JP3746222B2 - transmission - Google Patents
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- JP3746222B2 JP3746222B2 JP2001333618A JP2001333618A JP3746222B2 JP 3746222 B2 JP3746222 B2 JP 3746222B2 JP 2001333618 A JP2001333618 A JP 2001333618A JP 2001333618 A JP2001333618 A JP 2001333618A JP 3746222 B2 JP3746222 B2 JP 3746222B2
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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
- F16H3/093—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 with two or more countershafts
- F16H2003/0938—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 with two or more countershafts with multiple gears on the input shaft directly meshing with respective gears on the output shaft
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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
- F16H3/006—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion power being selectively transmitted by either one of the parallel flow paths
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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
- F16H3/093—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 with two or more countershafts
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Description
【０００１】
【発明の属する技術分野】
本発明は主に自動車のツインクラッチ式変速機に関するものである。
【０００２】
【従来の技術】
従来、例えば、自動車のツインクラッチ式変速機(1) として、図３に示すように、第１クラッチＤ１に接続する第１入力軸Ｘ１と、第２クラッチＤ２に接続し該第１入力軸Ｘ１に内挿される第２入力軸Ｘ２と、出力軸Ｘｏと、副軸Ｘｓおよびアイドラ軸ＸR とを有し、第１入力軸Ｘ１には４速段用および６速段用の駆動ギアＧ１８、Ｇ１９が回転可能に担持され、２速段用の駆動ギアＧ２０が固定的に担持され、更に該回転可能に担持されている２個のギアＧ１８、Ｇ１９をそれぞれ該第１入力軸Ｘ１に選択的に固定するカップリングＣ５が付設され、第２入力軸Ｘ２には１速段用、３速段用および５速段用の駆動ギアＧ２１、Ｇ２２、Ｇ２３が固定的に担持され、出力軸Ｘｏには該第１入力軸Ｘ１に回転可能に担持されている２個のギアＧ１８、Ｇ１９にそれぞれ噛合する４速段用および６速段用の被駆動ギアＧ２４、２５が固定的に担持され、第２入力軸Ｘ２に固定的に担持されている２個のギアＧ２１、Ｇ２３にそれぞれ噛合する１速段用および５速段用の被駆動ギアＧ２６、Ｇ２７が回転可能に担持され、かつ最クラッチ側において差動装置(4) に接続する出力ギアＧ１２が固定的に担持され、更に該回転可能に担持されている２個のギアＧ２６、Ｇ２７をそれぞれ該出力軸Ｘｏに選択的に固定するカップリングＣ６が付設され、副軸Ｘｓには該第２入力軸Ｘ２のギアＧ２２に噛合する３速段用の被駆動ギアＧ２８および該第２入力軸Ｘ２のギアＧ２１にアイドラ軸ＸR に固定的に担持されている１個のギアＧ２９を介して接続する１個のギアＧ３０が回転可能に担持され、第１入力軸Ｘ１のギアＧ１８に噛合するギアＧ３１が固定的に担持され、かつ第１入力軸Ｘ１のギアＧ２０に噛合する２速段用の被駆動ギアＧ３２が回転可能に担持され、更に回転可能に担持されている３個のギアＧ２８、Ｇ３０、Ｇ３２をそれぞれ副軸Ｘｓに選択的に固定するカップリングＣ７、Ｃ８がそれぞれ付設されている構成であって、該副軸ＸｓのギアＧ３２およびそのカップリングＣ８は出力軸Ｘｏの出力ギアＧ１２の側方スペースＳＰ内に収納されている変速機(1) が提供されている。
【０００３】
【発明が解決しようとする課題】
上記従来の構成では、２速または３速または後進を達成する場合に、第１入力軸Ｘ１の４速段用の駆動ギアＧ１８をアイドラギアとして使用するため、該ギアＧ１８には多大な負荷がかかり、該ギアＧ１８の軸受け部分の強度が不足し、変速機(1) の耐久性が低下するという問題がある。
そこで、該ギアＧ１８の軸受け部分の強度を確保するために、該ギアＧ１８の軸受け部分の径を大きくして該ギアＧ１８の軸受け容量を大きくすることも考えられるが、該ギアＧ１８のギア径は４速段の駆動ギアＧ１８と被駆動ギアＧ２４のギア比によって設定されているので、該ギアＧ１８のギア径を大きくすると、第１入力軸Ｘ１と出力軸Ｘｏの軸間距離も大きくなって変速機(1) のサイズが大きくなり、車両への搭載が困難になるという問題がある。
また、該ギアＧ１８の軸受け部分の軸長を長くして該ギアＧ１８の軸受け容量を大きくする場合には、軸長を長くした分だけ変速機(1) の軸方向のサイズが大きくなるという問題点がある。ツインクラッチ式の変速機(1) の場合、特に、ＦＦ方式でエンジン(2) を横置きにする場合には、変速機(1) の搭載スペースが狭くなるため、軸長さを長くすることは困難であるという問題もある。
【０００４】
更に、第１入力軸Ｘ１の２速段用の駆動ギアＧ２０は、低速段用のギアなのでギア径が小さく設定されており、該ギアＧ２０の径に応じて第１入力軸Ｘ１の径も小さく設定されている。すると、中空である該第１入力軸Ｘ１に内挿される第２入力軸Ｘ２は更に径を小さく設定する必要があるので、第２入力軸Ｘ２の強度が不足し、変速機(1) の耐久性が低下するという問題がある。
この場合にも、該ギアＧ２０のギア径は２速段の駆動ギアＧ２０と被駆動ギアＧ３２のギア比によって設定されており、該ギアＧ２０のギア径を大きくすると、第１入力軸Ｘ１と副軸Ｘｓの軸間距離が大きくなって変速機(1) のサイズが大きくなり、車両への搭載が困難になるという問題点がある。
【０００５】
【課題を解決するための手段】
本発明は上記従来の課題を解決するための手段として、第１クラッチＤ１に接続する第１入力軸Ｘ１と、第２クラッチＤ２に接続し該第１入力軸Ｘ１に内挿される第２入力軸Ｘ２と、出力軸Ｘｏと、副軸Ｘｓおよびアイドラ軸Ｘ R とを有し、
第１入力軸Ｘ１には、２個のギアＧ１、Ｇ２を担持せしめたスリーブＳ G と６速段用の駆動ギアＧ３とが回転可能に担持されるとともに２速段用の駆動ギアＧ４が固定的に担持され、更に前記２個のギアＧ１、Ｇ２および前記６速段用の駆動ギアＧ３をそれぞれ前記第１入力軸Ｘ１に選択的に固定する第１カップリングＣ１が付設され、
第２入力軸Ｘ２には、１速段用の駆動ギアＧ５と第１ギアが固定的に担持され、
出力軸Ｘｏには４速段を構成する４速段用の被駆動ギアＧ７と前記６速段用の駆動ギアＧ３に噛合する６速段用の被駆動ギアＧ８とが固定的に担持され、前記１速段用の駆動ギアＧ５に噛合する１速段用の被駆動ギアＧ９と５速段を構成する５速段用の被駆動ギアＧ１０とが回転可能に担持され、かつ最クラッチ側において差動装置 (4) に接続する出力ギアＧ１２が固定的に担持され、更に前記１速段用の被駆動ギアＧ９と前記５速段用の被駆 動ギアＧ１０とをそれぞれ前記出力軸Ｘｏに選択的に固定する第２カップリングＣ２が付設され、
副軸Ｘｓには、３速段を構成する３速段用の被駆動ギアＧ１３と、前記１速段用の駆動ギアＧ５にアイドラ軸Ｘ R に固定的に担持されているアイドラギアＧ１４を介して接続する後進段用の被駆動ギアＧ１５と、前記２速段用の駆動ギアＧ４に噛合する２速段用の被駆動ギアＧ１７とが回転可能に担持されるとともに、第２ギアが固定的に担持され、更に、前記３速段用の被駆動ギアＧ１３と前記後進段用の被駆動ギアＧ１５とを前記副軸Ｘｓに選択的に固定する第３カップリングと前記２速段用の被駆動ギアＧ１７を前記副軸Ｘｓに選択的に固定する第４カップリングＣ４とが付設されている構成であって、
前記２個のギアＧ１、Ｇ２のうちの一方のギアは前記第２ギアに噛合し、他方のギアは前記４速段用の被駆動ギアＧ７に噛合し、該一方のギアまたは該他方のギアには、該一方のギアと該他方のギアとを前記第１入力軸Ｘ１に選択的に固定する前記第１カップリングＣ１が付設されており、更に、前記第１ギアが前記３速段用の被駆動ギアＧ１３と前記５速段用の被駆動ギアＧ１０とに噛合される変速機(1) を提供するものである。
該一方のギアＧ１の径は該他方のギアＧ２の径よりも大きく設定されていることが望ましい。
【０００６】
【作用】
入力軸Ｘ１に回転可能に嵌着されるスリーブＳG に２個のギアＧ１、Ｇ２を担持せしめるので、該ギアＧ１、Ｇ２を担持するスリーブＳG の軸受け部分の軸長を長く設定して、該ギアＧ１、Ｇ２を担持するスリーブＳG の軸受け容量を大きくすることが出来、変速機(1) の耐久性を向上させることが出来る。
更に、該一方のギアＧ１の径を該他方のギアＧ２の径よりも所望な分だけ大きく設定すれば、軸間距離を変えることなくギア比を調節することが出来るので、ギア比の制限を受けることなくギアの径を設定することが出来る。
【０００７】
【発明の実施の形態】
本発明を図１に示す一実施例によって説明する。本実施例では、図１に示すような自動車のツインクラッチ式６段変速機(1) の場合を例示する。
図１に示すように、自動車の６段変速機(1) は中空である第１入力軸Ｘ１と、該第１入力軸Ｘ１に内挿される第２入力軸Ｘ２と、出力軸Ｘｏと、副軸Ｘｓおよびアイドラ軸ＸR とを有しており、該第１入力軸Ｘ１および第２入力軸Ｘ２にはエンジン(2) からの動力を伝達する第１クラッチＤ１および第２クラッチＤ２がそれぞれ接続されている。
【０００８】
該第１入力軸Ｘ１には、２個のギアＧ１、Ｇ２を担持せしめたスリーブＳG が回転可能に嵌着され、６速段用の駆動ギアＧ３が回転可能に担持され、２速段用の駆動ギアＧ４が固定的に担持され、更に該ギアＧ１、Ｇ３にはそれぞれハブＨ１、Ｈ２が設けられており、該ギアＧ１、Ｇ３の間にはスリーブＳ１を有するカップリングＣ１が付設されている。そして、該スリーブＳG の一方のギアＧ１の径は他方のギアＧ２の径よりも大きく設定されている。
【０００９】
第２入力軸Ｘ２には、１速段用の駆動ギアＧ５および３速段用あるいは５速段用の駆動ギアＧ６が固定的に担持されている。
【００１０】
出力軸Ｘｏには、該第１入力軸Ｘ１に回転可能に嵌着されているスリーブＳG の他方のギアＧ２および６速段用の駆動ギアＧ３にそれぞれ噛合する４速段用および６速段用の被駆動ギアＧ７、Ｇ８が固定的に担持され、該第２入力軸Ｘ２の１速段用および３速段用あるいは５速段用のギアＧ５、Ｇ６にそれぞれ噛合する１速段用および５速段用の被駆動ギアＧ９、Ｇ１０が回転可能に担持され、かつ、タイヤ(3) に動力を伝達する差動装置(4) のギアＧ１１に噛合する出力ギアＧ１２が固定的に担持され、更に、該ギアＧ９、Ｇ１０にはそれぞれハブＨ３、Ｈ４が設けられており、該ギアＧ９、Ｇ１０の間にはスリーブＳ２を有するカップリングＣ２が付設されている。そして、該出力ギアＧ１２は最クラッチ側に配置されている。
【００１１】
副軸Ｘｓには、第２入力軸Ｘ２のギアＧ６に噛合する３速段用の被駆動ギアＧ１３と、該第２入力軸Ｘ２のギアＧ５にアイドラ軸ＸR に固定的に担持されているギアＧ１４を介して接続する後進段用の被駆動ギアＧ１５が回転可能に担持され、第１入力軸Ｘ１に回転可能に嵌着されているスリーブＳG の一方のギアＧ１に噛合するギアＧ１６が固定的に担持され、かつ、第１入力軸Ｘ１のギアＧ４に噛合する２速段用の被駆動ギアＧ１７が回転可能に担持され、更に、該ギアＧ１３、Ｇ１５にはそれぞれハブＨ５、Ｈ６が設けられており、該ギアＧ１３、Ｇ１５の間にはスリーブＳ３を有するカップリングＣ３が付設されており、また更に、該ギアＧ１７にはハブＨ７が設けられており、該ギアＧ１７にはスリーブＳ４を有するカップリングＣ４が付設されている。そして、該ギアＧ１７およびそのカップリングＣ４は該出力軸Ｘｏの出力ギアＧ１２の側方スペースＳＰ内に収納されている。
本実施例以外、アイドラ軸ＸR のギアＧ１４は、アイドラ軸ＸR に回転可能に担持されていてもよい。
【００１２】
このように、入力軸Ｘ１に回転可能に嵌着されるスリーブＳG に２個のギアＧ１、Ｇ２を担持せしめることにより、該ギアＧ１、Ｇ２を担持するスリーブＳG の軸受け部分の軸長を長く設定して、該ギアＧ１、Ｇ２を担持するスリーブＳG の軸受け容量を大きくすることが出来、変速機(1) の耐久性を向上させることが出来る。
更に、該一方のギアＧ１の径を該他方のギアＧ２の径よりも所望な分だけ大きく設定すれば、軸間距離を変えることなくギア比を調節することが出来るので、ギア比の制限を受けることなくギアの径を設定することが出来る。
【００１３】
上記のように、ギア比の制限を受けることなくギアの径を設定することが出来るので、低速段用のギアにも関わらず２速段用の駆動ギアＧ４の径を大きく設定することが出来るので、該ギアＧ４の径に応じて第１入力軸Ｘ１の径も大きく設定することが出来、したがって、中空である該第１入力軸Ｘ１に内挿される第２入力軸Ｘ２は更に径を大きく設定することが可能となり、第２入力軸Ｘ２の強度を確保して、変速機(1) の耐久性を向上させることが可能となる。
また、軸間距離を変えることなくギア比を調節することが出来るので、第２入力軸Ｘ２のギアＧ６を３速段用と５速段用の駆動ギアとして共用することにより、ギア１対分の軸方向のスペースを省くことが出来るので、該スリーブＳG の軸受け部分の軸長を長くしても、変速機(1) の軸方向のサイズが大きくなることがない。
【００１４】
以下に上記構成の動作を説明する。
〔１速〕
スリーブＳ２を１速段用の被駆動ギアＧ９側へスライドさせて、カップリングＣ２と該ギアＧ９のハブＨ３とを接続すると、第２入力軸Ｘ２の回転は、１速段用の駆動ギアＧ５から１速段用の被駆動ギアＧ９を介して出力軸Ｘｏに伝達され、該出力軸Ｘｏの回転は出力ギアＧ１２を介して差動装置(4) のギアＧ１１に伝達され、１速が達成される。
【００１５】
〔２速〕
スリーブＳ４を２速段用の被駆動ギアＧ１７側へスライドさせて、カップリングＣ４と該ギアＧ１７のハブＨ７とを接続すると、第１入力軸Ｘ１の回転は、２速段用の駆動ギアＧ４から２速段用の被駆動ギアＧ１７を介して副軸Ｘｓに伝達され、更に副軸ＸｓのギアＧ１６から第１入力軸Ｘ１のスリーブＳG の一方のギアＧ１を介して該スリーブＳG に伝達され、該スリーブＳG の他方のギアＧ２から出力軸ＸｏのギアＧ７を介して出力軸Ｘｏに伝達され、該出力軸Ｘｏの回転は出力ギアＧ１２を介して差動装置(4) のギアＧ１１に伝達され、２速が達成される。
【００１６】
〔３速〕
スリーブＳ３を３速段用の被駆動ギアＧ１３側へスライドさせて、カップリングＣ３と該ギアＧ１３のハブＨ５とを接続すると、第２入力軸Ｘ２の回転は、３速段用あるいは５速段用の駆動ギアＧ６から３速段用の被駆動ギアＧ１３を介して副軸Ｘｓに伝達され、更に副軸ＸｓのギアＧ１６から第１入力軸Ｘ１のスリーブＳG の一方のギアＧ１を介して該スリーブＳG に伝達され、該スリーブＳG の他方のギアＧ２から出力軸ＸｏのギアＧ７を介して出力軸Ｘｏに伝達され、該出力軸Ｘｏの回転は出力ギアＧ１２を介して差動装置(4) のギアＧ１１に伝達され、３速が達成される。
【００１７】
〔４速〕
スリーブＳ１を第１入力軸Ｘ１のスリーブＳG の一方のギアＧ１側へスライドさせて、カップリングＣ１と該ギアＧ１のハブＨ１とを接続すると、第１入力軸Ｘ１の回転は、第１入力軸Ｘ１のスリーブＳG の一方のギアＧ１を介して該スリーブＳG に伝達され、該スリーブＳG の他方のギアＧ２から出力軸ＸｏのギアＧ７を介して出力軸Ｘｏに伝達され、該出力軸Ｘｏの回転は出力ギアＧ１２を介して差動装置(4) のギアＧ１１に伝達され、４速が達成される。
【００１８】
〔５速〕
スリーブＳ２を５速段用の被駆動ギアＧ１０側へスライドさせて、カップリングＣ２と該ギアＧ１０のハブＨ４とを接続すると、第２入力軸Ｘ２の回転は、３速段用あるいは５速段用の駆動ギアＧ６から５速段用の被駆動ギアＧ１０を介して出力軸Ｘｏに伝達され、該出力軸Ｘｏの回転は出力ギアＧ１２を介して差動装置(4) のギアＧ１１に伝達され、５速が達成される。
【００１９】
〔６速〕
スリーブＳ１を６速段用の駆動ギアＧ３側へスライドさせて、カップリングＣ１と該ギアＧ３のハブＨ２とを接続すると、第１入力軸Ｘ１の回転は、６速段用の駆動ギアＧ３から６速段用の被駆動ギアＧ８を介して出力軸Ｘｏに伝達され、該出力軸Ｘｏの回転は出力ギアＧ１２を介して差動装置(4) のギアＧ１１に伝達され、６速が達成される。
【００２０】
〔後進〕
スリーブＳ３を後進段用の被駆動ギアＧ１５側へスライドさせて、カップリングＣ３と該ギアＧ１５のハブＨ６とを接続すると、第２入力軸Ｘ２の回転は、第２入力軸Ｘ２のギアＧ５からアイドラ軸ＸR のギアＧ１４によって反転されて後進段用の被駆動ギアＧ１５を介して副軸Ｘｓに伝達され、更に副軸ＸｓのギアＧ１６から第１入力軸Ｘ１のスリーブＳG の一方のギアＧ１を介して該スリーブＳG に伝達され、該スリーブＳG の他方のギアＧ２から出力軸ＸｏのギアＧ７を介して出力軸Ｘｏに伝達され、該出力軸Ｘｏの回転は出力ギアＧ１２を介して差動装置(4) のギアＧ１１に伝達され、後進が達成される。
【００２１】
本実施例以外、図２に示すように、第１入力軸Ｘ１のスリーブＳG の他方のギアＧ２にハブＨ１が設けられており、該ギアＧ２、Ｇ３の間にスリーブＳ１を有するカップリングＣ１が付設されていてもよい。
この場合、４速を達成するために、スリーブＳ１を第１入力軸Ｘ１のスリーブＳG の他方のギアＧ２側へスライドさせて、カップリングＣ１と該ギアＧ２のハブＨ１とを接続すると、第１入力軸Ｘ１の回転は、第１入力軸Ｘ１のスリーブＳG の他方のギアＧ２から出力軸ＸｏのギアＧ７を介して出力軸Ｘｏに伝達され、該出力軸Ｘｏの回転は出力ギアＧ１２を介して差動装置(4) のギアＧ１１に伝達され、４速が達成される。
【００２２】
【発明の効果】
本発明では、変速機のサイズを大きくすることなく、ギアの強度と軸受の容量を確保することが出来、変速機の耐久性を向上させることが可能となる。
【図面の簡単な説明】
【図１】本発明の一実施例を示す説明図である。
【図２】本発明の他の実施例を示す説明図である。
【図３】従来例を示す説明図である。
【符号の説明】
1 変速機
2 エンジン
3 タイヤ
4 差動装置
Ｘ１ 第１入力軸
Ｘ２ 第２入力軸
Ｘｏ 出力軸
Ｘｓ 副軸
ＸR アイドラ軸
Ｄ１ 第１クラッチ
Ｄ２ 第２クラッチ
Ｇ１〜Ｇ１７ ギア
Ｃ１〜Ｃ４ カップリング
ＳG 、Ｓ１〜Ｓ４ スリーブ
Ｈ１〜Ｈ７ ハブ[0001]
BACKGROUND OF THE INVENTION
The present invention mainly relates to a twin clutch transmission of an automobile.
[0002]
[Prior art]
Conventionally, for example, as a twin clutch transmission (1) of an automobile, as shown in FIG. 3, a first input shaft X1 connected to a first clutch D1 and a first input shaft X1 connected to a second clutch D2 are shown. a second input shaft X2, an output shaft Xo to be inserted into the, and a counter shaft Xs and an idler shaft X R, the first input shaft X1 4-speed-step and 6-speed driving gear G18 for stage, G19 is rotatably supported, a driving gear G20 for the second speed stage is fixedly supported, and the two gears G18 and G19 that are rotatably supported are selectively selected as the first input shaft X1. The second input shaft X2 is fixedly loaded with driving gears G21, G22, G23 for the first gear, the third gear and the fifth gear, and is attached to the output shaft Xo. Are two gears G1 rotatably supported on the first input shaft X1. The driven gears G24 and 25 for the fourth speed stage and the sixth speed stage respectively meshing with G19 are fixedly supported on the two gears G21 and G23 fixedly supported on the second input shaft X2. The driven gears G26 and G27 for the first gear and the fifth gear that mesh with each other are rotatably supported, and the output gear G12 that is connected to the differential device (4) is fixedly supported on the outermost clutch side. Further, a coupling C6 for selectively fixing the two gears G26 and G27, which are rotatably supported, to the output shaft Xo, respectively, is provided, and the auxiliary shaft Xs is connected to the gear G22 of the second input shaft X2. one gear G30 connecting through one of the gear G29 to the gear G21 driven gear G28 and the second input shaft X2 for third gear meshing is fixedly supported on the idle shaft X R is Rotatably supported and second A gear G31 that meshes with the gear G18 of the input shaft X1 is fixedly supported, and a driven gear G32 for second gear that meshes with the gear G20 of the first input shaft X1 is rotatably supported and further rotatable. Couplings C7 and C8 for selectively fixing the three supported gears G28, G30, and G32 to the auxiliary shaft Xs are provided, respectively, and the gear G32 of the auxiliary shaft Xs and its cup are provided. The ring (C8) is provided with a transmission (1) housed in a side space SP of the output gear G12 of the output shaft Xo.
[0003]
[Problems to be solved by the invention]
In the conventional configuration described above, when the second speed, the third speed or the reverse speed is achieved, the drive gear G18 for the fourth speed stage of the first input shaft X1 is used as the idler gear, so that a great load is applied to the gear G18. There is a problem that the strength of the bearing portion of the gear G18 is insufficient and the durability of the transmission (1) is lowered.
Therefore, in order to ensure the strength of the bearing portion of the gear G18, it is possible to increase the bearing capacity of the gear G18 by increasing the diameter of the bearing portion of the gear G18. Since the gear ratio between the fourth-speed drive gear G18 and the driven gear G24 is set, if the gear diameter of the gear G18 is increased, the distance between the first input shaft X1 and the output shaft Xo is also increased. There is a problem that the size of the machine (1) becomes large and it becomes difficult to mount it on the vehicle.
In addition, when the shaft length of the bearing portion of the gear G18 is increased to increase the bearing capacity of the gear G18, the size of the transmission (1) in the axial direction increases as the shaft length is increased. There is a point. In the case of a twin-clutch transmission (1), especially when the engine (2) is installed horizontally in the FF system, the mounting space for the transmission (1) is reduced, so the shaft length must be increased. There is also a problem that is difficult.
[0004]
Furthermore, since the second-speed drive gear G20 of the first input shaft X1 is a gear for the low-speed stage, the gear diameter is set small, and the diameter of the first input shaft X1 is small according to the diameter of the gear G20. Is set. Then, since it is necessary to set the diameter of the second input shaft X2 inserted into the hollow first input shaft X1 further smaller, the strength of the second input shaft X2 is insufficient and the transmission (1) is durable. There is a problem that the performance is lowered.
Also in this case, the gear diameter of the gear G20 is set by the gear ratio between the second-speed drive gear G20 and the driven gear G32, and when the gear diameter of the gear G20 is increased, the first input shaft X1 and the sub-gear There is a problem that the distance between the axes Xs is increased, the size of the transmission (1) is increased, and the mounting on the vehicle becomes difficult.
[0005]
[Means for Solving the Problems]
As means for solving the above-mentioned conventional problems, the present invention provides a first input shaft X1 connected to the first clutch D1, and a second input shaft connected to the second clutch D2 and inserted into the first input shaft X1. X2, an output shaft Xo, a secondary shaft Xs and an idler shaft X R ,
The first input shaft X1, together with a drive gear G3 for the two sleeve S G and sixth speed that allowed carrying gear G1, G2 are rotatably carried on the driven gear G4 for the second gear fixed Furthermore, a first coupling C1 for selectively fixing the two gears G1, G2 and the driving gear G3 for the sixth gear to the first input shaft X1 is additionally provided.
The second input shaft X2 carries a first-speed drive gear G5 and a first gear fixedly,
The output shaft Xo fixedly carries a driven gear G7 for the fourth speed that constitutes the fourth speed and a driven gear G8 for the sixth speed that meshes with the driving gear G3 for the sixth speed, A first-speed driven gear G9 meshed with the first-speed drive gear G5 and a fifth-speed driven gear G10 that constitutes the fifth-speed gear are rotatably supported on the most clutch side. output gear G12 connecting to a differential gear (4) is fixedly carried, further said first speed driven gear G9 for stage and said fifth speed gear stage to be drive kinematic gears G10 and to each said output shaft Xo A second coupling C2 for selectively fixing is attached,
The counter shaft Xs, through a driven gear G13 for the 3-speed stages constituting the third gear, an idler gear G14 being fixedly carried on the idler shaft X R with the drive gear G5 for the first gear A reverse-stage driven gear G15 to be connected and a second-speed driven gear G17 meshing with the second-speed driving gear G4 are rotatably supported, and the second gear is fixed. And a third coupling for selectively fixing the driven gear G13 for the third speed stage and the driven gear G15 for the reverse speed stage to the auxiliary shaft Xs and the driven gear for the second speed stage. And a fourth coupling C4 for selectively fixing the gear G17 to the auxiliary shaft Xs.
One of the two gears G1 and G2 meshes with the second gear, and the other gear meshes with the driven gear G7 for the fourth gear, and the one gear or the other gear. Is provided with the first coupling C1 for selectively fixing the one gear and the other gear to the first input shaft X1, and the first gear is used for the third speed stage. The transmission (1) meshed with the driven gear G13 and the driven gear G10 for the fifth speed stage is provided.
The diameter of the one gear G1 is preferably set larger than the diameter of the other gear G2.
[0006]
[Action]
Since rotatably allowed to carry the two gears G1, G2 on the sleeve S G which is fitted to the input shaft X1, and set a longer axial length of the bearing portion of the sleeve S G carrying said gears G1, G2, it is possible to increase the bearing capacity of the sleeve S G carrying said gears G1, G2, transmission (1) durability can be improved in.
Furthermore, if the diameter of the one gear G1 is set to be larger than the diameter of the other gear G2 by a desired amount, the gear ratio can be adjusted without changing the inter-axis distance. The diameter of the gear can be set without receiving it.
[0007]
DETAILED DESCRIPTION OF THE INVENTION
The present invention is illustrated by the example shown in FIG. In this embodiment, the case of a twin clutch type six-speed transmission (1) of an automobile as shown in FIG. 1 is illustrated.
As shown in FIG. 1, the six-speed transmission (1) of an automobile has a hollow first input shaft X1, a second input shaft X2 inserted into the first input shaft X1, an output shaft Xo, and an auxiliary shaft. has a shaft Xs and idler shaft X R, connected to the first clutch D1 and a second clutch D2 to transmit power from the engine (2) is in said first input shaft X1 and said second input shaft X2 respectively Has been.
[0008]
The first input shaft X1, a sleeve S G which allowed carrying two gears G1, G2 is fitted rotatably, a drive gear G3 for the 6th speed stage is carried rotatably, the second-speed stage The drive gear G4 is fixedly supported, and the gears G1 and G3 are provided with hubs H1 and H2, respectively. A coupling C1 having a sleeve S1 is provided between the gears G1 and G3. Yes. Then, the diameter of one of the gear G1 of the sleeve S G is set to be larger than the diameter of the other gear G2.
[0009]
On the second input shaft X2, a drive gear G5 for the first speed stage and a drive gear G6 for the third speed stage or the fifth speed stage are fixedly supported.
[0010]
The output shaft Xo, the first rotatably fitted has been that the sleeve S G of the other gear G2 and the fourth gear and for sixth gear to each mesh with the drive gear G3 for the sixth speed to the input shaft X1 Driven gears G7 and G8 are fixedly supported and meshed with the first and third gears G5 and G6 of the second input shaft X2, respectively. The driven gears G9 and G10 for the fifth speed stage are rotatably supported, and the output gear G12 that meshes with the gear G11 of the differential device (4) that transmits power to the tire (3) is fixedly supported. Furthermore, the gears G9 and G10 are provided with hubs H3 and H4, respectively, and a coupling C2 having a sleeve S2 is provided between the gears G9 and G10. The output gear G12 is disposed on the most clutch side.
[0011]
The counter shaft Xs, a driven gear G13 for the third gear meshing with the gear G6 of said second input shaft X2, and is fixedly supported on the idle shaft X R to the gear G5 of said second input shaft X2 driven gear G15 for reverse gear connected through a gear G14 is rotatably carried on a gear G16 meshing with one of the gear G1 of the sleeve S G which is rotatably fitted to the first input shaft X1 is A second-speed driven gear G17 that is fixedly supported and meshes with the gear G4 of the first input shaft X1 is rotatably supported. Further, hubs H5 and H6 are provided on the gears G13 and G15, respectively. A coupling C3 having a sleeve S3 is provided between the gears G13 and G15. Further, a hub H7 is provided on the gear G17, and a sleeve S4 is provided on the gear G17. Coupling C with 4 is attached. The gear G17 and its coupling C4 are accommodated in a side space SP of the output gear G12 of the output shaft Xo.
Except this embodiment, the gear G14 of the idler shaft X R may be rotatably supported on idler shaft X R.
[0012]
By thus allowed to carry the two gears G1, G2 on the sleeve S G rotatably fitted to the input shaft X1, the shaft length of the bearing portion of the sleeve S G carrying said gears G1, G2 set longer, the gear G1, G2 can increase the bearing capacity of the sleeve S G carrying a transmission (1) durability can be improved in.
Furthermore, if the diameter of the one gear G1 is set to be larger than the diameter of the other gear G2 by a desired amount, the gear ratio can be adjusted without changing the inter-axis distance. The diameter of the gear can be set without receiving it.
[0013]
As described above, since the gear diameter can be set without being limited by the gear ratio, the diameter of the drive gear G4 for the second speed stage can be set large regardless of the gear for the low speed stage. Therefore, the diameter of the first input shaft X1 can be set larger according to the diameter of the gear G4. Therefore, the second input shaft X2 inserted into the hollow first input shaft X1 has a larger diameter. It becomes possible to set, and it is possible to secure the strength of the second input shaft X2 and improve the durability of the transmission (1).
In addition, since the gear ratio can be adjusted without changing the distance between the shafts, the gear G6 of the second input shaft X2 can be shared as the driving gear for the third speed stage and the fifth speed stage, thereby making it equivalent to one gear pair. since the axial space can be eliminated, even by increasing the axial length of the bearing portion of the sleeve S G, is not the size of the axial direction increases the transmission (1).
[0014]
The operation of the above configuration will be described below.
[1st gear]
When the sleeve S2 is slid to the driven gear G9 side for the first speed stage and the coupling C2 and the hub H3 of the gear G9 are connected, the rotation of the second input shaft X2 is the driving gear G5 for the first speed stage. Is transmitted to the output shaft Xo via the driven gear G9 for the first speed stage, and the rotation of the output shaft Xo is transmitted to the gear G11 of the differential device (4) via the output gear G12 to achieve the first speed. Is done.
[0015]
[2nd gear]
When the sleeve S4 is slid to the driven gear G17 side for the second speed stage and the coupling C4 and the hub H7 of the gear G17 are connected, the rotation of the first input shaft X1 is the driving gear G4 for the second speed stage. from being transmitted to the counter shaft Xs through the driven gear G17 for the second speed, further from said gear G16 of said counter shaft Xs through one of the gear G1 of the sleeve S G of said first input shaft X1 to said sleeve S G is transmitted, is transmitted to the output shaft Xo through the gear G7 of said output shaft Xo from the other gear G2 of said sleeve S G, the gear of the rotation of said output shaft Xo through the output gear G12 differential (4) G2 is transmitted and the second speed is achieved.
[0016]
[3rd speed]
When the sleeve S3 is slid to the driven gear G13 side for the third gear and the coupling C3 and the hub H5 of the gear G13 are connected, the rotation of the second input shaft X2 is for the third gear or the fifth gear. from the drive gear G6 of use through a driven gear G13 for the third gear is transmitted to the counter shaft Xs, further from said gear G16 of said counter shaft Xs through one of the gear G1 of the sleeve S G of said first input shaft X1 Is transmitted to the sleeve S G , is transmitted from the other gear G2 of the sleeve S G to the output shaft Xo through the gear G7 of the output shaft Xo, and the rotation of the output shaft Xo is transmitted to the differential device through the output gear G12. (4) is transmitted to the gear G11 to achieve the third speed.
[0017]
[4th gear]
The sleeve S1 is slid into one of the gear G1 side of the sleeve S G of said first input shaft X1, to connect said coupling C1 and hub H1 of said gear G1, rotation of the first input shaft X1, the first input via one of the gear G1 of the sleeve S G axis X1 is transmitted to said sleeve S G, it is transmitted to the output shaft Xo through the gear G7 of said output shaft Xo from the other gear G2 of said sleeve S G, the output The rotation of the shaft Xo is transmitted to the gear G11 of the differential device (4) through the output gear G12, and the fourth speed is achieved.
[0018]
[5-speed]
When the sleeve S2 is slid to the driven gear G10 side for the fifth gear and the coupling C2 and the hub H4 of the gear G10 are connected, the rotation of the second input shaft X2 is for the third gear or the fifth gear. Drive gear G6 is transmitted to output shaft Xo via driven gear G10 for the fifth speed stage, and the rotation of output shaft Xo is transmitted to gear G11 of the differential device (4) via output gear G12. 5th speed is achieved.
[0019]
[6th speed]
When the sleeve S1 is slid to the driving gear G3 side for the sixth speed stage and the coupling C1 and the hub H2 of the gear G3 are connected, the rotation of the first input shaft X1 is performed from the driving gear G3 for the sixth speed stage. It is transmitted to the output shaft Xo via the driven gear G8 for the sixth speed stage, and the rotation of the output shaft Xo is transmitted to the gear G11 of the differential device (4) via the output gear G12 to achieve the sixth speed. The
[0020]
[Backward]
When the sleeve S3 is slid toward the driven gear G15 for the reverse gear and the coupling C3 and the hub H6 of the gear G15 are connected, the rotation of the second input shaft X2 is started from the gear G5 of the second input shaft X2. is transmitted to the counter shaft Xs through the driven gear G15 for reverse speed is inverted by gear G14 of the idler shaft X R, further one gear of the sleeve S G of said first input shaft X1 from said gear G16 of said counter shaft Xs through G1 is transmitted to the sleeve S G, is transmitted to the output shaft Xo through the gear G7 of said output shaft Xo from the other gear G2 of said sleeve S G, and the rotation of said output shaft Xo through the output gear G12 Then, it is transmitted to the gear G11 of the differential device (4) to achieve reverse.
[0021]
Except this embodiment, as shown in FIG. 2, a hub H1 is provided on the other gear G2 of the sleeve S G of said first input shaft X1, the coupling C1 having a sleeve S1 is between the gears G2, G3 May be attached.
In this case, in order to achieve the fourth speed, the sleeve S1 by other slide to the gear G2 side of the sleeve S G of said first input shaft X1, to connect said coupling C1 and hub H1 of said gear G2, the rotation of the first input shaft X1 is transmitted to said output shaft Xo through the gear G7 of said output shaft Xo from the other gear G2 of the sleeve S G of said first input shaft X1, the rotation of said output shaft Xo is the output gear G12 To the gear G11 of the differential (4) through which the fourth speed is achieved.
[0022]
【The invention's effect】
In the present invention, the strength of the gear and the capacity of the bearing can be ensured without increasing the size of the transmission, and the durability of the transmission can be improved.
[Brief description of the drawings]
FIG. 1 is an explanatory view showing an embodiment of the present invention.
FIG. 2 is an explanatory view showing another embodiment of the present invention.
FIG. 3 is an explanatory diagram showing a conventional example.
[Explanation of symbols]
1 Transmission
2 Engine
3 tires
4 Differential X1 1st input shaft X2 2nd input shaft Xo Output shaft Xs Secondary shaft X R idler shaft D1 1st clutch D2 2nd clutch G1 to G17 Gear C1 to C4 Coupling S G , S1 to S4 Sleeve H1 H7 hub
Claims (2)
第１入力軸には、２個のギアを担持せしめたスリーブと６速段用の駆動ギアとが回転可能に担持されるとともに２速段用の駆動ギアが固定的に担持され、更に前記２個のギアおよび前記６速段用の駆動ギアをそれぞれ前記第１入力軸に選択的に固定する第１カップリングが付設され、 On the first input shaft, a sleeve carrying two gears and a drive gear for the sixth speed stage are rotatably supported, and a drive gear for the second speed stage is fixedly supported. A first coupling for selectively fixing the gears and the drive gear for the sixth speed stage to the first input shaft, respectively.
第２入力軸には、１速段用の駆動ギアと第１ギアが固定的に担持され、A drive gear for the first speed stage and a first gear are fixedly supported on the second input shaft,
出力軸には４速段を構成する４速段用の被駆動ギアと前記６速段用の駆動ギアに噛合する６速段用の被駆動ギアとが固定的に担持され、前記１速段用の駆動ギアに噛合する１速段用の被駆動ギアと５速段を構成する５速段用の被駆動ギアとが回転可能に担持され、かつ最クラッチ側において差動装置に接続する出力ギアが固定的に担持され、更に前記１速段用の被駆動ギアと前記５速段用の被駆動ギアとをそれぞれ前記出力軸に選択的に固定する第２カップリングが付設され、The output shaft fixedly carries a driven gear for the fourth speed stage that constitutes the fourth speed stage and a driven gear for the sixth speed stage that meshes with the driving gear for the sixth speed stage. The first gear driven gear meshing with the first drive gear and the fifth gear driven gear constituting the fifth gear are rotatably supported and connected to the differential device on the outermost clutch side. A gear is fixedly supported, and a second coupling for selectively fixing the driven gear for the first speed stage and the driven gear for the fifth speed stage to each of the output shafts is attached.
副軸には、３速段を構成する３速段用の被駆動ギアと、前記１速段用の駆動ギアにアイドラ軸に固定的に担持されているアイドラギアを介して接続する後進段用の被駆動ギアと、前記２速段用の駆動ギアに噛合する２速段用の被駆動ギアとが回転可能に担持されるとともに、第２ギアが固定的に担持され、更に、前記３速段用の被駆動ギアと前記後進段用の被駆動ギアとを前記副軸に選択的に固定する第３カップリングと前記２速段用の被駆動ギアを前記副軸に選択的に固定する第４カップリングとが付設されている構成であって、The countershaft is connected to a driven gear for the third speed stage that constitutes the third speed stage, and a reverse gear that is connected to the drive gear for the first speed stage via an idler gear fixedly supported on the idler shaft. A driven gear and a second gear driven gear meshing with the second gear are rotatably supported, a second gear is fixedly supported, and the third gear is further supported. A third coupling that selectively fixes the driven gear for the reverse gear and the driven gear for the reverse gear to the secondary shaft and a second coupling that selectively fixes the driven gear for the second speed stage to the secondary shaft. 4 couplings are attached, and
前記２個のギアのうちの一方のギアは前記第２ギアに噛合し、他方のギアは前記４速段用の被駆動ギアに噛合し、該一方のギアまたは該他方のギアには、該一方のギアと該他方のギアとを前記第１入力軸に選択的に固定する前記第１カップリングが付設されており、更に、前記第１ギアが前記３速段用の被駆動ギアと前記５速段用の被駆動ギアとに噛合されることを特徴とする変速機。One of the two gears meshes with the second gear, the other gear meshes with the driven gear for the fourth gear, and the one gear or the other gear has the gear The first coupling for selectively fixing one gear and the other gear to the first input shaft is provided, and the first gear further includes the driven gear for the third speed stage and the gear A transmission which is meshed with a driven gear for a fifth gear.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2001333618A JP3746222B2 (en) | 2001-10-31 | 2001-10-31 | transmission |
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| JP2001333618A JP3746222B2 (en) | 2001-10-31 | 2001-10-31 | transmission |
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| JP3746222B2 true JP3746222B2 (en) | 2006-02-15 |
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| CN103195879A (en) * | 2013-04-02 | 2013-07-10 | 天津市松正电动汽车技术股份有限公司 | Two speed transmission for hybrid power system |
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