JP4677650B2 - Planetary gear device for vehicle - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a planetary gear device provided in a vehicle for transmitting power from a prime mover.
[0002]
[Prior art]
A sun gear provided to be rotatable about one axis, a ring gear provided to be rotatable about an axis common to the sun gear, and a pinion pin parallel to the one axis, and about the one axis. A planetary gear device provided with a carrier member that rotatably supports a pinion that meshes with the sun gear and the ring gear by the pinion pin is provided in a power transmission path of the vehicle. For example, as shown in the “Aristo New Car Guide” (issued on August 27, 1997) issued by the service department of Toyota Motor Corporation, the friction engagement device is used as a component of plural sets of planetary gear devices. And automatic transmissions that switch gears by selectively connecting to each other or connecting to non-rotating members, or "Prius New Car Guide" issued by Toyota Motor Corporation Service Department (issued October 14, 1997) An internal combustion engine and a motor generator by selectively engaging the components of a set of planetary gear devices as described in the above with an internal combustion engine, a motor generator, a transmission, or a housing using a friction engagement device This is the case where it is used in a vehicle power combiner / distributor that combines or distributes the output from the vehicle.
[0003]
[Problems to be solved by the invention]
By the way, in the above planetary gear device for a vehicle, usually, a predetermined amount of lubricating oil is discharged from the lubricating oil passage formed in the shaft located at the shaft center toward the outer peripheral side, so that it is positioned on the outer peripheral side of the shaft. Each gear and the frictional engagement device to be lubricated are lubricated. However, when the vehicle is relatively suddenly started, when the friction engagement device is engaged while being slipped, that is, half-engaged, lubrication is insufficient with the conventional lubrication method. There was a disadvantage that the durability of the planetary gear unit was impaired.
[0004]
The present invention has been made against the background of the above circumstances, and an object of the present invention is to provide a planetary gear type for a vehicle in which sufficient durability can be obtained.
[0005]
[Means for Solving the Problems]
In order to achieve this object, the gist of the present invention is that a carrier that rotatably supports a sun gear, a ring gear, and a pinion meshing with the sun gear is provided in a housing so as to be rotatable around a common axis. A planetary gear device for a vehicle in which a ring gear and a carrier are selectively connected to an input member, an output member, or the housing via a plurality of friction engagement devices, (a) of the plurality of friction engagement devices A lubricating oil passage for supplying lubricating oil directly from the inner peripheral side to a friction member constituting at least one friction engaging device is provided, and (b) friction member is a plurality of plate-like members superimposed to each other in the axial direction, relative of the plurality of plate-like member for accommodating the lubricating oil guided by the lubricating oil passage (c) Cover member having an inner diameter smaller than the inner diameter of the large-径板shaped member to close the axial end of the diameter is formed on the inner peripheral side of the large major径板member lubricant receiving space substantially fluid-tight (D) the lubricating oil containing space is located between the large-diameter plate-like members of the plurality of plate-like members and is relative to the inner diameter of the large-diameter plate-like member. A plurality of small-diameter plate-like members having a small inner diameter and communicated with each other by through holes provided in the small-diameter plate-like member, and (e) the lubricating oil supply side farthest located in sliding contact with the friction member with having said smaller inner diameter than the inner diameter of the large径板member of the frictional member, both the and the cover member and the large-diameter plate-shaped member from in the provision of the flange that forms form the lubricating oil receiving space.
[0006]
【The invention's effect】
In this way, the lubricating oil guided by the lubricating oil passage is directly supplied from the inner peripheral side to the friction member constituting at least one of the plurality of friction engagement devices. Therefore, the friction member is suitably lubricated, and the durability of the friction engagement device, that is, the planetary gear device for a vehicle can be sufficiently obtained. Further, since the lubricating oil storage space formed on the inner peripheral side of the plurality of plate-like members stacked on each other in the axial direction is closed substantially oil-tightly by the seal member, a sufficient amount of lubricating oil is contained in the plate-like member. Directly supplied to the circumferential side.
[0007]
Other aspects of the invention
Here, preferably, the friction engagement device is a brake that selectively connects any of the sun gear, the ring gear, and the carrier to the housing.
[0008]
Preferably, in the planetary gear device for a vehicle, the sun gear is connected to the internal combustion engine, the carrier is connected to the input shaft of the transmission via the first clutch, and the ring gear is connected to the transmission via the second clutch. The lubricant oil is connected to a non-rotating member via a brake and the lubricating oil guided by the lubricating oil passage is supplied to a friction member constituting the brake. In this way, for example, in the friction running mode, it is possible to smoothly generate a relatively large driving force by simultaneously transmitting the outputs of the engine and the motor generator.
[0009]
Preferably, the plurality of plate-like members of the brake include a ring gear-side plate-like member that engages with the outer peripheral surface of the ring gear so as to be movable in the axial direction and relatively non-rotatable around the axis, and a housing. On the other hand, the housing side plate-like members that are movable in the axial direction and engage with each other so as to be relatively non-rotatable around the axial center are overlapped in the axial direction, and the lubricating oil containing space is The ring gear side plate-like member is formed between the outer peripheral surface of the ring gear and the ring gear side plate-like member and the housing side plate-like member, and the seal member is overlapped in the axial direction on the outer peripheral surface of the ring gear. The lubricating oil accommodating space is substantially liquid-tightly sealed at the outer position of the housing side plate member. In this way, the ring gear side plate-like member and the housing side plate-like member that are overlapped with each other in the axial direction are directly lubricated by the lubricating oil stored in the lubricating oil accommodating space.
[0010]
BEST MODE FOR CARRYING OUT THE INVENTION
Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.
[0011]
FIG. 1 is a skeleton diagram illustrating a configuration of a power transmission device of a four-wheel drive vehicle, that is, a front and rear wheel drive vehicle to which the present invention is applied. In this front and rear wheel drive vehicle, a front wheel system is driven by a first drive device having a first prime mover, that is, a main drive device 10, and a rear wheel system is driven by a second drive device having a second prime mover, that is, a sub drive device 12. It is a vehicle of the type which drives.
[0012]
The main drive device 10 includes an engine 14 that is an internal combustion engine that is operated by burning a mixture of air and fuel, and a motor generator (hereinafter referred to as MG) 16 that selectively functions as an electric motor and a generator. And a double pinion type planetary gear unit 18 and a continuously variable transmission 20 whose gear ratio is continuously changed. The engine 14 functions as a first prime mover, that is, a main prime mover. The engine 14 includes a throttle actuator 21 that drives the throttle valve in order to change the opening degree θ _TH of the throttle valve that controls the amount of intake air in the intake pipe.
[0013]
The planetary gear unit 18 is a combining / distributing mechanism that mechanically combines or distributes force, and includes three rotating elements provided so as to be independently rotatable around a common axis, that is, a damper to the engine 14. A sun gear 24 connected via the device 22, a carrier 28 connected to the input shaft 26 of the continuously variable transmission 20 via the first clutch C1 and to the output shaft of the MG 16, and a second clutch C2. And a ring gear 32 that is connected to the input shaft 26 of the continuously variable transmission 20 and connected to a non-rotating member such as the housing 30 via the brake B1. The carrier 28 supports a pair of pinions (planetary gears) 34 and 36 which mesh with the sun gear 24 and the ring gear 32 and mesh with each other so as to be able to rotate. The first clutch C1, the second clutch C2, and the brake B1 are hydraulically engaged when a plurality of overlapping friction plates are pressed by a hydraulic actuator or released by releasing the pressure. This is a friction engagement device.
[0014]
The MG 16 connected to the planetary gear unit 18 and its carrier 28 controls the power generation amount of the MG 16 in the operating state of the engine 14, that is, the rotational state of the sun gear 24, that is, the reaction force that is the rotational driving torque of the MG 16 is successively increased. An electric torque converter (ETC) device that smoothly increases the number of rotations of the ring gear 32 and enables smooth start acceleration of the vehicle by being generated in the carrier 28 so as to increase is configured. At this time, if the gear ratio ρ of the planetary gear unit 18 (the number of teeth of the sun gear 24 / the number of teeth of the ring gear 32) is 0.5, which is a general value, for example, the torque of the ring gear 32: the torque of the carrier 28: the sun gear 24 Torque = 1 / ρ: (1-ρ) / ρ: 1, the torque of the engine 14 is amplified to 1 / ρ times, for example, 2 times, and transmitted to the continuously variable transmission 20. It is called.
[0015]
The continuously variable transmission 20 is wound around a pair of variable pulleys 40 and 42 having variable effective diameters provided on the input shaft 26 and the output shaft 38, respectively, and the pair of variable pulleys 40 and 42. And an endless annular transmission belt 44. The pair of variable pulleys 40 and 42 are input so as to form a V-groove between the fixed rotating bodies 46 and 48 fixed to the input shaft 26 and the output shaft 38, respectively, and the fixed rotating bodies 46 and 48. Movable rotating bodies 50 and 52 that are movable in the axial direction with respect to the shaft 26 and the output shaft 38 and that are not relatively rotatable around the axis, and a variable pulley by applying thrust to the movable rotating bodies 50 and 52 And a pair of hydraulic cylinders 54 and 56 that change the transmission gear ratio γ (= input shaft rotational speed / output shaft rotational speed) by changing the engagement diameter of 40 and 42, that is, the effective diameter.
[0016]
The torque output from the output shaft 38 of the continuously variable transmission 20 is transmitted to the pair of front wheels 66 and 68 via the speed reducer 58, the differential gear device 60, and the pair of axles 62 and 64. It has become. In the present embodiment, a steering device that changes the steering angle of the front wheels 66 and 68 is omitted.
[0017]
The sub-drive device 12 includes a rear motor generator (hereinafter referred to as RMG) 70 that functions as a second prime mover, that is, a sub prime mover, and torque output from the RMG 70 is reduced by a speed reducer 72, a differential gear device 74, and 1 It is transmitted to a pair of rear wheels 80 and 82 via a pair of axles 76 and 78.
[0018]
FIG. 2 is a diagram simply showing the configuration of a hydraulic control circuit for switching the planetary gear unit 18 of the main drive unit 10 to various operation modes. The manual valve 92 mechanically connected to the shift lever 90 that is operated to the P, R, N, D, and B range positions by the driver responds to the operation of the shift lever 90 while using the shuttle valve 93. Then, in the D range, the B range, and the R range, the original pressure output from the oil pump (not shown) is supplied to the first pressure regulating valve 94 that regulates the engagement pressure of the first clutch C1. The original pressure is supplied to the second pressure regulating valve 95 that regulates the engagement pressure of C2, and the original pressure is supplied to the third pressure regulating valve 96 that regulates the engagement pressure of the brake B1 in the N range, the P range, and the R range. The second pressure regulating valve 95 and the third pressure regulating valve 96 control the engagement pressure of the second clutch C2 and the brake B1 in accordance with the output signal from the linear solenoid valve 97 driven by the hybrid control device 104, and the first pressure regulating valve 94. Controls the engagement pressure of the first clutch C <b> 1 according to an output signal from the electromagnetic on-off valve 98 that is a three-way valve that is duty-driven by the hybrid control device 104.
[0019]
FIG. 3 is a cross-sectional view showing the configuration of the power transmission device shown in FIG. In FIG. 3, the housing 30 housing the planetary gear device 18, the continuously variable transmission 20, and the like is used to separate the continuously variable transmission 20 and the planetary gear device 18 at a substantially central portion in the axial direction. An annular partition wall 90 having a relatively large thickness and high rigidity is fixed. If the partition wall 90 is provided at a substantially central portion of the housing 30, the rigidity of the entire housing 30 is increased, so that gear noise and vibration can be suppressed. Further, if the rigidity of the housing 30 is increased, the portion of the housing 30 that supports the variable pulleys 40 and 42 is less likely to be deformed by the tension of the transmission belt 44, so that the durability of the transmission belt 44 is also improved. In this embodiment, the partition wall 90 is fixed to the housing 30 with bolts 92, as shown in FIG. 4, which is a cross-sectional view of the planetary gear unit 18 shown in FIG. Yes.
[0020]
As shown in FIG. 3, the partition wall 90 is provided with a hydraulic oil passage 94 for supplying hydraulic oil to the clutch C2 and a hydraulic oil passage 95 (not shown) for supplying hydraulic oil to the clutch C1. The portion where the hydraulic oil passage 94 is provided is thicker than the other portions.
[0021]
As shown in detail in FIG. 4, the first clutch C <b> 1 includes a first clutch cylinder 96, a first clutch piston 98, a first clutch plate 100, and a first clutch disc 102. An annular first hydraulic oil chamber 104 to which hydraulic oil is supplied from the hydraulic oil passage 95 is formed between the first clutch piston 98.
[0022]
The first clutch plate 100 includes a plurality of fitting protrusions on the outer periphery, and the plurality of fitting protrusions are fitted with a plurality of fitting grooves formed on the inner periphery on the tip side of the first clutch cylinder 96. Thus, the first clutch cylinder 96 is engaged with the first clutch cylinder 96 so as to be relatively movable in the axial direction and non-rotatable around the axial center. Furthermore, a stopper ring 106 is fixed to the distal end side so as not to move in the axial direction, and the first clutch plate 100 is prohibited from further moving toward the distal end side of the first clutch cylinder 96. The first clutch disc 102 has a plurality of fitting projections on the inner periphery, and the fitting projections are arranged in parallel with the first clutch cylinder 96 in a state of being alternately positioned with the first clutch plate 100. By engaging with a plurality of fitting grooves formed in the cylindrical member 108 having a center, the first clutch cylinder 96 is relatively movable in the axial direction and is not relatively rotatable around the axial center. Match.
[0023]
The first clutch cylinder 96 forms a first hydraulic oil chamber 104 together with the first clutch piston 98 slidably fitted in the first clutch cylinder 96, and the central portion in the radial direction is connected to the input shaft 26. The first cylinder member 112 is fixed by welding, and the second cylinder member 114 is fixed to the first cylinder member 112 by welding while being positioned on the outer periphery of the first cylinder member 112. The second cylinder member 114 includes a cylindrical portion 118 parallel to the input shaft 26 and a ring portion 120 provided on the inner side in the vertical direction from the cylindrical portion 118. A plurality of fitting grooves into which the second clutch disk 134, which is a constituent member of the two clutch C2, is fitted are formed. If the 1st clutch cylinder 96 is comprised in this way, the 1st clutch cylinder 96 can be comprised compactly, and can be manufactured at low cost. Note that when the first clutch cylinder 96 is manufactured as a single member by integral press molding, the fitting groove cannot be formed on the ring portion 120 side of the outer peripheral surface, so the axial direction of the first clutch cylinder 96 The length of will become longer.
[0024]
Further, the second cylinder member 114 has an oil receiving passage 122 that opens to the inner peripheral side at predetermined intervals in the circumferential direction by the ring portion 120 being partially welded to the first cylinder member 112 in the circumferential direction. Is formed. The oil receiving path 122 receives lubricating oil scattered from the center side, and the lubricating oil received by the oil receiving path 122 is directly guided to the inner peripheral side of the second clutch C <b> 2 via the lubricating oil hole 123. In other words, the second clutch C2 is efficiently cooled because the second clutch C2 is guided with a different system of lubricating oil from the relatively high temperature lubricating oil that has cooled the first clutch C1.
[0025]
In the first clutch C1 configured as described above, when the hydraulic oil is supplied from the hydraulic oil passage 95 to the hydraulic oil chamber 104, the first clutch cylinder 96 is moved in the axial direction, thereby the first clutch C1. The clutch plate 100 and the first clutch disc 102 are engaged.
[0026]
Further, the second clutch C2 is configured in the same manner as the first clutch C1. Further, at the tips of the plurality of fitting grooves provided on the inner peripheral surface of the second clutch cylinder 124, a connection ring 126 is provided. Since the fitting protrusion provided on the outer periphery is fitted, and the plurality of fitting protrusions formed at the tip of the ring gear 32 are fitted in the fitting groove provided on the inner periphery of the connecting ring 126. The two-clutch cylinder 124 and the ring gear 32 are rotated together. Accordingly, the hydraulic oil is supplied from the hydraulic oil passage 94 to the second hydraulic oil chamber 128, and the second clutch piston 130 causes the plurality of alternately arranged second clutch plates 132 and the second clutch disks 134 to engage with each other. Thus, when the second clutch cylinder 124 and the input shaft 26 are connected, the ring gear 32 and the intermediate shaft 116 are integrally rotated.
[0027]
FIG. 5 is an enlarged sectional view of the brake B1 portion of FIG. The brake B1 includes a plurality of (three in the figure) brake plates 136 that function as housing-side plate-like members, and a plurality (four in the figure) brake disks 138 that function as ring-gear-side plate-like members. 136 and the brake disc 138 are alternately stacked in the axial direction. Each brake plate 136 includes a plurality of fitting protrusions on the outer periphery, and the fitting protrusions are fitted with a plurality of fitting grooves provided on the inner peripheral surface of the housing 30 which is a non-rotating member. Are engaged with each other so as to be relatively movable in the axial direction and not to be rotatable around the axial center.
[0028]
The brake disk 138 includes a plurality of fitting protrusions on the inner periphery, and the fitting protrusions are fitted with a plurality of fitting grooves provided on the outer peripheral surface of the ring gear 32, whereby the center axis with respect to the ring gear 32. Engageable relative to each other and non-rotatably around the axis.
[0029]
Further, on the brake piston 139 side in the axial direction of the brake plate 136, a flange 140 is provided on the outer side where the brake plate 136 and the brake disk 138 are overlapped, and the flange 140 is similar to the brake plate 136 in the housing. It is engaged with 30 so as to be relatively movable in the axial direction and not to be rotatable around the axial center. The gap between the flange 140 and the ring gear 32 is narrower than that between the brake plate 136 and the ring gear 32. A brake cover 142 is provided on the outer side opposite to the flange 140 of the outer side where the brake plate 136 and the brake disc 138 are overlapped, and the packing plate 144 is provided on the brake disc 138 side of the brake cover 142. Is fixed.
[0030]
The lubricant storage space 146 is formed on the outer peripheral surface of the brake plate 136, the brake disc 138, and the ring gear 32, the outer peripheral surface of the packing plate 144, the brake disc 138, and the ring gear 32, or the outer peripheral surface of the flange 140, the brake plate 136, and the ring gear 32. The lubricating oil storage spaces 146 are communicated with each other through a through hole 148 provided in the brake disk 138. Lubricating oil is directly supplied to the plurality of lubricating oil storage spaces 146 from a valve body (lubricating oil supply source) (not shown) by an electric pump through a lubricating oil passage 150 provided inside the housing 30 and the brake cover 142. To be supplied.
[0031]
Further, a sleeve 154 and a seal ring 156 are provided between the lubricating oil supply port 152 of the lubricating oil passage 150 and the ring gear 32, and the lubricating oil accommodation space 146 is sealed on the lubricating oil supply port 152 side. . Further, since the gap between the flange 140 located on the side farthest from the lubricating oil supply port 152 and the ring gear 32 is narrowed, the lubricating oil accommodation space 146 is closed substantially liquid-tight as a whole. That is, the sleeve 154, the seal ring 156, and the flange 140 function as seal members, and the lubricating oil from the lubricating oil passage 150 is efficiently stored in the lubricating oil storage space 146.
[0032]
When the lubricating oil is introduced into the lubricating oil accommodating space 146, the lubricating oil is sent radially outward by centrifugal force, so that the lubricating oil is sufficiently supplied between the brake plate 136 and the brake disc 138. Accordingly, when the hydraulic oil is supplied to the third hydraulic oil chamber 158 shown in FIG. 4 and the brake piston 139 is moved against the force of the spring 160, the brake plate 136 and the brake disc 138 are half-engaged. In addition, since the half-engagement is achieved smoothly, the driving force can be generated smoothly, and the brake plate 136 and the brake disc 138 are prevented from seizing.
[0033]
As described above, according to the present embodiment, the lubricating oil guided by the lubricating oil passage 150 is directly supplied from the inner peripheral side to the brake plate 136 and the brake disc 138 constituting the brake B1. The brake plate 136 and the brake disc 138 are preferably lubricated, and the durability of the planetary gear unit 18 can be sufficiently obtained.
[0034]
Further, according to the present embodiment, the lubricating oil accommodating space 146 formed on the inner peripheral side of the brake plate 136 and the brake disc 138 that are overlapped with each other in the axial direction is substantially oiled by the sleeve 154, the seal ring 156, and the flange 140. Since it is closed tightly, a sufficient amount of lubricating oil is supplied directly to the inner peripheral side of the brake plate 136 and the brake disc 138.
[0035]
Further, according to this embodiment, the sun gear 24 is connected to the engine 14, the carrier 28 is connected to the input shaft 26 of the continuously variable transmission 20 via the first clutch C1, and the ring gear 32 is connected to the second clutch C2. The lubricating oil is connected to the input shaft 26 of the continuously variable transmission 20 and to the housing 30 via the brake B1, and the lubricating oil guided by the lubricating oil passage 150 is a brake plate 136 constituting the brake B1. And the brake disc 138, in particular, in the friction running mode in which the brake B1 is frictionally engaged (slip engaged) when the engine 14 and the MG 16 are operated simultaneously in the R range. 14 and MG16 outputs are simultaneously transmitted to generate a relatively large driving force smoothly. Theft is possible.
[0036]
As mentioned above, although one Example of this invention was described based on drawing, this invention is applied also in another aspect.
[0037]
For example, in the above-described embodiment, the lubricating oil passage 150 for supplying the lubricating oil directly from the inner peripheral side is provided in the brake plate 136 and the brake disc 138 of the brake B1, but other friction members (for example, A lubricating oil passage for supplying lubricating oil directly from the inner peripheral side to the first clutch C1 or the friction member of the second clutch C2 may be provided.
[0038]
In the above-described embodiment, the partition wall 90 is a separate member from the housing 30 and is fixed to the housing 30 by the bolt 92. However, the housing 30 may be integrally formed as a shape having the partition wall 90. That is, the partition wall 90 may be a part of the housing 30.
[0039]
In the above-described embodiment, the sleeve 154 and the seal ring 156 are provided as the sealing member on the lubricating oil supply port 150 side, and the flange 140 is provided as the sealing member on the side opposite to the lubricating oil supply port 150. Even if the seal member is provided on only one of them, a temporary effect can be obtained. Therefore, the seal member may be provided only on one side.
[0040]
As mentioned above, although the Example of this invention was described in detail based on drawing, this is an embodiment to the last, and this invention implements in the aspect which added various change and improvement based on the knowledge of those skilled in the art. Can do.
[Brief description of the drawings]
FIG. 1 is a skeleton diagram illustrating a configuration of a power transmission device for a four-wheel drive vehicle including a double pinion type planetary gear device according to an embodiment of the present invention.
FIG. 2 is a diagram for explaining a main part of a hydraulic control circuit that controls the planetary gear device of FIG. 1;
3 is a cross-sectional view showing a configuration of the power transmission device of FIG. 1;
4 is a cross-sectional view of the planetary gear device portion of FIG. 3 cut along a cross section different from that of FIG. 3;
5 is an enlarged cross-sectional view of a portion of a brake B1 in FIG.
[Explanation of symbols]
18: planetary gear device 24: sun gear 28: carrier 30: housing 32: ring gear 34: pinion, 36: pinion C1: first clutch (friction engagement device)
C2: Second clutch (friction engagement device)
B1: Brake (friction engagement device)
136: Brake plate (friction member)
138: Brake disc (friction member)
140: Flange (seal member)
146: Lubricating oil storage space 150: Lubricating oil passage 154: Sleeve (seal member)
156: Seal ring (seal member)

Claims (5)

In the housing, a sun gear, a ring gear, and a carrier that rotatably supports a pinion that meshes with the sun gear are rotatably provided around a common axis, and the sun gear, the ring gear, and the carrier are input members via a plurality of friction engagement devices. In the planetary gear device for a vehicle that is selectively connected to the output member or the housing,
Of the friction member constituting at least one frictional engagement device of the plurality of frictional engagement devices, which provided a lubricating oil passage for supplying directly to the lubricating oil from the inner circumferential side ,
The friction member of the friction engagement device is a plurality of plate-like members stacked on each other in the axial direction,
The axial direction of the lubricating oil storage space formed on the inner peripheral side of the large-diameter plate-shaped member having a relatively large inner diameter among the plurality of plate-shaped members in order to store the lubricating oil guided by the lubricating oil passage A cover member having an inner diameter smaller than the inner diameter of the large-diameter plate member is provided to close one end of
The lubricating oil accommodating space is located between the large-diameter plate members of the plurality of plate-like members, and has a small-diameter plate-like member having an inner diameter relatively smaller than the inner diameter of the large-diameter plate-like member. Are formed by being divided into two, and communicated with each other through a through hole provided in the small-diameter plate member,
Has the inner diameter smaller inner diameter than the large径板member of the friction members with sliding contact with the said friction member located farthest from the supply side of the lubricating oil, the cover member and the large-diameter planetary gear device for a vehicle, characterized in that provided a flange that both forms form the lubricating oil receiving space between the plate-like member.   The planetary gear unit for a vehicle according to claim 1, wherein the friction engagement device is a brake that selectively connects any one of the sun gear, a ring gear, and a carrier to the housing. A plurality of plate-like members overlapped with each other in the axial direction of the friction engagement device includes a brake plate that is movable in the axial direction with respect to the housing and non-rotatably engaged with the housing, and a shaft with respect to the ring gear. A brake disc that is movable in the center direction and is relatively non-rotatable.
  The flange engages with the housing so as to be axially movable and relatively non-rotatable, and overlaps the brake disc together with the brake plate,
  The planetary gear device for a vehicle according to claim 1 or 2, wherein a gap between the flange and the ring gear is smaller than a gap between the brake plate and the ring gear. A brake cover fixed to the housing is provided at an outer position where the brake plate and the brake disc are overlapped and at a position opposite to the flange,
  Lubricating oil is supplied to the lubricating oil storage space via a lubricating oil passage formed in the housing and the brake cover and a lubricating oil supply port formed on the lubricating oil storage space side of the brake cover. The planetary gear device for a vehicle according to claim 3. The vehicle according to claim 4, wherein a seal ring is provided between an inner peripheral portion of the brake cover and an outer peripheral portion of the ring gear, and the brake cover side of the lubricating oil accommodating space is closed in a liquid-tight manner. Planetary gear unit for use.

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