JPS6140863B2 - - Google Patents

Abstract

PURPOSE:To prevent oil from degradation to improve the lubricating performance by supplying the oil scraped up by the right side support case and a ring gear through a cooling chamber provided in the front portion of a carrier cover. CONSTITUTION:Oil scraped up and splashed by the outer teeth of a ring gear 3 is introduced directly or from an oil catcher 27 into receiving ports 26, 28. The oil introduced into the receiving port 28 is supplied from a path 29 to the bearing for a pinion drive gear 2. The oil introduced into the receiving port 26 is sent from an introducing port 25 to a cooling chamber 21. Oil attached to the right side support case 3R is blocked by a catcher 31 during the rotation of the gear and enters the cooling chamber 21 from an introducing port 30. The oil in the cooling chamber 21 is cooled by air passing along the outer peipheral wall and passes through a discharge port 35 and cavity 34 to lubricate a bearing 11 and then sequentially passes through an inner through hole to lubricate the interior. Thus, the oil is prevented from degerdation caused by the rise of oil temperaure.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a reduction differential for a vehicle, and more particularly to a two-stage reduction type reduction differential in which rotation of a ring gear transmitted by a pinion drive gear is reduced by a planetary gear and transmitted to a differential. It relates to a lubricating device for equipment.

Hereinafter, the structure and operation of the speed reduction differential device of the above type will be explained based on FIG. 1. In the figure, a pinion drive gear 2, which is connected to an output shaft of a transmission (not shown) via a propulsion shaft, is supported by a sleeve 1b by tapered bearings 2a, 2b.
The sleeve is attached to the front end of the carrier cover 1a with bolts 1d. The pinion drive gear 2 meshes with external teeth 3a of a ring gear 3 which is supported on the rear side wall of the carrier cover 1a via side bearings 11 and 16, and the rotation of the pinion drive gear 2 causes the ring gear 3 to be decelerated and rotated. do. An adjustment nut 16A for adjusting the preload of the side bearing 16 is attached to the bearing cylinder portion 3La of the left side support case 3L, which is integrally fixed to the ring gear with a bolt 3L.
and is spline-coupled to substantially the carrier cover 1a.
A sun gear 4 assembled in a fixed state is attached so as to float through the bearing cylinder part 3La, and the tooth part 4a of the sun gear 4 and the ring gear 3
A plurality of planetary gears 5 meshing with internal teeth 3c of the differential case 6l are attached via bearings 7a to a shaft 7 fixed to the side surface of the differential case 6l. It revolves around the ring gear 3 at a rotation speed that is slower than the rotation speed of the ring gear 3. Inside the differential cases 6l, 6r that rotate as the planetary gear 5 revolves, a pair of side gears 8l, 8r are coaxially supported with the sun gear 4.
are in mesh with each other through four pinion gears 9a, 9b (two in the figure) supported by a cross-shaped spider shaft 17 at right angles to the first pair of side gears 8.
The inner end portions of axle shafts (not shown), which are connected to the left and right wheels, respectively, are fitted into the wheels 1 and 8r and are spline-connected. When the vehicle is running straight, the pinion gears 9a and 9b do not rotate around the spider shaft 17, and therefore the pair of side gears 8l and 8r are connected to the differential case 6.
The pinion gears 9a and 9b rotate in synchronization with the rotation of the spider shaft 17 and the pair of side gears 8 when the vehicle is turning.
It is well known that a rotational speed difference of 1 and 8r is allowed.

Further, a cylindrical right support case 3R fixed to the right side of the ring gear 3 and covering the differential cases 6l and 6r is supported by a side bearing 11 on one side wall at the rear of the carrier cover 1a. The side bearing 11 has an adjustment nut 11 similar to the side bearing 16.
It is attached to the carrier cover 1a with a preload defined by a.

The sliding parts and meshing parts of bearings, gears, etc. of such a reduction differential are lubricated by the ring gear, pinion drive gear, and support immersed in oil stored at the bottom of the space A surrounded by the carrier cover 1a and the housing 1c. The oil scraped up by a rotating body such as a case is captured above the front of the rotating body and then supplied to each lubricating main part. In this type of oil bath lubrication method, most of the oil that is stirred up by the rotation of the ring gear, which has the largest diameter, either falls back into the oil pool due to centrifugal force on the way, or falls between the ring gear and pinion drive gear. The oil is captured by the oil catcher integrally molded on the carrier cover above the meshing part of the pinion drive gear, and is supplied only to the front end bearing of the pinion drive gear, thereby lubricating the bearing of the support case and the main parts of the bearing inside the support case. In order to do this adequately, the amount of oil must be increased to raise the oil level in the oil reservoir, or oil must be captured from rotating bodies other than the ring gear and supplied to the necessary lubrication parts.

However, in the oil bath lubrication method, the amount of oil is increased to raise the oil level in the oil reservoir.
When lubricating the bearing part of the support case and the inside of the support case, the resistance to agitation of the oil by the ring gear etc. increases, the oil temperature rises, the oil tends to deteriorate, and the lubrication performance is impaired, which is undesirable.

On the other hand, even when lubricating the bearing part of the support case and the inside of the support case with oil scraped up by a rotating body other than the ring gear, such as the cylindrical right support case peripheral wall, the oil level decreases as the vehicle speed increases. In order for the right side support case, which has a smaller diameter than the ring gear, to be sufficiently immersed in oil even during high-speed rotation, it is necessary to increase the amount of oil and raise the oil level accordingly, which increases stirring resistance and increases oil temperature. , it is inevitable that the oil will deteriorate early and the lubrication performance will deteriorate.

In addition, as a conventional example of this system, for example, as shown in FIG. 2, a separate oil catcher 12 is fixed with bolts or the like to a partition wall that connects the rear end bearing of the pinion drive gear to the carrier cover peripheral wall. Right side support case 3R by 12
The oil scraped from the peripheral wall is guided to the side cavity 14 via the oil hole 13, and from this cavity the oil is transferred to the bearing 11 for the right support case bearing and the oil hole 3Ra provided in the right support case to the support. Some are designed to be supplied inside the case.

However, in this case, in order to guide enough oil into the support case 3R, the oil catcher 1
2 and the support case 3R are in contact as shown in Fig. 2B, and especially during high speed rotation, the oil collides with each other on the oil catcher 12 and the toy 12a, and as a result, the oil that has risen in temperature remains in the poles. Since the oil is supplied to the lubricating part through a short path, the oil temperature rises and the lubricating performance further deteriorates.If the oil amount is reduced to a certain extent to reduce stirring resistance, due to fluctuations in vehicle speed,
The amount of oil scraped by the oil catcher 12 changes greatly, and the amount of oil supplied to the main lubrication parts changes sensitively to fluctuations in vehicle speed, making it difficult to maintain stable lubrication performance.

Furthermore, as mentioned above, the conventional oil catcher is provided in contact with the outer peripheral wall of the right support case or close to it with a very small gap of 1 mm or less for the purpose of scraping off oil. To avoid interference between the catcher and the right support case, they must be molded separately from synthetic resin. Therefore, wear of the oil catch or heat generated when oil passes through the gap also results in an increase in oil temperature.

The present invention has been made in view of these conventional drawbacks, and has a structure in which the bearing part of the support case and the inside of the support case are lubricated by supplying oil scraped up by a ring gear together with the right support case at all vehicle speeds. In addition to ensuring a stable supply of oil over the area, a cooling chamber with good heat dissipation defined by the outer and inner walls of the carrier cover is interposed in the oil path to the lubricating part, and the oil is temporarily transferred to the lubricating part. A first object of the present invention is to provide a lubricating device for a two-stage reduction type reduction differential device, which effectively lowers the oil temperature while remaining in a cooling chamber, thereby greatly improving the lubrication performance.

Further, in addition to the above configuration, it is an object of the present invention to provide a two-stage reduction type reduction differential device which is equipped with an oil distribution mechanism that efficiently distributes and supplies the oil scraped up by the ring gear to the cooling chamber and the bearing section of the pinion drive gear. This is the second purpose.

In addition, a certain level is provided in the oil window of the cooling chamber where the oil that is splashed and splashed by the support case during high-speed rotation will fall, and a restriction is provided at the outlet of the cooling chamber to temporarily store the oil in the cooling chamber. A third object of the present invention is to provide a two-stage reduction type reduction differential device that is cooled by being exposed to the outer wall and suppresses a rise in oil temperature during high-speed rotation.

Embodiments of the present invention will be described below based on the drawings. However, since the structure of the gear reduction differential mechanism is the same as that shown in FIG. 1, the same reference numerals will be used for explanation.

The present invention is constructed by forming an oil path as described below by a partition wall integrally formed inside the carrier cover. In FIG. 3, the space above the pinion drive gear 2 in the carrier cover 1a and in front of the right support case 3R is partitioned by a partition wall into a cooling chamber 21.
form. The cooling chamber 21 includes a bottom wall 22 that closely covers the upper part of the pinion drive gear 2, a side wall 23 that faces the circumferential side of the ring gear 3 and stands upright from the bottom wall 22 in the front-back direction, and A side wall 24 including the rear end bearing portion and standing upright facing the peripheral wall of the right side support case 3R and the carrier cover 1a.
It is defined by the outer peripheral wall of. A first oil inlet 25 is provided at the front end of the side wall 23.
An oil passage is connected to the cooling chamber 21 from an oil receiving port 26 adjacent to the oil inlet 25 and in front of the external teeth of the ring gear 3 through the first oil inlet 25, and an oil passage is connected in parallel to the oil passage. A first oil catcher 27 consisting of an oil passage 29 connecting a socket 28 and a front end bearing portion of the pinion drive gear 2 is disposed by extending the wall portion of the cooling chamber 21.

On the other hand, in the side wall 24 facing the peripheral wall of the right support case 3R, a second oil inlet 30 that communicates the inside and outside of the cooling chamber 21 is provided on the side closer to the side wall 23, and the second oil inlet 30 is provided on the rear surface of the side wall 24. 30
A gutter-shaped second oil catcher 31 having a bottom surface slightly below the lower edge of the oil catcher 31 is provided with its upwardly curved tip protruding close to the upper part of the peripheral wall of the right support case 3R. The inlet portion of the second oil inlet 30 has a height D, as shown in FIG. It is sufficient that the height is as high as .

Further, the partition wall 33 extending rearward from the end of the second oil catcher 31 and standing upright has a cavity chamber 34.
The cavity 34 communicates with the bearing 11 of the right support case 3R, and also communicates with the case 3R via an oil hole 3Ra opened in the right support case 3R. An oil outlet 35 is provided in the side wall 24 to communicate the cooling chamber 21 with the oil outlet 34 .

With this configuration, rotation of the ring gear 3 in the direction of the arrow shown in the figure, which is immersed in the oil stored at the bottom of the space A surrounded by the carrier cover 1a and the housing 1c, causes the rotation of the ring gear 3 from the external teeth 3a of the ring gear 3 in the centrifugal direction. A portion of the oil splashed on the carrier cover 1a is distributed and introduced into the pair of parallel oil receiving ports 26 and 28 of the first oil catcher 27, either directly or along the inner circumferential surface of the carrier cover 1a. The oil introduced into one oil socket 28 is supplied to the front end bearing portion of the pinion drive gear 2 through the oil passage 29, and lubricates the bearing portion to make the rotation of the pinion drive gear 2 smooth. or,
The oil introduced into the other oil receiving port 26 flows into the cooling chamber 21 via the first oil inlet 25.

On the other hand, the lower part of the peripheral wall of the right support case 3R is also immersed in the oil, and therefore, when a part of the oil adhering to the peripheral wall of the case 3R due to the rotation of the case 3R passes through the second oil catcher 31, the catcher At the same time, the oil flows into the cooling chamber 21 from the second oil inlet 30.

In this way, the oil that has flowed into the cooling chamber 21 from the first oil inlet 25 and the second oil inlet 30 is cooled in the cooling chamber 21, and then the oil flows into the cooling chamber 21.
The oil flows out from the oil outlet 35 into the cavity 34, is supplied to the bearing 11 for the support case bearing, and lubricates the bearing 11, and is also supplied to the inside of the right support case 3R through the oil hole 3Ra, and is supplied to the inside of the right support case 3R, and is supplied to the bearing 11 for the support case bearing to lubricate the bearing 11. Side gears _8l , 8r and pinion gear 9a,
Lubricating the meshing part of the ring gear 9b and each bearing part, the meshing part between the internal teeth 3c of the ring gear and the planetary gear 5,
It lubricates the meshing part between the sun gear 4 and the planetary gear 5, and reaches the bearing 16 of the ring gear 3 through the communication groove 15 formed on the inner peripheral surface of the cylindrical portion 3La of the ring gear 3 and the inner peripheral surface of the housing 1. Lubricate.

With this configuration, the surface area that comes into contact with the oil in the cooling chamber 21 is large, and the outer circumferential wall of the front end of the carrier cover 1a that defines the cooling chamber 21 is connected to the air flowing from the front to the rear of the vehicle as the vehicle travels. Since the oil in the cooling chamber 21 is effectively dissipated by contact, the oil in the cooling chamber 21 is effectively cooled, and the lubrication performance of each of the above-mentioned lubrication main parts to which the oil is supplied after flowing out of the cooling chamber 21 can be improved.

In addition, since oil is supplied to the bearing portion 11 of the right side support case 3R and the inside of the right side support case 3R by also supplying a portion of the oil scraped up by the ring gear 3, the ring gear 3 is Even if the oil level decreases due to an increase in rotational speed and the amount of oil that adheres to the peripheral wall of the right side support case 3R and is scraped up decreases, the oil scraped up by the ring gear 3 with a large diameter provides a stable and sufficient oil supply. quantity can be secured. In other words, since the amount of oil in the carrier cover 1a can be reduced to just enough to immerse the ring gear 3 at high speeds, the temperature rise due to oil stirring resistance can be suppressed and the lubrication performance can be improved from this aspect as well.

In addition, the second oil inlet 30 is opened at the front of the peripheral wall of the right support case 3R, and the centrifugal force caused by the rotation of the right support case 3R easily causes the second oil inlet 30 to jump into the cooling chamber 21 (especially at high speeds). (Sometimes, the amount of oil that jumps directly into the cooling chamber 21 from the second oil inlet 30 without going through the second oil catcher 31 increases), because the second oil catcher 31 guides oil into the cavity 34 during low speed rotation. It is sufficient to have the function of damming up the flow of oil. That is, the oil catcher 1 shown in FIG.
2, it was necessary to scrape oil into the oil catcher 12, so it was necessary to bring the oil catcher 12 into contact with or sufficiently close to the peripheral wall of the right support case 3R, but in the present invention, during low speed rotation,
The oil scraped up by ring gear 3 flows into cooling chamber 2.
The oil that is guided to the cavity 34 via the second catcher 31 and scraped up by the right support case 3R is captured by the second catcher 31, guided to the cavity 34, and merges with the oil from the ring gear. Since the oil reaches inside the right support case 3R, it is sufficient for the second oil catcher 31 to have the function of damming up the oil as described above, so it is sufficient to widen the gap between its upper edge and the peripheral wall of the right support case 3R to about 5 mm. It can fulfill that function. Therefore, heat generation of the oil when passing through the gap between the second oil catcher 31 and the right side support case 3R peripheral wall can be suppressed.
In addition to suppressing the rise in oil temperature, the processing accuracy of the second oil catcher 31 is low and it can function satisfactorily even as cast, leading to cost reduction.

In addition, a device that conventionally had the function of scraping oil from the ring gear teeth and distributing it to the lubricating section is molded separately from the carrier cover, and the device is attached to a hole opened in the upper part of the front end wall of the carrier cover. There is also. However, in this case, it is difficult to form holes in the carrier cover, and the holes must be made small in terms of strength. Therefore, the oil supply device assembled into the hole is necessarily limited to a small size, and has the drawback that it lacks oil scraping ability and cannot perform its full function.

In contrast, the first oil catcher 27 of the present invention
The oil passage 29 is cast integrally with the carrier cover 1a, and the first oil catcher 27 functions as a reinforcing material, so the strength of the carrier cover 1a is further increased, and the oil socket can be set large, and the carrier cover Since the oil can also flow into the oil sockets 26 and 28 through the peripheral wall surface 1a, a sufficient amount of oil can be ensured. Therefore, the gap between the oil sockets 26, 28 and the three teeth of the ring gear can be widened, so that it can function satisfactorily as cast, and in this case as well, the rise in oil temperature can be suppressed and the lubrication performance can be improved.

As explained above, the present invention lubricates the bearing parts of the left and right side support cases and the inside of the support case by using a heat dissipating system that uses oil scraped up by a large diameter ring gear together with the right side support case and is integrally molded with the carrier cover. Because it is configured to supply oil through the cooling chamber, it is possible to ensure a stable and sufficient oil supply regardless of fluctuations in vehicle speed, and it is also possible to supply oil that has been effectively cooled within the cooling chamber, suppressing oil deterioration and improving lubrication performance. can be significantly improved.

Further, according to the second invention, in which an oil passage leading to a pinion drive gear is arranged in parallel with an oil catch that leads oil scooped up by a ring gear to a cooling chamber, an appropriate ratio between the oil catch and the oil passage can be achieved. Since the oil is distributed and supplied, each lubricating part within the housing can be lubricated evenly and stably. In addition, a certain level is provided in the oil window (second oil inlet) of the cooling chamber, into which the oil that is scraped up and scattered by the support case during high-speed rotation falls, and a restriction is provided at the outlet of the cooling chamber, and a temporary cooling chamber is installed. By storing oil in the cylinder and exposing it to the outer wall, the oil is cooled and the rise in oil temperature during high-speed rotation is suppressed, which suppresses oil deterioration and maintains a high level of lubrication performance over a long period of time.

[Brief explanation of the drawing]

Fig. 1 is a cross-sectional view showing the deceleration mechanism of a vehicle deceleration differential, Figs. 2 A and B are cross-sectional views and longitudinal sectional views of main parts showing the configuration of a conventional oil supply mechanism, and Figs. 3 A-- D shows an embodiment of the present invention, A is a partially sectional perspective view of the carrier body, B is a cross-sectional view, and C and D are longitudinal sectional views seen from the right side and the front, respectively. 1a...Carrier cover, 2...Pinion drive gear, 3...Ring gear, 3R...Right side support case, 4...Sun gear, 5...Planetary gear, 6l, 6r...Differential case, 11...Bearing, 21... Cooling chamber, 22...Bottom wall, 23,
24... Side wall, 25... First oil inlet, 2
6, 28...Oil socket, 27...First oil catcher, 29...Oil passage, 30...Second
Oil inlet, 31...second oil catcher,
34...Cavity part, 35...Oil outlet.

Claims (1)

[Scope of Claims] 1. A pinion drive gear that rotates when engine driving force is transmitted thereto, a ring gear that rotates with external teeth meshing with the pinion drive gear, and an internal tooth of the ring gear that is fixed coaxially with the ring gear. a planetary gear that meshes with a sun gear and revolves around its axis; a differential case that pivotally supports the planetary gear and rotates integrally with the rotation of the planetary gear; a support case that covers the outside of the differential case and is fixed to the ring gear; A vehicle comprising a carrier cover that rotatably encloses each of these rotating elements and a housing that pivotally supports an axle, and in which lubricating oil is stored at the bottom of a chamber surrounded by the carrier cover and the housing. In the reduction differential, a cooling chamber is formed by partitioning the front space above the pinion drive gear in the carrier cover with a partition wall that is integrated with the carrier cover, and a cooling chamber is formed on the side wall facing the circumferential side of the ring gear. A first oil catcher is provided extending from the wall of the cooling chamber, and a first oil catcher is provided to guide the oil scooped up by the ring gear into the cooling chamber through at least the first oil inlet; A second oil inlet is provided on the side wall of the cooling chamber facing the support case peripheral wall, and a gutter-shaped second oil catcher is provided protruding along the second oil inlet adjacent to the support case peripheral wall. A lubricating device for a reduction gear differential for a vehicle, characterized in that an oil outlet is opened facing a bearing part of a support case and a passage leading to the inside of the support case. 2 In the first oil catcher, a partition wall defines a passage for guiding the oil scooped up by the ring gear to the cooling chamber through the first oil inlet and a passage for guiding the oil to the bearing portion of the pinion drive gear in front of the ring gear. The lubricating device for a vehicle speed reduction differential according to claim 1, which is formed in a structure having an oil distribution function provided in parallel. 3. The second oil inlet is opened at a predetermined height from the bottom wall of the cooling chamber, and the oil outlet of the cooling chamber is formed with a restriction, so that the oil introduced into the cooling chamber is temporarily 3. The vehicle deceleration differential device according to claim 1 or 2, characterized in that the vehicle is stored in a cooling chamber.