each member. Do. In addition, the input shaft 20 is provided with a first radial lubricating oil passage 20c that transfers lubricating oil from the outside in the radial direction of the input shaft 20 to the axial oil passage 20b. The lubricating oil is guided from the axial supply oil passage 21 b of the fixed wall 21 to the first radial lubricating oil passage 20 c of the input shaft 20 via a bush 22.
[0023]
Further, the input shaft 20 is provided with a carrier communication oil passage 20d and a second radial lubrication oil passage 20e. The carrier communication oil passage 20 d guides the lubricating oil flowing into the thrust bearing 27 disposed in the space 26 to the carrier C. In addition, the second radial lubricating oil passage 20e is formed on the inner peripheral surface near the corner on the fixed wall 21 side formed by the flange 20a and the shaft portion, with the axial oil passage 20b along the axis and the space 26. It is provided in communication. The second radial lubricating oil passage 20e has a flow passage cross-sectional area smaller than that of the first radial lubricating oil passage 20c, so that the flow passage resistance is larger than that of the first radial lubricating oil passage 20c. ing.
[0024]
The carrier C of the Ravigneaux type planetary gear set 2 is provided with a pinion rotation shaft supply oil passage 24 which communicates with the pinion gear lubrication oil passage 23a of the pinion rotation shaft 23 of each pinion gear (long pinion P1, short pinion P2). Lubricating oil is supplied to the roller bearings that rotatably support the pinion gears P1 and P2 from the pinion gear lubricating oil passage 23a of the pinion rotating shaft 23 through the path, and the lubricating oil is supplied to the pinion gears P1 and P2 from there. Note that each pinion rotation shaft 23 is fixed to the carrier C by a pin 28.
On the other hand, lubricating oil is guided from the carrier communication oil passage 20d of the input shaft 20 to the pinion rotation shaft supply oil passage 24 of the carrier C via the bush 25 pressed into the carrier C. The pinion rotation shaft supply oil passage 24 and the bush 25 will be described later in detail.
[0025]
Further, here, the space 26 is defined by the surfaces of the flange 20a extending in the radial direction of the input shaft 20 and the fixed wall 21 that face each other in the axial direction of the input shaft 20, and the space 26 is defined as described above. A needle bearing 27 that supports the force of the input shaft 20 in the thrust direction is provided in a portion near the center of 26. On the other hand, in a portion on the outer peripheral side of the space 26, oil leakage is prevented by a seal of an oil passage for the clutch CL provided on the input shaft 20. The bearing 27 for supporting the thrust force of the input shaft 20 may be a bearing other than a needle bearing.
[0026]
Therefore, according to the carrier supporting and lubricating structure, as shown in FIG. 3, when lubricating the pinion gears P1 and P2 supported by the carrier C, when the input shaft 20 rotates at a low speed, the transmission case 1 moves away from the fixed wall. The oil that has flowed into the upstream-side lubricating oil passage 21a of the 21 flows into the shaft-center supply oil passage 21b and the axial-direction lubricating oil passage 21c as indicated by arrows A1 and A2. The oil flowing into the shaft supply oil passage 21b as shown by the arrow A2 flows from the first radial lubricating oil passage 20c through the bush 22 to the shaft oil passage 20b. As shown, it flows into the shaft oil passage 14a, which is the main oil passage, to cool motor / generators MG1 and MG2 (not shown in FIG. 3) and lubricate each part.
Here, the oil guided from the shaft oil passage 14a and cooling the motor / generators MG1 and MG2 is returned to the oil passage outside the outer periphery of the shaft 14 again to lubricate the members.
[0027]
On the other hand, the oil that has flowed into the axial lubricating oil passage 21c flows from the axial lubricating oil passage 21c through the space 26 into the carrier communication oil passage 20d and the second radial lubricating oil passage 20e of the input shaft 20. . At this time, the lubricating oil flows from the space 26 to the carrier communication oil passage 20d via the inflow from the outside to the inside of the needle bearing 27 disposed in the space 26 as shown by an arrow A4. Further, the oil that has flowed into the carrier communication oil passage 20d flows into the pinion rotation shaft supply oil passage 24 of the carrier C via the bush 25 as shown by an arrow A5, and from there, as shown by an arrow A6. Through the pinion gear lubricating oil passage 23a of the rotating shaft 23, it is supplied to the roller bearings supporting the pinion gears P1 and P2, and further to the pinion gears P1 and P2. The oil flowing from the space 26 into the second radial lubricating oil passage 20e flows into the axial oil passage 20b to cool the motor / generators MG1 and MG2 and lubricate each part in the same manner as described above. Do.
[0028]
Therefore, when the lubricating oil is supplied from the fixed wall 21 to the input shaft 20 at the time of low rotation of the input shaft 20, the lubricating oil is larger than the radially outer portion of the input shaft 20 having the large inflow resistance due to the interposition of the bush 22. The lubricating oil is delivered to the input shaft 20 via the space 26 from the axial lubricating oil passage 21c branched from the upstream side where the supply oil pressure is high, and the pinion gears P1 and P2 are lubricated via the pinion rotation shaft supply oil passage 24 of the carrier C. Therefore, the lubricating oil is supplied to the pinion rotary shaft supply oil passage 24 of the carrier C at a higher lubricating oil supply oil pressure than the shaft oil passage 20b of the input shaft 20. Lubricating oil can be sufficiently supplied to the pinion gear.
[0029]
On the other hand, when the input shaft 20 rotates at a high speed, in the space 26 between the input shaft 20 and the fixed wall 21, as the wall of the input shaft 20 rotates at a high rotation speed, the needle roller of the needle bearing 27 also becomes a half thereof. It rotates at the number of rotations. Therefore, when the input shaft 20 rotates at a high speed, a centrifugal force acts on the oil in the space 26, and there is a possibility that the centrifugal force prevents the inflow of the lubricating oil from the axial lubricating oil passage 21c into the space 26. is there. However, in this case, the oil flowing into the shaft oil passage 20b from the upstream lubricating oil passage 21a via the shaft supply oil passage 21b (including the oil blocked from flowing into the space 26) is subjected to centrifugal force. Accordingly, the oil flows from the shaft center oil passage 20b to the second radial lubrication oil passage 20e. In addition, since the centrifugal force due to the rotation of the input shaft 20 does not act at the time of low rotation, the lubricating oil is less likely to flow into the second radial lubricating oil passage 20e having a larger inflow resistance than the first radial lubricating oil passage 20c. I have.
[0030]
Therefore, according to the carrier supporting and lubricating structure, when the input shaft 20 rotates at a high speed, as shown by the arrow A7, the space 26 extends from the axial oil passage 20b through the second radial lubricating oil passage 20e. The lubricating oil flows into the inside of the needle bearing 27 arranged in the roller bearing, and through the carrier communication oil passage 20d and the pinion rotation shaft supply oil passage 24 of the carrier C as described above, the roller bearings supporting the pinion gears P1 and P2. Is supplied with lubricating oil. As a result, a sufficient amount of lubricating oil is supplied to the pinion rotary shaft supply oil passage 24 of the carrier C, so that even when the input shaft 20 rotates at a high speed, sufficient lubricating oil is supplied to the pinion gears P1 and P2 located above. Can be supplied.
[0031]
Thus, in the carrier supporting and lubricating structure of the hybrid transmission according to the present embodiment, as shown in FIG. 4 and FIG. 5, which is an enlarged view as seen from the direction of arrow D therein, the pinion rotary shaft supply oil passage of carrier C. In particular, a boss portion 29a and a substantially disk-shaped radial extension extending outward from the boss portion 29a in the radial direction and supporting one end portion of the pinion rotary shaft 23 are provided at the end portion (right end portion in the figure) on the 24th side. A pinion rotary shaft support member 29 having a portion 29b is provided, and the pinion rotary shaft support member 29 is disposed such that the boss portion 29a is located outside the radially extending portion 29b in the axial direction of the carrier C (in FIG. And the boss portion 29a is fitted to and supported by the input shaft 20 as an input shaft via the bush 25, and the pinion rotating shaft support member 29 is And it is opposed to the flange 20a of the radially extending portion 29b and the input shaft 20.
[0032]
In this case, the boss portion 29a of the pinion rotation shaft support member 29 having an L-shaped cross section has a radially outward portion of a portion protruding outward in the axial direction of the carrier C with respect to the radially extending portion 29b. A plate 32 for positioning one of the ring gears R1 and R2 in the axial direction is disposed between the opposed radially extending portion 29b and the flange 20a. Needle bearings 30 and 31 are disposed between the plate 32 and the radially extending portion 29b of the pinion rotary shaft support member 29, respectively, and the plate 32 is rotatably moved in the thrust direction (axial direction). We support about.
[0033]
Further, here, a circumferential groove is provided on the inner peripheral surface of the boss portion 29a of the pinion rotary shaft support member 29 of the carrier C to be used as the gallery 24a, and the axially extending portion 29b is connected to the pinion gear P1 from the gallery 24a. , P2 to form the above-described pinion rotation shaft supply oil passage 24, and to cover the end of the oil passage 24b opened to the gallery portion 24a on the inner peripheral surface of the boss portion 29a. The bush 25 having a length substantially matching the thickness (dimension in the axial direction) of the boss portion 29a is tightly fitted by press-fitting, and an oil hole 25a is provided in a central portion of the bush 25 in the axial direction.
[0034]
Therefore, according to the carrier supporting and lubricating structure of the hybrid transmission according to the present embodiment, the pinion rotary shaft supporting member 29 at one axial end of the carrier C extends radially outward from the boss portion 29a. And a boss portion 29a projecting outward from the carrier C in the axial direction with respect to the radially extending portion 29b having a required minimum thickness. The carrier C is supported by the boss 29a having a sufficient width, and a plate 32 as a separate member is arranged outside the carrier C adjacent to the radially extending portion 29b while supporting the one end of the carrier C with the boss 29a having a sufficient width. As a result, space efficiency can be improved, and a compact planetary gear device having a short axial dimension and a compact transmission can be constructed.
[0035]
In particular, according to the carrier supporting and lubricating structure of the hybrid transmission according to the present embodiment, the portion of boss portion 29a projecting outward in the axial direction of carrier C with respect to radially extending portion 29b extends radially outward. Since the plate 32 for positioning the ring gear R2 in the axial direction is disposed, when the teeth of the ring gear R2 are beveled, the plate which can restrict the displacement of the ring gear R2 due to the thrust direction force generated at the time of torque transmission. 32, the planetary gear set and thus the transmission can be made compact in the axial direction. Specifically, the boss portion 29a, the plate 32 and the needle bearings 30, 31 for supporting the plate portion 32 are simply provided on the input shaft 20. According to the above configuration, the dimension in the axial direction can be reduced by about 15 mm as compared with the case where they are arranged in the axial direction. It made.
[0036]
Further, according to this structure, since the ring gear R2 and the input shaft 20 can be driven and coupled by the clutch CL, no relative rotation occurs on both sides of the needle bearing 31 when the clutch CL is engaged, so that the life of the needle bearing 31 is extended. In the other needle bearing 30, when the vehicle advances, the direction of the output rotation of the carrier C and the direction of the engine rotation and, consequently, the direction of the rotation of the input shaft 20 coincide with each other. Therefore, the life can be extended.
[0037]
According to the carrier supporting and lubricating structure of the hybrid transmission according to the present embodiment, a circumferential groove is provided on the inner peripheral surface of boss portion 29a to serve as gallery portion 24a and axially extending portion 29b. An oil passage 24b is provided from the gallery portion 24a to the pinion gears P1 and P2, and the thickness of the boss portion 29a is provided on the inner peripheral surface of the boss portion 29a so as to substantially cover the end of the oil passage 24b opened to the gallery portion 24a. Is closely fitted, and the oil hole 25a is provided at the center of the bush 25 in the axial direction, so that the bush 25 also functions as a lid for the gallery 24a, and the gallery 24a of the carrier C also functions. And prevents the lubricating oil from flowing out of the oil passage 24b more than necessary and leaks slightly from between the bush 25 and the input shaft 20. The lubricating oil can be supplied to the needle bearings 30 and 31, and the lubricating oil supplied from the lubricating oil passage 21 a on the upstream side of the fixed wall 21 is transferred from the carrier communication oil passage 20 d of the input shaft 20 via the bush 25 to the carrier C. The roller bearings that rotatably support the pinion gears P1 and P2 can be supplied stably.
[0038]
As described above, the present invention has been described based on the illustrated examples, but the present invention is not limited to the above examples. For example, in the above-described embodiment, the carrier support structure of the planetary gear device of the present invention is applied to a hybrid transmission. However, the present invention can be applied to other transmissions within the scope of the claims.
[Brief description of the drawings]
FIG. 1 is a schematic configuration diagram illustrating a hybrid transmission to which a carrier support structure of a planetary gear device according to the present invention can be applied.
FIG. 2 is an actual configuration diagram showing a carrier support and lubrication structure of a hybrid transmission as a main part of the present embodiment based on the diagrammatic configuration diagram.
FIG. 3 is a partially enlarged sectional view of the actual configuration diagram shown in FIG. 2;
FIG. 4 is a cross-sectional view showing the carrier and its peripheral portion in the present embodiment shown in FIG.
FIG. 5 is an enlarged view as viewed in the direction of arrow D in FIG. 4;
[Explanation of symbols]
1 Transmission case 2 Ravigneaux type planetary gear set (differential device)
ENG engine (motor)
Reference Signs List 4 combined current two-layer motor MG1 first motor / generator MG2 second motor / generator 7 single pinion planetary gear set 8 double pinion planetary gear set 9 engine crankshaft 14 shaft 14a shaft center oil passage 20 input shaft (rotating member)
20a Flange 20b Axial oil passage 20c First radial lubricating oil passage 20d Carrier communicating oil passage 20e Second radial lubricating oil passage 21 Fixed wall 21a Upstream lubricating oil passage 21b Axial supply oil passage 21c Axial lubricating oil Path 22 Bush 23 Pinion rotation shaft 23a Pinion gear lubrication oil passage 24 Pinion rotation shaft supply oil passage 24a Gallery 24b Oil passage 25 Bush 25a Oil hole 26 Space 27 Needle bearing 28 Pin 29 Pinion rotation shaft support member 29a Boss 29b Radially extending Position 30 Needle bearing 31 Needle bearing 32 Plate S1 Sun gear S2 Sun gear P1 Long pinion P2 Short pinion C Carrier R Ring gear CL Clutch T Tire

Claims (3)

A first ring gear and a second ring gear, a first sun gear and a second sun gear respectively coupled to mutually different rotating elements, a long pinion meshing with the first ring gear and the first sun gear, A short pinion that meshes with the second ring gear and the second sun gear and meshes with the long pinion; and a driving force output element that rotatably supports the long pinion and the short pinion via a pinion rotation shaft, respectively. A planetary gear mechanism having:
An input shaft disposed on the same axis as the first sun gear and the second sun gear and serving as a driving force input element;
A clutch for drivingly coupling one of the first ring gear and the second ring gear to the input shaft;
A planetary gear device comprising: a brake that brakes rotation of the other of the first ring gear and the second ring gear;
A pinion rotation shaft supporting member provided at an axial end of the carrier and having a boss portion and a radially extending portion extending radially outward from the boss portion to support the pinion rotation shaft; Projecting outward in the axial direction of the carrier with respect to the radially extending portion to have an L-shaped cross section,
A carrier support structure for a planetary gear device, wherein the boss portion is supported by being fitted to the input shaft. The carrier support structure for a planetary gear device according to claim 1,
The first ring gear and the first ring gear are disposed radially outward of a portion of the boss portion of the pinion rotation shaft support member having an L-shaped cross section, which protrudes outward in the axial direction of the carrier with respect to the radially extending portion. A carrier supporting structure for a planetary gear device, wherein a plate for positioning one of the second ring gears in the axial direction is arranged. The carrier support structure for a planetary gear device according to claim 1 or 2,
Providing a circumferential groove on the inner peripheral surface of the boss portion of the carrier and making it a gallery portion, and providing an oil passage from the gallery portion to the pinion in the axially extending portion,
A bush having a length corresponding to the thickness of the boss portion is tightly fitted on the inner peripheral surface of the boss portion so as to hide the end of the oil passage opened to the gallery portion, and the axial direction of the bush is set. A carrier support structure for a planetary gear device, characterized in that an oil hole is provided in a central portion.

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