JP3330705B2 - Power transmission device - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a power transmission device used for a vehicle.

[0002]

2. Description of the Related Art A transfer 301 as shown in FIG. 7 is described in JP-A-3-42335. This is because a center differential 303 that distributes the driving force of the engine to the front wheel side and the rear wheel side, a front differential 305 that distributes the distributed driving force to the left and right front wheels, and a differential of the center differential 303 are amplified to reduce the differential. A differential limiting device 307 that performs differential limiting by torque.

[0003]

The center differential 303 and the front differential 305 are both bevel gear types.
The side gear 309 on the left side of the center differential 303 is formed integrally with the differential case 311 of the front differential 305, and the whole is made compact by omitting a connecting shaft as compared with a separate case. However, in a configuration using a bevel gear type differential mechanism, further reduction in size is impossible due to interference between gears. Further, since the bevel gear type differential mechanism does not have a differential limiting function, a differential limiting device is required to limit the differential, and the effect of miniaturization is correspondingly impaired.

Accordingly, an object of the present invention is to provide a small and lightweight power transmission device integrally provided with a differential mechanism and a mechanism interlocked with the differential mechanism.

[0005]

According to a first aspect of the present invention, there is provided a power transmission device which is slidably and rotatably housed in a differential case rotated by the driving force of an engine and in a storage hole provided in the differential case. A plurality of pinion gear sets each including first and second pinion gears; and a first and a second pinion gears disposed on the inner diameter side of the plurality of pinion gear sets, and each of which outputs a mesh driving force separately from the first and second pinion gears. has a differential mechanism having a side gear, a gear that is disposed in an intermediate portion of the differential case circumferential direction of the set between the bearing by the plurality of pinion gears sets the differential case, first side of said differential mechanism
And a gear mechanism that meshes with and interlocks with the gear.

A power transmission device according to a second aspect of the present invention includes a differential case rotated by the driving force of an engine and a first and second pinion gears slidably and rotatably housed in storage holes provided in the differential case. A first differential mechanism having a plurality of pinion gear sets, and first and second side gears disposed on the inner diameter side of the plurality of pinion gear sets and each of which outputs a meshing driving force separately from the first and second pinion gears. And a pinion gear supported by the differential case and disposed between the sets of the plurality of pinion gear sets.
And a planetary gear type second differential mechanism for transmitting and receiving power to and from the differential mechanism.

According to a third aspect of the present invention, there is provided a power transmission device comprising: a differential case which is rotated by a driving force of an engine; and a first and second pinion gears which are slidably and rotatably stored in storage holes provided in the differential case. A differential mechanism comprising: a plurality of pinion gear sets; and first and second side gears disposed on the inner diameter side of the plurality of pinion gear sets and respectively outputting first and second pinion gears and meshing driving force. A differential lock mechanism arranged between the sets of the plurality of pinion gear sets.

[0008]

According to the first aspect, the gear of the gear mechanism that operates in conjunction with the differential mechanism is supported on the differential case of the differential mechanism.
In addition, since the gear mechanism is configured by being arranged in the middle of the differential case circumferential direction between the sets of the pinion gear sets, no extra space is required for disposing the gear mechanism.
The power transmission device has been significantly reduced in size and weight.
Further, by disposing the gear mechanism at the intermediate portion in the circumferential direction of the differential case of the pinion gear set, it is possible to use an empty space between the pinion gear sets.
If the differential case is provided on the inner diameter side between the pinion gear sets, the diameter of the differential case increases accordingly, but by providing the gear set at the circumferentially intermediate portion of the differential case as in the invention of claim 1, the gear set It is not necessary to provide a special space for providing the above, so that the size can be reduced. In addition, the differential mechanism performs a differential and differential limiting operation by engaging a pinion gear formed of a helical gear and a side gear, so that a differential limiting device is not required, and the power transmission device is further reduced in size and weight. .

According to the second invention, the pinion gear of the planetary gear type second differential mechanism for transmitting and receiving power to and from the first differential mechanism is supported on the differential case of the first differential mechanism. And since it is arranged in the middle between the pinion gear sets, it is possible to realize a significant reduction in size and weight of the power transmission device without requiring any extra space for disposing the second differential mechanism. ing. In addition, the first differential mechanism performs differential and differential limiting operations by meshing between a pinion gear formed of a helical gear and a side gear, so that a differential limiting device is not required, and the power transmission device is further reduced in size and weight. Has become.

According to the third aspect, the differential lock mechanism is disposed in the middle of the pinion gear sets of the differential mechanism.
The power transmission device is significantly reduced in size and weight without requiring extra space for disposing the differential lock mechanism. In addition, the differential mechanism performs differential and differential limiting operations by meshing between a pinion gear formed of a helical gear and a side gear, so that a differential limiting device is not required, and the device is small and lightweight.

[0011]

1 and 2, an embodiment of the first invention will be described. FIG. 1 shows a vertically installed transfer 3 in which the power transmission device 1 of this embodiment is arranged in the front-rear direction of a four-wheel drive vehicle.
The left side of FIG. 1 corresponds to the front of the vehicle. Also, members and the like without reference numerals are not shown.

The transfer case 5 has bearings 6
A differential case 9 is supported via 7. The differential case 9 includes front and rear hollow bodies 11 and 13 integrated by welding, and is rotationally driven by a driving force of an engine via a transmission (not shown). A pair of hollow shafts 15 and 17 are arranged in the differential case 9, and are supported by the differential case 9 by respective shaft supports 19 and 21 and mutually supported by the shaft supports 22. Hollow shaft 15,
17, side gears 23 and 25 formed of helical gears are formed as first and second side gears, respectively.
A washer 27 is disposed between the side gears 23 and 25, a washer 29 is disposed between the hollow shaft 15 and the differential case 9, and a washer 31 is disposed between the side gear 25 and the differential case 9.

As shown in FIGS. 1 and 2, a long housing hole 33 and a short housing hole 35 are formed in the differential case 9, and the long housing hole 33 is provided with a long pinion gear 37 formed of a helical gear as a first pinion gear. A short pinion gear 39 composed of a helical gear is stored in the short storage hole 35 as a second pinion gear, and the long pinion gear 37 and the short pinion gear 3 are stored in the short storage hole 35.
9 constitute one pinion gear set. The long pinion gear 37 includes front and rear gear portions 41 and 43 and a small-diameter shaft portion 45 connecting the front and rear gear portions 41 and 43. The front gear portion 41 meshes with the front half of the short pinion gear 39, and Are meshed with the rear side gear 25.
The rear half of the short pinion gear 39 meshes with the front side gear 23. As shown in FIG.
Three sets of 7, 39 are arranged at equal intervals in the circumferential direction.

Thus, the differential mechanism 47 is configured.

The hollow shaft 15 (side gear 23) is spline-connected to an output shaft 49 for the rear wheel, and the hollow shaft 17 is spline-connected to a sprocket 51 for the front wheel. The sprocket 51 is supported on the transfer case 5 by bearings 53 and 55. The output shaft 49 penetrates through the sprocket 51 and is supported on the inner periphery thereof. A flange 57 is spline-connected to a rear end of the output shaft 49 and is fixed with a lock nut 59. Seals 61 and 63 are arranged between the transfer case 5, the differential case 9 and the flange 57, respectively.

The sprocket 51 is connected to another sprocket (not shown) via a chain 65, and further connected to a front differential via a propeller shaft (not shown) on the front wheel side. Further, the output shaft 49 is connected to a rear differential (a differential device on the rear wheel side) from a propeller shaft (not shown) on the rear wheel side via a flange 57.

The driving force of the engine for rotating the differential case 9 is transmitted from the pinion gears 37 and 39 to the side gears 23 and 2.
5 and each of the front and rear wheel driving force transmission systems, and is distributed to a front differential and a rear differential, and each differential distributes the distributed driving force to the left and right wheels of the front and rear wheels. When a driving resistance difference occurs between the front wheels and the rear wheels, the driving force of the engine is differentially distributed to the front and rear sides by the rotation of the pinion gears 37 and 39.

During torque transmission, each of the pinion gears 37, 39
Is pressed against the wall surfaces of the storage holes 33 and 35 by the reaction force of engagement with the side gears 25 and 23, and frictional resistance is generated.
Further, since the differential mechanism 47 is constituted by a helical gear, the side gears 23 and 25 are pressed against the differential case 9 via the washers 29 and 31 by the meshing thrust force with the pinion gears 37 and 39, or the And press against each other to generate frictional resistance. These frictional resistances increase as the transmission torque increases, and a torque-sensitive differential limiting function that strongly brakes the braking rotation of each gear as the transmission of the torque increases.

A differential lock mechanism 67 is provided on the differential case 9.
(Gear mechanism). A pinion shaft 73 fixed to the hollow bodies 11 and 13 supports a pinion gear 73 (gear) via a bearing 71. As shown in FIG. 2, three pinion gears 73 are arranged in the middle between the pinion gear sets, and are arranged at the same axial position as the gear portion 41 as shown in FIG. The pinion gear 73 is a spur gear, and meshes with a spur gear 75 formed on the hollow shaft 15 (side gear 23). Also, the pinion gear 7
A coupling sleeve 77 is meshed with the hollow body 11 so as to be movable in the axial direction.
Is formed.

The coupling sleeve 77 is operated to move in the front-rear direction via a fork (not shown) engaged with the circumferential groove 81. When the coupling sleeve 77 moves forward and engages with the spur gear 79, the side gear 23 is connected to the differential case 9, Differential mechanism 47
Are locked. When the gear is moved to the position shown in FIG. 1, the engagement with the spur gear 79 is released, and the differential becomes free.

The power transmission device 1 is constituted by the differential mechanism 47 and the differential lock mechanism 67.

Due to the differential limiting function of the differential mechanism 47, the vehicle can turn smoothly and stably, and even if one of the front and rear wheels idles on a rough road, the driving force is transmitted to the other wheel. The ability to travel on rough roads improves. In addition, during acceleration in which a large torque is applied, a large differential limiting force is obtained, and the straight running stability is improved. Locking the differential with the differential lock mechanism 67 further improves the straight running stability and rough road running performance.

As described above, according to the present embodiment, the pinion gear 73 of the differential lock mechanism 67 is disposed in the middle between the pinion gear sets of the differential mechanism 47, so that the size is reduced in the axial direction and the weight is reduced. In addition, since the differential mechanism 47 has the differential limiting function as described above, a differential limiting device is unnecessary, and the power transmission device 1 is further reduced in size and weight.

Next, an embodiment of the second invention will be described with reference to FIGS. FIG. 3 shows a power transmission device 83 of this embodiment.
Shows a transfer 85 placed horizontally in the width direction of a four-wheel drive vehicle. Hereinafter, the left and right directions are the left and right directions of the vehicle. Also, members and the like without reference numerals are not shown.

A differential case 91 of a center differential 89 is supported on the transfer case 87 via bearings 93 and 95. A ring gear 99 is fixed to the differential case 91 with bolts 97, and the ring gear 99 is engaged with an output gear (not shown) of the transmission. Thus, the driving force of the engine rotationally drives the differential case 91 via the transmission.

The center differential 89 includes a double pinion planetary gear type differential mechanism 101 (second differential mechanism). The internal gear 103 is formed in a differential case 91. Outer and inner pinion gears 105,1
Reference numeral 07 is supported by pinion shafts 111, 111 via bearings 109, 109. Each pinion shaft 111 has a left and right pinion carrier (diff case) 1
Both ends of the pinion carriers 113 and 115 are supported by welding.

The left pinion carrier 113 is formed integrally with the differential case 119 of the front differential 117.
The left end of the differential case 119 is supported by the differential case 91 via a shaft support 121. Right pinion carrier 1
Reference numeral 15 is supported by a differential case 91 via a shaft support 123. The sun gear 125 is formed on a hollow shaft 127. The hollow shaft 127 is supported by a pinion carrier 115 via a shaft support 129, and is spline-connected to another hollow shaft 131 at the right end.

A bevel gear 133 is spline-connected to the hollow shaft 131, and is prevented from falling off by a lock nut 134. The bevel gear 133 meshes with the bevel gear 135 to form a direction changing gear set 137. Bevel gear 1
The output shaft 139 is formed integrally with the front end of an output shaft 139 disposed in the traveling direction of the vehicle.
1, 143 supports the transfer case 87. A flange 145 is provided at the rear end of the output shaft 139.
Are spline-connected and fixed with nuts 147. The flange 145 is connected to a rear wheel side propeller shaft via a joint.

The differential case 91 (internal gear 10
The driving force of the engine that rotates 3) is the pinion gear 1
The drive force is distributed to the rear wheel driving force transmission system and the differential case 119 (pinion carrier 113) of the front differential 117 via the drive wheels 05 and 107, and when a drive resistance difference occurs between the front and rear wheels, the rotation and revolving of the pinion gears 105 and 107 occur. Thus, the driving force of the engine is differentially distributed to the front and rear sides.

In the differential case 119, left and right hollow shafts 14 are provided.
9, 151 are arranged, and a shaft support 153 is provided between each other.
And the left hollow shaft 149 is supported by the shaft support 1.
The right hollow shaft 151 is supported on the hollow shaft 127 (sun gear 125) via the shaft support 157 via the shaft 55. Axles 159, 161 on the front wheel side are spline-connected to the hollow shafts 149, 151, respectively, and are fixed by snap rings 163. The left axle 159 is supported by the differential case 91 via a shaft support 165, and is connected to the left front wheel by a flange 167. The right axle 161 passes through the hollow shafts 127 and 131, is supported by the hollow shaft 131 via a shaft support 169, and is connected to the right front wheel side by a flange 171. Seals 173 and 175 are arranged between the transfer case 87 and the axles 159 and 161, and seals 177 and 179 are arranged between the transfer case 87 and the hollow shaft 127 and the flange 145.

First and second side gears 181 and 183 formed of helical gears are formed on the hollow shafts 149 and 151. Washers 185 are arranged between the side gears 181 and 183, and washers 187 and 189 are arranged between the differential case 119 and the side gears 181 and 183, respectively.

The differential case 119 has long and short storage holes 19.
As shown in FIG. 4, three sets of the first pinion gear 195 are formed at equal intervals in the circumferential direction, and the first pinion gear 195 formed of a long helical gear is slidably and rotatably stored in the long storage hole 191. 193 has a second short helical
A pinion gear 197 is slidably housed therein.
The long pinion gear 195 has left and right gear portions 199, 201.
And a small-diameter shaft portion 203 connecting these, the left gear portion 199 meshes with the left side gear 181, and the right gear portion 201 meshes with the right half of the short pinion gear 197. The left half of the short pinion gear 197 meshes with the right side gear 183. Long pinion gear 1
95 and the short pinion gear 197 constitute one pinion gear set. Thus, the differential mechanism 205 (first differential mechanism) is configured, and the front differential 117 is configured.

The driving force of the engine distributed from the center differential 89 is distributed to the left and right front wheels from the pinion gears 195 and 197 via the side gears 181 and 183 and the axles 159 and 161. When this occurs, the driving force is differentially distributed to the left and right sides by the rotation of the pinion gears 195 and 197. Further, the torque-sensitive differential limiting function is obtained by the meshing reaction force and the meshing thrust force of the helical gear, similarly to the differential mechanism 47 of the above embodiment.
The turning performance, the ability to travel on rough roads, and the straight running stability of the vehicle are improved.

A power transmission 83 is constituted by the center differential 89 and the front differential 117.

Thus, according to the present embodiment, as shown in FIG. 4, the pinion gears 105 and 107 of the center differential 89 are arranged in the middle of the pinion gear sets of the front differential 117, as shown in FIG. Since the size becomes smaller in the axial direction and the front differential 117 does not require a differential limiting device, the power transmission device 83 is significantly reduced in size and weight.

The ring gear 99 is connected to the center differential 89
The internal gear 103 is fixed to the pinion carriers 113 and 115 side, and the differential case 1 of the front differential 117 is fixed.
19 may be formed integrally with the driving force of the engine from the pinion carriers 113 and 115. Alternatively, the first differential mechanism may be a center differential and the second differential mechanism may be a front differential, as opposed to the device 83 of the present embodiment.

Next, an embodiment of the third invention will be described with reference to FIGS.

In the present invention, the gear mechanism (the differential lock mechanism 67 in FIG. 1) in the embodiment of the first invention (see FIGS. 1 and 2) is replaced with another mechanism. Therefore,
The same reference numerals are given to the same components other than the differences,
The difference will be described, avoiding redundant description.

FIG. 5 shows a power transmission device 201 of this embodiment.
Is shown in a longitudinally disposed transfer 203 in the front-rear direction of a four-wheel drive vehicle, and the left side of FIG. 5 corresponds to the front of the vehicle.

The differential case 209 is the transfer case 5
And the hollow bodies 211,
213, and is rotationally driven by the driving force of the engine via a transmission (not shown). Hollow shafts 215 and 217 are arranged in the differential case 209, and these are supported on the differential case 209 by respective shaft supports 219 and 221. A side gear 223 made of a helical gear is spline-fitted on the hollow shaft 215 as a first side gear, and a side gear 225 made of a helical gear is formed integrally on the hollow shaft 217 as a second side gear. , A washer 231 between the side gear 225 and the differential case 209, and a differential lock mechanism 26 between the side gear 223 and the differential case 209, which will be described later.
Washers 229 are respectively disposed via sleeves 279 of the seventh embodiment.

As shown in FIGS. 5 and 6, the differential case 20
9, a long storage hole 33 and a short storage hole 35 are formed, and a long helical pinion gear 37 is slidably and rotatably stored in the long storage hole 33 as a first pinion gear.
A short helical pinion gear 39 is housed in the short housing hole 35 as a second pinion gear, and the long pinion gear 37 and the short pinion gear 39 constitute one set of pinion gears. The long pinion gear 37 includes front and rear gear portions 41 and 43 and a small-diameter shaft portion 45 connecting these gear portions, and the front gear portion 41 has a short pinion gear 3.
9 and the rear gear 43 is meshed with the rear side gear 25. The rear half of the short pinion gear 39 meshes with the front side gear 223. FIG.
, Four sets of pinion gears 37 and 39 are arranged at equal intervals in the circumferential direction.

Thus, the differential mechanism 247 is configured.

The hollow shaft 215 is provided with a differential lock mechanism 2 described later.
According to the moving operation of 67, it is possible to move a predetermined amount in the front-back direction. The hollow shaft 215 is connected to the output shaft 49 on the rear wheel side.
The hollow shaft 217 is spline-connected to the sprocket 51 on the front wheel side.

The driving force of the engine for rotating the differential case 209 is transmitted from the pinion gears 37 and 39 to the side gears 22.
3, 225 and the front wheel side and rear wheel side driving force transmission systems, and are distributed to the front differential and the rear differential, and each differential distributes the distributed driving force to the left and right of the front and rear wheels. When a driving resistance difference occurs between the front wheels and the rear wheels, the driving force of the engine is differentially distributed to the front and rear sides by the rotation of the pinion gears 37 and 39.

During torque transmission, each pinion gear 37, 39
Is pressed against the wall surfaces of the storage holes 33 and 35 by the reaction force of engagement with the side gears 225 and 223, and frictional resistance is generated. Further, since the differential mechanism 247 is constituted by a helical gear, each of the side gears 223 and 225 is
7 and 39, the washer 22
9, 231 or is pressed against each other via a washer 227 to generate frictional resistance. These frictional resistances increase as the transmission torque increases, and a torque-sensitive differential limiting function that strongly brakes the braking rotation of each gear as the transmission of the torque increases.
With this differential limiting function, the vehicle can turn smoothly and stably, and even if one of the front and rear wheels idles on a rough road, the driving force is sent to the other wheel to improve the rough road running performance. or,
During acceleration with a large torque, a large differential limiting force is obtained, and the straight running stability is improved.

On the other hand, the differential lock mechanism 267 is arranged between the pinion gear sets of the differential mechanism 247. That is, as shown in FIG. 5 and FIG.
A shaft 269 is fixed, and a large ring 273 is supported on the shaft 269. The support position is such that the large ring 273 has an arm 273 extending toward the center of the ring.
Since two pieces “a” are provided, the large ring 273 is supported on the shaft 269 by the arm portion 273a. The outer periphery of the large ring 273 is engaged with two grooves 275 a formed on the fork 275, and is positioned by the fork 275 in the front-rear direction. Further, the arm portion 273a
Has a groove 277a formed on the outer periphery of the small ring 277.
To position the small ring 277 in the front-rear direction. The small ring 277 is formed in the same shape as the large ring 273, and its arm 277a is
5 is engaged with an axially extending slit 279 a of the sleeve 279 fitted outside, and the tip of the arm 277 a is in contact with the outer diameter of the hollow body 215. The tip of the arm portion 277a is fixed in the front-rear direction by the step portion of the hollow body 215 and the snap ring 280.
7 positions the hollow body 215 in the front-rear direction. Further, the sleeve 279 has an inner diameter of the hollow body 215.
And spline fit. Thus, fork 275
Is moved in the front-rear direction, the large and small rings 273,
The hollow body 215 moves in the front-rear direction via 277. On the other hand, in the rotation direction, the sleeve 279
The small ring 277 rotates integrally with the hollow body 215, while the large ring 273 rotates integrally with the differential case 209, so that the relative rotation between the large ring 273 and the small ring 277 is possible.

Thus, the differential lock mechanism 267 is constructed, and its position is arranged at the same position in the front-rear direction as the gear portion 41 of the pinion gear 37.

FIG. 5 shows the differential lock release position of the differential lock mechanism 267. At this time, since the differential lock mechanism 267 does not restrict the movement of the side gears 223 and 225, the differential and differential limiting actions of the differential mechanism 247 are not restricted. On the other hand, when the fork 275 is shifted rearward (rightward) by a predetermined amount from this release state, the hollow body 215 moves rightward via the large and small rings 273 and 277, and the outer peripheral spline of the hollow body 215 is moved to the side gear 225. With a spline provided on the inner periphery of. Thus, the two side gears 223 and 225 rotate integrally via the hollow body 215,
Since relative rotation is not allowed, the differential mechanism 247 is locked. Locking the differential with the differential lock mechanism 267 further improves the straight running stability and rough road running performance.

The power transmission device 201 is constituted by the differential mechanism 247 and the differential lock mechanism 267.

As described above, according to the present embodiment, the differential lock mechanism 267 is arranged in the middle between the sets of the pinion gears of the differential mechanism 247, so that the arrangement thereof does not require an extra axial space and is compact and lightweight. Has been. Further, since the differential mechanism 247 has the differential limiting function as described above, the differential limiting device is not required, and the power transmission device 2
01 is further reduced in size and weight. Further, since four pinion gear sets can be arranged (see FIG. 6), the pinion gear set can be applied when a high torque is input, and the durability is improved.

[0051]

According to the first aspect of the present invention, the gear of the gear mechanism which operates in conjunction with the differential mechanism is arranged in the middle of the pair of pinion gears to constitute the gear mechanism. The power transmission device can be significantly reduced in size and weight without requiring extra space for installation. In addition, since the differential mechanism performs differential and differential limiting operations by engaging the helical gears, the need for a differential limiting device is eliminated, and the power transmission device is further reduced in size and weight.

According to the second invention, the pinion gear of the second differential mechanism for transmitting and receiving power to and from the first differential mechanism is supported by the differential case of the first differential mechanism.
The power transmission device can be significantly reduced in size and weight without requiring an extra space for disposing the differential mechanism. In addition, since the differential mechanism performs differential and differential limiting operations by engaging the helical gears, the need for a differential limiting device is eliminated, and the power transmission device is further reduced in size and weight.

According to the third aspect of the present invention, the differential lock mechanism is disposed in the middle between the pinion gear sets of the differential mechanism.
The power transmission device can be significantly reduced in size and weight without requiring extra space for disposing the differential lock mechanism. In addition, since the differential mechanism performs differential and differential limiting operations by engaging the helical gears, the need for a differential limiting device is eliminated, and the power transmission device is further reduced in size and weight.

[Brief description of the drawings]

FIG. 1 is a sectional view showing an embodiment of the first invention.

FIG. 2 is a sectional view taken along line AA of FIG.

FIG. 3 is a sectional view showing an embodiment of the second invention.

FIG. 4 is a sectional view taken along line BB of FIG. 3;

FIG. 5 is a sectional view showing an embodiment of the third invention.

FIG. 6 is a sectional view taken along line CC of FIG. 5;

FIG. 7 is a sectional view of a conventional example.

[Explanation of symbols]

1,83,201 Power transmission device 9,119,209 Differential case 23,25,181,183,223,225 Side gear 33,35,191,193 Storage hole 37,39,195,197 Pinion gear 47,247 Differential mechanism 67 Differential lock mechanism (gear mechanism) 267 Differential lock mechanism 73 Pinion gear (gear) 101 Differential mechanism (second differential mechanism) 105, 107 Pinion gear 205 Differential mechanism (first differential mechanism)

──────────────────────────────────────────────────続 き Continued on the front page (58) Field surveyed (Int. Cl. ⁷ , DB name) F16H 48/00-48/30 B60K 17/28-17/36

Claims (3)

(57) [Claims] 1. A differential case rotated by a driving force of an engine, and a plurality of pinion gear sets including first and second pinion gears slidably and rotatably stored in storage holes provided in the differential case. A differential mechanism disposed on the inner diameter side of the plurality of pinion gear sets, the differential mechanism having first and second pinion gears and first and second side gears that respectively output mesh driving force, and are supported by the differential case. The circumferential direction of the differential case between the sets of the plurality of pinion gear sets
And a gear disposed at an intermediate portion of the differential mechanism .
A power transmission device comprising: a gear mechanism that meshes with and interlocks with a side gear. 2. A differential case which is rotated by a driving force of an engine, and a plurality of pinion gear sets each comprising first and second pinion gears which are slidably and rotatably stored in storage holes provided in the differential case, respectively. A plurality of pinion gear sets,
A first differential mechanism having a second pinion gear and first and second side gears for respectively outputting a mesh driving force; and a pinion gear supported by the differential case and arranged between the plurality of pinion gear sets. And a second differential mechanism of a planetary gear type for transmitting and receiving power to and from the first differential mechanism. 3. A differential case that is rotated by a driving force of an engine, and a plurality of pinion gear sets including first and second pinion gears that are slidably and rotatably housed in storage holes provided in the differential case, and mesh with each other. A plurality of pinion gear sets,
A differential mechanism having a second pinion gear and first and second side gears each of which separately outputs a mesh driving force; and a differential lock mechanism arranged between the plurality of pinion gear sets. Power transmission device.