JP6332360B2 - Lubrication structure of power transmission device - Google Patents

Description

  The present invention belongs to a technical field related to a lubricating structure of a power transmission device.

  Conventionally, in a power transmission device such as a transmission of a vehicle, the lower part of a gear is immersed in an oil reservoir, and the oil in the oil reservoir is scraped up by the rotating gear, It is known to supply to a lubricated part (for example, refer to Patent Document 1).

  In Patent Document 1, oil scraped up by a gear is supplied to the same oil receiving portion through an oil supply path that varies depending on the rotational speed of the gear. That is, a rib (branching mechanism) having a triangular side surface is provided on the upper part of the gear, and this rib causes the oil movement direction to branch in different directions according to the rotational speed of the gear. The oil branched into the first oil receiving section is guided to the same oil receiving section through the first and second oil supply paths. And oil is supplied to a to-be-lubricated part from an oil receiving part.

JP 2003-336729 A

  Incidentally, the amount of oil in the oil reservoir (that is, the amount of immersion of the gear in the oil) is preferably reduced as much as possible from the viewpoint of reducing the rotational resistance of the gear, but the amount of oil in the oil reservoir (the amount of immersion above) When the amount is reduced, the amount of oil scraped by the gear is reduced, and it becomes difficult to supply a sufficient amount of oil to the lubricated portion.

  In the configuration as in Patent Document 1, the oil scooped up by the gear is supplied to the same oil receiving portion via the first or second supply path regardless of the rotational speed of the gear. It becomes easy to secure the oil supply amount to the lubrication part.

  However, in the configuration of Patent Document 1, since there is no member around the gear that guides the oil scraped up by the gear to the rib, most of the scraped up oil is scattered from the gear on the way. Therefore, only a small amount of oil adhering to the gear teeth may be supplied to the first or second oil supply path. For this reason, reducing the amount of oil in the oil reservoir (the amount of immersion above), especially when a sufficient amount of oil is required to be supplied to the lubricated part, such as during high gear rotation. There is a high possibility that the amount of oil supplied to the lubrication part will be insufficient.

  The present invention has been made in view of such a point, and an object of the present invention is to provide an oil storage device with a simple configuration in a lubricating structure of a power transmission device including a gear for scooping up oil in an oil storage unit. The amount of oil supplied to the lubricated portion can be ensured while reducing the amount of oil in the portion (the amount of immersion of the gear in the oil), especially when the gear rotates at a high speed.

  In order to achieve the above object, according to the present invention, an oil storage part in which oil is stored, a first gear in which a lower part is immersed in the oil in the oil storage part and scrapes the oil by rotation, and the first gear For a lubricating structure of a power transmission device provided with a second gear arranged on the upper side of one gear and meshing with the first gear, a portion immersed in oil in the oil reservoir in the outer peripheral portion of the first gear A guide that is disposed to face a portion from the first gear toward the rotation direction leading side and guides the oil scraped up by the first gear to be discharged in a tangential direction of the rotation of the first gear. A first discharge part that discharges oil scraped up by the first gear toward a meshing part between the first gear and the second gear; and the first discharge part. For the first gear A second discharge portion that is arranged side by side in the axial direction and discharges the oil scooped up by the first gear toward an oil collecting member that is disposed at a height higher than the first gear; And the second discharge part is configured to collect the oil discharged from the second discharge part by the oil collecting member when the rotational speed of the first gear is higher than a predetermined speed. The oil is discharged from the second discharge portion.

  With the above configuration, the oil scooped up by the first gear flows upward through the gap between the outer peripheral portion of the first gear and the guide member, and then from the first discharge portion to the first gear. While being discharged toward the meshing portion with the second gear, it is discharged from the second discharge portion toward the oil collecting member. By setting the amount of the gap to an appropriate amount, a sufficient amount of oil can flow upward through the gap, and sufficient oil can be discharged from the first discharge portion and the second discharge portion. it can. And from the 1st discharge part, oil can be supplied to the above-mentioned meshing part irrespective of the rotation speed of the 1st gear. As a result, even if the amount of oil in the oil storage part is reduced, the meshing part which is one of the parts to be lubricated can be reliably lubricated. Further, when the rotational speed of the first gear is higher than the predetermined speed, it is required to supply a sufficient amount of oil to the lubricated portion. At this time, the meshing portion is in contact with the first gear as described above. A sufficient amount of oil is supplied from the discharge part, and the oil discharged from the second discharge part is collected by the oil collecting member, so that the collected oil is meshed with the oil collecting member. It becomes possible to supply to the lubricated part other than the part. As a result, even when the amount of oil in the oil storage portion is reduced, a sufficient amount of oil can be supplied to the lubricated portion including the meshing portion when the first gear rotates at a high speed. In this way, the guide member is provided around the rotation side of the first gear in the rotation direction, and the oil amount of the oil reservoir (the amount of immersion of the gear in the oil) is reduced while the height of the upper first gear is particularly high. During rotation, the amount of oil supplied to the lubricated portion including the meshing portion can be ensured.

  Here, when the rotation speed of the first gear is equal to or lower than the predetermined speed, the oil collecting member is disposed at a height position higher than that of the first gear, so that the oil discharged from the second discharge portion. Is hard to be collected by the oil collecting member. However, when the first gear is at a low speed, there is no significant problem even if the amount of oil supplied to the lubricated parts other than the meshing part is reduced. Further, the oil supplied to the second gear through the meshing portion can be scattered from the second gear to the outside in the radial direction by the rotation of the second gear, and the scattered oil can be scattered. It can be made to collect by a collecting member. As a result, even when the first gear rotates at a low speed, as much oil as possible can be supplied to the lubricated part other than the meshing part.

  In one embodiment of the lubricating structure of the power transmission device, the first gear and the second gear are each formed with a tooth portion having a predetermined twist angle with respect to the axial direction, and the axial direction of the second gear. A flange-shaped member that is provided adjacent to a side of the tooth portion that is positioned behind the rotation direction of the tooth portion so as to rotate integrally with the second gear and has an outer diameter larger than the outer diameter of the tooth portion. The flange-shaped member is further provided with the oil supplied to the second gear through the meshing portion and attached to the flange-shaped member to the outside of the flange-shaped member in the radial direction by the rotation of the flange-shaped member. The oil collecting member is configured to collect oil scattered from the flange-like member.

  As a result, the oil supplied to the second gear through the meshing portion of the first gear and the second gear is caused by the twist of the tooth portion of the second gear, and the surface of the tooth portion is rotated along with the rotation of the second gear. To the flange-like member side and adhere to the flange-like member. The oil adhering to the flange-like member scatters radially outward from the flange-like member as the second gear and the flange-like member rotate, and the oil scattered from the flange-like member is captured by the oil collecting member. Be collected. Since the flange-shaped member has an outer diameter larger than the outer diameter of the tooth portion, it is possible to increase the centrifugal force acting on the oil, whereby the second gear is reduced by the low rotation of the first gear. Even with rotation, the amount of oil collected by the oil collecting member can be secured. Therefore, the oil supply amount to the lubricated part other than the meshing part can be ensured regardless of the rotation speeds of the first gear and the second gear.

  In the one embodiment, it is preferable that the first discharge portion is disposed closer to the flange-like member than the second discharge portion in the axial direction of the first gear.

  Thus, a larger amount of oil discharged from the first discharge portion is supplied to a portion closer to the flange-like member in the meshing portion of the first gear and the second gear, and adheres to the flange-like member. The amount of oil can be increased. As a result, the amount of oil collected by the oil collecting member can be increased.

  Or in the said one Embodiment, the said 1st discharge | release part may be arrange | positioned in the axial direction of the said 1st gear on the far side with respect to the said flange-shaped member rather than the said 2nd discharge | release part.

  With this configuration, the oil discharged from the first discharge portion is supplied more to the portion far from the flange-like member in the meshing portion of the first gear and the second gear, but is supplied to the meshing portion. As the second gear rotates, the oil flows to the flange-like member side along the surface of the tooth portion and scatters radially outward from the flange-like member, so that it is collected by the oil collecting member. There is no such thing as less oil.

  As described above, according to the lubricating structure of the power transmission device of the present invention, it opposes the portion of the outer periphery of the first gear from the portion immersed in the oil in the oil reservoir to the forward side in the rotational direction of the first gear. And a guide member that guides the oil scooped up by the first gear so as to be discharged in a tangential direction of the rotation of the first gear. The guide member is scraped by the first gear. A first discharge part for discharging the raised oil toward the meshing part of the first gear and the second gear; and adjacent to the first discharge part in the axial direction of the first gear. A second discharge part that is disposed and discharges the oil scooped up by the first gear toward an oil collecting member that is disposed at a height higher than the first gear, and In the second discharge portion, the rotation speed of the first gear is a predetermined speed. Is configured to discharge oil from the second discharge portion so that the oil discharged from the second discharge portion is collected by the oil collecting member when With the configuration, it is possible to secure the amount of oil supplied to the lubricated portion, particularly when the first gear rotates at a high speed, while reducing the amount of oil in the oil reservoir (the amount of gear immersed in the oil).

It is a figure showing typically a manual transmission as a power transmission device to which a lubrication structure concerning an embodiment of the present invention was applied. It is the II-II sectional view taken on the line of FIG. It is a perspective view of the gear train for 2nd speed. It is the perspective view which looked at the gear train for 2nd speed from the direction different from FIG. It is a perspective view which shows the modification of a flange-shaped member. FIG. 6 is a view corresponding to FIG. 3 showing a modification of the guide member. It is a figure which shows typically another manual transmission to which the lubrication structure which concerns on embodiment of this invention was applied.

  Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.

  FIG. 1 schematically shows a manual transmission 1 as a power transmission device to which a lubricating structure according to an embodiment of the present invention is applied. This manual transmission 1 is mounted in an engine room located at the front of a vehicle (in this embodiment, an FR vehicle), and is configured to be able to achieve six forward speeds and one reverse speed. A drive source (not shown) such as an engine is disposed on the front side of the vehicle (the left side in FIG. 1) of the manual transmission 1. The manual transmission 1 has a transmission case 5. The transmission case 5 includes a clutch housing 2, a transmission case 3, and an extension housing 4 that are sequentially arranged from the vehicle front side. A clutch 7 which will be described later is disposed in the clutch housing 2.

  In the transmission case 5, an input shaft 10 that extends in the horizontal direction and in the vehicle front-rear direction, and an output that is disposed on the same axis as the input shaft 10 on the side opposite to the driving source (vehicle rear side) of the input shaft 10. A shaft 20 is provided. An end of the input shaft 10 on the drive source side (the vehicle front side) is connected to the output shaft 6 of the drive source via a clutch 7 that is disconnected by a stepping operation of an occupant (driver) of the vehicle. . The end of the input shaft 10 on the side opposite to the driving source is fitted and supported rotatably on the end of the output shaft 20 on the side of the driving source. The output shaft 20 is connected to a rear wheel as a drive wheel via a propeller shaft, a differential mechanism, and the like.

  On the drive source side, the input shaft 10 is rotatably supported by a vertical wall portion 2 a provided in the clutch housing 2 via a bearing 41, and the output shaft 20 is provided in a vertical wall portion 3 a provided in the transmission case 3. And a vertical wall portion 4a provided in the extension housing 4 via a bearing 42 and a bearing 43, respectively, so as to be rotatable.

  Further, in the transmission case 5, a counter shaft 30 disposed in parallel with the input shaft 10 and the output shaft 20 is provided at a height position lower than the input shaft 10 and the output shaft 20. The end of the counter shaft 30 on the drive source side is rotatably supported by the vertical wall 2 a of the clutch housing 2 via a bearing 44, and the end of the counter shaft 30 on the counter drive source side is The vertical wall 3a and the vertical wall 4a of the extension housing 4 are rotatably supported via a bearing 45 and a bearing 46, respectively.

  The input shaft 10 includes a reverse drive gear 11, a first speed drive gear 12, a second speed drive gear 13, a third speed drive gear 14, a fourth speed drive gear 15, and a fifth speed drive in order from the drive source side. A gear 16 is provided. The reverse drive gear 11, the first speed drive gear 12, the second speed drive gear 13, the third speed drive gear 14 and the fourth speed drive gear 15 are fixed to the input shaft 10, and are the fifth speed drive gear. 16 is loosely fitted to the input shaft 10. The reverse drive gear 11 and the first speed drive gear 12 are formed integrally.

  The counter shaft 30 includes, in order from the drive source side, a reverse driven gear 21, a first speed driven gear 22, a second speed driven gear 23, a third speed driven gear 24, a fourth speed driven gear 25, and a fifth speed driven gear. A gear 26 and a reduction drive gear 27 are provided. The reverse driven gear 21, the first speed driven gear 22, the second speed driven gear 23, the third speed driven gear 24, and the fourth speed driven gear 25 are loosely fitted to the counter shaft 30, and the fifth speed driven gear 26. The reduction drive gear 27 is fixed to the counter shaft 30.

  The first-speed drive gear 12 and the first-speed driven gear 22 are always meshed with each other to form a first-speed gear train G1. The second-speed drive gear 13 and the second-speed driven gear 23 are always meshed with each other to form a second-speed gear train G2. The third-speed drive gear 14 and the third-speed driven gear 24 are always meshed with each other to form a third-speed gear train G3. The 4-speed drive gear 15 and the 4-speed driven gear 25 are always meshed with each other, and constitute a 4-speed gear train G4. The fifth speed drive gear 16 and the fifth speed driven gear 26 are always meshed with each other to form a fifth speed gear train G5. These gear trains G1 to G5 are called forward gear trains. The five forward gear stages are arranged in the mission case 3.

  The five forward speed gear trains are arranged so as to be a gear train for a lower gear speed on the drive source side in the axial direction of the input shaft 10 (a gear train for a gear stage having a larger reduction ratio on the drive source side). Will be. As a result, the outer diameters of the drive gears of the five forward shift gear trains provided on the input shaft 10 become smaller toward the drive source side, and the forward shift gear trains provided on the counter shaft 30 are reduced. The outer diameter of the driven gear increases toward the drive source side.

  In the transmission case 5 (in the transmission case 3), a reverse shaft (not shown) is provided that is disposed in parallel to the input shaft 10, the output shaft 20, and the counter shaft 30 and is fixed to the transmission case 3. Yes. A reverse idle gear (not shown) is loosely fitted to the reverse shaft. The reverse driving gear 11 and the reverse driven gear 21 are always meshed with the reverse idle gear. The reverse drive gear 11, the reverse driven gear 21, and the reverse idle gear constitute a reverse gear train GR.

  The output shaft 20 is provided with a reduction driven gear 17 that is always meshed with a reduction drive gear 27 provided on the counter shaft 30. The reduction drive gear 27 and the reduction driven gear 17 are arranged in the extension housing 4 and constitute a reduction gear train GN that reduces the rotation of the counter shaft 30 at a constant reduction ratio and outputs it to the output shaft 20. doing. Note that the reduction ratio of the reduction gear train GN can be set to 1.

  A reverse synchronization device for connecting and disconnecting the reverse driven gear 21 and the counter shaft 30 on the counter shaft 30 on the drive source side of the reverse driven gear 21 (between the reverse driven gear 21 and the bearing 44). 51 is provided.

  Between the first-speed driven gear 22 and the second-speed driven gear 23 on the counter shaft 30, between the first-speed driven gear 22 and the counter shaft 30, and between the second-speed driven gear 23 and the counter shaft 30, A 1-2 speed synchronizer 52 is provided for connecting and disconnecting the two.

  Between the third speed driven gear 24 and the fourth speed driven gear 25 in the counter shaft 30, between the third speed driven gear 24 and the counter shaft 30, and between the fourth speed driven gear 25 and the counter shaft 30, 3-4 speed synchronizer 53 for connecting and disconnecting between the two is provided.

  On the side opposite to the driving source of the fifth speed drive gear 16 in the input shaft 10 (between the fifth speed drive gear 16 and the output shaft 20), the input between the fifth speed drive gear 16 and the input shaft 10 and the input A 5-6 speed synchronizer 54 for connecting and disconnecting between the shaft 10 and the output shaft 20 is provided.

  The reverse synchronization device 51 is configured to fix the reverse driven gear 21 to the counter shaft 30 when a change lever (not shown) is shifted to a reverse speed by an occupant of the vehicle. As a result, the reverse gear train GR is in a power transmission state.

  That is, when the change lever is shifted to the reverse speed, the reverse driven gear 21 and the counter shaft 30 are connected by the reverse synchronization device 51, and the rotation of the input shaft 10 is countered by the reverse gear train GR. The rotation transmitted to the shaft 30 and transmitted to the counter shaft 30 is decelerated at a constant reduction ratio by the reduction gear train GN and transmitted to the output shaft 20.

  The first-second speed synchronizing device 52 fixes the first-speed driven gear 22 or the second-speed driven gear 23 to the counter shaft 30 when the change lever is shifted to the first speed or the second speed. ing. As a result, the first-speed gear train G1 or the second-speed gear train G2 enters the power transmission state.

  That is, when the change lever is shifted to the first speed or the second speed, the first-speed driven gear 22 or the second-speed driven gear 23 and the counter shaft 30 are connected by the first-second speed synchronization device 52, The rotation of the input shaft 10 is transmitted to the counter shaft 30 by the first-speed gear train G1 or the second-speed gear train G2, and the rotation transmitted to the counter shaft 30 is transmitted at a constant reduction ratio by the reduction gear train GN. It is decelerated and transmitted to the output shaft 20.

  The 3-4 speed synchronization device 53 fixes the 3rd speed driven gear 24 or the 4th speed driven gear 25 to the counter shaft 30 when the change lever is shifted to the 3rd speed or the 4th speed. ing. As a result, the third-speed gear train G3 or the fourth-speed gear train G4 enters the power transmission state.

  That is, when the change lever is shifted to the 3rd speed or the 4th speed, the 3rd speed driven gear 24 or the 4th speed driven gear 25 is connected to the counter shaft 30 by the 3-4 speed synchronizer 53, The rotation of the input shaft 10 is transmitted to the counter shaft 30 by the third-speed gear train G3 or the fourth-speed gear train G4, and the rotation transmitted to the counter shaft 30 is transmitted at a constant reduction ratio by the reduction gear train GN. It is decelerated and transmitted to the output shaft 20.

  The 5-6 speed synchronizer 54 fixes the 5th speed drive gear 16 to the input shaft 10 when the change lever is shifted to 5th speed. Thus, when the change lever is shifted to the fifth speed, the fifth speed gear train G5 is in a power transmission state.

  That is, when the change lever is shifted to the 5th speed, the 5-6 speed synchronizer 54 connects the 5th speed drive gear 16 and the input shaft 10, and the rotation of the input shaft 10 is for the 5th speed. The rotation is transmitted to the counter shaft 30 by the gear train G5, and the rotation transmitted to the counter shaft 30 is decelerated at a constant reduction ratio by the reduction gear train GN and transmitted to the output shaft 20.

  Further, the 5-6 speed synchronizer 54 is configured to directly connect the input shaft 10 and the output shaft 20 when the change lever is shifted to the 6th speed. Thereby, the input shaft 10 and the output shaft 20 are directly connected by the 5-6 speed synchronizer 54, and the rotation of the input shaft 10 is directly transmitted to the output shaft 20 without passing through the counter shaft 30. The

  As described above, the manual transmission 1 causes the rotation of the input shaft 10 to change the speed gear train (the reverse gear train GR and the five forward gears) provided between the input shaft 10 and the counter shaft 30. An output reduction type manual transmission that transmits the rotation transmitted to the countershaft 30 by the gear train) and the rotation transmitted to the countershaft 30 to the output shaft 20 after being decelerated by the reduction gear train GN at a constant reduction ratio. Has been.

  An oil reservoir 5a in which oil is stored is provided at the bottom of the transmission case 5 of the manual transmission 1 (specifically, in the transmission case 3 and the extension housing 4). The oil level OL of the oil reservoir 5a is indicated by a broken line in FIG.

  In addition, an oil collecting member 65 that collects the oil scooped up from the oil storing portion 5a by the second-speed driven gear 23 as described later is provided in the upper part in the mission case 3. The oil collecting member 65 has a bottom surface portion 65a extending in the axial direction of the input shaft 10 and left and right side surface portions 65b extending upward from the left and right end portions of the bottom surface portion 65a. It is formed in an open bowl shape.

  The oil collecting member 65 is located at the same position as the second-speed gear train G2 in the axial direction of the input shaft 10. On the drive source side and the counter drive source side of the oil collecting member 65, the oil collected by the oil collecting member 65 is transferred to the second speed driving gear 13 and the second speed driven gear in the transmission case 5. The oil supply members 66 for supplying to the lubricated parts excluding the meshing part 63 with 23 are respectively connected. These oil supply members 66 are formed in a bowl shape like the oil collecting member 65, and extend continuously from the oil collecting member 65 in the axial direction of the input shaft 10. The oil supply member 66 is inclined so that the oil collected by the oil collecting member 65 flows to the drive source side or the counter drive source side. The parts to be lubricated by the oil include, for example, the bearings 41 to 46, the meshing parts of a pair of gears of the gear trains G1 to G5, GN, and the meshing parts of a set of gears for the reverse gear train GR.

  As shown in FIG. 2, the input shaft 10 rotates in the R1 direction (clockwise direction in FIG. 2 as viewed from the drive source side), and the second-speed drive gear 13 fixed to the input shaft 10 also moves in the R1 direction. Rotate. The second-speed driven gear 23 that always meshes with the second-speed drive gear 13 rotates in the R2 direction (counterclockwise direction in FIG. 2). The oil collecting member 65 is located at an upper position in the transmission case 5 at substantially the same height position as the uppermost portion of the second-speed drive gear 13 (a height position higher than the second-speed driven gear 23). The second-speed drive gear 13 is disposed on the side of the advance side (right side in FIG. 2) in the rotation direction (R1 direction) of the second-speed drive gear 13.

  On the ceiling surface above the oil collecting member 65 in the mission case 3, a rib 3 b is provided so as to extend downward toward the oil collecting member 65. The rib 3b guides the oil that is scattered from the second-speed drive gear 13 and the flange-shaped member 60, which will be described later, and adheres to the ceiling surface and the rib 3b, to the oil collecting member 65, as will be described later. Is. Also, the rib 3b guides the oil that is discharged from a second discharge portion 71c of the guide member 71 described later and adheres to the ceiling surface and the rib 3b so as to drop to the oil collecting member 65.

  In the present embodiment, the drive gears 11 to 16 provided on the input shaft 10 and the driven gears 21 to 26 provided on the counter shaft 30 of the gear trains GR and G1 to G5 are respectively helical gears. . That is, each gear is formed with a tooth portion having a predetermined twist angle with respect to the axial direction of each gear. Similarly, the reduction drive gear 27 and the reduction driven gear 17 of the reduction gear train GN are also helical gears.

  The second speed gear train G2 will be described with reference to FIG. 3 and FIG. 4. The second speed drive gear 13 is predetermined with respect to the axial direction of the second speed drive gear 13 (same as the axial direction of the input shaft 10). A tooth portion 13a having a twist angle of 1 mm is formed. When the second-speed drive gear 13 rotates in the R1 direction, the tooth portion 13a is positioned such that the drive source side of the tooth portion 13a is on the rotation direction advance side and the counter drive source side of the tooth portion 13a is on the rotation direction delay side. It is formed to do.

  A tooth portion 23a having a predetermined twist angle with respect to the axial direction of the second-speed driven gear 23 (same as the axial direction of the counter shaft 30) is formed in the second-speed driven gear 23 that meshes with the second-speed drive gear 13. Has been. When the second-speed driven gear 23 rotates in the R2 direction as the second-speed drive gear 13 rotates, the tooth portion 23a has the drive source side of the tooth portion 23a positioned on the rotational direction advance side and the tooth portion 23a. The counter drive source side is positioned on the rotation direction delay side. The tooth portions 13a and 23a may be formed so that the drive source side of the tooth portions 13a and 23a is located on the rotation direction delay side and the counter drive source side of the tooth portions 13a and 23a is located on the rotation direction advance side.

  The lower part of the second-speed driven gear 23 is immersed in the oil in the oil reservoir 5a. Thus, the lowermost portion of the second-speed driven gear 23 and the tooth portion 23a located in the vicinity thereof are immersed in the oil in the oil reservoir 5a. In the present embodiment, the lower part of the reverse driven gear 21, the lower part of the first speed driven gear 22, and the lower part of the third speed driven gear 24 are also immersed in the oil in the oil reservoir 5 a.

  Since the lower part of the second-speed driven gear 23 is immersed in the oil in the oil reservoir 5a, the second-speed driven gear 23 scrapes the oil in the oil reservoir 5a by the rotation of the second-speed driven gear 23. increase. The oil scooped up by the second-speed driven gear 23 is supplied to the meshing portion 63 between the second-speed drive gear 13 and the second-speed driven gear 23 and the oil collecting member 65 as will be described later.

  As shown in FIG. 1 to FIG. 3, the second speed driven from the portion (the lowermost part in the present embodiment) immersed in the oil of the oil reservoir 5 a in the outer peripheral portion (tooth portion 23 a) of the second speed driven gear 23. The oil scraped up by the second-speed driven gear 23 is placed at a position opposite to the portion of the gear 23 that extends toward the rotation direction (the portion that moves from the lower side to the upper side by the rotation of the second-speed driven gear 23). A guide member 71 is disposed to guide the second speed driven gear 23 so as to be released in a tangential direction of rotation. The guide member 71 is a plate-like member that is bent in an arc shape in the thickness direction so as to have a constant interval with respect to the addendum circle of the tooth portion 23a.

  The oil scraped up by the second-speed driven gear 23 by the guide member 71 passes through the gap between the outer peripheral portion (tooth portion 23a) of the second-speed driven gear 23 and the guide member 71, and is stored in the oil reservoir. It flows from 5a to the upper side. The amount of the gap is set to such a value that as much oil as possible flows through the gap as long as the rotational resistance of the second-speed driven gear 23 is hardly affected.

  The guide member 71 has a substantially quadrant main body portion 71a as viewed from the axial direction of the second-speed driven gear 23, and is aligned with the main body portion 71a in the axial direction of the second-speed driven gear 23. The provided 1st discharge | release part 71b and the 2nd discharge | release part 71c are provided. In this embodiment, the 1st discharge | release part 71b is located in the counter drive source side, and the 2nd discharge | release part 71c is located in the drive source side.

  The first discharge portion 71b has an arc shape continuously to the main body portion 71a when viewed from the axial direction of the second-speed driven gear 23, and the meshing portion between the second-speed drive gear 13 and the second-speed driven gear 23 It extends to the vicinity of 63. Accordingly, the first discharge portion 71b discharges the oil scraped up by the second speed driven gear 23 toward the meshing portion 63 in the tangential direction.

  On the other hand, when viewed from the axial direction of the second-speed driven gear 23, the second discharge portion 71c is separated from the main body 71a by the oil collecting member 65 (strictly speaking, the second-speed drive gear 13 of the oil collecting member 65 is different from the second-speed driven gear 13). It extends linearly upward so as to go to the opposite side. As a result, the second discharge portion 71c causes the oil scraped up by the second-speed driven gear 23 to flow in the tangential direction and to the oil collection member 65 (strictly speaking, the second-speed drive gear of the oil collection member 65). To the side opposite to 13).

  When the rotational speed of the second-speed driven gear 23 is higher than a predetermined speed, the second discharge portion 71c is configured so that the oil discharged from the second discharge portion 71c is collected by the oil collecting member 65. The oil is discharged from the second discharge portion 71c. That is, when the rotational speed of the second-speed driven gear 23 is higher than the predetermined speed, the second discharge portion 71c is configured such that the oil discharged from the second discharge portion 71c reaches the upper side of the oil collecting member 65. Release oil at release rate. The oil discharged from the second discharge portion 71c directly enters the oil collecting member 65 or enters from the ceiling surface above the oil collecting member 65 via the rib 3b.

  Since the tip of the first discharge portion 71b is located in the vicinity of the meshing portion 63, oil is supplied from the first discharge portion 71b to the meshing portion 63 regardless of the rotational speed of the second-speed driven gear 23. .

  On the other hand, the tip (upper end) of the second discharge part 71c is separated from the oil collecting member 65. When the rotation speed of the second gear driven gear 23 is equal to or lower than the predetermined speed, the second discharge part 71c The released oil is difficult to be collected by the oil collecting member 65.

  Therefore, in the present embodiment, even when the rotational speed of the second-speed driven gear 23 is equal to or lower than the predetermined speed, the oil supplied to the second-speed drive gear 13 through the meshing portion 63 is supplied to the oil collecting member 65. It is configured to be supplied.

  Specifically, the outer diameter (tooth tip circle) of the tooth portion 13a is adjacent to the side located on the rotation direction delay side of the tooth portion 13a in the axial direction of the second-speed drive gear 13 (that is, the counter-drive source side). A flange-shaped member 60 having an outer diameter larger than (diameter) is provided. The flange-shaped member 60 is provided so as to rotate integrally with the second-speed drive gear 13.

  The flange-shaped member 60 is formed in a disk shape having a predetermined thickness in the axial direction of the second-speed drive gear 13. A side surface 60 a of the flange-shaped member 60 on the second speed drive gear 13 side is formed in a planar shape in a direction substantially orthogonal to the axial direction of the second speed drive gear 13.

  On the inner peripheral side of the side surface 60a of the flange-shaped member 60, a connecting portion 60b that is connected to the second-speed drive gear 13 is provided. The flange-shaped member 60 may be integrally formed with the second-speed drive gear 13 or may be formed separately from the second-speed drive gear 13 and then integrally coupled with the second-speed drive gear 13 using press-fitting or the like. You may do it.

  The oil supplied to the meshing part 63 from the first discharge part 71b of the guide member 71 adheres to the tooth part 13a located at the lower part of the second-speed drive gear 13 in the meshing part 63. The oil supplied from the discharge portion 71 b to the meshing portion 63 is supplied to the second-speed drive gear 13 via the meshing portion 63. The oil supplied to the second-speed drive gear 13 flows toward the flange-shaped member 60 along the surface of the tooth portion 13a as the second-speed drive gear 13 rotates due to the twist of the tooth portion 13a. That is, the oil supplied to the second-speed drive gear 13 (the oil adhering to the tooth portion 13a) is opposite to the driving source side (flange-like member 60) of the tooth portion 13a as shown by a region A indicated by a one-dot chain line in FIG. While moving to the upper side).

  Here, in this embodiment, the 1st discharge | release part 71b is arrange | positioned in the axial direction of the 2nd-speed driven gear 23 at the nearer side with respect to the flange-shaped member 60 than the 2nd discharge | release part 71c. As a result, a large amount of oil discharged from the first discharge portion 71b is supplied to the portion of the meshing portion 63 closer to the flange-like member 60, and the amount of oil adhering to the flange-like member 60 is increased. Can do.

  The oil that has moved upward while moving to the counter drive source side of the tooth portion 13 a of the second-speed drive gear 13 adheres to the side surface 60 a of the flange-shaped member 60. As shown in FIG. 2, the oil adhering to the side surface 60 a is rotated from the peripheral portion 60 c of the flange-like member 60 by the rotation of the flange-like member 60 that rotates in the R1 direction together with the second-speed drive gear 13. The oil that scatters outward in the radial direction and scatters from the flange-shaped member 60 is collected by the oil collecting member 65. The oil scattered from the flange-shaped member 60 directly enters the oil collecting member 65 or enters from the ceiling surface above the oil collecting member 65 via the rib 3b. The oil collected in the oil collecting member 65 in this way is supplied to the lubricated portion excluding the meshing portion 63 in the transmission case 5 via the oil supply member 66.

  Since the flange-shaped member 60 has an outer diameter larger than the outer diameter of the tooth portion 13a, the centrifugal force acting on the oil can be increased, whereby the second-speed driven gear 23 can be reduced to the predetermined speed or less. By rotating, the amount of oil collected by the oil collecting member 65 can be ensured even when the second-speed drive gear 13 is at a low rotation.

  In the present embodiment, the second-speed driven gear 23 corresponds to a first gear whose lower part is immersed in the oil in the oil reservoir 5a and scrapes the oil by rotation, and the second-speed drive gear 13 is the first gear. It corresponds to a second gear arranged on the upper side of the gear and meshing with the first gear.

  FIG. 5 shows a modification of the flange-shaped member 60. In this modified example, the flange-shaped member 60 provided adjacent to the second-speed drive gear 13 is recessed in the axial direction of the second-speed drive gear 13 and extends in the radial direction on the side surface 60a on the second-speed drive gear 13 side. A plurality of guide groove portions 60d are provided.

  The plurality of guide groove portions 60d are provided at equal intervals in the circumferential direction of the flange-shaped member 60, and between the adjacent guide groove portions 60d, protrusions 60e that protrude toward the second-speed drive gear 13 are formed. Yes. The protrusion 60e extends in the radial direction from the inner peripheral side toward the outer peripheral side to the peripheral edge 60c on the side surface 60a. Here, the protrusion 60e does not extend linearly in the radial direction of the flange-like member 60 when viewed from the axial direction of the second-speed drive gear 13, but when the flange-like member 60 rotates in the R1 direction, The protrusion 60e is curved so that the radially outer side is positioned on the delay side in the rotational direction as compared with the radially inner side.

  Thus, by forming the guide groove portion 60d on the side surface 60a of the flange-shaped member 60, the amount of oil attached to the side surface 60a and scattered from the peripheral portion 60c can be increased, and the oil collecting member 65 can be increased. The amount of oil collected can be increased.

  FIG. 6 shows a modification of the guide member 71. In this modification, the positional relationship in the axial direction of the second-speed driven gear 23 between the first discharge portion 71b and the second discharge portion 71c is opposite to that in the above embodiment, and the first discharge portion 71b In the axial direction of the second-speed driven gear 23, the second-speed driven portion 23 is disposed farther from the flange-like member 60 than the second discharge portion 71 c.

  As a result, a large amount of oil released from the first discharge portion 71b is supplied to the portion far from the flange-shaped member 60 in the meshing portion 63 of the second-speed drive gear 13 and the second-speed driven gear 23. However, the oil supplied to the meshing portion 63 flows to the flange-like member 60 side along the surface of the tooth portion 13 a as the second-speed drive gear 13 rotates, and the peripheral portion 60 c of the flange-like member 60. , The amount of oil collected by the oil collecting member 65 does not decrease.

  Therefore, in this embodiment, since the guide member 71 having the first discharge portion 71b and the second discharge portion 71c is provided around the rotation direction advance side of the second-speed driven gear 23, the oil storage portion 5a Even when the amount of oil is small and the amount of immersion of the second-speed driven gear 23 in the oil is small, when the rotational speed of the second-speed driven gear 23 is higher than the predetermined speed (a sufficient amount to the lubricated part) When the oil supply is required), the meshing portion 63 of the second-speed drive gear 13 and the second-speed driven gear 23 and the oil collecting member 65 (by extension, other than the meshing portion 63 are lubricated). Part) can be supplied with a sufficient amount of oil. Therefore, with a simple configuration, the amount of oil stored in the oil reservoir 5a (the amount of immersion of the second-speed driven gear 23 in the oil) is reduced, and particularly when the second-speed driven gear 23 is rotated at a high speed, The oil supply amount to the lubrication part can be ensured.

  Further, in the present embodiment, since the flange-shaped member 60 is provided adjacent to the second-speed drive gear 13, even at the time of low rotation where the rotation speed of the second-speed driven gear 23 is equal to or lower than the predetermined speed, The amount of oil collected by the oil collecting member 65 can be ensured.

  FIG. 7 schematically shows another manual transmission 101 to which the lubrication structure according to the embodiment of the present invention is applied. As with the manual transmission 1, the manual transmission 101 is also mounted in the engine room located at the front of the vehicle (FR vehicle), and is configured to be able to achieve 6 forward speeds and 1 reverse speed. . In addition, about the structure of the manual transmission 101, the same code | symbol is attached | subjected about the same part as FIG. 1, and the detailed description is abbreviate | omitted.

  In the transmission case 5 of the manual transmission 101, an input shaft 110 that extends in the horizontal direction and in the vehicle front-rear direction, and on the same axis line as the input shaft 110 on the opposite drive source side (vehicle rear side) of the input shaft 110. The output shaft 120 is provided. The end of the input shaft 110 on the drive source side is connected to the output shaft 6 of the drive source via the clutch 7. The end of the output shaft 120 on the drive source side is rotatably supported by the end of the input shaft 110 on the side opposite to the drive source.

  The input shaft 110 is rotatably supported by the vertical wall portion 2a of the clutch housing 2 via a bearing 141, and the output shaft 120 is respectively supported by the vertical wall portion 3a of the transmission case 3 and the vertical wall portion 4a of the extension housing 4. 142 and a bearing 143 are rotatably supported.

  In the transmission case 5, a counter shaft 130 disposed in parallel with the input shaft 110 and the output shaft 120 is provided at a height position lower than the input shaft 110 and the output shaft 120. The counter shaft 130 is rotatably supported by the vertical wall portion 2a of the clutch housing 2 and the vertical wall portion 3a of the transmission case 3 via a bearing 144 and a bearing 145, respectively.

  A reduction drive gear 111 is fixedly provided on the input shaft 110. The output shaft 120 includes, in order from the drive source side, a fifth speed driven gear 112, a second speed driven gear 113, a first speed driven gear 114, a fourth speed driven gear 115, a third speed driven gear 116, and A reverse driven gear 117 is provided loosely.

  The counter shaft 130 includes a reduction driven gear 121, a fifth speed drive gear 122, a second speed drive gear 123, a first speed drive gear 124, a fourth speed drive gear 125, and a third speed drive in order from the drive source side. A gear 126 and a reverse drive gear 127 are fixedly provided.

  The reduction drive gear 111 and the reduction driven gear 121 are always meshed with each other, and constitute a reduction gear train GN that reduces the rotation of the input shaft 110 at a constant reduction ratio and transmits it to the counter shaft 130.

  The first-speed driven gear 114 and the first-speed drive gear 124 are always meshed with each other to form a first-speed gear train G1. The second-speed driven gear 113 and the second-speed drive gear 123 are always meshed with each other to form a second-speed gear train G2. The third speed driven gear 116 and the third speed drive gear 126 are always meshed with each other to form a third speed gear train G3. The 4-speed driven gear 115 and the 4-speed drive gear 125 are always meshed with each other to form a 4-speed gear train G4. The 5-speed driven gear 112 and the 5-speed drive gear 122 are always meshed with each other to form a 5-speed gear train G5.

  The reverse driven gear 117 and the reverse drive gear 127 are loosely fitted in a reverse shaft (not shown) disposed in parallel with the input shaft 110, the output shaft 120, and the counter shaft 130 in the extension housing 4. Each of them is always meshed with an idle gear (not shown). The reverse driven gear 117, the reverse drive gear 127, and the reverse idle gear constitute a reverse gear train GR.

  A pair of gears of each of the gear trains GN, G1 to G5 and a set of gears of the reverse gear train GR are respectively helical gears like the manual transmission 1, and each of these gears has a gear of each gear. A tooth portion having a predetermined twist angle with respect to the axial direction is formed.

  On the drive source side of the fifth-speed driven gear 112 in the output shaft 120, a connection between the fifth-speed driven gear 112 and the output shaft 120 and between the input shaft 110 and the output shaft 120 is connected. A 6-speed synchronizer 151 is provided.

  Between the first-speed driven gear 114 and the second-speed driven gear 113 on the output shaft 120, between the first-speed driven gear 114 and the output shaft 120, and between the second-speed driven gear 113 and the output shaft 120, A 1-2 speed synchronizer 152 is provided for connecting and disconnecting the two.

  Between the third-speed driven gear 116 and the fourth-speed driven gear 115 on the output shaft 120, between the third-speed driven gear 116 and the output shaft 120, and between the fourth-speed driven gear 115 and the output shaft 120, 3-4 speed synchronizer 153 for connecting and disconnecting between the two is provided.

  The reverse driven gear 117 and the output shaft 120 are connected to and disconnected from the reverse driven gear 117 side of the output shaft 120 (between the reverse driven gear 117 and the bearing 142 in the extension housing 4). A reverse synchronizer 154 is provided.

  The 5th-6th speed synchronizer 151 fixes the 5th speed driven gear 112 to the output shaft 120 when the change lever is shifted to the 5th speed. As a result, the fifth-speed gear train G5 enters the power transmission state.

  That is, when the change lever is shifted to the fifth speed, the rotation of the input shaft 110 is decelerated at a constant reduction ratio by the reduction gear train GN and transmitted to the counter shaft 130, and is transmitted to the counter shaft 130. The rotation is transmitted to the output shaft 120 by the fifth gear train G5.

  Further, the 5-6 speed gear synchronizer 151 is configured to directly connect the input shaft 110 and the output shaft 120 when the change lever is shifted to the 6th speed. Thus, the input shaft 110 and the output shaft 120 are directly connected by the 5-6 speed synchronizer 151, and the rotation of the input shaft 110 is directly transmitted to the output shaft 120 without passing through the counter shaft 30. The

  The first-second gear synchronizing device 152 fixes the first-speed driven gear 114 or the second-speed driven 113 to the output shaft 120 when the change lever is shifted to the first speed or the second speed. ing. As a result, the first-speed gear train G1 or the second-speed gear train G2 enters the power transmission state.

  That is, when the change lever is shifted to the first speed or the second speed, it is decelerated at a constant reduction ratio by the reduction gear train GN and transmitted to the counter shaft 130, and the rotation transmitted to the counter shaft 130 is It is transmitted to the output shaft 120 by the first gear train G1 or the second gear train G2.

  The 3-4 speed synchronizer 153 fixes the 3rd speed driven gear 116 or the 4th speed driven gear 115 to the output shaft 120 when the change lever is shifted to 3rd speed or 4th speed. ing. As a result, the third-speed gear train G3 or the fourth-speed gear train G4 enters the power transmission state.

  That is, when the change lever is shifted to the 3rd speed or the 4th speed, the speed reduction gear train GN decelerates at a constant reduction ratio and is transmitted to the counter shaft 130, and the rotation transmitted to the counter shaft 130 is It is transmitted to the output shaft 120 by the third gear train G3 or the fourth gear train G4.

    The reverse synchronizer 154 fixes the reverse driven gear 117 to the output shaft 120 when the change lever is operated at a reverse speed. As a result, the reverse gear train GR is in a power transmission state.

  That is, when the change lever is shifted to the reverse speed, the speed is reduced by the reduction gear train GN at a constant reduction ratio and transmitted to the counter shaft 130. The rotation transmitted to the counter shaft 130 is the reverse gear. It is transmitted to the output shaft 120 by the row GR.

  As described above, the manual transmission 101 decelerates the rotation of the input shaft 110 at a constant reduction ratio by the reduction gear train GN, transmits the rotation to the counter shaft 130, and transmits the rotation transmitted to the counter shaft 130 to the output shaft 120. And the countershaft 130, an input reduction type manual transmission that transmits to the output shaft by a gear train for shift speeds.

  Similar to the manual transmission 1, an oil reservoir 5a is provided at the bottom of the manual transmission 101 in the transmission case 5 (in the transmission case 3). The oil level OL of the oil reservoir 5a is indicated by a broken line in FIG. That is, the lower parts of the reduction driven gear 121, the fifth speed drive gear 122, and the fourth speed drive gear 125 are immersed in the oil in the oil reservoir 5a.

  Further, like the manual transmission 1, a bowl-shaped oil collecting member 65 that collects the oil scooped up from the oil reservoir 5 a is provided on the upper part of the manual transmission 101 in the transmission case 3. Yes. On the drive source side and the counter drive source side of the oil collecting member 65, the oil collected by the oil collecting member 65 is transferred to the fifth speed driving gear 122 and the fifth speed driven gear in the transmission case 5. The oil supply members 66 for supplying to the lubricated parts excluding the meshing part 163 with 112 are respectively connected.

  In the manual transmission 101, the fifth speed drive gear 122 (corresponding to the first gear) scoops up the oil in the oil reservoir 5a, and the scooped up oil is collected by the oil collecting member 65. It is like that.

  The oil collecting member 65 is located at the same position as the fifth-speed gear train G5 in the axial direction of the input shaft 110. Similarly to the manual transmission 1, the oil collecting member 65 has a height position (5 (The height position higher than that of the speed driving gear 122) and is located on the side of the leading side in the rotational direction of the fifth speed driven gear 112 with respect to the uppermost portion. The 5-speed drive gear 122 rotates in the same direction as the 2-speed driven gear 23 of the manual transmission 1 (counterclockwise direction as viewed from the drive source side), and the 5-speed driven gear 112 It rotates in the same direction as the second-speed drive gear 13 of the machine 1 (clockwise direction when viewed from the drive source side).

  Similar to the manual transmission 1, a guide member 71 having a main body portion 71a, a first discharge portion 71b, and a second discharge portion 71c is disposed around the rotation direction advance side of the fifth-speed drive gear 122. . That is, the portion (the lowermost portion) immersed in the oil in the oil reservoir 5a in the outer peripheral portion of the fifth speed drive gear 122 to the forward side in the rotational direction of the fifth speed drive gear 122 (of the fifth speed drive gear 122). Guide that guides the oil scraped up by the fifth-speed drive gear 122 so as to be discharged in a tangential direction of the rotation of the fifth-speed drive gear 122 at a position opposite to the portion that moves from the lower side to the upper side by rotation. A member 71 is provided.

  From the first discharge portion 71b of the guide member 71, the oil scraped up by the fifth-speed drive gear 122 is engaged with the meshing portion 163 between the fifth-speed drive gear 122 and the fifth-speed driven gear 112 in the tangential direction. Is released towards

  From the second discharge portion 71c of the guide member 71, the oil scraped up by the fifth speed driving gear 122 is in the tangential direction and the oil collecting member 65 (strictly speaking, for the fifth speed of the oil collecting member 65). It is discharged toward the side opposite to the driven gear 112.

  When the rotational speed of the fifth-speed drive gear 122 is higher than a predetermined speed (different from the predetermined speed for the rotational speed of the second-speed driven gear 23), the second discharge section 71c is separated from the second discharge section 71c. The oil is discharged from the second discharge portion 71c so that the discharged oil is collected by the oil collecting member 65.

  In the manual transmission 101 as well, similarly to the manual transmission 1, the first discharge portion 71b is positioned on the counter drive source side, and the second discharge portion 71c is positioned on the drive source side. As described with reference to FIG. 6, the positional relationship in the axial direction of the fifth-speed drive gear 122 between the first discharge portion 71b and the second discharge portion 71c may be reversed.

  Further, a flange-like member 60 similar to the manual transmission 1 is provided adjacent to the fifth-speed driven gear 112. This flange-like member 60 is also integrally with the fifth-speed driven gear 112 adjacent to the side (counter-drive source side) located on the rotation direction delay side of the tooth portion in the axial direction of the fifth-speed driven gear 112. It is provided to rotate. A side surface 60 a of the flange-shaped member 60 on the fifth speed driven gear 112 side is formed in a planar shape in a direction substantially orthogonal to the axial direction of the fifth speed driven gear 112. As described with reference to FIG. 5, the guide groove portion 60d and the protruding portion 60e may be formed on the side surface 60a.

  As described above, the configuration of the oil supply to the oil collecting member 65 in the manual transmission 101 is the same as that of the manual transmission 1, and therefore the manual transmission 101 also has a simple configuration and the oil in the oil reservoir 5a. The amount of oil supplied to the lubricated portion including the meshing portion 163 can be ensured while reducing the amount (the amount of immersion of the 5-speed drive gear 122 in the oil), particularly when the 5-speed drive gear 122 is rotating at high speed. . Further, the amount of oil collected by the oil collecting member 65 can be ensured even when the fifth speed drive gear 122 is rotating at a low speed.

  The present invention is not limited to the embodiment described above, and can be substituted without departing from the spirit of the claims.

  For example, in the above embodiment, the second-speed driven gear 23 of the second-speed gear train G2 of the manual transmission 1 or the fifth-speed drive gear 122 of the fifth-speed gear train G5 of the manual transmission 101 is used in the present invention. As the first gear, the second-speed drive gear 13 of the second-speed gear train G2 of the manual transmission 1 or the fifth-speed driven gear 112 of the fifth-speed gear train G5 of the manual transmission 101 is used in the present invention. Although the second gear is used, the first gear may be a gear in which the lower part is immersed in the oil in the oil reservoir 5a in another gear train, and the second gear may be a gear that meshes with the gear. .

  In addition, the present invention is not limited to a manual transmission, and a first gear that has a lower part immersed in oil in an oil reservoir and scrapes the oil by rotation, is disposed on the upper side of the first gear, and the first gear. As long as the power transmission device includes a second gear that meshes with the power transmission device, the power transmission device can be applied to any power transmission device.

  The above-described embodiments are merely examples, and the scope of the present invention should not be interpreted in a limited manner. The scope of the present invention is defined by the scope of the claims, and all modifications and changes belonging to the equivalent scope of the claims are within the scope of the present invention.

  The present invention includes an oil storage part in which oil is stored, a first gear whose lower part is immersed in the oil in the oil storage part, and that scrapes up the oil by rotation, and is disposed above the first gear and This is useful for a lubricating structure of a power transmission device including a second gear meshing with the first gear.

DESCRIPTION OF SYMBOLS 1 Manual transmission 5a Oil storage part 13 2nd speed drive gear (2nd gear)
23 Second-speed driven gear (first gear)
60 flange-like member 65 oil collecting member 71 guide member 71b first discharge portion 71c second discharge portion 100 manual transmission 112 fifth gear driven gear (second gear)
122 5-speed drive gear (first gear)

Claims (4)

An oil storage part in which oil is stored; a first gear whose lower part is immersed in the oil in the oil storage part and scrapes up the oil by rotation; and the first gear disposed above the first gear; A lubricating structure of a power transmission device including a meshing second gear,
Oil that is disposed facing the portion of the outer peripheral portion of the first gear that is immersed in the oil in the oil storage portion to the leading side in the rotational direction of the first gear and is scooped up by the first gear A guide member that guides the first gear to be released in a tangential direction of rotation of the first gear,
The guide member is
A first discharge part that discharges oil scraped up by the first gear toward a meshing part of the first gear and the second gear;
Oil that is arranged in the axial direction of the first gear with respect to the first discharge portion and that is scooped up by the first gear is disposed at a height higher than that of the first gear. A second discharge part that discharges toward the collecting member;
Have
The second discharge part is configured to allow the oil discharged from the second discharge part to be collected by the oil collecting member when the rotational speed of the first gear is higher than a predetermined speed. A lubricating structure for a power transmission device, characterized in that it is configured to discharge oil from a discharge portion. In the lubricating structure of the power transmission device according to claim 1,
Each of the first gear and the second gear is formed with a tooth portion having a predetermined twist angle with respect to the axial direction.
Adjacent to the side of the tooth portion positioned in the rotational direction delay side in the axial direction of the second gear, it is provided to rotate integrally with the second gear, and has an outer diameter larger than the outer diameter of the tooth portion. A flange-shaped member having a diameter;
The flange-shaped member is configured to scatter oil supplied to the second gear through the meshing portion and attached to the flange-shaped member to the outside in the radial direction of the flange-shaped member by rotation of the flange-shaped member. Configured,
The lubricating structure for a power transmission device, wherein the oil collecting member is configured to collect oil scattered from the flange-shaped member. In the lubricating structure of the power transmission device according to claim 2,
The lubrication structure for a power transmission device, wherein the first discharge portion is disposed closer to the flange-like member than the second discharge portion in the axial direction of the first gear. In the lubricating structure of the power transmission device according to claim 2,
The lubrication structure for a power transmission device, wherein the first discharge portion is disposed on a side farther from the flange-like member than the second discharge portion in the axial direction of the first gear.