JP2629374B2 - Planetary gear set - Google Patents

Description

Description: TECHNICAL FIELD The present invention relates to a planetary gear device that efficiently lubricates a sun gear and the like.

2. Description of the Related Art A planetary gear device is known as one of mechanisms used as a transmission. Such a planetary gear device is widely used in a vehicle or an industrial machine. In particular, since the speed can be changed relatively smoothly even during power transmission or the size is relatively small, it is often used as an automatic transmission for an automobile. Used, for example,
As shown in JP-A-252857 and JP-A-61-130656, it is also used as an auxiliary transmission of a continuously variable transmission.

In a planetary gear device used as a transmission for a vehicle, lubrication with lubricating oil scattered by a rotating member in a housing of the transmission alone is not sufficient. In particular, the lubricating oil is located at a central portion and a relatively high load is applied. It is desired that the lubricating oil be forcibly supplied to the sun gear.

However, as described above, when a lubricating oil passage is provided in the rotating shaft to forcibly lubricate the sun gear located at the center of the planetary gear device, other oil passages are particularly provided in the rotating shaft. In the case where it is necessary to provide the device, there is a disadvantage that the structure becomes complicated, and the rotating shaft becomes thick and the device becomes large. On the other hand, lubricating oil may be guided or sprayed toward the sun gear to lubricate the vicinity of the sun gear from the outside, but since it is easily blocked by members around the sun gear,
It was difficult and inefficient to actively supply lubricating oil to the sun gear.

SUMMARY OF THE INVENTION The present invention has been made in view of the above circumstances, and an object of the present invention is to provide a planetary gear device that can easily and effectively supply lubricating oil to a sun gear of a planetary gear device. It is in.

Means for Solving the Problems To achieve the above object, the gist of the present invention is to provide a sun gear and a ring gear provided rotatably around one axis, a planetary gear meshing with them, and a planetary gear thereof. A carrier that rotatably supports a gear, an input shaft fitted to the sun gear so as to be relatively non-rotatable, and a clutch drum that slidably fits an annular piston that presses a friction member; and the carrier and the input shaft. (A) a cylindrical coupling member fixed to an inner peripheral portion of the clutch drum and spline-fitted to the input shaft; and (b) a bearing via a bearing. And (c) a support wall provided on the housing for rotatably supporting the input shaft.
A lubricating oil passage for supplying lubricating oil to the inner peripheral side of the cylindrical connecting member so as to travel toward the sun gear along a spline groove between the input shaft and the cylindrical connecting member.

In this manner, the lubricating oil fixed to the inner peripheral portion of the clutch drum and supplied to the inner peripheral side of the cylindrical connecting member that is spline-fitted with the input shaft is supplied to the input shaft. Is sent out to the sun gear side along the spline groove formed on the outer peripheral surface and the inner peripheral surface of the cylindrical coupling member, and in addition to being suitably lubricated, the entire spline fitting portion is further distant in the axial direction. When the lubricating oil is supplied to the sun gear, the sun gear and its vicinity are sufficiently lubricated. As a result, there is no need to provide a lubricating oil passage for lubricating the sun gear in the rotary shaft, and the sun gear of the planetary gear device can be lubricated simply, easily and efficiently.

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

FIG. 1 is a skeleton view showing a power transmission device of a vehicle provided with a planetary gear device according to one embodiment of the present invention. This power transmission device is provided in a lateral transaxle of an FF vehicle. In the figure, the power of the engine 8 is a fluid coupling 10 with a lock-up clutch, a belt-type continuously variable transmission (hereinafter referred to as CVT) 12, an auxiliary transmission (planetary gear unit) 14, a reduction gear unit 16, and a differential gear. The power is transmitted to a drive wheel 21 connected to a drive shaft 20 via the device 18.

The fluid coupling 10 includes a pump impeller 24 connected to the crankshaft 22 of the engine 8, a turbine impeller 28 fixed to the input shaft 26 of the CVT 12 and rotated by oil from the pump impeller 24, and a damper 30. And a lock-up clutch 32 fixed to the input shaft 26 via the input shaft 26. The lock-up clutch 32 is activated when, for example, the vehicle speed, the engine rotation speed, or the rotation speed of the turbine wheel 28 exceeds a predetermined value, and brings the crankshaft 22 and the input shaft 26 into a directly connected state.

The CVT 12 includes variable pulleys 36 and 38 provided on the input shaft 26 and the output shaft 34, respectively, and a transmission belt 40 wound around the variable pulleys 36 and 38. The variable pulleys 36 and 38 are provided on fixed rotating bodies 42 and 44 fixed to the input shaft 26 and the output shaft 34, respectively, and provided on the input shaft 26 and the output shaft 34 so as to be movable in the axial direction and to be relatively unrotatable around the axes. The movable rotators 46 and 48 are moved by the hydraulic cylinders 50 and 52 functioning as hydraulic actuators, so that the V-groove width, that is, the hanging diameter (effective diameter) of the transmission belt 40 is increased. The speed ratio γ of the CVT 12 (= the rotation speed N _in of the input shaft 26 / the rotation speed N _out of the output shaft 34) is changed. The hydraulic cylinder 50 is a so-called double-piston type and is operated exclusively to change the gear ratio γ, and the hydraulic cylinder 52 is exclusively operated so as to obtain the minimum clamping force in a range where the transmission belt 40 does not slip. Can be

The hydraulic pump 54 constitutes a hydraulic power source of a CVT hydraulic control device (not shown), and is always driven to rotate by a pump impeller 24 that rotates together with the engine 8. As the CVT hydraulic control device, for example, all or a part of those described in JP-A-62-9055, JP-A-62-196445, and JP-A-1-49749 are used. Machine 14 is controlled.

The width transmission 14 is a double pinion type planetary gear device that is serially connected to the rear stage of the CVT 12 and that can be selectively switched to a forward gear or a reverse gear according to the operation position of a shift lever (not shown). It is provided coaxially with the output shaft. The planetary gear device includes a sun gear 56 provided integrally with the output shaft 34, a ring gear 58 provided concentrically with the sun gear 56, and a pair of meshes with one and the other of the ring gear 58 and the sun gear 56 and with each other. A boss 64 provided concentrically with the planet gears 60 and 62, the sun gear 56 and the ring gear 58, a flange 66 extending from the boss 64 to the outer peripheral side, and the flange 66
A carrier 70 having a carrier pin 68 protruding from 66 in a direction parallel to the axis of the boss portion 64 and rotatably supporting the pair of planetary gears 60 and 62.

Further, the planetary gear device includes a forward clutch 72 that selectively connects the fixed rotating body 44 of the secondary variable pulley 38 and the carrier 70, and a housing that is fixed in position with the ring gear 58.
74, and a reverse brake 76 for selectively connecting the vehicle with the rear brake 74. Accordingly, when the forward clutch 72 is engaged, the fixed rotating body 44 and the carrier 70 are connected, and the output shaft 34 and the carrier 70 rotate integrally, so that the output shaft 34 and the carrier 70 are concentric with the boss 64 of the carrier 70. Is rotated in the forward direction. When the reverse brake 76 is engaged, the connection between the housing 74 and the ring gear 58 is made non-rotatable, so that the carrier 70 moves in the opposite direction to the output shaft 34, that is, in the reverse direction. And the first gear 78 is rotated. The first gear 78 functions as an output gear of the auxiliary transmission 14.

The second gear 80 and the third gear 82 are integrally connected via a common shaft portion, and are provided rotatably about an axis parallel to the axis of the first gear 78. The second gear 80 is meshed with the first gear 78, and has a larger diameter than the first gear 78. The third gear 82 has a smaller diameter than the second gear 80 and meshes with a large gear 84 of the differential gear device 18.
The first gear 78, the second gear 80, and the third gear 82 function as a reduction gear device.

The differential gear device 18 includes a pair of differential small gears 86 that rotate integrally with the large gear 84, and a pair of differential large gears 88 that mesh with the differential small gear 86 and are connected to the drive shaft 20. Have. Accordingly, the power transmitted from the auxiliary transmission 14 is equally distributed to the left and right drive shafts 20 in the differential gear device 18 and then transmitted to the left and right drive wheels 21.

FIG. 2 is a diagram showing the power transmission device shown in the skeleton view of FIG. 1 in more detail. In the figure, the housing 74
Is, for example, an aluminum die-cast product, and a first case integrally connected to each other by bolts.
74a, a second case 74b, and a third case 74c, a first chamber 90 accommodating the fluid coupling 10, and a CV
The second chamber 92 for housing the T12 and the third chamber for housing the auxiliary transmission 14
A chamber 94 and a fourth chamber 96 for accommodating the reduction gear device 16 and the differential gear device 18 are provided. The bolt 98 shown in the figure fixes the first case 74a and the second case 74b.

The rotor 100 of the hydraulic pump 54 has a gear shape,
It is fitted to the cylindrical part of the pump impeller 24 so as to be relatively rotatable and eccentric. The hydraulic pump case 102 has inner peripheral teeth that mesh with the rotor 100, and the first case 74a
Is fixed to the second case 74b by bolts 104 in a state fitted in a hole 103 formed in a portion corresponding to a partition between the first chamber 90 and the second chamber 92.

An opening 106 is provided in a part of the second case 74b.
An accumulator 110 is fixed to a valve body 108 in which a control valve for controlling the forward clutch 72 and the reverse brake 76 is incorporated by a bolt 107, and the valve body 108 is bolted to an opening edge of the opening 106 by a bolt 112. By being fixed, the accumulator 110 is moved to the second chamber 92.
Housed within. The accumulator 110 includes a bottomed cylindrical main body 114, a piston 116 slidably fitted in the main body 114 to change the internal volume, and a spring 118 for urging the piston 116 in a direction to reduce the internal volume. Have. A valve plate 109 for forming a hydraulic oil passage is fixed to one surface of the valve body 108 by bolts 111, and a cover 113 covering the valve plate 109 is fixed by bolts 112 together.

The accumulator 110 is connected to a hydraulic actuator that drives the forward clutch 72 or the reverse brake 76. The accumulator 110 alleviates an increase in the operating oil pressure supplied by the control valve due to a change in the internal volume, and the forward clutch 72 or the reverse brake 76
The purpose of this is to make the engagement smooth. As described above, since the accumulator 110 is configured separately from the second case 74b, the occurrence of burrows in the second case 74b is suppressed, and the yield of the second case 74b or the accumulator 110 is improved, and Waste meat on the back side of the bottomed cylindrical body 114 is removed. Also accumulator
Since 110 is configured separately from the second case 74b, the second case
The performance of the single unit can be checked in a state where the unit is detached from the case 74b. Further, by being configured as a separate body as described above, the drilling process for fitting the piston 116 into the main body 114 can be easily performed, and the processing station of the second case 74b corresponding to the drilling process can be performed. Becomes unnecessary.

The input shaft 26 of the CVT 12 is rotatably supported on the same axis as the crankshaft 22 by bearings 120 and 122 fitted to the second case 74b and the third case 74c. The output shaft 34 of the CVT 12 has bearings 124 and 12 fitted to the third case 74c and the second case 74b.
6 supports the input shaft 26 so as to be rotatable around an axis parallel to the input shaft 26. On the other hand, the first case 74a has the first gear 7
8, a fourth gear for supporting the second gear 80 and the third gear 82
Case 74d is fixed. The fourth case 74d also corresponds to a partition between the third chamber 94 and the fourth chamber 96. First
The shaft of the gear 78 is fixed to the output shaft by bearings 128 and 130 fitted to the first case 74a and the fourth case 74d.
It is rotatably supported on the same axis as 34. The common shaft of the second gear 80 and the third gear 82 is also provided in the first case.
Bearing 13 fitted to 74a and fourth case 74d
2 and 134, it is rotatably supported about an axis parallel to the first gear 78. The differential case 136 to which the large gear 84 is fixed and the pin for rotatably supporting the differential small gear 86 is fixed includes a first case 74a and a second case 74.
It is rotatably supported by bearings 138 and 140 fitted to b.

The second gear 80 is provided in the fourth chamber 96 of the first case 74a.
A peripheral wall 144 is protruded so as to surround a part of the differential gear device 18 side, and is scraped from the bottom in the fourth chamber 96 with the rotation of the large gear 84, the third gear 82, and the second gear 80. The raised lubricating oil is received by the peripheral wall 144, and a lubricating oil passage 146 for guiding the lubricating oil to the bearing 138 is provided. Thus, the bearing 138 to which a high load is applied is suitably lubricated. The second case 74b has a fourth room 9
A lubricating oil passage 147 is provided for receiving the lubricating oil flowing down on the inner wall surface of No. 6 and guiding it to the bearing 140. Thereby, the bearing 140 is suitably lubricated.

FIG. 3 is a diagram showing the auxiliary transmission 14 and the reduction gear device 16 in detail. In the figure, the second case 74b is connected to the third chamber 94.
The shaft end of the output shaft (that is, the input shaft of the auxiliary transmission 14) 34 penetrated to the side is formed with a small diameter, and a spline shaft portion 148 formed with a plurality of spline teeth is provided therein. ing. Cylinder body provided for forward clutch 72
The cylindrical connecting member 152 and the cylindrical connecting member 152 are integrally connected to each other so as not to rotate relative to each other, and the cylindrical connecting member 152 is spline-fitted to the spline shaft portion 148. An annular piston 154 is slidably fitted to a cylinder body 150 having an annular cylinder bore while being urged by a return spring 155.
The piston 0, the piston 154, the return spring 155, and the like function as a hydraulic actuator for operating the forward clutch 72.

The forward clutch 72 includes a plurality of plates 157 which are non-rotatably and axially movably engaged with an outer peripheral portion of the cylinder body 150, that is, a clutch drum, and a clutch hub fixed to a part of the carrier 70. A plurality of discs 1 which are engaged with the non-rotatable and axially movable parts 159 and are alternately positioned between the plates 157.
61 and a plate 157 and a disc 1
Power is transmitted by the pistons 154 pressing each other 61.

A sleeve 15 is provided in a through hole 156 provided in a part of the second case 74b for allowing the output shaft 34 to pass through to the third chamber 94 side.
8 are integrally fitted, and the cylindrical connecting member 1
A part of 52 is supported by the sleeve 158 and the second case 74b via the bearing 160. This second case 74b
The portion where the through hole 156 is formed functions as a support wall for supporting the output shaft 34. In addition, since the cylindrical connecting member 152 does not need to be centered by the output shaft 34, the spline fitting between the output shaft 34 and the cylindrical connecting member 152 is compared with the normal spline fitting. The clearance in the spline groove is greatly increased.

Further, the hydraulic pressure is supplied to the second case 74b to a pressure chamber formed by the cylinder body 150 and the cylinder 154 through a portion between the outer peripheral surface of the sleeve 158 and the inner peripheral surface of the through hole 156. Forward oil passage 162 is formed. A lubricating oil passage 164 for forcibly supplying lubricating oil to the spline shaft portion 148 is provided in a portion of the second case 74b where the through hole 156 is formed. Through hole 16 forming part of oil passage 164
6 are provided. The lubricating oil passage 164 has a hydraulic pump
A part of the hydraulic oil pumped by 54, for example, a part of the clutch pressure oil supplied to the fluid coupling 10 after the pressure is adjusted to operate the lock-up clutch 32 is supplied.

Incidentally, in the hydraulic actuator for operating the forward clutch 72, the hydraulic oil is supplied to the piston 154 to the pressure chamber, and when the pressure in the pressure chamber is high, the hydraulic oil is prevented from flowing out. A check valve 168 is provided to allow the hydraulic oil to flow out when the hydraulic oil in the pressure chamber is discharged and becomes low, and the disconnection characteristics of the forward clutch 72 are improved.

In the spline shaft portion 148 of the output shaft 34, the sun gear 56 is also spline-fitted adjacent to the cylindrical connecting member 152. The sun gear 5 of this cylindrical connecting member 152
While a cylindrical projection 170 is provided on the side 6, a cylindrical projection 172 is also provided on the side of the cylindrical connecting member 152 of the sun gear 56, and the projections 170 and 172 are relatively rotatable and liquid-tight. Is fitted. As a result, the clearance in spline fitting between the output shaft 34 and the sun gear 56 is larger than usual. On the other hand, the sun gear 56 can be positioned (centered) even before the output shaft 34 is inserted in the assembling step, so that the assembling is facilitated.

In the present embodiment as described above and above, the cylinder body 150 and the cylindrical connecting member 152 are provided via a bearing 160 provided between the inner peripheral surface of the cylindrical connecting member 152 and the outer peripheral surface of the sleeve 158. Since the output shaft 34 is rotatably supported by the second case 74b, the spline fitting between the output shaft 34, the cylindrical connecting member 152, and the sun gear 56 is a loose fitting having a large clearance. Even if the output shaft 34 is bent due to the tension, the cylindrical connecting member 15
2. The occurrence of center runout of the cylinder body 150, the sun gear 56 and the like is eliminated. In the case where the bearing 160 is not provided and a relatively dense spline fitting for centering the cylindrical connecting member 152, the cylinder body 150, the sun gear 56, etc. In such a case, the core runout easily occurs in those members, which causes noise and reduced durability.

In the present embodiment, as described above, the cylindrical connecting member
The lubricating oil passage 164 is formed by fitting the sun gear 56
From the spline shaft in the sleeve 158 through the through hole 166
The lubricating oil supplied to 148 is sent out toward sun gear 56 along the spline groove that is loosely fitted with the spline. Some of the spline teeth of the spline shaft portion 148 are removed as necessary to secure the flow rate of the lubricating oil. The lubricating oil thus sent out passes through the fitting portion with the sun gear 56, and the bearing 17 interposed between the sun gear 56 and the boss portion 64 of the carrier 70.
4 and further flow out to the outer peripheral side through the bearing 174. As a result, the entire spline shaft portion 148 is appropriately lubricated, and in addition to the sun gear 56 and the planetary gears 60 and 62, the ring gear 58, the reverse brake Lubrication such as 76 is effectively performed.

Further, the cylindrical connecting member 152 is provided with a leakage hole 175, and the lubricating oil that has passed through the fitting gap between the bearing 160 and the sleeve 158 and the cylindrical connecting member 152 flows out of the leakage hole 175 by centrifugal force. Spilled to the side and forward clutch 72
Lubrication is performed. In addition, sun gear
The cylindrical projection 172 formed on the 56 also has a leak port 177 for discharging lubricating oil to lubricate the plate 157, the disk 161 and the like of the forward clutch 72. Further, the lubricating oil that has passed through the fitting gap between the output shaft 34 and the sleeve 158 lubricates the bearing 126 to which a high load is applied by supporting the output shaft 34.

The shaft end of the output gear 78 is liquid-tightly fitted to the end of the output shaft 34, and is used to supply hydraulic oil to the hydraulic cylinder 52.
An oil passage 176 that penetrates the axis of the output gear 78 and the output shaft 34 is provided. A spline shaft 178 is also formed at the shaft end of the output gear 78, and the spline shaft 178 is formed.
The boss 64 of the carrier 70 is spline-fitted to the boss. As described above, a plurality of carrier pins 68 are erected on the disk-shaped flange portion 66 extending from one end of the cylindrical boss portion 64 toward the outer peripheral side, and the planetary gears 60 and 62 are provided with the needle bearings 180. And is rotatably supported by a carrier pin 68 via a. The tips of the carrier pins 68 are connected to each other by an annular connecting plate 182.

The planetary gear 60 is rotatably provided around an axis located on the outer peripheral side of the axis of the planetary gear 62, and is meshed with the inner peripheral teeth of the ring gear 58. The ring gear 58 is
The positioning plate 188 fixed to the second case 74b and the flange 66 of the carrier 70 via the sliding washers 184 and 186.
And it is positioned in the axial direction. The reverse brake 76 includes an annular anchor member 190 fixed to the second case 74b, and a plurality of plates 192 provided on the inner peripheral surface of the anchor member 190 so as to be relatively non-rotatable and axially movable. A plate 192 and a plurality of disks 194 alternately provided on the outer peripheral surface of the ring gear 58 so as to be relatively non-rotatable and movable in the axial direction are provided.
The rotation of the ring gear 58 is prevented by the four being pressed against each other. The piston 198 is slidably fitted in an annular cylinder bore 196 formed in the second case 74b, and is returned by a return spring 199. The cylinder 196, the piston 198, the return spring 199, and the like function as a hydraulic actuator for operating the reverse brake 76.

Carrier pins 68 erected on the flange portion 66 include:
A penetrating oil passage 202 is provided which includes a through-hole penetrating in the axial direction and having one end closed by a blind cover 200, and a hole extending from an intermediate portion of the through-hole to the inner peripheral side (the axial center side of the carrier 70). ing. Since the through oil passage 202 is provided from one surface of the flange portion 66 on the first gear 78 side toward the planetary gears 60 and 62 in order to lubricate the inner and outer peripheral portions of the planetary gears 60 and 62. is there.

A cylindrical receiver member 204 is attached to the flange portion 66 of the carrier 70 concentrically with the carrier 70. The receiver member 204 is attached to the boss 64 in the fourth case 74d.
A predetermined play is formed in a hole 206 formed to penetrate the bearing 130, and the tip thereof is mounted on the bearing 130.
, A conical portion 210 having a larger diameter as the distance from the end of the cylindrical portion 208, and a disc-shaped portion 212 extending in the outer peripheral direction from the end of the conical portion 210 are sequentially provided. ,
The disc-shaped portion 212 is fixed to the first gear 78 side of the flange portion 66 and closer to the outer peripheral side than the opening of the through oil passage 202.

In FIG. 2, in order to facilitate understanding,
Although the axes of the input shaft 26 and the output shaft 34, the first gear 78, the second gear 80, the third gear 82, and the drive wheels 20 are shown in a common plane, in reality, as shown in FIG. Are three-dimensionally arranged.

With the above configuration, regardless of whether the vehicle is stopped, in addition to the lubrication oil supplied from the lubricating oil passage 164 being lubricated to each part of the planetary gear device as described above, the receiver member 204 allows the vehicle to travel when the vehicle is running. The lubricating oil lubricates the planetary gears 60 and 62 and the reverse brake 76. That is, while the vehicle is running, the lubricating oil stored in the lower part of the fourth chamber 96 is
The lubricating oil is scraped up along the inner wall surface by 136, reaches the third gear 82 and the second gear 80, and is received by the peripheral wall 144 in a relatively large amount. It is carried to the portion where it meshes with one gear 78. As a result, the lubricating oil flows out of the meshing portion between the outer teeth of the first gear 78 and the outer teeth of the second gear 80. By such a pumping action, the pressure of the lubricating oil is increased at the outer peripheral portion of the first gear 78 surrounded by the first case 74a and the fourth case 74d, and a part of the lubricating oil is It flows out in a direction parallel to the axis, passes through the bearing 130, and is received by the cylindrical receiver member 204. The lubricating oil thus received is guided by the receiver member 204 and reaches the flange portion 66 of the carrier 70 as shown by the arrow in FIG. 60 and 6
2 is supplied to the inner peripheral surface of the sun gear 56 side. As a result, the inner peripheral surfaces of the needle bearing 180 and the planetary gears 60 and 62 are directly lubricated, and the durability of the auxiliary transmission 14 is enhanced. Generally, in order to transmit power smoothly and quietly, a planetary gear device needs to maintain a higher meshing accuracy than a normal transmission, and particularly maintains a high gear accuracy and a high supporting accuracy of each of the planetary gears 60 and 62. It is required to do. The ring gear 58 and the reverse brake 76 are also lubricated by the lubricating oil flowing from the planetary gears 60 and 62 to the outer peripheral side due to the centrifugal force.

 Hereinafter, the operation and effect of the present embodiment will be described.

In the present embodiment, the lubricating oil supplied to the inner peripheral side of the cylindrical connecting member 152 via the lubricating oil passage 164 and the through hole 166 of the sleeve 158 is loosely spline-fitted to the output shaft. The spline shaft 148 is fed out along the spline grooves of the cylindrical connection member 152 and the sun gear 56, and the entire spline shaft portion 148 is suitably lubricated. Further, the lubricating oil is also supplied to a bearing 174 or the like located at a position away from the opening of the lubricating oil passage 164, and the lubricating oil flowing through the bearing 174 causes the sun gear constituting the planetary gear device of the subtransmission 56, the planet gears 60 and 62, the carrier 70, etc. are sufficiently lubricated. As a result, it is not necessary to provide a dedicated lubricating oil passage in the output shaft 34 or the like for guiding the lubricating oil. The present invention provides a planetary gear device that can supply lubricating oil easily, easily, and effectively to a location that needs lubrication at a position away from the lubrication oil.

Further, in the present embodiment, since each part constituting the planetary gear device of the auxiliary transmission 14 is lubricated in advance by the start of the engine 8 before the vehicle starts moving, the load is also reduced by the power transmission accompanying the start. Sufficient lubricity is secured, and durability is enhanced.

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

For example, in the above-described embodiment, the spline fitting between the output shaft 34 and the sun gear 56 has a larger clearance than the normal spline fitting, but this is not always necessary. Even if it is not provided and normal spline fitting is used, a certain effect can be obtained. Further, the flow path of the lubricating oil may be formed only by removing the spline teeth as described above.

Further, in the above-described embodiment, the cylindrical connecting member 152
And output shaft 34 in spline fitting with sun gear 56
Although some of the spline teeth were removed as needed, instead of this, a plurality of oil grooves parallel to the axial direction were formed on the outer peripheral surface of each spline tooth,
The flow cross-sectional area of the lubricating oil may be ensured.

Further, in the above-described embodiment, the second
Although the sleeve 158 is provided between the case 74b and the bearing 160, the sleeve 158 may be provided integrally with the second case 74b, or another alternative to the sleeve 158 may be interposed. Is also good.

Further, in the above-described embodiment, the double pinion type planetary gear device (the auxiliary transmission 14) is described. However, a single pinion type planetary gear device, a planetary gear device having a multi-stage forward gear stage, and the like, The present invention can be applied to other types of planetary gear devices such as an automobile transmission in which a plurality of planetary gear devices are connected.

The above is merely an example of the present invention, and the present invention can be variously modified without departing from the spirit thereof.

[Brief description of the drawings]

FIG. 1 is a skeleton diagram of a power transmission device including one embodiment of the present invention. FIG. 2 is a diagram showing the power transmission device of FIG. 1 in detail. FIG. 3 is an enlarged view for explaining the auxiliary transmission shown in FIG. FIG. 4 is a view showing the arrangement of each element as viewed from the side surface of the housing of FIG. 14: auxiliary transmission (planetary gear) 34: output shaft (input shaft) 56: sun gear 58: ring gear 60,62: planetary gear 70: carrier 72: forward clutch (direct coupling clutch) 74b: second case (support wall) 150: Cylinder body (clutch drum) 152: Cylindrical connecting member 164: Lubricating oil passage

Claims (1)

(57) [Claims] A sun gear and a ring gear rotatably provided about one axis; a planetary gear meshing with the sun gear and a ring gear; a carrier rotatably supporting the planetary gear; A planetary gear device having an input shaft to be engaged and a clutch drum that slidably fits an annular piston that presses a friction member, and a direct connection clutch that directly connects the carrier and the input shaft. A cylindrical connecting member fixed to an inner peripheral portion and spline-fitted to the input shaft; a housing support wall rotatably supporting the input shaft via a bearing; and a housing support wall provided on the housing; Lubrication for supplying lubricating oil to the inner peripheral side of the cylindrical connecting member so as to travel toward the sun gear along a spline groove between the input shaft and the cylindrical connecting member. Planetary gear apparatus characterized by and a road.