WO2015079758A1 - Lubrication structure and lubrication method - Google Patents

Lubrication structure and lubrication method Download PDF

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Publication number
WO2015079758A1
WO2015079758A1 PCT/JP2014/072463 JP2014072463W WO2015079758A1 WO 2015079758 A1 WO2015079758 A1 WO 2015079758A1 JP 2014072463 W JP2014072463 W JP 2014072463W WO 2015079758 A1 WO2015079758 A1 WO 2015079758A1
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WO
WIPO (PCT)
Prior art keywords
rotating body
hole
lubricating oil
inner hole
shaft
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PCT/JP2014/072463
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French (fr)
Japanese (ja)
Inventor
清仁 細野
博仁 櫻井
佐藤　和彦
Original Assignee
愛知機械工業株式会社
清仁 細野
博仁 櫻井
佐藤　和彦
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Application filed by 愛知機械工業株式会社, 清仁 細野, 博仁 櫻井, 佐藤　和彦 filed Critical 愛知機械工業株式会社
Publication of WO2015079758A1 publication Critical patent/WO2015079758A1/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
    • F16H57/0457—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
    • F16H57/042—Guidance of lubricant
    • F16H57/043—Guidance of lubricant within rotary parts, e.g. axial channels or radial openings in shafts
    • F16H57/0431—Means for guiding lubricant directly onto a tooth surface or to foot areas of a gear, e.g. by holes or grooves in a tooth flank

Definitions

  • the present invention relates to a lubricating structure for supplying lubricating oil to an inner hole of a rotating body having an inner hole.
  • Japanese Patent Application No. 2013-245971 filed on November 28, 2013 is referred to as a related application, and the entire contents thereof are used as a citation by reference.
  • Japanese Utility Model Laid-Open No. 61-85767 discloses a speed change comprising a main drive shaft rotatably supported by a casing, and a main shaft rotatably supported by a shaft inner hole of the main drive shaft via a needle bearing.
  • the machine is disclosed.
  • a radial hole penetrating the shaft inner hole is formed in the main drive shaft, and an oil plate is provided at a position corresponding to the radial hole of the main drive shaft, thereby Is used to supply the lubricating oil present in the shaft hole to the inner shaft hole, that is, the needle bearing, through the radial hole by the oil plate.
  • the oil plate is provided only for the purpose of feeding the lubricating oil to the needle bearing, so it cannot be said that it is a rational component configuration. Even if the oil plate is provided, the lubricating oil cannot be efficiently supplied to the needle bearing due to the centrifugal force generated with the rotation of the main drive shaft.
  • the present invention has been made in view of the above, and an object thereof is to provide a rational lubrication structure capable of efficiently supplying lubricating oil to the inner hole of a rotating body.
  • the first rotating body having an inner hole and a second rotating body that performs rotation corresponding to the rotation of the first rotating body are provided.
  • at least part of the lubricating oil along the locus of the lubricating oil when viewed from the rotating first rotating body is introduced into the inner hole among the lubricating oil that is scraped up and scattered by the second rotating body. It is configured as follows.
  • “perform the rotation corresponding to the rotation of the first rotating body” typically corresponds to an aspect in which the second rotating body is rotated based on the rotation of the first rotating body.
  • a mode in which the first rotating body is rotated based on the rotation of the second rotating body is suitably included.
  • the second rotating body or the first rotating body is rotated based on the rotation of the first rotating body or the second rotating body
  • the second rotating body or the first rotating body is the first rotating body or
  • a mode in which the second rotating body or the first rotating body is indirectly rotated by the first rotating body or the second rotating body is included.
  • the lubricating oil that is scraped and scattered by the second rotating body has a locus along the tangential direction of the outer peripheral surface of the second rotating body when viewed from a stationary reference point. When viewed from the first rotating body, it has a locus along a predetermined curve. According to the present invention, among the lubricating oil that is scraped up and scattered by the second rotating body, at least a part of the lubricating oil along the locus along the predetermined curve is introduced into the inner hole. .
  • the locus along the predetermined curve is the locus (relative locus) of the lubricating oil when viewed from the rotating first rotating body. For this reason, the lubricating oil which is scraped up and scattered by the second rotating body can be efficiently supplied to the inner hole of the first rotating body.
  • the first rotating body is formed with a through-hole penetrating from the outer peripheral surface of the first rotating body to the inner hole.
  • the through-hole is comprised along a relative locus.
  • the relative locus is a locus of the lubricating oil when viewed from the rotating first rotating body.
  • the through hole has a center line that is offset from the radial direction line of the first rotating body to the rear in the rotational direction of the first rotating body.
  • the configuration is only to form a through hole having a center line that is offset rearward in the rotational direction of the rotating body with respect to the radial line of the rotating body, it is scraped up by the second rotating body. Therefore, it is possible to easily realize a configuration that follows the relative trajectory of the lubricating oil scattered.
  • the first rotating body has a first rotating shaft and a first gear provided on the first rotating shaft.
  • the second rotating body includes a second rotating shaft that is arranged in parallel to the first rotating shaft, and a second gear that is provided on the second rotating shaft and meshes with the first gear. And the through-hole is formed in the 1st rotating shaft.
  • the through hole is formed in the first rotating shaft. Therefore, it is easier to configure the through hole so as to follow the locus of the lubricating oil that scatters as compared to the configuration in which the first gear is formed with the through hole. Further, the spattered lubricating oil is not inhibited from entering the through hole by the tooth surface of the first gear. Accordingly, even when the first rotating body or the second rotating body has the first rotating shaft, the second rotating shaft, the first gear, or the second gear, the lubricating oil can be rationally and efficiently provided. Can be supplied to the inner hole.
  • the through hole is formed adjacent to the first gear.
  • the second gear is configured to overlap the through hole in the axial direction.
  • the second gear is configured to overlap the through hole in the axial direction, the lubricating oil can be directly scraped up toward the through hole. Thereby, the lubricating oil can be supplied more efficiently to the inner hole through the through hole.
  • the lubrication structure further includes a third rotating body supported rotatably in the inner hole via the bearing member. And it is comprised so that the lubricating oil which is scraped up and scattered by the 2nd rotary body may be supplied to a bearing member through a through-hole.
  • the bearing member disposed at a position where it is difficult to supply the lubricating oil it is possible to efficiently supply the lubricating oil to the bearing member disposed at a position where it is difficult to supply the lubricating oil.
  • an input reduction type transmission that includes an input shaft and an output shaft that is supported so as to be relatively rotatable via a pilot bearing inside the input shaft
  • the input shaft rotates in response to the rotation of the input shaft.
  • Lubricating oil that is scraped up and scattered by a rotating body (such as a gear) on the counter shaft can be efficiently supplied to the pilot bearing through a through hole formed in the input shaft.
  • an output reduction type transmission that includes an input shaft and an output shaft that supports the input shaft so as to be relatively rotatable via a pilot bearing
  • the output shaft rotates in accordance with the rotation of the input shaft.
  • Lubricating oil that is scraped and scattered by a rotating body (such as a gear) on the counter shaft can be efficiently supplied to the pilot bearing through a through hole formed in the output shaft.
  • an input shaft having an inner hole, a reduction drive gear provided on the input shaft, a counter shaft arranged in parallel with the input shaft, and provided on the counter shaft.
  • a reduction driven gear that meshes with the reduction drive gear, and an output shaft that is rotatably supported in the inner hole via a bearing member.
  • the said transmission is comprised so that the lubricating oil which is scraped up and scattered by the speed reduction driven gear may be supplied to an inner hole using the lubricating structure which concerns on this invention of the aspect mentioned above.
  • the lubricating oil is supplied to the inner hole using the lubricating structure according to the present invention in any one of the aspects described above, the same effects as the effects exhibited by the lubricating structure of the present invention, for example, For example, it is possible to provide a reasonable lubricating structure capable of efficiently supplying lubricating oil to the inner hole.
  • an input shaft having an inner hole, a drive gear provided on the input shaft, a counter shaft arranged in parallel with the input shaft, and a drive provided on the counter shaft.
  • a driven gear that meshes with the gear, an output drive gear that is provided on the counter shaft, an output shaft that is rotatably supported in the inner hole via a bearing member, and an output that is provided on the output shaft and meshes with the output drive gear And a driven gear.
  • the said transmission is comprised so that the lubricating oil which is scraped up and scattered by an output drive gear may be supplied to an inner hole using the lubricating structure which concerns on this invention of the aspect mentioned above.
  • the lubricating oil is supplied to the inner hole using the lubricating structure according to the present invention in any one of the aspects described above, the same effects as the effects exhibited by the lubricating structure of the present invention, for example, For example, it is possible to provide a reasonable lubricating structure capable of efficiently supplying lubricating oil to the inner hole.
  • the first rotating body having the inner hole and the second rotating body that performs rotation corresponding to the rotation of the first rotating body are provided, and the second rotating body
  • a lubrication method for supplying the scraped lubricating oil to the inner hole is configured.
  • a through hole that penetrates from the outer peripheral surface of the rotating body to the inner hole is formed in the rotating body. Then, the lubricating oil scraped up and scattered by the second rotating body is captured by the through hole and supplied to the inner hole.
  • the lubricating oil that is scooped up and scattered by the second rotating body is captured by the through hole and supplied to the inner hole, the lubricating oil that is scooped up and scattered by the second rotating body is And can be efficiently supplied to the inner hole of the first rotating body through the through hole.
  • a dedicated part for supplying lubricating oil to the inner hole of the first rotating body is unnecessary, the number of parts can be reduced, which is reasonable.
  • FIG. 3 is a sectional view taken along line XX in FIG. 2. It is explanatory drawing which shows the locus
  • 4 is an explanatory diagram showing a relative locus obtained by converting a locus of lubricating oil that can reach the inner hole 2b of the input shaft 2 into a rotational coordinate system in the input shaft 2.
  • FIG. It is explanatory drawing which shows a mode that the lubricating oil which is scraped up and scattered by the reduction driven gear RG 'is supplied to the inner hole 2b of the input shaft 2 through the through-hole 2c.
  • the transmission 1 includes an input shaft 2, an output shaft 6, a reduction gear mechanism GM, a speed change mechanism TM, and a casing 8.
  • lubricating oil for lubricating the components of the transmission 1 is stored in the casing 8.
  • the input shaft 2 corresponds to the “first rotating body”, “first rotating shaft”, and “input shaft” in the present invention
  • the counter shaft 4 corresponds to the “second rotating body”, “second rotating shaft” in the present invention.
  • the output shaft 6 is an example of an implementation configuration corresponding to the “third rotating body” and the “output shaft” in the present invention.
  • the side (lower side in FIG. 1) on which the input shaft 2 is arranged in the major axis direction of the transmission 1 is defined as “front side” or “front”, and the output shaft 6 1 is defined as “rear side” or “rearward”.
  • the input shaft 2 is a shaft to which power of an engine (not shown) is input via a clutch (not shown).
  • the input shaft 2 is rotatably supported by the casing 8 via a bearing B1.
  • the rear portion of the input shaft 2 (the portion opposite to the side where the clutch is disposed) is configured as a hollow portion in which an inner hole 2b is formed.
  • a reduction drive gear RG is integrally formed at the rear end portion of the input shaft 2.
  • the reduction drive gear RG is an example of an implementation configuration corresponding to the “rotor”, the “first gear”, and the “reduction drive gear” in the present invention.
  • the input shaft 2 has a diameter-expanded portion 2a on the front side (the side where the clutch is disposed) from the reduction drive gear RG.
  • the diameter-expanded portion 2a is diameter-expanded more in the radial direction than the other portion of the input shaft 2.
  • the input shaft 2 is positioned in the axial direction by bringing the front end face of the enlarged diameter portion 2a into contact with the bearing B1.
  • a through hole 2c penetrating from the outer peripheral surface to the inner hole 2b is formed in the enlarged diameter portion 2a.
  • three through holes 2 c are formed at equal intervals (120 ° intervals) in the circumferential direction.
  • the through-hole 2c is a rear side in the rotational direction of the input shaft 2 with respect to each of the virtual radial direction lines RL of the three input shafts 2 arbitrarily drawn so as to have a central angle of 120 ° from the center CP of the input shaft 2.
  • the center line CL is offset to the center line CL.
  • the offset amount is set to a value such that the through-hole 2c follows the relative locus of the lubricating oil that is scraped up by a reduction driven gear RG 'described later. Details of the setting of the through hole 2c will be described later.
  • the through hole 2c corresponds to the “through hole” in the present invention, and the virtual radial line RL is an example of an implementation configuration corresponding to the “radial line” in the present invention.
  • the aspect in which the through hole 2c has the center line CL that is offset to the rear side in the rotation direction of the input shaft 2 with respect to the virtual radial direction line RL of the input shaft 2 is " It is an example of the implementation structure corresponding to "having the center line offset in the rotation direction back of the rotary body with respect to the radial direction line.”
  • the counter shaft 4 is arranged in parallel to the input shaft 2 as shown in FIG.
  • the counter shaft 4 is rotatably supported by the casing 8 at the front end portion and the rear end portion via bearings B2 and B3.
  • a reduction driven gear RG ′ is integrally formed at the front end portion of the counter shaft 4.
  • the reduction driven gear RG ' meshes with the reduction drive gear RG.
  • the tooth width of the reduction driven gear RG ' is formed larger than the tooth width of the reduction drive gear RG as shown in FIG. Specifically, the tooth width of the reduction driven gear RG ′ is such that the reduction driven gear RG ′ protrudes further toward the bearing B1 (front side) than the reduction drive gear RG when the input shaft 2 and the counter shaft 4 are assembled to the casing 8. Is configured to do.
  • the reduction driven gear RG ′ is configured to overlap in the axial direction with respect to the through hole 2 c in the enlarged diameter portion 2 a of the input shaft 2.
  • the reduction driven gear RG ' is configured to overlap the through hole 2c in the axial direction, the lubricating oil can be directly scraped up toward the through hole 2c.
  • a reduction gear mechanism GM is constituted by the reduction driven gear RG 'and the reduction drive gear RG.
  • the input shaft 2 and the counter shaft 4 are connected by the reduction gear mechanism GM.
  • the power input to the input shaft 2 is transmitted to the counter shaft 4 by the reduction gear mechanism GM.
  • the reduction driven gear RG ' is an example of an implementation configuration corresponding to the "second rotating body”, “second gear”, and “deceleration driven gear” in the present invention.
  • the aspect in which the reduction driven gear RG ′ overlaps the through hole 2c in the enlarged diameter portion 2a of the input shaft 2 in the axial direction is “the second gear overlaps the through hole in the axial direction” in the present invention. It is an example of the implementation structure corresponding to an aspect.
  • the output shaft 6 is arranged coaxially with the input shaft 2 as shown in FIG.
  • the output shaft 6 is a shaft for outputting power.
  • One end of the output shaft 6 is rotatably supported in the inner hole 2b of the input shaft 2 via a pilot bearing PB.
  • the other end of the output shaft 6 is rotatably supported by the casing 8 via a bearing B4.
  • the pilot bearing PB is disposed inside the reduction drive gear RG as shown in FIG. That is, the pilot bearing PB is disposed such that the front end portion in the axial direction is adjacent to the through hole 2c. As shown in FIG. 2, the reduction drive gear RG is formed with a through hole 2d penetrating from the tooth bottom surface to the inner hole 2b.
  • the pilot bearing PB is an example of an implementation configuration corresponding to the “bearing member” in the present invention.
  • the speed change mechanism TM includes a plurality of drive gears G, a plurality of driven gears G ′, and a plurality of synchronizers S.
  • the plurality of drive gears G are provided on the counter shaft 4.
  • the plurality of driven gears G ′ are provided on the output shaft 6 so as to mesh with the drive gear G.
  • the synchronizer S selectively fixes, to the counter shaft 4 or the output shaft 6, a gear provided so as to be rotatable relative to the counter shaft 4 or the output shaft 6 among the driving gear G and the driven gear G ′.
  • the input shaft 2 or the counter shaft 4 and the output shaft 6 are connected by the speed change mechanism TM.
  • the power transmitted to the counter shaft 4 is output to the output shaft 6 through the speed change mechanism TM.
  • the locus of the lubricating oil scraped up by the reduction driven gear RG ′ is a straight line along the tangential direction of the reduction driven gear RG ′.
  • the lubricating oil scraped up and scattered by the reduction driven gear RG ′ it was released in the range from the point P1 (position of the rotation angle ⁇ 1) to the point P2 (position of the rotation angle ⁇ 2) on the circumference of the reduction driven gear RG ′.
  • the lubricating oil can reach the inner hole 2 b of the input shaft 2.
  • the locus of the lubricating oil that can reach the inner hole 2b of the input shaft 2 is the outer peripheral surface of the reduction driven gear RG ′ as shown in FIG.
  • the inner hole 2b of the input shaft 2 exist in a range from the common outer tangent line EL to the common inner tangent line IL. If the lubricating oil having a locus in the range is captured, the lubricating oil can be efficiently supplied to the inner hole 2b.
  • the locus of the lubricating oil swung up by the reduction driven gear RG ′ when viewed from the input shaft 2, that is, the relative locus, has a curved shape as shown in FIG. 5. Eggplant.
  • the relative locus of the lubricating oil having the curved shape can be obtained by converting the linear lubricating oil locus along the tangential direction of the reduction driven gear RG ′ shown in FIG. 4 into the rotational coordinate system of the input shaft 2.
  • the linear relative trajectory is determined if the gear diameter of the reduction driven gear RG ′, the center-to-center distance between the input shaft 2 and the counter shaft 4 and the gear ratio of the reduction drive gear RG and the reduction driven gear RG ′ are determined. It is uniquely determined regardless of the rotational speed of the input shaft 2.
  • the through hole 2 c is formed of lubricating oil existing in a range from the common outer tangent line EL to the common inner tangent line IL between the outer peripheral surface of the reduction driven gear RG ′ and the inner hole 2 b of the input shaft 2.
  • the locus LC solid line in FIG. 4
  • the locus LC ′ solid line in FIG. 5
  • the center line CL of the through hole 2c is offset to the rear side in the rotation direction of the input shaft 2 (thick arrow in FIG. 3) with respect to the virtual radial direction line RL of the input shaft 2, as shown in FIG. Will be present at that position.
  • the lubricating oil that is scraped up and scattered by the reduction driven gear RG ' has a curved relative locus as shown in FIG.
  • the through hole 2c formed in the input shaft 2 has a configuration along the curved relative trajectory, so that the lubricating oil that is scraped and scattered by the reduction driven gear RG ′ can be efficiently used. It can be captured by the through hole 2c and taken into the inner hole 2b.
  • the relative locus of the lubricating oil is determined by determining the gear diameter of the reduction driven gear RG ′, the distance between the centers of the input shaft 2 and the counter shaft 4 and the gear ratio of the reduction drive gear RG and the reduction driven gear RG ′. Since it is uniquely determined regardless of the rotation speed of the shaft 2, the capture of the lubricating oil by the through hole 2 c and the supply of the lubricating oil to the inner hole 2 b through the through hole 2 c depend on the rotation speed of the input shaft 2. There is nothing to do.
  • the aspect in which the lubricating oil that is scooped up and scattered by the reduction driven gear RG ′ is captured by the through hole 2c and taken into the inner hole 2b is “the lubricating oil that is scooped up and scattered by the second rotating body” It is an example of the implementation structure corresponding to "capturing and supplying to an inner hole.”
  • the input hole 2c formed in the input shaft 2 follows the relative locus of the lubricating oil that is scraped and scattered by the reduction driven gear RG ′.
  • the center line CL is offset to the rear side in the rotation direction of the input shaft 2 with respect to the virtual radial direction line RL of the shaft 2.
  • the through hole 2c is formed in the enlarged diameter portion 2a of the input shaft 2.
  • the reduction driven gear RG ' is configured to overlap the through hole 2c in the enlarged diameter portion 2a of the input shaft 2 in the axial direction.
  • lubricating oil can be directly scraped up toward the through-hole 2c.
  • the through hole 2c is set on the relative locus LC ′ (solid line in FIG. 5) obtained by converting the locus LC of the lubricating oil passing through to the rotational coordinate system of the input shaft 2. It is good also as a structure which sets the through-hole 2c on the relative locus
  • the center CP of the input shaft 2 is obtained. It is good also as a structure which sets a through-hole also on the relative locus calculated
  • the line in which the relative locus of the scattered lubricating oil crosses the section perpendicular to the axis of the input shaft 2 is linearly approximated as the center line CL of the through hole 2c. It is good also as a structure which makes the center line CL of the through-hole 2c the shape (curve
  • the three through holes 2c are formed in the circumferential direction of the enlarged diameter portion 2a in the input shaft 2, but the number of the through holes 2c is not limited thereto.
  • it is good also as a structure which forms the through-hole 2c only in one place in the enlarged diameter part 2a.
  • it does not necessarily need to form in the circumferential direction at equal intervals.
  • the through hole 2c is configured to be formed at only one location in the axial direction of the enlarged diameter portion 2a in the input shaft 2, but the through hole 2c is formed at two or more locations in the axial direction of the enlarged diameter portion 2a. It is good also as a structure.
  • the configuration is applied to the lubrication of the pilot bearing PB in the transmission 1, but the present invention is not limited to this.
  • it may be configured to apply lubrication to the bearing or the synchro mechanism S that rotatably supports the idle gear of the driven gear G ′ via the inner hole 2 b of the input shaft 2.
  • a through hole penetrating in the radial direction toward the bearing or the synchro mechanism S is formed from the inner hole 2b of the input shaft 2 or the inner hole formed in the output shaft 6 so as to communicate with the inner hole 2b. What is necessary is just to be the structure to do.
  • the configuration is applied to the transmission 1, but is not limited thereto.
  • the present invention can be applied to an apparatus or a mechanism that needs to supply lubricating oil to the inner hole of the rotating body.

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Abstract

Provided is a streamlined lubrication structure that can efficiently supply lubricating oil to an inner hole of a rotating body. The lubricating structure is configured so that lubricating oil that is scraped up and projected by a reduction-driven gear (RG') is supplied to the interior of an inner hole (2b) of an input shaft (2) via a through-hole (2c) formed in the input shaft (2). The through-hole (2c) is configured so as to have a center line (CL) that is offset counter to the direction of rotation of the input shaft (2) with respect to a virtual radius line (RL) of the input shaft (2), so as to follow the relative trajectory of the projected lubricating oil. Due to this configuration, projected lubricating oil can be efficiently drawn into the interior of the inner hole (2b) of the input shaft (2) via the through-hole (2c). Moreover, the lubrication structure is streamlined, in that the number of components can be reduced in comparison with conventional structures that require specialized components solely for supplying lubricating oil to the interior of the inner hole (2b).

Description

潤滑構造および潤滑方法Lubrication structure and lubrication method
　本発明は、内孔を有する回転体の当該内孔に潤滑油を供給するための潤滑構造に関する。 The present invention relates to a lubricating structure for supplying lubricating oil to an inner hole of a rotating body having an inner hole.
　２０１３年１１月２８日に出願された特願２０１３－２４５９７１号が、関連出願の参照とされ、その内容全体が参照による引用として用いられる。 Japanese Patent Application No. 2013-245971 filed on November 28, 2013 is referred to as a related application, and the entire contents thereof are used as a citation by reference.
　実開昭６１－８５７６７号公報は、ケーシングに回転可能に支持されたメインドライブシャフトと、当該メインドライブシャフトの軸内孔にニードルベアリングを介して回転可能に支持されたメインシャフトと、を備える変速機を開示している。当該公報に記載の変速機は、軸内孔に貫通する径方向孔をメインドライブシャフトに形成すると共に、メインドライブシャフトの径方向孔に対応した位置にオイルプレートを設けることによって、メインドライブシャフト周辺に存在する潤滑油を、オイルプレートにより径方向孔を介して軸内孔、即ち、ニードルベアリングに供給する潤滑構造を採用している。 Japanese Utility Model Laid-Open No. 61-85767 discloses a speed change comprising a main drive shaft rotatably supported by a casing, and a main shaft rotatably supported by a shaft inner hole of the main drive shaft via a needle bearing. The machine is disclosed. In the transmission described in the publication, a radial hole penetrating the shaft inner hole is formed in the main drive shaft, and an oil plate is provided at a position corresponding to the radial hole of the main drive shaft, thereby Is used to supply the lubricating oil present in the shaft hole to the inner shaft hole, that is, the needle bearing, through the radial hole by the oil plate.
実開昭６１－８５７６７号公報Japanese Utility Model Publication No. 61-85767
　しかしながら、上述した潤滑構造では、ニードルベアリングに潤滑油を送り込むためだけの目的でオイルプレートを設ける構成であるため、合理的な部品構成とは言えない。また、当該オイルプレートを設けたとしても、メインドライブシャフトの回転に伴って生ずる遠心力によって、ニードルベアリングに効率的に潤滑油を供給することができない。 However, in the above-described lubrication structure, the oil plate is provided only for the purpose of feeding the lubricating oil to the needle bearing, so it cannot be said that it is a rational component configuration. Even if the oil plate is provided, the lubricating oil cannot be efficiently supplied to the needle bearing due to the centrifugal force generated with the rotation of the main drive shaft.
　本発明は、上記に鑑みてなされたものであり、回転体の内孔に潤滑油を効率的に供給可能な合理的な潤滑構造を提供することを目的とする。 The present invention has been made in view of the above, and an object thereof is to provide a rational lubrication structure capable of efficiently supplying lubricating oil to the inner hole of a rotating body.
　上記課題を解決するため、本発明の潤滑構造の好ましい形態によれば、内孔を有する第１回転体と、当該第１回転体の回転に対応した回転を行う第２回転体と、を備え、第２回転体によって掻き上げられた潤滑油を内孔に供給する潤滑構造が構成される。当該潤滑構造では、第２回転体によって掻き上げられて飛散する潤滑油のうち、回転する第１回転体から見た際の潤滑油の軌跡に沿う潤滑油の少なくとも一部を内孔に導入するように構成されている。 In order to solve the above problems, according to a preferred embodiment of the lubricating structure of the present invention, the first rotating body having an inner hole and a second rotating body that performs rotation corresponding to the rotation of the first rotating body are provided. A lubricating structure for supplying the lubricating oil scraped up by the second rotating body to the inner hole is configured. In the lubricating structure, at least part of the lubricating oil along the locus of the lubricating oil when viewed from the rotating first rotating body is introduced into the inner hole among the lubricating oil that is scraped up and scattered by the second rotating body. It is configured as follows.
　本発明における「第１回転体の回転に対応した回転を行う」とは、典型的には、第１回転体の回転に基づいて第２回転体が回転される態様がこれに該当するが、第２回転体の回転に基づいて第１回転体が回転される態様を好適に包含する。なお、第２回転体または第１回転体が、第１回転体または第２回転体の回転に基づいて回転される態様としては、第２回転体または第１回転体が、第１回転体または第２回転体によって直接回転される態様の他、第２回転体または第１回転体が、第１回転体または第２回転体によって間接的に回転される態様を包含する。 In the present invention, “perform the rotation corresponding to the rotation of the first rotating body” typically corresponds to an aspect in which the second rotating body is rotated based on the rotation of the first rotating body. A mode in which the first rotating body is rotated based on the rotation of the second rotating body is suitably included. In addition, as an aspect in which the second rotating body or the first rotating body is rotated based on the rotation of the first rotating body or the second rotating body, the second rotating body or the first rotating body is the first rotating body or In addition to a mode in which the second rotating body is directly rotated, a mode in which the second rotating body or the first rotating body is indirectly rotated by the first rotating body or the second rotating body is included.
　第２回転体に掻き上げられて飛散する潤滑油は、静止している基準点から見た場合には、第２回転体の外周面の接線方向に沿った軌跡を有することになるが、回転する第１回転体から見た場合には、所定の曲線に沿った軌跡を有する。本発明によれば、第２回転体によって掻き上げられて飛散する潤滑油のうち、当該所定の曲線に沿った軌跡に沿う潤滑油の少なくとも一部を内孔に導入するように構成されている。なお、所定の曲線に沿った軌跡とは、回転する第１回転体から見た際の潤滑油の軌跡（相対軌跡）である。このため、第２回転体によって掻き上げられて飛散する潤滑油を、効率良く第１回転体の内孔に供給することができる。 The lubricating oil that is scraped and scattered by the second rotating body has a locus along the tangential direction of the outer peripheral surface of the second rotating body when viewed from a stationary reference point. When viewed from the first rotating body, it has a locus along a predetermined curve. According to the present invention, among the lubricating oil that is scraped up and scattered by the second rotating body, at least a part of the lubricating oil along the locus along the predetermined curve is introduced into the inner hole. . The locus along the predetermined curve is the locus (relative locus) of the lubricating oil when viewed from the rotating first rotating body. For this reason, the lubricating oil which is scraped up and scattered by the second rotating body can be efficiently supplied to the inner hole of the first rotating body.
　本発明に係る潤滑構造の更なる形態によれば、第１回転体には、当該第１回転体の外周面から内孔まで貫通する貫通孔が形成されている。そして、貫通孔は、相対軌跡に沿うよう構成されている。なお、相対軌跡とは、回転する第１回転体から見た際の潤滑油の軌跡である。 According to the further form of the lubricating structure according to the present invention, the first rotating body is formed with a through-hole penetrating from the outer peripheral surface of the first rotating body to the inner hole. And the through-hole is comprised along a relative locus. The relative locus is a locus of the lubricating oil when viewed from the rotating first rotating body.
　本形態によれば、第２回転体によって掻き上げられて飛散する潤滑油を、貫通孔を介して効率良く第１回転体の内孔に供給することができる。しかも、第１回転体の内孔に潤滑油を供給するためだけの専用部品が不要であるため、部品点数の削減も図ることができ、合理的である。 According to this embodiment, it is possible to efficiently supply the lubricating oil scraped up and scattered by the second rotating body to the inner hole of the first rotating body through the through hole. In addition, since a dedicated part for supplying lubricating oil to the inner hole of the first rotating body is not required, the number of parts can be reduced, which is reasonable.
　本発明に係る潤滑構造の更なる形態によれば、貫通孔は、第１回転体の径方向線に対して、当該第１回転体の回転方向後方にオフセットした中心線を有する構成とされている。 According to the further form of the lubrication structure according to the present invention, the through hole has a center line that is offset from the radial direction line of the first rotating body to the rear in the rotational direction of the first rotating body. Yes.
　本形態によれば、回転体の径方向線に対して、当該回転体の回転方向後方にオフセットした中心線を有する貫通孔を形成するのみの構成であるため、第２回転体によって掻き上げられて飛散する潤滑油の相対軌跡に沿うような構成を容易に実現することができる。 According to this embodiment, since the configuration is only to form a through hole having a center line that is offset rearward in the rotational direction of the rotating body with respect to the radial line of the rotating body, it is scraped up by the second rotating body. Therefore, it is possible to easily realize a configuration that follows the relative trajectory of the lubricating oil scattered.
　本発明に係る潤滑構造の更なる形態によれば、第１回転体は、第１回転軸と、当該第１回転軸に設けられた第１歯車と、を有している。また、第２回転体は、第１回転軸に平行配置された第２回転軸と、当該第２回転軸に設けられると共に第１歯車と噛み合う第２歯車と、を有している。そして、貫通孔は、第１回転軸に形成されている。 According to a further aspect of the lubricating structure according to the present invention, the first rotating body has a first rotating shaft and a first gear provided on the first rotating shaft. The second rotating body includes a second rotating shaft that is arranged in parallel to the first rotating shaft, and a second gear that is provided on the second rotating shaft and meshes with the first gear. And the through-hole is formed in the 1st rotating shaft.
　本形態によれば、第１回転体や第２回転体が、第１回転軸や第２回転軸および第１歯車や第２歯車を有する構成である場合には、貫通孔を第１回転軸に形成する構成であるため、第１歯車に当該貫通孔を形成する構成に比べて、飛散する潤滑油の軌跡に沿うように貫通孔を構成し易い。また、第１歯車の歯面等によって、飛散する潤滑油が貫通孔へ入り込むことを阻害されることもない。これにより、第１回転体や第２回転体が、第１回転軸や第２回転軸および第１歯車や第２歯車を有する構成である場合であっても、合理的かつ効率的に潤滑油を内孔に供給することができる。 According to this embodiment, when the first rotating body or the second rotating body has the first rotating shaft, the second rotating shaft, the first gear, or the second gear, the through hole is formed in the first rotating shaft. Therefore, it is easier to configure the through hole so as to follow the locus of the lubricating oil that scatters as compared to the configuration in which the first gear is formed with the through hole. Further, the spattered lubricating oil is not inhibited from entering the through hole by the tooth surface of the first gear. Accordingly, even when the first rotating body or the second rotating body has the first rotating shaft, the second rotating shaft, the first gear, or the second gear, the lubricating oil can be rationally and efficiently provided. Can be supplied to the inner hole.
　本発明に係る潤滑構造の更なる形態によれば、貫通孔は、第１歯車に隣接して形成されている。そして、第２歯車は、貫通孔と軸方向においてオーバーラップするよう構成されている。 According to a further aspect of the lubricating structure according to the present invention, the through hole is formed adjacent to the first gear. The second gear is configured to overlap the through hole in the axial direction.
　本形態によれば、第２歯車が、貫通孔に対して軸方向にオーバーラップする構成であるため、貫通孔に向けて直接的に潤滑油を掻き上げることができる。これにより、貫通孔を介した内孔への潤滑油の供給をより効率的に行うことができる。 According to this embodiment, since the second gear is configured to overlap the through hole in the axial direction, the lubricating oil can be directly scraped up toward the through hole. Thereby, the lubricating oil can be supplied more efficiently to the inner hole through the through hole.
　本発明に係る潤滑構造の更なる形態によれば、内孔に軸受部材を介して回転可能に支持された第３回転体をさらに備える。そして、第２回転体によって掻き上げられて飛散する潤滑油を、貫通孔を介して軸受部材に供給するよう構成されている。 According to a further aspect of the lubrication structure according to the present invention, the lubrication structure further includes a third rotating body supported rotatably in the inner hole via the bearing member. And it is comprised so that the lubricating oil which is scraped up and scattered by the 2nd rotary body may be supplied to a bearing member through a through-hole.
　本形態によれば、潤滑が必要であるが、潤滑油の供給が困難な位置に配置された軸受部材に対して、効率的に潤滑油を供給することができる。例えば、入力軸と、当該入力軸の内部にパイロットベアリングを介して相対回転可能に支持された出力軸と、を備えるインプットリダクションタイプの変速機の場合には、入力軸の回転に対応して回転するカウンタ軸上の回転体（歯車など）によって掻き上げられて飛散する潤滑油を、入力軸に形成した貫通孔を介してパイロットベアリングに効率的に供給することができる。また、入力軸と、パイロットベアリングを介して相対回転可能に当該入力軸を内部に支持する出力軸と、を備えるアウトプットリダクションタイプの変速機の場合には、入力軸の回転に対応して回転するカウンタ軸上の回転体（歯車など）によって掻き上げられて飛散する潤滑油を、出力軸に形成した貫通孔を介してパイロットベアリングに効率的に供給することができる。 According to this embodiment, although lubrication is necessary, it is possible to efficiently supply the lubricating oil to the bearing member disposed at a position where it is difficult to supply the lubricating oil. For example, in the case of an input reduction type transmission that includes an input shaft and an output shaft that is supported so as to be relatively rotatable via a pilot bearing inside the input shaft, the input shaft rotates in response to the rotation of the input shaft. Lubricating oil that is scraped up and scattered by a rotating body (such as a gear) on the counter shaft can be efficiently supplied to the pilot bearing through a through hole formed in the input shaft. In the case of an output reduction type transmission that includes an input shaft and an output shaft that supports the input shaft so as to be relatively rotatable via a pilot bearing, the output shaft rotates in accordance with the rotation of the input shaft. Lubricating oil that is scraped and scattered by a rotating body (such as a gear) on the counter shaft can be efficiently supplied to the pilot bearing through a through hole formed in the output shaft.
　本発明に係る変速機の好ましい形態によれば、内孔を有する入力軸と、当該入力軸に設けられた減速駆動歯車と、入力軸に平行配置されたカウンタ軸と、当該カウンタ軸に設けられ減速駆動歯車と噛合する減速被駆動歯車と、内孔に軸受部材を介して回転可能に支持された出力軸と、を備えている。そして、当該変速機は、減速被駆動歯車によって掻き上げられて飛散する潤滑油を、上述したいずれかの態様の本発明に係る潤滑構造を用いて内孔に供給するよう構成されている。 According to a preferred embodiment of the transmission according to the present invention, an input shaft having an inner hole, a reduction drive gear provided on the input shaft, a counter shaft arranged in parallel with the input shaft, and provided on the counter shaft. A reduction driven gear that meshes with the reduction drive gear, and an output shaft that is rotatably supported in the inner hole via a bearing member. And the said transmission is comprised so that the lubricating oil which is scraped up and scattered by the speed reduction driven gear may be supplied to an inner hole using the lubricating structure which concerns on this invention of the aspect mentioned above.
　本発明によれば、上述したいずれかの態様の本発明に係る潤滑構造を用いて潤滑油を内孔に供給する構成であるため、本発明の潤滑構造が奏する効果と同様の効果、例えば、内孔に潤滑油を効率的に供給可能な合理的な潤滑構造を提供することができる効果などを奏することができる。 According to the present invention, since the lubricating oil is supplied to the inner hole using the lubricating structure according to the present invention in any one of the aspects described above, the same effects as the effects exhibited by the lubricating structure of the present invention, for example, For example, it is possible to provide a reasonable lubricating structure capable of efficiently supplying lubricating oil to the inner hole.
　本発明に係る変速機の好ましい形態によれば、内孔を有する入力軸と、当該入力軸に設けられた駆動歯車と、入力軸に平行配置されたカウンタ軸と、当該カウンタ軸に設けられ駆動歯車と噛合する被駆動歯車と、カウンタ軸に設けられた出力駆動歯車と、内孔に軸受部材を介して回転可能に支持された出力軸と、出力軸に設けられ出力駆動歯車と噛合する出力被駆動歯車と、を備えている。そして、当該変速機は、出力駆動歯車によって掻き上げられて飛散する潤滑油を、上述したいずれかの態様の本発明に係る潤滑構造を用いて内孔に供給するよう構成されている。 According to a preferred embodiment of the transmission according to the present invention, an input shaft having an inner hole, a drive gear provided on the input shaft, a counter shaft arranged in parallel with the input shaft, and a drive provided on the counter shaft. A driven gear that meshes with the gear, an output drive gear that is provided on the counter shaft, an output shaft that is rotatably supported in the inner hole via a bearing member, and an output that is provided on the output shaft and meshes with the output drive gear And a driven gear. And the said transmission is comprised so that the lubricating oil which is scraped up and scattered by an output drive gear may be supplied to an inner hole using the lubricating structure which concerns on this invention of the aspect mentioned above.
　本発明によれば、上述したいずれかの態様の本発明に係る潤滑構造を用いて潤滑油を内孔に供給する構成であるため、本発明の潤滑構造が奏する効果と同様の効果、例えば、内孔に潤滑油を効率的に供給可能な合理的な潤滑構造を提供することができる効果などを奏することができる。 According to the present invention, since the lubricating oil is supplied to the inner hole using the lubricating structure according to the present invention in any one of the aspects described above, the same effects as the effects exhibited by the lubricating structure of the present invention, for example, For example, it is possible to provide a reasonable lubricating structure capable of efficiently supplying lubricating oil to the inner hole.
　本発明に係る潤滑方法の好ましい形態によれば、内孔を有する第１回転体と、当該第１回転体の回転に対応した回転を行う第２回転体と、を備え、第２回転体によって掻き上げられた潤滑油を内孔に供給する潤滑方法が構成される。回転体には、当該回転体の外周面から内孔まで貫通する貫通孔が形成されている。そして、第２回転体によって掻き上げられて飛散する潤滑油を貫通孔によって捕捉して内孔に供給する。 According to a preferred embodiment of the lubricating method of the present invention, the first rotating body having the inner hole and the second rotating body that performs rotation corresponding to the rotation of the first rotating body are provided, and the second rotating body A lubrication method for supplying the scraped lubricating oil to the inner hole is configured. A through hole that penetrates from the outer peripheral surface of the rotating body to the inner hole is formed in the rotating body. Then, the lubricating oil scraped up and scattered by the second rotating body is captured by the through hole and supplied to the inner hole.
　本発明によれば、第２回転体によって掻き上げられて飛散する潤滑油を貫通孔によって捕捉して内孔に供給する構成であるため、第２回転体によって掻き上げられて飛散する潤滑油が、貫通孔を介して効率良く第１回転体の内孔に供給され得る。しかも、第１回転体の内孔に潤滑油を供給するためだけの専用部品が不要な構成であるため、部品点数の削減も図ることができ、合理的である。 According to the present invention, since the lubricating oil that is scooped up and scattered by the second rotating body is captured by the through hole and supplied to the inner hole, the lubricating oil that is scooped up and scattered by the second rotating body is And can be efficiently supplied to the inner hole of the first rotating body through the through hole. In addition, since a dedicated part for supplying lubricating oil to the inner hole of the first rotating body is unnecessary, the number of parts can be reduced, which is reasonable.
　本発明によれば、回転体の内孔に潤滑油を効率的に供給可能な合理的な潤滑構造を提供することができる。 According to the present invention, it is possible to provide a rational lubricating structure capable of efficiently supplying lubricating oil to the inner hole of the rotating body.
本発明の実施の形態に係る潤滑構造を適用した変速機１の構成の概略を示す断面図である。It is sectional drawing which shows the outline of a structure of the transmission 1 to which the lubrication structure which concerns on embodiment of this invention is applied. 本発明の実施の形態に係る潤滑構造の要部を拡大して示す拡大図である。It is an enlarged view which expands and shows the principal part of the lubricating structure which concerns on embodiment of this invention. 図２のＸ－Ｘ断面図である。FIG. 3 is a sectional view taken along line XX in FIG. 2. リダクションドリブンギヤＲＧ’が掻き上げる潤滑油のうち、直接インプットシャフト２の内孔２ｂに到達し得る潤滑油の軌跡を示す説明図である。It is explanatory drawing which shows the locus | trajectory of the lubricating oil which can reach | attain directly the inner hole 2b of the input shaft 2 among the lubricating oil which the reduction driven gear RG 'scoops up. インプットシャフト２の内孔２ｂに到達し得る潤滑油の軌跡を、インプットシャフト２における回転座標系に変換した相対軌跡を示す説明図である。4 is an explanatory diagram showing a relative locus obtained by converting a locus of lubricating oil that can reach the inner hole 2b of the input shaft 2 into a rotational coordinate system in the input shaft 2. FIG. リダクションドリブンギヤＲＧ’によって掻き上げられて飛散する潤滑油が、貫通孔２ｃを介してインプットシャフト２の内孔２ｂに供給される様子を示す説明図である。It is explanatory drawing which shows a mode that the lubricating oil which is scraped up and scattered by the reduction driven gear RG 'is supplied to the inner hole 2b of the input shaft 2 through the through-hole 2c.
　次に、本発明を実施するための最良の形態を実施例を用いて説明する。なお、以上および以下の記載に係る構成ないし方法は、本発明にかかる「潤滑構造および潤滑方法」の製造および使用、当該「潤滑構造および潤滑方法」の構成要素の使用を実現せしめるべく、他の構成ないし方法と別に、あるいはこれらと組み合わせて用いることができる。本発明の代表的実施形態は、これらの組み合わせも包含し、添付図面を参照しつつ詳細に説明される。以下の詳細な説明は、本発明の好ましい適用例を実施するための詳細情報を当業者に教示するに留まり、本発明の技術的範囲は、当該詳細な説明によって制限されず、特許請求の範囲の記載に基づいて定められる。このため、以下の詳細な説明における構成や方法ステップの組み合わせは、広義の意味において、本発明を実施するのに全て必須であるというものではなく、添付図面の参照番号とともに記載された詳細な説明において、本発明の代表的形態を開示するに留まるものである。 Next, the best mode for carrying out the present invention will be described using examples. Note that the configurations and methods according to the above and the following descriptions are provided in order to realize the manufacture and use of the “lubricating structure and lubricating method” according to the present invention and the use of the components of the “lubricating structure and lubricating method”. It can be used separately or in combination with the structure or method. Exemplary embodiments of the present invention include these combinations and will be described in detail with reference to the accompanying drawings. The following detailed description is only to teach those skilled in the art with detailed information to implement preferred embodiments of the invention, and the scope of the invention is not limited by the detailed description, but is limited by the scope of the claims. It is determined based on the description. For this reason, combinations of configurations and method steps in the following detailed description are not all essential to implement the present invention in a broad sense, but are described in detail with reference numerals in the accompanying drawings. However, only representative embodiments of the present invention are disclosed.
　以下、本発明の実施形態につき、図１ないし図６を参照しつつ詳細に説明する。変速機１は、図１に示すように、インプットシャフト２と、アウトプットシャフト６と、リダクションギヤ機構ＧＭと、変速機構ＴＭと、ケーシング８と、を備えている。なお、ケーシング８内には、変速機１の構成要素を潤滑するための潤滑油が貯留されている。インプットシャフト２は、本発明における「第１回転体」、「第１回転軸」および「入力軸」に対応し、カウンタシャフト４は、本発明における「第２回転体」、「第２回転軸」および「カウンタ軸」に対応し、アウトプットシャフト６は、本発明における「第３回転体」および「出力軸」に対応する実施構成の一例である。なお、本実施の形態では、説明の便宜上、変速機１の長軸方向におけるインプットシャフト２が配置された側（図１における下側）を「前側」ないし「前方」として規定し、アウトプットシャフト６が配置された側（図１における上側）を「後側」ないし「後方」として規定する。

と、これらを収容するケーシング８と、を備える。 Hereinafter, embodiments of the present invention will be described in detail with reference to FIGS. 1 to 6. As shown in FIG. 1, the transmission 1 includes an input shaft 2, an output shaft 6, a reduction gear mechanism GM, a speed change mechanism TM, and a casing 8. Note that lubricating oil for lubricating the components of the transmission 1 is stored in the casing 8. The input shaft 2 corresponds to the “first rotating body”, “first rotating shaft”, and “input shaft” in the present invention, and the counter shaft 4 corresponds to the “second rotating body”, “second rotating shaft” in the present invention. The output shaft 6 is an example of an implementation configuration corresponding to the “third rotating body” and the “output shaft” in the present invention. In the present embodiment, for convenience of explanation, the side (lower side in FIG. 1) on which the input shaft 2 is arranged in the major axis direction of the transmission 1 is defined as “front side” or “front”, and the output shaft 6 1 is defined as “rear side” or “rearward”.

And a casing 8 for housing them.
　インプットシャフト２は、図示しないクラッチを介してエンジン（図示せず）の動力が入力されるシャフトである。インプットシャフト２は、ベアリングＢ１を介してケーシング８に回転可能に支持されている。インプットシャフト２の後方部分（クラッチが配置される側とは反対側の部分）は、図１および図２に示すように、内孔２ｂが形成された中空部として構成されている。また、インプットシャフト２の後端部には、リダクションドライブギヤＲＧが一体形成されている。リダクションドライブギヤＲＧは、本発明における「回転体」、「第１歯車」および「減速駆動歯車」に対応する実施構成の一例である。 The input shaft 2 is a shaft to which power of an engine (not shown) is input via a clutch (not shown). The input shaft 2 is rotatably supported by the casing 8 via a bearing B1. As shown in FIGS. 1 and 2, the rear portion of the input shaft 2 (the portion opposite to the side where the clutch is disposed) is configured as a hollow portion in which an inner hole 2b is formed. Further, a reduction drive gear RG is integrally formed at the rear end portion of the input shaft 2. The reduction drive gear RG is an example of an implementation configuration corresponding to the “rotor”, the “first gear”, and the “reduction drive gear” in the present invention.
　さらに、インプットシャフト２は、図２に示すように、リダクションドライブギヤＲＧよりも前側（クラッチが配置される側）に拡径部２ａが形成されている。拡径部２ａは、インプットシャフト２の他の部分よりも径方向に拡径されている。当該拡径部２ａの前側端面がベアリングＢ１に当接されることによって、インプットシャフト２の軸方向の位置決めがなされる。拡径部２ａには、外周面から内孔２ｂまで貫通する貫通孔２ｃが形成されている。 Further, as shown in FIG. 2, the input shaft 2 has a diameter-expanded portion 2a on the front side (the side where the clutch is disposed) from the reduction drive gear RG. The diameter-expanded portion 2a is diameter-expanded more in the radial direction than the other portion of the input shaft 2. The input shaft 2 is positioned in the axial direction by bringing the front end face of the enlarged diameter portion 2a into contact with the bearing B1. A through hole 2c penetrating from the outer peripheral surface to the inner hole 2b is formed in the enlarged diameter portion 2a.
　貫通孔２ｃは、図３に示すように、周方向に等間隔（１２０°間隔）に３箇所形成されている。貫通孔２ｃは、インプットシャフト２の中心ＣＰから中心角が１２０°となるように任意に引いた３本のインプットシャフト２の仮想径方向線ＲＬそれぞれに対して、インプットシャフト２の回転方向後側にオフセットした中心線ＣＬを有するように構成されている。 As shown in FIG. 3, three through holes 2 c are formed at equal intervals (120 ° intervals) in the circumferential direction. The through-hole 2c is a rear side in the rotational direction of the input shaft 2 with respect to each of the virtual radial direction lines RL of the three input shafts 2 arbitrarily drawn so as to have a central angle of 120 ° from the center CP of the input shaft 2. The center line CL is offset to the center line CL.
　当該オフセット量は、貫通孔２ｃが、後述するリダクションドリブンギヤＲＧ’により掻き上げられる潤滑油の相対軌跡に沿うような値に設定されている。貫通孔２ｃの設定についての詳細は後述する。貫通孔２ｃは、本発明における「貫通孔」に対応し、仮想径方向線ＲＬは、本発明における「径方向線」に対応する実施構成の一例である。また、貫通孔２ｃが、インプットシャフト２の仮想径方向線ＲＬに対して、インプットシャフト２の回転方向後側にオフセットした中心線ＣＬを有する態様は、本発明における「貫通孔は、回転体の径方向線に対して、回転体の回転方向後方にオフセットした中心線を有する」に対応する実施構成の一例である。 The offset amount is set to a value such that the through-hole 2c follows the relative locus of the lubricating oil that is scraped up by a reduction driven gear RG 'described later. Details of the setting of the through hole 2c will be described later. The through hole 2c corresponds to the “through hole” in the present invention, and the virtual radial line RL is an example of an implementation configuration corresponding to the “radial line” in the present invention. Further, the aspect in which the through hole 2c has the center line CL that is offset to the rear side in the rotation direction of the input shaft 2 with respect to the virtual radial direction line RL of the input shaft 2 is " It is an example of the implementation structure corresponding to "having the center line offset in the rotation direction back of the rotary body with respect to the radial direction line."
　カウンタシャフト４は、図１に示すように、インプットシャフト２に平行配置されている。カウンタシャフト４は、前端部および後端部がベアリングＢ２，Ｂ３を介してケーシング８に回転可能に支持されている。また、カウンタシャフト４の前端部には、リダクションドリブンギヤＲＧ’が一体形成されている。リダクションドリブンギヤＲＧ’は、リダクションドライブギヤＲＧと噛み合う。 The counter shaft 4 is arranged in parallel to the input shaft 2 as shown in FIG. The counter shaft 4 is rotatably supported by the casing 8 at the front end portion and the rear end portion via bearings B2 and B3. Further, a reduction driven gear RG ′ is integrally formed at the front end portion of the counter shaft 4. The reduction driven gear RG 'meshes with the reduction drive gear RG.
　リダクションドリブンギヤＲＧ’の歯幅は、図２に示すように、リダクションドライブギヤＲＧの歯幅よりも大きく形成されている。具体的には、リダクションドリブンギヤＲＧ’の歯幅は、インプットシャフト２およびカウンタシャフト４をケーシング８に組み付けた状態で、リダクションドリブンギヤＲＧ’がリダクションドライブギヤＲＧよりもベアリングＢ１側（前方側）へ突出するように構成されている。 The tooth width of the reduction driven gear RG 'is formed larger than the tooth width of the reduction drive gear RG as shown in FIG. Specifically, the tooth width of the reduction driven gear RG ′ is such that the reduction driven gear RG ′ protrudes further toward the bearing B1 (front side) than the reduction drive gear RG when the input shaft 2 and the counter shaft 4 are assembled to the casing 8. Is configured to do.
　即ち、リダクションドリブンギヤＲＧ’は、インプットシャフト２の拡径部２ａにおける貫通孔２ｃに対して軸方向にオーバーラップするように構成されている。このように、リダクションドリブンギヤＲＧ’が、貫通孔２ｃに対して軸方向にオーバーラップする構成であるため、貫通孔２ｃに向けて直接的に潤滑油を掻き上げることができる。リダクションドリブンギヤＲＧ’と、リダクションドライブギヤＲＧによって、リダクションギヤ機構ＧＭが構成される。 That is, the reduction driven gear RG ′ is configured to overlap in the axial direction with respect to the through hole 2 c in the enlarged diameter portion 2 a of the input shaft 2. Thus, since the reduction driven gear RG 'is configured to overlap the through hole 2c in the axial direction, the lubricating oil can be directly scraped up toward the through hole 2c. A reduction gear mechanism GM is constituted by the reduction driven gear RG 'and the reduction drive gear RG.
　リダクションギヤ機構ＧＭによってインプットシャフト２とカウンタシャフト４とが接続される。インプットシャフト２に入力された動力は、当該リダクションギヤ機構ＧＭによってカウンタシャフト４に伝達される。リダクションドリブンギヤＲＧ’は、本発明における「第２回転体」、「第２歯車」および「減速被駆動歯車」に対応する実施構成の一例である。また、リダクションドリブンギヤＲＧ’が、インプットシャフト２の拡径部２ａにおける貫通孔２ｃに対して軸方向にオーバーラップする態様は、本発明における「第２歯車は、貫通孔と軸方向においてオーバーラップする」態様に対応する実施構成の一例である。 The input shaft 2 and the counter shaft 4 are connected by the reduction gear mechanism GM. The power input to the input shaft 2 is transmitted to the counter shaft 4 by the reduction gear mechanism GM. The reduction driven gear RG 'is an example of an implementation configuration corresponding to the "second rotating body", "second gear", and "deceleration driven gear" in the present invention. Further, the aspect in which the reduction driven gear RG ′ overlaps the through hole 2c in the enlarged diameter portion 2a of the input shaft 2 in the axial direction is “the second gear overlaps the through hole in the axial direction” in the present invention. It is an example of the implementation structure corresponding to an aspect.
　アウトプットシャフト６は、図１に示すように、インプットシャフト２に同軸状に配置されている。アウトプットシャフト６は、動力を出力するためのシャフトである。アウトプットシャフト６の一端は、インプットシャフト２の内孔２ｂ内にパイロットベアリングＰＢを介して回転可能に支持されている。また、アウトプットシャフト６の他端は、ベアリングＢ４を介してケーシング８に回転可能に支持されている。 The output shaft 6 is arranged coaxially with the input shaft 2 as shown in FIG. The output shaft 6 is a shaft for outputting power. One end of the output shaft 6 is rotatably supported in the inner hole 2b of the input shaft 2 via a pilot bearing PB. The other end of the output shaft 6 is rotatably supported by the casing 8 via a bearing B4.
　パイロットベアリングＰＢは、図２に示すように、リダクションドライブギヤＲＧの内側に配置される。即ち、パイロットベアリングＰＢは、軸方向前側端部が貫通孔２ｃに隣接するように配置されている。なお、リダクションドライブギヤＲＧには、図２に示すように、歯底面から内孔２ｂまで貫通する貫通孔２ｄが形成されている。パイロットベアリングＰＢは、本発明における「軸受部材」に対応する実施構成の一例である。 The pilot bearing PB is disposed inside the reduction drive gear RG as shown in FIG. That is, the pilot bearing PB is disposed such that the front end portion in the axial direction is adjacent to the through hole 2c. As shown in FIG. 2, the reduction drive gear RG is formed with a through hole 2d penetrating from the tooth bottom surface to the inner hole 2b. The pilot bearing PB is an example of an implementation configuration corresponding to the “bearing member” in the present invention.
　変速機構ＴＭは、図１に示すように、複数の駆動ギヤＧと、複数の被動ギヤＧ’と、複数のシンクロ装置Ｓと、から構成されている。複数の駆動ギヤＧは、カウンタシャフト４に設けられている。複数の被動ギヤＧ’は、駆動ギヤＧと噛み合うようにアウトプットシャフト６に設けられている。シンクロ装置Ｓは、駆動ギヤＧまたは被動ギヤＧ’のうち、カウンタシャフト４またはアウトプットシャフト６と相対回転可能に設けられたギヤをカウンタシャフト４またはアウトプットシャフト６に選択的に固定する。変速機構ＴＭによって、インプットシャフト２またはカウンタシャフト４とアウトプットシャフト６とが接続される。カウンタシャフト４に伝達された動力は、当該変速機構ＴＭを介して、アウトプットシャフト６に出力される。 As shown in FIG. 1, the speed change mechanism TM includes a plurality of drive gears G, a plurality of driven gears G ′, and a plurality of synchronizers S. The plurality of drive gears G are provided on the counter shaft 4. The plurality of driven gears G ′ are provided on the output shaft 6 so as to mesh with the drive gear G. The synchronizer S selectively fixes, to the counter shaft 4 or the output shaft 6, a gear provided so as to be rotatable relative to the counter shaft 4 or the output shaft 6 among the driving gear G and the driven gear G ′. The input shaft 2 or the counter shaft 4 and the output shaft 6 are connected by the speed change mechanism TM. The power transmitted to the counter shaft 4 is output to the output shaft 6 through the speed change mechanism TM.
　次に、インプットシャフト２における貫通孔２ｃの設定について詳細に説明する。図４に示すように、リダクションドリブンギヤＲＧ’が掻き上げる潤滑油の軌跡は、リダクションドリブンギヤＲＧ’の接線方向に沿う直線となる。リダクションドリブンギヤＲＧ’によって掻き上げられて飛散する潤滑油のうち、リダクションドリブンギヤＲＧ’の周上の点Ｐ１（回転角度θ１の位置）から点Ｐ２（回転角度θ２の位置）までの範囲で放たれた潤滑油が、インプットシャフト２の内孔２ｂに到達し得る。 Next, the setting of the through hole 2c in the input shaft 2 will be described in detail. As shown in FIG. 4, the locus of the lubricating oil scraped up by the reduction driven gear RG ′ is a straight line along the tangential direction of the reduction driven gear RG ′. Of the lubricating oil scraped up and scattered by the reduction driven gear RG ′, it was released in the range from the point P1 (position of the rotation angle θ1) to the point P2 (position of the rotation angle θ2) on the circumference of the reduction driven gear RG ′. The lubricating oil can reach the inner hole 2 b of the input shaft 2.
　言い換えると、リダクションドリブンギヤＲＧ’によって掻き上げられて飛散する潤滑油のうち、インプットシャフト２の内孔２ｂに到達し得る潤滑油の軌跡は、図４に示すように、リダクションドリブンギヤＲＧ’の外周面とインプットシャフト２の内孔２ｂとの共通外接線ＥＬから共通内接線ＩＬまでの範囲に存在することになる。当該範囲に軌跡を有する潤滑油を捕捉するものとすれば、効率良く内孔２ｂに潤滑油を供給することができる。ここで、インプットシャフト２は回転することから、インプットシャフト２を基準に見た場合におけるリダクションドリブンギヤＲＧ’が掻き上げた潤滑油の軌跡、即ち、相対軌跡は、図５に示すような曲線状をなす。 In other words, of the lubricating oil that is scraped up and scattered by the reduction driven gear RG ′, the locus of the lubricating oil that can reach the inner hole 2b of the input shaft 2 is the outer peripheral surface of the reduction driven gear RG ′ as shown in FIG. And the inner hole 2b of the input shaft 2 exist in a range from the common outer tangent line EL to the common inner tangent line IL. If the lubricating oil having a locus in the range is captured, the lubricating oil can be efficiently supplied to the inner hole 2b. Here, since the input shaft 2 rotates, the locus of the lubricating oil swung up by the reduction driven gear RG ′ when viewed from the input shaft 2, that is, the relative locus, has a curved shape as shown in FIG. 5. Eggplant.
　当該曲線状をなす潤滑油の相対軌跡は、図４に示すリダクションドリブンギヤＲＧ’の接線方向に沿う直線状の潤滑油軌跡を、インプットシャフト２における回転座標系に変換することによって求めることができる。なお、当該直線状の相対軌跡は、リダクションドリブンギヤＲＧ’のギヤ径と、インプットシャフト２とカウンタシャフト４との中心間距離と、リダクションドライブギヤＲＧおよびリダクションドリブンギヤＲＧ’のギヤ比とが決まれば、インプットシャフト２の回転数に依らずに一義的に決まる。 The relative locus of the lubricating oil having the curved shape can be obtained by converting the linear lubricating oil locus along the tangential direction of the reduction driven gear RG ′ shown in FIG. 4 into the rotational coordinate system of the input shaft 2. The linear relative trajectory is determined if the gear diameter of the reduction driven gear RG ′, the center-to-center distance between the input shaft 2 and the counter shaft 4 and the gear ratio of the reduction drive gear RG and the reduction driven gear RG ′ are determined. It is uniquely determined regardless of the rotational speed of the input shaft 2.
　貫通孔２ｃは、図４および図５に示すように、リダクションドリブンギヤＲＧ’の外周面とインプットシャフト２の内孔２ｂとの共通外接線ＥＬから共通内接線ＩＬまでの範囲に存在する潤滑油の軌跡のうち、インプットシャフト２の中心ＣＰを通る潤滑油の軌跡ＬＣ（図４における実線）を、インプットシャフト２における回転座標系に変換することによって求めた相対軌跡ＬＣ’（図５における実線）に沿うように設定する。 As shown in FIGS. 4 and 5, the through hole 2 c is formed of lubricating oil existing in a range from the common outer tangent line EL to the common inner tangent line IL between the outer peripheral surface of the reduction driven gear RG ′ and the inner hole 2 b of the input shaft 2. Of the loci, the locus LC (solid line in FIG. 4) of the lubricating oil passing through the center CP of the input shaft 2 is converted into a relative locus LC ′ (solid line in FIG. 5) obtained by converting it into the rotational coordinate system of the input shaft 2. Set along.
　具体的には、上記により求めた相対軌跡ＬＣ’が、インプットシャフト２における軸方向に直角な断面（以下、軸直角断面という）を横切る部分を直線近似し、当該直線近似した直線を、貫通孔２ｃの中心線ＣＬとして規定する。これにより、貫通孔２ｃが潤滑油の相対軌跡に沿う構成としている。その結果、貫通孔２ｃの中心線ＣＬは、図３に示すように、インプットシャフト２の仮想径方向線ＲＬに対して、インプットシャフト２の回転方向（図３の太矢印）後側にオフセットされた位置に存在することになる。 Specifically, the portion of the relative trajectory LC ′ obtained as described above crosses a cross section perpendicular to the axial direction of the input shaft 2 (hereinafter referred to as an axial perpendicular cross section) is linearly approximated, and the straight line approximated is defined as a through hole. It is defined as a center line CL of 2c. Thereby, it is set as the structure where the through-hole 2c follows the relative locus | trajectory of lubricating oil. As a result, the center line CL of the through hole 2c is offset to the rear side in the rotation direction of the input shaft 2 (thick arrow in FIG. 3) with respect to the virtual radial direction line RL of the input shaft 2, as shown in FIG. Will be present at that position.
　次に、こうして構成された変速機１におけるパイロットベアリングＰＢへの潤滑油供給作用について説明する。インプットシャフト２に動力が入力されることによってインプットシャフト２が回転（図６の太矢印）されると、リダクションギヤ機構ＧＭを介してカウンタシャフト４が回転される。このとき、リダクションドリブンギヤＲＧ’がケーシング８の下方に溜められた潤滑油を掻き上げる。 Next, the operation of supplying the lubricating oil to the pilot bearing PB in the transmission 1 configured as described above will be described. When power is input to the input shaft 2 and the input shaft 2 is rotated (thick arrow in FIG. 6), the counter shaft 4 is rotated via the reduction gear mechanism GM. At this time, the reduction driven gear RG ′ scoops up the lubricating oil stored under the casing 8.
　リダクションドリブンギヤＲＧ’によって掻き上げられて飛散する潤滑油は、インプットシャフト２を基準に見た場合、図６に示すような曲線状の相対軌跡を有する。本実施の形態では、インプットシャフト２に形成した貫通孔２ｃは、当該曲線状となる相対軌跡に沿う構成をしているため、リダクションドリブンギヤＲＧ’によって掻き上げられて飛散する潤滑油を効率的に貫通孔２ｃによって捕捉し、内孔２ｂ内に取り込むことができる。 The lubricating oil that is scraped up and scattered by the reduction driven gear RG 'has a curved relative locus as shown in FIG. In the present embodiment, the through hole 2c formed in the input shaft 2 has a configuration along the curved relative trajectory, so that the lubricating oil that is scraped and scattered by the reduction driven gear RG ′ can be efficiently used. It can be captured by the through hole 2c and taken into the inner hole 2b.
　これにより、パイロットベアリングＰＢに十分な潤滑油を供給することができる。なお、潤滑油の相対軌跡は、リダクションドリブンギヤＲＧ’のギヤ径と、インプットシャフト２とカウンタシャフト４との中心間距離と、リダクションドライブギヤＲＧおよびリダクションドリブンギヤＲＧ’のギヤ比とが決まれば、インプットシャフト２の回転数に依らずに一義的に決まるため、貫通孔２ｃによる潤滑油の捕捉および貫通孔２ｃを介した内孔２ｂへの潤滑油の供給が、インプットシャフト２の回転数に左右されることがない。 Thus, sufficient lubricating oil can be supplied to the pilot bearing PB. It should be noted that the relative locus of the lubricating oil is determined by determining the gear diameter of the reduction driven gear RG ′, the distance between the centers of the input shaft 2 and the counter shaft 4 and the gear ratio of the reduction drive gear RG and the reduction driven gear RG ′. Since it is uniquely determined regardless of the rotation speed of the shaft 2, the capture of the lubricating oil by the through hole 2 c and the supply of the lubricating oil to the inner hole 2 b through the through hole 2 c depend on the rotation speed of the input shaft 2. There is nothing to do.
　即ち、インプットシャフト２の回転数が低回転領域から潤滑油がより必要とされる高回転領域まで安定した潤滑性能を確保することができる。リダクションドリブンギヤＲＧ’によって掻き上げられて飛散する潤滑油を貫通孔２ｃによって捕捉して内孔２ｂに取り込む態様は、本発明における「第２回転体によって掻き上げられて飛散する潤滑油を貫通孔によって捕捉して内孔に供給する」に対応する実施構成の一例である。 That is, stable lubrication performance can be ensured from the low rotational speed range of the input shaft 2 to the high rotational speed range where more lubricating oil is required. The aspect in which the lubricating oil that is scooped up and scattered by the reduction driven gear RG ′ is captured by the through hole 2c and taken into the inner hole 2b is “the lubricating oil that is scooped up and scattered by the second rotating body” It is an example of the implementation structure corresponding to "capturing and supplying to an inner hole."
　以上説明した本発明の実施の形態に係る潤滑構造によれば、インプットシャフト２に形成する貫通孔２ｃが、リダクションドリブンギヤＲＧ’によって掻き上げられて飛散する潤滑油の相対軌跡に沿うように、インプットシャフト２の仮想径方向線ＲＬに対して、インプットシャフト２の回転方向後側にオフセットした中心線ＣＬを有する構成としている。 According to the lubricating structure according to the embodiment of the present invention described above, the input hole 2c formed in the input shaft 2 follows the relative locus of the lubricating oil that is scraped and scattered by the reduction driven gear RG ′. The center line CL is offset to the rear side in the rotation direction of the input shaft 2 with respect to the virtual radial direction line RL of the shaft 2.
　これにより、リダクションドリブンギヤＲＧ’によって掻き上げられて飛散する潤滑油を効率良く貫通孔２ｃを介してインプットシャフト２の内孔２ｂ内に取り込むことができる。この結果、パイロットベアリングＰＢに十分な潤滑油を供給することができる。 Thereby, the lubricating oil that is scraped up and scattered by the reduction driven gear RG 'can be efficiently taken into the inner hole 2b of the input shaft 2 through the through hole 2c. As a result, sufficient lubricating oil can be supplied to the pilot bearing PB.
　また、インプットシャフト２の内孔２ｂ内に潤滑油を供給するためだけの専用部品が必要な従来構造に比べて、部品点数の削減も図ることができ、合理的である。しかも、貫通孔２ｃを、インプットシャフト２の仮想径方向線ＲＬに対して、インプットシャフト２の回転方向後側にオフセットするだけであるため、飛散する潤滑油の相対軌跡に沿うような構成を容易に実現することができる。 Also, it is possible to reduce the number of parts compared to the conventional structure that requires dedicated parts only for supplying lubricating oil into the inner hole 2b of the input shaft 2, which is reasonable. Moreover, since the through hole 2c is only offset to the rear side in the rotation direction of the input shaft 2 with respect to the virtual radial direction line RL of the input shaft 2, a configuration that follows the relative locus of the scattered lubricating oil is easy. Can be realized.
　また、本発明の実施の形態に係る潤滑構造によれば、貫通孔２ｃをインプットシャフト２の拡径部２ａに形成する構成である。これにより、貫通孔２ｃをリダクションドライブギヤＲＧに形成する構成に比べて、飛散する潤滑油の相対軌跡に沿うように貫通孔２ｃを構成し易い。また、飛散する潤滑油が貫通孔２ｃに到達するまでに、リダクションドライブギヤＲＧの歯面等に接触して、貫通孔２ｃへの潤滑油の流入が阻害されることもない。これにより、合理的かつ効率的に潤滑油を内孔２ｂ内に供給することができる。 Moreover, according to the lubrication structure according to the embodiment of the present invention, the through hole 2c is formed in the enlarged diameter portion 2a of the input shaft 2. Thereby, compared with the structure which forms the through-hole 2c in the reduction drive gear RG, it is easy to comprise the through-hole 2c along the relative locus of the scattered lubricating oil. Further, before the scattered lubricating oil reaches the through hole 2c, it does not come into contact with the tooth surface of the reduction drive gear RG and the flow of the lubricating oil into the through hole 2c is not hindered. As a result, the lubricating oil can be supplied into the inner hole 2b reasonably and efficiently.
　また、本発明の実施の形態に係る潤滑構造によれば、リダクションドリブンギヤＲＧ’が、インプットシャフト２の拡径部２ａにおける貫通孔２ｃに対して軸方向にオーバーラップする構成である。これにより、貫通孔２ｃに向けて直接的に潤滑油を掻き上げることができる。この結果、貫通孔を介した内孔への潤滑油の供給をより効率的に行うことができる。 Further, according to the lubrication structure according to the embodiment of the present invention, the reduction driven gear RG 'is configured to overlap the through hole 2c in the enlarged diameter portion 2a of the input shaft 2 in the axial direction. Thereby, lubricating oil can be directly scraped up toward the through-hole 2c. As a result, it is possible to more efficiently supply the lubricating oil to the inner hole through the through hole.
　本実施形態では、リダクションドリブンギヤＲＧ’の外周面とインプットシャフト２の内孔２ｂとの共通外接線ＥＬから共通内接線ＩＬまでの範囲に存在する潤滑油の軌跡のうち、インプットシャフト２の中心ＣＰを通る潤滑油の軌跡ＬＣを、インプットシャフト２における回転座標系に変換することによって求めた相対軌跡ＬＣ’（図５における実線）上に貫通孔２ｃを設定する構成としたが、インプットシャフト２の中心ＣＰを通らない潤滑油の軌跡を、回転座標系に変換することによって求めた相対軌跡上に貫通孔２ｃを設定する構成としても良い。 In the present embodiment, the center CP of the input shaft 2 out of the locus of the lubricating oil existing in the range from the common outer tangent line EL to the common inner tangent line IL between the outer peripheral surface of the reduction driven gear RG ′ and the inner hole 2b of the input shaft 2. The through hole 2c is set on the relative locus LC ′ (solid line in FIG. 5) obtained by converting the locus LC of the lubricating oil passing through to the rotational coordinate system of the input shaft 2. It is good also as a structure which sets the through-hole 2c on the relative locus | trajectory calculated | required by converting the locus | trajectory of the lubricating oil which does not pass center CP into a rotation coordinate system.
　また、インプットシャフト２の中心ＣＰを通る潤滑油の軌跡ＬＣを、インプットシャフト２における回転座標系に変換することによって求めた相対軌跡ＬＣ’上の貫通孔２ｃに加えて、インプットシャフト２の中心ＣＰを通らない潤滑油の軌跡を、回転座標系に変換することによって求めた相対軌跡上にも貫通孔を設定する構成としても良い。本形態によれば、より効果的に潤滑油を内孔２ｂに供給することができる。 Further, in addition to the through hole 2c on the relative locus LC ′ obtained by converting the locus LC of the lubricating oil passing through the center CP of the input shaft 2 into the rotational coordinate system of the input shaft 2, the center CP of the input shaft 2 is obtained. It is good also as a structure which sets a through-hole also on the relative locus calculated | required by converting the locus | trajectory of the lubricating oil which does not pass into a rotation coordinate system. According to this embodiment, the lubricating oil can be supplied to the inner hole 2b more effectively.
　本実施形態では、飛散する潤滑油の相対軌跡がインプットシャフト２の軸直角断面を横切る部分を直線近似した線を、貫通孔２ｃの中心線ＣＬとする構成としたが、飛散する潤滑油の相対軌跡がインプットシャフト２の軸直角断面を横切る部分そのままの形状（曲線）を貫通孔２ｃの中心線ＣＬとする構成としても良い。 In the present embodiment, the line in which the relative locus of the scattered lubricating oil crosses the section perpendicular to the axis of the input shaft 2 is linearly approximated as the center line CL of the through hole 2c. It is good also as a structure which makes the center line CL of the through-hole 2c the shape (curve | curve) as it is as the part where a locus | trajectory crosses the cross section orthogonal to the axis of the input shaft 2.
　本実施形態では、貫通孔２ｃは、インプットシャフト２における拡径部２ａの周方向に３箇所形成する構成としたが、貫通孔２ｃの数はこれに限定されるものではない。例えば、貫通孔２ｃを拡径部２ａに１箇所だけ形成する構成としても良い。あるいは、貫通孔２ｃを拡径部２ａに４箇所以上形成する構成としても良い。なお、貫通孔２ｃを周方向に複数箇所形成する場合には、必ずしも周方向に等間隔に形成する必要はない。 In the present embodiment, the three through holes 2c are formed in the circumferential direction of the enlarged diameter portion 2a in the input shaft 2, but the number of the through holes 2c is not limited thereto. For example, it is good also as a structure which forms the through-hole 2c only in one place in the enlarged diameter part 2a. Or it is good also as a structure which forms the through-hole 2c in four or more places in the enlarged diameter part 2a. In addition, when forming the through-hole 2c in multiple places in the circumferential direction, it does not necessarily need to form in the circumferential direction at equal intervals.
　本実施形態では、貫通孔２ｃは、インプットシャフト２における拡径部２ａの軸方向に１箇所のみ形成する構成としたが、貫通孔２ｃは、拡径部２ａの軸方向に２箇所以上形成する構成としても良い。 In the present embodiment, the through hole 2c is configured to be formed at only one location in the axial direction of the enlarged diameter portion 2a in the input shaft 2, but the through hole 2c is formed at two or more locations in the axial direction of the enlarged diameter portion 2a. It is good also as a structure.
　本実施形態では、変速機１におけるパイロットベアリングＰＢの潤滑に適用する構成としたが、これに限らない。例えば、インプットシャフト２の内孔２ｂを介して、被動ギヤＧ’のうち遊転ギヤを回転可能に支持するベアリングや、シンクロ機構Ｓの潤滑に適用する構成としても良い。この場合、インプットシャフト２の内孔２ｂあるいは当該内孔２ｂに連通するようにアウトプットシャフト６に形成された内孔から、上述したベアリングやシンクロ機構Ｓに向けて径方向に貫通する貫通孔を形成する構成とすれば良い。 In the present embodiment, the configuration is applied to the lubrication of the pilot bearing PB in the transmission 1, but the present invention is not limited to this. For example, it may be configured to apply lubrication to the bearing or the synchro mechanism S that rotatably supports the idle gear of the driven gear G ′ via the inner hole 2 b of the input shaft 2. In this case, a through hole penetrating in the radial direction toward the bearing or the synchro mechanism S is formed from the inner hole 2b of the input shaft 2 or the inner hole formed in the output shaft 6 so as to communicate with the inner hole 2b. What is necessary is just to be the structure to do.
　本実施形態では、変速機１に適用する構成としたが、これに限らない。例えば、回転体の内孔に潤滑油を供給する必要がある装置や機構に適用可能である。 In the present embodiment, the configuration is applied to the transmission 1, but is not limited thereto. For example, the present invention can be applied to an apparatus or a mechanism that needs to supply lubricating oil to the inner hole of the rotating body.
（実施形態の各構成要素と本発明の各構成要素の対応関係）
　本実施形態は、本発明を実施するための形態の一例を示すものである。したがって、本発明は、本実施形態の構成に限定されるものではない。 (Correspondence between each component of the embodiment and each component of the present invention)
This embodiment shows an example for carrying out the present invention. Therefore, the present invention is not limited to the configuration of the present embodiment.
　１　　変速機
　２　　インプットシャフト
　２ａ　拡径部
　２ｂ　内孔
　２ｃ　貫通孔
　２ｄ　貫通孔
　４　　カウンタシャフト
　６　　アウトプットシャフト
　８　　ケーシング
　Ｂ１　ベアリング
　Ｂ２　ベアリング
　Ｂ３　ベアリング
　Ｂ４　ベアリング
　ＧＭ　リダクションギヤ機構
　ＴＭ　変速機構
　ＲＧ　リダクションドライブギヤ
　ＲＧ’リダクションドリブンギヤ
　ＣＬ　中心線
　ＲＬ　仮想径方向線
　ＰＢ　パイロットベアリング
　Ｇ　　駆動ギヤ
　Ｇ’　被動ギヤ
　Ｓ　　シンクロ機構
　ＥＬ　共通外接線
　ＩＬ　共通内接線
　Ｐ１　点
　Ｐ２　点
　θ１　回転角度
　θ２　回転角度
　ＬＣ　軌跡
　ＬＣ’相対軌跡
　ＣＰ　インプットシャフトの中心 DESCRIPTION OF SYMBOLS 1 Transmission 2 Input shaft 2a Expanding part 2b Inner hole 2c Through hole 2d Through hole 4 Counter shaft 6 Output shaft 8 Casing B1 Bearing B2 Bearing B3 Bearing B4 Bearing GM Reduction gear mechanism TM Transmission mechanism RG Reduction drive gear RG 'Reduction driven gear CL Center line RL Virtual radial direction line PB Pilot bearing G Drive gear G 'Driven gear S Synchro mechanism EL Common external tangent line IL Common internal tangent line P1 point P2 point θ1 rotation angle θ2 rotation angle LC locus LC' relative locus CP Center of input shaft

Claims (9)

  1. 　内孔を有する第１回転体と、該第１回転体の回転に対応した回転を行う第２回転体と、を備え、前記第２回転体によって掻き上げられた潤滑油を前記内孔に供給する潤滑構造であって、
    　前記第２回転体によって掻き上げられて飛散する潤滑油のうち、回転する前記第１回転体から見た際の前記潤滑油の軌跡に沿う潤滑油の少なくとも一部を前記内孔に導入するよう構成されている　
    　潤滑構造。     A first rotating body having an inner hole; and a second rotating body that rotates in accordance with the rotation of the first rotating body, and supplies the lubricating oil scraped up by the second rotating body to the inner hole. A lubricating structure
    Of the lubricating oil that is scraped up and scattered by the second rotating body, at least part of the lubricating oil along the locus of the lubricating oil when viewed from the rotating first rotating body is introduced into the inner hole. It is configured
    Lubrication structure.
  2. 　前記第１回転体には、該第１回転体の外周面から前記内孔まで貫通する貫通孔が形成されており、
    　該貫通孔は、前記軌跡に沿うよう構成されている
    　請求項１に記載の潤滑構造。     In the first rotating body, a through hole penetrating from the outer peripheral surface of the first rotating body to the inner hole is formed,
    The lubricating structure according to claim 1, wherein the through hole is configured to follow the locus.
  3. 　前記貫通孔は、前記第１回転体の径方向線に対して、該第１回転体の回転方向後方にオフセットした中心線を有する構成とされている
    　請求項２に記載の潤滑構造。     The lubricating structure according to claim 2, wherein the through-hole has a center line that is offset rearward in the rotational direction of the first rotating body with respect to a radial line of the first rotating body.
  4. 　前記第１回転体は、第１回転軸と、該第１回転軸に設けられた第１歯車と、を有し、
    　前記第２回転体は、前記第１回転軸に平行配置された第２回転軸と、該第２回転軸に設けられると共に前記第１歯車と噛み合う第２歯車と、を有し、
    　前記貫通孔は、前記第１回転軸に形成されている
    　請求項２または３に記載の潤滑構造。     The first rotating body has a first rotating shaft and a first gear provided on the first rotating shaft,
    The second rotating body has a second rotating shaft arranged in parallel to the first rotating shaft, and a second gear provided on the second rotating shaft and meshing with the first gear,
    The lubricating structure according to claim 2, wherein the through hole is formed in the first rotating shaft.
  5. 　前記貫通孔は、前記第１歯車に隣接して形成されており、
    　前記第２歯車は、前記貫通孔と軸方向においてオーバーラップするよう構成されている
    　請求項４に記載の潤滑構造。     The through hole is formed adjacent to the first gear;
    The lubricating structure according to claim 4, wherein the second gear is configured to overlap the through hole in the axial direction.
  6. 　前記内孔に軸受部材を介して回転可能に支持された第３回転体をさらに備え、
    　前記第２回転体によって掻き上げられて飛散する潤滑油を、前記貫通孔を介して前記軸受部材に供給するよう構成されている
    　請求項２ないし５のいずれか１項に記載の潤滑構造。     A third rotating body rotatably supported by the inner hole via a bearing member;
    The lubricating structure according to any one of claims 2 to 5, wherein the lubricating oil that is scooped up and scattered by the second rotating body is supplied to the bearing member through the through hole.
  7. 　内孔を有する入力軸と、
    　該入力軸に設けられた減速駆動歯車と、
    　前記入力軸に平行配置されたカウンタ軸と、
    　該カウンタ軸に設けられ前記減速駆動歯車と噛合する減速被駆動歯車と、
    　前記内孔に軸受部材を介して回転可能に支持された出力軸と、
    　を備え、
    　前記減速被駆動歯車によって掻き上げられて飛散する潤滑油を、請求項１ないし６のいずれか１項に記載の潤滑構造を用いて前記内孔に供給するよう構成されている変速機。     An input shaft having an inner hole;
    A reduction drive gear provided on the input shaft;
    A counter shaft arranged parallel to the input shaft;
    A reduction driven gear provided on the counter shaft and meshing with the reduction driving gear;
    An output shaft rotatably supported by a bearing member in the inner hole;
    With
    A transmission configured to supply lubricating oil that is scraped and scattered by the reduction driven gear to the inner hole using the lubricating structure according to any one of claims 1 to 6.
  8. 　内孔を有する入力軸と、
    　該入力軸に設けられた駆動歯車と、
    　前記入力軸に平行配置されたカウンタ軸と、
    　該カウンタ軸に設けられ前記駆動歯車と噛合する被駆動歯車と、
    　前記カウンタ軸に設けられた出力駆動歯車と、
    　前記内孔に軸受部材を介して回転可能に支持された出力軸と、
    　前記出力軸に設けられ前記出力駆動歯車と噛合する出力被駆動歯車と、
    　を備え、
    　前記出力駆動歯車によって掻き上げられて飛散する潤滑油を、請求項１ないし６のいずれか１項に記載の潤滑構造を用いて前記内孔に供給するよう構成されている変速機。     An input shaft having an inner hole;
    A drive gear provided on the input shaft;
    A counter shaft arranged parallel to the input shaft;
    A driven gear provided on the counter shaft and meshing with the driving gear;
    An output drive gear provided on the counter shaft;
    An output shaft rotatably supported by a bearing member in the inner hole;
    An output driven gear provided on the output shaft and meshing with the output driving gear;
    With
    The transmission configured to supply the lubricating oil that is scraped and scattered by the output drive gear to the inner hole using the lubricating structure according to any one of claims 1 to 6.
  9. 　内孔を有する第１回転体と、該第１回転体の回転に対応した回転を行う第２回転体と、を備え、前記第２回転体によって掻き上げられた潤滑油を前記内孔に供給する潤滑方法であって、
    　前記第１回転体には、該第１回転体の外周面から前記内孔まで貫通する貫通孔が形成されており、
    　前記第２回転体によって掻き上げられて飛散する潤滑油を、回転する前記第１回転体から見た際の前記潤滑油の軌跡である相対軌跡に沿うよう構成されている前記貫通孔によって捕捉して前記内孔に供給する
    　潤滑方法。     A first rotating body having an inner hole; and a second rotating body that rotates in accordance with the rotation of the first rotating body, and supplies the lubricating oil scraped up by the second rotating body to the inner hole. A lubricating method for
    In the first rotating body, a through hole penetrating from the outer peripheral surface of the first rotating body to the inner hole is formed,
    The lubricating oil that is scraped up and scattered by the second rotating body is captured by the through-hole configured to follow a relative locus that is the locus of the lubricating oil when viewed from the rotating first rotating body. Lubrication method for supplying to the inner hole.
PCT/JP2014/072463 2013-11-28 2014-08-27 Lubrication structure and lubrication method WO2015079758A1 (en)

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EP3336385A1 (en) * 2016-12-16 2018-06-20 ZF Friedrichshafen AG Assembly for lubricating a transmission, motor vehicle transmission and motor vehicle

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR101795170B1 (en) 2015-11-27 2017-11-07 현대 파워텍 주식회사 Output shaft of automatic transmission with function of storing oil and automatic transmission having the same

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JPS5088769U (en) * 1973-12-18 1975-07-28
JPS5659060A (en) * 1979-10-22 1981-05-22 Toyota Motor Corp Bearing lubrication mechanism for speed change gear
JPS56108051U (en) * 1980-01-21 1981-08-21
JPS6194649U (en) * 1984-11-28 1986-06-18
JPH10153252A (en) * 1996-09-30 1998-06-09 Mazda Motor Corp Gear transmission structure

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JPS5088769U (en) * 1973-12-18 1975-07-28
JPS5659060A (en) * 1979-10-22 1981-05-22 Toyota Motor Corp Bearing lubrication mechanism for speed change gear
JPS56108051U (en) * 1980-01-21 1981-08-21
JPS6194649U (en) * 1984-11-28 1986-06-18
JPH10153252A (en) * 1996-09-30 1998-06-09 Mazda Motor Corp Gear transmission structure

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3336385A1 (en) * 2016-12-16 2018-06-20 ZF Friedrichshafen AG Assembly for lubricating a transmission, motor vehicle transmission and motor vehicle
DE102016225255A1 (en) * 2016-12-16 2018-06-21 Zf Friedrichshafen Ag Arrangement for lubricating a transmission, motor vehicle transmission and motor vehicle
CN108204445A (en) * 2016-12-16 2018-06-26 Zf腓特烈斯哈芬股份公司 For lubricating the component of speed changer, vehicle transmission and motor vehicle

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