JPH08135771A - Lubricating device for inter-axle differential - Google Patents

Abstract

PURPOSE: To enhance durability of an inter-axle diff. (differential) by adopting such very simple and less expensive mechanism as the more quickly the diff. rotates, the more large quantity of lubriclating oil is supplied to a gear mechanism part of the inter-axle diff., thereby enhancing lubricating ability. CONSTITUTION: A turbine blade 31 is fixed to an inner race 42 of a rolling bearing, which supports a side gear 34 of an inter-axle diff. 33 in a freely rotatable manner, while the gear face and the reverse face of the side gear is communicated, thereby forming an oil feeding passage. Lubricating oil in an oil reservoir 47 is sent with pressure in the direction of the shaft by means of the turbine blade 31, so that the lubricating oil is supplied to a gear mechanism part of the inter-axle diff.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an inter-axle differential (abbreviation of inter-axle differential gear mechanism) lubricating device, and more particularly to a turbine bearing fixed to an inner race of a rolling bearing for rotatably supporting a side gear. By supplying a lubricating oil to the gear mechanism part of the inter-axle diff by an extremely simple and inexpensive mechanism that only rotates together with the inner race, it becomes unnecessary to process the oil supply pump and the complicated oil supply passage in the rotary shaft. The present invention relates to a lubrication device for an inter-axle diff, which supplies a larger amount of lubricating oil to a gear mechanism section as the inter-axle diff rotates at a higher speed to improve lubricity and durability of the inter-axle diff.

[0002]

2. Description of the Related Art In FIG.
Is used for a vehicle having two-axle rear wheels to absorb the difference in the rotational speeds of the two-axle rear wheels to enable smooth running. Axle vehicle 1
It has a front wheel 2, a rear front wheel 3 and a rear rear wheel 4.

The interaxle diff 5 is a side gear 6,
The drive gear 8, the first diff pinion 9 and the second diff pinion 10 are configured as a differential mechanism that meshes with each other in a square shape. The first diff pinion 9 and the second diff pinion 10 are connected to the output shaft 13 of the engine 12. The input shaft 14 is rotatably supported by a supporting member (not shown).

The drive gear 8 is the input shaft 1
4 is rotatably supported by a shaft 4, and can be connected and disconnected to and from the input shaft 14 via the clutch mechanism 11.

The drive gear 8 has a hollow first output shaft 24.
Further, a gear 18 that meshes with the gear 16 is integrally formed on the first output shaft 24, and a gear 18 is provided to a rear front wheel differential gear mechanism 15 that transmits a rotational force to the rear front wheel 3. The side gear 6 is connected to the rear rear wheel differential gear mechanism 19 that transmits the rotational force to the rear rear wheel 4 by the integrally connected second output shaft 25.

The rear front wheel differential gear mechanism 15 and the rear rear wheel differential gear mechanism 19 are constructed as a differential mechanism in which a side gear 20, a drive gear 21, a first differential pinion 22 and a second differential pinion 23 mesh with each other in a square shape. The mechanism is exactly the same, and the first diff pinion 22 and the second diff pinion 23 are connected to the left and right wheels of the rear front wheel 3 and the rear rear wheel 4, respectively.

When the engine 12 is started and the output shaft 13 and the input shaft 14 are rotated in the direction of arrow A, the rotation is transmitted to the interaxle differential 5 via the clutch mechanism 11 to rotate the drive gear 8. The rotation is transmitted to the side gear 6 via the first diff pinion 9 and the second diff pinion 10.

When the drive gear 8 rotates, the gear 16 rotates in the direction of arrow B via the gear 18, and the rotation is transmitted to the rear front wheel differential gear mechanism 15 and further transmitted to the rear front wheel 3 to generate the rear front wheel 3. Is rotated in the direction of arrow C.

The rotation of the side gear 6 is caused by the rotation of the second output shaft 2
5 is rotated in the direction of arrow D to be transmitted to the rear rear wheel differential gear mechanism 19, and further transmitted to the rear rear wheel 4 to rotate the rear rear wheel 4 in the direction of arrow E.

When the vehicle 1 operates a steering wheel while driving and bends a curve or the like, a space between the rear front wheel 3 and the rear rear wheel 4 and between the rear front wheel 3 is generated.
Also, a rotation difference occurs between the left and right wheels of the rear rear wheel 4, but the difference in rotation between the rear front wheel 3 and the rear rear wheel 4 is absorbed by the differential mechanism of the interaxle differential 5 operating. The rotation difference between the left and right wheels of the rear front wheel 3 is caused by the differential mechanism of the rear front wheel differential gear mechanism 15, and the rotation difference between the left and right wheels of the rear rear wheel 4 is determined by the rear rear wheel differential gear mechanism 1.
The differential mechanism 9 operates to absorb the rotation difference and enable smooth traveling.

As described above, in the interaxle diff 5, the side gear 6, the drive gear 8, the first diff pinion 9 and the second diff pinion 10, which mesh with each other as the vehicle 1 travels, rotate at high speed, so that the sliding portion and the Although it is important to lubricate the meshing portion, in the conventional lubrication, the inter-axle differential case (not shown) is provided with a lubrication hole, and the internal differential mechanism is lubricated from the lubrication hole. Since the side gear 6, the drive gear 8, the first diff pinion 9 and the second diff pinion 10 constituting the differential mechanism are rotating at high speed and the interaxle diff case is also rotating, centrifugal force acts on the lubricating oil. Since it scatters outward, the differential mechanism cannot be sufficiently lubricated, the temperature inside the inter-axle differential 5 rises, and there is room for improvement to improve durability performance. There was.

Further, as another conventional lubricating device, a special oil supply pump is provided, and a lubricating oil passage formed in the axial direction of the input shaft 14 is communicated with the lubricating oil passage so as to communicate with the lubricating oil passage in the radial direction of the input shaft 14. There is one in which the differential mechanism of the interaxle diff 5 is configured to be lubricated from the inside by the lubrication hole formed in, but it requires a dedicated lubrication pump and its drive unit, and further, the input shaft 1
4 had to process complicated lubricating oil passages and oil supply holes, and had a disadvantage that the mechanism was large and complicated, and the cost was high.

[0013]

SUMMARY OF THE INVENTION The present invention has been made to eliminate the above-mentioned drawbacks of the prior art. The object of the present invention is to fix turbine blades to the rotary member of an interaxle differential. It is installed and rotated together with the rotating member to pump the lubricating oil in the axial direction to supply oil to the meshing surface of the interaxle diff gear, so that the meshing surface of the interaxle diff gear is reliably lubricated with a simple mechanism. It is possible to eliminate the need for a fuel pump dedicated to the interaxle differential.

Another object is to provide a turbine blade fixed to an inner race of a rolling bearing which supports a side gear of an interaxle diff, and to connect a gear surface and a rear surface of the side gear to form an oil supply passage. This allows the lubricating oil to be pumped in the axial direction by the turbine blades to be fed from the oil feed passage of the side gear to the gear of the interaxle diff from the inside. The purpose of this is to ensure that the meshing surfaces can be reliably and sufficiently lubricated, and that a larger amount of lubricating oil can be lubricated as the rotation speed increases so as to prevent the temperature inside the interaxle differential from rising and improve the durability performance.

[0015]

SUMMARY OF THE INVENTION In summary, the present invention (claim 1) is a turbine which is fixed to a rotary member of an interaxle differential and rotates together with the rotary member to axially pump lubricating oil stored in an oil sump. A blade and an oil supply passage for lubricating the lubricating oil pumped by the turbine blade by lubricating the meshing surface of the gear of the interaxle diff.

Further, according to the present invention (claim 2), the lubricating oil which is fixed to the inner race of the rolling bearing which rotatably supports the side gear of the interaxle diff and rotates together with the inner race is stored in the oil sump. A turbine blade for pressure-feeding in a direction, and an oil supply passage that communicates the gear surface and the back surface of the side gear and supplies the lubricating oil pressure-fed by the turbine blade to the meshing surface of the gear of the interaxle diff. It is a feature.

[0017]

The inter-axle differential lubrication device of the present invention is constructed such that turbine blades are fixed to the inner race of the rolling bearing that supports the side gears of the inter-axle differential, and the lubricating oil is pumped axially by the turbine blades. Therefore, it is possible to supply the lubricating oil in an amount proportional to the rotation speed of the interaxle diff, and to supply a sufficient amount of lubricating oil to the meshing surface of the gear of the interaxle diff at high speed rotation that requires a large amount of lubricating oil. As a result, the durability of the interaxle diff is improved.

The lubricating device is a simple mechanism in which turbine blades are fixed to the inner race of the rolling bearing,
It can be manufactured inexpensively without causing a failure.

[0019]

DESCRIPTION OF THE PREFERRED EMBODIMENTS The present invention will be described below with reference to the embodiments shown in the drawings. 1 to 4, an interaxle differential lubrication device 30 according to the present invention includes turbine blades 31 and an oil supply passage 32.

First, the structure of the interaxle diff 33 will be described. The bevel gears of the side gear 34, the drive gear 35, the first diff pinion 36, and the second diff pinion 38 are configured as a differential mechanism in which they mesh with each other in a square shape. The first diff pinion 36 and the second diff pinion 38 are rotatably supported by a support member 40 fitted to an input shaft 39 connected to an engine (not shown).

A spur gear 35a and a clutch gear 35b are integrally formed in the drive gear 35, and the drive gear 35 is rotatably supported on an input shaft 39. The clutch gear 35b is formed on the input shaft 39 by a clutch ring 41. It is connected to the gear 39a so that the connection with the input shaft 39 can be made.

The spur gear 35a is a first output shaft (not shown).
It is configured to be meshed with a spur gear (not shown) formed on the rear wheel and to transmit power to a rear front wheel differential gear mechanism (not shown).

The side gear 34 is provided with an inner race 42 press-fitted on the back surface of the side gear 34, an outer race 44 press-fitted into the interaxle differential case 43, and a plurality of roll-rotatably arranged between the inner race 42 and the outer race 44. A rolling bearing 46 composed of rollers 45 is rotatably disposed in the interaxle differential case 43.

An oil seal 50 is arranged between the inner race 42 and the outer race 44 to seal the differential mechanism portion.

A male spline 48a formed on the second output shaft 48 is spline-fitted to a female spline 34a formed on the shaft center of the side gear 34, and the rear rear wheel (see FIG. It is connected to a rear rear wheel differential gear mechanism (not shown) that transmits rotational force to the rear rear wheel differential gear mechanism (not shown).

The rotation of the input shaft 39 is
The drive gear 35 is rotated by being transmitted to the drive gear 35 via the clutch gear 39a, the clutch ring 41, and the clutch gear 35b, and the rotation is further transmitted via the first differential pinion 36 and the second differential pinion 38.
4, but the power is transmitted via the spur gear 35a and the first output shaft (not shown) and the rear front wheel differential gear mechanism (not shown) and the second output shaft 48. The differential mechanism operates according to the load acting on the rear rear wheel differential gear mechanism (not shown), and absorbs the rotation difference between the rear front wheel (not shown) and the rear rear wheel (not shown). Thus, the side gear 34 is configured to rotate.

The turbine blades 31 are for axially pumping the lubricating oil 49 stored in the oil sump 47, and a plurality of blades 31a are formed on the entire circumference to be pressed into the inner race 42. It is fixed and the inner race 4
It is designed to rotate with 2.

5 and 6, when the turbine blade 31 rotates in the direction of arrow F, the lubricating oil 49 is pumped in the axial direction (direction of arrow G).

In the oil supply passage 32, the lubricating oil 49 pumped by the turbine blades 31 is supplied with the side gear 34, the drive gear 35, the first diff pinion 36 and the second diff pinion 38.
And a side gear 3 for guiding oil to the meshing surface of the oil supply hole, provided in the oil seal 50.
4 is a communication hole 34 provided so that the gear surface and the back surface of the gear 4 communicate with each other.
b and.

Lubricating oil 49 in the oil reservoir 47, which is pumped by the turbine blades 31, is passed through the through holes 50a and the through holes 34b to the meshing surfaces of the side gear 34, the drive gear 35, the first diff pinion 36 and the second diff pinion 38. It is configured to refuel and lubricate in the direction of arrow H.

The present invention is configured as described above,
The operation will be described below. 1, 3, 5, and 6, when the engine is started and the input shaft 39 rotates, the rotation is transmitted to the drive gear 35 via the clutch gear 39a, the clutch ring 41, and the clutch gear 35b. Rotate the drive gear.

The rotation of the drive gear 35 is transmitted to the side gear 34 via the first diff pinion 36 and the second diff pinion 38, depending on the magnitude of the load acting on the rear front wheel differential gear mechanism and the rear rear wheel differential gear mechanism. The differential mechanism of the inter-axle diff 33 operates to rotate the side gear 34 at an appropriate rotation speed.

The turbine blade 31 press-fitted into the side gear 34 rotates together with the side gear 34 in the arrow F direction to pump the lubricating oil 49 stored in the oil sump 47 in the axial direction (arrow G direction). The side gear 3 is passed through the conduction hole 50a provided in the seal 50 and the conduction hole 34b provided by connecting the gear surface and the back surface of the side gear 34 to each other.
4, drive gear 35, first differential pinion 36 and second
The meshing surface of the diff pinion 38 is lubricated in the direction of arrow H to lubricate the meshing surface of each gear.

Since the lubricating oil 49 in the oil sump 47 passes through the rolling bearing 46 and is sucked by the turbine blade 31,
At the same time as oil is supplied to the meshing surface of the gear, oil is also supplied to the rolling bearing 46, and the bearing is also lubricated.

The amount of lubricating oil 49 supplied by the turbine blades 31 is determined in proportion to the rotational speed of the turbine blades 31, and when the vehicle travels at high speed, the interaxle differential 33 also rotates at high speed and a large amount of lubricating oil 49 is supplied. However, the side gear 34 can also rotate at a high speed at the time of traveling at a high speed to supply a large amount of lubricating oil 49 to the meshing surface of the gear.

[0036]

As described above, according to the present invention, the turbine blade is fixedly arranged on the rotary member of the interaxle differential as described above, and is rotated together with the rotary member to pump the lubricating oil in the axial direction so that the interaxle differential gear is rotated. Since the gear meshing surface is lubricated, there is an effect that the gear meshing surface of the interaxle diff can be reliably lubricated with a simple mechanism, and an oil pump dedicated to the interaxle diff can be eliminated. .

Further, the turbine blade is fixedly arranged on the inner race of the rolling bearing supporting the side gear of the interaxle diff, and the gear surface and the back surface of the side gear are communicated with each other to form the oil supply passage. The lubricating oil that is pumped in the direction can be supplied from the oil supply passage of the side gear to the gear of the interaxle diff from the inside, and as a result, it is possible to reliably and sufficiently lubricate the meshing surface of the gear of the differential mechanism that rotates at high speed. In addition, the higher the rotation speed, the larger the amount of lubricating oil that can be supplied, so that the temperature inside the interaxle differential can be prevented from increasing and the durability performance can be improved.

[Brief description of drawings]

FIG. 1 is a vertical cross-sectional view of an interaxle differential lubrication device.

FIG. 2 is an exploded perspective view of essential parts of an interaxle differential lubrication device.

FIG. 3 is an enlarged vertical sectional view of a main part of a lubrication device for an inter-axle differential.

FIG. 4 is a perspective view of a side gear in which an oil supply passage is formed.

FIG. 5 is a front view of a turbine blade.

FIG. 6 is a side view showing the oil supply action of the turbine blades.

FIG. 7 is an overall configuration diagram of a vehicle equipped with an interaxle differential.

[Explanation of symbols]

 30 Interaxle differential lubricator 31 Turbine blade 32 Oil supply path 33 Interaxle differential 34 Side gear 42 Inner race 46 Rolling bearing 47 Oil sump 49 Lubricating oil

Claims (2)

[Claims] 1. A turbine blade fixed to a rotary member of an interaxle diff and rotating together with the rotary member to axially pump the lubricating oil stored in an oil sump, and the lubricating oil pumped by the turbine blade. An interaxle differential lubrication device, comprising: an oil supply passage for supplying oil to a meshing surface of a gear of the interaxle differential for lubrication. 2. A turbine blade fixed to an inner race of a rolling bearing that rotatably supports a side gear of an interaxle diff, and rotating together with the inner race to pump lubricating oil stored in an oil sump in an axial direction. Lubrication of an inter-axle differential, characterized by comprising: an oil supply passage that connects the gear surface and the back surface of the side gear to each other to supply the lubricating oil pressure-fed by the turbine blades to the meshing surface of the gear of the inter-axle differential. apparatus.