JP4234947B2 - Drive unit for hydraulic pressure generator - Google Patents

Drive unit for hydraulic pressure generator Download PDF

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Publication number
JP4234947B2
JP4234947B2 JP2002145349A JP2002145349A JP4234947B2 JP 4234947 B2 JP4234947 B2 JP 4234947B2 JP 2002145349 A JP2002145349 A JP 2002145349A JP 2002145349 A JP2002145349 A JP 2002145349A JP 4234947 B2 JP4234947 B2 JP 4234947B2
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Japan
Prior art keywords
planetary gear
hydraulic pressure
generator
rotating
power
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Expired - Fee Related
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JP2002145349A
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JP2003336725A (en
Inventor
昌俊 足立
昌洋 小嶋
二郎 金子
一利 本池
孝昌 竹内
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Aisin AW Co Ltd
Toyota Motor Corp
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Aisin AW Co Ltd
Toyota Motor Corp
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
    • B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
    • B60K6/22—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs
    • B60K6/38—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs characterised by the driveline clutches
    • B60K6/383—One-way clutches or freewheel devices
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
    • B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
    • B60K6/22—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs
    • B60K6/36—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs characterised by the transmission gearings
    • B60K6/365—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs characterised by the transmission gearings with the gears having orbital motion
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
    • B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
    • B60K6/22—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs
    • B60K6/40—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs characterised by the assembly or relative disposition of components
    • B60K6/405—Housings
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
    • B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
    • B60K6/42—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by the architecture of the hybrid electric vehicle
    • B60K6/44—Series-parallel type
    • B60K6/445—Differential gearing distribution type
    • 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
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/0021—Generation or control of line pressure
    • F16H61/0025—Supply of control fluid; Pumps therefore
    • F16H61/0028—Supply of control fluid; Pumps therefore using a single pump driven by different power sources
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K1/00—Arrangement or mounting of electrical propulsion units
    • B60K1/02—Arrangement or mounting of electrical propulsion units comprising more than one electric motor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/0434—Features relating to lubrication or cooling or heating relating to lubrication supply, e.g. pumps ; Pressure control
    • F16H57/0436—Pumps
    • F16H57/0439—Pumps using multiple pumps with different power sources or a single pump with different power sources, e.g. one and the same pump may selectively be driven by either the engine or an electric motor
    • 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
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/0021—Generation or control of line pressure
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/60—Other road transportation technologies with climate change mitigation effect
    • Y02T10/62—Hybrid vehicles

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • General Engineering & Computer Science (AREA)
  • Arrangement Of Transmissions (AREA)
  • Hybrid Electric Vehicles (AREA)
  • General Details Of Gearings (AREA)

Description

【０００１】
【発明の属する技術分野】
この発明は、回転装置の動力により油圧発生装置を駆動するように構成された油圧発生装置用の駆動装置に関するものである。
【０００２】
【従来の技術】
従来、車両の動力伝達装置などにおいて、オイル必要部位にオイルを供給するために、回転装置の動力により油圧発生装置を駆動し、油圧発生装置から吐出されたオイルをオイル必要部位に供給する装置が知られており、その一例が特開平１０−８９４４６号公報に記載されている。この公報に記載された車両は、駆動力源としてエンジンおよび第２のモータを有するハイブリッド車である。エンジンおよび第２のモータは、その回転軸線同士が同心状に配置されており、エンジンと第２のモータとの間に遊星歯車機構が配置されている。
【０００３】
遊星歯車機構は、サンギヤおよびリングギヤと、サンギヤおよびリングギヤに噛合されるピニオンギヤを保持したキャリヤとを有し、エンジンのクランクシャフトがキャリヤに連結され、第２のモータの出力軸がリングギヤに連結されている。また、遊星歯車機構とエンジンとの間には、第１のモータが配置されており、第１のモータと遊星歯車機構のサンギヤとが連結されている。そして、第１のモータのトルクが遊星歯車機構を経由してエンジンに伝達されて、エンジンがクランキングされるとともに、エンジンまたは第２のモータの少なくとも一方のトルクが遊星歯車機構に伝達されて、そのトルクがリングリヤを経由して車輪に伝達される。
【０００４】
一方、動力伝達装置などのオイル必要部位にオイルを供給する油圧発生装置が設けられている。この油圧発生装置は、歯車ポンプにより構成されており、エンジンのクランクシャフトに連結されたキャリヤ軸および第２のモータの出力軸と、歯車ポンプのロータとが選択手段により連結されている。選択手段は、キャリヤ軸および第２のモータの出力軸に対応してそれぞれ設けられたワンウェイクラッチを有し、キャリヤ軸または第２のモータの出力軸のうち、回転数が高い方の動力により油圧発生装置を駆動するように構成されている。
【０００５】
【発明が解決しようとする課題】
しかしながら、上記の公報においては、油圧発生装置と、油圧発生装置を駆動する回転装置としてのエンジンおよび第２のモータと、遊星歯車機構とが、共に同心状に配置されているため、遊星歯車機構の回転軸線方向において、各システムの配置スペース（全長）が長くなり、車載性が低下するという問題があった。
【０００６】
この発明は上記の事情を背景としてなされたものであり、遊星歯車機構の回転軸線方向における部品の配置スペースを可及的に短くすることのできる油圧発生装置の駆動装置を提供することを目的としている。
【０００７】
【課題を解決するための手段およびその作用】
上記の目的を達成するために、請求項１の発明は、第１の回転装置および第２の回転装置と、回転軸線を中心として回転する３つの回転要素を有する遊星歯車機構とを備え、この遊星歯車機構の第１の回転要素が前記第１の回転装置に連結され、前記遊星歯車機構の第２の回転要素が第２の回転装置に連結されているとともに、前記第１の回転装置の動力または前記第２の回転装置の動力のうち、選択された一方の動力により回転されて油圧を発生する油圧発生装置を備えた油圧発生装置用の駆動装置において、前記第２の回転装置と前記遊星歯車機構と、この遊星歯車機構の第３の回転要素に連結された発電機とが同一の回転軸線上に配置されているとともに、前記遊星歯車機構と前記油圧発生装置とが、非同心状に配置されており、前記第１の回転装置が車輪に動力を伝達する第１の駆動力源としての機能を有し、前記第２の回転装置が車輪に動力を伝達する第２の駆動力源としての機能を有しているとともに、前記遊星歯車機構のサンギヤに連結された発電機が設けられており、前記回転軸線方向で、前記第２の回転装置と発電機との間に、前記遊星歯車機構および油圧発生装置が配置されており、前記第２の回転装置の出力を制御する変速機構が設けられているとともに、前記回転軸線方向で、前記遊星歯車機構および油圧発生装置と変速機構との間に、前記第２の回転装置が配置されていることを特徴とするものである。この発明において、同心状とは、同一の回転軸線を中心として回転すること、または、回転軸線同士が同心状に配置されていることを意味する。
【０００８】
請求項２の発明は、請求項１の構成に加えて、前記遊星歯車機構は、サンギヤと、このサンギヤと同心状に配置されたリングギヤと、前記サンギヤおよびリングギヤに噛合するピニオンギヤを保持するキャリヤとを備えているとともに、前記第１の回転要素がキャリヤであり、前記第２の回転要素がリングギヤであることを特徴とするものである。
【０００９】
請求項１または２の発明によれば、回転軸線方向における遊星歯車機構および油圧発生装置の配置スペースが狭められる。また、請求項１または２の発明によれば、第２の回転装置と発電機との間の空間に、遊星歯車機構および油圧発生装置が配置される。また、第２の回転装置および発電機の外径よりも、遊星歯車機構の外径の方が小さい場合は、遊星歯車機構の外側に油圧発生装置を配置すれば、第２の回転装置および発電機よりも外側に、油圧発生装置が突出することが抑制される。さらに、請求項１または２の発明によれば、遊星歯車機構および油圧発生装置と変速機構とが、回転軸線方向において別々の位置に配置されるため、これらの干渉が回避される。
【００１０】
請求項３の発明は、請求項１または２の構成に加えて、前記第１の回転装置の動力または前記第２の回転装置の動力のうち、いずれか一方の動力を選択し、かつ、選択された動力により油圧発生装置を駆動する選択装置が設けられており、前記遊星歯車機構の回転軸線方向で、この遊星歯車機構の配置領域と、前記選択装置の配置領域とが重なっていることを特徴とするものである。
【００１１】
請求項３の発明によれば、請求項１または２の発明と同様の作用が生じる他に、回転軸線方向における遊星歯車機構および選択装置の配置スペースが狭められる。
【００１６】
請求項４の発明は、請求項１ないし３のいずれかの構成に加えて、前記回転軸線を中心とする半径方向において、前記第２の回転装置または前記発電機の配置領域と、前記油圧発生装置の配置領域とが重なっていることを特徴とするものである。
【００１７】
請求項４の発明によれば、請求項１ないし３のいずれかの発明と同様の作用が生じるほかに、回転軸線を中心とする半径方向において、第２の回転装置または発電機よりも外側に、油圧発生装置が突出する量が一層少なくなる。
【００１８】
【発明の実施の形態】
つぎに、この発明を図面を参照しながら具体的に説明する。図１は、この発明の一実施例であるＦ・Ｒ（フロントエンジン・リヤドライブ；エンジン前置き後輪駆動）形式のハイブリッド車両（以下、車両と略記する）Ｖｅの概略構成図である。図１において、車両Ｖｅは、エンジン１および電動モータ２を有している。そして、エンジン１または電動モータ２のうちの少なくとも一方の動力が、車輪３に伝達されるように構成されている。
【００１９】
前記エンジン１としては内燃機関、具体的にはガソリンエンジン、ディーゼルエンジン、ＬＰＧエンジンなどを用いることができる。このエンジン１のクランクシャフト４は、車両Ｖｅの前後方向に配置された回転軸線Ａ１を中心として回転可能である。クランクシャフト４には、トルクリミッタ５、ダンパ機構６を介してインプットシャフト７が連結されている。また、車両Ｖｅの前後方向において、エンジン１の後方にはケーシング８が設けられており、ケーシング８の内部Ｂ１にインプットシャフト７が配置されている。
【００２０】
また、ケーシング８の内部Ｂ１には、前記電動モータ２および発電機９が配置されている。なお、この実施例では、電動モータ２および発電機９として、電気エネルギを機械エネルギに変換する力行機能と、機械エネルギを電気エネルギに変換する回生機能とを兼備したモータ・ジェネレータが用いられている。すなわち、蓄電装置（図示せず）の電力を電動モータ２または発電機９の少なくとも一方に供給し、電動モータ２または発電機９のうちの少なくとも一方を電動機として駆動することができる。これとは逆に、外力を与えて電動モータ２または発電機９のうちの少なくとも一方を回転させて発電し、その電力を蓄電装置に充電することもできる。
【００２１】
前記発電機９は、ステータ１０およびロータ１１と有しており、ステータ１０はケーシング８に固定されている。ロータ１１はステータ１０の内側に配置されており、ロータ１１には中空シャフト１２が連結されている。このロータ１１と中空シャフト１２とが一体回転可能に連結され、中空フャフト１２の内部にインプットシャフト７が配置されている。インプットシャフト７と中空シャフト１２とは相対回転可能である。さらに、前記インプットシャフト７には回転軸線方向に延ばされた油路５４が形成され、かつ、油路５４から半径方向に延ばされた油路５５が形成されている。
【００２２】
さらに、ケーシング８の内面には、回転軸線方向に所定間隔をおいて隔壁２４，２５が形成されている。２つの隔壁２４，２５には軸孔が形成されており、その軸孔内にインプットシャフト７が配置されている。そして、ケーシング８の内部Ｂ１であって、隔壁２４と隔壁２５との間に発電機収納室Ｃ１が形成され、発電機収納室Ｃ１内に発電機９が配置されている。なお、隔壁２４，２５に取り付けられた軸受２６により、中空シャフト１２が保持されている。
【００２３】
また、前記電動モータ２は、車両Ｖｅの前後方向において、発電機９の後方に配置されている。電動モータ２は、ステータ２０およびロータ２１を有している。ステータ２０はケーシング８に固定され、ステータ２０の内側にロータ２１が配置されている。また、ロータ２１と一体回転する中空シャフト２２が設けられている。中空シャフト２２は中間シャフト２３の外周に相対回転可能に取り付けられている。中空シャフト２２および中間シャフト２３は回転軸線Ａ１を中心として相対回転可能である。中間シャフト２３には回転軸線方向に延ばされた油路５３が形成されており、油路５３から半径方向に延ばされた油路５６が形成されている。また、中空シャフト２２には半径方向に延ばされた油路５７が形成されており、油路５６と油路５７とが連通されている。
【００２４】
一方、ケーシング８の内面であって、車両Ｖｅの前後方向における隔壁２５よりも後方には、回転軸線方向に所定間隔をおいて隔壁２７，２８が形成されている。２つの隔壁２７，２８には軸孔が形成されており、その軸孔内に中間シャフト２３が配置されている。そして、ケーシング８の内部Ｂ１であって、隔壁２７と隔壁２８との間に電動モータ収納室Ｄ１が形成され、電動モータ収納室Ｄ１内に電動モータ２が配置されている。なお、隔壁２７，２８に取り付けられた軸受２９により、中空シャフト２２が保持されている。
【００２５】
さらに、車両Ｖｅの前後方向において、発電機９と電動モータ２との間、具体的には、隔壁２５と隔壁２７との間の空間Ｇ１には、動力分割機構としての遊星歯車機構１３が設けられている。この遊星歯車機構１３は、いわゆるシングルピニオン形式の遊星歯車機構である。すなわち、遊星歯車機構１３は、中空シャフト１２と一体回転するサンギヤ１４と、サンギヤ１４と同心状に配置された環状体１５と、環状体１５の内周に形成されたリングギヤ（インナーギヤ）１６と、サンギヤ１４およびリングギヤ１６に噛合するピニオンギヤ１７を保持したキャリヤ１８と、環状体１５の外周に形成されたアウターギヤ１９とを有している。キャリヤ１８の外周にはアウターギヤ３０が形成されている。なお、リングギヤ１６を有する環状体１５の外径は、電動モータ２および発電機９の外径よりも小さい。
【００２６】
前記遊星歯車機構１３および電動モータ２および発電機９は、同一の回転軸線Ａ１上に配置されている。前記油路５５は、遊星歯車機構１３の内側に開口している。なお、アウターギヤ３０の歯数とアウターギヤ１９の歯数とは同一に設定されている。前記キャリヤ１８とインプットシャフト７とが一体回転するように連結されている。また、前記中間シャフト２３と環状体１５とが一体回転するように連結されている。
【００２７】
一方、ケーシング８の内部Ｂ１であって、回転軸線方向における電動モータ２と発電機９との間には、オイルポンプ３１が設けられている。具体的には、回転軸線Ａ１を中心とする半径方向において、遊星歯車機構１３の外側にオイルポンプ３１が配置されている。このオイルポンプ３１は、隔壁２７に固定されたボデー３２と、ボデー３２の内部に回転可能に配置されたロータ３３とを有している。ロータ３３には回転軸３４が連結されている。ロータ３３および回転軸３４は、回転軸線Ｅ１を中心として一体回転する。そして、回転軸線Ｅ１と回転軸線Ａ１とは相互に平行に、かつ、非同心状に配置されている。
【００２８】
また、回転軸３４の外周には２つのギヤ３５，３６が取り付けられている。ギヤ３５，３６も空間Ｇ１内に設けられており、ギヤ３５の歯数とギヤ３５の歯数とは同一に設定されている。なお、回転軸線Ａ１を中心とする半径方向において、電動モータ２または発電機９の配置領域の少なくとも一部と、オイルポンプ３１の配置領域の少なくとも一部が重なっている。
【００２９】
このように、アウターギヤ３０とギヤ３５との間の変速比と、アウターギヤ１９とギヤ３６との間の変速比とが、同一に設定されている。そして、ギヤ３５とアウターギヤ３０とが噛合され、ギヤ３６とアウターギヤ１９とが噛合されている。さらに、ギヤ３５と回転軸３４とがワンウェイクラッチ３７により連結され、ギヤ３６と回転軸３４とがワンウェイクラッチ３８により連結されている。
【００３０】
ここで、回転軸３４とギヤ３５，３６とが一体回転する向き、および回転軸３４とギヤ３５，３６とが相対回転する向きが共に同じとなるように、ワンウェイクラッチ３７，３８の回転規制方法および回転許容方向が同じに設定されている。上記構成により、アウターギヤ１９またはアウターギヤ３０のうち、回転数が高い方のギヤの動力が回転軸３４に伝達されて、その回転軸３４に伝達される動力によりオイルポンプ３１が駆動される。また、回転軸線Ａ１方向において、ギヤ３５，３６およびワンウェイクラッチ３７，３８の配置領域の少なくとも一部と、遊星歯車機構１３の配置領域の少なくとも一部とが重なっている。
【００３１】
一方、オイルポンプ３１の吸い込み口３９は、オイルパン（図示せず）に接続されている。また、オイルポンプ３１の吐出口から吐出されるオイルの一部が流れるオイル供給管４０が、ケーシング８の内部に設けられている。オイル供給管４０には分岐部４１を介して２つの副供給管４２，４３が接続されている。副供給管４２の開口部は発電機収納室Ｃ１に配置され、副供給管４３の開口部は電動モータ収納室Ｄ１に配置されている。なお、オイルポンプ３１から吐出されたオイルは、油路５３，５４にも供給されるように構成されている。
【００３２】
さらにケーシング８の内部Ｂ１であって、車両Ｖｅの前後方向で隔壁２８よりも後方の空間Ｆ１には、リダクション機構４４が設けられている。このリダクション機構４４は、いわゆるシングルピニオン形式の遊星歯車機構により構成されている。すなわち、リダクション機構４４は、中空シャフト２２と一体回転するサンギヤ４５と、サンギヤ４５と同心状に配置されたリングギヤ４６と、サンギヤ４５およびリングギヤ４６に噛合するピニオンギヤ４７を保持したキャリヤ４８とを有している。このキャリヤ４８はケーシング８に固定されている。また、前記油路５７は空間Ｆ１に開口している。上記のように構成されたオイルポンプ３１、オイル供給管４０、副供給管４２，４３、油路５３，５４，５５，５６，５７などにより、潤滑装置が構成されている。
【００３３】
さらに、ケーシング８の内部Ｂ１の空間Ｆ１から、ケーシング８の外部に亘って、アウトプットシャフト４９が設けられている。ケーシング８の軸孔には軸受５０が取り付けられており、アウトプットシャフト４９は軸受５０により保持されている。したがって、アウトプットシャフト４９は回転軸線Ａ１を中心として回転可能である。また、アウトプットシャフト４９と中間シャフト２３とが一体回転するように連結され、アウトプットシャフト４９とリングギヤ４６とが一体回転するように連結されている。なお、アウトプットシャフト４９にはパーキングギヤ５１が取り付けられており、ケーシング８の内部Ｂ１にはパーキングギヤ５１に係合・離脱してアウトプットシャフト４９の回転を防止・許容するパーキング機構（図示せず）が設けられている。
【００３４】
つぎに、車両Ｖｅの制御について説明する。まず、車両Ｖｅが停止している際にエンジン１を始動する場合は、蓄電装置（図示せず）から発電機９に電力を供給して、発電機９を電動機として駆動させる。そして、発電機９のトルクが、サンギヤ１４に伝達されると、リングギヤ１９が反力要素となり、キャリヤ１８が回転する。このキャリヤ１８のトルクは、インプットシャフト７を経由してクランクシャフト４に伝達される。
【００３５】
このようにして、エンジン１がクランキングされるとともに、エンジン１がガソリンエンジンであれば、燃料噴射制御および点火制御がおこなわれて、エンジン１が自律回転する。このエンジン１のトルクは、クランクシャフト４、インプットシャフト７、キャリヤ１８を介して環状体１５に伝達される。環状体１５のトルクは、中間シャフト２３、アウトプットシャフト４９を経由して車輪３に伝達される。なお、エンジン１の回転時には、エンジン１の動力の一部を遊星歯車機構１３を経由して発電機９に伝達し、発電機９で発電された電力を蓄電装置に充電することもできる。つまり、遊星歯車機構１３は、エンジン１の動力を車輪３と発電機９とに分割する、いわゆる動力分割機構としての機能を備えている。
【００３６】
また、蓄電装置の電力が電動モータ２に供給されて、電動モータ２が駆動されると、そのトルクが中空シャフト２２、サンギヤ４５、ピニオンギヤ４７、サンギヤ４６を経由してアウトプットシャフト４９に伝達される。この場合、リダクション機構４４のキャリヤ４８が反力要素となり、電動モータ２の回転方向とが逆方向にリングギヤ４６が回転する。さらに、電動モータ２の回転速度に対して、アウトプットシャフト４９の回転速度は減速される。
【００３７】
このように、車両Ｖｅにおいては、エンジン１または電動モータ２のうち、少なくとも一方の動力を車輪３に伝達することができる。そして、エンジン１および電動モータ２の動力は、アウトプットシャフト４９で合成されて、合成された動力が車輪３に伝達される。
【００３８】
これに対して、車両Ｖｅが惰力走行する場合は、車輪３の回転エネルギを電動モータ２または発電機９のうちの少なくとも一方に伝達し、電動モータ２または発電機９の少なくとも一方を発電機として機能させ、発生した電力を蓄電装置に充電することもできる。
【００３９】
そして、この実施例によれば、遊星歯車機構１３の回転軸線Ａ１と、オイルポンプ３１の回転軸線Ｅ１とが非同心状に配置されている。したがって、回転軸線Ａ１方向において、遊星歯車機構１３およびオイルポンプ３１の配置スペースを狭くすることができ、車両Ｖｅの前後方向におけるケーシング８の全長が短くなり、車載性が向上する。
【００４０】
また、この実施例においては、遊星歯車機構１３の回転軸線Ａ１方向において、遊星歯車機構１３の配置領域と、ギヤ３５，３６およびワンウェイクラッチ３７，３８の配置領域とが、少なくとも一部で重なっている。したがって、車両Ｖｅの前後方向において、遊星歯車機構１３およびギヤ３５，３６およびワンウェイクラッチ３７，３８の配置スペースが狭められ、車載性が一層向上する。
【００４１】
さらにこの実施例によれば、発電機９と電動モータ２との間にある空間Ｇ１に、遊星歯車機構１３およびオイルポンプ３１を配置している。したがって、オイルポンプ３１を配置する専用の空間を確保する必要がなく、車載性が一層向上する。特に、発電機９または電動モータ２の外径よりも、遊星歯車機構１３の外径の方が小さく設定され、遊星歯車機構１３の外側にオイルポンプ１３が配置されているため、発電機９または電動モータ２の外側に向けてオイルポンプ１３の突出する量が抑制され、車載性が一層向上する。さらにこの実施例によれば、遊星歯車機構１３およびオイルポンプ３１とリダクション機構４４とが、回転軸線Ａ１方向において別々の位置に配置されるため、これらの干渉が回避される。
【００４２】
ここで、オイルポンプ３１の駆動による潤滑機能および冷却機能について説明する。まず、エンジン１が駆動されている場合について説明する。エンジン１の動力がキャリヤ１８に伝達されると、そのトルクの一部がギヤ３５に伝達されるとともに、ワンウェイクラッチ３７が係合されて、ギヤ３５のトルクが回転軸３４を経由してオイルポンプ３１に伝達される。このようにしてオイルポンプ３１が駆動されて、オイルパンのオイルが汲み上げられる。
【００４３】
そして、オイルポンプ３１から吐出されたオイルが、オイル供給管４０および副供給管４２，４３を経由して、発電機収納室Ｃ１および電動モータ収納室Ｄ１に供給される。電動モータ収納室Ｄ１に供給されたオイルは、油路５２を経由して空間Ｆ１に供給されて、リダクション機構４４がオイルにより潤滑および冷却される。また、オイル供給管４０のオイルの一部は、遊星歯車機構１３に供給される。したがって、車両Ｖｅが停止している場合でも、エンジン１が運転されていれば、そのエンジン１の動力によりオイルポンプ３１を駆動して、発熱部位、摩耗部位、摺動部位などを有するオイル必要部位に、オイルが供給され、オイル必要部位を強制的に潤滑および冷却できる。この実施例では、発電機収納室Ｃ１、空間Ｇ１，Ｆ１、電動モータ収納室Ｄ１などが、オイル必要部に相当する。
【００４４】
つぎに、エンジン１が停止され、かつ、電動モータ２が駆動されて、電動モータ２のトルクが車輪３に伝達されるモード、つまり、電動モータ２による走行モードが選択された場合について説明する。この場合は、電動モータ２の動力が、アウトプットシャフト４９および中間シャフト２３を経由して、アウタギヤ１９およびギヤ３６に伝達される。すると、ワンウェイクラッチ３８が係合されて、ギヤ３６のトルクが回転軸３４を経由してオイルポンプ３１に伝達される。したがって、前述と同様にして、オイルポンプ３１のオイルによりオイル必要部位にオイルを供給できる。
【００４５】
さらに、エンジン１および電動モータ２が共に駆動されている場合は、ギヤ３５またはギヤ３６のうち、回転数の高い方のギヤに対応するワンウェイクラッチが係合され、回転数が低い方のギヤに対応するワンウェイクラッチが解放される。そして、回転数が高い方のギヤのトルクが回転軸３４に伝達されて、オイルポンプ３１が駆動される。言い換えれば、エンジン１の動力または電動モータの動力のうち、いずれか一方の動力が選択されて、選択された動力によりオイルポンプ３１が駆動される。
【００４６】
つまり、エンジン１および電動モータ２という２つの動力源に対する潤滑機能を、１つのオイルポンプ３１で実施することができる。したがって、潤滑装置の部品点数の増加を抑制でき、製造コストの低減、ユニットのコンパクト化、質量の低減を図ることができる。また、エンジン１および電動モータ２が共に駆動される場合でも、一方の動力のみでオイルポンプ３１が駆動されるため、オイルポンプ３１からオイルが必要以上に吐出されることを防止できる。したがって、潤滑装置ユニットの効率向上に貢献できるとともに、エンジン１の動力が無駄になることもなく、燃費を向上することもできる。
【００４７】
また、エンジン１または電動モータ２のうち、いずれの動力によりオイルポンプ３１を駆動するかの選択が、ワンウェイクラッチ３７，３８の機能により、機械的におこなわれる。このため、エンジン１または電動モータ２のうち、いずれの動力によりオイルポンプ３１を駆動するかの選択をおこなうために、電気的な制御システムを設ける必要がない。また、ギヤ３５またはギヤ３６のうち、回転数が高い方のギヤで伝達される動力により、オイルポンプ３１が駆動される。うまり、焼き付く可能性が高い方の回転部材により伝達される動力でオイルポンプ３１が駆動される。したがって、オイルポンプ３１の吐出量を、回転数が高い方の回転部材の回転数に見合ったものとすることができる。
【００４８】
さらに、図１に示すようなパワートレーンを有するＦＲ車両においては、車輪に動力を伝達するための回転部材が、同一の回転軸線Ａ１上に配置されている。このため、ＦＦ車両のように、インプットシャフトとは異なる回転軸線上に配置されている回転部材（カウンタギヤ、デファレンシャルのリングギヤなど）により掻き上げられるオイルを、インプットシャフト側のオイル必要部に供給することはできないが、この実施例においては、このような不都合を回避できる。特に、電動モータ２の動力により車両Ｖｅが走行する場合に、潤滑に必要なオイルを確保することができる。
【００４９】
さらに、この実施例においては、ワンウェイクラッチ３７，３８を、オイルポンプ３１のロータ３３の内側に設けることなく、ワンウェイクラッチ３７，３８と、ロータ３３とが同じ回転軸線Ｅ１上に配置されている。したがって、オイルポンプ３１のオイル吐出機能が、ワンウェイクラッチ３７，３８により制約を受けることなく、オイルポンプ３１の構造の自由度が高まる。その結果、必要以上の吐出量を持つオイルポンプを構成する必要がなく、潤滑装置ユニットの効率向上に貢献できる。
【００５０】
さらに、エンジン１を停止し、かつ、電動モータ２のトルクを、アウトプットシャフト４９を経由して車輪３に伝達する際には、アウトプットシャフト４９と共に中間シャフト２３も回転する。中間シャフト２３が回転すると、環状部材１５も回転するが、サンギヤ１４とピニオンギヤ１７との噛み合い部分、リングギヤ１６とピニオンギヤ１７との噛み合い部分における噛み合い抵抗（言い換えれば負荷）は少ない。したがって、動力分割機構１３で焼き付きや摩耗が発生する可能性は低い。
【００５１】
これに対して、電動モータ２のトルクがリダクション機構４４を経由して車輪３に伝達される場合は、リダクション機構４４におけるギヤ同士の噛み合い部分に大きな負荷が発生し、オイルによる潤滑が必要となる。そして、この実施例においては、電動モータ２の動力のみで車両が走行する場合も、オイルポンプ３１を駆動して、その吐出オイルを油路５２を経由させてリダクション機構４４に供給することができる。
【００５２】
さらにこの実施例によれば、オイルポンプ３１から吐出されるオイルにより、電動モータ２をも冷却することができる。したがって、ケーシング８の内部に、動力分割機構１３、発電機９などを潤滑・冷却する装置の他に、特別な冷却構造などの付属物を設けることなく、ケーシング８の内部でオイルの流れが完結する簡素な構造で、電動モータ２を冷却することができる。さらに、ギヤなどの回転部材でオイルを掻き上げ、そのオイルで電動モータを冷却する構成の比較例と、オイル供給管４０、副供給管４３、油路５２などを用いて強制的に電動モータ２を冷却する実施例とを比較した場合、この実施例の方が、電動モータ２の冷却に必要なオイル量を、確実に電動モータ収納室Ｄ１に供給することができ、冷却効果が高い。
【００５３】
さらにこの実施例においては、オイルポンプ３１から吐出されたオイルの一部が、インプットシャフト５４および中間シャフト２３の軸心に形成されている油路５３，５４に供給され、そのオイルにより、ケーシング８内の摺動部、例えば、動力分割機構１３およびリダクション機構４４を、潤滑および冷却することもできる。したがって、電動モータ２の冷却と、摺動部の潤滑および冷却に対応して、２つの潤滑装置を別々に設ける必要がなく、潤滑装置のユニットをコンパクトに構成できる。
【００５４】
またこの実施例では、電動モータ２を冷却するオイルを、オイル供給管４０、副供給管４２，４３を経由して輸送している。つまり、ケーシング自体を切削加工して油路を形成し、その油路からオイルを供給する比較例と、実施例とを比較した場合、実施例の方が、オイルの供給方向、オイルを供給する断面積などの自由度が高い。また、実施例によれば、オイルの供給先毎に、管の断面積を変えることにより、オイルの必要量に応じて、オイルの供給量を設定できる。
【００５５】
またこの実施例では、リダクション機構４４を構成するキャリヤ４８がケーシング８に固定されているため、油路５７から空間Ｆ１に供給されるオイルを、サンギヤ４５の回転にともなう遠心力で外側に送る際に、オイルの流れがキャリヤ４８で阻害されるが、油路５２を経由して空間Ｆ１に供給されるオイルにより、リダクション機構４４を潤滑することができる。
【００５６】
ここで、この実施例の構成とこの発明の構成との対応関係を説明すれば、エンジン１がこの発明の第１の回転装置および第１の駆動力源に相当し、電動モータ２がこの発明の第２の回転装置および第２の駆動力源に相当し、サンギヤ１４、キャリヤ１８、リングギヤ１６がこの発明の遊星歯車機構および３つの回転要素に相当し、キャリヤ１８がこの発明の第１の回転要素に相当し、リングギヤ１６がこの発明の第２の回転要素に相当し、サンギヤ１４がこの発明の第３の回転要素に相当し、オイルポンプ３１がこの発明の油圧発生装置に相当し、回転軸線Ａ１がこの発明の回転軸線に相当し、リダクション機構４４がこの発明の変速機構に相当し、ギヤ３５，３６およびワンウェイクラッチ３７，３８がこの発明の選択装置に相当する。
【００５７】
【発明の効果】
以上説明したように請求項１または２の発明によれば、回転軸線方向で、遊星歯車機構および油圧発生装置の配置スペースを狭めることができる。したがって、回転軸線方向における駆動装置の全長をなるべく短縮することができ、車載性が向上する。また、第２の回転装置および発電機の外径よりも、遊星歯車機構の外径の方が小さい場合は、遊星歯車機構の外側に油圧発生装置を配置すれば、第２の回転装置および発電機よりも外側に、油圧発生装置が突出することを抑制できる。また、請求項１または２の発明によれば、第２の回転装置と発電機との間の空間を、遊星歯車機構および油圧発生装置の配置空間として利用できる。したがって、回転軸線方向の全長を一層短くでき、車載性が一層向上する。また、請求項１または２の発明によれば、遊星歯車機構および油圧発生装置と変速機構とが、回転軸線方向において別々の位置に配置されるため、油圧発生装置と変速機構との干渉を回避できる。
【００５８】
請求項３の発明によれば、請求項１または２の発明と同様の効果を得られる他に、回転軸線方向で、遊星歯車機構および選択装置の配置スペースを狭めることができる。したがって、車載性が一層向上する。
【００６１】
請求項４の発明によれば、請求項１ないし３のいずれかの発明と同様の効果を得られるほかに、回転軸線を中心とする半径方向において、第２の回転装置または発電機よりも外側に、油圧発生装置が突出する量が一層少なくなり、車載性が向上する。
【図面の簡単な説明】
【図１】 この発明のハイブリッド車両のパワートレーンの構成例を示す図である。
【符号の説明】
１…エンジン、 ２…電動モータ、 ３…車輪、 ９…発電機、 １３…遊星歯車機構、 １４…サンギヤ、 １６…リングギヤ、 １８…キャリヤ、 ３１…オイルポンプ、 ３５，３６…ギヤ、 ３７，３８…ワンウェイクラッチ、 ４４…リダクション機構、 Ａ１，Ｅ１…回転軸線。[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a drive unit for a hydraulic pressure generator configured to drive the hydraulic pressure generator by the power of a rotating device.
[0002]
[Prior art]
2. Description of the Related Art Conventionally, in a power transmission device of a vehicle or the like, there is a device that drives a hydraulic pressure generator by power of a rotating device and supplies oil discharged from the hydraulic pressure generator to an oil required portion in order to supply oil to the oil required portion. One known example is described in Japanese Patent Laid-Open No. 10-89446. The vehicle described in this publication is a hybrid vehicle having an engine and a second motor as driving force sources. The rotation axes of the engine and the second motor are arranged concentrically, and a planetary gear mechanism is arranged between the engine and the second motor.
[0003]
The planetary gear mechanism has a sun gear and a ring gear, and a carrier holding a pinion gear meshed with the sun gear and the ring gear, the engine crankshaft is connected to the carrier, and the output shaft of the second motor is connected to the ring gear. Yes. A first motor is disposed between the planetary gear mechanism and the engine, and the first motor and the sun gear of the planetary gear mechanism are connected to each other. The torque of the first motor is transmitted to the engine via the planetary gear mechanism, the engine is cranked, and the torque of at least one of the engine or the second motor is transmitted to the planetary gear mechanism, The torque is transmitted to the wheels via the ring rear.
[0004]
On the other hand, a hydraulic pressure generator for supplying oil to a necessary oil part such as a power transmission device is provided. This hydraulic pressure generator is constituted by a gear pump, and a carrier shaft connected to an engine crankshaft and an output shaft of a second motor and a rotor of the gear pump are connected by a selection means. The selection means has one-way clutches respectively provided corresponding to the carrier shaft and the output shaft of the second motor, and is hydraulically driven by the power having the higher rotational speed of the carrier shaft or the output shaft of the second motor. The generator is configured to be driven.
[0005]
[Problems to be solved by the invention]
However, in the above publication, the oil pressure generating device, the engine and the second motor as a rotating device for driving the oil pressure generating device, and the planetary gear mechanism are all arranged concentrically. In the direction of the rotation axis, the arrangement space (full length) of each system becomes long, and there is a problem that the in-vehicle performance is deteriorated.
[0006]
The present invention has been made against the background described above, and it is an object of the present invention to provide a drive device for a hydraulic pressure generator capable of shortening the arrangement space of components in the rotational axis direction of a planetary gear mechanism as much as possible. Yes.
[0007]
[Means for Solving the Problem and Action]
  In order to achieve the above object, the invention of claim 1 comprises a first rotating device and a second rotating device, and a planetary gear mechanism having three rotating elements that rotate about a rotation axis. The first rotating element of the planetary gear mechanism is connected to the first rotating device, the second rotating element of the planetary gear mechanism is connected to the second rotating device, and the first rotating device of the first rotating device A driving device for a hydraulic pressure generator including a hydraulic pressure generator that generates a hydraulic pressure by being rotated by a selected one of the power or the power of the second rotating device, the second rotating device, The planetary gear mechanism and the generator connected to the third rotating element of the planetary gear mechanism are disposed on the same rotation axis, and the planetary gear mechanism and the hydraulic pressure generator are non-concentric. Placed inThe first rotating device has a function as a first driving force source that transmits power to the wheels, and the second rotating device serves as a second driving force source that transmits power to the wheels. And a generator connected to the sun gear of the planetary gear mechanism is provided between the second rotating device and the generator in the rotation axis direction. And a hydraulic pressure generating device, a transmission mechanism for controlling the output of the second rotating device is provided, and between the planetary gear mechanism and the hydraulic pressure generating device and the transmission mechanism in the rotational axis direction. The second rotating device is disposed on theIt is characterized by. In the present invention, the term “concentric” means that the axes rotate about the same axis of rotation, or the axes of rotation are arranged concentrically.
[0008]
According to a second aspect of the present invention, in addition to the configuration of the first aspect, the planetary gear mechanism includes a sun gear, a ring gear arranged concentrically with the sun gear, and a carrier holding a pinion gear meshing with the sun gear and the ring gear. The first rotating element is a carrier, and the second rotating element is a ring gear.
[0009]
  According to the first or second aspect of the present invention, the space for arranging the planetary gear mechanism and the hydraulic pressure generator in the direction of the rotation axis is reduced.. According to the first or second aspect of the present invention, the planetary gear mechanism and the hydraulic pressure generator are disposed in the space between the second rotating device and the generator. Further, when the outer diameter of the planetary gear mechanism is smaller than the outer diameters of the second rotating device and the generator, the second rotating device and the power generation can be achieved by disposing a hydraulic pressure generator outside the planetary gear mechanism. It is possible to prevent the hydraulic pressure generator from protruding outside the machine. Furthermore, according to the first or second aspect of the present invention, the planetary gear mechanism, the hydraulic pressure generating device, and the speed change mechanism are arranged at different positions in the rotation axis direction, so that interference between them is avoided.
[0010]
According to a third aspect of the present invention, in addition to the configuration of the first or second aspect, any one of the power of the first rotating device and the power of the second rotating device is selected and selected. A selection device for driving the hydraulic pressure generating device with the generated power is provided, and the arrangement region of the planetary gear mechanism and the arrangement region of the selection device overlap in the rotation axis direction of the planetary gear mechanism. It is a feature.
[0011]
According to the invention of claim 3, in addition to the effects similar to those of the invention of claim 1 or 2, the space for arranging the planetary gear mechanism and the selection device in the direction of the rotation axis is narrowed.
[0016]
  ClaimThe invention of claim 4 is the invention of claims 1 to 3.In addition to any of the configurations, the arrangement area of the second rotating device or the generator and the arrangement area of the hydraulic pressure generator overlap each other in the radial direction centered on the rotation axis. To do.
[0017]
  ClaimAccording to invention of Claim 4, Claims 1 thru | or 3 ofIn addition to the effects similar to any of the inventions, the amount of the hydraulic pressure generator protruding further outward than the second rotating device or the generator in the radial direction centered on the rotation axis is further reduced.
[0018]
DETAILED DESCRIPTION OF THE INVENTION
Next, the present invention will be specifically described with reference to the drawings. FIG. 1 is a schematic configuration diagram of a hybrid vehicle (hereinafter abbreviated as a vehicle) Ve of an FR type (front engine / rear drive; engine front and rear wheel drive) according to an embodiment of the present invention. In FIG. 1, a vehicle Ve has an engine 1 and an electric motor 2. The power of at least one of the engine 1 or the electric motor 2 is transmitted to the wheels 3.
[0019]
As the engine 1, an internal combustion engine, specifically, a gasoline engine, a diesel engine, an LPG engine, or the like can be used. The crankshaft 4 of the engine 1 is rotatable around a rotation axis A1 disposed in the front-rear direction of the vehicle Ve. An input shaft 7 is connected to the crankshaft 4 via a torque limiter 5 and a damper mechanism 6. Further, a casing 8 is provided behind the engine 1 in the front-rear direction of the vehicle Ve, and an input shaft 7 is disposed inside the casing 8.
[0020]
Further, the electric motor 2 and the generator 9 are arranged in the interior B <b> 1 of the casing 8. In this embodiment, as the electric motor 2 and the generator 9, a motor / generator having both a power running function for converting electrical energy into mechanical energy and a regeneration function for converting mechanical energy into electrical energy is used. . That is, the electric power of the power storage device (not shown) can be supplied to at least one of the electric motor 2 or the generator 9 and at least one of the electric motor 2 or the generator 9 can be driven as an electric motor. On the contrary, it is also possible to generate power by applying an external force to rotate at least one of the electric motor 2 or the generator 9 and charge the power storage device.
[0021]
The generator 9 has a stator 10 and a rotor 11, and the stator 10 is fixed to the casing 8. The rotor 11 is disposed inside the stator 10, and a hollow shaft 12 is connected to the rotor 11. The rotor 11 and the hollow shaft 12 are coupled so as to be integrally rotatable, and the input shaft 7 is disposed inside the hollow shaft 12. The input shaft 7 and the hollow shaft 12 are relatively rotatable. Further, an oil passage 54 extending in the rotation axis direction is formed in the input shaft 7, and an oil passage 55 extending in the radial direction from the oil passage 54 is formed.
[0022]
Furthermore, partition walls 24 and 25 are formed on the inner surface of the casing 8 at a predetermined interval in the rotation axis direction. A shaft hole is formed in the two partition walls 24 and 25, and the input shaft 7 is disposed in the shaft hole. A generator storage chamber C1 is formed between the partition wall 24 and the partition wall 25 in the interior B1 of the casing 8, and the generator 9 is disposed in the generator storage chamber C1. The hollow shaft 12 is held by a bearing 26 attached to the partition walls 24 and 25.
[0023]
The electric motor 2 is disposed behind the generator 9 in the front-rear direction of the vehicle Ve. The electric motor 2 has a stator 20 and a rotor 21. The stator 20 is fixed to the casing 8, and a rotor 21 is disposed inside the stator 20. A hollow shaft 22 that rotates integrally with the rotor 21 is provided. The hollow shaft 22 is attached to the outer periphery of the intermediate shaft 23 so as to be relatively rotatable. The hollow shaft 22 and the intermediate shaft 23 are relatively rotatable about the rotation axis A1. An oil passage 53 extending in the rotation axis direction is formed in the intermediate shaft 23, and an oil passage 56 extending in the radial direction from the oil passage 53 is formed. An oil passage 57 extending in the radial direction is formed in the hollow shaft 22, and the oil passage 56 and the oil passage 57 are communicated with each other.
[0024]
On the other hand, on the inner surface of the casing 8 and behind the partition wall 25 in the front-rear direction of the vehicle Ve, partition walls 27 and 28 are formed at a predetermined interval in the rotation axis direction. A shaft hole is formed in the two partition walls 27 and 28, and the intermediate shaft 23 is disposed in the shaft hole. An electric motor storage chamber D1 is formed in the casing B1 between the partition wall 27 and the partition wall 28, and the electric motor 2 is arranged in the electric motor storage chamber D1. The hollow shaft 22 is held by a bearing 29 attached to the partition walls 27 and 28.
[0025]
Further, in the front-rear direction of the vehicle Ve, a planetary gear mechanism 13 as a power split mechanism is provided in the space G1 between the generator 9 and the electric motor 2, specifically, between the partition wall 25 and the partition wall 27. It has been. The planetary gear mechanism 13 is a so-called single pinion type planetary gear mechanism. That is, the planetary gear mechanism 13 includes a sun gear 14 that rotates integrally with the hollow shaft 12, an annular body 15 that is arranged concentrically with the sun gear 14, and a ring gear (inner gear) 16 that is formed on the inner periphery of the annular body 15. The carrier 18 holds a pinion gear 17 that meshes with the sun gear 14 and the ring gear 16, and the outer gear 19 is formed on the outer periphery of the annular body 15. An outer gear 30 is formed on the outer periphery of the carrier 18. The outer diameter of the annular body 15 having the ring gear 16 is smaller than the outer diameters of the electric motor 2 and the generator 9.
[0026]
The planetary gear mechanism 13, the electric motor 2, and the generator 9 are disposed on the same rotation axis A1. The oil passage 55 opens to the inside of the planetary gear mechanism 13. The number of teeth of the outer gear 30 and the number of teeth of the outer gear 19 are set to be the same. The carrier 18 and the input shaft 7 are connected to rotate integrally. Further, the intermediate shaft 23 and the annular body 15 are connected so as to rotate integrally.
[0027]
On the other hand, an oil pump 31 is provided inside the casing 8 and between the electric motor 2 and the generator 9 in the rotation axis direction. Specifically, the oil pump 31 is disposed outside the planetary gear mechanism 13 in the radial direction about the rotation axis A1. The oil pump 31 includes a body 32 fixed to the partition wall 27, and a rotor 33 that is rotatably disposed inside the body 32. A rotation shaft 34 is connected to the rotor 33. The rotor 33 and the rotation shaft 34 rotate integrally around the rotation axis E1. The rotation axis E1 and the rotation axis A1 are arranged parallel to each other and non-concentrically.
[0028]
Two gears 35 and 36 are attached to the outer periphery of the rotating shaft 34. The gears 35 and 36 are also provided in the space G1, and the number of teeth of the gear 35 and the number of teeth of the gear 35 are set to be the same. In the radial direction centered on the rotation axis A1, at least a part of the arrangement region of the electric motor 2 or the generator 9 and at least a part of the arrangement region of the oil pump 31 overlap.
[0029]
In this way, the transmission ratio between the outer gear 30 and the gear 35 and the transmission ratio between the outer gear 19 and the gear 36 are set to be the same. The gear 35 and the outer gear 30 are engaged with each other, and the gear 36 and the outer gear 19 are engaged with each other. Further, the gear 35 and the rotating shaft 34 are connected by a one-way clutch 37, and the gear 36 and the rotating shaft 34 are connected by a one-way clutch 38.
[0030]
Here, the rotation restricting method of the one-way clutches 37, 38 is such that the direction in which the rotating shaft 34 and the gears 35, 36 rotate integrally and the direction in which the rotating shaft 34 and the gears 35, 36 rotate relative to each other are the same. And the allowable rotation direction are set to be the same. With the above configuration, the power of the outer gear 19 or the outer gear 30 with the higher rotational speed is transmitted to the rotating shaft 34, and the oil pump 31 is driven by the power transmitted to the rotating shaft 34. Further, at least a part of the arrangement region of the gears 35 and 36 and the one-way clutches 37 and 38 overlaps at least a part of the arrangement region of the planetary gear mechanism 13 in the direction of the rotation axis A1.
[0031]
On the other hand, the suction port 39 of the oil pump 31 is connected to an oil pan (not shown). An oil supply pipe 40 through which a part of the oil discharged from the discharge port of the oil pump 31 flows is provided in the casing 8. Two sub supply pipes 42 and 43 are connected to the oil supply pipe 40 via a branching portion 41. The opening of the sub supply pipe 42 is disposed in the generator storage chamber C1, and the opening of the sub supply pipe 43 is disposed in the electric motor storage chamber D1. Note that the oil discharged from the oil pump 31 is also supplied to the oil passages 53 and 54.
[0032]
Further, a reduction mechanism 44 is provided in a space F <b> 1 inside the casing 8 and behind the partition wall 28 in the front-rear direction of the vehicle Ve. The reduction mechanism 44 is constituted by a so-called single pinion type planetary gear mechanism. That is, the reduction mechanism 44 includes a sun gear 45 that rotates integrally with the hollow shaft 22, a ring gear 46 that is disposed concentrically with the sun gear 45, and a carrier 48 that holds a pinion gear 47 that meshes with the sun gear 45 and the ring gear 46. ing. The carrier 48 is fixed to the casing 8. The oil passage 57 is open to the space F1. The oil pump 31, the oil supply pipe 40, the sub supply pipes 42 and 43, the oil passages 53, 54, 55, 56, and 57 configured as described above constitute a lubrication device.
[0033]
Further, an output shaft 49 is provided from the space F <b> 1 in the inside B <b> 1 of the casing 8 to the outside of the casing 8. A bearing 50 is attached to the shaft hole of the casing 8, and the output shaft 49 is held by the bearing 50. Therefore, the output shaft 49 can rotate around the rotation axis A1. Further, the output shaft 49 and the intermediate shaft 23 are connected so as to rotate integrally, and the output shaft 49 and the ring gear 46 are connected so as to rotate integrally. A parking gear 51 is attached to the output shaft 49, and a parking mechanism (not shown) that engages and disengages the parking gear 51 to prevent / allow rotation of the output shaft 49 inside the casing 8. Is provided.
[0034]
Next, control of the vehicle Ve will be described. First, when the engine 1 is started when the vehicle Ve is stopped, electric power is supplied from a power storage device (not shown) to the generator 9 to drive the generator 9 as an electric motor. When the torque of the generator 9 is transmitted to the sun gear 14, the ring gear 19 becomes a reaction force element, and the carrier 18 rotates. The torque of the carrier 18 is transmitted to the crankshaft 4 via the input shaft 7.
[0035]
In this way, the engine 1 is cranked, and if the engine 1 is a gasoline engine, fuel injection control and ignition control are performed, and the engine 1 rotates autonomously. The torque of the engine 1 is transmitted to the annular body 15 via the crankshaft 4, the input shaft 7 and the carrier 18. Torque of the annular body 15 is transmitted to the wheel 3 via the intermediate shaft 23 and the output shaft 49. When the engine 1 rotates, a part of the motive power of the engine 1 can be transmitted to the generator 9 via the planetary gear mechanism 13, and the electric power generated by the generator 9 can be charged to the power storage device. That is, the planetary gear mechanism 13 has a function as a so-called power split mechanism that splits the power of the engine 1 into the wheels 3 and the generator 9.
[0036]
When the electric power of the power storage device is supplied to the electric motor 2 and the electric motor 2 is driven, the torque is transmitted to the output shaft 49 via the hollow shaft 22, the sun gear 45, the pinion gear 47, and the sun gear 46. . In this case, the carrier 48 of the reduction mechanism 44 serves as a reaction force element, and the ring gear 46 rotates in the direction opposite to the rotation direction of the electric motor 2. Further, the rotational speed of the output shaft 49 is reduced with respect to the rotational speed of the electric motor 2.
[0037]
Thus, in the vehicle Ve, at least one power of the engine 1 or the electric motor 2 can be transmitted to the wheels 3. The power of the engine 1 and the electric motor 2 is combined by the output shaft 49, and the combined power is transmitted to the wheels 3.
[0038]
On the other hand, when the vehicle Ve travels by repulsion, the rotational energy of the wheels 3 is transmitted to at least one of the electric motor 2 or the generator 9, and at least one of the electric motor 2 or the generator 9 is transmitted to the generator. The generated power can be charged to the power storage device.
[0039]
According to this embodiment, the rotation axis A1 of the planetary gear mechanism 13 and the rotation axis E1 of the oil pump 31 are arranged non-concentrically. Therefore, the arrangement space of the planetary gear mechanism 13 and the oil pump 31 can be narrowed in the direction of the rotation axis A1, the overall length of the casing 8 in the front-rear direction of the vehicle Ve is shortened, and the onboard performance is improved.
[0040]
In this embodiment, the arrangement region of the planetary gear mechanism 13 and the arrangement region of the gears 35 and 36 and the one-way clutches 37 and 38 overlap at least partially in the direction of the rotational axis A1 of the planetary gear mechanism 13. Yes. Therefore, in the front-rear direction of the vehicle Ve, the arrangement space for the planetary gear mechanism 13, the gears 35 and 36, and the one-way clutches 37 and 38 is narrowed, and the onboard performance is further improved.
[0041]
Furthermore, according to this embodiment, the planetary gear mechanism 13 and the oil pump 31 are arranged in the space G1 between the generator 9 and the electric motor 2. Therefore, it is not necessary to secure a dedicated space for disposing the oil pump 31, and the in-vehicle performance is further improved. In particular, the outer diameter of the planetary gear mechanism 13 is set to be smaller than the outer diameter of the generator 9 or the electric motor 2, and the oil pump 13 is disposed outside the planetary gear mechanism 13. The amount by which the oil pump 13 protrudes toward the outside of the electric motor 2 is suppressed, and the in-vehicle performance is further improved. Furthermore, according to this embodiment, the planetary gear mechanism 13, the oil pump 31, and the reduction mechanism 44 are disposed at different positions in the direction of the rotation axis A1, and thus interference thereof is avoided.
[0042]
Here, a lubrication function and a cooling function by driving the oil pump 31 will be described. First, the case where the engine 1 is driven will be described. When the power of the engine 1 is transmitted to the carrier 18, a part of the torque is transmitted to the gear 35 and the one-way clutch 37 is engaged, and the torque of the gear 35 is transmitted to the oil pump via the rotating shaft 34. 31. In this way, the oil pump 31 is driven and the oil in the oil pan is pumped up.
[0043]
The oil discharged from the oil pump 31 is supplied to the generator storage chamber C1 and the electric motor storage chamber D1 via the oil supply pipe 40 and the sub supply pipes 42 and 43. The oil supplied to the electric motor storage chamber D1 is supplied to the space F1 via the oil passage 52, and the reduction mechanism 44 is lubricated and cooled by the oil. A part of the oil in the oil supply pipe 40 is supplied to the planetary gear mechanism 13. Therefore, even when the vehicle Ve is stopped, if the engine 1 is in operation, the oil pump 31 is driven by the power of the engine 1 and the oil-required part having a heat generation part, a wear part, a sliding part, and the like. In addition, oil is supplied to force lubricate and cool parts where oil is necessary. In this embodiment, the generator storage chamber C1, the spaces G1 and F1, the electric motor storage chamber D1, and the like correspond to the oil required portion.
[0044]
Next, a case where the engine 1 is stopped and the electric motor 2 is driven to transmit the torque of the electric motor 2 to the wheels 3, that is, the traveling mode by the electric motor 2 is selected will be described. In this case, the power of the electric motor 2 is transmitted to the outer gear 19 and the gear 36 via the output shaft 49 and the intermediate shaft 23. Then, the one-way clutch 38 is engaged, and the torque of the gear 36 is transmitted to the oil pump 31 via the rotating shaft 34. Accordingly, in the same manner as described above, the oil can be supplied to the oil required portion by the oil of the oil pump 31.
[0045]
Further, when both the engine 1 and the electric motor 2 are driven, the one-way clutch corresponding to the gear 35 or the gear 36 having the higher rotational speed is engaged, and the gear having the lower rotational speed is engaged. The corresponding one-way clutch is released. Then, the torque of the gear having the higher rotational speed is transmitted to the rotating shaft 34, and the oil pump 31 is driven. In other words, either one of the power of the engine 1 or the power of the electric motor is selected, and the oil pump 31 is driven by the selected power.
[0046]
That is, the lubrication function for the two power sources of the engine 1 and the electric motor 2 can be performed by the single oil pump 31. Therefore, the increase in the number of parts of the lubricating device can be suppressed, and the manufacturing cost can be reduced, the unit can be made compact, and the mass can be reduced. Further, even when both the engine 1 and the electric motor 2 are driven, the oil pump 31 is driven by only one power, so that it is possible to prevent oil from being discharged from the oil pump 31 more than necessary. Therefore, it is possible to contribute to improving the efficiency of the lubrication device unit, and it is possible to improve fuel efficiency without wasting power of the engine 1.
[0047]
The selection of which power to drive the oil pump 31 from the engine 1 or the electric motor 2 is mechanically performed by the function of the one-way clutches 37 and 38. For this reason, it is not necessary to provide an electrical control system in order to select which power of the engine 1 or the electric motor 2 drives the oil pump 31. Further, the oil pump 31 is driven by the power transmitted by the gear 35 or the gear 36 having the higher rotational speed. The oil pump 31 is driven by the power transmitted by the rotating member that is more likely to burn and seize. Therefore, the discharge amount of the oil pump 31 can be matched with the rotational speed of the rotating member having the higher rotational speed.
[0048]
Further, in an FR vehicle having a power train as shown in FIG. 1, rotating members for transmitting power to the wheels are arranged on the same rotation axis A1. For this reason, as in the FF vehicle, the oil scraped up by the rotating member (counter gear, differential ring gear, etc.) disposed on the rotation axis different from the input shaft is supplied to the oil required portion on the input shaft side. Although this is not possible, this inconvenience can be avoided in this embodiment. In particular, when the vehicle Ve travels by the power of the electric motor 2, oil necessary for lubrication can be secured.
[0049]
Further, in this embodiment, the one-way clutches 37 and 38 and the rotor 33 are arranged on the same rotation axis E1 without providing the one-way clutches 37 and 38 inside the rotor 33 of the oil pump 31. Therefore, the oil discharge function of the oil pump 31 is not restricted by the one-way clutches 37 and 38, and the degree of freedom of the structure of the oil pump 31 is increased. As a result, it is not necessary to configure an oil pump having a discharge amount that is higher than necessary, and it is possible to contribute to improving the efficiency of the lubricating device unit.
[0050]
Further, when the engine 1 is stopped and the torque of the electric motor 2 is transmitted to the wheels 3 via the output shaft 49, the intermediate shaft 23 also rotates together with the output shaft 49. When the intermediate shaft 23 rotates, the annular member 15 also rotates. However, the meshing resistance (in other words, the load) at the meshing portion between the sun gear 14 and the pinion gear 17 and the meshing portion between the ring gear 16 and the pinion gear 17 is small. Therefore, there is a low possibility that seizure or wear will occur in the power split mechanism 13.
[0051]
On the other hand, when the torque of the electric motor 2 is transmitted to the wheels 3 via the reduction mechanism 44, a large load is generated in the meshing portion of the gears in the reduction mechanism 44, and lubrication with oil is necessary. . In this embodiment, even when the vehicle travels only with the power of the electric motor 2, the oil pump 31 can be driven and the discharged oil can be supplied to the reduction mechanism 44 via the oil passage 52. .
[0052]
Furthermore, according to this embodiment, the electric motor 2 can also be cooled by the oil discharged from the oil pump 31. Accordingly, the oil flow is completed inside the casing 8 without providing any special cooling structure or the like in addition to the device for lubricating and cooling the power split mechanism 13 and the generator 9 inside the casing 8. The electric motor 2 can be cooled with a simple structure. Further, the electric motor 2 is forcibly used by using a comparative example in which the oil is scraped up by a rotating member such as a gear and the electric motor is cooled by the oil, and the oil supply pipe 40, the sub supply pipe 43, the oil passage 52, and the like. In this embodiment, the amount of oil necessary for cooling the electric motor 2 can be reliably supplied to the electric motor storage chamber D1, and the cooling effect is higher.
[0053]
Furthermore, in this embodiment, part of the oil discharged from the oil pump 31 is supplied to oil passages 53 and 54 formed in the shaft centers of the input shaft 54 and the intermediate shaft 23, and the casing 8 The inner sliding portion, for example, the power split mechanism 13 and the reduction mechanism 44 can be lubricated and cooled. Therefore, it is not necessary to separately provide two lubrication devices corresponding to the cooling of the electric motor 2 and the lubrication and cooling of the sliding portion, and the unit of the lubrication device can be made compact.
[0054]
In this embodiment, the oil for cooling the electric motor 2 is transported via the oil supply pipe 40 and the sub supply pipes 42 and 43. That is, when the comparative example in which the casing itself is cut to form an oil passage and the oil is supplied from the oil passage is compared with the embodiment, the embodiment supplies the oil in the oil supply direction. High degree of freedom in cross-sectional area. According to the embodiment, the supply amount of oil can be set according to the required amount of oil by changing the cross-sectional area of the pipe for each oil supply destination.
[0055]
Further, in this embodiment, since the carrier 48 constituting the reduction mechanism 44 is fixed to the casing 8, when the oil supplied from the oil passage 57 to the space F 1 is sent to the outside by the centrifugal force accompanying the rotation of the sun gear 45. In addition, although the oil flow is inhibited by the carrier 48, the reduction mechanism 44 can be lubricated by the oil supplied to the space F <b> 1 via the oil passage 52.
[0056]
Here, the correspondence between the configuration of this embodiment and the configuration of the present invention will be described. The engine 1 corresponds to the first rotating device and the first driving force source of the present invention, and the electric motor 2 corresponds to the present invention. The sun gear 14, the carrier 18, and the ring gear 16 correspond to the planetary gear mechanism and the three rotating elements of the present invention, and the carrier 18 corresponds to the first rotating device and the second driving force source of the present invention. The ring gear 16 corresponds to the second rotating element of the present invention, the sun gear 14 corresponds to the third rotating element of the present invention, the oil pump 31 corresponds to the hydraulic pressure generator of the present invention, The rotation axis A1 corresponds to the rotation axis of the present invention, the reduction mechanism 44 corresponds to the speed change mechanism of the present invention, and the gears 35 and 36 and the one-way clutches 37 and 38 correspond to the selection device of the present invention.
[0057]
【The invention's effect】
  As described above, according to the first or second aspect of the present invention, the arrangement space for the planetary gear mechanism and the hydraulic pressure generator can be reduced in the direction of the rotation axis. Therefore, the overall length of the drive device in the direction of the rotation axis can be shortened as much as possible, and the in-vehicle performance is improved. Further, when the outer diameter of the planetary gear mechanism is smaller than the outer diameters of the second rotating device and the generator, the second rotating device and the power generation can be achieved by disposing a hydraulic pressure generator outside the planetary gear mechanism. The oil pressure generator can be prevented from protruding outside the machine.. According to the first or second aspect of the invention, the space between the second rotating device and the generator can be used as an arrangement space for the planetary gear mechanism and the hydraulic pressure generator. Therefore, the overall length in the direction of the rotation axis can be further shortened, and the on-vehicle performance is further improved. According to the first or second aspect of the present invention, the planetary gear mechanism, the hydraulic pressure generating device, and the transmission mechanism are arranged at different positions in the rotation axis direction, so that interference between the hydraulic pressure generating device and the transmission mechanism is avoided. it can.
[0058]
According to the invention of claim 3, in addition to obtaining the same effect as that of the invention of claim 1 or 2, the arrangement space of the planetary gear mechanism and the selection device can be narrowed in the direction of the rotation axis. Therefore, the onboard performance is further improved.
[0061]
  ClaimAccording to invention of Claim 4, Claims 1 thru | or 3 ofIn addition to obtaining the same effect as any one of the inventions, the amount of the oil pressure generating device protruding further outward from the second rotating device or the generator in the radial direction around the rotation axis is reduced. Improves.
[Brief description of the drawings]
FIG. 1 is a diagram showing a configuration example of a power train of a hybrid vehicle according to the present invention.
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 1 ... Engine, 2 ... Electric motor, 3 ... Wheel, 9 ... Generator, 13 ... Planetary gear mechanism, 14 ... Sun gear, 16 ... Ring gear, 18 ... Carrier, 31 ... Oil pump, 35, 36 ... Gear, 37, 38 ... one-way clutch, 44 ... reduction mechanism, A1, E1 ... rotation axis.

Claims (4)

第１の回転装置および第２の回転装置と、回転軸線を中心として回転する３つの回転要素を有する遊星歯車機構とを備え、この遊星歯車機構の第１の回転要素が前記第１の回転装置に連結され、前記遊星歯車機構の第２の回転要素が第２の回転装置に連結されているとともに、前記第１の回転装置の動力または前記第２の回転装置の動力のうち、選択された一方の動力により回転されて油圧を発生する油圧発生装置を備えた油圧発生装置用の駆動装置において、
前記第２の回転装置と前記遊星歯車機構と、この遊星歯車機構の第３の回転要素に連結された発電機とが同一の回転軸線上に配置されているとともに、前記遊星歯車機構と前記油圧発生装置とが、非同心状に配置されており、
前記第１の回転装置が車輪に動力を伝達する第１の駆動力源としての機能を有し、前記第２の回転装置が車輪に動力を伝達する第２の駆動力源としての機能を有しているとともに、前記遊星歯車機構のサンギヤに連結された発電機が設けられており、前記回転軸線方向で、前記第２の回転装置と発電機との間に、前記遊星歯車機構および油圧発生装置が配置されており、
前記第２の回転装置の出力を制御する変速機構が設けられているとともに、前記回転軸線方向で、前記遊星歯車機構および油圧発生装置と変速機構との間に、前記第２の回転装置が配置されていることを特徴とする油圧発生装置用の駆動装置。A first rotating device, a second rotating device, and a planetary gear mechanism having three rotating elements rotating around a rotation axis, wherein the first rotating element of the planetary gear mechanism is the first rotating device. And the second rotating element of the planetary gear mechanism is connected to the second rotating device, and the power of the first rotating device or the power of the second rotating device is selected. In a drive device for a hydraulic pressure generator having a hydraulic pressure generator that is rotated by one power to generate hydraulic pressure,
The second rotating device, the planetary gear mechanism, and a generator connected to a third rotating element of the planetary gear mechanism are disposed on the same rotation axis, and the planetary gear mechanism and the hydraulic pressure are arranged. The generator is arranged non-concentrically ,
The first rotating device has a function as a first driving force source that transmits power to the wheels, and the second rotating device has a function as a second driving force source that transmits power to the wheels. And a generator connected to the sun gear of the planetary gear mechanism is provided between the second rotating device and the generator in the direction of the rotation axis. The device is located,
A transmission mechanism for controlling the output of the second rotating device is provided, and the second rotating device is disposed between the planetary gear mechanism, the hydraulic pressure generating device, and the transmission mechanism in the rotation axis direction. which do drive for the hydraulic pressure generating apparatus according to claim Rukoto. 前記遊星歯車機構は、サンギヤと、このサンギヤと同心状に配置されたリングギヤと、前記サンギヤおよびリングギヤに噛合するピニオンギヤを保持するキャリヤとを備えているとともに、前記第１の回転要素がキャリヤであり、前記第２の回転要素がリングギヤであることを特徴とする請求項１に記載の油圧発生装置用の駆動装置。  The planetary gear mechanism includes a sun gear, a ring gear arranged concentrically with the sun gear, and a carrier that holds the sun gear and a pinion gear that meshes with the ring gear, and the first rotating element is a carrier. The drive device for a hydraulic pressure generator according to claim 1, wherein the second rotating element is a ring gear. 前記第１の回転装置の動力または前記第２の回転装置の動力のうち、いずれか一方の動力を選択し、かつ、選択された動力により油圧発生装置を駆動する選択装置が設けられており、前記遊星歯車機構の回転軸線方向で、この遊星歯車機構の配置領域と、前記選択装置の配置領域とが重なっていることを特徴とする請求項１または２に記載の油圧発生装置用の駆動装置。  A selection device is provided that selects one of the power of the first rotating device or the power of the second rotating device, and drives the hydraulic pressure generator with the selected power, 3. The drive device for a hydraulic pressure generator according to claim 1, wherein an arrangement region of the planetary gear mechanism and an arrangement region of the selection device overlap with each other in a rotation axis direction of the planetary gear mechanism. . 前記回転軸線を中心とする半径方向において、前記第２の回転装置または前記発電機の配置領域と、前記油圧発生装置の配置領域とが重なっていることを特徴とする請求項１ない３のいずれかに記載の油圧発生装置用の駆動装置。 In the radial direction around the pre-Symbol rotation axis, said second rotary device or arrangement region of the generator, according to claim 1 to 3, characterized in that the overlap and the arrangement region of the hydraulic pressure generating device A drive device for a hydraulic pressure generator according to any one of the above.
JP2002145349A 2002-05-20 2002-05-20 Drive unit for hydraulic pressure generator Expired - Fee Related JP4234947B2 (en)

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JP4145250B2 (en) * 2004-01-27 2008-09-03 トヨタ自動車株式会社 Hybrid vehicle drive system
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JP4151635B2 (en) * 2004-09-27 2008-09-17 トヨタ自動車株式会社 Vehicle drive device
JP4315087B2 (en) * 2004-09-27 2009-08-19 トヨタ自動車株式会社 Vehicle drive device
WO2006035982A2 (en) * 2004-09-27 2006-04-06 Toyota Jidosha Kabushiki Kaisha Drive apparatus for vehicle
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JP4059877B2 (en) 2004-10-14 2008-03-12 トヨタ自動車株式会社 Hybrid drive device
WO2006137602A1 (en) * 2005-06-24 2006-12-28 Toyota Jidosha Kabushiki Kaisha Drive device for vehicle
DE102007045032A1 (en) 2006-10-16 2008-04-17 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Pump e.g. oil pump, drive arrangement for use in hybrid vehicle drive train, has pump drive unit connected with drive device via freewheel device or with another drive device via another freewheel device
JP4898508B2 (en) * 2007-03-20 2012-03-14 トヨタ自動車株式会社 Lubrication structure and vehicle drive device
JP4311477B2 (en) 2007-05-11 2009-08-12 トヨタ自動車株式会社 Hybrid drive device
JP4203527B1 (en) * 2007-07-18 2009-01-07 アイシン・エィ・ダブリュ株式会社 Hybrid vehicle drive device
JP4858495B2 (en) 2008-06-20 2012-01-18 トヨタ自動車株式会社 Vehicle power transmission device
US8226516B2 (en) * 2010-06-07 2012-07-24 GM Global Technology Operations LLC Electric torque converter with dual-driven main pump
JP5500380B2 (en) * 2010-09-14 2014-05-21 アイシン・エィ・ダブリュ株式会社 Cooling structure of rotating electric machine
JP5325188B2 (en) 2010-09-24 2013-10-23 アイシン・エィ・ダブリュ株式会社 Hydraulic pressure generator and drive device
JP5297429B2 (en) * 2010-09-24 2013-09-25 アイシン・エィ・ダブリュ株式会社 Hydraulic pressure generator and drive device
JP5654411B2 (en) * 2011-04-27 2015-01-14 本田技研工業株式会社 Vehicle drive device
JP2013023011A (en) * 2011-07-19 2013-02-04 Toyota Motor Corp Power transmission device for hybrid vehicle
JP5747779B2 (en) * 2011-10-18 2015-07-15 トヨタ自動車株式会社 Lubricator for power transmission device
US9180869B2 (en) * 2011-11-11 2015-11-10 Toyota Jidosha Kabushiki Kaisha Hybrid drive system
JP5875075B2 (en) * 2012-09-28 2016-03-02 アイシン・エィ・ダブリュ株式会社 Vehicle drive device
JP6302294B2 (en) * 2014-03-11 2018-03-28 株式会社Ｓｕｂａｒｕ Vehicle drive device

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP7325165B2 (en) 2016-12-02 2023-08-14 雪印メグミルク株式会社 Oil and fat composition and plastic oil and fat composition containing the oil and fat composition

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