WO2016204200A1 - Transmission - Google Patents

Transmission Download PDF

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Publication number
WO2016204200A1
WO2016204200A1 PCT/JP2016/067855 JP2016067855W WO2016204200A1 WO 2016204200 A1 WO2016204200 A1 WO 2016204200A1 JP 2016067855 W JP2016067855 W JP 2016067855W WO 2016204200 A1 WO2016204200 A1 WO 2016204200A1
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WO
WIPO (PCT)
Prior art keywords
gear
transmission
shaft
speed
lubricating oil
Prior art date
Application number
PCT/JP2016/067855
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French (fr)
Japanese (ja)
Inventor
慎志 鎌田
Original Assignee
いすゞ自動車株式会社
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Filing date
Publication date
Application filed by いすゞ自動車株式会社 filed Critical いすゞ自動車株式会社
Publication of WO2016204200A1 publication Critical patent/WO2016204200A1/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
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H57/021—Shaft support structures, e.g. partition walls, bearing eyes, casing walls or covers with bearings
    • 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

Definitions

  • the present invention relates to a transmission, and more particularly to a technique for supplying lubricating oil in the transmission.
  • lubricating oil is supplied to each part in the transmission in order to reduce friction generated in a plurality of gears and the like.
  • a technique for supplying lubricating oil to a planetary gear mechanism in a transmission is known (see Patent Document 1).
  • the present invention has been made in view of the above problems, and an object thereof is to provide a technique capable of appropriately supplying lubricating oil to a gear.
  • a transmission according to an aspect of the present invention is provided with a shaft capable of releasing lubricating oil from the inside in a radial direction, one or more gears provided on the shaft, and a lower portion of the shaft. And a guide portion having a guide surface extending in the axial direction of the shaft toward the gear and capable of guiding the lubricating oil discharged from the shaft toward the gear.
  • the shaft is formed with a radial flow path for discharging the internal lubricating oil in the radial direction, and is attached to the shaft so as to face the outlet of the radial flow path. It may further include a dispersion / release member capable of dispersing and releasing the lubricating oil discharged from the outlet in a plurality of radial directions, and the guide surface of the guide member may be disposed below the dispersion / release member.
  • the transmission may further include a bearing that supports the shaft, a transmission case, and a bearing retainer that supports the transmission case on the bearing, and the bearing retainer may include a guide portion.
  • the bearing retainer may be integrally formed.
  • the gear may be a planetary gear mechanism.
  • the height of the guide surface of the guide member may be higher than the height of the lower end of the sun gear of the planetary gear mechanism.
  • lubricating oil can be appropriately supplied to the gear.
  • FIG. 1 shows an outline of a mechanical automatic manual transmission according to an embodiment of the present invention.
  • FIG. 2 is a sectional view of the periphery of the auxiliary transmission according to the embodiment of the present invention.
  • FIG. 3 is a front view of the bearing retainer according to the embodiment of the present invention.
  • FIG. 1 shows an outline of a mechanical automatic manual transmission according to an embodiment of the present invention.
  • a mechanical automatic manual transmission (hereinafter also referred to as a transmission) 1 includes an input shaft 10, a main shaft 11 arranged coaxially with the input shaft 10, and coaxially with the main shaft 11 on the output side of the main shaft 11.
  • the auxiliary transmission 60 arranged, and the counter shaft 12 and the reverse idler shaft 16 arranged in parallel with the input shaft 10 and the main shaft 11 are provided.
  • the input main gear 13 is provided on the input shaft 10 so as to be integrally rotatable.
  • the main shaft 11 includes, in order from the input side, a first hub 21, a 5th / 9th speed main gear M5, a 3rd / 7th speed main gear M3, a second hub 31, a 2nd / 6th speed main gear M2, a first speed main gear M1, A third hub 41, a reverse main gear MR, a guide piece 53, and a sun gear 61 of the auxiliary transmission 60 are provided.
  • the 5-speed / 9-speed main gear M5, 3-speed / 7-speed main gear M3, 2-speed / 6-speed main gear M2, 1-speed main gear M1, and reverse main gear MR are provided on the main shaft 11 so as to be relatively rotatable.
  • the second hub 31, the third hub 41, the guide piece 53, and the sun gear 61 are provided on the main shaft 11 so as to be integrally rotatable.
  • the auxiliary transmission 60 transmits the rotation of the main shaft 11 to the carrier 63 (output shaft) by switching between the high range and the low range.
  • the auxiliary transmission 60 is configured by, for example, a planetary gear mechanism.
  • the auxiliary transmission 60 includes a sun gear 61, a plurality of planetary gears 62 disposed around the sun gear 61 so as to mesh with the sun gear 61, and a ring gear 64 formed with internal teeth that mesh with the planetary gear 62.
  • a carrier 63 that rotatably supports the plurality of planetary gears 62.
  • the output side of the carrier 63 has a cylindrical shape coaxial with the main shaft 11.
  • An output side of the ring gear 64 surrounds a cylindrical portion of the carrier 63, and an annular portion 65 that can rotate relative to the carrier 63 is formed.
  • a fourth hub 66 is provided in the annular portion 65 so as to be integrally rotatable.
  • the main shaft 11 Inside the main shaft 11, it extends in the axial direction and extends in the axial direction to the outer peripheral surface of the main shaft 11 from the axial flow channel 11 a to flow the lubricating oil.
  • One or more radial flow paths 11b for discharging from the opening (exit) are formed.
  • the radial flow path 11b is formed in each of the fifth speed / 9th speed main gear M5, the third speed / 7th speed main gear M3, the second speed / 6th speed main gear M2, the first speed main gear M1, the reverse main gear MR, and the guide piece 53. It is provided at a position facing the peripheral surface.
  • the counter shaft 12 meshes with the input counter gear 14 meshed with the input main gear 13 and the 5th / 9th counter gear C5 and 3rd / 7th main gear M3 meshed with the 5th / 9th main gear M5 in order from the input side.
  • a reverse counter gear CR that meshes with the idler gear 17 is provided.
  • the input counter gear 14, the 5th / 9th counter gear C5, the 3rd / 7th counter gear C3, the 2nd / 6th counter gear C2, the 1st speed counter gear C1, and the reverse counter gear CR are integrated with the counter shaft 12. It is provided so as to be rotatable. On the output side of the countershaft 12, a countershaft brake 15 for braking the rotation of the countershaft 12 is provided.
  • An idler gear 17 is provided on the reverse idler shaft 16 so as to be relatively rotatable.
  • the idler gear 17 meshes with the reverse counter gear CR and the reverse main gear MR.
  • a first sleeve 22 is attached to the first hub 21 so that it cannot rotate but can move in the axial direction.
  • a synchronizer ring may be interposed between the first sleeve 22 and each of the input main gear 13 and a dog gear (not shown) fixed to each of the fifth speed / 9th speed main gear M5.
  • a shift fork (not shown) that moves the first sleeve 22 in the axial direction is engaged with the outer circumferential groove of the first sleeve 22.
  • a second sleeve 32 is attached to the second hub 31 so as not to rotate but to move in the axial direction.
  • a synchronizer ring may be interposed between the second sleeve 32 and a dog gear (not shown) fixed to each of the third speed / 7th speed main gear M3 and the second speed / 6th speed main gear M2.
  • a shift fork (not shown) that moves the second sleeve 32 in the axial direction is engaged with the outer circumferential concave groove of the second sleeve 32.
  • a third sleeve 42 is attached to the third hub 41 so as not to rotate but to move in the axial direction.
  • a synchronizer ring may be interposed between the third sleeve 42 and a dog gear (not shown) fixed to each of the first speed main gear M1 and the reverse main gear MR.
  • a shift fork (not shown) that moves the third sleeve 42 in the axial direction is engaged with the outer circumferential concave groove of the third sleeve 42.
  • the third sleeve 42 moves in the direction of arrow A in the drawing and is spline-engaged with the dog gear connected to the first-speed main gear M1, the input main gear 13, the input counter gear 14, the first-speed counter gear C1, and the first-speed main gear M1 are passed through.
  • power is transmitted to the main shaft 11.
  • the range of the sub-transmission 60 is fixedly set to one range (for example, the low range). Therefore, the carrier 63 rotates at the first speed.
  • the third sleeve 42 moves in the direction of arrow B in the drawing and is spline-engaged with the dog gear connected to the reverse main gear MR, the input main gear 13, the input counter gear 14, the reverse counter gear CR, the idler gear 17, and the reverse main gear MR are passed through.
  • power is transmitted to the main shaft 11.
  • the range of the sub-transmission 60 is fixedly set to one range (for example, the low range).
  • the carrier 63 rotates in the reverse direction.
  • a fourth sleeve 67 is attached to the fourth hub 66 so as not to rotate but to move in the axial direction.
  • a synchronizer ring may be interposed between the fourth sleeve 67 and the dog gear of the dog plate 71 and the dog gear fixed to the carrier 63.
  • a shift fork (not shown) that moves the fourth sleeve 67 in the axial direction is engaged with the outer circumferential groove of the fourth sleeve 67.
  • the fourth sleeve 67 moves in the direction of arrow A in the figure and meshes with the dog gear of the dog plate 71 fixed to the transmission case 2 (for example, the center case 2b), the ring gear 64 is fixed to the transmission case 2.
  • the sub-transmission 60 is in the low range. That is, when the main shaft 11 is rotated by the auxiliary transmission 60, the carrier 63 is rotated at a reduction ratio greater than 1.
  • the fourth sleeve 67 moves in the direction of the arrow B in the drawing and meshes with a dog gear (not shown) fixed to the carrier 63 by spline, the ring gear 64 and the carrier 63 are fixed so as to rotate together, and the sub-gear is rotated.
  • the state of the transmission 60 is in the high range. That is, the main shaft 11 and the carrier 63 are directly connected by the auxiliary transmission 60.
  • the transmission case 2 front case 2 a, center case 2 b, rear case 2 c, etc. except for the input side end of the input shaft 10 and the output side end of the carrier 63. ).
  • Lubricating oil for lubricating each part is supplied to the inside of the transmission case 2.
  • an oil pipe 80 for sucking the lubricating oil stored in the bottom is disposed.
  • the oil pipe 80 is connected to an oil pump (not shown), and the lubricating oil sucked through the oil pipe 80 is supplied to, for example, the axial flow path 11 a of the main shaft 11.
  • FIG. 2 is a sectional view of the periphery of the auxiliary transmission according to the embodiment of the present invention.
  • the main shaft 11 is rotatably supported by the transmission case 2 (center case 2b) via a bearing 51.
  • the bearing 51 is fixed (supported) to the center case 2 b by a bearing retainer 52.
  • a guide piece 53 (an example of a dispersion release member) is fixed to the main shaft 11 so as to be rotatable together with the main shaft 11 at a position in the arrow B direction from the bearing 51 of the main shaft 11.
  • An annular distribution space 53 a is formed in the guide piece 53 so as to surround the outer periphery of the main shaft 11 at a portion facing the outlet of the radial flow path 11 b of the main shaft 11.
  • the guide piece 53 is formed with a plurality of discharge holes 53b extending in the radial direction from the circulation space 53a.
  • the discharge hole 53b is formed to be inclined toward the sub-transmission 60 (in the direction of arrow B).
  • the lubricating oil supplied to the axial flow path 11a of the main shaft 11 reaches the flow space 53a of the guide piece 53 through the radial flow path 11b.
  • the lubricating oil that has reached the circulation space 53a is dispersed and discharged toward the auxiliary transmission 60 from the plurality of discharge holes 53b.
  • the bearing retainer 52 has a guide portion 52 a having a guide surface extending in the axial direction of the main shaft 11 from the lower side of the guide piece 53 to the side surface of the sun gear 61 of the auxiliary transmission 60.
  • the guide portion 52 a receives the lubricating oil discharged downward from the discharge hole 53 b of the guide piece 53 and guides it to the side surface of the sun gear 61.
  • the height of the upper surface of the guide portion 52 a is equal to or higher than the height of the lower tooth portion of the sun gear 61. Accordingly, the lubricating oil can be appropriately supplied to the meshing portion between the sun gear 61 and the planetary gear 62 by the guide portion 52a.
  • FIG. 3 is a front view of a bearing retainer according to an embodiment of the present invention. 3 is a view of the bearing retainer as seen from the direction of arrow B in FIG. In FIG. 3, the positions of the bearings 51 of the main shaft 11 and the counter shaft 12 supported by the bearing retainer are indicated by broken lines.
  • the bearing retainer 52 has an approximately 8 shape, and a through hole 52b through which the main shaft 11 passes and a through hole 52c through which the counter shaft 12 passes are formed.
  • a substantially arc-shaped guide portion 52a is provided at the lower peripheral portion of the through hole 52b.
  • the bearing retainer 52 is integrally formed by a predetermined mold, for example. Thus, since the bearing retainer 52 is integrally molded, it is not necessary to prepare the guide portion 52a as another configuration, and the number of parts in the transmission 1 can be prevented from increasing.
  • the bearing retainer 52 is fixed to the transmission case 2 (the wall of the center case 2b) by, for example, a bolt 54.
  • the through hole 52b is smaller than the outer diameter of the bearing 51 that supports the main shaft 11, and the peripheral portion of the through hole 52b acts to hold the bearing 51 against the center case 2b.
  • the through hole 52c is smaller than the outer diameter of the bearing 51 that supports the countershaft 12, and the peripheral portion of the through hole 52c acts to hold the bearing 51 against the center case 2b.
  • the guide oil 52a of the bearing retainer 52 guides the lubricating oil released from the main shaft 11 in the radial direction to the sun gear 61 of the auxiliary transmission 60.
  • Lubricating oil can be effectively supplied to each part of the auxiliary transmission 60 (for example, a meshing portion between the sun gear 61 and the planetary gear 62).
  • the guide retainer 52a is provided on the bearing retainer 52 fixed to the transmission case 2, it is necessary to prepare a new component for attaching the guide 52a and to consider the arrangement of the component. And can be handled relatively easily.
  • the guide retainer 52a is provided by integrally molding the bearing retainer 52, the number of parts in the transmission 1 can be suppressed.
  • the guide portion 52a guides the lubricating oil to the gear of the sub-transmission 60.
  • the present invention is not limited to this, and the lubricating oil is guided to other gears in the transmission 1. You may make it do.
  • the guide retainer 52a is provided in the bearing retainer 52.
  • the present invention is not limited to this, and the guide may be provided in another member.
  • the transmission of the present invention is useful in that the lubricating oil can be appropriately supplied to the gear.

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

Abstract

A transmission 1 is configured so as to have: a main shaft 11 capable of discharging lubricating oil in a radial direction from the interior; a sun gear 61 provided to the main shaft 11; and a guide part 52a disposed below the main shaft 11, extending in the axial direction of the main shaft 11 toward the sun gear 61, and having a guide surface capable of guiding the lubricating oil discharged from the main shaft 11 toward the sun gear 61.

Description

変速機transmission
　本発明は、変速機に関し、特に、変速機において潤滑油を供給する技術に関する。 The present invention relates to a transmission, and more particularly to a technique for supplying lubricating oil in the transmission.
　従来、変速機においては、複数のギヤ等に発生する摩擦を低減するために変速機内の各部に潤滑油を供給している。例えば、変速機内の遊星歯車機構に潤滑油を供給する技術が知られている（特許文献１参照）。 Conventionally, in a transmission, lubricating oil is supplied to each part in the transmission in order to reduce friction generated in a plurality of gears and the like. For example, a technique for supplying lubricating oil to a planetary gear mechanism in a transmission is known (see Patent Document 1).
日本国実開平６－４７７６４号公報Japanese National Utility Model Publication No. 6-47764
　変速機においては、如何にギヤに潤滑油を供給するかが非常に重要である。例えば、遊星歯車機構を有する変速機においては、メインシャフトから遊星歯車機構の内部に至るオイル流路を形成することが考えられるが、構造が複雑であるので対応が困難であり、対応する場合には、多大なコストを要する問題がある。 In transmissions, how to supply lubricant to gears is very important. For example, in a transmission having a planetary gear mechanism, it may be possible to form an oil flow path from the main shaft to the inside of the planetary gear mechanism. Is a problem that requires a great deal of cost.
　また、遊星歯車機構に限らず、変速機内の他のギヤに潤滑油を供給する場合にあっても、種々の制約があって対応が困難な場合が多い。 Also, not only the planetary gear mechanism but also when supplying lubricating oil to other gears in the transmission, it is often difficult to respond due to various restrictions.
　本発明は、上記課題に鑑みなされたものであり、その目的は、潤滑油をギヤに適切に供給することのできる技術を提供することにある。 The present invention has been made in view of the above problems, and an object thereof is to provide a technique capable of appropriately supplying lubricating oil to a gear.
　上述の目的を達成するため、本発明の一観点に係る変速機は、内部から径方向に潤滑油を放出可能なシャフトと、シャフトに設けられた１以上のギヤと、シャフトの下方に配置されるとともに、ギヤに向かってシャフトの軸方向に延び、シャフトから放出された潤滑油を前記ギヤに向けて案内可能な案内面を有する案内部と、を有する。 In order to achieve the above object, a transmission according to an aspect of the present invention is provided with a shaft capable of releasing lubricating oil from the inside in a radial direction, one or more gears provided on the shaft, and a lower portion of the shaft. And a guide portion having a guide surface extending in the axial direction of the shaft toward the gear and capable of guiding the lubricating oil discharged from the shaft toward the gear.
　上記変速機において、シャフトには、内部の潤滑油を径方向に放出する径方向流路が形成されており、径方向流路の出口と対向するようにシャフトに装着され、径方向流路の出口から放出された潤滑油を複数の径方向に分散して放出可能な分散放出部材をさらに有し、案内部材の案内面は、分散放出部材の下方に配置されていてもよい。 In the above transmission, the shaft is formed with a radial flow path for discharging the internal lubricating oil in the radial direction, and is attached to the shaft so as to face the outlet of the radial flow path. It may further include a dispersion / release member capable of dispersing and releasing the lubricating oil discharged from the outlet in a plurality of radial directions, and the guide surface of the guide member may be disposed below the dispersion / release member.
　また、上記変速機において、シャフトを支持するベアリングと、変速機ケースと、変速機ケースをベアリングに支持するベアリングリテーナをさらに有し、ベアリングリテーナが案内部を有していてもよい。また、上記変速機において、ベアリングリテーナは、一体成型されていてもよい。 The transmission may further include a bearing that supports the shaft, a transmission case, and a bearing retainer that supports the transmission case on the bearing, and the bearing retainer may include a guide portion. In the above transmission, the bearing retainer may be integrally formed.
　また、上記変速機において、ギヤは、遊星歯車機構のギヤであってもよい。また、上記変速機において、案内部材の案内面の高さは、遊星歯車機構のサンギヤの下端の高さよりも高くてもよい。 In the above transmission, the gear may be a planetary gear mechanism. In the above transmission, the height of the guide surface of the guide member may be higher than the height of the lower end of the sun gear of the planetary gear mechanism.
　本発明によると、潤滑油をギヤに適切に供給することができる。 According to the present invention, lubricating oil can be appropriately supplied to the gear.
図１は、本発明の一実施形態に係る機械式自動マニュアル変速機の概要を示す。FIG. 1 shows an outline of a mechanical automatic manual transmission according to an embodiment of the present invention. 図２は、本発明の一実施形態に係る副変速機の周辺の断面図である。FIG. 2 is a sectional view of the periphery of the auxiliary transmission according to the embodiment of the present invention. 図３は、本発明の一実施形態に係るベアリングリテーナの正面図である。FIG. 3 is a front view of the bearing retainer according to the embodiment of the present invention.
　以下、添付図面に基づいて、本発明の一実施形態に係る変速機について説明する。同一の部品には同一の符号を付してあり、それらの名称および機能も同じである。したがって、それらについての詳細な説明は繰返さない。 Hereinafter, a transmission according to an embodiment of the present invention will be described with reference to the accompanying drawings. The same parts are denoted by the same reference numerals, and their names and functions are also the same. Therefore, detailed description thereof will not be repeated.
　図１は、本発明の一実施形態に係る機械式自動マニュアル変速機の概要を示す。 FIG. 1 shows an outline of a mechanical automatic manual transmission according to an embodiment of the present invention.
　機械式自動マニュアル変速機（以下、変速機とも記載する）１は、インプットシャフト１０と、インプットシャフト１０と同軸に配置されたメインシャフト１１と、メインシャフト１１の出力側にメインシャフト１１と同軸に配置された副変速機６０と、インプットシャフト１０及びメインシャフト１１と平行に配置されたカウンタシャフト１２及びリバースアイドラシャフト１６と、を備えている。 A mechanical automatic manual transmission (hereinafter also referred to as a transmission) 1 includes an input shaft 10, a main shaft 11 arranged coaxially with the input shaft 10, and coaxially with the main shaft 11 on the output side of the main shaft 11. The auxiliary transmission 60 arranged, and the counter shaft 12 and the reverse idler shaft 16 arranged in parallel with the input shaft 10 and the main shaft 11 are provided.
　インプットシャフト１０には、インプットメインギヤ１３が一体回転可能に設けられている。メインシャフト１１には、入力側から順に、第１ハブ２１、５速／９速メインギヤＭ５、３速／７速メインギヤＭ３、第２ハブ３１、２速／６速メインギヤＭ２、１速メインギヤＭ１、第３ハブ４１、リバースメインギヤＭＲ、ガイドピース５３、副変速機６０のサンギヤ６１が設けられている。５速／９速メインギヤＭ５、３速／７速メインギヤＭ３、２速／６速メインギヤＭ２、１速メインギヤＭ１、及びリバースメインギヤＭＲは、メインシャフト１１に相対回転可能に設けられ、第１ハブ２１、第２ハブ３１、第３ハブ４１、ガイドピース５３、及びサンギヤ６１はメインシャフト１１に一体回転可能に設けられている。 The input main gear 13 is provided on the input shaft 10 so as to be integrally rotatable. The main shaft 11 includes, in order from the input side, a first hub 21, a 5th / 9th speed main gear M5, a 3rd / 7th speed main gear M3, a second hub 31, a 2nd / 6th speed main gear M2, a first speed main gear M1, A third hub 41, a reverse main gear MR, a guide piece 53, and a sun gear 61 of the auxiliary transmission 60 are provided. The 5-speed / 9-speed main gear M5, 3-speed / 7-speed main gear M3, 2-speed / 6-speed main gear M2, 1-speed main gear M1, and reverse main gear MR are provided on the main shaft 11 so as to be relatively rotatable. The second hub 31, the third hub 41, the guide piece 53, and the sun gear 61 are provided on the main shaft 11 so as to be integrally rotatable.
　副変速機６０は、メインシャフト１１の回転をハイと、ローの２つのレンジの何れかに切り替えてキャリア６３（アウトプットシャフト）に伝達する。副変速機６０は、例えば、遊星歯車機構により構成される。具体的には、副変速機６０は、サンギヤ６１と、サンギヤ６１と噛合するようにサンギヤ６１の周囲に配置された複数のプラネタリギヤ６２と、プラネタリギヤ６２と噛合する内歯が形成されたリングギヤ６４と、複数のプラネタリギヤ６２を回転可能に支持するキャリア６３とを有する。キャリア６３の出力側は、メインシャフト１１と同軸の円柱形状となっている。リングギヤ６４の出力側は、キャリア６３の円柱形状の部分を取り囲み、キャリア６３と相対回転可能な円環部６５が形成されている。円環部６５には、第４ハブ６６が一体回転可能に設けられている。 The auxiliary transmission 60 transmits the rotation of the main shaft 11 to the carrier 63 (output shaft) by switching between the high range and the low range. The auxiliary transmission 60 is configured by, for example, a planetary gear mechanism. Specifically, the auxiliary transmission 60 includes a sun gear 61, a plurality of planetary gears 62 disposed around the sun gear 61 so as to mesh with the sun gear 61, and a ring gear 64 formed with internal teeth that mesh with the planetary gear 62. And a carrier 63 that rotatably supports the plurality of planetary gears 62. The output side of the carrier 63 has a cylindrical shape coaxial with the main shaft 11. An output side of the ring gear 64 surrounds a cylindrical portion of the carrier 63, and an annular portion 65 that can rotate relative to the carrier 63 is formed. A fourth hub 66 is provided in the annular portion 65 so as to be integrally rotatable.
　メインシャフト１１の内部には、軸方向に延び、潤滑油を流すための軸方向流路１１ａと、軸方向流路１１ａからメインシャフト１１の外周面に径方向に延び、潤滑油を外周面の開孔（出口）から放出するための１以上の径方向流路１１ｂが形成されている。径方向流路１１ｂは、例えば、５速／９速メインギヤＭ５、３速／７速メインギヤＭ３、２速／６速メインギヤＭ２、１速メインギヤＭ１、リバースメインギヤＭＲ、及びガイドピース５３のそれぞれの内周面に対向する位置に設けられている。 Inside the main shaft 11, it extends in the axial direction and extends in the axial direction to the outer peripheral surface of the main shaft 11 from the axial flow channel 11 a to flow the lubricating oil. One or more radial flow paths 11b for discharging from the opening (exit) are formed. For example, the radial flow path 11b is formed in each of the fifth speed / 9th speed main gear M5, the third speed / 7th speed main gear M3, the second speed / 6th speed main gear M2, the first speed main gear M1, the reverse main gear MR, and the guide piece 53. It is provided at a position facing the peripheral surface.
　カウンタシャフト１２には、入力側から順に、インプットメインギヤ１３と噛合するインプットカウンタギヤ１４、５速／９速メインギヤＭ５と噛合する５速／９速カウンタギヤＣ５、３速／７速メインギヤＭ３と噛合する３速／７速カウンタギヤＣ３、２速／６速メインギヤＭ２と噛合する２速／６速カウンタギヤＣ２、１速メインギヤＭ１と噛合する１速カウンタギヤＣ１、リバースメインギヤＭＲと噛合する後述するアイドラギヤ１７と噛合するリバースカウンタギヤＣＲが設けられている。インプットカウンタギヤ１４、５速／９速カウンタギヤＣ５、３速／７速カウンタギヤＣ３、２速／６速カウンタギヤＣ２、１速カウンタギヤＣ１、及びリバースカウンタギヤＣＲは、カウンタシャフト１２に一体回転可能に設けられている。カウンタシャフト１２の出力側には、カウンタシャフト１２の回転を制動するためのカウンタシャフトブレーキ１５が設けられている。 The counter shaft 12 meshes with the input counter gear 14 meshed with the input main gear 13 and the 5th / 9th counter gear C5 and 3rd / 7th main gear M3 meshed with the 5th / 9th main gear M5 in order from the input side. 3 speed / 7 speed counter gear C3, 2 speed / 6 speed counter gear C2 meshing with 2/6 speed main gear M2, 1st speed counter gear C1 meshing with 1st speed main gear M1, meshing with reverse main gear MR A reverse counter gear CR that meshes with the idler gear 17 is provided. The input counter gear 14, the 5th / 9th counter gear C5, the 3rd / 7th counter gear C3, the 2nd / 6th counter gear C2, the 1st speed counter gear C1, and the reverse counter gear CR are integrated with the counter shaft 12. It is provided so as to be rotatable. On the output side of the countershaft 12, a countershaft brake 15 for braking the rotation of the countershaft 12 is provided.
　リバースアイドラシャフト１６には、アイドラギヤ１７が相対回転可能に設けられている。アイドラギヤ１７は、リバースカウンタギヤＣＲと、リバースメインギヤＭＲと噛合している。 An idler gear 17 is provided on the reverse idler shaft 16 so as to be relatively rotatable. The idler gear 17 meshes with the reverse counter gear CR and the reverse main gear MR.
　第１ハブ２１には、回転不能且つ軸方向に移動可能に第１スリーブ２２が取り付けられている。なお、第１スリーブ２２と、インプットメインギヤ１３及び５速／９速メインギヤＭ５のそれぞれに固定されている図示しないドグギヤとのそれぞれの間にシンクロナイザリングが介装されていてもよい。第１スリーブ２２の外周凹溝には、第１スリーブ２２を軸方向に移動させる図示しないシフトフォークが係合されている。 A first sleeve 22 is attached to the first hub 21 so that it cannot rotate but can move in the axial direction. A synchronizer ring may be interposed between the first sleeve 22 and each of the input main gear 13 and a dog gear (not shown) fixed to each of the fifth speed / 9th speed main gear M5. A shift fork (not shown) that moves the first sleeve 22 in the axial direction is engaged with the outer circumferential groove of the first sleeve 22.
　第１スリーブ２２が図中矢印Ａ方向に移動してインプットメインギヤ１３のドグギヤとスプライン噛合すると、インプットシャフト１０とメインシャフト１１とが直結されて動力が伝達される。この結果、副変速機６０のレンジがローに設定されている場合には、キャリア６３は、４速相当で回転し、副変速機６０のレンジがハイに設定されている場合には、キャリア６３は、８速相当で回転する。 When the first sleeve 22 moves in the direction of arrow A in the drawing and engages with the dog gear of the input main gear 13 by spline, the input shaft 10 and the main shaft 11 are directly connected to transmit power. As a result, when the range of the auxiliary transmission 60 is set to low, the carrier 63 rotates at a speed equivalent to the fourth speed, and when the range of the auxiliary transmission 60 is set to high, the carrier 63 is rotated. Rotates at 8th speed.
　第１スリーブ２２が図中矢印Ｂ方向に移動して５速／９速メインギヤＭ５に接続されているドグギヤとスプライン噛合すると、インプットメインギヤ１３、インプットカウンタギヤ１４、５速／９速カウンタギヤＣ５、５速／９速メインギヤＭ５、を介してメインシャフト１１に動力が伝達される。この結果、副変速機６０のレンジがローに設定されている場合には、キャリア６３は、５速相当で回転し、副変速機６０のレンジがハイに設定されている場合には、キャリア６３は、９速相当で回転する。 When the first sleeve 22 moves in the direction of arrow B in the drawing and is spline-engaged with the dog gear connected to the 5-speed / 9-speed main gear M5, the input main gear 13, the input counter gear 14, the 5-speed / 9-speed counter gear C5, Power is transmitted to the main shaft 11 via the 5th / 9th speed main gear M5. As a result, when the range of the auxiliary transmission 60 is set to low, the carrier 63 rotates at the fifth speed, and when the range of the auxiliary transmission 60 is set to high, the carrier 63 is rotated. Rotates at 9th speed.
　第２ハブ３１には、回転不能且つ軸方向に移動可能に第２スリーブ３２が取り付けられている。なお、第２スリーブ３２と、３速／７速メインギヤＭ３及び２速／６速メインギヤＭ２のそれぞれに固定されている図示しないドグギヤとのそれぞれの間にシンクロナイザリングが介装されていてもよい。第２スリーブ３２の外周凹溝には、第２スリーブ３２を軸方向に移動させる図示しないシフトフォークが係合されている。 A second sleeve 32 is attached to the second hub 31 so as not to rotate but to move in the axial direction. A synchronizer ring may be interposed between the second sleeve 32 and a dog gear (not shown) fixed to each of the third speed / 7th speed main gear M3 and the second speed / 6th speed main gear M2. A shift fork (not shown) that moves the second sleeve 32 in the axial direction is engaged with the outer circumferential concave groove of the second sleeve 32.
　第２スリーブ３２が図中矢印Ａ方向に移動して３速／７速メインギヤＭ３に接続されているドグギヤとスプライン噛合すると、インプットメインギヤ１３、インプットカウンタギヤ１４、３速／７速カウンタギヤＣ３、３速／７速メインギヤＭ３を介して動力がメインシャフト１１に伝達される。この結果、副変速機６０のレンジがローに設定されている場合には、キャリア６３は、３速相当で回転し、副変速機６０のレンジがハイに設定されている場合には、キャリア６３は、７速相当で回転する。 When the second sleeve 32 moves in the direction of arrow A in the drawing and is spline-engaged with the dog gear connected to the 3rd / 7th main gear M3, the input main gear 13, the input counter gear 14, the 3rd / 7th counter gear C3, Power is transmitted to the main shaft 11 via the 3rd / 7th speed main gear M3. As a result, when the range of the auxiliary transmission 60 is set to low, the carrier 63 rotates at the third speed, and when the range of the auxiliary transmission 60 is set to high, the carrier 63 is rotated. Rotates at 7th speed.
　第２スリーブ３２が図中矢印Ｂ方向に移動して２速／６速メインギヤＭ２に接続されているドグギヤとスプライン噛合すると、インプットメインギヤ１３、インプットカウンタギヤ１４、２速／６速カウンタギヤＣ２、２速／６速メインギヤＭ２を介して、メインシャフト１１に動力が伝達される。この結果、副変速機６０のレンジがローに設定されている場合には、キャリア６３は、２速相当で回転し、副変速機６０のレンジがハイに設定されている場合には、キャリア６３は、６速相当で回転する。 When the second sleeve 32 moves in the direction of arrow B in the drawing and is spline-engaged with the dog gear connected to the 2nd / 6th speed main gear M2, the input main gear 13, the input counter gear 14, the 2nd / 6th speed counter gear C2, Power is transmitted to the main shaft 11 via the 2nd / 6th speed main gear M2. As a result, when the range of the auxiliary transmission 60 is set to low, the carrier 63 rotates at a speed equivalent to the second speed, and when the range of the auxiliary transmission 60 is set to high, the carrier 63 is rotated. Rotates at the sixth speed.
　第３ハブ４１には、回転不能且つ軸方向に移動可能に第３スリーブ４２が取り付けられている。なお、第３スリーブ４２と、１速メインギヤＭ１及びリバースメインギヤＭＲのそれぞれに固定されている図示しないドグギヤとのそれぞれの間にシンクロナイザリングが介装されていてもよい。第３スリーブ４２の外周凹溝には、第３スリーブ４２を軸方向に移動させる図示しないシフトフォークが係合されている。 A third sleeve 42 is attached to the third hub 41 so as not to rotate but to move in the axial direction. A synchronizer ring may be interposed between the third sleeve 42 and a dog gear (not shown) fixed to each of the first speed main gear M1 and the reverse main gear MR. A shift fork (not shown) that moves the third sleeve 42 in the axial direction is engaged with the outer circumferential concave groove of the third sleeve 42.
　第３スリーブ４２が図中矢印Ａ方向に移動して１速メインギヤＭ１に接続されているドグギヤとスプライン噛合すると、インプットメインギヤ１３、インプットカウンタギヤ１４、１速カウンタギヤＣ１、１速メインギヤＭ１を介して動力がメインシャフト１１に伝達される。本実施形態の変速機１では、１速の変速段が選択される場合には、副変速機６０のレンジは、一方のレンジ（例えば、ローのレンジ）に固定的に設定されるようになっているので、キャリア６３は、１速相当で回転する。 When the third sleeve 42 moves in the direction of arrow A in the drawing and is spline-engaged with the dog gear connected to the first-speed main gear M1, the input main gear 13, the input counter gear 14, the first-speed counter gear C1, and the first-speed main gear M1 are passed through. Thus, power is transmitted to the main shaft 11. In the transmission 1 of the present embodiment, when the first speed is selected, the range of the sub-transmission 60 is fixedly set to one range (for example, the low range). Therefore, the carrier 63 rotates at the first speed.
　第３スリーブ４２が図中矢印Ｂ方向に移動してリバースメインギヤＭＲに接続されているドグギヤとスプライン噛合すると、インプットメインギヤ１３、インプットカウンタギヤ１４、リバースカウンタギヤＣＲ、アイドラギヤ１７、リバースメインギヤＭＲを介して、メインシャフト１１に動力が伝達される。本実施形態の変速機１では、後退（リバース）の変速段が選択される場合には、副変速機６０のレンジは、一方のレンジ（例えば、ローのレンジ）に固定的に設定されるようになっているおり、キャリア６３は、逆回転する。 When the third sleeve 42 moves in the direction of arrow B in the drawing and is spline-engaged with the dog gear connected to the reverse main gear MR, the input main gear 13, the input counter gear 14, the reverse counter gear CR, the idler gear 17, and the reverse main gear MR are passed through. Thus, power is transmitted to the main shaft 11. In the transmission 1 of the present embodiment, when the reverse gear is selected, the range of the sub-transmission 60 is fixedly set to one range (for example, the low range). The carrier 63 rotates in the reverse direction.
　第４ハブ６６には、回転不能且つ軸方向に移動可能に第４スリーブ６７が取り付けられている。なお、第４スリーブ６７と、ドグプレート７１のドグギヤ及びキャリア６３に固定されているドグギヤとのそれぞれの間にシンクロナイザリングが介装されていてもよい。第４スリーブ６７の外周凹溝には、第４スリーブ６７を軸方向に移動させる図示しないシフトフォークが係合されている。 A fourth sleeve 67 is attached to the fourth hub 66 so as not to rotate but to move in the axial direction. A synchronizer ring may be interposed between the fourth sleeve 67 and the dog gear of the dog plate 71 and the dog gear fixed to the carrier 63. A shift fork (not shown) that moves the fourth sleeve 67 in the axial direction is engaged with the outer circumferential groove of the fourth sleeve 67.
　第４スリーブ６７が図中矢印Ａ方向に移動して、変速機ケース２（例えば、センターケース２ｂ）に固定されているドグプレート７１のドグギヤとスプライン噛合すると、リングギヤ６４が変速機ケース２に固定され、副変速機６０の状態がローのレンジとなる。すなわち、副変速機６０によって、メインシャフト１１が回転すると、キャリア６３は１より大きい減速比で回転する。 When the fourth sleeve 67 moves in the direction of arrow A in the figure and meshes with the dog gear of the dog plate 71 fixed to the transmission case 2 (for example, the center case 2b), the ring gear 64 is fixed to the transmission case 2. The sub-transmission 60 is in the low range. That is, when the main shaft 11 is rotated by the auxiliary transmission 60, the carrier 63 is rotated at a reduction ratio greater than 1.
　一方、第４スリーブ６７が図中矢印Ｂ方向に移動して、キャリア６３に固定されている図示しないドグギヤとスプライン噛合すると、リングギヤ６４と、キャリア６３とが一体回転するように固定されて、副変速機６０の状態がハイのレンジとなる。すなわち、副変速機６０によって、メインシャフト１１とキャリア６３とが直結される。 On the other hand, when the fourth sleeve 67 moves in the direction of the arrow B in the drawing and meshes with a dog gear (not shown) fixed to the carrier 63 by spline, the ring gear 64 and the carrier 63 are fixed so as to rotate together, and the sub-gear is rotated. The state of the transmission 60 is in the high range. That is, the main shaft 11 and the carrier 63 are directly connected by the auxiliary transmission 60.
　変速機１においては、基本的には、インプットシャフト１０の入力側端部と、キャリア６３の出力側端部とを除いて、変速機ケース２（フロントケース２ａ、センターケース２ｂ、リアケース２ｃ等）内に収容される。変速機ケース２の内部には、各部を潤滑させるための潤滑油が供給されている。 In the transmission 1, basically, the transmission case 2 (front case 2 a, center case 2 b, rear case 2 c, etc.) except for the input side end of the input shaft 10 and the output side end of the carrier 63. ). Lubricating oil for lubricating each part is supplied to the inside of the transmission case 2.
　変速機ケース２の底部近傍には、底部に貯留している潤滑油を吸引するためのオイルパイプ８０が配置されている。オイルパイプ８０は、図示しないオイルポンプに接続されており、オイルパイプ８０を介して吸引された潤滑油は、例えば、メインシャフト１１の軸方向流路１１ａに供給される。 In the vicinity of the bottom of the transmission case 2, an oil pipe 80 for sucking the lubricating oil stored in the bottom is disposed. The oil pipe 80 is connected to an oil pump (not shown), and the lubricating oil sucked through the oil pipe 80 is supplied to, for example, the axial flow path 11 a of the main shaft 11.
　次に、メインシャフト１１の出力側に設けられた副変速機６０の周辺の構成について説明する。 Next, the configuration around the auxiliary transmission 60 provided on the output side of the main shaft 11 will be described.
　図２は、本発明の一実施形態に係る副変速機の周辺の断面図である。 FIG. 2 is a sectional view of the periphery of the auxiliary transmission according to the embodiment of the present invention.
　メインシャフト１１は、ベアリング５１を介して変速機ケース２（センターケース２ｂ）に回転可能に支持されている。ベアリング５１は、ベアリングリテーナ５２により、センターケース２ｂに固定（支持）されている。 The main shaft 11 is rotatably supported by the transmission case 2 (center case 2b) via a bearing 51. The bearing 51 is fixed (supported) to the center case 2 b by a bearing retainer 52.
　メインシャフト１１のベアリング５１よりも矢印Ｂ方向の位置には、ガイドピース５３（分散放出部材の一例）がメインシャフト１１と一体回転可能に固定されている。ガイドピース５３には、メインシャフト１１の径方向流路１１ｂの出口に臨む部分に、メインシャフト１１の外周を取り囲むように円環形状の流通空間５３ａが形成されている。また、ガイドピース５３には、流通空間５３ａから径方向に延びる複数の放出孔５３ｂが形成されている。放出孔５３ｂは、例えば、副変速機６０側（矢印Ｂ方向）に傾いて形成されている。このような構成により、メインシャフト１１の軸方向流路１１ａに供給された潤滑油は、径方向流路１１ｂを通ってガイドピース５３の流通空間５３ａに到達する。そして、流通空間５３ａに到達した潤滑油は、複数の放出孔５３ｂから副変速機６０に向けて分散して放出される。 A guide piece 53 (an example of a dispersion release member) is fixed to the main shaft 11 so as to be rotatable together with the main shaft 11 at a position in the arrow B direction from the bearing 51 of the main shaft 11. An annular distribution space 53 a is formed in the guide piece 53 so as to surround the outer periphery of the main shaft 11 at a portion facing the outlet of the radial flow path 11 b of the main shaft 11. Further, the guide piece 53 is formed with a plurality of discharge holes 53b extending in the radial direction from the circulation space 53a. For example, the discharge hole 53b is formed to be inclined toward the sub-transmission 60 (in the direction of arrow B). With such a configuration, the lubricating oil supplied to the axial flow path 11a of the main shaft 11 reaches the flow space 53a of the guide piece 53 through the radial flow path 11b. The lubricating oil that has reached the circulation space 53a is dispersed and discharged toward the auxiliary transmission 60 from the plurality of discharge holes 53b.
　ベアリングリテーナ５２は、ガイドピース５３の下方から副変速機６０のサンギヤ６１の側面までメインシャフト１１の軸方向に延びる案内面を有する案内部５２ａを有する。 The bearing retainer 52 has a guide portion 52 a having a guide surface extending in the axial direction of the main shaft 11 from the lower side of the guide piece 53 to the side surface of the sun gear 61 of the auxiliary transmission 60.
　案内部５２ａは、ガイドピース５３の放出孔５３ｂから下方に放出された潤滑油を受けて、サンギヤ６１の側面まで案内する。案内部５２ａの上面の高さは、サンギヤ６１の下側の歯部の高さ以上となっている。したがって、案内部５２ａにより、サンギヤ６１とプラネタリギヤ６２との噛合部分に適切に潤滑油を供給することができる。 The guide portion 52 a receives the lubricating oil discharged downward from the discharge hole 53 b of the guide piece 53 and guides it to the side surface of the sun gear 61. The height of the upper surface of the guide portion 52 a is equal to or higher than the height of the lower tooth portion of the sun gear 61. Accordingly, the lubricating oil can be appropriately supplied to the meshing portion between the sun gear 61 and the planetary gear 62 by the guide portion 52a.
　図３は、本発明の一実施形態に係るベアリングリテーナの正面図である。図３は、図２における矢印Ｂ方向側からベアリングリテーナを見た図である。なお、図３においては、ベアリングリテーナが支持するメインシャフト１１及びカウンタシャフト１２のベアリング５１の位置を破線で示している。 FIG. 3 is a front view of a bearing retainer according to an embodiment of the present invention. 3 is a view of the bearing retainer as seen from the direction of arrow B in FIG. In FIG. 3, the positions of the bearings 51 of the main shaft 11 and the counter shaft 12 supported by the bearing retainer are indicated by broken lines.
　ベアリングリテーナ５２は、略８の字状であり、メインシャフト１１を通す貫通孔５２ｂと、カウンタシャフト１２を通す貫通孔５２ｃとが形成されている。貫通孔５２ｂの下方の周縁部分には、略円弧形状の案内部５２ａが設けられている。ベアリングリテーナ５２は、例えば、所定の金型によって一体成型される。このように、ベアリングリテーナ５２は、一体成型されるので、案内部５２ａを別の構成として用意する必要がなく、変速機１における部品点数を増加させずに済む。ベアリングリテーナ５２は、例えば、ボルト５４により変速機ケース２（センターケース２ｂの壁）に固定される。 The bearing retainer 52 has an approximately 8 shape, and a through hole 52b through which the main shaft 11 passes and a through hole 52c through which the counter shaft 12 passes are formed. A substantially arc-shaped guide portion 52a is provided at the lower peripheral portion of the through hole 52b. The bearing retainer 52 is integrally formed by a predetermined mold, for example. Thus, since the bearing retainer 52 is integrally molded, it is not necessary to prepare the guide portion 52a as another configuration, and the number of parts in the transmission 1 can be prevented from increasing. The bearing retainer 52 is fixed to the transmission case 2 (the wall of the center case 2b) by, for example, a bolt 54.
　貫通孔５２ｂは、メインシャフト１１を支持するベアリング５１の外径よりも小さくなっており、貫通孔５２ｂの周縁部分が、ベアリング５１をセンターケース２ｂに押さえるように作用する。 The through hole 52b is smaller than the outer diameter of the bearing 51 that supports the main shaft 11, and the peripheral portion of the through hole 52b acts to hold the bearing 51 against the center case 2b.
　また、貫通孔５２ｃは、カウンタシャフト１２を支持するベアリング５１の外径よりも小さくなっており、貫通孔５２ｃの周縁部分が、ベアリング５１をセンターケース２ｂに押さえるように作用する。 The through hole 52c is smaller than the outer diameter of the bearing 51 that supports the countershaft 12, and the peripheral portion of the through hole 52c acts to hold the bearing 51 against the center case 2b.
　以上説明したように、本実施形態に係る変速機１によると、メインシャフト１１から径方向に放出された潤滑油をベアリングリテーナ５２の案内部５２ａが副変速機６０のサンギヤ６１に案内するので、副変速機６０の各部（例えば、サンギヤ６１とプラネタリギヤ６２との噛合部分）に潤滑油を効果的に供給することができる。また、変速機ケース２に固定されるベアリングリテーナ５２に案内部５２ａを設けるようにしたので、案内部５２ａを取り付けるための新たな構成部を用意して、その構成部の配置等を考慮する必要がなく、比較的容易に対応できる。また、ベアリングリテーナ５２を一体成型して案内部５２ａを設けるようにしたので、変速機１における部品点数を抑えることができる。 As described above, according to the transmission 1 according to the present embodiment, the guide oil 52a of the bearing retainer 52 guides the lubricating oil released from the main shaft 11 in the radial direction to the sun gear 61 of the auxiliary transmission 60. Lubricating oil can be effectively supplied to each part of the auxiliary transmission 60 (for example, a meshing portion between the sun gear 61 and the planetary gear 62). In addition, since the guide retainer 52a is provided on the bearing retainer 52 fixed to the transmission case 2, it is necessary to prepare a new component for attaching the guide 52a and to consider the arrangement of the component. And can be handled relatively easily. In addition, since the guide retainer 52a is provided by integrally molding the bearing retainer 52, the number of parts in the transmission 1 can be suppressed.
　なお、本発明は、上述の実施形態に限定されるものではなく、本発明の趣旨を逸脱しない範囲で、適宜変形して実施することが可能である。 It should be noted that the present invention is not limited to the above-described embodiment, and can be appropriately modified and implemented without departing from the spirit of the present invention.
　例えば、上記実施形態では、案内部５２ａにより副変速機６０のギヤに潤滑油を案内するようにしていたが、本発明はこれに限られず、変速機１内の他のギヤに潤滑油を案内するようにしてもよい。 For example, in the above embodiment, the guide portion 52a guides the lubricating oil to the gear of the sub-transmission 60. However, the present invention is not limited to this, and the lubricating oil is guided to other gears in the transmission 1. You may make it do.
　また、上記実施形態では、ベアリングリテーナ５２に案内部５２ａを設けるようにしていたが、本発明はこれに限られず、別の部材に案内部を設けるようにしてもよい。 In the above embodiment, the guide retainer 52a is provided in the bearing retainer 52. However, the present invention is not limited to this, and the guide may be provided in another member.
　本出願は、2015年06月18日付で出願された日本国特許出願（特願2015-122855）に基づくものであり、その内容はここに参照として取り込まれる。 This application is based on a Japanese patent application (Japanese Patent Application No. 2015-122855) filed on June 18, 2015, the contents of which are incorporated herein by reference.
　本発明の変速機は、潤滑油をギヤに適切に供給することができるという点において有用である。 The transmission of the present invention is useful in that the lubricating oil can be appropriately supplied to the gear.
１　変速機
２　変速機ケース
２ａ　フロントケース
２ｂ　センターケース
２ｃ　リアケース
１０　インプットシャフト
１１　メインシャフト
１２　カウンタシャフト
１３　インプットメインギヤ
１４　インプットカウンタギヤ
１６　リバースアイドラシャフト
１７　アイドラギヤ
２１　第１ハブ
２２　第１スリーブ
３１　第２ハブ
３２　第２スリーブ
４１　第３ハブ
４２　第３スリーブ
５１　ベアリング
５２　ベアリングリテーナ
５２ａ　案内部
５３　ガイドピース
６０　副変速機
６１　サンギヤ
６２　プラネタリギヤ
６３　キャリア
６４　リングギヤ
６６　第４ハブ
６７　第４スリーブ
Ｍ１　１速メインギヤ
Ｍ２　２速／６速メインギヤ
Ｍ３　３速／７速メインギヤ
Ｍ５　５速／９速メインギヤ
ＭＲ　リバースメインギヤ
Ｃ１　１速カウンタギヤ
Ｃ２　２速／６速カウンタギヤ
Ｃ３　３速／７速カウンタギヤ
Ｃ５　５速／９速カウンタギヤ
ＣＲ　リバースカウンタギヤ DESCRIPTION OF SYMBOLS 1 Transmission 2 Transmission case 2a Front case 2b Center case 2c Rear case 10 Input shaft 11 Main shaft 12 Counter shaft 13 Input main gear 14 Input counter gear 16 Reverse idler shaft 17 Idler gear 21 1st hub 22 1st sleeve 31 2nd hub 32 2nd sleeve 41 3rd hub 42 3rd sleeve 51 Bearing 52 Bearing retainer 52a Guide part 53 Guide piece 60 Sub transmission 61 Sun gear 62 Planetary gear 63 Carrier 64 Ring gear 66 4th hub 67 4th sleeve M1 1st speed main gear M2 2nd speed / 6-speed main gear M3 3-speed / 7-speed main gear M5 5-speed / 9-speed main gear MR Reverse main gear C1 1-speed counter gear C2 2-speed / 6-speed counter gear C3 3-speed / 7-speed Counter gear C5 5-speed / 9-speed counter gear CR Reverse counter gear

Claims (6)

  1. 　内部から径方向に潤滑油を放出可能なシャフトと、
    　前記シャフトに設けられた１以上のギヤと、
    　前記シャフトの下方に配置されるとともに、前記ギヤに向かって前記シャフトの軸方向に延び、前記シャフトから放出された潤滑油を前記ギヤに向けて案内可能な案内面を有する案内部と、
    を有する変速機。     A shaft capable of releasing lubricating oil from the inside in the radial direction;
    One or more gears provided on the shaft;
    A guide portion disposed below the shaft and extending in an axial direction of the shaft toward the gear, and having a guide surface capable of guiding the lubricating oil discharged from the shaft toward the gear;
    A transmission having
  2. 　前記シャフトには、内部の潤滑油を径方向に放出する径方向流路が形成されており、
    　前記径方向流路の出口と対向するように前記シャフトに装着され、前記径方向流路の出口から放出された潤滑油を複数の径方向に分散して放出可能な分散放出部材をさらに有し、
    　前記案内部材の前記案内面は、前記分散放出部材の下方に配置されている請求項１に記載の変速機。     The shaft is formed with a radial flow path for discharging the internal lubricating oil in the radial direction,
    A dispersion release member mounted on the shaft so as to face the outlet of the radial flow path and capable of dispersing and releasing the lubricating oil discharged from the outlet of the radial flow path in a plurality of radial directions is further provided. ,
    The transmission according to claim 1, wherein the guide surface of the guide member is disposed below the dispersion release member.
  3. 　前記シャフトを支持するベアリングと、
    　変速機ケースと、
    　前記変速機ケースを前記ベアリングに支持するベアリングリテーナをさらに有し、
    　前記ベアリングリテーナが前記案内部を有する請求項１又は請求項２に記載の変速機。     A bearing that supports the shaft;
    A transmission case;
    A bearing retainer for supporting the transmission case on the bearing;
    The transmission according to claim 1, wherein the bearing retainer has the guide portion.
  4. 　前記ベアリングリテーナは、一体成型されている請求項３に記載の変速機。 The transmission according to claim 3, wherein the bearing retainer is integrally molded.
  5. 　前記ギヤは、遊星歯車機構のギヤである請求項１から請求項４の何れか１項に記載の変速機。 The transmission according to any one of claims 1 to 4, wherein the gear is a gear of a planetary gear mechanism.
  6. 　前記案内部材の前記案内面の高さは、前記遊星歯車機構のサンギヤの下端の高さよりも高い請求項５に記載の変速機。 The transmission according to claim 5, wherein a height of the guide surface of the guide member is higher than a height of a lower end of a sun gear of the planetary gear mechanism.
PCT/JP2016/067855 2015-06-18 2016-06-15 Transmission WO2016204200A1 (en)

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JP2015122855A JP2017008984A (en) 2015-06-18 2015-06-18 transmission
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CN112984085A (en) * 2019-12-12 2021-06-18 东风商用车有限公司 Gearbox total component layer lubricating structure

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2019090467A (en) * 2017-11-14 2019-06-13 いすゞ自動車株式会社 Lubrication structure of power transmission device

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JPS6241959U (en) * 1985-08-31 1987-03-13
JPH0233961U (en) * 1988-08-29 1990-03-05
JPH0250345B2 (en) * 1988-06-14 1990-11-02 Honda Motor Co Ltd
JPH10281245A (en) * 1997-03-31 1998-10-23 Mitsubishi Motors Corp Belt type transmission for vehicle
JP5557147B2 (en) * 2011-02-04 2014-07-23 アイシン・エィ・ダブリュ株式会社 Vehicle drive device

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Publication number Priority date Publication date Assignee Title
JPS6241959U (en) * 1985-08-31 1987-03-13
JPH0250345B2 (en) * 1988-06-14 1990-11-02 Honda Motor Co Ltd
JPH0233961U (en) * 1988-08-29 1990-03-05
JPH10281245A (en) * 1997-03-31 1998-10-23 Mitsubishi Motors Corp Belt type transmission for vehicle
JP5557147B2 (en) * 2011-02-04 2014-07-23 アイシン・エィ・ダブリュ株式会社 Vehicle drive device

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112984085A (en) * 2019-12-12 2021-06-18 东风商用车有限公司 Gearbox total component layer lubricating structure

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