JP2020153446A - Lubricating structure of differential gear device - Google Patents

Abstract

To efficiently supply lubricating oil to engaging elements.SOLUTION: A differential gear device comprises: an input shaft 32; a first output shaft 34; a second output shaft 33; a spider shaft 41 provided on the input shaft 32 so as to be rotatable integrally; a pinion gear 42 rotatably provided on the spider shaft 41; a first side gear 44 engaging with the pinion gear 42, and for transmitting power to the first output shaft 34; a second side gear 45 engaging with the pinion gear 42, and for transmitting power to the second output shaft 33; and a pump 50 capable of supplying lubricating oil to engaging parts between the pinion gear 42 and the side gears 44 and 45. The pump 50 is an internal gear pump comprising a pump housing 51, an outer rotor 58, and an inner rotor 59. The pump housing 51 is provided so as to be rotatable integrally with the first side gear 44. The inner rotor 59 is provided so as to be rotatable integrally with the input shaft 32 or the second output shaft 33.SELECTED DRAWING: Figure 4

Description

The present disclosure relates to a lubrication structure for a differential gear device.

Conventionally, in vehicles such as trucks, a rear two-axis drive vehicle in which both the rear front axle and the rear rear axle serve as drive axes is known. In such a rear two-axle drive vehicle, since the power of the driving force source is transmitted to the rear front drive shaft and the rear rear drive shaft, an inter provided with a differential gear mechanism that absorbs the difference rotation between these two shafts. An axle differential gear device (intermediate differential gear device) is used (see, for example, Patent Documents 1 and 2).

JP-A-2015-178350 Japanese Unexamined Patent Publication No. 2013-124739

In the intermediate differential gear device described in the above patent document, the rotating shaft of the oil pump that supplies lubricating oil to the differential gear mechanism is connected to the rear front output shaft that transmits power to the rear front drive shaft. For this reason, the oil pump will continue to be driven even in a state where lubrication is not required and the differential gear mechanism does not rotate differently, such as when the rear front drive wheels and the rear rear drive wheels rotate in substantially the same rotation in a straight line. Become. As a result, the increase in rotational resistance due to the unnecessary supply of lubricating oil may lead to deterioration of fuel efficiency.

Further, in the intermediate differential gear device described in the above patent document, the front drive wheel does not rotate after touching the road surface in the derailed state in which the rear rear drive wheel floats from the road surface, so that the oil pump stops driving. become. Therefore, even though the differential gear mechanism is in a state where lubrication is required to absorb a large difference rotation, the supply of lubricating oil may be stopped, which may cause seizure or the like in the differential gear mechanism.

An object of the present disclosure is to provide a lubrication structure for a differential gear device capable of efficiently supplying lubricating oil to a meshing element.

The lubrication structure of the differential gear device of the present disclosure includes an input shaft to which power is transmitted from a driving force source, a first output shaft to which power can be transmitted from the input shaft, and power can be transmitted from the input shaft. The second output shaft, the spider shaft rotatably provided on the input shaft, the pinion gear rotatably provided on the spider shaft, mesh with the pinion gear, and transmit power to the first output shaft. It is possible to supply lubricating oil to the first side gear, the second side gear that meshes with the pinion gear, and at least the meshing portion between the pinion gear and the first and second side gears to transmit power to the second output shaft. The pump is an inscribed gear pump having a pump housing, an outer rotor housed in the pump housing, and an inner rotor, and the pump housing can rotate integrally with the first side gear. The inner rotor is provided so as to be rotatable integrally with the input shaft or the second output shaft.

Further, the differential gear device is an intermediate differential gear device of a rear two-axle drive vehicle including a rear front drive shaft and a rear rear drive shaft, and the first output shaft supplies power to the rear front drive shaft. The second output shaft can transmit power to the rear-rear drive shaft, can rotate relative to the input shaft, and can rotate integrally with the first side gear. The pump housing is provided so as to be integrally rotatable with the first output shaft, and further includes a driven gear that meshes with the drive gear. The pump housing is provided so as to be integrally rotatable with the drive gear, and the inner rotor is provided. It is preferable that it is provided so as to be integrally rotatable with the input shaft.

Further, the differential gear device is an intermediate differential gear device of a rear two-axle drive vehicle including a rear front drive shaft and a rear rear drive shaft, and the first output shaft supplies power to the rear front drive shaft. The second output shaft is provided so that the second side gear can be integrally rotated, and power can be transmitted to the rear-rear drive shaft, and the second output shaft can be relatively rotated to the second output shaft. The pump housing further includes a drive gear provided so as to be integrally rotatable with the first side gear, and a driven gear which is provided so as to be integrally rotatable with the first output shaft and meshes with the drive gear. It is preferable that the inner rotor is provided so as to be integrally rotatable with the drive gear, and the inner rotor is provided so as to be integrally rotatable with the second input shaft.

According to the technique of the present disclosure, the lubricating oil can be efficiently supplied to the meshing element.

It is a schematic overall block diagram which shows the vehicle which concerns on this embodiment. It is a schematic diagram which shows the rear-front differential gear device and the rear-rear differential gear device which concerns on this embodiment. It is a schematic partial cross-sectional view which shows the intermediate differential gear apparatus provided with the lubrication structure which concerns on 1st Embodiment. It is a schematic cross-sectional view which shows the oil pump which is the main part of the lubrication structure which concerns on 1st Embodiment, and its peripheral structure. It is a schematic partial cross-sectional view which shows the intermediate differential gear apparatus provided with the lubrication structure which concerns on 2nd Embodiment. It is a schematic cross-sectional view which shows the oil pump which is the main part of the lubrication structure which concerns on 2nd Embodiment, and its peripheral structure.

Hereinafter, the lubrication structure of the differential gear device according to the present embodiment will be described with reference to the accompanying drawings. The same parts have the same reference numerals, and their names and functions are also the same. Therefore, detailed explanations about them will not be repeated.

[First Embodiment]
FIG. 1 is a schematic overall configuration diagram showing a vehicle 1 according to the present embodiment. The vehicle 1 is, for example, a rear two-axle drive vehicle such as a truck. An engine 10 is mounted on the vehicle 1 as an example of a driving force source. A transmission 12 is detachably connected to the engine 10 via a clutch device 11. An intermediate differential gear device 30 is connected to the transmission 12 via a first propeller shaft 13.

A rear-front differential gear device 60 is connected to the intermediate differential gear device 30 via a rear-front output shaft 34, which will be described in detail later. The left and right rear front drive wheels 20L and 20R are connected to the rear front differential gear device 60 via the left and right rear front drive shafts 18L and 18R, respectively.

Further, the rear-rear differential gear device 70 is connected to the intermediate differential gear device 30 via the second propeller shaft 14. The left and right rear rear drive wheels 21L and 21R are connected to the rear rear differential gear device 70 via the left and right rear rear drive shafts 19L and 19R, respectively. In the figure, reference numerals 22L and 22R indicate the left and right front wheels (steering wheels), respectively.

As shown in FIG. 2, the rear-front differential gear device 60 includes a rear-front housing 61, a rear-front drive pinion gear 62, a rear-front ring gear 63, and a rear-front, which are attached to the vehicle body via a suspension device (not shown). It includes a cage 64, a plurality of rear front pinion gears 65, a pair of left and right rear front side gears 66 and 67, and a rear front spider shaft 68. Each of these gear mechanisms 62 to 68 is housed in the rear front housing 61.

The rear-front drive pinion gear 62 is provided at the output end of the rear-front output shaft 34 so as to be integrally rotatable. The rear-front drive pinion gear 62 always meshes with the rear-front ring gear 63.

The rear front ring gear 63 is fixed to the rear front cage 64 by bolts or the like (not shown). The rear front pinion gear 65 is rotatably supported by a rear front spider shaft 68 provided in the rear front cage 64. The rear front pinion gear 65 always meshes with the left and right rear front side gears 66 and 67. The rear front side gears 66 and 67 are spline-fitted to the left and right rear front drive shafts 18L and 18R, respectively.

The rear-front cage 64, the rear-front pinion gear 65, the rear-front side gears 66 and 67, and the rear-front spider shaft 68 absorb the difference rotation between the left and right rear-front drive shafts 18L and 18R while transmitting torque. A gear mechanism is configured.

The rear-rear differential gear device 70 includes a rear rear housing 71, a rear rear drive pinion gear 72, a rear rear ring gear 73, a rear rear cage 74, and a plurality of rear rear housings 71, which are attached to the vehicle body via a suspension device (not shown). It includes a rear pinion gear 75, a pair of left and right rear rear side gears 76 and 77, and a rear rear spider shaft 78. Each of these gear mechanisms 72 to 78 is housed in the rear-rear housing 71.

The rear-rear drive pinion gear 72 is provided at the output end of the second propeller shaft 14 so as to be integrally rotatable. The rear-rear drive pinion gear 72 always meshes with the rear-rear ring gear 73.

The rear rear ring gear 73 is fixed to the rear rear cage 74 by bolts or the like (not shown). The rear-rear pinion gear 75 is rotatably supported by a rear-rear spider shaft 78 provided in the rear-rear cage 74. The rear rear pinion gear 75 always meshes with the left and right rear rear side gears 76 and 77. The rear rear side gears 76 and 77 are spline-fitted to the left and right rear rear drive shafts 19L and 19R, respectively.

The rear-rear cage 74, the rear-rear pinion gear 75, the rear-rear side gears 76 and 77, and the rear-rear spider shaft 78 absorb the difference rotation of the left and right rear-rear drive shafts 19L and 19R while transmitting torque. A gear mechanism is configured.

[Intermediate differential gear device]
FIG. 3 is a schematic partial cross-sectional view showing an intermediate differential gear device 30 having a lubrication structure according to the first embodiment.

As shown in FIG. 3, the intermediate differential gear device 30 of the first embodiment includes an intermediate housing 31 joined to the rear front housing 61 of the rear front differential gear device 60 with bolts and nuts (not shown) and an input shaft. 32 (input shaft of the present disclosure), through shaft 33 (second output shaft of the present disclosure), rear front output shaft 34 (first output shaft of the present disclosure), and drive gear 35 (drive gear of the present disclosure). A driven gear 36 (the driven gear of the present disclosure), an intermediate differential gear mechanism 40, and an oil pump 50 (the pump of the present disclosure) are provided.

The input shaft 32 is connected to the rear end of the first propeller shaft 13 and is rotatably supported by an intermediate housing 31 via a bearing (not shown). Lubricating oil pumped by the oil pump 50 from the bottom side of the intermediate housing 31 through an oil passage (indicated by reference numeral 80 in FIG. 4) provided in the intermediate housing 31 is engaged with the input shaft 32. A radial oil passage 81 and an axial oil passage 82 for supplying the elements and sliding elements are provided.

The through shaft 33 is provided coaxially with the input shaft 32, and is rotatably supported by the intermediate housing 31 and / or the rear / front housing 61 via bearings (not shown). A second propeller shaft 14 is connected to the rear end of the through shaft 33.

The rear-front output shaft 34 is provided parallel to the input shaft 32 and the through shaft 33. At the rear end of the rear-front output shaft 34, a rear-front drive pinion gear 62 of the rear-front differential gear device 60 is provided so as to be integrally rotatable. The rear-front output shaft 34 is rotatably supported by the intermediate housing 31 and / or the rear-front housing 61 via bearings (not shown).

The drive gear 35 is provided so as to be relatively rotatable at a portion of the input shaft 32 in front of the intermediate differential gear mechanism 40. The driven gear 36 is provided so as to be integrally rotatable with the rear / front output shaft 34, and always meshes with the drive gear 35.

The intermediate differential gear mechanism 40 includes an intermediate spider shaft 41 (spider shaft of the present disclosure), a plurality of intermediate pinion gears 42 (pinion gears of the present disclosure), an intermediate cage 43, and a rear front side gear 44 (first of the present disclosure). A side gear) and a rear rear side gear 45 (second side gear of the present disclosure) are provided.

The intermediate spider shaft 41 is provided so as to be integrally rotatable with the input shaft 32. The intermediate pinion gear 42 is rotatably supported by the intermediate spider shaft 41. The rear front side gear 44 is provided on the rear end side of the drive gear 35 so as to be integrally rotatable by splicing or the like. The rear-rear side gear 45 is provided on the front end side of the through shaft 33 so as to be integrally rotatable by splicing or the like. The rear / rear side gear 45 is arranged coaxially with the rear / front side gear 44 so as to face the intermediate pinion gear 42. The rear front side gear 44 and the rear rear side gear 45 always mesh with the intermediate pinion gear 42. Lubricating oil is supplied to these meshing portions via the axial oil passage 82 and the radial oil passage 81.

The intermediate differential gear device 30 configured as described above distributes the power transmitted from the input shaft 32 via the intermediate spider shaft 41 from the intermediate pinion gear 42 to the rear front side gear 44 and the rear rear side gear 45. To do. The power distributed to the rear front side gear 44 is transmitted to the rear front differential gear device 60 via the drive gear 35, the driven gear 36, and the rear front output shaft 34, while the power distributed to the rear rear side gear 45. Is transmitted to the rear-rear differential gear device 70 via the through shaft 33 and the second propeller shaft 14.

Further, in the intermediate differential gear device 30, when a difference rotation occurs between the rear front drive shafts 18L and 18R and the rear rear drive shafts 19L and 19R, the intermediate pinion gear 42 rotates around the intermediate spider shaft 41. Along with this, by absorbing the difference rotation between the rear front side gear 44 and the rear rear side gear 45, power is transmitted while giving a differential to the rear front drive shafts 18L and 18R and the rear rear drive shafts 19L and 19R. To do.

The oil pump 50 is a so-called inscribed gear pump, and includes a pump housing 51, an outer rotor 58 housed in the pump housing 51, and an inner rotor 59. The details of the oil pump 50 according to the first embodiment will be described below.

FIG. 4 is a schematic cross-sectional view showing the oil pump 50, which is a main part of the lubrication structure according to the first embodiment, and its peripheral configuration.

The pump housing 51 is formed in a substantially cylindrical shape having a hollow hole through which the input shaft 32 is inserted, and is supported by the input shaft 32 and the intermediate housing 31 so as to be relatively rotatable. More specifically, the pump housing 51 is supported on the outer periphery on the front end side thereof by a pair of outer peripheral slip rings 90 and 91 so as to be relatively rotatable relative to the intermediate housing 31. Further, the pump housing 51 is supported on the inner circumference on the rear end side by a pair of slip rings 92 and 93 for the inner circumference so as to be relatively rotatable by the input shaft 32. The pair of outer peripheral slip rings 90 and 91 are arranged to face each other with the oil passage 80 provided in the intermediate housing 31 interposed therebetween, and the pair of inner peripheral slip rings 92 and 93 have diameters provided in the input shaft 32. They are arranged so as to face each other with the directional oil passage 81 in between.

An annular suction groove 52 recessed inward in the radial direction from between the pair of outer peripheral slip rings 90 and 91 is provided on the front end side of the pump housing 51. The suction groove 52 communicates with the oil passage 80 via the facing spaces of the outer peripheral slip rings 90 and 91. Further, on the bottom side of the suction groove 52, a suction oil passage 53 that extends the pump housing 51 in the axial direction and communicates with the rotor accommodating chamber 54 is provided. The suction groove 52 and the suction oil passage 53 function as suction ports for sucking lubricating oil from the oil passage 80 into the rotor accommodating chamber 54.

On the rear end side of the pump housing 51, an annular discharge groove 56 that is recessed radially outward from between the pair of inner peripheral slip rings 92 and 93 is provided. The discharge groove 56 communicates with the radial oil passage 81 via the facing spaces of the inner peripheral slip rings 92 and 93. Further, on the bottom side of the discharge groove 56, a discharge oil passage 55 that extends the pump housing 51 in the axial direction and communicates with the rotor accommodating chamber 54 is provided. The discharge oil passage 55 and the discharge groove 56 function as discharge ports for discharging lubricating oil from the rotor accommodating chamber 54 to the axial oil passage 81.

In the present embodiment, the pump housing 51 is provided so as to be integrally rotatable with the drive gear 35, and is integrally rotated with the rear front side gear 44 and the drive gear 35 as they rotate.

The outer rotor 58 is housed in the rotor storage chamber 54 of the pump housing 51 so as to be relatively rotatable. An inner peripheral tooth (not shown) is provided on the inner circumference of the outer rotor 58. The inner peripheral teeth of the outer rotor 58 always mesh with the outer peripheral teeth (not shown) provided on the outer periphery of the inner rotor 59.

The inner rotor 59 is housed in the rotor storage chamber 54 of the pump housing 51 so as to be relatively rotatable. In the present embodiment, the inner rotor 59 is provided so as to be integrally rotatable on the input shaft 32, and integrally rotates together with the input shaft 32, the intermediate spider shaft 41, and the intermediate cage 43.

According to the first embodiment configured as described above, the pump housing 51 of the oil pump 50 is provided so as to be integrally rotatable with the drive gear 35 provided with the rear and front side gears 44, and the inner rotor of the oil pump 50. The 59 is provided so as to be integrally rotatable on an input shaft 32 provided with an intermediate spider shaft 41 and an intermediate cage 43. With this configuration, the input shaft 32 and the drive gear 35 are substantially the same when the rear front drive wheels 20L and 20R and the rear rear drive wheels 21L and 21R rotate in a straight line at substantially the same rotation speed. When rotating at the number of revolutions, the pump housing 51 and the inner rotor 59 rotate integrally with each other, so that the drive of the oil pump 50 is stopped. On the other hand, when the input shaft 32 and the drive gear 35 rotate at different rotation speeds, such as when the vehicle 1 turns or when any of the drive wheels 20L, 20R, 21L, and 21R is removed, the pump housing 51 and When the inner rotors 59 rotate relative to each other, the oil pump 50 is in a driving state for discharging lubricating oil.

That is, when the difference rotation does not occur between the side gears 44 and 45 of the intermediate differential gear mechanism 40, such as when the vehicle 1 is traveling in a straight line, the driving of the oil pump 50 is stopped, and the driving of the vehicle 1 is stopped or the drive wheels are turned. When a difference rotation occurs between the side gears 44 and 45 of the intermediate differential gear mechanism 40, such as when the wheels of 20L, 20R, 21L, and 21R are removed, the oil pump 50 can be switched to a driving state for discharging lubricating oil. It is configured in. As a result, when lubrication is not required for the intermediate differential gear mechanism 40 to prevent differential rotation, the increase in rotational resistance is suppressed by stopping the oil pump 50, and fuel efficiency can be effectively improved. Become. Further, when lubrication is required to cause a differential rotation in the intermediate differential gear mechanism 40, the lubrication efficiency of the intermediate differential gear mechanism 40 is improved by driving the oil pump 50, and the intermediate differential gear mechanism 40 is seized. It becomes possible to effectively prevent the occurrence of such factors.

[Second Embodiment]
FIG. 5 is a schematic partial cross-sectional view showing an intermediate differential gear device 30 having a lubrication structure according to a second embodiment.

As shown in FIG. 5, in the first embodiment, the intermediate differential gear device 30 of the second embodiment replaces the front-rear arrangement relationship between the rear front side gear 44 and the rear rear side gear 45. Since the same configurations are designated by the same reference numerals and their functions are the same, detailed description thereof will be omitted.

The rear-rear side gear 45 is provided on the front end side of the through shaft 33 so as to be integrally rotatable by splicing or the like. The rear front side gear 44 is provided so as to be relatively rotatable at a portion rearward of the rear rear side gear 45 of the through shaft 33. Further, the rear front side gear 44 is provided so as to be integrally rotatable with the drive gear 35 which can rotate relative to the through shaft 33 via the oil pump 50. The through shaft 33 is provided with a radial oil passage 81 for supplying lubricating oil to the intermediate differential gear mechanism 40 and an axial oil passage 82.

In the second embodiment, the pump housing 51 of the oil pump 50 is provided so as to be integrally rotatable with the rear front side gear 44 and the drive gear 35, and the inner rotor 59 of the pump housing 51 is integrated with the rear rear side gear 45. The rotatable through shaft 33 is integrally rotatable. Hereinafter, more details of the oil pump 50 according to the second embodiment will be described.

FIG. 6 is a schematic cross-sectional view showing the oil pump 50, which is a main part of the lubrication structure according to the second embodiment, and its peripheral configuration.

The pump housing 51 is formed in a substantially cylindrical shape having a hollow hole through which the through shaft 33 is inserted, and is supported by the through shaft 33 and the intermediate housing 31 so as to be relatively rotatable. More specifically, the pump housing 51 is rotatably supported on the outer periphery on the rear end side by a pair of outer peripheral slip rings 90, 91 to the intermediate housing 31. Further, the inner circumference of the pump housing 51 on the front end side thereof is supported by a pair of inner circumference slip rings 92 and 93 so as to be relatively rotatable by the through shaft 33. The pair of outer peripheral slip rings 90 and 91 are arranged to face each other with the oil passage 80 provided in the intermediate housing 31 interposed therebetween, and the pair of inner peripheral slip rings 92 and 93 have diameters provided in the through shaft 32. They are arranged so as to face each other with the directional oil passage 81 in between.

On the rear end side of the pump housing 51, an annular suction groove 52 that is recessed inward in the radial direction from between the pair of outer peripheral slip rings 90 and 91 is provided. The suction groove 52 communicates with the oil passage 80 via the facing spaces of the outer peripheral slip rings 90 and 91. Further, on the bottom side of the suction groove 52, a suction oil passage 53 that extends the pump housing 51 in the axial direction and communicates with the rotor accommodating chamber 54 is provided. The suction groove 52 and the suction oil passage 53 function as suction ports for sucking lubricating oil from the oil passage 80 into the rotor accommodating chamber 54.

On the front end side of the pump housing 51, an annular discharge groove 56 that is recessed radially outward from between the pair of inner peripheral slip rings 92 and 93 is provided. The discharge groove 56 communicates with the radial oil passage 81 via the facing spaces of the inner peripheral slip rings 92 and 93. Further, on the bottom side of the discharge groove 56, a discharge oil passage 55 that extends the pump housing 51 in the axial direction and communicates with the rotor accommodating chamber 54 is provided. The discharge oil passage 55 and the discharge groove 56 function as discharge ports for discharging lubricating oil from the rotor accommodating chamber 54 to the axial oil passage 81.

In the present embodiment, the pump housing 51 is provided between the rear front side gear 44 and the drive gear 35 so as to be integrally rotatable with the rear front side gear 44 and the drive gear 35. Further, the inner rotor 59 is provided so as to be integrally rotatable with the through shaft 33, and integrally rotates with the through shaft 33 and the rear rear side gear 45.

According to the second embodiment configured as described above, the pump housing 51 of the oil pump 50 is provided so as to be integrally rotatable with the rear front side gear 44, and the inner rotor 59 of the oil pump 50 has a through shaft 33. It is provided so as to be integrally rotatable with the rear side gear 45 via the rear rear side gear 45. With this configuration, the rear front drive wheels 20L and 20R and the rear and rear drive wheels 21L and 21R rotate at substantially the same number of revolutions, such as when the vehicle 1 is traveling in a straight line. When the side gear 45 rotates at substantially the same rotation speed, the pump housing 51 and the inner rotor 59 rotate integrally with each other, so that the drive of the oil pump 50 is stopped. On the other hand, when the rear front side gear 44 and the rear rear side gear 45 rotate at different rotation speeds, such as when the vehicle 1 turns or when any of the drive wheels 20L, 20R, 21L, and 21R is removed, the pump When the housing 51 and the inner rotor 59 rotate relative to each other, the oil pump 50 is in a driving state for discharging lubricating oil.

That is, when the difference rotation does not occur between the side gears 44 and 45 of the intermediate differential gear mechanism 40, such as when the vehicle 1 is traveling in a straight line, the driving of the oil pump 50 is stopped, and the driving of the vehicle 1 is stopped or the drive wheels are turned. When a difference rotation occurs between the side gears 44 and 45 of the intermediate differential gear mechanism 40, such as when the wheels of 20L, 20R, 21L, and 21R are removed, the oil pump 50 can be switched to a driving state for discharging lubricating oil. It is configured in. As a result, as in the first embodiment, when lubrication is not required for the intermediate differential gear mechanism 40 to prevent differential rotation, the increase in rotational resistance is suppressed by stopping the oil pump 50, which effectively improves fuel efficiency. It will be possible to improve. Further, when lubrication is required in which the intermediate differential gear mechanism 40 causes a difference rotation, the lubrication efficiency of the intermediate differential gear mechanism 40 can be reliably improved by driving the oil pump 50.

In particular, in the second embodiment, the pump housing 51 is provided on the rear front side gear 44 and the inner rotor 59 is integrally rotatable on the rear rear side gear 45, so that the pump housing 51 is provided on the rear front side gear 44 and the inner rotor. Compared to the first embodiment in which the 59 is integrally rotatable on the input shaft 32, the relative rotation speed difference between the pump housing 51 and the inner rotor 59 that occurs during turning or derailing can be secured to be large (for example, about twice). It is configured in. That is, when lubrication is required to cause differential rotation in the intermediate differential gear mechanism 40, more lubricating oil is supplied, and seizure of the intermediate differential gear mechanism 40 is more effectively prevented. Becomes possible.

[Other]
It should be noted that the present disclosure is not limited to the above-described embodiment, and can be appropriately modified and implemented without departing from the gist of the present disclosure.

For example, in the intermediate differential gear device 30 of the second embodiment, the through shaft 33 is extended to the front side of the rear rear side gear 45, and the inner rotor 59 is integrally rotatably provided in the extended portion to provide a pump housing. The 51 may be provided on the input shaft 32 so as to be integrally rotatable. Also in this case, the same action and effect as those of the first embodiment can be obtained.

Further, the application of this embodiment is not limited to the intermediate differential gear device 30, and if the device includes a differential gear mechanism, other devices such as the rear front differential gear device 60 and the rear rear differential gear device 70 can be applied. It can be widely applied to a differential gear device, a transfer device having a planetary gear mechanism, or the like. When applied to a planetary gear mechanism, for example, the pump housing 51 is integrally rotatably provided on the planetary carrier and the inner rotor 59 is integrally rotatable on the sun gear, or the pump housing 51 is integrally rotated on the ring gear and the inner rotor 59 is integrally rotated on the planetary carrier. It may be provided if possible.

Further, the vehicle 1 is not limited to the truck, and can be widely applied to vehicles other than the truck.

1 vehicle 10 engine (driving force source)
11 Clutch 12 Transmission 13 1st propeller shaft 14 2nd propeller shaft 30 Intermediate differential gear device 31 Intermediate housing 32 Input shaft (input shaft)
33 Through shaft (second output shaft)
34 Rear front output shaft (first output shaft)
35 drive gear (drive gear)
36 Driven gear (driven gear)
40 Intermediate differential gear device (differential gear device)
41 Intermediate spider shaft (spider shaft)
42 Intermediate pinion gear (pinion gear)
43 Intermediate cage 44 Rear front side gear (1st side gear)
45 Rear rear side gear (second side gear)
50 oil pump (pump)
51 Pump housing 58 Outer rotor 59 Inner rotor 60 Rear front differential gear device 70 Rear rear differential gear device

Claims (3)

The input shaft to which the power from the driving force source is transmitted, and
A first output shaft capable of transmitting power from the input shaft and
A second output shaft capable of transmitting power from the input shaft and
A spider shaft that is integrally rotatable with the input shaft and
A pinion gear rotatably provided on the spider shaft and
A first side gear that meshes with the pinion gear and transmits power to the first output shaft.
A second side gear that meshes with the pinion gear and transmits power to the second output shaft.
A pump capable of supplying lubricating oil to at least the meshing portions of the pinion gear and the first and second side gears is provided.
The pump is an inscribed gear pump having a pump housing, an outer rotor housed in the pump housing, and an inner rotor.
The pump housing is provided so as to be rotatable integrally with the first side gear.
A lubrication structure for a differential gear device, wherein the inner rotor is provided so as to be rotatable integrally with the input shaft or the second output shaft. The differential gear device is an intermediate differential gear device for a rear two-axis drive vehicle including a rear front drive shaft and a rear rear drive shaft.
The first output shaft can transmit power to the rear front drive shaft, and can transmit power to the rear front drive shaft.
The second output shaft can transmit power to the rear-rear drive shaft, and
A drive gear that can rotate relative to the input shaft and that can rotate integrally with the first side gear.
It is provided so as to be rotatable integrally with the first output shaft, and further includes a driven gear that meshes with the drive gear.
The pump housing is provided so as to be rotatable integrally with the drive gear.
The lubrication structure for a differential gear device according to claim 1, wherein the inner rotor is provided so as to be rotatable integrally with the input shaft. The differential gear device is an intermediate differential gear device for a rear two-axis drive vehicle including a rear front drive shaft and a rear rear drive shaft.
The first output shaft can transmit power to the rear front drive shaft, and can transmit power to the rear front drive shaft.
The second output shaft is provided with the second side gear so as to be integrally rotatable, and can transmit power to the rear-rear drive shaft.
A drive gear that can rotate relative to the second output shaft and that can rotate integrally with the first side gear.
It is provided so as to be rotatable integrally with the first output shaft, and further includes a driven gear that meshes with the drive gear.
The pump housing is provided so as to be rotatable integrally with the drive gear.
The lubrication structure for a differential gear device according to claim 1, wherein the inner rotor is provided so as to be rotatable integrally with the second input shaft.

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