JPH0343518B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION [Industrial Technical Field] 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]

Conventional lubrication mechanisms for the outer circumference of rotating shafts include:
For example, there is one described in NISSAN Service Bulletin No. 440 published by Nissan Motor Co., Ltd. in June 1981. 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 has a radial hole that is open to the outer circumference. The tip of the pipe is inserted into the pipe, and the rear end of this pipe is supported by a non-rotating part, and the lubricant 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.
A plurality of the radial holes are provided in the axial direction of the rotating shaft, and the lubricating fluid supplied from the tip of the pipe passes through the axial holes and is sequentially supplied to the radial holes.

However, in the conventional lubrication mechanism, the pipe tip does not reach any of the plurality of radial holes provided in the axial direction. For this reason, in the case of multiple radial holes, the difference in perspective from the pipe tip becomes large, so for each radial hole, the amount of lubricant supplied is different between the one near the pipe tip and the one far from the pipe tip. The former is larger than the latter. For this reason, in the conventional example, the amount of lubricating fluid supplied to the outer periphery of the rotating shaft differs in the axial direction, and as a result, the degree of lubrication may become non-uniform in the axial direction.

In order to solve this problem, it may be possible to increase the amount of lubricant supplied from the pipe, but this may result in excessive lubricant being supplied to the radial hole near the tip of the pipe. However, there is a problem in that the driving force for supply and the total amount of lubricant supplied must be increased. Another solution would be to increase the diameter of the radial holes in proportion to the distance from the pipe, but this method would allow each radial hole to be opened with its diameter changed individually. This is a problem that increases manufacturing costs.

[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. The aim is to make the total amount of lubricant supplied to each radial hole as uniform as possible without increasing the total amount of lubricant supplied and without changing the diameter of the radial hole. There is.

[Structure of the invention]

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 a rotating shaft supported by a non-rotating portion and having a pipe. a lubricating fluid guide member whose tip end is inserted into the axial hole of the rotating shaft and guides the lubricating fluid to the axial hole through the inside of the pipe, and a plurality of the radial holes are provided in the axial direction of the rotating shaft. In the lubrication mechanism for the outer periphery of a rotating shaft, the outer periphery of the pipe of the lubricant guide member is formed into a gentle taper, and the outer periphery of the pipe is formed between the outer periphery of the pipe and the inner periphery of the axial hole of the rotating shaft into which the pipe is inserted. In addition, the pipe tip 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. It applies to the lubrication mechanism around the outer circumference of the rotating shaft, which is extended.

〔Example〕

Next, the present invention will be explained based on the embodiments shown in FIG. 1 and below. Figure 1 shows a transaxle type manual transmission, a gear train, a final reduction gear, and a differential device. 1 is a clutch housing, 2 is a truss transmission case, and both 1 and 2 are integrated. A differential housing 3 is configured by the extended portion. An input shaft 100, a main shaft 200, and a reverse idler gear shaft 300 are installed in parallel to the transmission case 2, respectively.

The input shaft 100 has bearings 101,1
02, and has one end protruding into the clutch housing 1, and a clutch disk of a clutch device (not shown) is spline-coupled to the protruding end. 103 is a clutch release bearing for operating the clutch device. The input shaft 100 includes a first gear 11 from the bearing 101 side to the bearing 102 direction.
0, reverse gear 160, second gear 120, third gear 130, fourth gear 140, and fifth gear 150 are provided in this order.

1st gear 110, reverse gear 160, and 2nd gear 120 are all formed integrally with input shaft 100, and 3rd gear 130, 4th gear 140, and 5th gear 150 are rotatably formed on input shaft 100. is fitted directly onto the outside. 3rd gear 1
A 3-4 speed synchronizing device 131 is provided between the input shaft 100 and the 4th speed gear 140, and a 5th speed synchronizing device 131 is provided between the 5th speed gear 150 and the bearing 102. Device 1
51 is provided.

The main shaft 220 has a tapered roller bearing 201,
202, which includes an output gear 270, a first speed main gear 2
10, a reverse main gear 260, a second speed main gear 220, a third speed main gear 230, a fourth speed main gear 240, and a fifth speed main gear 250 are provided.
Output gear 270 is main shaft 200
1-speed main gear 210,
The 2nd speed main gear 220 is rotatably fitted directly onto the main shaft 200, and the 3rd speed main gear 23
0, 4th speed main gear 240, 5th speed main gear 25
0 is spline-fitted to the main shaft 200 and rotates integrally with the main shaft 200. A 1-2 speed synchronizer 211 is provided in the main shaft 200 between the 1st speed main gear 210 and the 2nd speed main gear 220, and a reverse main gear 260 is formed in a coupling sleeve 212 of this synchronizer 211.

1st speed gear 110 and 1st speed main gear 210, 2nd speed gear 120 and 2nd speed main gear 220, 3rd speed gear 1
30 and 3rd speed main gear 230, 4th speed gear 140 and 4th speed main gear 240, and 5th speed gear 150 and 5th speed main gear 250, respectively, are always in mesh with each other.

The reverse idler gear shaft 300 has a bracket 2 whose tip is fitted into the front cover 22 of the transmission case 2 and fixed to the rear end.
3 is fixed to the transmission case 2 with a bolt 24, and this bracket 23 and bolt 2
Rotation is stopped by 4. A reverse idler gear 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 300 are not in the same plane;
60, when the reverse idler gear 360 is in the chain line position, it simultaneously meshes with the reverse gear 160 and the reverse main gear 260 and transfers the rotation of the input shaft 100 to the main shaft 200. It is designed to communicate.

An axial hole 170 extending in the axial direction is bored in the center of the end of the input shaft 100 opposite to the clutch, and a radial hole extends from the axial hole 170 toward the outer periphery of the input shaft 100. 171, 172, and 173 are drilled. 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 13.
Facing the inner surface of the input shaft 100, the space between the input shaft 100 and each of the gears is lubricated as described later. Reference numerals 104, 105, and 106 are circumferential grooves on the outer periphery of the input shaft 100, which communicate with the outer ends of the radial holes 171, 172, and 173, respectively.

A lubricant guide member 4, which is also shown in FIGS. 2 and 3, is arranged in the axial hole 170. Lubricant guide member 4
, the tip passes past the radial hole 171 and the radial hole 17
It consists of a pipe 41 extending to the second side, a flange 42 integrally formed at the end of the pipe, and a protrusion 44 integrally formed on the surface of the pipe 41 near the outer periphery of the flange 42, and is entirely made of synthetic resin. Most of the pipe 41 except the base end has an axial hole 17.
Inserted into 0. The outer diameter of the pipe 41 is the axial hole 1
There is a slight gap between it and 70.
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. The base end of the pipe 41 communicates with a gap 25 formed at the inner end of the transmission case 2, and lubricating fluid is introduced into the gap 25 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 pinched between the outer ring of the bearing 102 and the transmission case 2, so that the lubricant guide member 4 The whole thing is made unrotatable.

An axial hole 280 is also formed at the clutch side end of the main shaft 200, and radial holes 281 and 282 are formed between this and the inner surfaces of the first speed main gear 210 and second speed main gear 220. In addition, a lubricant guide member 5 is disposed at the opening of the axial hole 280 to introduce the lubricant supplied into the gap 26 through a path not shown into the axial hole 280.
Furthermore, radial holes 281 and 282 provide lubrication between the main shaft 200 and the first-speed main gear 210 and second-speed main gear 220.

Inside the differential housing 3,
A differential gear case 400 is rotatably supported by bearings 401 and 402. 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. ring gear 4
20 is constantly meshed with the output gear 270 to constitute a final reduction gear.

A pinion mate shaft 430 is installed inside the differential gear case 400 and is prevented from coming off by a pin 431. Two pinion gears 440 are fitted onto the pinion mate shaft 430 so as to be rotatable facing each other. A differential gear is constructed by individually meshing two Saiya gears 450. Both side gears 450 have
The inner ends of two drive shafts (not shown) each having a front driving wheel attached to their outer ends are individually fixed. 4
60 is a ring gear for a speedometer.

Next, the effect will be explained.

The transmission in Figure 1 shows the neutral position, and the input shaft 1 is connected from the engine through the clutch.
The rotational force transmitted to input shaft 100 causes first speed gear 110, reverse gear 160, and second speed gear 120 to rotate together with input shaft 100, so that first speed main gear 210 and second speed main gear 220 also rotate at all times. However, at this neutral position, 3rd gear 1
No rotational force is transmitted to 30, 4th gear 140, 5th gear 150, and reverse idler gear 360, and 1st gear main gear 210 and 2nd gear main gear 220
Since the main shaft 200 is only idling, the rotational force of the engine has not yet been transmitted to the main shaft 200.

Therefore, when shifting to the forward 1st gear position, 1-2
The speed synchronizer 211 operates to the first speed side and transmits the rotational force of the first speed main gear 210 to the main shaft 200 via the synchronizer 211. In this way, the main shaft 200 rotates due to the gear ratio between the first speed gear 110 and the first speed main gear 210, and rotational force is transmitted from the output gear 270 that rotates together with the main shaft 200 to the ring gear 420, thereby decelerating the differential gear case 400. and rotate. And differential gear case 40
0, the pinion mate shaft 4
30 rotates around its longitudinal center to rotate the pinion gear 440 on a circular orbit, thereby rotating both side gears 450 while allowing differential movement between them. The rotation of this side gear 450 is directly transmitted to the drive wheels (front wheels) via the drive shaft.

Furthermore, when shifting to the second forward 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 transmitted to the main shaft 200 via this synchronizer 211. Thus, the main shaft 200 rotates depending on the gear ratio between the second speed gear 120 and the second speed main gear 220.
Next, when shifting to the third forward speed position, the 3rd-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 third-speed gear 130 is transmitted to main gear 200 via third-speed main gear 230, which is always in mesh with third-speed gear 130. Depending on the shift to the 4th forward speed position, the 3rd-4th speed synchronizer 131 operates to the 4th speed side, causing the input shaft 100 and the 4th speed gear 140 to rotate together. So 4th gear 14
The rotational force of 0 is transmitted to the main shaft 200 via the 4th speed main gear 240. Furthermore, when shifted to the 5th forward speed position, the 5th speed synchronizer 151
operates to rotate input shaft 100 and fifth gear 150 together, and the rotational force of fifth gear 150 is transmitted to main shaft 200 via fifth gear main gear 250. The rotational force of the main shaft 200 at each of these shift positions is transmitted to the driving wheels via the differential device in the same manner as described above.

Further, when shifted to the reverse position, the reverse idler gear 360 slides on the reverse idler gear shaft 300 to the position indicated by the chain line in FIG.
mesh with. As a result, the rotational force of the reverse gear 160 is transmitted to the reverse main gear 260 via the reverse idler gear 360, and this rotational force is further transmitted to the main shaft 200, which rotates integrally with the coupling sleeve 212 on which the reverse main gear 260 is formed. transmitted to. In this case, a reverse idler gear 360 is provided in the rotational force transmission path.
is interposed, so the main shaft 200 is
It rotates in the opposite direction to the case of the first to fifth forward speeds.
The rotational force of the main shaft 200 is then transmitted to the drive wheels through the same path as described above, but the rotation direction is reversed.

Next, input shaft 100 and 3rd gear 1
To explain the lubrication between 30, 4th gear 140, and 5th gear 150, the lubricant supplied to the gap 25 through a path (not shown) is introduced into the axial hole 170 from the pipe 41 of the lubricant guide member 4. Ru. The lubricating fluid flows from the axial hole 170 through the radial holes 171, 172, and 173 into the circumferential groove 1.
04, 105, and 106, 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, the tip of the pipe 41 is connected to a radial hole 171.
Since the lubricant extends past the radial hole 172 in the direction of the radial hole 172, the lubricant is sufficiently supplied even to the radial hole 173 at the back of the axial hole 170.

The reason why the lubricant is sufficiently supplied to the back of the axial hole 170 when the pipe 41 extends deep is that the pipe 41 is supported by a non-rotating part, so the lubricant is not lubricated inside. This is because no centrifugal force acts on the liquid, and therefore the lubricating liquid is not forced in the centrifugal direction, so its flow resistance becomes extremely small. The lubricant is supplied to the radial hole 171 from the tip of the pipe 41 through the gap between the outer circumference of the pipe 41 and the inner circumference of the axial hole 170. Since the tip of the pipe 41 and the axial hole 170 are relatively close to each other, sufficient lubricating fluid 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 away 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 by this embodiment. In this example, the lubricating fluid is supplied to the radial holes 171 sufficiently, and since the lubricating fluid is supplied to the radial holes 171 from the outlet end of the pipe 41 to the outside thereof, the radial holes 171, 172 , 173 has also become nearly uniform. In particular, since the pipe 41 has a tapered shape that gradually becomes thinner at the tip, the lubricant that enters the gap between the input shaft 100 and the pipe 41 flows through the gap into the input shaft 100.
It is difficult for the liquid to flow backwards towards the end face.

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 inner side of the radial hole 172. A communication hole 45 is opened in the pipe 41 at a position corresponding to the radial hole 171 so that lubricant can be supplied from halfway to the radial hole 171 which is far from the tip of the pipe 41. . For the radial hole 172, the radial hole 171 of the first embodiment (particularly in FIG. 3) is used.
Similarly, lubricating fluid can be supplied through the gap between the inner periphery of the axial hole 170 and the outer periphery of the pipe 41. 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. The radial hole 172 has a communication hole 46
In addition to the lubricating liquid supplied from the pipe 41, there is lubricating liquid 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 communication hole 46 is small. Other configurations and operations are similar to those of the first embodiment.

The amount of lubricant supplied to each radial hole can be controlled by setting the presence or absence of communication holes 45, 46 and their diameter according to conditions such as the distance between each radial hole 171, 172, 173. uniformity throughout.

Note that in these embodiments, the present invention was applied to the input shaft 100 of a manual transmission as a rotating shaft, but the rotating shaft may be the main shaft 200, or it may be rotated in a device separate from the transmission. Of course, the present invention may also be applied to a shaft.

〔Effect of the invention〕

As explained above, according to the present invention, a gap is interposed between the outer circumference of the pipe of the lubricant guide member and the inner circumference of the axial hole of the rotating shaft, and the tip of the pipe is connected to the outer circumference of 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 tip of the pipe approaches the radial hole located on the inner side of the axial hole, so that the lubricant is sufficiently supplied to the radial hole. In addition, lubricating fluid is supplied to the radial hole where the pipes overlap from the tip of the pipe through the gap between the pipe and the axial hole. Thus, without increasing the total amount of lubricant supplied,
Further, there is an effect that the lubricating liquid can be supplied to each radial hole as uniformly as possible without changing the diameter of the radial hole.

In particular, the present invention is a lubricant guide member that is inserted into a rotating shaft of a pipe, and utilizes a gap between the pipe and the rotating shaft to cause the lubricant from the tip of the pipe to flow backward, so that it Among the holes, the lubricating liquid is smoothly supplied to the radial hole closest to the end surface of the rotating shaft, and since the lubricating liquid guide member of the present invention is supported by the non-rotating part, this makes it possible to Since centrifugal force does not act on the guided lubricating liquid, the smooth progress of the lubricating liquid within the pipe is ensured, thereby making it possible to supply a sufficient amount of lubricating liquid. Further, since the pipe of the lubricant guide member of the present invention has a tapered outer surface, the distance between the pipe and the rotary shaft is wide at the tip of the pipe and narrow at the opposite side. For this reason, the lubricating fluid that flows backwards from the pipe tip to the outside of the pipe is supplied to the radial hole in the middle, but it also has the effect of preventing it from flowing further backwards from here and reaching the end surface of the rotating shaft. .

[Brief explanation of drawings]

Fig. 1 is an overall sectional view showing a first embodiment of the present invention, Fig. 2 is a perspective view of a lubricant guide member, Fig. 3 is an enlarged view of the main part of Fig. 1, and Fig. 4 is a second embodiment. FIG. 5 is an enlarged sectional view of the main part of the third embodiment. DESCRIPTION OF SYMBOLS 1...Clutch housing, 2...Transmission case, 3...Differential housing, 4...Lubricant guide member, 41...Pipe, 42...Flange portion, 44...Protrusion, 45,
46... Communication hole, 100... Input shaft, (rotating shaft), 200... Main shaft, 300... Reverse idler gear shaft,
400...differential gear case, 43
0...Pinion mate shaft, 440...Pinion gear, 450...Side gear.

Claims (1)

[Claims] 1. An axial hole formed continuously from the end opening,
and a rotary shaft each having a radial hole extending radially from the axial hole and opening to the outer periphery; a lubricating fluid guide member that guides the lubricating fluid to the axial hole through the rotary shaft, and a plurality of the radial holes are provided in the axial direction of the rotary shaft. The outer circumferential surface is formed into a gentle taper, and a gap is interposed between the outer circumference of the pipe and the inner circumference of the axial hole of the rotary shaft into which the pipe is inserted, with the tip end of the pipe wide and the end face of the rotary shaft sandwiched. Along with letting
A lubrication mechanism for the outer periphery of a rotary shaft, characterized in that a pipe tip is arranged to extend deeper into the axial hole than the radial hole closest to the end surface of the rotary shaft among the plurality of radial holes.