WO2019208642A1 - Vehicle power transmission device - Google Patents

Vehicle power transmission device Download PDF

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Publication number
WO2019208642A1
WO2019208642A1 PCT/JP2019/017458 JP2019017458W WO2019208642A1 WO 2019208642 A1 WO2019208642 A1 WO 2019208642A1 JP 2019017458 W JP2019017458 W JP 2019017458W WO 2019208642 A1 WO2019208642 A1 WO 2019208642A1
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WO
WIPO (PCT)
Prior art keywords
oil
gear
power transmission
transmission device
vehicle power
Prior art date
Application number
PCT/JP2019/017458
Other languages
French (fr)
Japanese (ja)
Inventor
山田　賢
土橋　誠
誠人 西田
敬士 葛原
康夫 木間
勇司 古賀
慶明 小西
Original Assignee
本田技研工業株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
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Publication date
Application filed by 本田技研工業株式会社 filed Critical 本田技研工業株式会社
Priority to CN201980027814.5A priority Critical patent/CN112020618B/en
Priority to JP2020515528A priority patent/JP6923753B2/en
Priority to DE112019002135.4T priority patent/DE112019002135T5/en
Publication of WO2019208642A1 publication Critical patent/WO2019208642A1/en

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/0447—Control of lubricant levels, e.g. lubricant level control dependent on temperature
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/042—Guidance of lubricant
    • F16H57/0421—Guidance of lubricant on or within the casing, e.g. shields or baffles for collecting lubricant, tubes, pipes, grooves, channels or the like
    • F16H57/0423—Lubricant guiding means mounted or supported on the casing, e.g. shields or baffles for collecting lubricant, tubes or pipes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/0457—Splash lubrication
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/0467—Elements of gearings to be lubricated, cooled or heated
    • F16H57/0469—Bearings or seals
    • F16H57/0471—Bearing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/048—Type of gearings to be lubricated, cooled or heated
    • F16H57/0482—Gearings with gears having orbital motion
    • F16H57/0483—Axle or inter-axle differentials

Definitions

  • the present invention relates to a vehicle power transmission device that lubricates a bearing that supports a differential gear on a gear case with oil scraped up by a final driven gear provided in a differential gear housed in a front portion of the gear case.
  • the rotation of the motor shaft of the electric motor is differential through a counter drive gear provided on the motor shaft, a counter driven gear provided on the counter shaft, a final drive gear provided on the counter shaft, and a final driven gear provided on the differential shaft.
  • An axle drive device for transmitting to a gear is known from Japanese Patent Application Laid-Open No. 2004-228561.
  • the present invention has been made in view of the above-described circumstances, and it is an object of the present invention to effectively lubricate a bearing that supports a differential gear with oil that is scraped up by a final driven gear provided in a differential gear that is housed in a front portion of a gear case.
  • a gear case a differential gear housed in a front portion of the gear case, a bearing for supporting the differential gear on a side wall of the gear case, A final driven gear provided on the outer periphery of the differential gear; and a final drive gear that transmits a driving force of a driving source to the final driven gear via an input shaft, the final driven gear being forward of the input shaft in the vehicle traveling direction.
  • the vehicle power transmission device characterized in that the oil collecting recess is provided is proposed.
  • an oil guide wall arranged along the rear lower part of the final driven gear is provided, and the meshing portion is horizontally arranged to collect the oil.
  • a vehicular power transmission device is proposed which is located between a recess and the oil guide wall.
  • an oil pump is provided at a lower portion of the gear case, and the oil guide wall includes a first space for housing the final driven gear, and the oil.
  • a vehicular power transmission device is proposed, which is disposed between the second space in which the pump is accommodated.
  • the oil level of the oil staying at the bottom of the gear case is located below the upper end of the oil guide wall, and the oil guide wall
  • a vehicle power transmission device is proposed in which an opening for communicating the first space and the second space is formed in a lower portion of the vehicle.
  • a vehicle power transmission device in addition to the fourth feature, is proposed in which the opening is positioned above the lower end of the final driven gear. .
  • a motor case that houses therein the electric motor that is the drive source is coupled to the gear case
  • a vehicular power transmission device is proposed in which an internal space of the motor case and a communication hole for communicating the internal space of the gear case are formed below the oil level of oil staying at the bottom of the gear case.
  • the oil collecting recess disposed forward of the center of the final driven gear faces the bearing.
  • a bottom wall extending radially inward, a front inclined wall connected to the front side of the bottom wall and inclined at a first inclination angle, and a rear inclination inclined to a rear side of the bottom wall and inclined at a second inclination angle
  • a vehicle power transmission device having a wall and a groove-like cross section, wherein the second inclination angle is smaller than the first inclination angle.
  • a vehicle power transmission device characterized in that the width of the bottom wall decreases toward the bearing.
  • an inclination start line of the rear inclined wall constituting the rear edge of the groove-shaped cross section is formed with respect to the rear in the horizontal direction.
  • the angle is set to be 90 ° or more when the vehicle climbs at the maximum climb angle, and the angle formed by the inclination start line of the front inclined wall constituting the front edge of the groove-shaped cross section with respect to the rear in the horizontal direction is
  • a vehicle power transmission device is proposed which is set to be 170 ° or less when the vehicle descends at a maximum descending angle.
  • the electric motor 11 of the embodiment corresponds to the drive source of the present invention
  • the left housing 15 of the embodiment corresponds to the motor case of the present invention
  • the central housing 16 and the right housing 17 of the embodiment correspond to the present invention
  • the angular roller bearing 32 of the embodiment corresponds to the bearing of the present invention.
  • a vehicle power transmission device includes a gear case, a differential gear housed in a front portion of the gear case, a bearing that supports the differential gear on a side wall of the gear case, and an outer periphery of the differential gear.
  • a final driven gear is provided, and a final drive gear that transmits the driving force of the drive source to the final driven gear via the input shaft, and the final driven gear is disposed on the front side in the vehicle traveling direction with respect to the input shaft.
  • An oil collecting recess that collects oil collected from the bottom of the gear case by the final driven gear and supplies it to the bearing is provided on the side wall in front of the meshing portion of the final driven gear and the final drive gear. Even if the oil is blocked by the meshing part of the final driven gear and the final drive gear and becomes difficult to reach the bearing, the oil that has passed through the meshing part of the final driven gear and the final drive gear is efficiently collected by the oil collecting recess and supplied to the bearing. By doing so, the bearing can be effectively lubricated.
  • the oil guide wall is disposed along the rear lower portion of the final driven gear, and the meshing portion is positioned between the oil collecting recess and the oil guide wall in the horizontal direction. Even if the oil driven up by the final driven gear is obstructed by the meshing part and it is difficult to reach the bearing, the oil driven up by the final driven gear is supplied forward along the oil guide wall and efficiently supplied to the oil collecting recess.
  • the bearing can be lubricated.
  • the oil pump is disposed below the gear case, and the oil guide wall is disposed between the first space that houses the final driven gear and the second space that houses the oil pump. Therefore, the oil guide wall functions as a baffle plate to suppress the oil surface undulation caused by the rotation of the differential gear, thereby preventing the oil pump from sucking air.
  • the oil level of the oil staying at the bottom of the gear case is located below the upper end of the oil guide wall, and the first and second storage portions are disposed below the oil guide wall. Is formed so that the first storage portion and the second storage portion partitioned by the oil guide wall are communicated with each other by the opening portion, and the oil level of the first storage portion and the second storage portion is increased. In addition, it is possible to equalize, and it is difficult to entrain air when the oil passes through the opening, thereby preventing generation of bubbles.
  • the opening since the opening is located above the lower end of the final driven gear, the opening can be formed without causing the bottom of the gear case to bulge downward, and the large size of the gear case. Is prevented.
  • a motor case that houses an electric motor as a driving source is coupled to the gear case, and a communication hole that communicates the internal space of the motor case and the internal space of the gear case is provided in the gear case. Since it is formed below the oil level of the oil staying at the bottom, even if the oil in the gear case internal space flows out of the communication hole into the motor case internal space, The bearing can be reliably lubricated.
  • the oil collecting concave portion arranged in front of the center of the final driven gear has a bottom wall extending radially inward toward the bearing and a front side of the bottom wall.
  • a front inclined wall inclined at one inclination angle and a rear inclined wall connected to the rear side of the bottom wall and inclined at a second inclination angle are formed in a groove-like cross section, and the second inclination angle is the first inclination angle. Since the angle is smaller than the angle, the oil is efficiently guided to the bottom wall of the oil collecting recess by the rear inclined wall having a weak inclination angle, and the oil is effectively blocked by the front inclined wall having a strong inclination angle to be used as a bearing. Can be supplied automatically.
  • the eighth feature of the present invention since the width of the bottom wall decreases toward the bearing, the oil collected in the oil collecting recess can be efficiently supplied to the bearing.
  • the angle formed by the inclination start line of the rear inclined wall constituting the trailing edge of the groove-shaped cross section with respect to the rear in the horizontal direction is when the vehicle climbs at the maximum climb angle.
  • the angle formed by the inclination start line of the front inclined wall constituting the front edge of the groove-shaped cross section with respect to the horizontal rear is set to be 90 ° or more, and is 170 ° when the vehicle descends at the maximum downhill angle. Since it is set to be as follows, oil can be reliably supplied to the bearings when the vehicle is traveling uphill or downhill.
  • FIG. 1 is a longitudinal sectional view (cross-sectional view taken along line 1-1 of FIG. 2) of a power unit of an automobile.
  • FIG. 2 is a view taken along line 2-2 of FIG.
  • FIG. 3 is a view taken along line 3-3 in FIG.
  • First embodiment 4 is an enlarged sectional view taken along line 4-4 of FIG.
  • FIG. 5 is an explanatory diagram of the action when the automobile is climbing up and down.
  • the power unit of the electric vehicle includes a motor housing 14 that houses an electric motor 11, a speed reducer 12, and a differential gear 13.
  • the motor housing 14 is divided into three in the vehicle width direction.
  • a first accommodating portion 43 is defined between the left housing 15 and the central housing 16, and a second accommodating portion 44 is defined between the central housing 16 and the right housing 17.
  • the electric motor 11 disposed in the first housing portion 43 includes a motor shaft 20 supported by the left housing 15 and the central housing 16 via ball bearings 18 and 19, respectively, a rotor 21 fixed to the motor shaft 20, And a stator 22 fixed to the central housing 16 so as to surround the outer periphery of the rotor 21. Oil is stored at the bottom of the motor housing 14, and the oil level is OL.
  • the speed reducer 12 disposed in the second housing portion 44 includes a first speed reduction gear 23 fixed to the tip of the motor shaft 20 protruding rightward from the right housing 17, and an angular roller on each of the central housing 16 and the right housing 17.
  • a reduction shaft 26 supported via bearings 24 and 25, a second reduction gear 27 fixed to the reduction shaft 26 and meshing with the first reduction gear 23, and a final drive gear 28 fixed to the reduction shaft 26
  • a final driven gear 29 fixed to the outer periphery of the differential gear 13 and meshing with the final drive gear 28.
  • the differential case 30 that constitutes the outline of the differential gear 13 disposed in the second accommodating portion 44 is supported by the central housing 16 and the right housing 17 via angular roller bearings 31 and 32, respectively, and from the differential case 30 to the left.
  • An inboard joint 34 provided at the tip of the extended long left output shaft 33 projects outward from the left housing 15, and an inboard joint 36 provided at the tip of the short right output shaft 35 extending rightward from the differential case 30 extends from the right housing 17. Projects outward.
  • the left inboard joint 34 is connected to the left rear wheel via a left half shaft (not shown), and the left inboard joint 36 is connected to the right rear wheel via a right half shaft (not shown).
  • the left end of the left output shaft 33 whose right end is supported by the differential gear 13 is supported by the left housing 15 via a ball bearing 37.
  • the first housing portion 43 and the second housing portion 44 are positioned on the side wall 16 a of the central housing 16 that partitions the first housing portion 43 and the second housing portion 44 at a position lower than the oil level OL.
  • a communication hole 16b is formed to communicate with each other.
  • An oil pump 45 and an oil strainer 46 are disposed in the rear lower part of the second housing portion 44 so as to overlap each other, and a front first space 47 for housing the differential gear 13, an oil pump 45 and an oil strainer 46.
  • An arcuate oil guide wall 16c is formed along the outer periphery of the final driven gear 29 so as to partition the second space 48 on the rear side for housing the final driven gear 29.
  • An opening 49 that allows the first space 47 and the second space 48 to communicate with each other is formed below the lower end of the oil guide wall 16c.
  • FIG. 3 shows the left side surface of the right housing 17 coupled to the right side surface of the central housing 16.
  • the side wall 17 a of the right housing 17 includes a circular concave portion 17 b that covers the right side surface of the differential gear 13, and a concave portion.
  • the oil collecting recess 50 extends obliquely forward and upward from the center of the differential gear 13 toward the radially outer side.
  • the oil collecting recess 50 includes a flat bottom wall 50 a and a front inclined wall 50 b extending obliquely forward from the front end of the bottom wall 50 a and continuing to the wall surface of the recess 17 b of the right housing 17. And a rear inclined wall 50c extending obliquely rearward from the rear end of the bottom wall 50a and continuing to the wall surface of the recess 17b of the right housing 17 and having a groove shape in cross section.
  • the width of the bottom wall 50a is gradually reduced from the radially outer side to the inner side, and the radially inner end thereof is connected to the bearing support hole 17c.
  • the inclination angle of the front inclined wall 50b with respect to the plane orthogonal to the axis of the differential gear 13 (the split surface of the right housing 17) is the first inclination angle ⁇ 1
  • the inclination angle of the rear inclination wall 50c is the second inclination angle ⁇ 2.
  • the second inclination angle ⁇ 2 is set smaller than the first inclination angle ⁇ 1. That is, the front inclined wall 50 b stands with respect to the split surface of the right housing 17, and the rear inclined wall 50 c lies with respect to the split surface of the right housing 17.
  • the first housing portion 43 partitioned between the left housing 15 and the central housing 16 of the motor housing 14 and the second housing portion 44 partitioned between the central housing 16 and the right housing 17 of the motor housing 14 are the central housing 16. Since the communication holes 16b are connected to each other, the oil staying in the second storage portion 44 is supplied to the first storage portion 43 and used for lubrication and cooling of the electric motor 11.
  • the oil in the first space 47 and the second space 48 on the front side of the second storage portion 44 travels through the opening 49,
  • the oil level OL of the first space 47 and the second space 48 on the rear side can be made uniform.
  • the opening 49 is at a position much lower than the oil level OL, it is difficult to entrain air when the oil passes through the opening 49, and generation of bubbles can be prevented.
  • the opening 49 is located above the lower end of the final driven gear 29, the opening 49 can be formed without causing the bottom of the central housing 16 to bulge downward, and the motor housing 14 is prevented from being enlarged.
  • the oil guide wall 16c disposed between the first space 47 that accommodates the oil pump 45 and the second space 48 that accommodates the final driven gear 29 functions as a baffle plate, and the oil surface generated by the rotation of the differential gear 13
  • the oil pump 45 can be prevented from sucking air.
  • the oil guide wall 16c along the rear lower portion of the final driven gear 29, the oil scooped up by the final driven gear 29 is supplied forward along the oil guide wall 16c, and the oil on the side wall 17a of the right housing 17 is supplied.
  • the collecting recess 50 can be supplied.
  • the oil is smoothly guided to the rear inclined wall 50c and reaches the bottom wall 50a, where the front inclined having a large first inclined angle ⁇ 1.
  • the angular roller bearing 32 that flows radially inward along the bottom wall 50a, passes through the bearing support hole 17c, and supports the right end of the differential gear 13 to the right housing 17 is lubricated.
  • the width of the bottom wall 50a of the oil collecting recess 50 decreases toward the angular roller bearing 32, the oil collected in the oil collecting recess 50 can be efficiently directed to the angular roller bearing 32. .
  • the differential gear 13 is disposed at the front portion of the motor housing 14, and the final drive gear 28 and the final driven gear are provided in a path through which the oil driven by the final driven gear 29 along the oil guide wall 16c is supplied to the angular roller bearing 32. Since the 29 meshing portions 38 (see FIG. 2) are located, the supply of oil is hindered by the meshing portions 38, and the oil may not easily reach the oil collecting recess 50.
  • the first housing portion 43 and the second housing portion 44 of the motor housing 14 communicate with each other through a communication hole 16b lower than the oil level OL, and the oil in the second housing portion 44 is used to lubricate and cool the electric motor 11. Even if the amount of oil in the second storage portion 44 decreases after flowing into the first storage portion 43, the amount of oil necessary for the angular roller bearing 32 is compensated for by the oil collection effect of the oil collection recess 50. Oil can be supplied.
  • FIG. 5 (A) shows a state where the vehicle climbs at the maximum possible climb angle ⁇ .
  • the tilt start line 50e which is the rear edge of the rear inclined wall 50c of the oil collecting recess 50, is also tilted rearward, but the tilt start line 50e is rearward in the horizontal direction.
  • the formed angle ⁇ is set to 90 ° or more.
  • FIG. 5B shows a state where the vehicle descends at the assumed maximum descending angle ⁇ .
  • the inclination start line 50d that is the front edge of the front inclined wall 50b of the oil collecting recess 50 is also inclined forward, but the inclination start line 50d forms the rear in the horizontal direction.
  • the angle ⁇ is set to 170 ° or less.
  • the bearing of the present invention is not limited to the angular roller bearing 32 of the embodiment, and may be any type of bearing.
  • the drive source of the present invention is not limited to the electric motor 11 of the embodiment, and may be another type of drive source such as an engine.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Details Of Gearings (AREA)

Abstract

A vehicle power transmission device in which a side wall (17a) forwardly of a meshing portion (38) between a final driven gear (29) and a final drive gear (28) is provided with an oil-collecting recess (50) which collects oil that has been scooped up by the final driven gear (29) from a bottom portion of a gear case (16, 17) and supplies the oil to a bearing (32). Accordingly, even when the oil scooped up by the final driven gear (29) is blocked by the meshing portion (38) and becomes less likely to reach the bearing (32), the oil that has passed through the meshing portion (38) can be collected by the oil-collecting recess (50) efficiently and supplied to the bearing (32), whereby the bearing (32) supporting the differential gear (13) can be lubricated effectively.

Description

車両用動力伝達装置Power transmission device for vehicle
　本発明は、ギヤケースの前部に収納されるディファレンシャルギヤに設けたファイナルドリブンギヤで掻き上げたオイルで、ディファレンシャルギヤをギヤケースに支持するベアリングを潤滑する車両用動力伝達装置に関する。 The present invention relates to a vehicle power transmission device that lubricates a bearing that supports a differential gear on a gear case with oil scraped up by a final driven gear provided in a differential gear housed in a front portion of the gear case.
　電動モータのモータ軸の回転を、モータ軸に設けたカウンタドライブギヤと、カウンタ軸に設けたカウンタドリブンギヤと、カウンタ軸に設けたファイナルドライブギヤと、デフ軸に設けたファイナルドリブンギヤとを介してディファレンシャルギヤに伝達する車軸駆動装置が、下記特許文献１により公知である。 The rotation of the motor shaft of the electric motor is differential through a counter drive gear provided on the motor shaft, a counter driven gear provided on the counter shaft, a final drive gear provided on the counter shaft, and a final driven gear provided on the differential shaft. An axle drive device for transmitting to a gear is known from Japanese Patent Application Laid-Open No. 2004-228561.
日本特開２００５－２０１３１６号公報Japanese Unexamined Patent Publication No. 2005-201316
　ところで、上記従来の車軸駆動装置は、ディファレンシャルギヤがギヤケースの前部に配置されているため、ディファレンシャルギヤに設けたファイナルドリブンギヤでギヤケースの底部に滞留するオイルを後上方に掻き上げて被潤滑部を潤滑しようとしても、ファイナルドリブンギヤの後部はファイナルドライブギヤの前部と噛合しているため、せっかくファイナルドリブンギヤが掻き上げたオイルがファイナルドリブンギヤおよびファイナルドライブギヤの噛合部に阻止されて被潤滑部に届き難くなるという課題に対し、カウンタ軸に設けたカウンタドリブンギヤでオイルを後上方に掻き上げて被潤滑部に供給することで対処している。 By the way, in the above conventional axle drive device, since the differential gear is arranged at the front part of the gear case, the oil staying at the bottom part of the gear case is scraped upward and rearward by the final driven gear provided in the differential gear. Even if you try to lubricate, the rear part of the final driven gear meshes with the front part of the final drive gear. The problem of difficulty is addressed by using a counter driven gear provided on the counter shaft to rake up the oil rearward and supply it to the lubricated part.
　しかしながら、このような方法では、カウンタドリブンギヤの直径を大きくする必要があるため、ギヤケースの上下方向の寸法が大型化するという問題がある。 However, such a method has a problem that the vertical dimension of the gear case is increased because the diameter of the counter driven gear needs to be increased.
　本発明は前述の事情に鑑みてなされたもので、ギヤケースの前部に収納されるディファレンシャルギヤに設けたファイナルドリブンギヤが掻き上げるオイルで、ディファレンシャルギヤを支持するベアリングを効果的に潤滑することを目的とする。 The present invention has been made in view of the above-described circumstances, and it is an object of the present invention to effectively lubricate a bearing that supports a differential gear with oil that is scraped up by a final driven gear provided in a differential gear that is housed in a front portion of a gear case. And
　上記目的を達成するために、本発明の第１の特徴によれば、ギヤケースと、前記ギヤケースの前部に収納されたディファレンシャルギヤと、前記ディファレンシャルギヤを前記ギヤケースの側壁に支持するベアリングと、前記ディファレンシャルギヤの外周に設けられたファイナルドリブンギヤと、駆動源の駆動力を入力軸を介して前記ファイナルドリブンギヤに伝達するファイナルドライブギヤとを備え、前記ファイナルドリブンギヤは前記入力軸に対して車両進行方向前方側に配置される車両用動力伝達装置であって、前記ファイナルドリブンギヤおよび前記ファイナルドライブギヤの噛合部の前方の前記側壁に、前記ギヤケースの底部から前記ファイナルドリブンギヤにより掻き上げられたオイルを収集して前記ベアリングに供給するオイル収集凹部が設けられることを特徴とする車両用動力伝達装置が提案される。 To achieve the above object, according to a first aspect of the present invention, a gear case, a differential gear housed in a front portion of the gear case, a bearing for supporting the differential gear on a side wall of the gear case, A final driven gear provided on the outer periphery of the differential gear; and a final drive gear that transmits a driving force of a driving source to the final driven gear via an input shaft, the final driven gear being forward of the input shaft in the vehicle traveling direction. A power transmission device for a vehicle disposed on a side, wherein oil collected from the bottom of the gear case by the final driven gear is collected on the side wall in front of the meshing portion of the final driven gear and the final drive gear. Supply to the bearing The vehicle power transmission device, characterized in that the oil collecting recess is provided is proposed.
　また本発明の第２の特徴によれば、前記第１の特徴に加えて、前記ファイナルドリブンギヤの後下部に沿うように配置されたオイルガイド壁を備え、前記噛合部は水平方向で前記オイル収集凹部と前記オイルガイド壁との間に位置することを特徴とする車両用動力伝達装置が提案される。 According to a second feature of the present invention, in addition to the first feature, an oil guide wall arranged along the rear lower part of the final driven gear is provided, and the meshing portion is horizontally arranged to collect the oil. A vehicular power transmission device is proposed which is located between a recess and the oil guide wall.
　また本発明の第３特徴によれば、前記第２の特徴に加えて、前記ギヤケースの下部に配置されたオイルポンプを備え、前記オイルガイド壁は前記ファイナルドリブンギヤを収容する第１空間と前記オイルポンプを収容する第２空間との間に配置されることを特徴とする車両用動力伝達装置が提案される。 According to a third feature of the present invention, in addition to the second feature, an oil pump is provided at a lower portion of the gear case, and the oil guide wall includes a first space for housing the final driven gear, and the oil. A vehicular power transmission device is proposed, which is disposed between the second space in which the pump is accommodated.
　また本発明の第４の特徴によれば、前記第３の特徴に加えて、前記ギヤケースの底部に滞留するオイルの油面は前記オイルガイド壁の上端よりも下方に位置し、前記オイルガイド壁の下部に前記第１空間および前記第２空間を連通させる開口部が形成されることを特徴とする車両用動力伝達装置が提案される。 According to a fourth feature of the present invention, in addition to the third feature, the oil level of the oil staying at the bottom of the gear case is located below the upper end of the oil guide wall, and the oil guide wall A vehicle power transmission device is proposed in which an opening for communicating the first space and the second space is formed in a lower portion of the vehicle.
　また本発明の第５の特徴によれば、前記第４の特徴に加えて、前記開口部は前記ファイナルドリブンギヤの下端よりも上方に位置することを特徴とする車両用動力伝達装置が提案される。 According to a fifth feature of the present invention, in addition to the fourth feature, a vehicle power transmission device is proposed in which the opening is positioned above the lower end of the final driven gear. .
　また本発明の第６の特徴によれば、前記第１～第５の何れか１つの特徴に加えて、内部に前記駆動源である電動モータを収納するモータケースが前記ギヤケースに結合され、前記モータケースの内部空間および前記ギヤケースの内部空間を連通させる連通孔が該ギヤケースの底部に滞留するオイルの油面よりも下方に形成されることを特徴とする車両用動力伝達装置が提案される。 According to a sixth feature of the present invention, in addition to any one of the first to fifth features, a motor case that houses therein the electric motor that is the drive source is coupled to the gear case, A vehicular power transmission device is proposed in which an internal space of the motor case and a communication hole for communicating the internal space of the gear case are formed below the oil level of oil staying at the bottom of the gear case.
　また本発明の第７の特徴によれば、前記第１～第６の何れか１つの特徴に加えて、前記ファイナルドリブンギヤの中心よりも前方に配置された前記オイル収集凹部は、前記ベアリングに向かって径方向内向きに延びる底壁と、前記底壁の前側に連なって第１傾斜角で傾斜する前側傾斜壁と、前記底壁の後側に連なって第２傾斜角で傾斜する後側傾斜壁とを有して溝状断面に形成され、前記第２傾斜角は前記第１傾斜角よりも小さいことを特徴とする車両用動力伝達装置が提案される。 According to a seventh feature of the present invention, in addition to any one of the first to sixth features, the oil collecting recess disposed forward of the center of the final driven gear faces the bearing. A bottom wall extending radially inward, a front inclined wall connected to the front side of the bottom wall and inclined at a first inclination angle, and a rear inclination inclined to a rear side of the bottom wall and inclined at a second inclination angle There is proposed a vehicle power transmission device having a wall and a groove-like cross section, wherein the second inclination angle is smaller than the first inclination angle.
　また本発明の第８の特徴によれば、前記第７の特徴に加えて、前記底壁の幅は前記ベアリングに向かって減少することを特徴とする車両用動力伝達装置が提案される。 Further, according to an eighth feature of the present invention, in addition to the seventh feature, there is proposed a vehicle power transmission device characterized in that the width of the bottom wall decreases toward the bearing.
　また本発明の第９の特徴によれば、前記第７または第８の特徴に加えて、溝状断面の後縁を構成する前記後側傾斜壁の傾斜開始線が水平方向後方に対して成す角度は、車両が最大登坂角で登坂するときに９０°以上となるように設定され、溝状断面の前縁を構成する前記前側傾斜壁の傾斜開始線が水平方向後方に対して成す角度は、車両が最大降坂角で降坂するときに１７０°以下になるように設定されることを特徴とする車両用動力伝達装置が提案される。 According to a ninth feature of the present invention, in addition to the seventh or eighth feature, an inclination start line of the rear inclined wall constituting the rear edge of the groove-shaped cross section is formed with respect to the rear in the horizontal direction. The angle is set to be 90 ° or more when the vehicle climbs at the maximum climb angle, and the angle formed by the inclination start line of the front inclined wall constituting the front edge of the groove-shaped cross section with respect to the rear in the horizontal direction is A vehicle power transmission device is proposed which is set to be 170 ° or less when the vehicle descends at a maximum descending angle.
　なお、実施の形態の電動モータ１１は本発明の駆動源に対応し、実施の形態の左ハウジング１５は本発明のモータケースに対応し、実施の形態の中央ハウジング１６および右ハウジング１７は本発明のギヤケースに対応し、実施の形態のアンギュラローラベアリング３２は本発明のベアリングに対応する。 The electric motor 11 of the embodiment corresponds to the drive source of the present invention, the left housing 15 of the embodiment corresponds to the motor case of the present invention, and the central housing 16 and the right housing 17 of the embodiment correspond to the present invention. The angular roller bearing 32 of the embodiment corresponds to the bearing of the present invention.
　本発明の第１の特徴によれば、車両用動力伝達装置は、ギヤケースと、ギヤケースの前部に収納されたディファレンシャルギヤと、ディファレンシャルギヤをギヤケースの側壁に支持するベアリングと、ディファレンシャルギヤの外周に設けられたファイナルドリブンギヤと、駆動源の駆動力を入力軸を介してファイナルドリブンギヤに伝達するファイナルドライブギヤとを備え、ファイナルドリブンギヤは入力軸に対して車両進行方向前方側に配置される。 According to the first aspect of the present invention, a vehicle power transmission device includes a gear case, a differential gear housed in a front portion of the gear case, a bearing that supports the differential gear on a side wall of the gear case, and an outer periphery of the differential gear. A final driven gear is provided, and a final drive gear that transmits the driving force of the drive source to the final driven gear via the input shaft, and the final driven gear is disposed on the front side in the vehicle traveling direction with respect to the input shaft.
　ファイナルドリブンギヤおよびファイナルドライブギヤの噛合部の前方の側壁に、ギヤケースの底部からファイナルドリブンギヤにより掻き上げられたオイルを収集してベアリングに供給するオイル収集凹部が設けられるので、ファイナルドリブンギヤにより掻き上げられたオイルがファイナルドリブンギヤおよびファイナルドライブギヤの噛合部に阻止されてベアリングに届き難くなっても、ファイナルドリブンギヤおよびファイナルドライブギヤの噛合部を通過したオイルをオイル収集凹部で効率的に収集してベアリングに供給することで、ベアリングを効果的に潤滑することができる。 An oil collecting recess that collects oil collected from the bottom of the gear case by the final driven gear and supplies it to the bearing is provided on the side wall in front of the meshing portion of the final driven gear and the final drive gear. Even if the oil is blocked by the meshing part of the final driven gear and the final drive gear and becomes difficult to reach the bearing, the oil that has passed through the meshing part of the final driven gear and the final drive gear is efficiently collected by the oil collecting recess and supplied to the bearing. By doing so, the bearing can be effectively lubricated.
　また本発明の第２の特徴によれば、ファイナルドリブンギヤの後下部に沿うように配置されたオイルガイド壁を備え、噛合部は水平方向でオイル収集凹部とオイルガイド壁との間に位置するので、ファイナルドリブンギヤが掻き上げたオイルが噛合部に邪魔されてベアリングに届き難くなっても、ファイナルドリブンギヤが掻き上げたオイルをオイルガイド壁に沿って前方に供給し、オイル収集凹部に効率的に供給してベアリングを潤滑することができる。 According to the second aspect of the present invention, the oil guide wall is disposed along the rear lower portion of the final driven gear, and the meshing portion is positioned between the oil collecting recess and the oil guide wall in the horizontal direction. Even if the oil driven up by the final driven gear is obstructed by the meshing part and it is difficult to reach the bearing, the oil driven up by the final driven gear is supplied forward along the oil guide wall and efficiently supplied to the oil collecting recess. The bearing can be lubricated.
　また本発明の第３の特徴によれば、ギヤケースの下部に配置されたオイルポンプを備え、オイルガイド壁はファイナルドリブンギヤを収容する第１空間とオイルポンプを収容する第２空間との間に配置されるので、オイルガイド壁がバッフルプレートとして機能してディファレンシャルギヤの回転により発生する油面の波立ちを抑制し、オイルポンプがエアを吸入するのを防止することができる。 According to the third aspect of the present invention, the oil pump is disposed below the gear case, and the oil guide wall is disposed between the first space that houses the final driven gear and the second space that houses the oil pump. Therefore, the oil guide wall functions as a baffle plate to suppress the oil surface undulation caused by the rotation of the differential gear, thereby preventing the oil pump from sucking air.
　また本発明の第４の特徴によれば、ギヤケースの底部に滞留するオイルの油面はオイルガイド壁の上端よりも下方に位置し、オイルガイド壁の下部に第１収容部および第２収容部を連通させる開口部が形成されるので、オイルガイド壁で仕切られた第１収容部および第２収容部を開口部で連通させ、第１収容部および第２収容部の油面の高さを均等化することができ、しかもオイルが開口部を通過する際にエアを巻き込み難くして泡の発生を防止することができる。 According to the fourth aspect of the present invention, the oil level of the oil staying at the bottom of the gear case is located below the upper end of the oil guide wall, and the first and second storage portions are disposed below the oil guide wall. Is formed so that the first storage portion and the second storage portion partitioned by the oil guide wall are communicated with each other by the opening portion, and the oil level of the first storage portion and the second storage portion is increased. In addition, it is possible to equalize, and it is difficult to entrain air when the oil passes through the opening, thereby preventing generation of bubbles.
　また本発明の第５の特徴によれば、開口部はファイナルドリブンギヤの下端よりも上方に位置するので、ギヤケースの底部を下方に膨らませることなく開口部を形成することが可能となり、ギヤケースの大型化が防止される。 According to the fifth feature of the present invention, since the opening is located above the lower end of the final driven gear, the opening can be formed without causing the bottom of the gear case to bulge downward, and the large size of the gear case. Is prevented.
　また本発明の第６の特徴によれば、内部に駆動源である電動モータを収納するモータケースがギヤケースに結合され、モータケースの内部空間およびギヤケースの内部空間を連通させる連通孔が該ギヤケースの底部に滞留するオイルの油面よりも下方に形成されるので、ギヤケースの内部空間のオイルが連通孔からモータケースの内部空間に流出しても、オイル収集凹部のオイル収集作用でギヤケース内のオイルでベアリングを確実に潤滑することができる。 According to a sixth aspect of the present invention, a motor case that houses an electric motor as a driving source is coupled to the gear case, and a communication hole that communicates the internal space of the motor case and the internal space of the gear case is provided in the gear case. Since it is formed below the oil level of the oil staying at the bottom, even if the oil in the gear case internal space flows out of the communication hole into the motor case internal space, The bearing can be reliably lubricated.
　また本発明の第７の特徴によれば、ファイナルドリブンギヤの中心よりも前方に配置されたオイル収集凹部は、ベアリングに向かって径方向内向きに延びる底壁と、底壁の前側に連なって第１傾斜角で傾斜する前側傾斜壁と、底壁の後側に連なって第２傾斜角で傾斜する後側傾斜壁とを有して溝状断面に形成され、第２傾斜角は第１傾斜角よりも小さいので、傾斜角の弱い後側傾斜壁でオイルをオイル収集凹部の底壁部に効率的に案内するとともに、そのオイルを傾斜角の強い前側傾斜壁で塞き止めてベアリングに効率的に供給することができる。 According to the seventh aspect of the present invention, the oil collecting concave portion arranged in front of the center of the final driven gear has a bottom wall extending radially inward toward the bearing and a front side of the bottom wall. A front inclined wall inclined at one inclination angle and a rear inclined wall connected to the rear side of the bottom wall and inclined at a second inclination angle are formed in a groove-like cross section, and the second inclination angle is the first inclination angle. Since the angle is smaller than the angle, the oil is efficiently guided to the bottom wall of the oil collecting recess by the rear inclined wall having a weak inclination angle, and the oil is effectively blocked by the front inclined wall having a strong inclination angle to be used as a bearing. Can be supplied automatically.
　また本発明の第８の特徴によれば、底壁の幅はベアリングに向かって減少するので、オイル収集凹部に収集したオイルをベアリングに指向させて効率的に供給することができる。 Further, according to the eighth feature of the present invention, since the width of the bottom wall decreases toward the bearing, the oil collected in the oil collecting recess can be efficiently supplied to the bearing.
　また本発明の第９の特徴によれば、溝状断面の後縁を構成する後側傾斜壁の傾斜開始線が水平方向後方に対して成す角度は、車両が最大登坂角で登坂するときに９０°以上となるように設定され、溝状断面の前縁を構成する前側傾斜壁の傾斜開始線が水平方向後方に対して成す角度は、車両が最大降坂角で降坂するときに１７０°以下になるように設定されるので、車両の登坂走行時にも降坂走行時にもベアリングにオイルを確実に供給することができる。 According to the ninth feature of the present invention, the angle formed by the inclination start line of the rear inclined wall constituting the trailing edge of the groove-shaped cross section with respect to the rear in the horizontal direction is when the vehicle climbs at the maximum climb angle. The angle formed by the inclination start line of the front inclined wall constituting the front edge of the groove-shaped cross section with respect to the horizontal rear is set to be 90 ° or more, and is 170 ° when the vehicle descends at the maximum downhill angle. Since it is set to be as follows, oil can be reliably supplied to the bearings when the vehicle is traveling uphill or downhill.
図１は自動車のパワーユニットの縦断面図（図２の１－１線断面図）である。（第１の実施の形態）FIG. 1 is a longitudinal sectional view (cross-sectional view taken along line 1-1 of FIG. 2) of a power unit of an automobile. (First embodiment) 図２は図１の２－２線矢視図である。（第１の実施の形態）FIG. 2 is a view taken along line 2-2 of FIG. (First embodiment) 図３は図１の３－３線矢視図である。（第１の実施の形態）FIG. 3 is a view taken along line 3-3 in FIG. (First embodiment) 図４は図３の４－４線拡大断面図である。（第１の実施の形態）4 is an enlarged sectional view taken along line 4-4 of FIG. (First embodiment) 図５は自動車の登坂時および降坂時の作用説明図である。（第１の実施の形態）FIG. 5 is an explanatory diagram of the action when the automobile is climbing up and down. (First embodiment)
１１　　　　電動モータ（駆動源）
１３　　　　ディファレンシャルギヤ
１５　　　　左ハウジング（モータケース）
１６　　　　中央ハウジング（ギヤケース）
１６ｂ　　　連通孔
１６ｃ　　　オイルガイド壁
１７　　　　右ハウジング（ギヤケース）
１７ａ　　　側壁
２０　　　　入力軸
２８　　　　ファイナルドライブギヤ
２９　　　　ファイナルドリブンギヤ
３２　　　　アンギュラローラベアリング（ベアリング）
３８　　　　噛合部
４５　　　　オイルポンプ
４７　　　　第１空間
４８　　　　第２空間
４９　　　　開口部
５０        オイル収集凹部
５０ａ      底壁
５０ｂ      前側傾斜壁
５０ｃ      後側傾斜壁
５０ｄ　　　前側傾斜壁の傾斜開始線
５０ｅ　　　後側傾斜壁の傾斜開始線
θ１        第１傾斜角
θ２　　　　第２傾斜角
α　　　　　後側傾斜壁の傾斜開始線が水平方向後方に対して成す角度
β　　　　　前側傾斜壁の傾斜開始線が水平方向後方に対して成す角度 11 Electric motor (drive source)
13 Differential gear 15 Left housing (motor case)
16 Central housing (gear case)
16b Communication hole 16c Oil guide wall 17 Right housing (gear case)
17a Side wall 20 Input shaft 28 Final drive gear 29 Final driven gear 32 Angular roller bearing (bearing)
38 meshing portion 45 oil pump 47 first space 48 second space 49 opening 50 oil collecting recess 50a bottom wall 50b front side inclined wall 50c rear side inclined wall 50d front side inclined wall inclination start line 50e rear side inclined wall inclination start line θ1 First tilt angle θ2 Second tilt angle α Angle formed by the tilt start line of the rear tilt wall with respect to the rear in the horizontal direction β Angle formed by the tilt start line of the front tilt wall with respect to the rear in the horizontal direction
　以下、図１～図５に基づいて本発明の実施の形態を説明する。 Hereinafter, embodiments of the present invention will be described with reference to FIGS.
第１の実施の形態First embodiment
　図１および図２に示すように、電気自動車のパワーユニットは、内部に電動モータ１１、減速機１２およびディファレンシャルギヤ１３を収納するモータハウジング１４を備えており、モータハウジング１４は車幅方向に３分割された左ハウジング１５、中央ハウジング１６および右ハウジング１７からなる。左ハウジング１５および中央ハウジング１６の間には第１収容部４３が区画され、中央ハウジング１６および右ハウジング１７の間には第２収容部４４が区画される。 As shown in FIGS. 1 and 2, the power unit of the electric vehicle includes a motor housing 14 that houses an electric motor 11, a speed reducer 12, and a differential gear 13. The motor housing 14 is divided into three in the vehicle width direction. The left housing 15, the central housing 16, and the right housing 17. A first accommodating portion 43 is defined between the left housing 15 and the central housing 16, and a second accommodating portion 44 is defined between the central housing 16 and the right housing 17.
　第１収容部４３に配置された電動モータ１１は、左ハウジング１５および中央ハウジング１６にそれぞれボールベアリング１８，１９を介して支持されたモータ軸２０と、モータ軸２０に固定されたロータ２１と、ロータ２１の外周を取り囲むように中央ハウジング１６に固定されたステータ２２とを備える。モータハウジング１４の底部にはオイルが貯留されており、そのオイルレベルはＯＬである。 The electric motor 11 disposed in the first housing portion 43 includes a motor shaft 20 supported by the left housing 15 and the central housing 16 via ball bearings 18 and 19, respectively, a rotor 21 fixed to the motor shaft 20, And a stator 22 fixed to the central housing 16 so as to surround the outer periphery of the rotor 21. Oil is stored at the bottom of the motor housing 14, and the oil level is OL.
　第２収容部４４に配置された減速機１２は、右ハウジング１７から右側に突出するモータ軸２０の先端に固設された第１減速ギヤ２３と、中央ハウジング１６および右ハウジング１７にそれぞれアンギュラローラベアリング２４，２５を介して支持された減速軸２６と、減速軸２６に固設されて第１減速ギヤ２３に噛合する第２減速ギヤ２７と、減速軸２６に固設されたファイナルドライブギヤ２８と、ディファレンシャルギヤ１３の外周に固設されてファイナルドライブギヤ２８に噛合するファイナルドリブンギヤ２９とを備える。 The speed reducer 12 disposed in the second housing portion 44 includes a first speed reduction gear 23 fixed to the tip of the motor shaft 20 protruding rightward from the right housing 17, and an angular roller on each of the central housing 16 and the right housing 17. A reduction shaft 26 supported via bearings 24 and 25, a second reduction gear 27 fixed to the reduction shaft 26 and meshing with the first reduction gear 23, and a final drive gear 28 fixed to the reduction shaft 26 And a final driven gear 29 fixed to the outer periphery of the differential gear 13 and meshing with the final drive gear 28.
　第２収容部４４に配置されたディファレンシャルギヤ１３の外郭を構成するデフケース３０は、中央ハウジング１６および右ハウジング１７にそれぞれアンギュラローラベアリング３１，３２を介して支持されており、デフケース３０から左方向に延びる長い左出力軸３３の先端に設けたインボードジョイント３４が左ハウジング１５から外側に突出し、デフケース３０から右方向に延びる短い右出力軸３５の先端に設けたインボードジョイント３６が右ハウジング１７から外側に突出する。左側のインボードジョイント３４は、不図示の左ハーフシャフトを介して左後輪に接続され、また左側のインボードジョイント３６は、不図示の右ハーフシャフトを介して右後輪に接続される。右端をディファレンシャルギヤ１３に支持された左出力軸３３の左端は、左ハウジング１５にボールベアリング３７を介して支持される。 The differential case 30 that constitutes the outline of the differential gear 13 disposed in the second accommodating portion 44 is supported by the central housing 16 and the right housing 17 via angular roller bearings 31 and 32, respectively, and from the differential case 30 to the left. An inboard joint 34 provided at the tip of the extended long left output shaft 33 projects outward from the left housing 15, and an inboard joint 36 provided at the tip of the short right output shaft 35 extending rightward from the differential case 30 extends from the right housing 17. Projects outward. The left inboard joint 34 is connected to the left rear wheel via a left half shaft (not shown), and the left inboard joint 36 is connected to the right rear wheel via a right half shaft (not shown). The left end of the left output shaft 33 whose right end is supported by the differential gear 13 is supported by the left housing 15 via a ball bearing 37.
　図２から明らかなように、第１収容部４３および第２収容部４４を区画する中央ハウジング１６の側壁１６ａには、オイルレベルＯＬよりも低い位置で第１収容部４３および第２収容部４４を相互に連通させる連通孔１６ｂが形成される。第２収容部４４の後下部には、オイルポンプ４５およびオイルストレーナ４６が上下に重なるように配置されており、ディファレンシャルギヤ１３を収納する前側の第１空間４７と、オイルポンプ４５およびオイルストレーナ４６を収納する後側の第２空間４８とを仕切るように、ファイナルドリブンギヤ２９の外周に沿う円弧状のオイルガイド壁１６ｃが形成される。オイルガイド壁１６ｃの下端の下方には、第１空間４７および第２空間４８を相互に連通させる開口部４９が形成される。 As apparent from FIG. 2, the first housing portion 43 and the second housing portion 44 are positioned on the side wall 16 a of the central housing 16 that partitions the first housing portion 43 and the second housing portion 44 at a position lower than the oil level OL. A communication hole 16b is formed to communicate with each other. An oil pump 45 and an oil strainer 46 are disposed in the rear lower part of the second housing portion 44 so as to overlap each other, and a front first space 47 for housing the differential gear 13, an oil pump 45 and an oil strainer 46. An arcuate oil guide wall 16c is formed along the outer periphery of the final driven gear 29 so as to partition the second space 48 on the rear side for housing the final driven gear 29. An opening 49 that allows the first space 47 and the second space 48 to communicate with each other is formed below the lower end of the oil guide wall 16c.
　図３は、中央ハウジング１６の右側面に結合される右ハウジング１７の左側面を示すものであり、右ハウジング１７の側壁１７ａには、ディファレンシャルギヤ１３の右側面を覆う円形の凹部１７ｂと、凹部１７ｂの中心に形成されてディファレンシャルギヤ１３の右端を支持するアンギュラローラベアリング３２が嵌合するベアリング支持孔１７ｃと、凹部１７ｂの一部を溝状に窪ませたオイル収集凹部５０とが形成される。オイル収集凹部５０は、ディファレンシャルギヤ１３の中心から径方向外側に向かって前上方に斜めに延びている。 FIG. 3 shows the left side surface of the right housing 17 coupled to the right side surface of the central housing 16. The side wall 17 a of the right housing 17 includes a circular concave portion 17 b that covers the right side surface of the differential gear 13, and a concave portion. A bearing support hole 17c formed in the center of 17b and into which an angular roller bearing 32 for supporting the right end of the differential gear 13 is fitted, and an oil collecting recess 50 in which a part of the recess 17b is recessed in a groove shape are formed. . The oil collecting recess 50 extends obliquely forward and upward from the center of the differential gear 13 toward the radially outer side.
　図３および図４に詳細に示すように、オイル収集凹部５０は、平坦な底壁５０ａと、底壁５０ａの前端から斜め前方に延びて右ハウジング１７の凹部１７ｂの壁面に連なる前側傾斜壁５０ｂと、底壁５０ａの後端から斜め後方に延びて右ハウジング１７の凹部１７ｂの壁面に連なる後側傾斜壁５０ｃとを有して断面溝状に形成される。底壁５０ａは径方向外側から内側に向かって幅が次第に縮小しており、その径方向内端はベアリング支持孔１７ｃに接続している。 As shown in detail in FIGS. 3 and 4, the oil collecting recess 50 includes a flat bottom wall 50 a and a front inclined wall 50 b extending obliquely forward from the front end of the bottom wall 50 a and continuing to the wall surface of the recess 17 b of the right housing 17. And a rear inclined wall 50c extending obliquely rearward from the rear end of the bottom wall 50a and continuing to the wall surface of the recess 17b of the right housing 17 and having a groove shape in cross section. The width of the bottom wall 50a is gradually reduced from the radially outer side to the inner side, and the radially inner end thereof is connected to the bearing support hole 17c.
　ディファレンシャルギヤ１３の軸線に直交する平面（右ハウジング１７の割り面）に対する前側傾斜壁５０ｂの傾斜角を第１傾斜角θ１とし、後側傾斜壁５０ｃの傾斜角を第２傾斜角をθ２としたとき、２傾斜角θ２は第１傾斜角θ１よりも小さく設定される。つまり前側傾斜壁５０ｂは右ハウジング１７の割り面に対して立っており、後側傾斜壁５０ｃは右ハウジング１７の割り面に対して寝ている。 The inclination angle of the front inclined wall 50b with respect to the plane orthogonal to the axis of the differential gear 13 (the split surface of the right housing 17) is the first inclination angle θ1, and the inclination angle of the rear inclination wall 50c is the second inclination angle θ2. At this time, the second inclination angle θ2 is set smaller than the first inclination angle θ1. That is, the front inclined wall 50 b stands with respect to the split surface of the right housing 17, and the rear inclined wall 50 c lies with respect to the split surface of the right housing 17.
　次に、上記構成を備えた本発明の実施の形態の作用を説明する。 Next, the operation of the embodiment of the present invention having the above configuration will be described.
　モータハウジング１４の左ハウジング１５および中央ハウジング１６間に区画された第１収容部４３と、モータハウジング１４の中央ハウジング１６および右ハウジング１７間に区画された第２収容部４４とは、中央ハウジング１６に形成した連通孔１６ｂで相互に連通するので、第２収容部４４に滞留するオイルは第１収容部４３に供給されて電動モータ１１の潤滑および冷却に供される。 The first housing portion 43 partitioned between the left housing 15 and the central housing 16 of the motor housing 14 and the second housing portion 44 partitioned between the central housing 16 and the right housing 17 of the motor housing 14 are the central housing 16. Since the communication holes 16b are connected to each other, the oil staying in the second storage portion 44 is supplied to the first storage portion 43 and used for lubrication and cooling of the electric motor 11.
　車両の走行に伴って第２収容部４４に滞留するオイル油面が変動すると、第２収容部４４の前側の第１空間４７および第２空間４８のオイルは開口部４９を通して行き来することで、第１空間４７および後側の第２空間４８のオイルレベルＯＬを均一化することができる。このとき、開口部４９はオイルレベルＯＬよりもずっと低い位置にあるので、オイルが開口部４９を通過する際にエアを巻き込み難くして泡の発生を防止することができる。しかも開口部４９はファイナルドリブンギヤ２９の下端よりも上方に位置するので、中央ハウジング１６の底部を下方に膨らませることなく開口部４９を形成することが可能となり、モータハウジング１４の大型化が防止される。 When the oil oil level staying in the second storage portion 44 changes as the vehicle travels, the oil in the first space 47 and the second space 48 on the front side of the second storage portion 44 travels through the opening 49, The oil level OL of the first space 47 and the second space 48 on the rear side can be made uniform. At this time, since the opening 49 is at a position much lower than the oil level OL, it is difficult to entrain air when the oil passes through the opening 49, and generation of bubbles can be prevented. Moreover, since the opening 49 is located above the lower end of the final driven gear 29, the opening 49 can be formed without causing the bottom of the central housing 16 to bulge downward, and the motor housing 14 is prevented from being enlarged. The
　またオイルポンプ４５を収容する第１空間４７とファイナルドリブンギヤ２９を収容する第２空間４８との間に配置されるオイルガイド壁１６ｃはバッフルプレートとして機能し、ディファレンシャルギヤ１３の回転により発生する油面の波立ちを抑制し、オイルポンプ４５がエアを吸入するのを防止することができる。 The oil guide wall 16c disposed between the first space 47 that accommodates the oil pump 45 and the second space 48 that accommodates the final driven gear 29 functions as a baffle plate, and the oil surface generated by the rotation of the differential gear 13 The oil pump 45 can be prevented from sucking air.
　さらにファイナルドリブンギヤ２９の後下部に沿うようにオイルガイド壁１６ｃを配置したことで、ファイナルドリブンギヤ２９が掻き上げたオイルをオイルガイド壁１６ｃに沿って前方に供給し、右ハウジング１７の側壁１７ａのオイル収集凹部５０に供給することができる。 Further, by arranging the oil guide wall 16c along the rear lower portion of the final driven gear 29, the oil scooped up by the final driven gear 29 is supplied forward along the oil guide wall 16c, and the oil on the side wall 17a of the right housing 17 is supplied. The collecting recess 50 can be supplied.
　オイル収集凹部５０の後側傾斜壁５０ｃの第２傾斜角θ２は小さいため、オイルは後側傾斜壁５０ｃにスムーズに案内されて底壁５０ａに達し、そこで大きい第１傾斜角θ１を有する前側傾斜壁５０ｂに塞き止められることで、底壁５０ａに沿って径方向内側に流れ、ベアリング支持孔１７ｃを通過してディファレンシャルギヤ１３の右端部を右ハウジング１７に支持するアンギュラローラベアリング３２を潤滑する。このとき、オイル収集凹部５０の底壁５０ａの幅はアンギュラローラベアリング３２に向かって減少するので、オイル収集凹部５０で収集したオイルをアンギュラローラベアリング３２に指向させて効率的に供給することができる。 Since the second inclined angle θ2 of the rear inclined wall 50c of the oil collecting recess 50 is small, the oil is smoothly guided to the rear inclined wall 50c and reaches the bottom wall 50a, where the front inclined having a large first inclined angle θ1. By being blocked by the wall 50b, the angular roller bearing 32 that flows radially inward along the bottom wall 50a, passes through the bearing support hole 17c, and supports the right end of the differential gear 13 to the right housing 17 is lubricated. . At this time, since the width of the bottom wall 50a of the oil collecting recess 50 decreases toward the angular roller bearing 32, the oil collected in the oil collecting recess 50 can be efficiently directed to the angular roller bearing 32. .
　ディファレンシャルギヤ１３はモータハウジング１４の前部に配置されており、ファイナルドリブンギヤ２９がオイルガイド壁１６ｃに沿って掻き上げるオイルがアンギュラローラベアリング３２に供給される経路には、ファイナルドライブギヤ２８およびファイナルドリブンギヤ２９の噛合部３８（図２参照）が位置するため、その噛合部３８によってオイルの供給が阻害されてしまい、オイル収集凹部５０にオイルが届き難くなる可能性がある。 The differential gear 13 is disposed at the front portion of the motor housing 14, and the final drive gear 28 and the final driven gear are provided in a path through which the oil driven by the final driven gear 29 along the oil guide wall 16c is supplied to the angular roller bearing 32. Since the 29 meshing portions 38 (see FIG. 2) are located, the supply of oil is hindered by the meshing portions 38, and the oil may not easily reach the oil collecting recess 50.
　しかしながら、本実施の形態によれば、オイル収集凹部５０によってオイルを積極的に収集してアンギュラローラベアリング３２に供給するので、ファイナルドライブギヤ２８およびファイナルドリブンギヤ２９の噛合部３８によってオイルの供給が阻害されても、それを補ってアンギュラローラベアリング３２に必要な量のオイルを供給することができる。 However, according to the present embodiment, since oil is actively collected by the oil collecting recess 50 and supplied to the angular roller bearing 32, the supply of oil is obstructed by the meshing portion 38 of the final drive gear 28 and the final driven gear 29. Even if this is done, the required amount of oil can be supplied to the angular roller bearing 32 in addition to that.
　またモータハウジング１４の第１収容部４３および第２収容部４４はオイルレベルＯＬよりも低い連通孔１６ｂで連通しており、電動モータ１１を潤滑・冷却するために第２収容部４４のオイルが第１収容部４３に流出し、第２収容部４４のオイル量が減少しても、オイル収集凹部５０によるオイルの収集効果により、補ってオイル量の減少をアンギュラローラベアリング３２に必要な量のオイルを供給することができる。 The first housing portion 43 and the second housing portion 44 of the motor housing 14 communicate with each other through a communication hole 16b lower than the oil level OL, and the oil in the second housing portion 44 is used to lubricate and cool the electric motor 11. Even if the amount of oil in the second storage portion 44 decreases after flowing into the first storage portion 43, the amount of oil necessary for the angular roller bearing 32 is compensated for by the oil collection effect of the oil collection recess 50. Oil can be supplied.
　図５（Ａ）は、車両が想定される最大登坂角δで登坂するときの状態を示している。この場合、モータハウジング１４は前上がりに傾斜するため、オイル収集凹部５０の後側傾斜壁５０ｃの後縁である傾斜開始線５０ｅも後方に傾斜するが、その傾斜開始線５０ｅが水平方向後方と成す角度αは９０°以上に設定される。これにより、車両が想定される最大登坂角δで登坂する場合であっても、重力で下向きに付勢されるオイルをオイル収集凹部５０に確実に導入することができる。 FIG. 5 (A) shows a state where the vehicle climbs at the maximum possible climb angle δ. In this case, since the motor housing 14 is tilted upward, the tilt start line 50e, which is the rear edge of the rear inclined wall 50c of the oil collecting recess 50, is also tilted rearward, but the tilt start line 50e is rearward in the horizontal direction. The formed angle α is set to 90 ° or more. Thus, even when the vehicle climbs at the assumed maximum climb angle δ, it is possible to reliably introduce oil urged downward by gravity into the oil collecting recess 50.
　図５（Ｂ）は、車両が想定される最大降坂角δで降坂するときの状態を示している。この場合、モータハウジング１４は前下がりに傾斜するため、オイル収集凹部５０の前側傾斜壁５０ｂの前縁である傾斜開始線５０ｄも前方に傾斜するが、その傾斜開始線５０ｄが水平方向後方と成す角度βは１７０°以下に設定される。これにより、車両が想定される最大降坂角δで降坂する場合であっても、オイル収集凹部５０の前側傾斜壁５０ｂがアンギュラローラベアリング３２に向かって１０゜以上の下り傾斜になり、オイル収集凹部５０に収集したオイルをスムーズにアンギュラローラベアリング３２に供給することができる。 FIG. 5B shows a state where the vehicle descends at the assumed maximum descending angle δ. In this case, since the motor housing 14 is inclined forward and downward, the inclination start line 50d that is the front edge of the front inclined wall 50b of the oil collecting recess 50 is also inclined forward, but the inclination start line 50d forms the rear in the horizontal direction. The angle β is set to 170 ° or less. Thus, even when the vehicle descends at the assumed maximum descending angle δ, the front inclined wall 50b of the oil collecting recess 50 is inclined downward by 10 ° or more toward the angular roller bearing 32, and the oil collecting The oil collected in the recess 50 can be smoothly supplied to the angular roller bearing 32.
　以上、本発明の実施の形態を説明したが、本発明はその要旨を逸脱しない範囲で種々の設計変更を行うことが可能である。 Although the embodiments of the present invention have been described above, various design changes can be made without departing from the scope of the present invention.
　例えば、本発明のベアリングは実施の形態のアンギュラローラベアリング３２に限定されず、任意の種類のベアリングであっても良い。 For example, the bearing of the present invention is not limited to the angular roller bearing 32 of the embodiment, and may be any type of bearing.
　また本発明の駆動源は実施の形態の電動モータ１１に限定されず、エンジンのような他種の駆動源であっても良い。 The drive source of the present invention is not limited to the electric motor 11 of the embodiment, and may be another type of drive source such as an engine.

Claims (9)

  1. 　ギヤケース（１６，１７）と、前記ギヤケース（１６，１７）の前部に収納されたディファレンシャルギヤ（１３）と、前記ディファレンシャルギヤ（１３）を前記ギヤケース（１６，１７）の側壁（１７ａ）に支持するベアリング（３２）と、前記ディファレンシャルギヤ（１３）の外周に設けられたファイナルドリブンギヤ（２９）と、駆動源（１１）の駆動力を入力軸（２０）を介して前記ファイナルドリブンギヤ（２９）に伝達するファイナルドライブギヤ（２８）とを備え、前記ファイナルドリブンギヤ（２９）は前記入力軸（２０）に対して車両進行方向前方側に配置される車両用動力伝達装置であって、
    　前記ファイナルドリブンギヤ（２９）および前記ファイナルドライブギヤ（２８）の噛合部（３８）の前方の前記側壁（１７ａ）に、前記ギヤケース（１６，１７）の底部から前記ファイナルドリブンギヤ（２９）により掻き上げられたオイルを収集して前記ベアリング（３２）に供給するオイル収集凹部（５０）が設けられることを特徴とする車両用動力伝達装置。     The gear case (16, 17), the differential gear (13) housed in the front part of the gear case (16, 17), and the differential gear (13) are supported on the side wall (17a) of the gear case (16, 17). Bearing (32), a final driven gear (29) provided on the outer periphery of the differential gear (13), and a driving force of a drive source (11) to the final driven gear (29) via an input shaft (20). A final drive gear (28) for transmitting, and the final driven gear (29) is a vehicle power transmission device disposed on the front side in the vehicle traveling direction with respect to the input shaft (20),
    The final driven gear (29) is scraped from the bottom of the gear case (16, 17) to the side wall (17a) in front of the meshing portion (38) of the final driven gear (29) and the final drive gear (28). An oil collecting recess (50) for collecting the collected oil and supplying it to the bearing (32) is provided.
  2. 　前記ファイナルドリブンギヤ（２９）の後下部に沿うように配置されたオイルガイド壁（１６ｃ）を備え、前記噛合部（３８）は水平方向で前記オイル収集凹部（５０）と前記オイルガイド壁（１６ｃ）との間に位置することを特徴とする、請求項１に記載の車両用動力伝達装置。 An oil guide wall (16c) arranged along the rear lower part of the final driven gear (29) is provided, and the meshing part (38) is horizontally aligned with the oil collecting recess (50) and the oil guide wall (16c). The vehicle power transmission device according to claim 1, wherein the vehicle power transmission device is located between the two.
  3. 　前記ギヤケース（１６，１７）の下部に配置されたオイルポンプ（４５）を備え、前記オイルガイド壁（１６ｃ）は前記ファイナルドリブンギヤ（２９）を収容する第１空間（４７）と前記オイルポンプ（４５）を収容する第２空間（４８）との間に配置されることを特徴とする、請求項２に記載の車両用動力伝達装置。 An oil pump (45) is provided below the gear case (16, 17), and the oil guide wall (16c) includes a first space (47) for housing the final driven gear (29) and the oil pump (45). The vehicle power transmission device according to claim 2, wherein the vehicle power transmission device is disposed between the second space and the second space.
  4. 　前記ギヤケース（１６，１７）の底部に滞留するオイルの油面は前記オイルガイド壁（１６ｃ）の上端よりも下方に位置し、前記オイルガイド壁（１６ｃ）の下部に前記第１空間（４７）および前記第２空間（４８）を連通させる開口部（４９）が形成されることを特徴とする、請求項３に記載の車両用動力伝達装置。 The oil level of the oil staying at the bottom of the gear case (16, 17) is located below the upper end of the oil guide wall (16c), and the first space (47) is located below the oil guide wall (16c). 4. The vehicle power transmission device according to claim 3, wherein an opening (49) that communicates with the second space (48) is formed. 5.
  5. 　前記開口部（４９）は前記ファイナルドリブンギヤ（２９）の下端よりも上方に位置することを特徴とする、請求項４に記載の車両用動力伝達装置。 The vehicle power transmission device according to claim 4, wherein the opening (49) is located above a lower end of the final driven gear (29).
  6. 　内部に前記駆動源である電動モータ（１１）を収納するモータケース（１５）が前記ギヤケース（１６，１７）に結合され、前記モータケース（１５）の内部空間および前記ギヤケース（１６，１７）の内部空間を連通させる連通孔（１６ｂ）が該ギヤケース（１６，１７）の底部に滞留するオイルの油面よりも下方に形成されることを特徴とする、請求項１～請求項５の何れか１項に記載の車両用動力伝達装置。 A motor case (15) that houses the electric motor (11) as the drive source is coupled to the gear case (16, 17), and the internal space of the motor case (15) and the gear case (16, 17) The communication hole (16b) for communicating the internal space is formed below the oil level of the oil staying at the bottom of the gear case (16, 17). The vehicle power transmission device according to claim 1.
  7. 　前記ファイナルドリブンギヤ（２９）の中心よりも前方に配置された前記オイル収集凹部（５０）は、前記ベアリング（３２）に向かって径方向内向きに延びる底壁（５０ａ）と、前記底壁（５０ａ）の前側に連なって第１傾斜角（θ１）で傾斜する前側傾斜壁（５０ｂ）と、前記底壁（５０ａ）の後側に連なって第２傾斜角（θ２）で傾斜する後側傾斜壁（５０ｃ）とを有して溝状断面に形成され、前記第２傾斜角（θ２）は前記第１傾斜角（θ１）よりも小さいことを特徴とする、請求項１～請求項６の何れか１項に記載の車両用動力伝達装置。 The oil collecting recess (50) disposed in front of the center of the final driven gear (29) includes a bottom wall (50a) extending radially inward toward the bearing (32), and the bottom wall (50a). ) And the front inclined wall (50b) inclined at the first inclination angle (θ1) and the rear inclined wall connected to the rear side of the bottom wall (50a) and inclined at the second inclination angle (θ2). The first inclination angle (θ1) is smaller than the first inclination angle (θ1), and the second inclination angle (θ2) is smaller than the first inclination angle (θ1). The vehicle power transmission device according to claim 1.
  8. 　前記底壁（５０ａ）の幅は前記ベアリング（３２）に向かって減少することを特徴とする、請求項７に記載の車両用動力伝達装置。 The vehicle power transmission device according to claim 7, wherein the width of the bottom wall (50a) decreases toward the bearing (32).
  9. 　溝状断面の後縁を構成する前記後側傾斜壁（５０ｃ）の傾斜開始線（５０ｅ）が水平方向後方に対して成す角度（α）は、車両が最大登坂角で登坂するときに９０°以上となるように設定され、溝状断面の前縁を構成する前記前側傾斜壁（５０ｂ）の傾斜開始線（５０ｄ）が水平方向後方に対して成す角度（β）は、車両が最大降坂角で降坂するときに１７０°以下になるように設定されることを特徴とする、請求項７または請求項８に記載の車両用動力伝達装置。 The angle (α) formed by the inclination start line (50e) of the rear inclined wall (50c) constituting the rear edge of the groove-shaped cross section with respect to the rear in the horizontal direction is 90 ° when the vehicle climbs at the maximum climb angle. The angle (β) formed by the inclination start line (50d) of the front inclined wall (50b) constituting the front edge of the groove-shaped cross section with respect to the rear in the horizontal direction is the maximum downhill angle of the vehicle. The vehicle power transmission device according to claim 7, wherein the vehicle power transmission device is set to be 170 ° or less when descending at a slope.
PCT/JP2019/017458 2018-04-26 2019-04-24 Vehicle power transmission device WO2019208642A1 (en)

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JP2020515528A JP6923753B2 (en) 2018-04-26 2019-04-24 Vehicle power transmission device
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CN112020618A (en) 2020-12-01

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