JP2017067119A - Thrust washer and lubrication structure - Google Patents

Abstract

PROBLEM TO BE SOLVED: To properly supply lubricant to a gap between adjacent members provided on a rotational axis, and properly supply lubricant to an inner peripheral side.SOLUTION: A thrust washer is a substantially toric thrust washer 80 provided in an output shaft 11 in an integrally rotatable manner, and includes, on at least one surface 81A: one or more oil introduction grooves 85 inclined in a predetermined rotational direction to a radial of the output shaft 11, and formed so as to extend from an inner periphery to an outer periphery; and a cutout part 82 adjacent to an opening part 85a on an outer peripheral side of the oil introduction groove 85, and formed on a downstream side in the predetermined rotational direction.SELECTED DRAWING: Figure 2

Description

  The present invention relates to a thrust washer that is attached to a rotating shaft and supplies lubricating oil to an inner peripheral surface side, and a lubricating structure including the thrust washer.

  Conventionally, in a transmission, a plurality of gears, a hub, a bearing, and the like are arranged in the axial direction on a rotating shaft (shaft) via a thrust washer. Some gears arranged on the rotating shaft are provided on the shaft via a needle bearing. For such a gear, it is necessary to supply lubricating oil to the needle bearing on the inner peripheral side of the gear.

  In order to reduce the contact resistance between the thrust washer and the gear in contact with the thrust washer, and to reduce the wear of the thrust washer and gear, it is necessary to supply lubricating oil between the thrust washer and the gear. is necessary.

  For example, a technique is known in which the contact surface between the gear and the thrust washer is lubricated by forming an oil groove through which the lubricating oil flows in the contact surface of the gear with the thrust washer.

  In addition, in a differential gear device, a technique is known in which an oil introduction groove extending from the outer peripheral side of the washer toward the inner peripheral side is formed to introduce lubricating oil to the inner peripheral side of the washer (for example, Patent Document) 1).

JP-A-8-210473

  For example, by forming an oil groove on the side of a member such as a gear, it is possible to reduce friction with the thrust washer. However, if an oil groove is formed in the gear, the process of creating the gear becomes complicated. End up. Further, if an oil groove is formed in a gear or the like, burrs are generated around the oil groove, and the burrs may cause damage to the gear or the like.

  Further, in a transmission, in order to lubricate the rotating shaft with a member such as a gear, a hub, or a bearing provided on the rotating shaft, it is required to supply more lubricating oil to the inner peripheral side of the member. ing.

  The present invention has been made in view of the above problems, and the object thereof is to appropriately supply the lubricating oil between adjacent members provided on the rotating shaft and to appropriately supply the lubricating oil to the inner peripheral side. It is to provide technology that can be supplied.

  In order to achieve the above-mentioned object, a thrust washer according to an aspect of the present invention is a substantially annular thrust washer provided to be rotatable integrally with a rotating shaft, and has at least one surface with respect to the diameter of the rotating shaft. One or more oil introduction grooves formed to be inclined in a predetermined rotation direction and extending from the inner periphery to the outer periphery, and a cut formed on the downstream side in the predetermined rotation direction adjacent to the outer peripheral opening of the oil introduction groove. A notch.

  In the thrust washer, the cutout portion includes a radial surface portion having a radial surface extending in the radial direction and a vertical surface portion having a vertical surface extending in a direction perpendicular to the radial direction from an inner peripheral side end portion of the radial surface. It may be configured.

  The thrust washer may have a short diameter portion that is formed at a position immediately before the notch portion on the downstream side in the predetermined rotation direction and has an outer diameter shorter than the maximum outer diameter of the thrust washer.

  In the thrust washer, an engagement groove that engages with an engagement member provided on the rotating shaft may be formed on the inner periphery of the thrust washer.

  Further, in the thrust washer, an oil introduction groove and a notch portion may be formed on the other surface so that when the front and back surfaces of the thrust washer are reversed, the same state as that of the one surface is obtained.

  A lubricating structure according to another aspect of the present invention includes a rotating shaft, a substantially annular thrust washer provided on the rotating shaft, and a member provided on the rotating shaft adjacent to the thrust washer. One or more oil introduction grooves formed on the at least one surface of the thrust washer in a predetermined rotation direction with respect to the diameter of the rotation shaft and extending from the inner periphery to the outer periphery, and the oil introduction groove And a notch formed on the downstream side in a predetermined rotation direction adjacent to the outer peripheral opening.

  According to the present invention, the lubricating oil can be appropriately supplied between adjacent members provided on the rotating shaft, and the lubricating oil can be appropriately supplied to the inner peripheral side.

It is a figure showing the whole manual transmission composition which has a lubrication structure concerning one embodiment of the present invention. (A) is a figure showing a lubrication structure concerning one embodiment of the present invention. (B) is a front view of a thrust washer according to an embodiment of the present invention. (C) is a side view of a thrust washer according to an embodiment of the present invention.

  Hereinafter, a manual transmission having a lubricating structure according to an embodiment of the present invention will be described with reference to the accompanying drawings. The same parts are denoted by the same reference numerals, and their names and functions are also the same. Therefore, detailed description thereof will not be repeated.

  FIG. 1 is a diagram showing an overall configuration of a manual transmission having a lubricating structure according to an embodiment of the present invention.

  A manual transmission (hereinafter referred to as “transmission”) 1 includes an input shaft 10, an output shaft 11 disposed coaxially with the input shaft 10, a counter shaft 12 disposed in parallel with the input shaft 10 and the output shaft 11, and A reverse idler shaft 15 is provided. In the transmission 1, basically, the input side end portion of the input shaft 10 and the output side end portion of the output shaft 11 are excluded in the transmission case 2 (the front case 2 a and the rear case 2 b). Be contained. The transmission case 2 contains lubricating oil for lubricating each part.

  The input shaft 10 is rotatably supported by a bearing 17 on the front case 2a. The bearing 17 has a function (seal function) that prevents inflow of lubricating oil from the outside of the transmission case 2 (front side of the front case 2a) to the inside of the transmission case 2 (back side of the front case 2a). Have.

  An input main gear 13 is provided on the input shaft 10 so as to be integrally rotatable. A support hole is formed on the rear side of the input shaft 10 so that the front end of the output shaft 11 is rotatably supported via a needle bearing (not shown).

  The output shaft 11 includes, in order from the input side (front side), the first hub 21, the third speed main gear M3, the first thrust washer 70, the sixth speed main gear M6, the fifth speed main gear M5, the second speed main gear M2, and the third hub 41. A first speed main gear M1, a fourth hub 51, a reverse main gear MR, and a second thrust washer 80 are provided. The third speed main gear M3, the first thrust washer 70, the second speed main gear M2, the first speed main gear M1, and the reverse main gear MR are provided on the output shaft 11 so as to be relatively rotatable, and the first hub 21, the sixth speed main gear M6, and the fifth speed. The main gear M5, the third hub 41, the fourth hub 51, and the second thrust washer 80 are provided on the output shaft 11 so as to be integrally rotatable. In the present embodiment, the sixth speed main gear M6 and the fifth speed main gear M5 are formed integrally with the output shaft 11.

  The counter shaft 12 is supported on the front case 2a by a bearing 18 so as to be rotatable substantially horizontally. The bearing 18 has a function (seal function) that prevents inflow of lubricating oil from the outside of the transmission case 2 (front side of the front case 2a) to the inside of the transmission case 2 (back side of the front case 2a). Have.

  The counter shaft 12 includes, in order from the input side, an input counter gear 14 that meshes with the input main gear 13, a third speed counter gear C3 that meshes with the third speed main gear M3, a sixth speed counter gear C6 that meshes with the sixth speed main gear M6, and a second The hub 31, the fifth speed counter gear C5 that meshes with the fifth speed main gear M5, the second speed counter gear C2 that meshes with the second speed main gear M2, the first speed counter gear C1 that meshes with the first speed main gear M1, and the reverse idler gear 16 A reverse counter gear CR that meshes with the main gear MR is provided. The input counter gear 14, the third speed counter gear C 3, the second hub 31, the second speed counter gear C 2, the first speed counter gear C 1 and the reverse counter gear CR are provided on the counter shaft 12 so as to be integrally rotatable, and the fifth speed counter gear C 5. The 6-speed counter gear C6 is provided on the count shaft 12 so as to be relatively rotatable.

  Inside the countershaft 12, the shaft center extends in the axial direction around the shaft center, the shaft center hole 12a for introducing the lubricant, and the shaft center hole 12a extends in the radial direction from the shaft center hole 12a to the outer peripheral surface of the countershaft 12. And one or more radial flow paths 12b for discharging the gas from the openings on the outer peripheral surface.

  The first sync mechanism 20 includes a first hub 21 fixed to the output shaft 11, an input dog gear 22 fixed to the input main gear 13, a third speed dog gear 23 fixed to the third speed main gear M3, and a first hub. 21 includes a first sleeve 24 that is non-rotatable and movable in the axial direction, and a pair of synchronizer rings SR interposed between the first sleeve 24 and each of the dog gears 22 and 23. A first shift fork F <b> 1 that moves the first sleeve 24 in the axial direction is engaged with the outer circumferential concave groove of the first sleeve 24.

  When the first sleeve 24 moves forward and meshes with the input dog gear 22, the power transmission path is directly connected from the input shaft 10 to the output shaft 11, and the output shaft 11 rotates at the fourth speed. When the first sleeve 24 moves rearward and is splined with the third speed dog gear 23, the power transmission path becomes the input main gear 13, the input counter gear 14, the third speed counter gear C3, the third speed main gear M3, and the output shaft 11 is in the third speed. Rotate at the equivalent.

  The second synchronization mechanism 30 includes a second hub 31 fixed to the countershaft 12, a sixth speed dog gear 32 fixed to the sixth speed counter gear C6, a fifth speed dog gear 33 fixed to the fifth speed counter gear C5, A second sleeve 34 is attached to the second hub 31 so as not to rotate and is movable in the axial direction, and a pair of synchronizer rings SR interposed between the second sleeve 34 and each of the dog gears 32 and 33. ing. A second shift fork F <b> 2 that moves the second sleeve 34 in the axial direction is engaged with the outer circumferential groove of the second sleeve 34.

  When the second sleeve 34 moves forward and meshes with the 6-speed dog gear 32 by spline, the power transmission path becomes the input main gear 13, the input counter gear 14, the 6-speed counter gear C6, the 6-speed main gear M6, and the output shaft 11 is 6-speed. Rotate at the equivalent. When the second sleeve 34 moves rearward and engages with the 5-speed dog gear 33 by spline, the power transmission path becomes the input main gear 13, the input counter gear 14, the 5-speed counter gear C5, and the 5-speed main gear M5, and the output shaft 11 moves to the 5-speed. Rotate at the equivalent.

  The third sync mechanism 40 includes a third hub 41 fixed to the output shaft 11, a second speed dog gear 42 fixed to the second speed main gear M2, a first speed dog gear 43 fixed to the first speed main gear M1, A third sleeve 44 is attached to the hub 41 so as not to rotate and is movable in the axial direction, and a pair of synchronizer rings SR interposed between the third sleeve 44 and the dog gears 42 and 43, respectively. . A third shift fork F3 that moves the third sleeve 44 in the axial direction is engaged with the outer circumferential groove of the third sleeve 44.

  When the third sleeve 44 moves forward and meshes with the second-speed dog gear 42 by spline, the power transmission path becomes the input main gear 13, the input counter gear 14, the second-speed counter gear C2, and the second-speed main gear M2, and the output shaft 11 moves to the second speed. Rotate at the equivalent. When the third sleeve 44 moves rearward and engages with the first-speed dog gear 43 by spline, the power transmission path becomes the input main gear 13, the input counter gear 14, the first-speed counter gear C1, the first-speed main gear M1, and the output shaft 11 moves to the first speed. Rotate at the equivalent.

  The fourth sync mechanism 50 is attached to the fourth hub 51 fixed to the output shaft 11, the reverse dog gear 53 fixed to the reverse main gear MR, and the fourth hub 51 so as not to be rotatable and movable in the axial direction. A fourth sleeve 54 and a synchronizer ring SR interposed between the fourth sleeve 54 and the reverse dog gear 53 are provided. A fourth shift fork F4 that moves the fourth sleeve 54 in the axial direction is engaged with the outer circumferential groove of the fourth sleeve 54.

  When the fourth sleeve 54 moves rearward and engages with the reverse dog gear 53 by spline, the power transmission path becomes the input main gear 13, input counter gear 14, reverse counter gear CR, reverse idler gear 16, reverse main gear MR, and the output shaft 11. Reverses.

  Next, the lubricating structure included in the range X in FIG. 1 will be described.

  2A is a view showing a lubricating structure according to an embodiment of the present invention, and FIG. 2B is a front view of a thrust washer according to an embodiment of the present invention. c) is a side view of a thrust washer according to an embodiment of the present invention. 2A is an enlarged view of a range X in FIG.

  The lubricating structure 8 includes an output shaft 11, a bearing 19, a second thrust washer 80, a reverse main gear MR, and a needle bearing 90.

The bearing 19 rotatably supports the output shaft 11.
A reverse main gear MR is provided on the front side of the bearing 19 of the output shaft 11 with a second thrust washer 80 interposed therebetween. The output shaft 11 is provided with an engaging member (for example, a ball member) 11a for engaging the second thrust washer 80 so as to be integrally rotatable.

  The reverse main gear MR is provided on the output shaft 11 via a needle bearing 90 so as to be relatively rotatable. In the space in which the needle bearing 90 is mounted, the lubricating oil can flow in the axial direction.

  The second thrust washer 80 is a substantially annular flat plate, and is provided on the output shaft 11 as shown in FIG. In the state where the second thrust washer 80 is provided on the output shaft 11, when the vehicle on which the transmission 1 is mounted moves forward, in FIG. Rotate. Here, the direction in which the second thrust washer 80 rotates when the vehicle equipped with the transmission 1 moves forward is referred to as the forward rotation direction.

  An engagement groove 87 that engages with the engagement member 11 a of the output shaft 11 is formed on the inner periphery of the second thrust washer 80. The second thrust washer 80 can rotate integrally with the output shaft 11 by engaging the engaging groove 87 with the engaging member 11 a of the output shaft 11.

  Further, one surface 81A of the second thrust washer 80 is inclined to the downstream side in the forward rotation direction with respect to the diameter of the output shaft 11 and extends from the inner periphery to the outer periphery (in the figure, the surface 81A has 2 ) Oil introduction groove 85 is formed.

  A cutout portion 82 penetrating from one surface 81A to the other surface 81B is formed on the downstream side in the forward rotation direction adjacent to the opening 85a on the outer peripheral side of the oil introduction groove 85.

  The notch portion 82 has a radial surface portion 84 having a surface (radial surface) extending in the radial direction of the output shaft 11, and an inner peripheral side end portion of the radial surface of the radial surface portion 84 in a direction perpendicular to the radial direction. And a vertical surface portion 83 having an extending surface (vertical surface).

  With such a configuration, the opening 85a of the oil introduction groove 85 is opened in the tangential direction on the radially outer side of the second thrust washer 80 and on the downstream side in the forward rotation direction. For this reason, when the second thrust washer 80 rotates in the forward rotation direction, the lubricant that scatters from the periphery toward the outer periphery or the lubricant that reaches the space of the notch 82 is introduced into the opening 85a. It will be efficiently taken into the groove 85.

  Further, in the present embodiment, a short diameter portion 86 having a diameter shorter than the maximum outer diameter of the second thrust washer 80 is formed on the downstream side in the forward rotation direction adjacent to the notch portion 82. Yes. According to the short diameter portion 86, the lubricating oil existing around the second thrust washer 80 can be effectively collected in the notch portion 82 via the space on the outer diameter side of the short diameter portion 86, and the opening portion The amount of the lubricating oil taken into the oil introduction groove 85 from 85a can be increased.

  The other surface (back surface) 81B of the second thrust washer 80 has an oil introduction groove 85 and a notch so that when the front and back surfaces of the second thrust washer 80 are reversed, the same state as the one surface 81A is obtained. 82 is formed. Specifically, as shown in FIG. 2B, when viewed from the one surface 81A side, the surface 81B is inclined to the upstream side in the forward rotation direction with respect to the diameter of the output shaft 11. One or more oil introduction grooves 85 formed to extend from the inner periphery to the outer periphery are formed, and on the upstream side in the forward rotation direction adjacent to the outer peripheral opening 85a of the oil introduction groove 85 on the back surface 81B side, A notch 82 is formed so as to penetrate from the surface 81A to the other surface 81B.

  Thus, even if the front and back of the second thrust washer 80 are reversed, the state of the oil introduction groove 85 and the notch 82 is the same. Therefore, when performing the attaching operation for attaching the second thrust washer 80 to the output shaft 11. In addition, it is not necessary to be aware of the front and back of the second thrust washer 80, and it is possible to appropriately prevent a mounting error in the mounting operation.

  Next, the flow of the lubricating oil in the lubricating structure 8 will be described.

  During operation of the transmission 1, the lubricating oil is frequently splashed up in the transmission 1 by rotating gears and the like provided on the shaft such as the output shaft 11. For this reason, the lubricant is dripped onto the second thrust washer 80 from above or scattered from the surroundings.

  In such a state, the lubricating oil that has reached the periphery of the second thrust washer 80 is taken into the oil introduction groove 85 via the notch 82 or directly from the opening 85 a of the oil introduction groove 85. Along the inner circumferential side of the second thrust washer 80 (arrow R1).

  Here, since the oil introduction groove 85 faces the rear side surface of the reverse main gear MR, the lubricating oil adheres to the rear side surface of the reverse main gear MR. Here, the reverse main gear MR and the second thrust washer 80 may rotate together (when shifting backward) or may be rotated relative (when not shifting backward). In the case of relative rotation, the surface of the reverse main gear MR facing the oil introduction groove 85 changes sequentially, so that lubricating oil can be supplied to the entire surface of the reverse main gear MR. In the case of integral rotation, there is no problem because friction is unlikely to occur, but even in this case, the surface of the reverse main gear MR and the surface of the second thrust washer 80 are in contact with each other. As a result, the lubricating oil flowing through the oil introduction groove 85 permeates, so that the lubricating oil can be appropriately supplied to the contacting portion.

  Furthermore, the lubricating oil that has flowed to the inner peripheral side of the second thrust washer 80 flows into the space of the needle bearing 90 communicating with the oil introduction groove 85, and flows forward in the axial direction of the output shaft 11 (arrow R2). . Thereby, the lubrication between the needle bearing 90 and the reverse main gear MR can be promoted, and the lubricating oil can be supplied to a portion in front of the axial reverse main gear MR.

  As described above, according to the lubricating structure 8 according to the embodiment of the present invention, the one surface 81A of the second thrust washer 80 is inclined to the downstream side in the forward rotation direction with respect to the diameter of the output shaft 11. An oil introduction groove 85 extending from the inner periphery to the outer periphery is formed, and from the one surface 81A to the other surface on the downstream side in the forward rotation direction adjacent to the opening 85a on the outer periphery side of the oil introduction groove 85. Since the notch portion 82 penetrating to 81B is formed, the lubricating oil existing around the second thrust washer 80 can be taken into the oil introduction groove 85 effectively. Therefore, the lubrication of the contact surface with the reverse main gear MR can be promoted, and the lubricating oil can be appropriately supplied to the inner peripheral side of the second thrust washer 80 and the reverse main gear MR.

  In addition, this invention is not limited to the above-mentioned embodiment, In the range which does not deviate from the meaning of this invention, it can change suitably and can implement.

  For example, in the above embodiment, the notch portion 82 is configured by the parallel surface portion 84 and the vertical surface portion 83. However, the present invention is not limited to this, and the shape of the notch portion is, for example, sandwiched. It may be composed of two planes with acute angles, or may be composed of two planes with obtuse angles, and the cross-sectional shape of the notch portion is arbitrary. The shape may be

  Moreover, in the said embodiment, when the front and back of the 2nd thrust washer 80 are replaced, the shape and arrangement | positioning of the oil introduction groove | channel 85 and the notch part 82 of the back surface (surface 81B) are the surface side (surface 81A). The shape and arrangement of the oil introduction groove 85 and the notch portion 82 are the same, but the present invention is not limited to this, and the shape of the oil introduction groove 85 and the notch portion 82 is changed when the front and back are replaced. Or the arrangement may be different.

  In the above embodiment, the manual transmission (MT) that shifts the sleeve by directly moving the sleeve by operating the operation lever of the driver is taken as an example, but the mechanical automatic that shifts by moving the sleeve by the actuator. The present invention may be applied to a manual transmission (AMT).

DESCRIPTION OF SYMBOLS 1 Transmission 2a Front case 2b Rear case 8 Lubrication structure 10 Input shaft 11 Output shaft 11 Engagement member 12 Counter shaft 12a Shaft center hole 13 Input main gear 14 Input counter gear 15 Reverse idler shaft 16 Reverse idler gear 22 Input dog gear 23 3-speed dog gear 24, 34, 44, 54 Sleeve 32 6-speed dog gear 33 5-speed dog gear 42 2-speed dog gear 43 1-speed dog gear 52 Reverse dog gear 80 2nd thrust washer 81A Surface (surface)
81B side (back side)
82 Notch portion 83 Vertical surface portion 84 Radial surface portion 85 Oil introduction groove 86 Short diameter portion 87 Engagement groove 90 Needle bearing C1 First speed counter gear C2 Second speed counter gear C3 Third speed counter gear C5 Five speed counter gear C6 Six speed counter Gear M1 1st speed main gear M2 2nd speed main gear M3 3rd speed main gear M5 5th speed main gear M6 6th speed main gear MR Reverse main gear

Claims (6)

A substantially annular thrust washer provided so as to be integrally rotatable on a rotating shaft,
One or more oil introduction grooves formed on at least one surface and extending from the inner periphery to the outer periphery in a predetermined rotation direction with respect to the diameter of the rotation shaft;
A notch formed on the downstream side in the predetermined rotation direction adjacent to the outer peripheral opening of the oil introduction groove;
Thrust washer with. The notch is configured by a radial surface portion having a radial surface extending in the radial direction, and a vertical surface portion having a vertical surface extending in a direction perpendicular to the radial direction from an inner peripheral side end portion of the radial surface. The thrust washer according to claim 1. The thrust washer according to claim 2, further comprising a short diameter portion that is formed at a position immediately before the notch portion on the downstream side in the predetermined rotation direction and has an outer diameter shorter than a maximum outer diameter of the thrust washer. The thrust washer according to any one of claims 1 to 3, wherein an engagement groove that engages with an engagement member provided on the rotating shaft is formed on an inner periphery of the thrust washer. The oil introduction groove and the notch are formed on the other surface so as to be in the same state as the one surface when the front and back surfaces of the thrust washer are reversed. Item 5. The thrust washer according to any one of Items 4 to 9. A lubricating structure having a rotating shaft, a substantially annular thrust washer provided on the rotating shaft, and a member provided adjacent to the thrust washer on the rotating shaft;
The thrust washer is
One or more oil introduction grooves formed on at least one surface, which are inclined in a predetermined rotation direction with respect to the diameter of the rotation shaft and extend from the inner periphery to the outer periphery;
A notch formed on the downstream side in the predetermined rotation direction adjacent to the outer peripheral opening of the oil introduction groove;
Lubricating structure having

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