CN101992679A - 双行星排四轴混合动力传动装置 - Google Patents

双行星排四轴混合动力传动装置 Download PDF

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Publication number
CN101992679A
CN101992679A CN2009101944705A CN200910194470A CN101992679A CN 101992679 A CN101992679 A CN 101992679A CN 2009101944705 A CN2009101944705 A CN 2009101944705A CN 200910194470 A CN200910194470 A CN 200910194470A CN 101992679 A CN101992679 A CN 101992679A
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China
Prior art keywords
motor
gear
planet
double planetary
planetary row
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Granted
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CN2009101944705A
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CN101992679B (zh
Inventor
李书福
杨健
张彤
余卫
马智涛
于海生
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Jiangxi Dingsheng New Material Technology Co ltd
Original Assignee
SHANGHAI HUAPU GUORUN AUTO CO Ltd
Zhejiang Geely Holding Group Co Ltd
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Application filed by SHANGHAI HUAPU GUORUN AUTO CO Ltd, Zhejiang Geely Holding Group Co Ltd filed Critical SHANGHAI HUAPU GUORUN AUTO CO Ltd
Priority to CN2009101944705A priority Critical patent/CN101992679B/zh
Priority to EP10811107.1A priority patent/EP2472144B1/en
Priority to JP2012525853A priority patent/JP5784606B2/ja
Priority to KR1020127004909A priority patent/KR101700676B1/ko
Priority to PCT/CN2010/001283 priority patent/WO2011022940A1/zh
Publication of CN101992679A publication Critical patent/CN101992679A/zh
Priority to US13/399,197 priority patent/US8382624B2/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/72—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with a secondary drive, e.g. regulating motor, in order to vary speed continuously
    • F16H3/727—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with a secondary drive, e.g. regulating motor, in order to vary speed continuously with at least two dynamo electric machines for creating an electric power path inside the gearing, e.g. using generator and motor for a variable power torque path
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
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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
    • 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
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    • B60K6/50—Architecture of the driveline characterised by arrangement or kind of transmission units
    • B60K6/54—Transmission for changing ratio
    • B60K6/547—Transmission for changing ratio the transmission being a stepped gearing
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    • B60L15/00—Methods, circuits, or devices for controlling the traction-motor speed of electrically-propelled vehicles
    • B60L15/20—Methods, circuits, or devices for controlling the traction-motor speed of electrically-propelled vehicles for control of the vehicle or its driving motor to achieve a desired performance, e.g. speed, torque, programmed variation of speed
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    • B60L3/0061—Detecting, eliminating, remedying or compensating for drive train abnormalities, e.g. failures within the drive train relating to electrical machines
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    • B60L50/10—Electric propulsion with power supplied within the vehicle using propulsion power supplied by engine-driven generators, e.g. generators driven by combustion engines
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    • F16H3/727—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with a secondary drive, e.g. regulating motor, in order to vary speed continuously with at least two dynamo electric machines for creating an electric power path inside the gearing, e.g. using generator and motor for a variable power torque path
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Abstract

本发明公开了一种双行星排四轴混合动力传动装置，包括一个拉威挪式行星齿轮传动机构改进而来的双行星排、设于其左侧的发动机、设于其右侧主要起发电作用的电机A和主要起驱动作用的电机B以及由齿轮传动的主减速器，此外还设有可锁止发动机的第一锁止离合器以及可锁止电机A的第二锁止离合器，电机A与双行星排的小太阳轮连接，电机B则与大太阳轮连接。本发明通过改变与电机B连接的行星轮系的传动比，降低了系统对电机的设计和制造要求，电机集成后简化了冷却系统的结构和控制，电机A增加锁止功能，避免了在零转速附近的低效工作状态。本发明适用于机电混合动力汽车的混合动力耦合与传输。

Description

双行星排四轴混合动力传动装置
技术领域
本发明涉及一种汽车动力传动装置，尤其是一种用于混合动力汽车的双行星排四轴混合动力传动装置。
背景技术
由于能源短缺以及公众环保意识的增强，环保的电动汽车或燃料电池汽车便应运而生，然而由于技术的制约，上述类型的汽车还难以在短时间内全面推广，因此，技术上比较成熟的混合动力汽车是目前比较理想的一种选择。
混合动力汽车(HEV)作为一种新兴的节能环保型汽车，其技术和市场处于一种蓬勃的发展阶段，混合动力汽车(HEV)与传统汽车及纯电动汽车相比，最大差别是动力系统。对于并联和混联式HEV，动力耦合系统负责将HEV的多个动力组合在一起，实现多动力源间合理的功率分配并把动力传给驱动桥，它在HEV开发中处于重要地位，其性能直接关系到HEV整车性能是否达到设计要求，是HEV最核心部分。行星轮系具有多自由度、输入输出灵活可控的特点，而且结构紧凑、体积小、速比大、因此被越来越多的混合动力汽车动力耦合系统所采用，这也是当今混合动力汽车动力总成发展的一种趋势。
1997年丰田推出首款混合动力汽车Prius，2005年又推出了搭载最新第3代机电混合动力系统的2006款Prius，仍采用THS混联式结构，行星齿轮系统对发动机的输出功率进行重新分配，达到合理平衡发动机负荷的目的。附图1所示即为丰田Prius混合动力轿车的动力传动装置结构原理图，包括发动机E、电机AMG1、电机BMG2以及包括一个单行星排的动力耦合系统等部件，在此机构中，发动机E通过减震阻尼器与单行星排的行星架a相连，并通过行星齿轮b将动力传递给外齿圈c和太阳轮d，外齿圈c与输出轴相连，输出轴通过减速齿轮组e和电机MG2的转子相连，太阳轮d与电机MG1的转子相连，输出轴通过链传动系统f、主减速器g以及差速器h将动力传递给车轮。该系统将发动机E大部分转矩直接传递到输出轴上，将小部分转矩传给电机AMG1以用于发电，电机AMG1发出的电能根据指令用于电池充电或驱动电机BMG2，以增加驱动力。这种结构可以通过调节电机AMG1的转矩和转速使发动机一直处于高效率区或低排放区，此外，通过调节行星排各元件的转速，使其像无级变速器一样工作。
然而，由于上述动力传动装置的两个电机MG1、MG2布置在单行星排的两侧，并共用一套冷却系统，因此电机冷却系统布置复杂，电机系统集成度低，并且行星排两侧的传动轴不等长，不利于前舱布置。此外，电机AMG1和发动机E并排布置于行星排同侧，由于两者距离比较近，并且电机AMG1的最佳工作温度为60℃，而发动机E的最佳工作温度为90℃，因此电机AMG1会受到发动机E散热的影响而快速升温，使相应的电机冷却系统经常处于工作状态，进而影响整车的效率。
由于上述动力传动装置采用单排行星轮系，其减速比低，从而要求电机的转速变化范围宽，对转矩的要求高，所以，对电机的制造精度、转速/扭矩特性及其动平衡要求十分苛刻；为了达到足够的减速比，输出轴的减速装置采用了包括链传动系统f、主减速器g的多级传动部件，进一步加大了系统的复杂性，提高了系统对空间布置的要求。
中国专利文献上公开的一种公开号为CN 101149094A的基于双行星排的混合动力驱动装置，包括内燃机、电机、动力输出端以及前、后行星排，前行星排的行星架与后行星排的齿圈相连接，前后行星排的太阳轮共同连接到电机轴上，发动机通过离合器可选择地与前行星排的齿圈或行星架连接，后行星排的行星架与输出端连接。由于其前、后行星排为并排布置，因此其外形尺寸较大，结构不够紧凑；由于只有二个输入轴和一个电机，因此，对电机的控制要求比较高。
发明内容
本发明是为了克服现有技术的混合动力传动装置存在的行星轮系减速比低、结构不紧凑、对电机的要求高、电机的集成度低以及冷却系统复杂的不足，提供一种结构紧凑、传动效率高、对电机的转矩等特性要求低并且其冷却系统简单易控制的双行星排四轴混合动力传动装置。
为了实现上述目的，本发明采用以下技术方案：一种双行星排四轴混合动力传动装置，包括发动机、电机A、电机B以及一个主减速器，所述传动装置设有由第一行星排和第二行星排集成为一体的双行星排，第一行星排包括小太阳轮、行星架、短行星轮以及外齿圈，第二行星排包括大太阳轮、长行星轮以及和第一行星排共用的行星架、短行星轮和外齿圈，所述长行星轮分别与短行星轮和大太阳轮啮合，发动机曲轴与行星架连接，外齿圈通过主减速器输出动力，小太阳轮的转轴与电机A转子相连接，小太阳轮转轴的延伸段连接一个第二锁止离合器，可转动地套设在小太阳轮转轴外的大太阳轮的转轴与电机B转子相连接，所述行星架设有第一锁止离合器。
本发明的电机A主要起发电作用，而电机B则主要起驱动作用，所采用的双行星排传动系统是从拉威挪(Ravigneaux)式齿轮变速机构改进而来，由于是三个输入轴和一个输出轴的四轴系统，因此，比一般的单行星排三轴传动系统有更多的控制模式，有利于通过对电机A和电机B的转矩控制使发动机始终处于其高效率或低排放的最佳工作状态，提高系统的传动效率，降低排放，节省能源；与现有的拉威挪(Ravigneaux)式齿轮变速机构相比，本发明减小了电机B所连接的行星轮系传动比，因而可减小对电机B的转速和转矩的要求，从而有效地降低了电机B的加工制造难度和生产成本。此外，由于采用双行星排传动机构增大了系统的减速比，从而简化了主减速器的结构，而两个行星排集成为一体，大大简化了结构，可显著缩小其外形尺寸，有利于空间布置。
由于本发明采用了改进的拉威挪(Ravigneaux)式齿轮变速机构，因此，分别与小太阳轮、太阳轮连接的电机A和电机B可设于双行星排远离发动机曲轴的一侧，从而可避免发动机的散热对电机A和电机B的影响，有利于电机A和电机B的集成，有效简化电机冷却系统的结构和控制，并提高传动装置的效率，同时还可使行星排两侧的传动轴长度接近，有利于前舱的布置。
当汽车在高速行驶时，电机A的转速需控制在零转速附近以调节发动机的功率输出，因而电机A的效率很低，并且系统的输出功率与功率需求总是会有一些波动，并存在一定的滞后性，这都增加了控制的难度，本发明通过设于电机A转轴的第二锁止离合器将电机A锁止，从而避免了电机A工作在零转速附近，显著地提高整车的传动效率。
本发明的传动装置在处于纯电驱动模式时，设于行星架上的第一锁止离合器将行星架连同与其连接的发动机曲轴一并锁止，因而可避免发动机曲轴的倒转，同时降低纯电驱动时系统控制的复杂度。
作为优选，所述电机A和电机B集成为一体，既可简化其冷却系统的结构，有方便对冷却系统的控制，同时有利于提高电机A以及电机B的可靠性和稳定性。
作为优选，所述短行星轮与长行星轮的个数为3个～4个，并在圆周方向等分排列，从而有利于整个行星排的受力均匀。
作为优选，所述主减速器是一个齿轮组传动机构，从而使整个传动装置的结构更为紧凑。
因此，本发明具有如下有益效果：(1)采用改进的拉威挪(Ravigneaux)式行星齿轮传动机构，降低了系统对电机B的设计和制造要求；(2)通过对两个电机的控制使发动机始终工作在最佳工作区域，提高传动效率，降低排放；(3)通过离合器锁止电机A，避免其在零转速附近工作，提高系统的效率；(4)在纯电驱动模式下，通过锁止离合器锁止发动机，可避免发动机的倒转，简化系统的控制；(5)两个电机设于行星排远离发动机的一侧，并集成为一体，避免发动机的散热对电机的影响，简化电机冷却系统的结构和控制，提高系统的效率。
附图说明
图1是丰田Prius混合动力传动装置的结构原理图；
图2是本发明的结构原理图。
图中标号说明：
1-发动机            2-电机A        3-电机B       4-主减速器
5-双行星排          6-小太阳轮     7-行星架      8-短行星轮
9-外齿圈            10-大太阳轮    11-长行星轮   12-曲轴
13-第一锁止离合器   14--第二锁止离合器           15-减震阻尼器
16-差速器齿轮       17-主减速齿轮                18-主减速输入齿轮
19-主减速输出齿轮   20-壳体                      21-差速器
具体实施方式
下面结合附图对本发明做进一步的描述。
在图2所示的实施例中，本发明的双行星排四轴混合动力传动装置包括壳体20、发动机1、电机A2、电机B3、第一锁止离合器13、第二锁止离合器14、主减速器4以及设于发动机右边的一个由拉威挪行星齿轮机构改进而来的双行星排5，双行星排5中的第一行星排包括小太阳轮6、行星架7、设于行星架7上的短行星轮8以及外齿圈9，短行星轮8分别与小太阳轮6以及外齿圈9啮合，为了受力平衡，短行星轮8设置3个，并在圆周方向等分布置，发动机的曲轴12通过一个减震阻尼器15与行星架7相连接，外齿圈9通过由齿轮组构成的主减速器4与差速器齿轮16相连接，所属主减速器4包括设于外齿圈9和减震阻尼器15之间与外齿圈9相连接的主减速齿轮17、设于主减速齿轮17旁侧并与其啮合的主减速输入齿轮18、与主减速输入齿轮18同轴相连接的主减速输出齿轮19，主减速输出齿轮19与差速器齿轮16啮合输出动力，第一行星排的小太阳轮转轴与设于双行星排5右侧的电机A转子相连接，转轴的延伸段与第二锁止离合器14的一边相连接，第二锁止离合器14的另一边与传动装置的壳体20相连接；双行星排5中的第二行星排包括一个可转动地套设在小太阳轮6的转轴外的大太阳轮10、同样设于第一行星排的行星架7上的长行星轮11，所述长行星轮11除了与大太阳轮10啮合外还与短行星轮8啮合，但不与外齿圈9啮合，与短行星轮8相同，长行星轮11也设置3个并在圆周方向等分布置，大太阳轮10的转轴与设于电机A2和双行星排5之间的电机B3的转子相连接，行星架7上用于安装短行星轮8的短行星轮轴在其右侧延伸端与第一锁止离合器13的一边相连接，第一锁止离合器13的另一边则固定在传动装置的壳体20上，当第一锁止离合器13锁止行星架7时，与其相连接的发动机1即被锁止；同设于双行星排5右侧的电机A 2和电机B 3集成为一体，并共用一套冷却系统，既方便其加工制造，又便于冷却系统的控制。
由于本发明的传动装置采用双行星排机构，因此可实现无级变速，发动机1、电机B 3以及电机A 2三个输入的转矩耦合后传递到输出端，并通过主减速器4传递到差速器21，最终传递到车轮，因此，在实际使用时，上述三个输入端的不同工作模式和状态的组合可以产生多种不同的输出模式。下面就汽车在起步、前进、倒档和驻车四种模式下其输入端典型的工作状态以及相应的动力传递路线做一描述：
1.起步：本发明采用电启动，为了防止发动机1倒转，用第一锁止离合器13锁止发动机1，电机B 3处于驱动状态，其转矩通过大太阳轮10、长行星轮11、短行星轮8、外齿圈9、主减速器4、差速器21传递到车轮，短行星轮8同时带动小太阳轮6空转。另外，当蓄电池的电量不足时，可采用机电混合模式，用第二锁止离合器14锁止电机A 2而放开第一锁止离合器13，此时，电机B 3的转矩通过大太阳轮10、长行星轮11、短行星轮8、外齿圈9、主减速器4、差速器21传递到车轮，而短行星轮同时带动行星架7转动，并通过减震阻尼器17启动发动机1。
2.前进：如果起步时采用纯电驱动模式，发动机1被第一锁止离合器13锁止，则可通过改变电机B 3的转矩和转速改变输出端的转速；如果采用机电混合模式，发动机1被启动，则可松开第二锁止离合器14，并使电机A2处于发电状态，通过调整电机A 2和电机B 3的转矩，使输出端逐渐加速，并将一部分发动机1的转矩通过小太阳轮6传递给电机A 2发电，以用于蓄电池的充电，从而使发动机1能处于理想的工作区域，提高传动效率；当汽车在机电混合模式下处于高速行驶状态时，可用第二锁止离合器14锁止电机A 2，从而保证发动机全部的转矩传递到输出端，以提高传动效率，此时的电机B 3则可作为辅助动力，从而确保发动机1始终处于最佳工作状态，以节省能源。
3.倒档：采用第一锁止离合器13锁止发动机1，改变电机B 3的转向，即可实现汽车的倒档，从而方便电机B 3的控制。
4.驻车：当汽车处于驻车状态时，汽车的停车锁止装置将输出端锁止，因此，此时的外齿圈9处于锁止状态，而电机A 2和电机B 3均处于发电状态，发动机1的转矩通过行星架7分别传递到电机A 2和电机B 3发电并用于蓄电池的充电。
当汽车在下坡时，汽车的惯性通过差速器21、主减速器4传递到外齿圈9，此时的外齿圈9成为动力输入端，其转矩反馈给电机A 2、电机B 3用于发电并用于蓄电池的充电，以节省能源。
以上所列只是本发明的常用工作模式的一些组合方式，本发明采用双行星排四轴传动机构结合两个锁止离合器A、B，使其在相同的工作原理下输入轴可有多种工作模式与状态的组合方式，任何基于本发明的技术所衍生的工作模式和控制方式都没有脱离本发明的精神范畴。

Claims (5)

1.一种双行星排四轴混合动力传动装置，包括发动机(1)、电机A(2)、电机B(3)以及一个主减速器(4)，其特征是，所述传动装置设有由第一行星排和第二行星排集成为一体的双行星排(5)，第一行星排包括小太阳轮(6)、行星架(7)、短行星轮(8)以及外齿圈(9)，第二行星排包括大太阳轮(10)、长行星轮(11)以及和第一行星排共用的行星架(7)、短行星轮(8)和外齿圈(9)，所述长行星轮(11)分别与短行星轮(8)和大太阳轮(10)啮合，发动机曲轴(12)与行星架(7)连接，外齿圈(9)通过主减速器(4)输出动力，小太阳轮(6)的转轴与电机A的转子相连接，小太阳轮转轴的延伸段连接一个第二锁止离合器(14)，可转动地套设在小太阳轮转轴外的大太阳轮(10)的转轴与电机B转子相连接，所述行星架(7)设有第一锁止离合器(13)。
2.根据权利要求1所述的双行星排四轴混合动力传动装置，其特征是，所述电机A(2)和电机B(3)集成为一体。
3.根据权利要求1或2所述的双行星排四轴混合动力传动装置，其特征是，所述短行星轮(8)与长行星轮(11)的个数为3个～4个，并在圆周方向等分排列。
4.根据权利要求1或2所述的双行星排四轴混合动力传动装置，其特征是，所述主减速器(4)是一个齿轮组传动机构。
5.根据权利要求3所述的双行星排四轴混合动力传动装置，其特征是，所述主减速器(4)是一个齿轮组传动机构。
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