JPS6081595A - Lubricating mechanism for outer periphery of rotary shaft - Google Patents

Abstract

PURPOSE:To make uniform the quantity of a lubricating oil supplied into each radial hole, by a construction wherein the tip of a lubricating pipe is extended to the deeper side of an axial hole beyond the one of a plurality of radial holes which one is the nearest to an end face of a rotary shaft. CONSTITUTION:An end part of an input shaft 100 is provided with the axial hole 170 along the center thereof, and the radial holes 171-173 are provided in the directions from the hole 170 toward the outer periphery of the shaft 100. A lubricating oil guide member 4 is disposed in the axial hole 170. The guide member 4 comprises a pipe 41 the tip of which is extended beyond the radial hole 171 to the side of the radial hole 172, a flange 42 provided as one body with an end part of the pipe 41, and a projection 44 provided on a surface on the side of the pipe 41 in the vicinity of the outer periphery of the flange 42.

Description

DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a lubrication mechanism that lubricates the outer periphery of a rotating shaft through an axial hole and a radial hole.

[Conventional example]

As a conventional lubrication mechanism for the outer circumference of a rotating shaft, for example, NrSS published by Nissan Motor Co., Ltd. in June 1942
There is something as described in AN Service Bulletin No. 440. That is, this lubrication mechanism has an axial hole that is continuously formed from the end face opening of the rotating shaft, and a radial hole that extends radially from the axial hole and opens to the outer periphery, and The tip of a pipe is inserted inside, and the rear end of this pipe is supported by a non-rotating part, and the lubricating fluid is guided and supplied to the axial hole through the inside of the pipe, and then to the outer circumference of the rotating shaft via the radial hole. It lubricates the A plurality of the radial holes are provided in the axial direction of the rotating shaft, and the lubricant supplied from the tip of the pipe passes through the axial holes and is sequentially supplied to the radial holes.

However, in the conventional /l'JJ sliding mechanism, the pipe tip does not reach any of the plurality of radial holes provided in the axial direction. For this reason, if there are multiple radial holes, the distance difference from the pipe tip will be large, so for each radial hole, the amount of lubricant supplied will be different between the one near the pipe tip and the one far away from the pipe tip. The former is larger than the latter. Therefore, in the conventional example, the amount of lubricant supplied to the outer circumference of the rotating shaft differs in the axial direction,
As a result, the degree of lubrication may become uneven in the axial direction.

To solve this problem, it may be possible to increase the amount of lubricant supplied from the pipe, but depending on your method,
An excessive amount of lubricating liquid may be supplied to the radial hole near the tip of the pipe, so there is a problem in that the driving force for supply and the total amount of lubricating liquid supplied must be increased. Another solution is to make the diameter of the radial hole proportional to the distance l15tt from the pipe, but according to this method, the diameter of each radial hole can be changed individually. This is a problem that increases manufacturing costs since it is necessary to open a tJ.

[Purpose of the invention]

The present invention has been made by focusing on such conventional problems, and the tip of the pipe is located at the back of the axial hole than the radial hole closest to the end surface of the rotating shaft among the plurality of radial holes. By arranging the lubricant in an extended manner, the total amount of lubricant supplied does not increase and the diameter of the radial hole does not change.
The purpose is to make the amount of lubricant supplied to each radial hole as uniform as possible.

[Structure of the invention]

That is, the present invention provides a rotary shaft having an axial hole continuously formed from an end face opening, and a radial hole extending radially from the axial hole and opening to the outer periphery, and supported by a non-rotating portion. and a lubricating liquid guide member whose tip end of the pipe is inserted into the axial hole of the rotating shaft and guides the lubricating liquid to the axial hole through the inside of the pipe, and the radial hole has a plurality of radial holes in the axial direction of the rotating shaft. Moisture around the outer circumference of the rotating shaft provided? In the mechanism, a gap is interposed between the outer periphery of the pipe of the lubricant guide member and the inner periphery of the axial hole, and the tip of the pipe is positioned closer to the radial hole closest to the end surface of the rotating shaft among the plurality of radial holes. This also applies to the lubrication fI mechanism on the outer periphery of the rotating shaft, which is characterized by being extended to the back side of the axial hole.

〔Example〕

Next, the present invention will be explained based on the embodiments shown in FIG. 1 and below. Figure 1 shows the gear train, final reduction gear, and differential device of a transaxle type manual transmission, where ■ is the clutch housing, 2 is the transmission case, and both are extensions that are integrated with 1.2. The differential housing 3 is configured by this. An input shaft 100, a main shaft 1-200, and a reverse idler gear shaft 300 are installed in parallel to the transmission case 2, respectively.

Impnotoshaft I-100 is rotatably supported by bearings 10t and 102, and has one end protruding into clutch housing I, and a clutch disc of a clutch device (not shown) is spline-coupled to the protruding end. Reference numeral 103 is a Tarano Chile release bearing for operating the clutch device. Inbunotoshaf +-10
0, from the bearing 101 side to the bearing 102 direction, 1st gear 1
A 10° reverse gear, 160, 2nd speed gear, 120. 3rd speed gear, 130.4th speed gear, 140.5th speed gear 150 are sequentially installed.

1st gear 110. Reverse gear 160.2nd gear 120
Both are integrally formed with the invsotoshaft 1-100, and the 3rd gear 130.4th gear 140.5th gear 1
50 is rotatably fitted directly onto the ~inbu notoshaf 1-100. Between the 3rd gear 130 and the 4th gear 140, an imp/nod shaft 00 is provided with a 3-4 continuous period device 131, and between the 5th gear 150 and the bearing 102, an input shaft is provided. 100 to 5 consecutive period device 1
51 is provided.

The main shaft 200 is rotatably supported by tapered roller bearings 201 and 202, and includes a rear main gear 270, a put gear 270, a first speed main gear 210, a reverse main gear 260, a second speed main gear 220, and a third speed main gear 230.4. Speed main gear 240.5 speed main gear 250
is provided.

The output gear 270 is formed integrally with the main shaft 200, the 1st speed main gear 21o, the 2nd speed main gear 220 are rotatably fitted directly onto the main shaft h 200, and the 3rd speed main gear 23o.

The 4-speed main gear 24o and the s-speed main gear 250 are spline-fitted to the main shaft 200 so that they rotate together. ■ A 1-2 consecutive period device 211 is provided in the main shaft l-200 between the speed main gear 210 and the second speed main gear 220, and a rehearsing main gear 260 is formed in the compression sleeve 212 of this synchronizer 211. .

■Speed gear 11 () and 1st speed main gear 210.2nd speed gear 1
20 and 2nd speed main gear 220. 3rd speed keyed 130 and 3rd speed main gear 230. 4th speed gear 140 and 4th speed main gear 2
40.5-speed gear 150 and 5-speed main gear 250 are always meshed with each other.

The reverse idler gear shaft 300 has a tip fitted into the front cover 22 of the transmission case 2, a bracket 23 fixed to the l&end and fixed to the transmission case 2 with a bolt 24, and is prevented from rotating by the bracket 23 and the bolt 24. ing. A reverse idler gear 1-360 is fitted onto the reverse idler gear shaft 300 so as to be rotatable and slidable in the axial direction. In FIG. 3, the sections of the input shaft 100 and main shaft 200 and the section of the reverse idler gear shaft l-300 are not on the same plane, so the reverse idler gear 360 and the reverse main gear 260 are separated. The reverse idler gear 360 is shown as
When in the chain line position, it meshes with the reverse gear R-160 and the rehearsing main gear 260 at the same time to transmit the rotation of the input shaft 100 to the main shaft 200.

An axial hole 170 that extends in the axial direction is bored in the center of the end of the input shaft 100 opposite to the clutch, and the input shaft 10 is formed through the axial hole 170.
Radial holes 171, 172, 173 are bored toward the outer periphery of 0. This situation is particularly shown in detail in an enlarged manner in FIG. The outer end of the radial hole 171 faces the inner surface of the fifth speed gear 150, the outer end of the radial hole 172 faces the inner surface of the fourth speed gear 140, and the outer end of the radial hole 173 faces the inner surface of the third speed gear 130. The space between the input shaft 100 and each of the gears is lubricated as described later. 104,
Reference numerals 105 and 106 denote circumferential grooves on the outer periphery of the input shaft, which communicate with the outer ends of the radial holes 171, 172, and 173 individually.

A lubricant guide A4, which is also shown in FIG. 2.3, is arranged in the axial hole 170. The liquid guide part 4 includes a pipe 41 whose tip extends past the longitudinal hole 171 and toward the radial hole 172, and a flange 42 integrally formed at the end of the pipe 41.
and the pipe 4111+ near the outer periphery of the flange 42
The entire pipe 4I is made of synthetic resin, and most of the pipe 4I except the base end is inserted into the axial hole 170. The outer diameter of the pipe 41 is such that there is some clearance between it and the axial hole 170.
Moreover, it tapers so that the diameter becomes slightly smaller toward the tip. Therefore, the gap between the axial hole 170 and the pipe 41 becomes slightly larger as it approaches the tip of the pipe 41. Further, the base end of the pipe 41 communicates with a gap 25 formed at the inner end of the transmission case 2.
A lubricating liquid is introduced into 5 through a path not shown. The protrusion 44 of the flange 42 fits into the inner surface of the outer ring of the bearing 102, and the outer edge of the flange 42 is
It is pinched between the outer ring of the bearing 102 and the I/transmission case 2, making the entire lubricant guide member 4 unrotatable.

An axial hole 280 is also formed in the first part of the clutch side part of the main shaft 200, and this and the first speed main gear 210
．． A radial hole 281 is provided between the inner surface of the second speed main gear 220 and the inner surface of the second speed main gear 220.
282 is formed. Further, the opening of the axial hole 280 has /Ii! l pFj, the growth guide member 5 is arranged to introduce the lubricating fluid supplied into the gap 26 through a path not shown into the axial hole 280, and further into the radial holes 284, 282.
The main shaft 200 and the 1st speed main gear 21
This is to lubricate the gap between the main gear 220 and the 0.2 speed main gear 220.

Inside the differential housing 3, a bearing 4'
Differential gear case 40 by 01,402
0 is rotatably supported. A ring gear 420 is fixed to the differential gear case 400 with bolts 421. Bolts 421 press and fix flange 410 of differential gear case 400 and inward flange 422 of ring gear 420. The ring gear 420 is always meshed with the automatic gear 270 to constitute a final reduction gear.

A pinion mate shaft 430 is installed inside the differential gear case 4oo and is prevented from being pulled out with a pin 431. Two pinion gears 440 are fitted onto the pinion mate shaft 430 so as to be rotatable facing each other. The two Zydogyas 450 are individually engaged to form a differential device. Both side gears 45
0, the inner ends of two drive shafts (not shown) each having a front drive wheel attached to their outer ends are individually fixed. 460
is a ring gear for a speedometer.

Next, the action will be explained.

The transmission shown in FIG. 1 is in a neutral position, and the rotational force transmitted from the engine to the implant gear 1-1 gear 71-100 through the clutch causes the input shaft 100 and the first gear 11O, reverse gear 160. 2nd gear 12
Therefore, the first speed main gear 210 and the second speed main gear 220 also rotate at all times. However, in this neutral position, no rotational force is transmitted to the 3rd speed gear 130, ξ Liao gear 140, 5th speed gear 150, and reverse idler gear 360, and the 1st speed main gear 210 and 2nd speed main gear 220 are also just idling. Therefore, the rotational force of the engine has not yet been transmitted to the main shaft 200.

Therefore, when shifting to the 1st forward speed position, the 1st-2nd speed synchronizer 211 operates to the 1st speed side, and the rotational force of the 1st speed main gear 210 is transferred to the main shaft l'' via this synchronizer 211.
200. Thus, ■speed gears 110 and 1
Main shaft 2 due to the gear ratio with main gear 210
00 rotates, and the rotational force is transmitted to the ring gear 420 from the gears 1 to 270 that rotate together with it.
The differential gear case 400 is decelerated and rotated. Due to the rotation of the differential gear case 400, the double-member shaft 430 rotates around its center in the longitudinal direction, and rotates the pinion gear 440 on a circular orbit, thereby allowing both side gears 450 to operate differentially. Rotate and rotate. This Zytoga 45
The zero rotation is directly transmitted to the drive wheels (front wheels) via the drive shirt 1-.

Further, when shifting to the forward second speed position, the 1st-2nd speed synchronizer 211 operates to the 2nd speed side, and the rotational force of the 2nd speed main gear 220 is transferred to the main shaft 20 via this synchronizer 211.
Transmitted to 0. In this way, the main shaft 20 is
0 rotates. Next, when shifting to the 3rd forward speed position, 3
- The 4th speed synchronizer 131 operates to the 3rd speed side, causing the input shaft 100 and the 3rd speed gear 130 to rotate together.

The rotational force of the 3rd speed gear 130 is transmitted to the main shaft 200 via the 3rd speed main gear 230 that is always in mesh with the third speed gear 130. Depending on the shift to the forward 4th gear position, 3-
The 4-speed synchronizer J31 operates to the 4-speed side and rotates the input shaft -100 and the 4-speed gear 140 together. Therefore, the rotational force of the 4th gear 140 is the same as that of the 4th gear main gear 240.
It is transmitted to the main shuffle l-2QO via. Furthermore, when shifted to the forward 5th speed position, the 5th speed synchronizer 1
51 is activated and the impact shaft 100 and 5th gear 1
50 is rotated integrally with the 5th speed gear 1'l.The rotational force of the 50 is transmitted through the 5th speed main gear 250 to the main shaft
200. The rotational force of the main shaft 200 at each of these shift 1-positions is transmitted to the driving wheels through the same differential gear as described above.

Also, when the reverse position is moved, the rehearsing idle gear shirt 1-360 will change to the reverse idle gear shirt 1-30.
0 to the position indicated by the chain line in Fig. 1, and set reverse gear 1.
60 and the rehearsing gear 260. As a result, the rotational force of the reverse gear 160 is transmitted to the rehearsing main gear 260 via the reverse idler gear 360, and this rotational force is further transmitted to the main shaft, which rotates integrally with the compacting sleeve 212 on which the rehearsing main gear 260 is formed. 1 to 200. In this case, since the reverse idler gear 360 is interposed in the rotational force transmission path, the main shaft 200 is
Rotates in the opposite direction to the speed.

The rotational force of the main shaft 200 is transmitted to the drive wheels through the same path as described above, but the rotational direction is reversed.
To explain the lubrication between the speed gear 140 and the fifth speed gear 150, the lubricating fluid supplied to the gap 25 through a path not shown is /Ii! The synovial fluid guiding part 4 is introduced from the pipe 41 into the axial hole 170.

The lubricating fluid flows from the axial hole 70 to the radial hole 171.
172 and 173 respectively to the circumferential groove 104°105.1
06, where it is guided in the circumferential direction of the outer surface of the input shaft 100 and is supplied between each gear 130, 140, 150 and the input shaft 100 to lubricate each friction portion. Here, since the tip of the pipe 41 extends past the radial hole 171 and toward the radial hole 172, the 7% moisture liquid is sufficiently supplied even to the radial hole 173 at the back of the axial hole 170. Ru.

In this way, if the pipe 4I extends deep, the axial hole 1
The reason why the lubricating fluid is sufficiently supplied to the depths of the pipe 70 is that the pipe 41 is supported by a non-rotating part, so that inside the pipe 41 /li! No centrifugal force acts on the 19% solution,
This is because the lubricating fluid is not forced in the centrifugal direction, and its flow resistance becomes extremely small. In addition, the supply of /l1iI synovial fluid to the radial hole 171 is performed using the vibrator 4.
It is performed from one tip through the gap between the outer periphery of the vibrator 41 and the inner periphery of the axial hole 170. Pipe 41 tip and axial hole 1
70, sufficient lubricant is supplied to the axial hole 170 even through the gap as described above.

In this way, the tip of the pipe 41, which was conventionally far from the radial holes 173, 172, is closer in this embodiment, so the amount of lubricant supplied to the radial holes 173, 172, which conventionally was at risk of being insufficient, has been reduced in this embodiment. While it is sufficient for
/lj? to radial direction γL171? Since the Fk liquid is also supplied from the tip, which is the outlet of the pipe 41, through the outside thereof, it is sufficiently supplied to each radial hole 171, 172, 173.
The amount of lubricating fluid supplied to the system has also become nearly uniform. In particular, pipe 41
Since the tip is tapered to become gradually thinner, the moisturizing liquid that enters the gap between the input shaft 100 and the pipe 41 is difficult to flow back through the gap toward the end of the input shaft 100.

FIG. 4 is a diagram showing a second embodiment of the present invention, and shows an example in which the tip of a pipe 41 overlaps the radial holes 171 and 172 and extends to the back side of the radial hole 172. .

A communicating hole 45 is opened in the pipe 41 at a position corresponding to the radial hole 171. The lubricant can be supplied from halfway to the radial hole 171 located far from the tip of the tube 41. Similarly to the radial hole 171 of the first embodiment (particularly shown in FIG. 3), the radial hole 172 is designed so that lubricating fluid can be supplied through the gap between the inner periphery of the axial hole 170 and the outer periphery of the vibrator 41. It's Nishide.

Other configurations and operations are similar to those of the first embodiment.

FIG. 5 is a diagram showing a third embodiment of the present invention, in which the diameter of the communication hole 45 corresponding to the radial hole 171 of the second embodiment is enlarged, and the position corresponding to the radial hole 172 is This is an example in which a small diameter communication hole 46 is provided. Radial hole +72
In addition to the lubricating fluid supplied from the communicating hole 46, there is lubricating fluid supplied from the tip of the pipe 41 through the gap between the axial hole 170 and the pipe 41, so the diameter of the communicating hole 46 is small. It has become. Other configurations and operations are similar to those of the first embodiment.

The amount of lubricant supplied to each radial direction TL can be adjusted by setting the presence or absence of the communication hole 45, 46 and its diameter according to conditions such as the distance between each radial hole 171, 172, 173. is as uniform as possible.

Note that in these embodiments, the present invention was applied to the input shaft 100 of a manual transmission as a rotating shaft.
Of course, the rotating shaft may be the main shaft 200, or may be applied to a shaft that rotates in a device other than the transmission.

〔Effect of the invention〕

As explained above, according to the present invention, a gap is interposed between the outer periphery of the pipe of the lubricant guide member and the inner periphery of the axial hole of the rotating shaft, and the tip of the pipe is connected to the rotating shaft of the plurality of radial holes. The radial hole closest to the end face of the axial hole is extended to the back of the axial hole. For this reason, the pipe tip approaches the radial hole on the back side of the axial hole, so
The radial holes are sufficiently supplied with lubricating fluid. In addition, lubricating fluid is supplied to the radial hole in which the pipe is overlapping from the tip of the pipe through the gap between the pipe and the axial hole. In this way, the lubricant can be supplied to each radial hole as uniformly as possible without increasing the total amount of lubricant supplied or changing the diameter of the radial hole.

[Brief explanation of the drawing]

FIG. 1 is an overall sectional view showing the first embodiment of the present invention;
The figure is a perspective view of the lubricant guide member, Figure 3 is an enlarged view of the main part of Figure 1, Figure 4 is an enlarged sectional view of the main part of the second embodiment, and Figure 5 is an enlarged view of the main part of the third embodiment. FIG. ■...Clutch housing, 2...L-transmission case, 3...Differential housing, 4...Lubricant guide member, 41...Pipe, 42...
...Flange part, 44...Protrusion, 45.46...Communication hole, 100...Input shaft (rotating shirt l
-), 200... Main shaft, 300... Reverse idler gear shaft, 400... Differential gear case, 430... Pinion no. 1-shaft 440- - Pinion gear, 450... Zydogya, Patent applicant Nissan Motor Co., Ltd. Agent Patent Attorney Tetsuya Mori Agent Patent Attorney Yoshiaki Naito Agent Patent Attorney Shimizu Authorized Agent Patent Attorney Submission Complaints

Claims (1)

[Claims] A rotary shaft having an axial hole continuously formed from an end face opening and a radial hole extending radially from the axial hole and opening to the outer periphery, supported by a non-rotating part, and having a rotatable tip end of the pipe. a lubricating fluid guide member that is inserted into an axial hole of the shaft and guides lubricating fluid to the axial hole through the inside of a pipe, and a plurality of longitudinal holes are provided in the axial direction of the rotating shaft. Water around the outside! In the H & structure, a gap is interposed between the outer circumference of the pipe of the wet blue liquid guide part and the inner circumference of the axial hole, and the tip of the pipe is
A rotary shirt 1--outer periphery moisture lh mechanism, characterized in that, among the plurality of radial holes, the one-row hole closest to the end surface of the rotary shaft is extended to the back side of the axial hole.