JP2011163365A - Lubricating oil supply device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a lubricating oil supply device capable of enhancing capability of sending lubricating oil to an oil receiving portion. <P>SOLUTION: The lubricating oil supply device 1-1 is installed in a power transmission device 1 for a vehicle in which the lubricating oil is supplied from an oil receiving portion 8 to a lubricated portion. The lubricating oil supply device includes: a pair of gears 5 and 7 disposed on the lower side of the oil receiving portion in the vertical direction and mutually engaged to receive the lubricating oil; and a guiding passage 17 communicating with an engaged part 40 of a pair of the gears. The guiding passage is connected to a side drawn into a tooth formed on the engaged portion of a pair of the gears. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  The present invention relates to a lubricating oil supply apparatus.

  2. Description of the Related Art Conventionally, in a power transmission device in which lubricating oil is supplied from an oil receiving portion to a lubricated portion, a technique for sending the lubricating oil to an oil receiving portion on the upper side in the vertical direction by rotation of a gear is known. For example, in Patent Document 1, in an oil supply device that supplies oil scooped up by a rotating member to an oil receiving portion, the moving direction of the scooped up oil is branched in different directions depending on the rotation speed of the rotating member. A technique including a branching mechanism is disclosed.

JP 2003-336729 A

  However, when the lubricating oil is sent upward by the rotation of the rotating member, the lubricating oil may not reach the oil receiving portion at a low vehicle speed or when the height from the rotating member to the oil receiving portion is large. On the other hand, when trying to cope with the addition or strengthening of the oil pump, there are problems such as an increase in cost and an increase in drag torque.

  An object of the present invention is to provide a lubricating oil supply device capable of improving the ability to send lubricating oil to an oil receiving portion.

  The lubricating oil supply device of the present invention is provided in a power transmission device of a vehicle in which lubricating oil is supplied from an oil receiving portion to a lubricated portion, and is a lubricating oil supplying device that supplies lubricating oil to the oil receiving portion, A pair of gears arranged below the oil receiving portion in the vertical direction and meshing with each other, receiving supply of lubricating oil, a guide passage communicating the meshing portion of the pair of gears and the oil receiving portion; The guide passage is connected to a side into which teeth formed on the pair of gears in the meshing portion are drawn.

  In the lubricating oil supply apparatus, it is preferable that the guide passage is opposed to a side of the meshing portion where the teeth are drawn in a direction parallel to a tangent line of the pair of gears in the meshing portion.

  The lubricating oil supply device includes a pair of wall portions facing each other in the axial direction with the meshing portion interposed therebetween, and the wall portion is connected to a member constituting the guide passage, and the pair of wall portions It is preferable that the space part between is continuous with the guide passage.

  In the lubricating oil supply device, it is preferable that the lubricating oil is supplied to the meshing portion by one of the pair of gears sending out the lubricating oil stored in the power transmission device by rotation.

  In the lubricating oil supply device, the gear that sends out the stored lubricating oil by rotation is a ring gear of a differential mechanism that is arranged coaxially with the driving wheel of the vehicle and connected to the driving wheel. preferable.

  Unlike the pair of gears, the lubricating oil supply device includes a third gear disposed vertically below the pair of gears, and the third gear is stored in the power transmission device. It is preferable to supply the lubricating oil to the pair of gears by sending out the lubricating oil by rotation.

  The lubricating oil supply apparatus includes a passage member that guides the lubricating oil sent by the third gear to the pair of gears, and the passage member extends along the circumferential direction of the third gear. And a first component that forms a first passage into which the lubricating oil sent by the third gear flows between the third gear and the lubricating oil in the first passage. A second component that forms a second passage that leads to the pair of gears, and the second passage is in a flow direction of the lubricating oil along a rotation direction of the third gear in the first passage. The lubricating oil supply device is further connected to the first passage on the upstream side in the flow direction from the outlet formed on the downstream side, and the lubricating oil supply device further includes the lubricating oil in the first passage and the second passage. A restraining structure that suppresses the flow from the connecting portion toward the outlet. It is preferable to obtain.

  In the lubricating oil supply apparatus, it is preferable that, on the tangent line of the pair of gears in the meshing portion, the side where the teeth are drawn from the meshing portion is directed upward in the vertical direction as the meshing portion is separated. .

  The lubricating oil supply apparatus according to the present invention includes a pair of gears that are meshed with each other and that are supplied with the lubricating oil, and a guide passage that communicates the meshing part of the pair of gears with the oil receiving part. Further, the guide passage is connected to the side where the teeth formed in the pair of gears in the meshing portion are drawn. Thereby, according to the lubricating oil supply device of the present invention, it is possible to improve the ability to send the lubricating oil to the oil receiving portion by sending the lubricating oil pushed out by the meshing of the pair of gears to the oil receiving portion. There is an effect.

FIG. 1 is a front view showing the power transmission device according to the first embodiment. FIG. 2 is a side view showing the power transmission device according to the first embodiment. FIG. 3 is a perspective view showing the guide member according to the first embodiment. FIG. 4 is a diagram illustrating a meshing portion of a pair of gears. FIG. 5 is a front view showing a power transmission device according to a first modification of the first embodiment. FIG. 6 is a front view showing a power transmission device according to a second modification of the first embodiment. FIG. 7 is a front view showing a power transmission device according to a third modification of the first embodiment. FIG. 8 is a front view showing the power transmission device according to the second embodiment. FIG. 9 is a front view showing a power transmission device according to the third embodiment. FIG. 10 is a diagram illustrating an example of a lubricating oil supply apparatus based on the combination of the embodiments.

  Hereinafter, an embodiment of a lubricating oil supply apparatus according to the present invention will be described in detail with reference to the drawings. In addition, this invention is not limited by this embodiment. In addition, constituent elements in the following embodiments include those that can be easily assumed by those skilled in the art or those that are substantially the same.

(First embodiment)
The first embodiment will be described with reference to FIGS. 1 to 4. The present embodiment relates to a lubricating oil supply device that is provided in a power transmission device of a vehicle in which lubricating oil is supplied from an oil receiving portion to a lubricated portion and supplies the lubricating oil to the oil receiving portion. FIG. 1 is a front view showing a power transmission device according to the first embodiment of the present invention, FIG. 2 is a side view (viewed at A) showing the power transmission device according to the first embodiment, and FIG. FIG. 4 is a perspective view showing a guide member according to the embodiment, and FIG. 4 is a view showing meshing portions of a pair of gears.

  The lubricating oil supply device according to the present embodiment supplies lubricating oil to the oil receiving portion, and includes a duct-like case (guide member described later) in the diff ring gear (final ring gear) and the drive pinion gear 5. Thus, the lubricating oil pressure pushed out by the meshing of the gear induces the lubricating oil to a location that could not be reached by the conventional differential scraping structure. Thereby, cost reduction of an oil pump and reduction of drag torque are achieved.

  In FIG. 1, the code | symbol 1 shows the power transmission device of a hybrid vehicle (not shown). Reference numeral 1-1 denotes the lubricating oil supply device of the present embodiment. The power transmission device 1 has a case 2. In the case 2, a counter drive gear 3, a counter driven gear 4, a drive pinion gear 5, an MG2 reduction gear 6, a diff ring gear 7, an oil receiving portion 8, a storage portion 9, and a guide member 10 are provided. The counter drive gear 3 is disposed on the front side in the vehicle front-rear direction with respect to the counter driven gear 4, and the MG2 reduction gear 6 and the diff ring gear 7 are disposed on the rear side in the vehicle front-rear direction with respect to the counter driven gear 4.

  The counter drive gear 3 is connected to the output shaft of the engine (not shown) and the rotation shaft of the first motor generator (MG1) via a planetary gear mechanism, and the engine output is divided into the counter drive gear 3 and the MG1. Is input. The counter driven gear 4 and the drive pinion gear 5 are arranged on the same axis and rotate integrally. The counter driven gear 4 meshes with the counter drive gear 3. As shown in FIG. 2, the MG2 reduction gear 6 is connected to the rotating shaft 22 of the rotor 21 of the second motor generator (MG2) 20 and rotates integrally with the rotor 21. As shown in FIG. 1, the MG2 reduction gear 6 meshes with the counter driven gear 4. The MG2 reduction gear 6 has a smaller diameter than the counter driven gear 4, and the output of the MG2 (20) is amplified and transmitted from the MG2 reduction gear 6 to the counter driven gear 4.

  The drive pinion gear 5 meshes with the diff ring gear 7, and the engine output torque and the output torque of the MG 2 (20) input to the counter driven gear 4 are transmitted to the def ring gear 7 via the drive pinion gear 5. The In FIG. 2, the code | symbol 23 is arrange | positioned coaxially with the drive wheel of the vehicle which is not shown in figure, and shows the differential mechanism connected with the drive wheel. The differential ring gear 7 is a ring gear of the differential mechanism 23 and rotates in conjunction with the rotation of the drive wheel. An arrow Y1 in FIG. 1 indicates the rotation direction of the diff ring gear 7 when the vehicle moves forward. The MG2 reduction gear 6 is disposed above the diff ring gear 7 in the vertical direction.

  A storage portion 9 for storing lubricating oil (for example, ATF) is formed in the lower portion of the case 2 in the vertical direction. The diff ring gear 7 is disposed in the lower part of the case 2, and when the lubricating oil is stored in the storage portion 9, a part of the def ring gear 7 is immersed in the stored lubricating oil. An oil receiving portion 8 is provided in the case 2 on the upper side in the vertical direction from the diff ring gear 7. The oil receiving portion 8 is configured to be able to store lubricating oil, and the lubricating oil in the oil receiving portion 8 is supplied to the lubricated portion of the power transmission device 1. The oil receiving portion 8 is partitioned from the lower space in the case 2 by ribs 8 a protruding from the inner wall surface of the case 2. The lubricating oil in the oil receiving portion 8 is supplied to the MG2 (20) via the supply hole 8b and to the MG1 via the supply hole 8c, and lubricates and cools MG1 and MG2 (20). The lubricating oil in the oil receiving portion 8 may be supplied to other lubricated portions of the power transmission device 1.

The diff ring gear 7 rotates in conjunction with the rotation of the drive wheel and sends out the lubricating oil in the reservoir 9. Conventionally, a technique is known in which a rotating member such as a diff ring gear 7 is used to lift up the lubricating oil in a reservoir to a supply destination such as an oil receiving portion in the upper part of the vertical direction. In such a situation, there is a problem that the lubricant does not reach the supplier or a sufficient amount is not supplied.
(A) At low vehicle speed (because the rotation speed of the diff ring gear is small).
(B) The supply destination is high as viewed from the differential shaft (because the momentum of the lubricating oil is insufficient with respect to the height).
(C) The supply destination is behind the vehicle relative to the diff ring gear (because it is difficult to direct the direction of the lubricant to protrude).
(D) When the vehicle is going up a hill (because the lubricating oil around the diff ring gear is increased and the momentum of the lubricating oil popping out is lost).

  The lubricating oil supply apparatus 1-1 of the present embodiment includes a guide passage 17 that communicates the meshing portion 40 between the diff ring gear 7 and the drive pinion gear 5 and the oil receiving portion 8. Lubricating oil pushed out from the tooth spaces of the diff ring gear 7 and the drive pinion gear 5 is guided to the oil receiving portion 8 by the guide passage 17 engaging the def ring gear 7 and the drive pinion gear 5. As a result, the lubricating oil can be supplied to the oil receiving portion 8 even at low vehicle speeds or when the oil receiving portion 8 is at a high position when viewed from the rotation shaft of the diffring gear 7. Moreover, the lubricating oil supply apparatus 1-1 has the side surface cover part 13 which is a pair of wall part which mutually opposes in an axial direction on both sides of the meshing part 40 of the diff ring gear 7 and the drive pinion gear 5. Thereby, the lubricating oil pushed out from the tooth groove in the meshing portion 40 is suppressed from flowing out to the side of the diff ring gear 7 and the drive pinion gear 5. Therefore, the lubricating oil pushed out from the tooth gap flows toward the guide passage 17 and is efficiently sent to the oil receiving portion 8 through the guide passage 17.

  In the present embodiment, the drive pinion gear 5 and the diffring gear 7 are arranged vertically below the oil receiving portion 8 and mesh with each other, thereby constituting a pair of gears that receive supply of lubricating oil. Further, the diff ring gear 7 supplies the lubricating oil to the meshing portion 40 by sending out the lubricating oil stored in the power transmission device 1 (storage portion 9) by rotation.

  The guide member 10 includes a cylindrical portion 11 that constitutes the guide passage 17, an outer peripheral surface cover portion 12 that covers the outer peripheral surfaces of the drive pinion gear 5 and the diff ring gear 7, and a side surface that covers the side surfaces of the drive pinion gear 5 and the diff ring gear 7. And a cover portion 13. The guide passage 17 is a passage that guides the lubricating oil pushed out from the tooth grooves of the drive pinion gear 5 and the diff ring gear 7 to the oil receiving portion 8 when the drive pinion gear 5 and the diff ring gear 7 are engaged with each other.

  Reference numeral L <b> 1 indicates an imaginary line segment that connects the central axis of the drive pinion gear 5 and the central axis of the diffring gear 7. The vehicle rear side of the imaginary line segment L1 is a side where the teeth of the drive pinion gear 5 and the diff ring gear 7 approach each other by rotation. The vehicle rear side of the imaginary line segment L1 is a side on which the teeth formed on the drive pinion gear 5 and the diff ring gear 7 are drawn toward the meshing portion 40 between the drive pinion gear 5 and the diff ring gear 7. . On the “side where the teeth are drawn”, the other teeth enter into one of the tooth grooves of the drive pinion gear 5 and the diff ring gear 7 in accordance with the rotation, and are brought into an engaged state.

  On the other hand, the front side of the vehicle from the imaginary line segment L1 is a side where the teeth of the drive pinion gear 5 and the diff ring gear 7 are separated from each other by rotation. The front side of the vehicle with respect to the imaginary line segment L1 is the side on which the teeth formed on each of the drive pinion gear 5 and the diff ring gear 7 are fed out from the meshing portion 40. On the “side where the teeth are fed”, the other teeth come out from one tooth groove of the drive pinion gear 5 and the diff ring gear 7 with the rotation, and the meshing state is canceled.

  The guide passage 17 is connected to the side where the teeth formed in the drive pinion gear 5 and the diff ring gear 7 in the meshing portion 40 are drawn. In other words, the guide passage 17 connects the oil receiving portion 8 and the gap 14 between the drive pinion gear 5 and the diff ring gear 7 on the vehicle rear side of the imaginary line segment L1. Here, the gap 14 is a space between the outer peripheral surface of the drive pinion gear 5 and the outer peripheral surface of the diff ring gear 7. The cylindrical portion 11 has a chimney shape (cylindrical shape) having a rectangular cross section in which the guide passage 17 is formed. The cylindrical part 11 has a vertical lower end opened in the gap 14 and an upper end opened in the inflow port 81 of the oil receiving part 8. A portion of the tubular portion 11 on the side of the meshing portion 40 extends from the meshing portion 40 toward the rear of the vehicle. That is, the guide passage 17 faces the side in which the teeth in the meshing portion 40 are drawn in a direction parallel to the tangent line T of the drive pinion gear 5 and the diffring gear 7 in the meshing portion 40.

  The outer peripheral surface cover portion 12 is formed along the outer peripheral surfaces of the drive pinion gear 5 and the diff ring gear 7, and faces the outer peripheral surfaces in the radial direction with a gap. A differential outer peripheral surface cover portion 12 a formed along the outer peripheral surface of the differential ring gear 7 extends from the vicinity of the lower end in the vertical direction of the differential ring gear 7 to the gap 14. A passage 15 is formed. A pinion outer peripheral surface cover portion 12 b formed along the outer peripheral surface of the drive pinion gear 5 extends from the gap 14 to the vicinity of the upper end in the vertical direction of the drive pinion gear 5. A lubricating oil passage 16 is formed. The outer peripheral surface cover portion 12 prevents the lubricating oil adhering to the drive pinion gear 5 and the diff ring gear 7 from being scattered.

  The side cover portion 13 is a plate-shaped component formed along the side surfaces of the drive pinion gear 5 and the diff ring gear 7. The side cover portions 13 are arranged on both sides in the axial direction with the drive pinion gear 5 and the diffring gear 7 interposed therebetween, and face each other in the axial direction. The side cover portion 13 protrudes radially inward from the outer peripheral surface cover portion 12, and the side surface cover portions 13 disposed on both sides in the axial direction are connected to each other by the outer peripheral surface cover portion 12. The side cover part 13 prevents the lubricating oil rotating together with the diff ring gear 7 from escaping in the axial direction, and a large amount of lubricating oil is supplied to the meshing part 40.

  The side cover portion 13 is a pair of wall portions facing each other in the axial direction across the meshing portion 40 of the drive pinion gear 5 and the diffring gear 7, and has side wall surfaces sandwiching the meshing portion 40. . The side cover portion 13 is connected to the cylindrical portion 11 that is a member constituting the guide passage 17. As shown in FIG. 3, the wall surfaces 13 a that face each other in the axial direction in the side cover portion 13 have side wall surfaces 13 b that correspond to the meshing portions 40. The side wall surface 13b is disposed with the meshing portion 40 interposed therebetween, and faces the side surfaces of the drive pinion gear 5 and the diff ring gear 7 with a slight gap therebetween. As shown in FIG. 3, the space portion 13 c between the side cover portions 13 and 13 is continuous with the guide passage 17. As will be described below with reference to FIG. 4, the side wall surface 13 b suppresses the lubricating oil pushed out due to the engagement between the drive pinion gear 5 and the diffring gear 7 from being released sideways.

  In FIG. 4, reference numeral 5 d indicates a tooth groove between the teeth 5 t and the teeth 5 t of the drive pinion gear 5, and reference numeral 7 d indicates a tooth groove between the teeth 7 t and the teeth 7 t of the diffring gear 7. When the drive pinion gear 5 and the diff ring gear 7 rotate, the tooth grooves 5d and 7d are filled with lubricating oil. When the drive pinion gear 5 and the diff ring gear 7 mesh with each other at the meshing portion 40, the teeth 7 t of the diff ring gear 7 enter the tooth groove 5 d of the drive pinion gear 5, and the drive pinion gear enters the tooth groove 7 d of the diff ring gear 7. 5 teeth 5t enter. Thereby, the lubricating oil in the tooth spaces 5d and 7d loses its place and is pushed out from the tooth spaces 5d and 7d. The extruded lubricating oil not only flows from the tooth grooves 5d and 7d toward the gap 14 as indicated by the arrow Y2, but also tends to flow laterally from the tooth grooves 5d and 7d.

  However, in the lubricating oil supply apparatus 1-1 of the present embodiment, the side cover 13 is provided with the side wall surface 13 b (see FIG. 3), and in the meshing portion 40 from the tooth grooves 5 d and 7 d to the side (axial direction). ) Is prevented from being pushed out. As a result, the lubricating oil pushed out from the tooth grooves 5 d and 7 d flows toward the gap 14 and flows into the guide passage 17. Lubricating oil is continuously supplied to the meshing portion 40 by the drive pinion gear 5 and the diff ring gear 7, and the lubricating oil is pushed out from the tooth grooves 5 d and 7 d, whereby the hydraulic pressure in the gap 14 increases. Therefore, the lubricating oil flows into the guide passage 17 from the gap 14 due to the pressure, is pushed up toward the oil receiving portion 8, and is supplied to the oil receiving portion 8.

  Thus, in the lubricating oil supply apparatus 1-1 of this embodiment, it meshes with the pressure of the lubricating oil pushed out from the tooth grooves 5d and 7d by meshing of the drive pinion gear 5 and the diff ring gear 7 in the meshing portion 40. Lubricating oil is supplied from the portion 40 to the oil receiving portion 8 through the guide passage 17. Since the lubricating oil is pushed up the induction passage 17 by the pressure, the lubricating oil can be supplied to the oil receiving portion 8 even at the low vehicle speed when the rotational speed of the diff ring gear 7 is low. That is, as compared with the conventional method in which the lubricating oil is sent to the oil receiving portion 8 by the rotational force of the diff ring gear 7, the lubricating oil can be supplied to the oil receiving portion 8 from a low vehicle speed. 1 ability can be improved.

  Further, since the outer peripheral surface cover portion 12 and the side surface cover portion 13 are provided, it is possible to prevent the lubricating oil attached to the drive pinion gear 5 and the diff ring gear 7 from being scattered before reaching the meshing portion 40. As a result, a large amount of lubricating oil concentrates on the meshing portion 40. Thereby, the oil pressure in the gap 14 is easily increased, so that the lubricating oil is sent to the oil receiving portion 8 from a lower vehicle speed stage.

  Further, on the tangent line T between the drive pinion gear 5 and the diff ring gear 7 in the meshing portion 40, the side (vehicle rear side) T <b> 1 where the teeth are drawn from the meshing portion 40 is the upper side in the vertical direction as the meshing portion 40 is separated. Head for. In other words, the tangent line T goes upward in the vertical direction as it goes in the direction in which the tooth surface behind the rotation direction in the meshing portion 40 faces. As a result, the gap 14 (the side where the teeth in the meshing portion 40 are drawn) is filled with the lubricating oil, and the oil pressure in the gap 14 is increased by the engagement of the drive pinion gear 5 and the diffring gear 7 to send out the lubricating oil. Efficiency can be improved.

  In the guide member 10 of the present embodiment, the side cover portion 13 may be omitted. Even in such a configuration, if the outer peripheral surface cover portion 12 is provided and lubricating oil can be accumulated between the outer peripheral surface cover portion 12 and the outer peripheral surfaces of the drive pinion gear 5 and the diff ring gear 7, a large amount of lubrication is achieved. It is possible to send oil to the meshing part 40.

  The power transmission device 1 of the present embodiment is a power transmission device for a hybrid vehicle, but is not limited to this. The lubricating oil supply device 1-1 may be applied to a power transmission device mounted on a vehicle other than the hybrid vehicle, for example, a power transmission device of an MT (manual transmission). Moreover, the lubricating oil supply apparatus 1-1 may be applied to power transmission apparatuses other than a vehicle.

(First modification of the first embodiment)
A first modification of the first embodiment will be described. FIG. 5 is a front view showing a power transmission device according to this modification. The difference between the lubricating oil supply device 1-11 of the present modification and the lubricating oil supply device 1-1 of the first embodiment is that when the rotation of the diff ring gear 7 is at a high speed, the oil receiving device is received via the guide passage 17. Not only the lubricating oil is sent to the portion 8, but also the lubricating oil is sent to the oil receiving portion 8 without passing through the guide passage 17 due to the rotational force of the diffring gear 7. Accordingly, an excessive amount of lubricating oil supplied to the gap 14 at high vehicle speed is suppressed, and drag loss is reduced, so that transmission efficiency of the power transmission device 1 is improved.

  As shown in FIG. 5, the differential outer peripheral surface cover portion 12 a of this modified example covers only the upper part of the outer peripheral surface of the differential ring gear 7 in the vertical direction. As a result, when the rotational speed of the diffring gear 7 is high, as shown by an arrow Y3, the lubricating oil separated from the defling gear 7 due to the rotational momentum is between the guide member 10 and the inner peripheral surface 2a of the case 2. To reach the oil receiver 8. In other words, the drive pinion gear 5 and the diff ring gear 7 are pushed out by meshing with each other and not only the lubricating oil is supplied to the oil receiving portion 8 through the gap 14 and the guide passage 17 but also guided by the rotational force of the diff ring gear 7. Lubricating oil is supplied to the oil receiving portion 8 without passing through the passage 17. Thus, by supplying the lubricating oil through two different paths, a sufficient amount of lubricating oil is supplied to the oil receiving portion 8 even at high vehicle speeds. Further, as the rotational speed of the diff ring gear 7 increases, the amount of lubricating oil that separates from the def ring gear 7 increases due to the momentum of rotation. As a result, an excessive amount of lubricating oil sent to the meshing portion 40 by the diff ring gear 7 at high vehicle speed is suppressed, and drag loss is reduced.

  In addition, the installation range of the differential outer peripheral surface cover part 12a can be determined based on, for example, the relationship between the rotational speed of the differential ring gear 7 and the state of the flow of the lubricating oil leaving the differential ring gear 7 by the rotation. The state of the lubricating oil flow may be a position where the lubricating oil is separated from the differential ring gear 7, an amount of the lubricating oil that is separated, a direction in which the separated lubricating oil is scattered, or the like. For example, when the rotational momentum of the diff ring gear 7 becomes sufficiently large and the lubricating oil can be sent to the oil receiving portion 8 with the rotational momentum, the outer circumference of the differential ring so as not to hinder the flow of the lubricating oil away from the diff ring gear 7. What is necessary is just to set the installation range of the surface cover part 12a.

  Note that the shape of the guide member 10 that allows the lubricating oil to fly toward the oil receiving portion 8 by the rotational momentum of the diff ring gear 7 at a high vehicle speed is not limited to that shown in FIG. For example, by providing a cutout portion or a through hole in the outer peripheral surface cover portion 12 or the side surface cover portion 13, the lubricating oil leaving the defring gear 7 may fly toward the oil receiving portion 8.

(Second modification of the first embodiment)
A second modification of the first embodiment will be described. FIG. 6 is a front view showing a power transmission device according to this modification. The lubricating oil supply device 1-12 of this modification is different from the lubricating oil supply device 1-1 of the first embodiment in that an opening / closing valve 18 is provided on the guide member 10. The on-off valve 18 is provided in the differential outer peripheral surface cover portion 12a and communicates or blocks between the passage 15 and the outside. The on-off valve 18 opens and closes according to the pressure in the passage 15 and closes when the pressure in the passage 15 is low, and opens when the pressure in the passage 15 is high. As a result, at the low vehicle speed, the on-off valve 18 is closed and the lubricating oil in the passage 15 is suppressed from flowing out, and the lubricating oil is efficiently sent to the meshing portion 40 by the diff ring gear 7. On the other hand, the open / close valve 18 is opened at high vehicle speed, and the lubricating oil in the passage 15 can flow out to the outside and flow toward the oil receiving portion 8.

(Third Modification of First Embodiment)
A third modification of the first embodiment will be described. FIG. 7 is a front view showing a power transmission device according to this modification. The difference between the lubricating oil supply device 1-13 of this modification and the lubricating oil supply device 1-1 of the first embodiment is that the guide member 10 does not have the outer peripheral surface cover portion 12. Thereby, the guide member 10 can be made compact.

  As shown in FIG. 7, the guide member 10 includes a cylindrical part 11 and a side cover part 13. As in the first embodiment, the side cover 13 is disposed on both sides in the axial direction with the drive pinion gear 5 and the diffring gear 7 interposed therebetween, and faces each other in the axial direction. The side cover portion 13 of this modification is disposed only in the vicinity of the meshing portion 40 including the meshing portion 40 of the drive pinion gear 5 and the diffring gear 7. In other words, the installation range of the side cover portion 13 is a range that is required for suppressing the lubricating oil from flowing out from the meshing portion 40 in the axial direction.

  Even if the outer peripheral surface cover portion 12 is not provided, when the rotational speed of the diff ring gear 7 is low, the lubricating oil is sent to the meshing portion 40 while being held between the teeth of the def ring gear 7. . Therefore, the lubricating oil pushed out by the meshing of the drive pinion gear 5 and the diffring gear 7 in the meshing portion 40 is supplied to the oil receiving portion 8 through the guide passage 17. When the rotational speed of the diff ring gear 7 is high, the lubricating oil leaving the def ring gear 7 passes through the space outside the guide passage 17 and is an oil receiving portion as in the first modification of the first embodiment. 8 (see arrow Y3 in FIG. 5). The gap between the outer peripheral surface of the drive pinion gear 5 and the diff ring gear 7 and the cylindrical portion 11 is as much as possible so that the lubricating oil pushed out in the meshing portion 40 can be prevented from leaking outside from the gap 14. It is desirable to make it smaller.

(Second Embodiment)
The second embodiment will be described with reference to FIG. In the second embodiment, members having the same functions as those described in the above embodiment are denoted by the same reference numerals, and redundant description is omitted. FIG. 8 is a front view showing the power transmission device according to the second embodiment.

  In the lubricating oil supply device 1-2 of the second embodiment, the lubricating oil pushed out by meshing between the counter driven gear 4 and the MG2 reduction gear 6 is supplied to the oil receiving portion 8. When the lubricating oil is sent upward in the vertical direction by the momentum generated by the rotation of the diffring gear 7, the momentum is not sufficient at a low vehicle speed, and the lubricating oil may not reach the oil receiving portion 8. For example, when the MG2 (20) is enlarged and the difference in height between the diffring gear 7 and the MG2 reduction gear 6 is increased, the inlet 81 of the oil receiving portion 8 is provided at a high position corresponding to this, and the low vehicle speed is reduced. Sometimes the lubricating oil cannot reach the oil receiver 8.

  According to the lubricating oil supply device 1-2 of the present embodiment, even if the lubricating oil does not reach the oil receiving portion 8 at a low vehicle speed, if the lubricating oil reaches the MG2 reduction gear 6, the oil receiving portion 8 Can be supplied with lubricating oil. Therefore, it is possible to improve the ability to send the lubricating oil to the oil receiving portion 8 in the lubricating oil supply device 1-2.

  The guide member 30 includes a cylindrical portion 31 constituting the guide passage 37, an outer peripheral surface cover portion 32 that covers the outer peripheral surfaces of the counter driven gear 4 and the MG2 reduction gear 6, and side surfaces of the counter driven gear 4 and the MG2 reduction gear 6. And a side cover portion 33 for covering. The guide passage 37 guides the lubricating oil pushed out when the counter driven gear 4 and the MG2 reduction gear 6 mesh with each other to the oil receiving portion 8.

  Reference numeral L <b> 2 indicates a virtual line segment that connects the central axis of the counter driven gear 4 and the central axis of the MG <b> 2 reduction gear 6. The upper side in the vertical direction from the imaginary line segment L2 is the side where the teeth formed on the counter driven gear 4 and the MG2 reduction gear 6 are drawn into the meshing portion 41 (the teeth of the counter driven gear 4 and the MG2 reduction gear 6 are rotated by rotation). (The sides that are close to each other). The guide passage 37 connects the oil receiving portion 8 and the gap 24 between the counter driven gear 4 and the MG2 reduction gear 6 on the upper side in the vertical direction with respect to the virtual line segment L2. The gap 24 is a space between the outer peripheral surface of the counter driven gear 4 and the outer peripheral surface of the MG2 reduction gear 6. That is, the guide passage 37 is connected to the side where the teeth of the counter driven gear 4 and the MG2 reduction gear 6 in the meshing portion 41 are drawn. The cylindrical portion 31 constituting the guide passage 37 has a chimney shape (cylindrical shape) with a rectangular cross section.

  The inlet 81 of the oil receiver 8 is formed at the rear end of the oil receiver 8 in the vehicle front-rear direction, and is located on the vehicle rear side of the MG2 reduction gear 6. A second inflow port 82 is formed in the rib 8 a that forms the oil receiving portion 8. The second inflow port 82 is disposed on the vehicle front side with respect to the inflow port 81, and is formed at a position facing the meshing portion 41 of the counter driven gear 4 and the MG2 reduction gear 6 in the rib 8a in the vertical direction. Yes. The central axis of the MG2 reduction gear 6 is located above the central axis of the counter driven gear 4 in the vertical direction. Correspondingly, the guide passage 37 has an inclination toward the vehicle front side toward the upper side in the vertical direction, and the opening portion on the upper side in the vertical direction in the cylindrical portion 31 faces the vehicle front side. . The second inlet 82 faces the opening on the upper side in the vertical direction of the cylindrical portion 31, and the lubricating oil flowing out from the guide passage 37 flows into the oil receiving portion 8 through the second inlet 82.

  The side surface cover portion 33 is a plate-shaped component formed along the side surfaces of the counter driven gear 4 and the MG2 reduction gear 6. The side cover portions 33 are disposed on both sides in the axial direction with the counter drive gear 4 and the MG2 reduction gear 6 interposed therebetween, and face each other in the axial direction. The pair of side surface cover portions 33, 33 project radially inward from the outer peripheral surface cover portion 32 and are connected to each other by the outer peripheral surface cover portion 32. Further, the side surface cover portion 33 is formed continuously with the cylindrical portion 31, and the space portion between the pair of side surface cover portions 33, 33 is continuous with the guide passage 37.

  The side cover portions 33 and 33 are a pair of wall portions facing each other in the axial direction with the meshing portion 41 between the counter driven gear 4 and the MG2 reduction gear 6 interposed therebetween. In the side surface cover portion 33, the side wall surfaces 33 b facing each other are opposed to the side surfaces of the counter driven gear 4 and the MG2 reduction gear 6 with a slight gap. By providing the side wall surface 33 b, it is possible to prevent the lubricating oil pushed out by the meshing of the counter driven gear 4 and the MG2 reduction gear 6 in the meshing portion 41 from being removed in the axial direction, and the lubricating oil is directed toward the gap 24. Pushed out. The lubricating oil pushed into the gap 24 is sent to the oil receiving portion 8 via the guide passage 37 by hydraulic pressure.

  Lubricating oil is supplied to the counter driven gear 4 and the MG2 reduction gear 6 which are a pair of gears engaged with each other by a diff ring gear 7 as a third gear. The diff ring gear 7 is arranged below the counter driven gear 4 and the MG2 reduction gear 6 in the vertical direction, and supplies the lubricant to the MG2 reduction gear 6 by sending out the lubricant stored in the storage portion 9 by rotation. To do. Even at low vehicle speeds where the lubricating oil that is blown off by the rotation of the diff ring gear 7 does not reach the oil receiving portion 8, if the lubricating oil reaches the MG 2 reduction gear 6, the lubricating oil is engaged by the MG 2 reduction gear 6. The lubricating oil is supplied to the oil receiving portion 8 through the guide passage 37. Further, at high vehicle speed, the lubricating oil sent by the rotational momentum of the diff ring gear 7 flows into the oil receiving portion 8 through the inflow port 81. Therefore, according to the lubricating oil supply apparatus 1-2 of this embodiment, the capability to send lubricating oil to an oil receiving part can be improved.

  Note that the counter driven gear 4 is supplied with lubricating oil not only through the path to the MG2 reduction gear 6 by the diff ring gear 7 but also through other paths. For example, the lubricating oil is supplied to the counter driven gear 4 through a path that moves from the diff ring gear 7 to the drive pinion gear 5 due to meshing between the def ring gear 7 and the drive pinion gear 5, or a path that jumps from the def ring gear 7 to the counter driven gear 4. The Therefore, even when the vehicle speed is low, a large amount of lubricating oil is sent to the meshing portion 41 and supplied to the oil receiving portion 8 through the guide passage 37.

(Third embodiment)
A third embodiment will be described with reference to FIG. In the third embodiment, members having the same functions as those described in the above embodiment are denoted by the same reference numerals, and redundant description is omitted. FIG. 9 is a side view showing the power transmission device according to the present embodiment.

  The lubricating oil supply device 1-3 of the present embodiment differs from the lubricating oil supply device 1-2 of the second embodiment in that the lubricating oil is MG2 by the rotational force of the diff ring gear 7 and the pressure generated by the pump action. It is a point sent to the ring gear 6. Thereby, compared with the case where lubricating oil is sent only with the rotational force of the diffring gear 7, the capability of sending lubricating oil upward in the vertical direction can be improved. Further, by providing a passage for guiding the lubricating oil to the MG2 reduction gear 6, more lubricating oil can be supplied to the MG2 reduction gear 6. Similar to the second embodiment, the diff ring gear 7 supplies lubricating oil to the counter driven gear 4 and the MG2 reduction gear 6 as a third gear.

  As shown in FIG. 9, the lubricating oil supply device 1-3 includes a passage member 50 in addition to the guide member 30 similar to that of the second embodiment. The passage member 50 guides the lubricating oil sent by the diff ring gear 7 to the counter driven gear 4 and the MG2 reduction gear 6, and has a first component 51 and a second component 52. The first component 51 is provided to face the diffring gear 7 along the circumferential direction of the diffring gear 7, and is a first passage that is a passage through which lubricating oil sent by the defling gear 7 flows between the first component 51. 53 is formed. The first component 51 is formed in a shape corresponding to the outer peripheral surface 7a and a pair of side wall portions 51a opposed to each other with the diffring gear 7 in the axial direction and the outer peripheral surface 7a of the diffring gear 7 in the radial direction. And a curved surface portion 51b. The radially outer ends of the side wall portions 51a and 51a are connected to each other by a curved surface portion 51b. That is, the first component 51 faces the both side surfaces and the outer peripheral surface 7a of the diff ring gear 7, respectively.

  The installation area of the first component 51 in the circumferential direction of the diff ring gear 7 is an area slightly smaller than the half circumference of the diff ring gear 7 and the tooth surface in the rotational direction of the diff ring gear 7 faces upward in the vertical direction. It is an area. In other words, the circumferential range in which the first passage 53 is formed with respect to the diff ring gear 7 corresponds to the range in which the lubricating oil is sent upward in the vertical direction by the rotation of the diff ring gear 7. As a result, the lubricating oil inlet 53 a in the first passage 53 is positioned at the lower end in the vertical direction of the first passage 53, and is formed on the downstream side in the lubricating oil flow direction along the rotational direction of the diffring gear 7. The outlet 53 b is located at the upper end in the vertical direction of the first passage 53. In the inflow port 53a, the outer peripheral surface of the curved surface portion 51b is in contact with the bottom surface of the case 2, and the lubricating oil sent by the rotation of the diff ring gear 7 flows into the first passage 53 from the inflow port 53a.

  The second component 52 is connected to the first passage 53 to form a second passage 54 that guides the lubricating oil in the first passage 53 to the oil receiving portion 8. The second passage 54 is connected to the first passage 53 on the upstream side of the outlet 53 b in the flow direction of the lubricating oil along the rotation direction of the diff ring gear 7 in the first passage 53. In the following description, the upstream side and the downstream side in the flow direction of the lubricating oil along the rotational direction (Y4) of the diff ring gear 7 in the first passage 53 are simply referred to as “upstream side of the first passage 53” and “first passage 53”. Called “downstream of”. An opening is formed in the curved surface 51b of the first component 51, and this opening is a connecting portion 53c between the first passage 53 and the second passage 54, and an inlet of the second passage 54. It has become. That is, the connection portion 53 c that is the inflow port of the second passage 54 faces the outer peripheral surface 7 a of the diffring gear 7 in the radial direction.

  The second component portion 52 is formed in a chimney shape (cylindrical shape) having a rectangular cross section in which the second passage 54 is formed, and extends in the vertical direction from the connection portion 53 c toward the oil receiving portion 8. Yes. Since the second component 52 is cylindrical and the other ends of the second passage 54 are closed, the movement direction of the lubricating oil in the second passage 54 is restricted only to the axial direction of the second component 52, and By suppressing the oil pressure from dropping, the force for guiding the lubricating oil upward increases. The cross-sectional area of the second passage 54 is larger than the cross-sectional area of the first passage 53. The lower end of the second passage 54 is connected to the first passage 53 at the connection portion 53 c, and the upper end opens toward the inlet 81 of the oil receiving portion 8. A guide passage 55 that guides the lubricating oil to the MG2 reduction gear 6 is provided at the upper end of the second component 52 in the vertical direction. The guide passage 55 connects the upper opening in the vertical direction of the second passage 54 and the lower portion of the MG2 reduction gear 6. The lubricating oil that flows out from the second passage 54 and is guided to the MG2 reduction gear 6 by the guide passage 55 adheres to the MG2 reduction gear 6 and is sent to the meshing portion 41. That is, the lubricating oil is guided to the counter driven gear 4 and the MG2 reduction gear 6 by the second passage 54.

  When the diff ring gear 7 rotates, the lubricating oil in the reservoir 9 is sent to the def ring gear 7 and flows into the first passage 53 from the inflow port 53a. The oil pressure in the first passage 53 is increased by continuously feeding the lubricating oil into the first passage 53 by the diff ring gear 7. As the hydraulic pressure in the first passage 53 rises, the lubricating oil in the first passage 53 rises toward the oil receiving portion 8 through the second passage 54. That is, the diff ring gear 7 and the passage member 50 function as a pump that increases the hydraulic pressure of the lubricating oil and sends the lubricating oil upward.

  The lubricating oil flowing in the first passage 53 along the rotation direction of the diffring gear 7 due to the hydraulic pressure and the rotation of the diffring gear 7 flows from the connection portion 53c to the second passage 54 toward the outlet 53b and the second passage 54, respectively. Although it is going to flow, the lubricating oil supply apparatus 1-3 of this embodiment is provided with the suppression structure which suppresses that a lubricating oil flows in the 1st channel | path 53 toward the outflow port 53b from the connection part 53c. In this suppression structure, the second passage 54 extends radially outward from the connection portion 53c, and lubricating oil that receives centrifugal force easily flows toward the second passage 54. 54, the oil receiving portion 8 side is located on the downstream side of the first passage 53 relative to the connection portion 53c side, and the lubricating oil easily flows from the first passage 53 to the second passage 54 along the tangential direction. That is, the flow passage cross-sectional area of the two passages 54 is larger than the flow passage cross-sectional area of the first passage 53, and the outlet 53b is positioned above the connecting portion 53c in the vertical direction. The suppression structure of the present embodiment is configured to include the passage member 50 and the diff ring gear 7.

As a restraining structure, the gap between the diff ring gear 7 and the first component 51 on the downstream side in the flow direction with respect to the connection portion 53c is such that the diff ring gear 7 and the first component portion on the upstream side in the flow direction with respect to the connection portion 53c. It is preferable that it is smaller than the gap with 51.
Moreover, it is preferable that a stepped portion extending in a direction in which the lubricating oil flowing along the wall surface is guided to the connecting portion 53c is provided on the wall surface facing the diff ring gear 7 in the side wall portion 51a.
In addition, as a restraining structure, an oil passage may be provided that guides the lubricating oil pushed out from the tooth groove to the outflow port 53b when the pair of gears mesh with each other.

  As described above, the connection portion 53c is formed at a position facing the outer peripheral surface of the diffring gear 7, and the second passage 54 extends radially outward from the connection portion 53c. The lubricating oil fed into the second passage 54 by the momentum of the rotation of the gear 7 can move upward in the second passage 54 by the momentum. As described above, in the lubricating oil supply apparatus 1-3 according to the present embodiment, the lubricating oil is not only utilized by the energy (momentum) due to the rotational force of the diff ring gear 7 but also by the pump effect of the def ring gear 7 and the passage member 50. It is sent upward in the case 2. In addition, the lubricating oil is prevented from flowing from the connection portion 53c toward the outlet 53b, and the flow of the lubricating oil toward the second passage 54 is promoted, so that the inside of the case 2 is interposed via the second passage 54. Lubricant is sent to the top of Therefore, the lubricating oil is efficiently supplied to the MG2 reduction gear 6 at a low vehicle speed. Further, at high vehicle speed, the momentum of the lubricating oil sent to the second passage 54 by the diff ring gear 7 is increased, so that the momentum of the lubricating oil flowing out from the second passage 54 upward in the vertical direction is increased. For this reason, the lubricating oil jumping out from the second passage 54 can flow directly into the oil receiving portion 8.

When the second component 52 is cylindrical and the connecting portion 53c is formed at a position facing the outer peripheral surface of the diffring gear 7, it has at least one of the following configurations (1) to (4). By doing so, it is possible to suppress the occurrence of a vortex that changes the direction of the lubricating oil flow toward the oil receiving portion 8 in the second passage 54 to the flow toward the connection portion 53c.
(1) The width of the second passage 54 in the axial direction of the diff ring gear 7 approximates the width of the outer peripheral surface of the diff ring gear 7.
(2) When the diffring gear 7 is a helical gear, the second passage 54 has a tooth surface on the front side in the rotational direction of the diffring gear 7 in the axial direction of the defling gear 7 from the connecting portion 53c toward the oil receiving portion 8. Inclined to the facing side.
(3) The second component 52 has inner wall surfaces facing each other in the axial direction of the diffring gear 7 across the second passage 54, and among the mutually facing inner wall surfaces, the teeth on the rear side in the rotational direction of the diffring gear 7 A protruding portion that protrudes toward the other inner wall surface is formed on the inner wall surface facing the surface.
(4) A rectifying member is disposed in the second passage 54.

Moreover, when the 2nd structure part 52 is cylindrical, it is preferable to have at least one structure of the following (5) or (6).
(5) In the second passage 54, the flow passage cross-sectional area on the oil receiving portion 8 side is smaller than the flow passage cross-sectional area on the connection portion 53c side.
(6) A structure in which the movement of the lubricating oil from the connection portion 53c side toward the oil receiving portion 8 side in the second passage 54 is allowed and the movement of the lubricating oil from the oil receiving portion 8 side toward the connection portion 53c side is suppressed. Prepare.

  The above embodiments can be combined as appropriate. FIG. 10 is a diagram illustrating an example of the lubricating oil supply device 1-4 based on the combination of the embodiments. For example, as shown in FIG. 10, the lubricating oil supply apparatus 1-4 includes a guide member 10 (see FIG. 5) according to a first modification of the first embodiment and a guide member 30 (see FIG. 5). You may make it have both of (refer FIG. 8). In this case, the oil receiving portion 8 has a second inflow port 82 similar to that in the second embodiment. At low vehicle speeds, the lubricating oil adhering to the diff ring gear 7 is sent to the meshing portion between the diff ring gear 7 and the drive pinion gear 5 and flows into the oil receiving portion 8 through the guide passage 17 (see arrow Y5). When the vehicle speed is high, the lubricating oil separated from the diff ring gear 7 rises toward the oil receiver 8. Here, since the diff ring gear 7 is a helical gear, the lubricating oil flies obliquely toward the MG2 reduction gear 6 depending on the direction of the tooth stripe (see arrow Y7). Thereby, the lubricating oil separated from the diff ring gear 7 can move toward the MG2 reduction gear 6 without being obstructed by the guide member 10. The lubricating oil that has reached the MG2 reduction gear 6 is pushed out by meshing of the gear in the meshing portion 41 and flows into the oil receiving portion 8 from the second inlet 82 via the guide passage 37.

  As described above, the lubricating oil supply device according to the present invention is useful for supplying the lubricating oil to the oil receiving portion of the power transmission device, and is particularly suitable for improving the ability to send the lubricating oil to the oil receiving portion. Yes.

DESCRIPTION OF SYMBOLS 1 Power transmission device 1-1, 1-2, 1-3, 1-4 Lubricating oil supply device 2 Case 4 Counter driven gear 5 Drive pinion gear 6 MG2 reduction gear 7 Defring gear 8 Oil receiving part 9 Storage part 10,30 Guide member 11, 31 Tubular part 12, 32 Outer peripheral surface cover part 13, 33 Side cover part 14, 24 Gap 17, 37 Guide passage 40, 41 Engagement part 50 Passage member 81 Inlet 82 Second inlet

Claims (8)

A lubricating oil supply device that is provided in a power transmission device of a vehicle in which lubricating oil is supplied from an oil receiving portion to a lubricated portion, and that supplies the lubricating oil to the oil receiving portion,
A pair of gears arranged below the oil receiving portion in the vertical direction and meshing with each other to receive supply of lubricating oil;
A guide passage communicating the meshing portion of the pair of gears and the oil receiving portion,
The said guide path is connected to the side in which the tooth | gear formed in the said pair of gear in the said mesh part is drawn in. The lubricating oil supply apparatus characterized by the above-mentioned. In the lubricating oil supply apparatus according to claim 1,
The lubricating oil supply device, wherein the guide passage faces a side of the meshing portion where the teeth are drawn in a direction parallel to a tangent line of the pair of gears in the meshing portion. In the lubricating oil supply apparatus according to claim 1 or 2,
A pair of wall portions facing each other in the axial direction across the meshing portion;
The wall portion is connected to a member constituting the guide passage, and a lubricating oil supply apparatus in which a space portion between the pair of wall portions is continuous with the guide passage. The lubricating oil supply apparatus according to any one of claims 1 to 3,
The lubricating oil supply device in which the lubricating oil is supplied to the meshing portion when one of the pair of gears sends out the lubricating oil stored in the power transmission device by rotation. In the lubricating oil supply apparatus according to claim 4,
The gear that sends out the stored lubricating oil by rotation is a lubricating oil supply device that is arranged on the same axis as the driving wheel of the vehicle and is a ring gear of a differential mechanism connected to the driving wheel. The lubricating oil supply apparatus according to any one of claims 1 to 3,
Unlike the pair of gears, including a third gear disposed vertically below the pair of gears,
The third gear is a lubricating oil supply device that supplies lubricating oil to the pair of gears by sending out the lubricating oil stored in the power transmission device by rotation. In the lubricating oil supply apparatus according to claim 6,
A passage member for guiding the lubricating oil sent by the third gear to the pair of gears;
The passage member is
A first passage is provided along the circumferential direction of the third gear so as to face the third gear and into which the lubricant sent by the third gear flows between the third gear and the third gear. A first component to
A second component forming a second passage for guiding the lubricating oil in the first passage to the pair of gears;
Have
The second passage is connected to the first passage on the upstream side in the flow direction from the outlet formed on the downstream side in the flow direction of the lubricating oil along the rotation direction of the third gear in the first passage. Connected,
The lubricating oil supply device further includes a suppression structure that suppresses the lubricating oil from flowing from the connection portion with the second passage toward the outlet in the first passage. The lubricating oil supply apparatus according to any one of claims 1 to 7,
In the tangent line of the pair of gears in the meshing portion, the lubricating oil supply device in which the side into which the teeth are drawn from the meshing portion is directed upward in the vertical direction as it is separated from the meshing portion.

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