JPH0221052A - Epicycle gear device - Google Patents

Abstract

PURPOSE:To locate the core position of a triple gear with high accuracy and simplify the assembly work by supporting a rotary shaft side rotor rotatable with housing, and forming a structure that the rotary shaft side rotor and the triple gear are engaged mutually. CONSTITUTION:A cylinder shape projection 170 provided projectingly on the side of a triple gear 56 of a connecting member 152 is fitted relatively rotatable into a cylinder shape projection 172 provided projectingly in the connecting member 152 of the triple gear 56. For this reason, the triple gear 56 is supported rotatable by the second case 74b of the housing via the connecting member 152 and a bearing 160 so as to be cored with high accuracy. At the time of assembly, when a carrier 70 is combined concentric with the triple gear 56 engaged on the shaft end of an output shaft 34, a ring projection of a thrust bearing installed in the holl of the carrier 70 is easily fitted into the holl of the triple gear 56 so as to facilitate the assembly work.

Description

DETAILED DESCRIPTION OF THE INVENTION Field of the Invention The present invention relates to a technique for improving durability caused by eccentricity of a sun gear of a planetary gear system.

Conventional technology Planetary gear devices are widely used in vehicles and industrial machinery, and are particularly useful as automatic transmissions for automobiles because they can shift relatively smoothly even during power transmission and are relatively compact. are also widely used, and are also used as sub-transmissions of continuously variable transmissions, as shown in, for example, Japanese Patent Application Laid-open No. 60-252857 and Japanese Patent Application Laid-open No. 61130656.

A type of 'tI star gear device as described above includes a rotating shaft on which spline teeth are formed, a sun gear that is spline-fitted to the shaft end of the rotating shaft so as not to be relatively rotatable, and meshing with the sun gear. A carrier that rotatably supports a planetary gear, a ring gear that meshes with the planetary gear, and a clutch provided between the rotating shaft and the carrier, and power is transmitted between the rotating shaft and the carrier. Type % Formula % Problems to be Solved by the Invention By the way, in the planetary gear device of the above type, the clutch that connects the rotating shaft and the carrier is supported by a rotating shaft-side rotating body that rotates together with the rotating shaft on the shell. and a friction member supported by a carrier-side rotary body that rotates together with the carrier, and the rotary shaft-side rotary body is adjacent to a non-shaft end side of the sun gear. The rotary shaft is spline-fitted to the rotating shaft.

However, normally, a gap is formed in the spline fitting between the sun gear and the rotating shaft to create a predetermined play, making it impossible to obtain relative positional accuracy in the direction perpendicular to the axis between the sun gear and the rotating shaft. , there were various inconveniences. For example, when assembling, the rotating body on the rotating shaft side of the clutch and the sun gear are spline-fitted to the rotating shaft, and then the thrust bearing is interposed between the boss portion of the carrier and the sun gear, and the rotating body is fitted onto the shaft end of the rotating shaft. When assembling the carrier concentrically with the sun gear, when fitting the annular protrusion of the thrust bearing pre-attached to one of the sun gear and carrier into the other of the sun gear and carrier, the core of the sun gear does not protrude, causing the assembly to fail. The work was extremely difficult. In addition, when lubricating oil is fed toward the shaft end of the rotating shaft along the tooth traces of the spline part, the lubricating oil is released from between the rotating body on the rotating shaft side and the sun gear. There was a drawback that the thrust bearing was not sufficiently lubricated.

The present invention has been made against the background of the above circumstances,
The purpose is to provide a planetary gear device in which the core position of the sun gear is positioned with high precision.

Means for Solving the Problems In order to achieve the above object, the gist of the present invention is to provide a rotary shaft having spline teeth formed thereon, and a shaft end portion of the rotary shaft that is spline-fitted in a manner that prevents relative rotation. a carrier that rotatably supports a planetary gear that meshes with the sun gear; a ring gear that meshes with the planetary gear; a friction member supported by a rotating shaft-side rotating body that rotates with the rotating shaft; and a friction member that rotates with the carrier. A clutch is provided that connects the rotating shaft and the carrier by frictionally engaging a friction member supported by the carrier-side rotating body, and the rotating shaft-side rotating body of the clutch is connected to the non-shaft end side of the sun gear. In a planetary gear device spline-fitted to the rotating shaft in a state adjacent to the rotating shaft, the rotating body on the rotating shaft side is rotatably supported by a housing, and the rotating body on the rotating shaft side and the sun gear are mutually connected. It's because they fit together.

In this way, the rotary shaft-side rotary body of the clutch that rotates with the rotary shaft is rotatably supported by the housing, and the rotary shaft-side rotary body and the sun gear are fitted into each other. Therefore, the sun gear is supported in a concentric position with high precision by the housing via the rotating body on the rotating shaft side. For this reason, when assembling, the rotating body of the clutch on the rotating shaft side and the sun gear are spline-fitted to the rotating shaft, and then, while interposing a thrust hair ring between the 71ζ space part of the carrier and the sun gear, When assembling the carrier concentrically with the sun gear fitted at the end,
The annular protrusion of the thrust ring previously attached to one of the sun gear and the carrier can be easily fitted into the other of the sun gear and the carrier, simplifying the assembly work. In addition, when lubricating oil is supplied to the shaft end side of the rotating shaft along the tooth traces of the spline teeth, the lubricating oil released from between the connecting member and the sun gear can be easily restricted. The bearings are sufficiently lubricated and the durability of the planetary gear is increased.

EXAMPLE Hereinafter, an example of the present invention will be described in detail based on the drawings.

FIG. 2 is a schematic diagram showing a power transmission device for a vehicle equipped with a planetary gear device according to an embodiment of the present invention.

This power transmission device is installed in a transverse transaxle of a front-wheel drive vehicle. In the figure, the power of the engine 8 is powered by a fluid coupling I with a lock-up clutch.
O, belt type continuously variable transmission (hereinafter referred to as CVT) 12,
The signal is transmitted to the drive wheels 21 connected to the drive shaft 20 via the sub-shift [14], the reduction gear device 16, and the differential gear device 18.

A pump impeller 24 connected to the fluid cambling crank shaft 22 and a CV
The turbine wheel 28 includes a turbine wheel 28 fixed to the input shaft 26 of the T 12 and rotated by oil from the pump wheel 24, and a lock-up clutch 32 fixed to the input shaft 26 via a damper 30.

The lock-up clutch 32 is activated when, for example, the vehicle speed, the engine rotational speed, or the rotational speed of the turbine wheel 28 exceeds a predetermined value, and connects the crankshaft 22 and the input shaft 26 directly.

The CVT 12 includes variable pulleys 36 and 38 provided on the human power shaft 26 and the output shaft 34, respectively, and a power transmission belt 40 wound around the variable pulleys 36 and 38. The variable pulleys 36 and 38 are connected to the human power shaft 2.
6 and the fixed rotating body 4 fixed to the output shaft 34, respectively.
2 and 44, and movable rotary bodies 46 and 48, which are provided on the human power shaft 26 and the output shaft 34, respectively, so as to be movable in the axial direction but not relatively rotatable about the axes. By being moved by the functioning hydraulic cylinders 50 and 52, the groove width, that is, the hanging diameter (effective diameter) of the transmission belt 40 is changed, and the transmission ratio T of the CVTI 2 (-human power shaft 26) is changed.
The rotational speed N. n/output rotation speed N. )
is about to change. The hydraulic cylinder 50 is of a so-called double piston type and is operated exclusively to change the gear ratio T, and the hydraulic cylinder 52 is operated exclusively to obtain the minimum clamping force within a range where the transmission belt 40 does not slip. It will be done. The hydraulic pump 54 constitutes a hydraulic power source of a CVT hydraulic control device (not shown), and is constantly driven to rotate by a pump impeller 24 that rotates together with the engine 8. - Riki CV
As the T hydraulic control device, for example, JP-A-62-90
No. 55, Japanese Patent Application Publication No. 196445/1983, and Japanese Patent Application No. 1983
The CVT 12 and the auxiliary transmission [14] are controlled by using all or part of what is described in No. 2208781.

The sub-transmission 14 is a double-binion type planetary gear device connected in series to the rear stage of the CVT 12 and selectively switched to a forward gear or a reverse gear A/speed according to the operation position of a shift lever (not shown). It is provided coaxially with the output shaft 34 of. This 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,
A pair of planetary gears 60 that mesh with one and the other of the ring gear 58 and sun gear 56 and mesh with each other.
and 62, a boss portion 64 provided concentrically with the sun gear 56 and ring gear 58, a flange portion 66 extending from the boss portion 64 toward the outer periphery, and a flange portion 66 protruding from the flange portion 66 in a direction parallel to the axis of the boss portion 64. A pair of 't'
A carrier 70 having a carrier bin 68 rotatably supporting the single star gears 60 and 62 is provided. Further, this planetary gear device includes a forward clutch 72 that selectively connects between the fixed rotating body 44 of the secondary variable pulley 38 and the carrier 70, and a forward clutch 72 that selectively connects between the ring gear 58 and the housing 74 that is fixed in position. The rear brake 76 is connected to the reverse brake 76. Therefore, 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 they are concentric with the boss portion 64 of the carrier 70. The first gear 78 connected to is rotated in the forward direction. Further, when the reverse brake 76 is engaged, the housing 7
4 and the ring gear 58 are connected, and the ring gear 58
is in a non-rotating state, so the direction opposite to the output shaft 34,
That is, the carrier 70 and the first gear 78 are rotated in the reverse direction. This first gear 7°8 functions as an output gear of the sub-transmission 14.

The second gear 80 and the third gear 82 are integrally connected via a common shaft, and are rotatably provided around an axis parallel to the axis of the first gear 78. Second gear 8
0 is meshed with the first gear 78, and the first gear 7
It has a larger diameter than 8.

The third gear 82 has a smaller diameter than the second gear 80, and is meshed with the large gear 84 of the differential gear device I8. The first gear 78, the second gear 80, and the third gear 82 are
It functions as a reduction gear.

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 gears 86 and are connected to the drive shaft 20. We are prepared. Therefore, the power transmitted from the sub-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. 3 is a diagram showing the power transmission device shown in the schematic diagram of FIG. 2 in more detail. In the figure, the housing 74 is, for example, an aluminum die-cast product,
First cases 74 integrally connected to each other by bolts
a, a second case 74b, and a third gauge 74c, and a first chamber 9 that accommodates the fluid coupling 10.
0, the second chamber 92 that accommodates the CVT 12, and the sub-transmission 1.
4, and a fourth chamber 96 that accommodates the reduction gear group 7716 and the differential gear unit 18. The bolt 98 shown in the figure is attached to the first case 74.
a and the second case 74b are fixed.

The rotor 100 of the hydraulic pump 54 has a gear shape, and is fitted into the cylindrical portion of the pump impeller 24 in a relatively rotatable and eccentric manner. The hydraulic pump case 102 is
The rotor 100 has internal teeth that mesh with the rotor 100, and the first
It is fixed to the second case 74b with a bolt 104 while being fitted into a hole 103 formed in a portion corresponding to a partition wall between the first chamber 90 and the second chamber 92 of the case 74a.

An opening 106 is provided in a part of the second case 74b. An accumulator 110 is fixed to a valve body 108 incorporating a control valve for controlling the forward clutch 72 and the reverse brake 76 with bolts 107, and the valve body 108 is attached to the opening edge of the opening 106 by a pole 112. The accumulator 110 is housed in the second chamber 92 by being fixed to the second chamber 92 . The accumulator 110 includes a bottomed cylindrical main body 114, a piston 116 that is slidably fitted into the main body 114 to change the internal volume, and a spring 118 that biases the piston 116 in a direction to reduce the internal volume. We are prepared. A valve plate 109 for forming a hydraulic oil passage is fixed to one surface of the valve body 108 by a pole 111, and a cover 113 covering it is fixed by tightening together with the bolts 112. The accumulator 110 is connected to a hydraulic actuator that drives the forward clutch 72 or the reverse brake 76, and reduces the increase in the hydraulic pressure supplied by the control valve due to a change in internal volume.
This is to ensure smooth engagement. As described above, since the accumulator 110 is configured separately from the second case 74b, the generation of holes in the second case 74b is suppressed, and the yield of the second case 74b or the accumulator 110 is improved. Wasted meat on the back side of the bottomed cylindrical main body 114 is removed. Also,
Since the accumulator 110 is constructed separately from the second case 74b, the performance of the accumulator 110 can be checked as a standalone unit while being removed from the second case 74b. Furthermore, by being configured as a separate body as described above, it is possible to easily perform the drilling process for fitting the piston 116 into the main body 114, and the second case 74b corresponding to the drilling process can be easily performed. One processing station is not required.

The input shaft 26 of the CVT 12 has a bearing 120 fitted into the second case 74b and the third case 74c.
and 122, it is rotatably supported on the same axis as the crankshaft 22. Output shaft 3 of CVT12
4 is rotatably supported around an axis parallel to the input shaft 26 by bearings 124 and 126 fitted in the third case 74c and the second case 74b.

On the other hand, the first case 74a includes a fourth case 7 for supporting the first gear 78, the second gear 80, and the third gear 82.
4d is fixed. This fourth case 74d also corresponds to a partition wall between the third chamber 94 and the fourth chamber 96. The shaft portion of the first gear 78 has hair rings 128 and 13 fitted into the first case 74a and the fourth case 74d.
0, it is rotatably supported on the same axis as the output shaft 34. Further, the common shaft portion of the second gear 80 and the third gear 82 is also connected to the first case 74a and the fourth case 74d.
The first gear 78 is supported rotatably about an axis parallel to the first gear 78 by bearings 132 and 134 fitted therein. The differential case 136 to which the large gear 84 is fixed and a pin rotatably supporting the differential small gear 86 is fixed includes a first case 74a and a second case 74b.
It is rotatably supported by bearings 138 and 140 fitted in the. Note that the first case 74a includes a peripheral wall 144 that receives lubricating oil scraped up from the bottom of the fourth chamber 96 as the large gear 84, third gear 82, and second gear 80 rotate; Lubricating oil passage 146 for guiding received lubricating oil to bearing 138
is provided.

FIG. 1 is a diagram showing the sub-transmission 14 and the reduction gear device 16 in detail. In the figure, the shaft end of the output shaft 34 that is passed through from the second case 74b to the third chamber 94 side is formed to have a small diameter, and a spline shaft portion 148 in which a plurality of spline teeth are formed is provided there. It is being A cylinder body having an annular cylinder bore, that is, a clutch drum 150 is integrally fixed to a cylindrical connecting member 152 that is spline-fitted to the spline shaft portion 148. An annular piston 154 is slidably fitted. Clutch drum 150, piston 154, return spring 1
55 and the like function as a hydraulic actuator for operating the forward cruncher 2.

The forward clutch 72 includes a plurality of annular plates 157 that are engaged with the outer circumference of the clutch drum 150 so as to be non-rotatable and movable in the axial direction, and a clutch hub 159 that is fixed to a part of the carrier 70. The plate 1 is engaged in a relatively non-rotatable and axially movable manner.
57 and a plurality of annular disks 161 alternately positioned between the plates 157 and the disks 161, and when the plates 157 and the disks 161 are pressed against each other by the piston 154, power is transmitted. In this embodiment, the plate 157 and the disk 161 respectively correspond to the friction members of the forward clutch 72, and the clutch drum 150 and the connecting member 152 correspond to the plate 1.
The clutch hub 159 corresponds to a carrier-side rotating body that supports the disk 161, and the clutch hub 159 corresponds to a carrier-side rotating body that supports the disk 161.

In order to pass the output shaft 34 to the third chamber 94 side, a second
A sleeve 158 is fitted into a through hole 156 provided in the case 74b, and the connecting member 152 and the clutch drum 150 fixed thereto are supported by the inner peripheral surface of the sleeve 158 via a hair ring 160. At the same time, the cylinder body 1 is inserted between a part of the outer peripheral surface of this sleeve 158 and the inner peripheral surface of the through hole 156.
A forward oil passage 162 is formed for supplying hydraulic pressure to a pressure chamber formed by the cylinder 150 and the cylinder 154. The sleeve 158 also includes a spline shaft portion 1.
A through hole 166 is provided that forms a part of a lubricating oil passage 164 that forcibly supplies lubricating oil to 4B. A portion of the hydraulic oil pumped by the hydraulic pump 54 is supplied to the lubricating oil passage 164, and the pressure is regulated to operate the lock-up clutch 32.
A part of the clutch pressure oil is supplied to the clutch.

In the hydraulic actuator for operating the forward clutch 72, the piston 154 is supplied with hydraulic pressure to the pressure chamber and prevents hydraulic oil from flowing out when the pressure inside the pressure chamber is high. A check valve 168 is provided that allows the hydraulic oil to flow out when the pressure of the hydraulic oil in the pressure chamber is exhausted and becomes low, thereby improving the disengagement characteristics of the forward clutch 72.

A sun gear 56 is also spline-fitted to the shaft end of the output shaft 34 (spline shaft portion 148) in a state adjacent to the connecting member 152. A cylindrical protrusion 170 is provided on the sun gear 56 side of the rotor connecting member 152,
A cylindrical projection 17 is also provided on the connecting member 152 side of the sun gear 56.
2 are provided, and these protrusions 170 and 172 are relatively rotatably and liquid-tightly fitted. This results in
Sun gear 56 includes connecting member 152 and bearing 16
Since it is rotatably supported by the second case 74b of the housing 74 via the second case 74b, it is centered with high precision.

Further, by fitting the protrusions 17O and 172 as described above, the lubricating oil passage 164 is connected to the spline shaft portion 14.
The lubricating oil fed along the tooth traces of No. 8 passes through the fitting part with the sun gear 56 and is inserted into the thrust bearing 174 interposed between the sun gear 56 and the boss part 64 of the carrier 70.
It is designed so that it can flow out to the outer circumferential side through. Note that a small number of spline teeth may be removed when lubricating oil is fed along the tooth traces of the spline shaft portion 148. As a result of the above, in addition to the lubrication of the spline shaft portion 14B, the lubricating oil flowing out to the outer circumferential side through the bearing 174 is used to lubricate the sun gear 56 and the planetary gear 60 located on the outer circumferential side thereof.
．． 62, ring gear 58, reverse brake 76, etc. are lubricated. The connecting member 152 also has a leak hole 175.
is provided so that the lubricating oil that has passed through the fitting gap between the bearing 160 and the sleeve 158 and the connecting member 152 flows out from the leakage hole 175 to the outer circumferential side by centrifugal force, thereby lubricating the forward clutch 72. It has become. Furthermore, a cylindrical projection 17 formed on the sun gear 56
2 is also provided with a leak port 177 to lubricate the forward clutch 72.

The shaft end of the output gear 78 is fluid-tightly fitted to the end of the output shaft 34 , and an oil passage passing through the shaft center of the output gear 78 and the output shaft 34 is used to supply hydraulic oil to the hydraulic cylinder 52 . A passage 176 is provided.

Also, a spline shaft portion 17B is also provided at the shaft end of the output gear 78.
is formed, and the boss portion 64 of the carrier 70 is spline-fitted into the spline shaft portion 178.

As mentioned 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 circumference, and the planetary gears 60 and 62 are connected to the needle. Carrier pin 6 via bearing 180
It is rotatably supported by 8. The distal ends of these carrier pins 68 are connected to each other by an annular connecting plate 1B2.

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 meshes with the inner teeth of the ring gear 58. ring gear 5
8 through sliding washers 184 and 186.
It is positioned in the axial direction by being sandwiched between a positioning plate 188 fixed to the case 74b and the flange portion 66 of the carrier 70. The reverse brake 76 includes an annular anchor member 190 fixed to the second case 74b;
A plurality of plates 19 are provided on the inner peripheral surface of this anchor member 190 so as to be relatively non-rotatable and movable in the axial direction.
2, and a plurality of disks 194 that are non-rotatable and movable in the axial direction on the outer peripheral surface of the ring gear 58 and are provided alternately with the plates 192, and the pistons 198 cause the plates 192 and the disks 194 to mutually move. Rotation of the ring gear 58 is prevented by being pressed. The piston 19B is slidably fitted into an annular cylinder pore 196 formed in the second case 74b, and is returned by a return spring 199. The above cylinder 196, piston 19
8. Return spring 199 etc. are reverse brake 7
This corresponds to the hydraulic actuator that operates 6.

The carrier pin 68 erected in the flange portion 66 includes a through hole that penetrates in the axial direction and is closed at one end by a blind cover 200, and a through hole that extends from the middle of the through hole to the inner circumferential side (the axial center of the carrier 70). A through-oil passage 202 consisting of a hole extending to the side) is provided. This penetrating oil passage 202 is connected to the planetary gear 60
In order to lubricate the inner and outer peripheral parts of the planetary gear 60 and 62, one surface of the first gear 78 of the flange part 66 is
and 62.

A cylindrical receiver member 204 is attached to the flange portion 66 of the carrier A770 so as to be concentric with the carrier 70. The receiver member 204 of the fourth case 74 <
1, the cylindrical portion 20 is fitted into the hole 206 formed to allow the boss portion 64 to pass therethrough while forming a predetermined play, so that the tip thereof is brought close to the bearing 130.
8, a conical part 210 whose diameter becomes larger as the distance from the end of the cylindrical part 208 increases, and a disc-shaped part 212 extending in the outer circumferential direction from the end of the conical part 210. 212 is the first gear 78 side of the flange portion 66,
It is fixed on the outer peripheral side of the opening of the through oil passage 202.

In addition, in FIG. 3, for easy understanding, the input shaft 26, the output shaft 34, the first gear 78, and the second gear 8 are shown.
0 and 3rd! Although the respective axes of the wheel 82 and the drive shaft 20 are shown in a common plane, they are actually arranged three-dimensionally.

Therefore, in this embodiment configured as above, the cylindrical protrusion 170 protruding toward the sun gear 56 side of the connecting member 152 on the spline shaft portion 148 of the output shaft 34 serves as the connecting member of the sun gear A 56. Since the sun gear 56 is fitted into a cylindrical protrusion 172 protruding from the cylindrical projection 152 side so as to be relatively rotatable, the sun gear 56 can be rotated by the second case 74b of the housing 74 via the connecting member 152 and the bearing 160. It is supported by and centered with high precision. Therefore, during assembly, the connecting member 152 and the sun gear 56 are spline-fitted to the spline shaft portion 14B of the output shaft 34, and then the thrust ring 1 is inserted between the boss portion 64 of the carrier 70 and the sun gear 56.
When the carrier 70 is concentrically combined with the sun gear 56 fitted to the shaft end of the output shaft 34 while interposing the carrier 74, the annular protrusion of the thrust bearing 174 installed in the hole of the carrier 70 is inserted into the hole of the sun gear 56. It can be easily fitted and the assembly work is simple. The thrust bearing 174 includes a retainer having an axially projecting annular projection, and prior to assembly of the 'tl star gearing, one of the annular projections of the retainer is inserted into a hole in the connecting member 152 and into a boss in the carrier 64. When the carrier 70 is concentrically assembled with the sun gear 56 fitted to the shaft end of the output shaft 34, the other annular protrusion of the retainer acts as a connecting member. However, if the core of the carrier 64 is not exposed, it is difficult to fit the other annular projection of the retainer into the other of the connecting member 152 and the carrier 64. There it was.

Further, according to this embodiment, as described above, the lubricating oil path 16
4, the lubricating oil is pumped through the spline shaft portion 148.
When the lubricating oil is fed to the shaft end side of the output shaft 34 along the tooth traces of the lubricating oil, the lubricating oil released from between the connecting member 152 and the sun gear 56 can be easily restricted according to the diameter of the leakage hole 177. , the thrust bearing 174 is sufficiently lubricated to increase the durability of the planetary gear. Finally, the connecting member 152
If the connecting member 152 and the sun gear 56 are not fitted to each other, lubricating oil may leak indefinitely or unstably from between the connecting member 152 and the sun gear 56, causing the thrust bearing 17
4 was not sufficiently lubricated.

Further, according to this embodiment, the sun gear 56 is connected to the connecting member 1.
52 and the hair ring 160, the output shaft 34 is rotatably supported by the second case 7/Ib of the housing 74, so that the output shaft 34 is not bent due to the tension of the transmission belt 40 of the CVT 12 when the vehicle is running backwards. Even if it occurs,
The sun gear 56 is not eccentric, and the generation of gear noise caused by the eccentricity is suitably eliminated.

Although one embodiment of the present invention has been described above based on the drawings,
The invention also applies in other aspects.

For example, in the embodiment described above, the cylindrical projection 170 that is a part of the connecting member 152 is fitted into the cylindrical projection 172 protruding from the connecting member 152 side of the sun gear 56 so as to be relatively rotatable. However, on the contrary, the connecting member 152
The cylindrical projection 172, which is a part of the connecting member 152, may be fitted into the cylindrical projection 170 of the connecting member 152. In short, it is sufficient that the sun gear 56 is fitted to the coupling member 152 so as to be immovable relative to the axis in a direction perpendicular to the axis.

Further, in the above embodiment, the connecting member 152 is rotatably supported by the second case 74b via the bearing 160, so that the rotating body on the rotating shaft side of the forward clutch 72 is accurately positioned. drum 15
0 may be rotatably supported by the second case 74b.

In addition, in the above-mentioned embodiment, a double pinion type planetary gear unit (auxiliary transmission 14) for switching between forward and forward travel is explained, but a single pinion type planetary gear unit, multi-stage forward gear stage, etc. The present invention can also be applied to other types of planetary gear devices, such as a planetary gear device equipped with a planetary gear device and an automobile transmission in which a plurality of planetary gear devices are connected.

The above-mentioned embodiment is merely one embodiment of the present invention, and various modifications may be made to the present invention without departing from the spirit thereof.

[Brief explanation of the drawing]

FIG. 2 is a schematic diagram of a power transmission device including one embodiment of the present invention. FIG. 3 is a diagram illustrating the power transmission device of FIG. 2 in detail. FIG. 1 is an enlarged view illustrating the sub-transmission shown in FIG. 2. FIG. 14: Sub-transmission (planetary float device) 34: Output shaft (rotating shaft) 56: Sun gear 58: 60°70 Near 2 Near 4: Ring gear 62: Planetary gear carrier forward clutch (clutch) Housing: Spline shaft: Clutch tram ( (rotating body on the rotating shaft side): Connection member (rotating body on the rotating shaft side) Nibrate (frictional member): Clutch hub (rotating body on the carrier side): Disc (frictional member) n Fig. 2

Claims (1)

[Scope of Claims] A rotating shaft on which spline teeth are formed, a sun gear that is spline-fitted to the shaft end of the rotating shaft so as to be relatively non-rotatable, and a carrier that rotatably supports a planetary gear that meshes with the sun gear. , a ring gear meshing with the planetary gear, a friction member supported by a rotating shaft-side rotating body rotating together with the rotating shaft, and a friction member supported by a carrier-side rotating body rotating together with the carrier are brought into frictional engagement; A planetary gear comprising a clutch connecting the rotating shaft and the carrier, the rotating body on the rotating shaft side being spline-fitted to the rotating shaft in a state adjacent to the non-shaft end side of the sun gear. A planetary gear device, characterized in that the rotating shaft-side rotating body is rotatably supported by a housing, and the rotating shaft-side rotating body and the sun gear are fitted into each other.