CN102303512A - 混合动力车辆 - Google Patents
混合动力车辆 Download PDFInfo
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- CN102303512A CN102303512A CN2010102291662A CN201010229166A CN102303512A CN 102303512 A CN102303512 A CN 102303512A CN 2010102291662 A CN2010102291662 A CN 2010102291662A CN 201010229166 A CN201010229166 A CN 201010229166A CN 102303512 A CN102303512 A CN 102303512A
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- oil pump
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/0434—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
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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
- B60K6/36—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
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- 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
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- 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
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- Hybrid Electric Vehicles (AREA)
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Abstract
本发明涉及可缩小宽度方向突出,特别是不向曲轴一侧偏置突出的混合动力车辆。该混合动力车辆包括:发动机(5);电机(6);将发动机和电机的动力传递给后轮(WR)的动力传递机构(7);及随着曲轴(50)的旋转润滑发动机与动力传递机构的油泵(9)。油泵在油泵轴(91)的一端,经由单向离合器(94)设置有油泵从动齿轮(92),该油泵从动齿轮与初级驱动齿轮(58)连接,利用电机的动力旋转,初级驱动齿轮与将电机的动力传递给后轮的电机从动齿轮(59)一体地旋转。在油泵轴的另一端,通过单向离合器(95)设置有与发动机凸轮链条(39)连接并利用发动机的动力旋转的油泵从动链轮(93)。电机从动齿轮配置在曲轴的一侧,凸轮链条配置在曲轴的另一侧。
Description
技术领域
本发明涉及一种带有内燃机和电动机两个驱动源的混合动力车辆。
背景技术
作为混合动力车辆用的动力单元,公知技术有例如专利文献1的混合动力车辆用动力单元(例如,专利文献1)。
专利文献1的混合动力车辆用的动力单元,包括:将来自电动机的驱动力通过单向离合器驱动油泵的第一驱动径路和将来自内燃机的驱动力通过单向离合器驱动油泵的第二驱动径路。这两个单向离合器通过驱动油泵的油泵驱动轴在轴向连接地设置(并联)着。该油泵设置在内燃机曲轴的一侧,在曲轴一侧的突出量大。四轮车辆的内燃机与两轮车辆的内燃机相比是大型的,为了便于确保配置空间,可配置在曲轴的一侧。
专利文献1:(日本)特许第4203527号
然而,在两轮车辆中,需要尽力地避免宽度方向的突出,特别是,不希望偏向曲轴的一侧。
发明内容
鉴于此,本发明的目的是,提供一种可缩小宽度方向的突出,特别是不向曲轴一侧偏置地突出的混合动力车辆。
为了实现上述目的,第一方面记载的发明,提供一种混合动力车辆,其包括:内燃机;电动机;将上述内燃机与上述电动机的动力传递给被驱动部的动力传递机构;以及随着曲轴的旋转润滑上述内燃机与上述动力传递机构的油泵,
上述油泵在油泵轴的一端,经由第一单向离合器设置有第一输入部,该第一输入部与将上述电动机的动力传递给上述被驱动部的传递部件一体旋转的输出部连接,并通过上述电动机的动力进行旋转,在上述油泵轴的另一端,通过第二单向离合器设置有与上述内燃机的凸轮链条连接并利用上述内燃机的动力旋转的第二输入部,
上述传递部件配置在上述曲轴的一侧,上述凸轮链条配置在上述曲轴的另一侧。
另外,第二方面记载的发明,在第一方面记载的混合动力车辆中,上述油泵轴随着通过上述电动机的动力而旋转的上述第一输入部和通过上述内燃机的动力而旋转的上述第二输入部中的旋转速度快的一方进行旋转。
另外,第三方面记载的发明,在第一方面记载的混合动力车辆中,上述油泵本体位于支持上述曲轴的曲轴箱和上述传递部件之间,上述第一输入部位于上述油泵本体和上述传递部件之间。
另外,第四方面记载的发明,在第一方面记载的混合动力车辆中,上述第一输入部配置在气缸的一侧,上述第二输入部配置在上述气缸的另一侧。
另外,第五方面记载的发明,在第一方面记载的混合动力车辆中,上述油泵本体位于上述第一输入部和上述第二输入部之间。
另外,第六方面记载的发明,在第一方面记载的混合动力车辆中,上述第二输入部比上述第一输入部具有可高旋转的传动比。
另外,第七方面记载的发明,在第一方面记载的混合动力车辆中,在上述动力传递机构的中间轴(日文:カウンタ軸)的端部,设置有接受润滑油的飞沫油回收部件,
容纳在上述飞沫油回收部件中的润滑油经由上述中间轴内的油路进行润滑。
另外,第八方面记载的发明,在第一方面记载的混合动力车辆中,在上述中间轴的下方设置有车速检测用齿轮,该车速检测用齿轮设置在能浸入储留在曲轴箱下面的润滑油中的位置,
从上述曲轴箱朝前方延伸设置的肋指向上述动力传递机构的变速齿轮系。
根据第一方面记载的混合动力车辆,由于在随着曲轴的旋转润滑内燃机与动力传递机构的油泵的油泵轴上设置有第一输入部,第一输入部与输出部连接,该输出部与将电动机的动力传递给被驱动部的部件一体地旋转,因此,即使在通过电动机进行EV行驶的情况下,也能驱动油泵,用润滑油来润滑内燃机和动力传递机构。因此,即使在EV行驶时曲轴停止的状态下,也能润滑内燃机和动力传递机构。
另外,由于在油泵轴的一端经由第一单向离合器设置有利用电动机的动力而旋转的第一输入部,在油泵轴的另一端经由第二单向离合器设置有与内燃机的凸轮链条连接并利用内燃机的动力而旋转的第二输入部,因此,可通过电动机和内燃机的任意一方有选择地驱动油泵,润滑内燃机和动力传递机构。
进一步,由于传递部件配置在曲轴的一侧,凸轮链条配置在曲轴的另一侧,所以,可缩小宽度方向的突出,特别是能防止向曲轴一侧偏置地突出。
根据第二方面记载的混合动力车辆,由于油泵随着通过电动机的动力而旋转的第一输入部和通过内燃机的动力而旋转的第二输入部中的旋转速度快的一方进行旋转,所以,可对应行驶状态进行适当地润滑。
根据第三方面记载的混合动力车辆,由于油泵本体位于支持曲轴的曲轴箱和传递部件之间,第一输入部位于油泵本体和传递部件之间,所以,可将油泵本体配置在有限的空间内。
根据第四方面记载的混合动力车辆,由于将第一及第二输入部隔着气缸配置在相反的对极位置上,所以,可以将所必要的空间分配在气缸的左右,使油泵小型化。
根据第五方面记载的混合动力车辆,由于油泵本体位于第一输入部和第二输入部之间,所以,可将油泵本体配置在有限的空间内。
根据第六方面记载的混合动力车辆,由于第二输入部比第一输入部具有可高旋转的传动比,所以,发动机起动后,可通过凸轮链条驱动油泵进行适当的润滑。
根据第七方面记载的混合动力车辆,由于在动力传递机构的中间轴的端部,设置有接受润滑油的飞沫油回收部件,容纳在上述飞沫油回收部件中的润滑油经由上述中间轴内的油路进行润滑,因此,可有效地回收飞散的润滑油进行润滑。
根据第八方面记载的混合动力车辆,由于在中间轴的下方设置有车速检测用齿轮,该车速检测用齿轮设置在能浸入储留在曲轴箱下面的润滑油中的位置,从该曲轴箱朝前方延伸设置的肋指向上述动力传递机构的变速齿轮系,因此,利用车速检测用齿轮的旋转,可有效地对变速齿轮系供给润滑油。
附图说明
图1是本发明动力混合车辆一个实施方式的两轮车辆的侧视图。
图2是图1所示两轮车辆的动力单元的轴向剖面图。
图3是图1所示两轮车辆的动力单元的局部剖面图。
图4是动力单元的变速机构的剖面图。
图5是沿图4中Ⅴ-Ⅴ线的剖面图。
图6是沿图4中Ⅵ-Ⅵ线的剖面图。
图7是沿图4中Ⅶ-Ⅶ线的剖面图。
图8是动力单元变速部空档的剖面图。
图9是选择了动力单元变速部的驱动模式状态的剖面图。
图10是选择了动力单元变速部的低速模式状态的剖面图。
图11是图3的局部放大图。
图12是局部切开动力单元的、从侧方看到的侧视图。
图13是图12中的局部放大图。
图14是中间轴端部的局部放大图。
图15是图1所示两轮车辆动力单元的轴直行方向的剖面图。
附图标记说明
1两轮摩托车(混合动力车辆)
2车体车架,5-发动机(内燃机)
6电机(电动机)
7动力传递机构
8两级离心离合器(变速机构)
9油泵
39凸轮链条
50曲轴
54气缸
57曲轴箱
58初级驱动齿轮(输出部)
59电机从动齿轮(传递部件)
71中间轴
76车速检测用输入齿轮(车速检测用齿轮)
79飞沫油回收部件
91油泵轴
92油泵从动齿轮(第一输入部)
93油泵从动链轮(第二输入部)
94单向离合器(第一单向离合器)
95单向离合器(第二单向离合器)
571下面
572肋
710油路
736低速齿轮对(变速齿轮系)
737高速齿轮对(变速齿轮系)
O车体中心线
P动力单元
WR后轮(被驱动轮)。
具体实施方式
下文,参照附图,说明本发明动力混合车辆的一个实施方式。图1是本发明动力混合车辆的一个实施方式的侧视图。
本发明的动力混合车辆是两轮摩托车。该两轮摩托车1的车体车架2包括:可转向地支撑前叉24的前管21;从该前管21向后下方延伸的主车架22;以及连接地设置在该主车架22的后部并向后上方延伸的左右一对后车架23。前轮WF轴支撑在前叉24的下端,在前叉24的上部连接有杆状转向车把25,在前叉24上,支持有覆盖前轮WF上方的前护板26a。另外,在该两轮摩托车1上,设有从前护板26a的上方延伸到后下方并用来保护驾驶员腿部的腿护罩26b。
在主车架22的下方,配置有以气缸轴线C为大致水平方向使曲轴50(参照图2)指向车体宽度方向地配设的发动机(内燃机)5。该发动机5通过上述悬架板27…及枢轴板28支持,悬挂在车体车架2上。
在上述枢轴板28上,可上下摆动地支撑着后叉29的前端部,后轮WR轴支撑在后叉29的后端。另外,在车体车架2的后车架23…和后叉29之间设置有后缓冲器30。
上述发动机5与电机(电动机)6及动力传递机构7一起,构成下文的动力单元P,动力传递机构7的输出通过驱动链条31传递给作为被驱动部的后轮WR。
另外,在上述发动机5的上方,配置有油门机构32、起动电机33以及固定在主车架22上的空气滤清器36(参照图12)。在后轮WR的上方,配置有燃料箱34,配置在该燃料箱34前方的收纳箱35和上述燃料箱34的上方,用例如前后排列式的乘车用座S可开闭地覆盖。
下文,参照图2和图3,详细说明本实施方式的动力混合车辆的动力单元。图2和图3是图1所示两轮车辆的动力单元的剖面图,O是表示宽度方向中心的车体中心线。
动力单元P主要包括:作为驱动源的发动机5和电机6、将发动机5和电机6的动力传递给后轮WR的动力传递机构7、在发动机5和动力传递机构7之间对发动机5的动力进行变速且传递给动力传递机构7而作为变速机构的两级离心离合器8以及油泵9。
在电机6和起动电机33上连接有图中未图示的蓄电池,蓄电池在电机6作为发动机发挥功能时以及当起动电机33作为起动机发挥功能时,对它们供给电力,在电机6作为发电机发挥功能时,构成以再生电力被充电的结构。此外,蓄电池可以搭载在例如图1的B1所示的与燃料箱34轴向邻接的空间中,还可以搭载在B2所示的左右腿护罩26b内的空间中。
在发动机5的进气管内转动自由地设有控制空气量的节流阀321(参照图15)。该节流阀321容纳在油门机构32内,对应于搭乘者操作的油门松紧(未图示)的操作量转动。此外,在本实施方式中,搭载有TBW(配线连接油门,日文:スロツトル·バイ·ワイヤ)系统,检测驾驶员操作的加速器的开度,根据该检测的加速器开度及各种来自传感器的信号,计算出节流阀321的最合适的开度,根据该计算的节流阀开度,通过促动器320(参照图12)进行节流阀321的开闭。此外,在图12中,符号321是构成连接发动机5和空气滤清器36的进气通路322的节流阀体,323表示节流阀轴,324表示喷嘴,570表示发动机悬架,558表示排气管。
该发动机5具有经由连杆51连接到曲轴50上的活塞52。活塞52可在设置于缸体53上的气缸54内滑动,缸体53以气缸54的轴线C大致呈水平地配设着。在缸体53的前面固定有缸盖55a和头盖55b,通过缸盖55a、气缸54及活塞52形成燃烧混合气体的燃烧室。此外,如图1所示,在头盖55b的左右设有腿护罩26b。
在缸盖55a上,配设有控制向燃烧室的混合气体的进气或排气的阀门551、552(参照图15)和火花塞56。阀门551、552的开闭通过轴支撑在缸盖55a上的凸轮轴37的旋转控制。凸轮轴37的一端备有从动链轮38,从动链轮38与设在曲轴50一端的驱动链轮40之间悬挂有环状凸轮链条39。另外,在邻接驱动链轮的曲轴50上,通过花键嵌合一体地安装有连接到起动电机33上的起动用从动齿轮41。
曲轴50通过轴承42、42分别支持在左曲轴箱57L与右曲轴箱57R(下面,将左曲轴箱57L与右曲轴箱57R合在一起称作曲轴箱57)上,曲轴箱57宽度方向左侧与定子箱43连接,其内部容纳有所谓外转子形式的电机的交流发电机44(交流发电机ACG)。在曲轴箱57宽度方向右侧,连接有容纳两级离心离合器8的曲轴箱盖80,进一步,曲轴箱盖80的右侧端部通过轴承45与支持曲轴50的离合器盖85连接。在位于缸体53侧方的曲轴箱盖80内的前方空间中连接有电机壳体60。在电机壳体60内部,一体地容纳有在电机输出轴61上安装有电机驱动齿轮62的电机6。
而且,在曲轴50的左侧端部,安装有与构成交流发电机44的内定子441对置的外转子442,其右侧端部上,以花键嵌合有两级离心离合器8的第一离合器内圈81。另外,在曲轴50上,在连杆51和第一离合器内圈81之间,以可与曲轴50相对自由旋转地覆盖其外周的方式,配置有初级驱动齿轮58和外周轴46。
初级驱动齿轮58与安装在下文的动力传递机构7的主轴70上的初级从动齿轮72啮合,同时,在初级驱动齿轮58上,相邻接并一体旋转地安装有直径大于初级驱动齿轮58的电机从动齿轮59。
电机从动齿轮59与电机驱动齿轮62啮合,具有内径部向右侧开口的空间,通过容纳在该空间中的单向离合器47连接到外周轴46上。
该单向离合器47在外周轴46的转速大于电机从动齿轮59的转速时进行连接,将外周轴46的动力传递给电机从动齿轮59,在电机从动齿轮59的转速大于外周轴46的转速时断开,切断动力传递。
两级离心离合器8例如如图4~图7所示,由第一离合器内圈81、第二离合器内圈82、行星齿轮机构83及棘轮式离合机构84构成。如上所述,第一离合器内圈81以花键方式嵌合在曲轴50上,与曲轴50一体地旋转。另一方面,第二离合器内圈82以花键方式嵌合在外周轴46的外周上,与外周轴46一体地旋转。
行星齿轮机构83由太阳轮831、内齿轮832、在太阳轮831与内齿轮832之间啮合的行星齿轮833以及支持行星齿轮833的行星齿轮架834构成。行星齿轮架834与第二离合器内圈82连接,构成一体旋转的结构。
内齿轮832具有作为第一离合器内圈81和第二离合器内圈82的离合器外圈的功能,当第一离合器内圈81的转速达到第一给定转速时,第一离合器内圈81的配重和第二离合器内圈832的内周面处于接触的连接状态,进一步,当第二离合器内圈82的转速达到比第一给定转速快的第二给定转速时,第二离合器内圈82的配重和内齿轮832的内周面处于接触的连接状态。太阳轮831与棘轮式离合机构84连接。
棘轮式离合机构84的构成包括:具有相对外周轴46的外周自由旋转地配置的法兰部840的棘轮支持部件841;通过法兰部840支持的多个棘轮843以及从离合器壳体盖80延伸设置的棘轮支撑部844。行星齿轮机构83的太阳轮831以花键嵌合在棘轮支持部件841的外周上,构成一体旋转的结构。并且,利用来自太阳轮831的动力,使齿轮支持部件841以逆时针方向旋转时,棘轮843与从离合器壳体盖80延伸设置的棘轮支撑部844的槽845卡合,对棘轮支持部件841的旋转进行锁定,相反地,当棘轮支持部件841以顺时针方向旋转时,棘轮843不与棘轮支撑部844的槽845卡合,棘轮支持部件841空转。此外,在各槽845中烧结固定有防震橡胶846。
这样构成的两级离心离合器8在曲轴50没有到达第一给定转速时,使与曲轴50一体旋转的第一离合器内圈81和内齿轮832的内周面处于不连接的非连接状态,不会把曲轴50的动力传递给动力传递机构7。
另一方面,当曲轴50达到第一给定转速时,第一离合器内圈81的配重和内齿轮832的内周面处于接触的连接状态。这时,内齿轮832以顺时针方向旋转,行星齿轮架834通过与内齿轮832啮合的行星齿轮833也以顺时针方向旋转,将逆时针方向的旋转扭矩作用在太阳轮831上。并且,通过与太阳轮831以花键嵌合的棘轮支持部件841,将逆时针方向的旋转扭矩作用在棘轮843上,由于棘轮843与棘轮支撑部844的槽845卡合,所以,将太阳轮831锁定。因此,从曲轴50传递到行星齿轮架834上的动力减速,被传递给与行星齿轮架834一体旋转的外周轴46。并且,外周轴46的转速大于与电机6的电机驱动齿轮62啮合的电机从动齿轮59的转速时,单向离合器47进行连接,将曲轴50的动力传递给与电机从动齿轮59一体旋转的初级驱动齿轮58,进一步,通过与初级驱动齿轮58啮合,经由初级从动齿轮72传递给动力传递机构7。
另一方面,通过电机6的驱动,电机从动齿轮59的转速大于外周轴46的转速时,单向离合器47断开,不会把曲轴50的动力传递给动力传递机构7。
另外,通过第一离合器内圈81的连接,当与行星齿轮架834连接的第二离合器内圈82的转速达到第二给定转速时,第二离合器内圈82的配重和内齿轮832的内周面处于接触的连接状态。这时,通过第二离合器内圈82,内齿轮832与行星齿轮架834一体旋转,并且与太阳轮831成为一体。换句话说,行星齿轮机构83成为一体。这时,通过与太阳轮831以花键嵌合的棘轮支持部件841,将顺时针方向的旋转扭矩作用在棘轮843上,棘轮843不与棘轮支撑部844的槽845卡合,棘轮支持部件841空转。从而,从曲轴50传递给行星齿轮机构83的动力不减速,被传递给与行星齿轮架834一体旋转的外周轴46。接着,当外周轴46的转速大于与电机6的电机驱动齿轮62啮合的电机从动齿轮59的转速时,单向离合器47进行连接,将曲轴50的动力传递给与电机从动齿轮59一体旋转的初级驱动齿轮58,进一步,通过与初级驱动齿轮58啮合,经由初级从动齿轮72传递给动力传递机构7。
另一方面,利用电机6的驱动,在电机从动齿轮59的转速大于外周轴46的转速时,单向离合器47断开,不会把曲轴50的动力传递给动力传递机构7。
电机6如上所述,由安装在电机输出轴61上的电机驱动齿轮62构成,电机驱动齿轮62总是与设在曲轴50周围的电机从动齿轮59啮合。借此,电机6的动力利用电机驱动齿轮62与电机从动齿轮59的啮合传递给电机从动齿轮59,并由与电机从动齿轮59一体旋转的初级驱动齿轮58,通过与初级驱动齿轮58的啮合,经由初级从动齿轮72传递给动力传递机构7。这里,由于电机从动齿轮59通过单向离合器47连接到外周轴46上,所以,只有电机从动齿轮59的转速大于外周轴46的转速时,电机6的动力才传递给动力传递机构7。这时,由于单向离合器47断开,所以,电机6的动力不会传递给外周轴46。另一方面,当外周轴46的转速大于电机从动齿轮59的转速时,由于曲轴50的动力传递给动力传递机构7,所以,电机6与曲轴50连接。这时,可以对应于蓄电池SOC,以电机6为辅助手段,也可以进行再生充电,通过零扭矩的控制,减轻负载。
接着,说明动力传递机构7。
动力传递机构7的构成包括设置在主轴70和中间轴71之间的变速部73,在主轴70的右侧端部,安装有与配设在上述曲轴50的外周上的初级驱动齿轮58啮合的初级从动齿轮72。在中间轴71的左侧端部,安装有驱动链轮74,传递给主轴70的动力,通过卷挂在驱动链轮74上的驱动链条31(参照图1),传递给驱动轮WR。另外,在中间轴71的右侧端部,设有与车速检测用输入齿轮76啮合的车速检测用输出齿轮77,车速检测用输入齿轮76自由旋转地配设在辅助轴75上。另外,在曲轴箱57上,在与车速检测用输入齿轮76对置的位置,设有检测速度的检测部78。
变速部73的构成包括:相对自由旋转地配设在主轴70外周的低速驱动齿轮731;配置在主轴70外周上并与主轴70一体旋转,沿着其轴线自由滑动设置的高速驱动换档齿轮732;以花键嵌合在中间轴71的外周上并与中间轴71一体旋转的低速从动齿轮733;相对自由旋转地配设在中间轴71外周的高速从动齿轮734;以及配置在中间轴71外周上并与中间轴71一体旋转,沿着其轴线自由滑动设置的换档机构735。这里,低速驱动齿轮731与低速从动齿轮733始终啮合,构成低速齿轮对736,高速驱动换挡齿轮732与高速从动齿轮734始终啮合,构成高速齿轮对737。
变速部73通常设定成以使用高速齿轮对737的驱动模式行驶,在需要更大扭矩的情况下,以使用低速齿轮对736的低速模式行驶。从而,通过驾驶员摆动换档踏板(图中未示),从空档向驱动模式、低速模式进行齿轮变换。
在空档下,如图8所示,高速驱动换档齿轮732与低速驱动齿轮731不卡合,而且,换档机构735与高速从动齿轮734也不卡合。因此,例如,即使主轴70旋转,即使通过低速齿轮对736和高速齿轮对737的任意一个,也不给中间轴71传递动力。
此外,驾驶员为了从空档选择驱动模式,将换档踏板(图中未示)向一侧摆动时,如图9所示,换档机构735向高速从动齿轮734侧滑动,使形成于高速从动齿轮734上的卡合部734a与形成于换档机构735上的卡合部735a卡合。借此,将输入给主轴70的动力如图中箭头所示那样,从高速驱动换档齿轮732通过高速齿轮对737、换档机构735传递给中间轴71的驱动链轮74。另外,驾驶员为了返回空档,将换档踏板向另一侧摆动时,换档机构735返回空档位置,解除卡合部734a与卡合部735a的卡合。
另一方面,驾驶员为了从驱动模式选择低速模式,将换档踏板进一步向一侧摆动时,如图10所示,换档机构735返回空档位置,解除卡合部734a与卡合部735a的卡合,而且,高速驱动换档齿轮732向低速驱动齿轮731侧滑动,使形成于低速驱动齿轮731上的卡合部731a与形成于高速驱动换档齿轮732上的卡合部732a卡合。借此,将输入给主轴70的动力通过高速驱动换档齿轮732、低速齿轮对736传递给中间轴71的驱动链轮74。另外,驾驶员为了从低速模式选择驱动模式或返回空档,将换档踏板向一侧或另一侧摆动时,变成上述的驱动模式或空档。
利用这样构成的混合动力车辆的动力单元P,通过以下第一及第二传递路径的两种传递路径传递动力,使两轮摩托车1行驶。
(1)第一传递路径是所谓的发动机行驶中的传递路径,是将发动机5的动力通过曲轴50、两级离心离合器8、外周轴46、单向离合器47、电机从动齿轮59(初级驱动齿轮58)、初级从动齿轮72及动力传递机构7传递给驱动轮WR的传递路径。在该第一传递路径中,在两级离心离合器8与动力传递机构7的变速部73中分别进行两阶段的变速。此外,在第一传递路径中,在一边传递动力一边行驶中,通过驱动电机6,可进行加速行驶(日文:アシスト走行),另外,也可以以电机6作为负载,进行再生充电。
(2)第二传递路径是所谓的EV行驶中的传递路径,将电机6的动力通过电机输出轴61、电机驱动齿轮62、电机从动齿轮59(初级驱动齿轮58)、初级从动齿轮72、动力传递机构7及驱动链条31传递给驱动轮WR的传递路径。这时,如上文所述,电机6的动力通过单向离合器47的空转不会传递给曲轴50。另外,在该第二传递路径中,在动力传递机构7的变速部73中进行两阶段的变速。
该第一及第二传递路径的切换是通过单向离合器47机械地进行的,基于单向离合器47外径侧的电机从动齿轮59的转速与内径侧外周轴46的转速,如果外周轴46的转速大于电机从动齿轮59的转速,就通过第一传递路径传递动力,如果电机从动齿轮59的转速大于外周轴46的转速,就通过第二传递路径传递动力。
这样构成的动力单元P如图2所示,将电机6及两级离心离合器8相对发动机5偏向车体宽度方向一侧而配置,车体中心线O位于发动机5的活塞52的中心与电机6之间。
下面,参照图11~图15,说明本发明的油润滑。在图12、图15中,箭头表示动力单元搭载在车辆上状态的方向。
油泵9如图11所示,包括油泵本体90、隔着油泵本体90设置在油泵轴91上的右侧端部的作为第一输入部的油泵从动齿轮92以及设置在左侧端部的作为第二输入部的油泵从动链轮93。如图12所示,从侧面看配置在电机6的下方且后方,将油供给动力单元P的各部分,例如发动机5及动力传递机构7。
油泵从动齿轮92通过单向离合器94设置在油泵轴91上,始终与将来自发动机5和电机6的动力传递给动力传递机构7的初级驱动齿轮58啮合。单向离合器94在外径侧的油泵从动齿轮92的转速大于内径侧油泵轴91的转速时进行连接,将油泵从动齿轮92的动力传递给油泵轴91,在油泵轴91的转速大于油泵从动齿轮92的转速时断开,切断动力传递。
油泵从动链轮93通过单向离合器95设置在油泵轴91上,与挂在凸轮轴37的从动链轮38和曲轴50的驱动链轮40上的凸轮链条39连接。单向离合器95在外径侧的油泵从动链轮93的转速大于内径侧油泵轴91的转速时进行连接,将油泵从动链轮93的动力传递给油泵轴91,在油泵轴91的转速大于油泵从动链轮93的转速时断开,切断动力传递。
因此,基于设置在油泵轴91端部的油泵从动齿轮92和油泵从动链轮93的旋转差,当油泵从动齿轮92的转速大于油泵从动链轮93的转速时,单向离合器94进行连接,将油泵从动齿轮92的动力通过单向离合器94传递给油泵轴91。这时,由于单向离合器95断开,所以油泵轴91的动力不传递给油泵从动链轮93。另一方面,当油泵从动链轮93的转速大于油泵从动齿轮92的转速时,单向离合器95进行连接,将油泵从动链轮93的动力通过单向离合器95传递给油泵轴91。这时,由于单向离合器94断开,油泵轴91的动力不传递给油泵从动齿轮92。此外,将油泵从动链轮93的这一方设定成比油泵从动齿轮92具有可高旋转的传动比。
这样构成的油泵9,油泵本体90位于支持曲轴50的曲轴箱57和电机从动齿轮59之间,油泵从动齿轮92位于油泵本体90和电机从动齿轮59之间。另外,油泵从动齿轮92在曲轴50的轴线方向上相对气缸54配设在一侧,油泵从动链轮93配设在另一侧。此外,发动机行驶时通过曲轴50的旋转,从油泵从动链轮93输入动力,电机行驶时通过初级驱动齿轮58的旋转,从油泵从动齿轮92输入动力。另外,电机加速行驶时,由作为高旋转侧的油泵从动链轮93传递动力,可对应行驶状态进行适当地润滑。
另外,如图13及图14所示,在动力传递机构7的中间轴71的右侧端部,设有飞沫油回收部件79,该飞沫油回收部件79接受从初级驱动齿轮58或初级从动齿轮72等的齿轮飞出的油,并将飞出的油向中间轴71内所形成的油路710内导引。飞沫油回收部件79通过转动止动部件790不旋转地固定在曲轴箱57上,接受部795朝向初级驱动齿轮58或初级从动齿轮72开口。
另外,如图15所示,在曲轴箱57上,从下面571到前方延伸设置有由动力传递机构7的低速和高速齿轮对736、737构成的指向齿轮系的肋572,曲轴箱57和肋572所形成的空间中储留有车速检测用输入齿轮76的一部分可浸渍的油。因此,通过车速检测用输入齿轮76的旋转,将油供给到动力传递机构7的齿轮系。
如上所述,根据本实施方式的混合动力车辆,油泵9在油泵轴91上设有作为第一输入部的油泵从动齿轮92,油泵从动齿轮92与作为输出部的初级驱动齿轮58连接,初级驱动齿轮58与将电机6的动力传递给变速器7的电机从动齿轮59一体旋转,所以,即使在通过电机6进行EV行驶的情况下,也能驱动油泵9,来润滑发动机5和变速器7。因此,即使在EV行驶时曲轴50停止的状态下,也能润滑发动机5和变速器7。
另外,由于在油泵轴91的一端通过第一单向离合器94设置有利用电机6的动力旋转的油泵从动齿轮92,在油泵轴91的另一端,通过单向离合器95设有与发动机5的凸轮链条39连接并利用发动机5的动力旋转的油泵从动链轮93。因此,可通过发动机5和电机6的任意一方有选择地驱动油泵9,可润滑发动机5和变速器7。
进一步,电机从动齿轮59配置在曲轴50的一侧,凸轮链条39配置在曲轴50的另一侧,所以,可缩小宽度方向的突出,特别是能防止向曲轴50一侧偏置地突出。
另外,由于油泵9随着通过电机6的动力旋转的油泵从动齿轮92和通过发动机5的动力旋转的油泵从动链轮93中的旋转速度快的一方进行旋转,所以,可对应行驶状态进行适当地润滑。
另外,油泵本体90位于支持曲轴50的曲轴箱57和电机从动齿轮59之间,油泵从动齿轮92位于油泵本体90和电机从动齿轮59之间,因此,可将油泵本体90配置在有限的空间中。
另外,由于将油泵从动齿轮92和油泵从动链轮93隔着气缸54配置在相反的对极位置上,所以,可以将所必要的空间在气缸54的左右分配,使油泵9小型化。
另外,由于油泵本体90位于油泵从动齿轮92和油泵从动链轮93之间,因此,可将油泵本体90配置在有限的空间中。
另外,由于将油泵从动链轮93的这一方设定成比油泵从动齿轮92具有可高速旋转的传动比,所以,发动机起动后,可进行通过凸轮链条37驱动油泵9的适当的润滑。
另外,在动力传递机构7的中间轴71的端部,设置有接受来自齿轮的飞沫油的飞沫油回收部件79,容纳在飞沫油回收部件79中的油通过中间轴71内的油路710进行润滑,因此,可有效地回收飞散的油而进行润滑。
另外,由于车速检测用输入齿轮76设置在中间轴71的下方,并设置在能浸入储留在曲轴箱57下面571的油中的位置,从该曲轴箱57朝前方延伸设置的肋572指向动力传递机构7的变速齿轮系,因此,利用车速检测用输入齿轮76的旋转,可有效地对动力传递机构7的变速齿轮系供给润滑油。
此外,本发明并不限定于上述实方式,可进行适当地变更和改进等。
Claims (8)
1.一种混合动力车辆,其特征在于,包括:内燃机;电动机;将所述内燃机与所述电动机的动力传递给被驱动部的动力传递机构;以及随着曲轴的旋转润滑所述内燃机与所述动力传递机构的油泵,
所述油泵在油泵轴的一端,经由第一单向离合器设置有第一输入部,该第一输入部与将所述电动机的动力传递给所述被驱动部的传递部件一体旋转的输出部连接,并通过所述电动机的动力进行旋转,在所述油泵轴的另一端,通过第二单向离合器设置有与所述内燃机的凸轮链条连接并利用所述内燃机的动力旋转的第二输入部,
所述传递部件配置在所述曲轴的一侧,所述凸轮链条配置在所述曲轴的另一侧。
2.根据权利要求1所述的混合动力车辆,其特征在于,所述油泵轴随着通过所述电动机的动力而旋转的所述第一输入部和通过所述内燃机的动力而旋转的所述第二输入部中的旋转速度快的一方进行旋转。
3.根据权利要求1所述的混合动力车辆,其特征在于,油泵本体位于支持所述曲轴的曲轴箱和所述传递部件之间,所述第一输入部位于所述油泵本体和所述传递部件之间。
4.根据权利要求1所述的混合动力车辆,其特征在于,所述第一输入部配置在气缸的一侧,所述第二输入部配置在气缸的另一侧。
5.根据权利要求1所述的混合动力车辆,其特征在于,所述油泵本体位于所述第一输入部和所述第二输入部之间。
6.根据权利要求1所述的混合动力车辆,其特征在于,所述第二输入部比所述第一输入部具有可高旋转的传动比。
7.根据权利要求1所述的混合动力车辆,其特征在于,在所述动力传递机构的中间轴的端部,设置有接受润滑油的飞沫油回收部件,
容纳在所述飞沫油回收部件中的润滑油经由所述中间轴内的油路进行润滑。
8.根据权利要求1所述的混合动力车辆,其特征在于,在所述中间轴的下方设置有车速检测用齿轮,该车速检测用齿轮设置在能浸入储留在曲轴箱下面的润滑油中的位置,
从所述曲轴箱朝前方延伸设置的肋指向所述动力传递机构的变速齿轮系。
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JP2009087778A JP5339606B2 (ja) | 2009-03-31 | 2009-03-31 | ハイブリッド自動二輪車 |
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EP (1) | EP2255987B1 (zh) |
JP (1) | JP5339606B2 (zh) |
KR (1) | KR101055533B1 (zh) |
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US20100243348A1 (en) | 2010-09-30 |
KR20100109378A (ko) | 2010-10-08 |
EP2255987A1 (en) | 2010-12-01 |
JP2010235056A (ja) | 2010-10-21 |
JP5339606B2 (ja) | 2013-11-13 |
ES2575692T3 (es) | 2016-06-30 |
EP2255987B1 (en) | 2016-06-01 |
US8636090B2 (en) | 2014-01-28 |
TW201102287A (en) | 2011-01-16 |
TWI422502B (zh) | 2014-01-11 |
KR101055533B1 (ko) | 2011-08-08 |
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