JP2017150633A - Lubrication member - Google Patents

Abstract

PROBLEM TO BE SOLVED: To expand a supply range of a lubricant to a lubricated member.SOLUTION: In a lubrication member 70 which is arranged at a rotating shaft 20, and scatters a lubricant by integrally rotating together with the rotating shaft 20, the lubrication member 70 has: an internal peripheral face 71 which is fit with the rotating shaft 20 at the inside; and an external peripheral face 73 on which a plurality of blade parts 72 for scooping up the lubricant are arranged. A plurality of the blade parts 72 extend substantially in parallel with the rotating shaft 20, and are aligned in a peripheral direction of the rotating shaft 20, and the lubrication member 70 has an inclined face 75 which is inclined to a direction orthogonal to the rotating shaft 20, and straddles the adjacent blade parts.SELECTED DRAWING: Figure 2

Description

  The present invention relates to a lubricating member that is provided on a rotating shaft and that scatters lubricating oil by rotating integrally with the rotating shaft.

  Conventionally, a rotating shaft (main shaft, counter shaft, etc.) used in a transmission of an automobile is lubricated by supplying lubricating oil to a lubricated member such as a gear or a bearing provided in the transmission to prevent seizure. Some have members.

  As an example, for example, in Patent Document 1, a disc-shaped slinger (lubricating member) is provided at the shaft end of the countershaft, and the lubricating member is spattered by rotating the lubricating member so that the lubricating member is dispersed in the transmission. The member to be lubricated in the radial direction of rotation is lubricated.

  Further, the lubricating member has a conical surface for adjusting the scattering direction of the lubricating oil, and the conical surface is inclined with respect to the radial direction of the counter shaft. Therefore, in the lubricating member, the lubricating oil can be deflected and scattered in the direction inclined by the inclination angle with respect to the radial direction of the lubricating member by the inclination of the conical surface.

  As a result, in the conventional lubricating member, the lubricating oil can be supplied not only to the member to be lubricated in the radial direction of the lubricating member in the transmission but also to the member to be lubricated in a direction oblique to the radial direction. .

JP 59-205066 A

  By the way, the amount of the lubricating oil scraped up by the conical surface of this conventional lubricating member is small, and the lubricating oil scattered by the rotation has a small granular mass.

  Therefore, in this conventional lubricating member, the scattering distance of the lubricating oil is shortened, and the lubricating oil cannot be supplied to the member to be lubricated at a remote position, so the range in which the lubricating oil can be supplied is limited. End up.

  Therefore, an object of the present invention is to provide a lubricating member capable of widening the range in which lubricating oil can be supplied to the member to be lubricated.

  In order to achieve the above object, the lubricating member according to the present invention is provided on the rotating shaft and scatters lubricating oil by rotating integrally with the rotating shaft. And an outer peripheral surface provided with a plurality of wings for scooping up the lubricating oil. The plurality of wings extend substantially in parallel with the rotating shaft, are provided side by side in the circumferential direction of the rotating shaft, and the lubricating member is in a direction perpendicular to the rotating shaft. It has an inclined surface that inclines and straddles between adjacent wings.

  In the lubricating member of the present invention, the collected amount of lubricating oil is scraped up by the plurality of wings provided on the outer peripheral surface, and the collected amount of lubricating oil is scattered. In this case, the scattered lubricating oil particles have a large mass and a long scattering distance, so that the lubricating oil can be supplied to a member to be lubricated at a distant position.

  Therefore, according to the lubricating member of the present invention, the range in which lubricating oil can be supplied to the member to be lubricated can be widened.

It is a skeleton figure which shows the structure of the drive device for vehicles to which this invention is applied. It is a perspective view of a lubricating member. It is a longitudinal cross-sectional view of a lubricating member. It is a front view of the rotating shaft direction of a lubricating member. It is a figure which shows the example of the lubricating member which mixed the inclined surface from which an angle differs.

  Embodiments of the present invention will be described below with reference to the drawings.

  FIG. 1 is a skeleton diagram showing the configuration of a vehicle drive device to which the present invention is applied. This drive device 10 is mainly used for FF (front engine / front drive) type vehicles.

  As shown in the figure, the drive device 10 includes an engine 12, a clutch 14, a manual transmission 16, and a final reduction gear 17. The clutch 14 is, for example, a dry single-plate friction clutch, and appropriately cuts off the rotational driving force from the engine 12 at the time of shifting.

  The manual transmission 16 is used for a manual transmission of an automobile, and is, for example, a stepped transmission of 5 forward speeds and 1 reverse speed.

  In the manual transmission 16, an input shaft 18 and a counter shaft 20 that are rotating shafts are arranged in parallel. The input shaft 18 is rotatably supported by bearings 22 and 24, and the countershaft 20 is rotatably supported by bearings 26 and 28.

  A first speed drive gear 34a, a reverse drive gear 36a, a second speed drive gear 38a, a third speed drive gear 40a, a fourth speed drive gear 42a, and a fifth speed drive gear 44a are arranged on the input shaft 18 in order from the engine 12 side. ing.

  The first speed drive gear 34a, the reverse drive gear 36a, and the second speed drive gear 38a are fixed to the input shaft 18 so as not to rotate relative to each other by integral molding, press-fitting, spline fitting, or the like. The third speed drive gear 40a, the fourth speed drive gear 42a, and the fifth speed drive gear 44a are fitted to the input shaft 18 so as to be relatively rotatable.

  On the countershaft 20, a drive pinion gear 32, a first speed driven gear 34b, a second speed driven gear 38b, a third speed driven gear 40b, a fourth speed driven gear 42b, and a fifth speed driven gear 44b are arranged in this order from the bearing 26 side.

  Here, the drive pinion gear 32 meshes with the ring gear 30 of the final reduction gear 17. The first speed driven gear 34b is a first speed drive gear 34a, the second speed driven gear 38b is a second speed drive gear 38a, the third speed driven gear 40b is a third speed drive gear 40a, the fourth speed driven gear 42b is a fourth speed drive gear 42a, The 5-speed driven gear 44b always meshes with the 5-speed drive gear 44a.

  The first speed driven gear 34b and the second speed driven gear 38b are fitted to the counter shaft 20 so as to be rotatable relative to each other. The drive pinion gear 32, the third speed driven gear 40b, the fourth speed driven gear 42b, and the fifth speed driven gear 44b are fixed to the counter shaft 20 so as not to be relatively rotatable by integral molding, press-fitting, spline fitting, or the like.

  The rotation driving force output from the manual transmission 16 is decelerated when it is transmitted from the drive pinion gear 32 to the ring gear 30 of the final reduction gear 17.

  The final reduction gear 17 includes a pair of side gears 46R and 46L. The rotational drive force after deceleration transmitted to the ring gear 30 is supplied to drive shafts 48R and 48L connected to the side gears 46R and 46L by spline fitting or the like, respectively. To the left and right drive wheels (not shown). The final reduction gear 17 is of a bevel gear type.

  In the manual transmission 16, a first synchromesh device 50 is provided between the third speed drive gear 40 a and the fourth speed drive gear 42 a of the input shaft 18, and also on the bearing 24 side of the fifth speed drive gear 44 a of the input shaft 18. Is provided with a second synchromesh device 52. The first synchronizing device 50 and the second synchronizing device 52 are spline-fitted to the input shaft 18 and are slidable in the axial direction.

  A third synchronous meshing device 54 is provided between the first speed driven gear 34b and the second speed driven gear 38b of the countershaft 20. The third synchromesh device 54 is splined to the countershaft 20 and is slidable in the axial direction. Further, the third synchronous meshing device 54 is configured integrally with the reverse driven gear 36b. As described above, since the third synchronous meshing device 54 is spline-fitted to the counter shaft 20, the reverse driven gear 36 b configured integrally therewith is not rotatable relative to the counter shaft 20.

  Further, the manual transmission 16 is provided with a reverse gear idler shaft 56 in parallel with the input shaft 18 and the counter shaft 20. The idler shaft 56 is fitted with an idler gear 58 that can rotate relative to the shaft and can move in the axial direction. The idler gear 58 indicated by the solid line in FIG. 1 indicates the position when the reverse gear is not selected, while the idler gear 58 indicated by the alternate long and short dash line is when the reverse gear is selected. The position of the idler gear 58 is shown.

  In the manual transmission 16, the gear position is selected according to the shift position of a shift lever (not shown) operated by the driver.

  Here, the operation of each synchronous meshing device when the shift lever is operated will be described.

  When the first forward speed is selected by operating the shift lever, the sleeve 54s integrated with the reverse driven gear 36b of the third synchronous meshing device 54 of the countershaft 20 is moved to the first speed driven gear 34b side by a shift fork (not shown). And is connected to the meshing clutch 34c. As a result, the first-speed driven gear 34b that meshes with the first-speed drive gear 34a of the input shaft 18 is connected to the countershaft 20, and a power transmission path is established by the speed ratio of the first forward speed.

  The operation of the second forward speed or the fifth forward speed is the same as that of the first forward speed, but the differences are as follows.

  In the second forward speed, the sleeve 54s of the third synchronous meshing device 54 of the countershaft 20 moves to the second speed driven gear 38b side and is connected to the meshing clutch 38c. As a result, the second speed driven gear 38 b that meshes with the second speed drive gear 38 a of the input shaft 18 is connected to the counter shaft 20.

  At the third forward speed, the sleeve 50s of the first synchronous meshing device 50 of the input shaft 18 moves to the third speed drive gear 40a side and is connected to the meshing clutch 40c. As a result, the third-speed drive gear 40 a that meshes with the third-speed driven gear 40 b of the counter shaft 20 is connected to the input shaft 18.

  In the fourth forward speed, the sleeve 50s of the first synchromesh device 50 moves to the fourth speed drive gear 42a side and is connected to the mesh clutch 42c. As a result, the 4-speed drive gear 42 a that meshes with the 4-speed driven gear 42 b of the countershaft 20 is connected to the input shaft 18.

  At the fifth forward speed, the sleeve 52s of the second synchronous meshing device 52 of the input shaft 18 moves to the fifth speed drive gear 44a side and is connected to the meshing clutch 44c. As a result, the 5-speed drive gear 44 a that meshes with the 5-speed driven gear 44 b of the countershaft 20 is connected to the input shaft 18.

  When the reverse gear is selected, the idler gear 58 of the idler shaft 56 is moved to the position indicated by the one-dot chain line in FIG. 1 by the shift fork. At this time, the third synchronous meshing device 54 of the countershaft 20 is not moved by the shift fork. As a result, the input idler gear 58a of the idler gear 58 is meshed with the reverse drive gear 36a of the input shaft 18, and the output idler gear 58b is meshed with the reverse driven gear 36b of the third synchronous meshing device 54 to transmit power by the reverse gear ratio. A route is established. Note that the input idler gear 58a and the output idler 58b of the idler gear 58 rotate integrally.

  In FIG. 1, the output idler gear 58b and the reverse driven gear 36b are arranged at positions where they cannot be engaged as indicated by broken lines, but actually, the output idler gear 58b and the reverse driven gear 36b can be engaged with each other. An idler shaft 56 and an idler gear 58 are disposed at a position between the input shaft 18 and the counter shaft 20. Therefore, when the reverse gear is selected, the rotational driving force input to the input shaft 18 is transmitted to the counter shaft 20 via the idler gear 58.

  Next, the lubricating member of the present invention will be described. The lubricating member of the present invention is provided on a countershaft (rotary shaft) of a manual transmission.

  Specifically, as shown in FIG. 1, the lubricating member 70 is provided between the third speed driven gear 40 b and the fourth speed driven gear 42 b of the countershaft 20.

  The lubricating member 70 is not only a member to be lubricated such as the first synchromesh device 50 in the radial direction of rotation in the manual transmission 16, but also in a reverse position away from the lubricating member 70 other than the radial direction. Lubricating oil can also be supplied to the lubricated members such as the stage idler shaft 56 and the idler gear 58.

  These reverse gear idler shafts 56 and the like are lubricated members that need to be lubricated, but in the manual transmission 16, the lubricating oil that is scraped up by each gear such as the countershaft 20 is difficult to reach. Lubricating oil needs to be supplied by the lubricating member 70.

  Therefore, the structure of the lubricating member, which is a feature of the present invention, will be described with reference to FIGS. 2 is a perspective view of the lubricating member, FIG. 3 is a longitudinal sectional view of the lubricating member, and FIG. 4 is a front view of the lubricating member in the rotation axis direction.

  As shown in FIG. 2, the lubricating member 70 is a substantially cylindrical member, and has an inner peripheral surface 71 for fitting the counter shaft 20 that is a rotating shaft inside, and a plurality of wings 72 that scoop up lubricating oil. And an outer peripheral surface 73 provided with.

  As shown in FIG. 3, when the counter shaft 20 is fitted on the inner peripheral surface 71 of the lubricating member 70, the lubricating member 70 is provided with the unevenness of the engaging portion 74 provided on the inner peripheral surface 71 and the counter corresponding thereto. The lubricating member 70 is fixed to the countershaft 20 so as not to rotate relative to the countershaft 20 by fitting with the unevenness of the engaging portion (not shown) provided on the outer peripheral surface of the shaft 20.

  Thereby, when a rotational driving force is transmitted to the countershaft 20, the countershaft 20 and the lubricating member 70 are rotated together.

  The lubrication member 70 is fixed to the countershaft 20 so that the side indicated by the arrow a in FIG. 3 of the lubrication member 70 faces the third speed driven gear 40b shown in FIG.

  As shown in FIGS. 2 to 4, the plurality of wings 72 of the lubricating member 70 are arranged so that each wing extends in parallel with the countershaft 20 and in the circumferential direction of the countershaft 20. It is provided side by side.

  That is, the lubricating member 70 rotates integrally with the countershaft 20 by fitting the countershaft 20 that is a rotating shaft on the inner peripheral surface 71 on the inner side thereof, and also lubricates the outer peripheral surface 73 by the rotation thereof. A plurality of wing portions 72 to be scraped are provided. The plurality of wing portions 72 are provided so that each wing portion is orthogonal to the rotational direction of the lubricating member 70 (counter shaft 20), and are arranged in the circumferential direction of the lubricating member 70.

  Therefore, in the lubricating member 70, when the countershaft 20 that is the rotating shaft and the lubricating member 70 rotate integrally, the lubricating oil is interposed between adjacent wings of the plurality of wings 72 provided on the outer peripheral surface 73 thereof. As a result, a plurality of wings 72 scrapes up the collected amount of lubricating oil.

  The plurality of wings 72 of the lubricating member 70 only have to be provided so that each wing extends substantially in parallel with the countershaft 20, that is, the axis of the countershaft 20 as described above. It may be provided so as to extend parallel to the direction, or may be provided so as to extend slightly obliquely with respect to the axial direction of the countershaft 20.

  Further, the surfaces of the plurality of wing portions 72 of the lubricating member 70 are formed by two wing surfaces 72a and 72b as shown in FIG. The blade surface 72a is formed so that the tip thereof is inclined toward the rear side in the rotation direction of the lubricating member 70 indicated by the arrow in FIG. The other wing surface 72 b is formed to extend in parallel with the radial direction of the lubricating member 70.

  That is, as shown in FIG. 4, in the plurality of wings 72 of the lubricating member 70, the circumferential interval 72 d of the lubricating member 70 (counter shaft 20) formed by the wings adjacent to each other approaches the rotational axis of the lubricating member 70. It is narrowed according to.

  Thereby, in the lubricating member 70, the lubricating oil taken in between the adjacent wings of the plurality of wings 72 by rotation is substantially formed by the wing surfaces 72a and 72b between the adjacent wings. In the triangular prism space, the lubricant members 70 are gathered together with the rotation.

  In this case, the amount of lubricating oil to be scattered becomes a collective amount and the mass becomes large, so that the scattering distance becomes long, and the lubricating oil can be supplied to a member to be lubricated at a remote position.

  As a result, the lubricating member 70 supplies the lubricating oil in an amount necessary for lubrication to the lubricated member 70 in the radial direction of the lubricating member 70, in particular, to the member to be lubricated above the lubricating member 70 in the manual transmission 16. . Note that the member to be lubricated to which the lubricating oil is supplied in this manner is specifically the first synchronous meshing device 50 shown in FIG.

  Further, as shown in FIG. 3, the lubricating member 70 has an inclined surface 75 that is inclined with respect to a direction orthogonal to the countershaft 20 and straddles between adjacent wing portions.

  Therefore, in the lubricating member 70, the lubricating oil taken in and aggregated between the adjacent wings of the plurality of wings 72 by the rotation is scattered toward the inclination direction of the inclined surface 75 straddling the wings. Be made.

  As a result, an amount necessary for lubrication is also required for a member to be lubricated that is located away from the lubricating member 70 and that is difficult to reach the lubricating oil scooped up by each gear such as the countershaft 20 in the manual transmission 16. Of lubricating oil is supplied. The members to be lubricated to which the lubricating oil is supplied in this manner are specifically the reverse gear idler shaft 56, idler gear 58 and the like shown in FIG.

  Thus, in the lubricating member 70, not only the lubricated member in the radial direction of rotation (including the lubricated member in the radial position) but also the direction inclined with respect to the direction orthogonal to the rotational axis, That is, the lubricating oil can be supplied also to the lubricated member at the position of the inclined surface 75 in the inclination direction.

  In the lubricating member 70, the direction in which the lubricating oil is scattered can be set by adjusting the inclination angle of the inclined surface 75 straddling between the wing portions adjacent to each other.

  The inclination angle θ of the inclined surface 75 may be the same for all the inclined surfaces between the wings, or the angle of several inclined surfaces may be θx and the angle of the remaining inclined surfaces may be θy. May be. That is, the inclined surfaces between the wings may be mixed with inclined surfaces having different angles.

  For example, as shown in FIG. 5, the angles θa of the five inclined surfaces 75 in the region indicated by “A” are all “20 °”, and the angles θb of the five inclined surfaces 75 in the region indicated by “B” are all The angle θc of the four inclined surfaces 75 in the region indicated by “40 °” and “C” is set to “0 °”.

  By doing so, in the lubricating member 70, it is possible to set a plurality of types of regions where the lubricating oil can be supplied.

DESCRIPTION OF SYMBOLS 10 Drive apparatus 12 Engine 14 Clutch 16 Manual transmission 17 Final reduction gear 18 Input shaft 20 Counter shaft 22, 24 Bearing 26, 28 Bearing 30 Ring gear 32 Drive pinion gear 70 Lubrication member 71 Inner peripheral surface 72 Feather portion 72a Feather surface 72b Feather surface 72d interval 73 outer peripheral surface 74 engaging portion 75 inclined surface

Claims (1)

In the lubricating member provided on the rotating shaft and splashing lubricating oil by rotating integrally with the rotating shaft,
The lubricating member has an inner peripheral surface on which the rotating shaft is fitted inside, and an outer peripheral surface provided with a plurality of wings for scooping up the lubricating oil,
The plurality of wings extend substantially in parallel to the rotation shaft, are provided side by side in the circumferential direction of the rotation shaft, and the lubricating member is inclined with respect to a direction orthogonal to the rotation shaft. A lubrication member comprising an inclined surface straddling between adjacent wings.

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