WO2014006679A1 - 車両用手動変速機 - Google Patents
車両用手動変速機 Download PDFInfo
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- WO2014006679A1 WO2014006679A1 PCT/JP2012/066910 JP2012066910W WO2014006679A1 WO 2014006679 A1 WO2014006679 A1 WO 2014006679A1 JP 2012066910 W JP2012066910 W JP 2012066910W WO 2014006679 A1 WO2014006679 A1 WO 2014006679A1
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- WIPO (PCT)
- Prior art keywords
- shaft
- output shaft
- gear
- input shaft
- housing
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Classifications
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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
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
- F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
- F16H3/087—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears
- F16H3/091—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears including a single countershaft
- F16H3/0915—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears including a single countershaft with coaxial input and output shafts
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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
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
- F16H2200/0047—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising five forward speeds
Definitions
- the present invention relates to a vehicle manual transmission.
- M / T vehicle manual transmissions having a plurality of shift stages for forward movement
- an M / T having the structure shown in FIG. 6 is assumed.
- This M / T is an I / P shaft connected to the clutch, an O / P shaft connected to the drive wheel side and arranged coaxially with the I / P shaft, and a position eccentric from the I / P shaft.
- a counter shaft disposed in parallel with the I / P shaft.
- the counter shaft is provided with a final drive gear so as not to be relatively rotatable
- the O / P shaft is provided with a final driven gear so as not to be relatively rotatable.
- the final drive gear and the final driven gear are always meshed.
- the O / P shaft rotates at a lower rotational speed than the counter shaft.
- the ratio of the rotational speed of the I / P shaft to the rotational speed of the O / P shaft is referred to as a “reduction ratio”.
- a gear stage from “1st speed” (low speed side, large reduction ratio) to “5th speed” (high speed side, small reduction ratio) is provided, and “4th speed” reduction ratio is provided.
- the reduction ratio of the gear stage other than “4th speed” is set to other than “1”.
- Gear speeds other than “fourth speed” are realized by driving the corresponding sleeves and fixing the idle gears of the corresponding gear stages to the shaft where the idle gears are arranged so as not to rotate relative to each other.
- the power transmission system at this time is composed of “I / P shaft ⁇ gear pair of corresponding gears ⁇ counter shaft ⁇ final drive gear ⁇ final driven gear ⁇ O / P shaft”.
- the “fourth speed” gear stage (also referred to as “direct gear shift gear”) drives the corresponding sleeve so that the direct coupling piece provided on the O / P shaft so as not to rotate relative to the I / P shaft. This is realized by fixing the relative rotation to be impossible.
- the power transmission system at this time is constituted by “I / P shaft ⁇ direct connection piece ⁇ O / P shaft”.
- the structure shown in FIG. 6 is also referred to as “output (O / P) reduction structure”.
- the housing includes a housing A and a housing B.
- the housing A accommodates and supports the I / P shaft and the counter shaft.
- the housing B is connected to the housing A at an end portion close to the O / P shaft in the axial direction of the housing A, and houses and supports the O / P shaft.
- the O / P shaft is rotatably supported by the housing using a bearing A and a bearing B.
- the bearing A is disposed at a “position between the direct connection piece and the final driven gear” on the O / P shaft.
- the bearing A is inserted and fixed to a bearing surface formed on the outer periphery of the opening provided at the “end near the O / P shaft” of the housing A.
- the bearing B is disposed at a “position far from the I / P shaft in the axial direction with respect to the final driven gear” in the O / P shaft.
- the bearing B is fixed to the housing B.
- the outer diameter of the direct connection piece is the outer diameter of the bearing A in order to avoid the direct connection piece from interfering with the bearing surface when the direct connection piece is inserted into the opening. Need to be smaller than.
- the outer diameter of the direct connection piece In order to sufficiently secure the capacity of the synchronizer provided close to the direct connection piece in order to reduce the rotational speed difference between the direct connection piece and the I / P shaft, the outer diameter of the direct connection piece The larger the value, the better.
- the outer diameter of the direct connection piece is increased, the outer diameter of the bearing A needs to be increased.
- Increasing the outer diameter of the bearing A leads to an increase in the size of the housing A or an increase in the distance between the I / P shaft and the countershaft, which in turn leads to an increase in the size of the entire M / T.
- the arrival of M / T that can suppress the increase in size of the entire M / T while maintaining the outer diameter of the direct connection piece at a large value has been desired.
- an object of the present invention is an M / T having an “O / P reduction structure”, which can suppress an increase in the overall size of the M / T while maintaining a large outer diameter of the direct connection piece. There is to do.
- the feature of the M / T having the “O / P reduction structure” according to the present invention is that the outer diameter of the direct connection piece is larger than the outer diameter of the first bearing (corresponding to the bearing A described above).
- This structure is different from the above-described procedure (see FIGS. 7 and 8) when the O / P shaft subassembly is assembled to the first housing (corresponding to the housing A described above) (FIGS. 2 to 4 described later). Can be realized (details will be described later).
- the outer diameter of the first bearing (corresponding to the bearing A described above) can be reduced while increasing the outer diameter of the direct connection piece.
- the enlargement of the entire M / T can be suppressed while maintaining the outer diameter of the direct connection piece at a large value.
- the direct connection piece can be connected to the output shaft (corresponding to the above-described O / P shaft) in a relatively non-rotatable manner by spline fitting having a gap.
- the counter shaft has a cylindrical shape having an internal space for circulating lubricating oil, and an oil hole penetrating in the radial direction is provided at a position corresponding to the directly connecting piece in the axial direction of the counter shaft. Preferably it is formed.
- the lubricating oil in the internal space is directed toward the direct connection piece through the oil hole by utilizing the centrifugal force acting on the lubricating oil in the internal space as the counter shaft rotates. Can be applied.
- the lubricating oil can be supplied to the gap of the spline fitting portion between the direct coupling piece and the output shaft, and abnormal heat generation or the like of the spline fitting portion can be suppressed.
- FIG. 2 is a first enlarged view of a Y portion of FIG. 1 for explaining a procedure for assembling an O / P shaft subassembly to a housing HgA for the manual transmission shown in FIG. 1.
- FIG. 4 is a second enlarged view of the Y portion of FIG. 1 for explaining the procedure for assembling the O / P shaft subassembly to the housing HgA for the manual transmission shown in FIG. 1.
- FIG. 6 is a third enlarged view of the Y portion of FIG. 1 for explaining the procedure for assembling the O / P shaft subassembly to the housing HgA for the manual transmission shown in FIG. 1.
- FIG. 7 is a first enlarged view of a Y portion of FIG. 6 for explaining a procedure when the sub assembly of the O / P shaft is assembled to the housing A for the manual transmission shown in FIG. 6.
- FIG. 7 is a second enlarged view of the Y portion of FIG. 6 for explaining a procedure when the sub-assembly of the O / P shaft is assembled to the housing A for the manual transmission shown in FIG. 6.
- the manual transmission M / T includes five shift speeds (1st to 5th gears) for forward movement and one shift speed (reverse) for backward movement, and in particular, an engine (output shaft of the engine). ) Is applied to an FR vehicle arranged vertically with respect to the vehicle.
- description of the reverse gear is omitted.
- the M / T includes an I / P shaft connected to a clutch, an O / P shaft arranged coaxially with the I / P shaft, and an I / P. And a counter shaft arranged in parallel with the I / P shaft at a position eccentric from the shaft.
- the I / P shaft is connected to an output shaft (not shown) of the engine via a clutch.
- the O / P shaft is connected to drive wheels (left and right rear wheels) via a connection mechanism (differential, etc.) not shown.
- This M / T is disposed behind the engine via a clutch so that the axis of the M / T is oriented vertically with respect to the vehicle.
- the fourth speed can also be referred to as a “directly connected gear stage”.
- HgA contains an I / P shaft and a counter shaft
- HgB contains an O / P shaft.
- the I / P shaft includes a bearing BrC (press-fitted / fixed) provided in the clutch housing and a cylindrical end (large end) formed on the “end near the I / P shaft” of the O / P shaft.
- the bearing BrG (press-fitted and fixed) provided inside the diameter portion) is rotatably supported in the HgA.
- a bearing BrA is provided on the outer peripheral surface of the “cylindrical end portion of the O / P shaft” (press-fit / fixed), and this BrA is provided on the “end portion close to the O / P shaft” of HgA. It is press-fitted and fixed to a bearing surface (see FIG. 1) formed on the outer periphery of the opening.
- BrG is substantially anchored to HgA (via BrA).
- the countershaft is rotatably supported in HgA by a bearing BrD (press-fit / fixed) provided in the clutch housing and a bearing BrE (press-fit / fixed) provided in HgB.
- a bearing BrD press-fit / fixed
- a bearing BrE press-fit / fixed
- the O / P shaft is rotatably supported in the HgB by the BrA press-fitted and fixed to the bearing surface of HgA and the bearing BrB provided (press-fitted and fixed) on the HgB.
- the I / P shaft has a fixed gear G1i for the first speed, a fixed gear G2i for the second speed, a fixed gear G5i for the fifth speed, an idle gear G3i for the third speed, a third speed- Four-speed switching hubs H2 are coaxially provided.
- G1i, G2i, and G5i are provided on the I / P shaft so as not to rotate relative to each other.
- G1i, G2i, and G5i are integrally formed with the I / P shaft by using a manufacturing method such as forging.
- G3i is provided to be rotatable relative to the I / P shaft via a bearing BrF press-fitted into the I / P shaft.
- the hub H2 is press-fitted into the I / P shaft and is provided on the I / P shaft so as not to be relatively rotatable.
- the countershaft In order from the side closer to the clutch, the countershaft includes a first-speed idler gear G1o, a first-second-speed switching hub H1, a second-speed idler gear G2o, a fifth-speed idler gear G5o, A 5-speed hub H3 and a 3-speed fixed gear G3o are coaxially provided.
- G3o is integrally formed with the countershaft using a manufacturing method such as forging.
- the outer diameter of the countershaft is continuously constant and the outer circumference of the countershaft is axially
- An outer spline (spline groove) is provided continuously.
- G1o, G2o, and G5o are directly inserted and arranged on the counter shaft so as to be relatively rotatable without a bearing member (bearing, bush, etc.).
- Inner splines are formed in the insertion holes of H1 and H3.
- H1 and H3 are provided on the countershaft so as not to rotate relative to each other by spline fitting with the outer spline of the countershaft.
- Axial fixation of G1o, H1, G2o, G5o, and H3 with respect to the countershaft can be achieved by providing snap rings (not shown) or the like on both sides of each member in the axial direction.
- G1o, G2o, G3o, and G5o are always in mesh with G1i, G2i, G3i, and G5i provided on the I / P shaft, respectively. Further, a final drive gear Gfi is provided at the “end near the O / P shaft” of the counter shaft. Similarly to G3o, Gfi is also integrally formed with the countershaft by using a manufacturing method such as forging.
- the O / P shaft is coaxially provided with the cylindrical end portion (large-diameter portion) that opens to the outside (left side in FIG. 1) at the “end portion close to the I / P shaft”. It has been.
- a direct connection piece P is coaxially provided at a position outside the BrA on the outer periphery of the cylindrical end portion (on the left side in FIG. 1).
- an outer spline spline groove
- An inner spline is formed in the P insertion hole.
- the direct connection piece P is provided on the cylindrical end portion (accordingly, the O / P shaft) so as not to rotate relative thereto by spline fitting with the outer spline at the cylindrical end portion.
- Axial fixation to the cylindrical end of P (and thus the O / P shaft) can be achieved by providing snap rings (not shown) or the like on both sides of P in the axial direction.
- the outer diameter of P is larger than the outer diameter of BrA.
- a final driven gear Gfo is provided in a portion between the BrA and BrB in the axial direction of the O / P shaft (a portion other than the cylindrical end portion).
- Gfo is also integrally formed with the O / P shaft using a manufacturing method such as forging.
- Gfo always meshes with Gfi provided on the countershaft.
- the number of teeth (outer diameter) of Gfo is larger than the number of teeth (outer diameter) of Gfi.
- the M / T gear position is switched with respect to the sleeve S1 that is axially moved relative to H1 on the outer periphery of the hub H1 and non-rotatably spline-fitted, and to the H2 on the outer periphery of the hub H2.
- a sleeve S2 that is spline-fitted so as to be relatively movable in the axial direction and not rotatable relative to the sleeve S3, and a sleeve S3 that is spline-fitted so as to be relatively movable in the axial direction relative to H3 on the outer periphery of the hub H3 and not relatively rotatable. This is achieved by adjusting and driving the respective axial positions.
- the axial positions of S1 to S3 are adjusted and driven through a plurality of link mechanisms (not shown) according to the operation of a shift lever (not shown) by the driver.
- the sleeve S1 can be selectively spline-fitted with a piece that rotates integrally with the G1o and a piece that rotates together with the G2o according to the axial position thereof.
- the sleeve S2 can be selectively spline-fitted with the piece that rotates integrally with the G3i and the directly connecting piece P according to the position in the axial direction.
- the sleeve S3 can be spline-fitted with a piece that rotates integrally with the G5o according to its axial position.
- GT1 is represented by ((number of teeth of G1o) / (number of teeth of G1i)) ⁇ GTf.
- GTf is represented by ((number of teeth of Gfo) / (number of teeth of Gfi)).
- final reduction ratio is established.
- GT2 is represented by ((number of teeth of G2o) / (number of teeth of G2i)) ⁇ GTf.
- the relationship GT1> GT2 is established.
- GT3 is represented by ((number of teeth of G3o) / (number of teeth of G3i)) ⁇ GTf.
- the relationship GT2> GT3 is established.
- the M / T reduction ratio is set to the fifth reduction ratio GT5 ( ⁇ 1).
- GT5 is represented by ((G5o number of teeth) / (G5i number of teeth)) ⁇ GTf.
- the relationship GT4> GT5 is established.
- the M / T structure is the “output (O / P) reduction structure” described above.
- an “O / P shaft subassembly” into which the bearings BrA and BrB are press-fitted and fixed is inserted into the opening of the housing HgA from the cylindrical end side (with white arrows).
- BrA is assembled to the bearing surface of the opening (press-fitted / fixed).
- the direct connection piece P is also simultaneously inserted into the cylindrical end, and as a result, the direct connection piece P is spline-fitted with the outer spline of the cylindrical end.
- the direct connection piece P is connected to the cylindrical end by spline fitting (so-called loose fitting) having a gap. It is connected so that it cannot rotate relative to the part.
- the countershaft has an elongated cylindrical shape.
- the internal space of the countershaft is used for circulating lubricating oil.
- Lubricating oil is pumped into the internal space of the countershaft from one end side of the countershaft using one of known methods.
- an oil hole Z penetrating in the radial direction is formed at a “position corresponding to the direct connection piece P in the axial direction” of the counter shaft.
- a centrifugal force acts on the lubricating oil in the internal space as the countershaft rotates. As shown in FIG. 5, using this centrifugal force, the lubricating oil in the internal space is applied toward the direct connection piece P through the oil hole Z. As a result, the lubricating oil can be supplied to the gap of the spline fitting portion (loose fitting) between the directly connecting piece P and the cylindrical end portion of the O / P shaft. As a result, the occurrence of abnormal heat generation or the like in the spline fitting portion can be suppressed.
- the outer diameter of the direct connection piece P is larger than the outer diameter of the bearing BrA (see FIG. 1).
- a synchronizer is actually provided close to the direct connection piece P.
- the outer diameter of the direct connection piece P is larger.
- the housing HgA is increased in size or the distance between the I / P shaft and the countershaft is increased, resulting in an increase in the size of the entire M / T. Therefore, the smaller the outer diameter of the bearing BrA, the better.
- the outer diameter of the direct connection piece P is larger than the outer diameter of the bearing BrA (see FIG. 1). This means that the outer diameter of the bearing BrA can be reduced while increasing the outer diameter of the direct connection piece P. As a result, it is possible to suppress an increase in the size of the entire M / T while maintaining the outer diameter of the direct connection piece P at a large value (thus ensuring a sufficient capacity of the synchronizer).
- the outer diameter of the countershaft is continuously constant within a wide range in the axial direction including the “portion where G1o, H1, G2o, G5o, and H3 are arranged” in the countershaft.
- An outer spline spline groove
- the countershaft can be processed very easily compared to the case where the countershaft has a stepped cylindrical shape within the axial range including the “part where the idle gear and hub are provided” in the countershaft. .
- each member is inserted into the counter shaft in the order of H3, G5o, G2o, H1, and G1o, and a snap ring (not shown) or the like is provided on both sides in the axial direction of each member. Assembly of the assembly is easily completed.
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Abstract
Description
図1に示すように、本発明の実施形態に係るM/Tは、クラッチと接続されたI/Pシャフトと、I/Pシャフトと同軸的に配置されたO/Pシャフトと、I/Pシャフトから偏心した位置にてI/Pシャフトと平行に配置されたカウンタシャフトと、を備える。I/Pシャフトは、クラッチを介してエンジンの出力軸(図示せず)と接続されている。O/Pシャフトは、図示しない接続機構(ディファレンシャル等)を介して駆動輪(左右後輪)と接続されている。このM/Tは、M/Tの軸が車両に対して縦向きになるようにクラッチを介してエンジンの後方に配置される。以下、O/Pシャフトの回転速度に対するI/Pシャフトの回転速度の割合を「減速比」と呼ぶものとすると、4速の減速比は「1」に設定されている。従って、4速は「直結変速段」と呼ぶこともできる。
次に、上記のように構成されたM/Tの作動について説明する。以下、M/Tの各変速段について順に説明していく。
シフトレバーが1速に対応する位置に操作されると、スリーブS2、S3は非接続状態(図1に示す状態)に維持される一方で、スリーブS1のみが駆動されて、G1oと一体回転するピースとスプライン嵌合する1速状態(図1に示す状態から左側へ移動した状態)となる。これにより、M/T内において、(I/Pシャフト→G1i→G1o→S1→H1→カウンタシャフト→Gfi→Gfo→O/Pシャフト)という動力伝達系統が形成される。この結果、車両前進時において、M/Tの減速比が1速の減速比GT1(>1)に設定される。GT1は、((G1oの歯数)/(G1iの歯数))・GTfで表わされる。ここで、GTfは((Gfoの歯数)/(Gfiの歯数))で表わされる。以下、GTfを「最終減速比」と呼ぶ。上述のように、GTf>1の関係が成立する。
シフトレバーが2速に対応する位置に操作されると、スリーブS2、S3は非接続状態(図1に示す状態)に維持される一方で、スリーブS1のみが駆動されて、G2oと一体回転するピースとスプライン嵌合する2速状態(図1に示す状態から右側へ移動した状態)となる。これにより、M/T内において、(I/Pシャフト→G2i→G2o→S1→H1→カウンタシャフト→Gfi→Gfo→O/Pシャフト)という動力伝達系統が形成される。この結果、車両前進時において、M/Tの減速比が2速の減速比GT2(>1)に設定される。GT2は、((G2oの歯数)/(G2iの歯数))・GTfで表わされる。GT1>GT2の関係が成立する。
シフトレバーが3速に対応する位置に操作されると、スリーブS1、S3は非接続状態(図1に示す状態)に維持される一方で、スリーブS2のみが駆動されて、G3iと一体回転するピースとスプライン嵌合する3速状態(図1に示す状態から左側へ移動した状態)となる。これにより、M/T内において、(I/Pシャフト→H2→S2→G3i→G3o→カウンタシャフト→Gfi→Gfo→O/Pシャフト)という動力伝達系統が形成される。この結果、車両前進時において、M/Tの減速比が3速の減速比GT3(>1)に設定される。GT3は、((G3oの歯数)/(G3iの歯数))・GTfで表わされる。GT2>GT3の関係が成立する。
シフトレバーが4速(即ち、直結変速段)に対応する位置に操作されると、スリーブS1、S3は非接続状態(図1に示す状態)に維持される一方で、スリーブS2のみが駆動されて、直結用ピースPとスプライン嵌合する4速状態(直結状態、図1に示す状態から右側へ移動した状態)となる。これにより、M/T内において、(I/Pシャフト→H2→S2→P→O/Pシャフト)という動力伝達系統が形成される。この結果、車両前進時において、M/Tの減速比が4速の減速比GT4(=1)に設定される。GT3>GT4の関係が成立する。
シフトレバーが5速に対応する位置に操作されると、スリーブS1、S2は非接続状態(図1に示す状態)に維持される一方で、スリーブS3のみが駆動されて、G5oと一体回転するピースとスプライン嵌合する5速状態(図1に示す状態から左側へ移動した状態)となる。これにより、M/T内において、(I/Pシャフト→G5i→G5o→S3→H3→カウンタシャフト→Gfi→Gfo→O/Pシャフト)という動力伝達系統が形成される。この結果、車両前進時において、M/Tの減速比が5速の減速比GT5(<1)に設定される。GT5は、((G5oの歯数)/(G5iの歯数))・GTfで表わされる。GT4>GT5の関係が成立する。以上、このM/Tの構造は、上述した「アウトプット(O/P)リダクション構造」である。
上述のように、このM/Tでは、直結用ピースPの外径は、ベアリングBrAの外径より大きい(図1を参照)。従って、上述した図7~図8に示した手順を用いて、O/PシャフトにベアリングBrAと直結用ピースPとを予め組み付けた「O/Pシャフトのサブアッセンブリ」を直結用ピースP側からハウジングHgAの前記開口部に挿入しようとしても、直結用ピースPが前記軸受面と干渉して挿入できない。
図1に示すように、カウンタシャフトは、細長の円筒形状を呈している。カウンタシャフトの内部空間は、潤滑油を流通するために使用される。潤滑油は、周知の手法の一つを利用して、カウンタシャフトの一端側からカウンタシャフトの内部空間内に圧送される。図1に示すように、カウンタシャフトにおける「軸方向において直結用ピースPに対応する位置」には、径方向に貫通する油穴Zが形成されている。
次に、上記のように構成された本発明の実施形態に係るM/Tの作用・効果について説明する。
Claims (2)
- 車両のエンジンの出力軸と駆動輪とを結ぶ動力伝達系統に介装され、前進用に複数の変速段を有する車両用手動変速機であって、
ハウジングと、
前記ハウジングに回転可能に支持されるとともに前記エンジンの出力軸との間で動力伝達系統が形成される入力軸と、
前記入力軸と同軸的且つ前記入力軸に対して相対回転可能に前記ハウジングに回転可能に支持され、前記駆動輪との間で動力伝達系統が形成される出力軸と、
前記入力軸から偏心した位置にて前記入力軸と平行に前記ハウジングに回転可能に支持されるカウンタ軸と、
それぞれが前記入力軸又は前記カウンタ軸に相対回転不能に設けられた複数の固定ギヤであってそれぞれが前記複数の変速段のうちの1つに対応する複数の固定ギヤと、
それぞれが前記カウンタ軸又は前記入力軸に相対回転可能に設けられた複数の遊転ギヤであってそれぞれが前記複数の変速段のうちの1つに対応するとともに対応する変速段の前記固定ギヤと常時歯合する複数の遊転ギヤと、
前記複数の変速段のうち前記出力軸の回転速度に対する前記入力軸の回転速度の割合である減速比が1となる直結変速段を実現するために使用される直結用ピースであって、前記出力軸の両端部のうち前記入力軸に近い側の一端部に前記出力軸と相対回転不能に設けられた直結用ピースと、
前記カウンタ軸に同軸的且つ相対回転不能に配置された最終駆動ギヤと、
前記出力軸における前記直結用ピースに対して前記入力軸から遠い側の位置に前記出力軸と相対回転不能に配置された、前記最終駆動ギヤと常時歯合する最終被動ギヤと、
前記複数の変速段のうち前記直結変速段以外の選択された1つの変速段に対応する遊転ギヤを対応する遊転ギヤが配置されている軸に対して相対回転不能に固定することによって、前記減速比を前記選択された1つの変速段に対応する1以外の値に設定し、又は、前記直結用ピースを前記入力軸に対して相対回転不能に固定することによって前記減速比を1に設定する切替機構と、
を備え、
前記ハウジングは、
少なくとも前記入力軸及び前記カウンタ軸を収容・支持する第1ハウジング部と、
前記第1ハウジング部における軸方向において前記出力軸に近い側の端部にて前記第1ハウジング部に連結されるとともに少なくとも前記出力軸を収容・支持する第2ハウジング部と、
を備え、
前記出力軸は、
前記出力軸における前記直結用ピースと前記最終被動ギヤとの間の位置に配設されるとともに、前記第1ハウジング部の前記端部に設けられた開口部の外周に形成された軸受面に挿入・固定された第1ベアリングと、
前記出力軸における軸方向において前記最終被動ギヤに対して前記入力軸から遠い側の位置に配設されるとともに、前記第2ハウジング部に固定された第2ベアリングと、
を用いて前記ハウジングに回転可能に支持され、
前記直結用ピースの外径が前記第1ベアリングの外径より大きい、車両用手動変速機。 - 請求項1に記載の車両用手動変速機において、
前記直結用ピースは、隙間を有するスプライン嵌合によって前記出力軸と相対回転不能に連結され、
前記カウンタ軸は、潤滑油を流通するための内部空間を有する円筒形状を呈し、
前記カウンタ軸における軸方向において前記直結用ピースに対応する位置には、径方向に貫通する油穴が形成された、車両用手動変速機。
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CN104791428A (zh) * | 2015-04-28 | 2015-07-22 | 陕西法士特齿轮有限责任公司 | 一种换挡轻便汽车变速器 |
WO2019167591A1 (ja) * | 2018-03-01 | 2019-09-06 | 日立オートモティブシステムズ株式会社 | 内燃機関の可変圧縮比機構のためのアクチュエータおよび内燃機関用機器に用いられるアクチュエータ |
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JPH0293151A (ja) * | 1988-09-29 | 1990-04-03 | Aisin Seiki Co Ltd | 歯車式手動変速機 |
JPH10103427A (ja) * | 1996-09-30 | 1998-04-21 | Mazda Motor Corp | 歯車式変速機構造 |
JP2012122579A (ja) * | 2010-12-10 | 2012-06-28 | Okamura Corp | ギヤ装置における軸受の潤滑構造 |
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JPH0293151A (ja) * | 1988-09-29 | 1990-04-03 | Aisin Seiki Co Ltd | 歯車式手動変速機 |
JPH10103427A (ja) * | 1996-09-30 | 1998-04-21 | Mazda Motor Corp | 歯車式変速機構造 |
JP2012122579A (ja) * | 2010-12-10 | 2012-06-28 | Okamura Corp | ギヤ装置における軸受の潤滑構造 |
Cited By (2)
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CN104791428A (zh) * | 2015-04-28 | 2015-07-22 | 陕西法士特齿轮有限责任公司 | 一种换挡轻便汽车变速器 |
WO2019167591A1 (ja) * | 2018-03-01 | 2019-09-06 | 日立オートモティブシステムズ株式会社 | 内燃機関の可変圧縮比機構のためのアクチュエータおよび内燃機関用機器に用いられるアクチュエータ |
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