CN101900192A - 混合动力汽车功率分流能量再生液压机械无级变速器 - Google Patents

混合动力汽车功率分流能量再生液压机械无级变速器 Download PDF

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CN101900192A
CN101900192A CN2010101981092A CN201010198109A CN101900192A CN 101900192 A CN101900192 A CN 101900192A CN 2010101981092 A CN2010101981092 A CN 2010101981092A CN 201010198109 A CN201010198109 A CN 201010198109A CN 101900192 A CN101900192 A CN 101900192A
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motor
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CN101900192B (zh
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陈斌
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Ningbo New & High Xieli Mechanoelectric Hydraulic Co Ltd
NINGBO SURELY MEH CO Ltd
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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
    • 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
    • F16H61/38—Control of exclusively fluid gearing
    • F16H61/40—Control of exclusively fluid gearing hydrostatic
    • F16H61/4078—Fluid exchange between hydrostatic circuits and external sources or consumers
    • F16H61/4096—Fluid exchange between hydrostatic circuits and external sources or consumers with pressure accumulators
    • 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
    • B60K6/08—Prime-movers comprising combustion engines and mechanical or fluid energy storing means
    • B60K6/12—Prime-movers comprising combustion engines and mechanical or fluid energy storing means by means of a chargeable fluidic accumulator
    • 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
    • F16H47/00—Combinations of mechanical gearing with fluid clutches or fluid gearing
    • F16H47/02—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the volumetric type
    • F16H47/04—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the volumetric type the mechanical gearing being of the type with members having orbital motion
    • 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
    • F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
    • F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
    • F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
    • F16H37/08—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
    • F16H37/0833—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths
    • F16H37/084—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths at least one power path being a continuously variable transmission, i.e. CVT
    • F16H2037/088—Power split variators with summing differentials, with the input of the CVT connected or connectable to the input shaft
    • 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
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    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
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    • Y02T10/60—Other road transportation technologies with climate change mitigation effect
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Abstract

一种以多功能行星差动轮系齿轮泵和通轴式液压变量泵(马达)两大基本元件组成的功率分流能量再生液压机械无级变速器，利用行星差动轮系齿轮泵同时具有液压定量泵(马达)和行星轮系分速、汇速两种功能的特性，替换现有液压机械无级变速器中的行星轮系和液压定量泵(马达)两个元件，用通轴式液压变量泵(马达)与行星差动轮系齿轮泵的动力输入轴或动力输出轴同轴连接，构成单轴向布局功率分流液压机械无级变速器。该变速器，不但有无级变速特性，还可在制动时将汽车惯性动能转换为液压势能储存在高压蓄能器中，当汽车起动和加速时，通过工作在油马达状态的行星差动轮系齿轮泵和通轴式液压变量泵将液压势能转换为机械能驱动汽车。

Description

混合动力汽车功率分流能量再生液压机械无极变速器
技术领域
本发明是油液混合动力汽车功率分流能量再生无极变速器，在以多功能行星差动轮系齿轮泵为核心元件组成的功率分流液压机械无极变速器基础上，连接摩擦制动器、液压蓄能器、压力、流量传感器和液压阀控制回路构成，属液压机械混合传动***，具有安全缓冲器、缓冲联轴器、制动能量回收、液压蓄能、动力再生和无极变速传动功能，采用本发明改进的汽车可减小发动机功率20％～40％，回收制动能量80％以上，当传统制动***失灵时，可缓冲制动停车同时回收惯性动能，以液压静压势能形式储存在蓄能器中，提供起步和加速时所需能量。特别适合起停频繁的城市公交和主要行驶在城市道路的各类汽车使用。
背景技术
现已公开的功率分流液压机械无极变速器，由液压定量泵(马达)、液压变量泵(马达)、行星轮系三大基本元件组成，不但体积大、效率低、重量重、噪声大、而且功能单一、安装困难，难以商品化应用。如美国Sundstrand公司采用液压定量泵(马达)、液压变量泵(马达)、行星轮系三大基本元件，和两个多片摩擦离合器四对齿轮组成DMT25双轴平行功率分流液压机械无极变速器，由于体积大、重量重、功能单一、安装困难最终停产。
发明内容
现有功率分流液压机械无极变速器必须由液压定量泵(马达)、液压变量泵(马达)、行星轮系三大基本元件组成，因此体积大、效率低、重量重、功能单一、噪声大、安装困难，为解决这一技术难题，本发明提供一种以多功能行星差动轮系齿轮泵和通轴式液压变量泵(马达)两大基本元件为核心，连接摩擦制动器、液压蓄能器、压力、流量传感器和液压阀控制回路构成的功率分流能量再生液压机械无极变速器。
本发明解决现有功率分流液压机械无极变速器体积大、效率低、重量重、功能单一、噪声大、安装困难诸多技术难题所采取的技术方案是：利用本公司已获授权专利《油液混合动力汽车多功能驱动元件》专利号ZL.200920168053.9、本次申请中名称为行星差动轮系齿轮泵同时具有液压定量泵(马达)和行星轮系分速、汇速两大功能的特性，替换现有组成功率分流液压机械无极变速器中的行星轮系和液压定量泵(马达)两个元件，采用通轴式液压变量泵(马达)替换传统结构变量泵(马达)，并将通轴式液压变量泵(马达)轴与行星差动轮系齿轮泵的动力输入轴或动力输出轴同轴连接，构成单轴向布局汇速型或分速型功率分流能量再生液压机械无极变速器。由此构成的变速器，不但有无级变速特性，还可在减速和制动时将汽车惯性动能转换为液压势能储存在高压蓄能器中，当汽车起动和加速时，利用高压蓄能器储存的液压势能，通过工作在油马达状态的行星差动轮系齿轮泵和通轴式液压变量泵转换为机械能驱动汽车，经济巡航时，无极变速器还可根据不同时速自动调解发动机转速，寻找最佳工作区域。
采用本发明改进现有汽车传动***，传动件功率密度大，能量转换、蓄能、再生效率高，不但能通过减小发动机排量，提高发动机工作效率方法节省油耗，还可最大程度回收、储存、再生制动能量，回收、再生总效率可达70％，是油电混合动力方案的四倍，当传统制动***失灵时，可通过制动能量回收功能缓冲制动停车，同时回收惯性动能，以液压静压势能形式储存在蓄能器中，提供起步和加速时所需能量。对长时间行驶在城市道路的车辆，节能减排效果尤为突出，采用本发明改进城市公交车，可节油30％，每辆车每年节油10吨多，按目前燃油价格计算每辆车每年节省7万多元燃油费，减少CO2排放20多吨，经济效益和社会效益尤其突出。
附图说明
图1是本发明(分速型)液压机械无极变速器基本单元的轴向局部剖视示意图，图中1.动力输出轴，2.通轴式液压变量泵(马达)，3.通轴式液压变量泵(马达)进油口，4.通轴式液压变量泵(马达)出油口，5.螺栓，6.行星差动轮系齿轮泵，7.行星差动轮系齿轮泵进油口，8.行星差动轮系齿轮泵出油口，9.摩擦制动器，10.动力输入轴。
图2是本发明(分速型)液压机械无极变速器基本单元工作原理图。
图3是本发明(汇速型)液压机械无极变速器基本单元的轴向局部剖视示意图。
图4是本发明油液混合动力汽车功率分流能量再生(分速型)液压机械无极变速器工作原理图，图中11.低压蓄能器，12.液压控制阀块，13.速度传感器，14.高压蓄能器，15.压力传感器。
具体实施方式
图1中行星差动轮系齿轮泵(6)的输出轴同轴联接通轴式液压变量泵(2)的动力输出轴(1)，用螺栓(5)紧固两元件，由两个功能元件组成功率分流(分速形)液压机械无极变速器基本单元。通轴式液压变量泵(马达)(2)动力输出轴(1)与动力输入轴是同一轴，行星差动轮系齿轮泵(6)的行星轮系三大运动元件中心太阳轮、行星架、内齿圈的任何一件为动力输入轴(10)，其余两件中任何一件与通轴式液压变量泵(马达)(2)动力输出轴(1)轴相联接，这种联接方式轮流变换共有6种变化型式，由于行星差动轮系齿轮泵(6)的三大运动元件都没有与泵壳固定，所以行星差动轮系齿轮泵(6)的输出扭矩等于输入扭矩，行星轮系齿轮泵(6)的作用有两个，一是将动力输入轴(10)的机械扭矩传递给动力输出轴(1)，二是将部分机械能转变为液压流体静压能，输送给通轴式液压变量泵(马达)(2)，由通轴式液压变量泵(马达)(2)将液压流体静压能转变为旋转机械扭矩与输入扭矩叠加在动力输出轴(1)，动力输出轴(1)与动力输入轴(10)的转速差决定行星差动轮系齿轮泵(6)的液压输出流量，转速差越大，输出流量越大，加大通轴式液压变量泵(2)的排量，输出扭矩加大，行星差动轮系齿轮泵(6)输出的液压流量加大，动力输出轴(1)转速降低。
图3所示实施例行中，行星差动轮系齿轮泵(6)的输入轴同轴联接通轴式液压变量泵(2)的动力输出轴，用螺栓(5)紧固两元件，由两个功能元件组成功率分流能量再生(汇速型)液压机械无极变速器基本单元。
图4中点划线框内是分速型液压机械无极变速器基本单元，摩擦制动器(9)静止部分与泵壳固定，运动部分与动力输入轴(10)固定，通轴式液压变量泵(马达)进油口(3)、通轴式液压变量泵(马达)出油口(4)、行星差动轮系齿轮泵进油口(7)两个、行星差动轮系齿轮泵出油口(8)两个、低压蓄能器(11)、高压蓄能器(14)都接入液压控制阀块(12)，压力传感器(15)接在高压蓄能器(14)的进出油口，检测高压蓄能器(14)压力，速度传感器(13)接在动力输出轴(1)处，检测动力输出轴(1)转速，汽车及其它形式负载制动减速时，摩擦制动器(9)贴合制动，低压蓄能器(11)通过液压控制阀块(12)接通行星差动轮系齿轮泵(6)和通轴式液压变量泵(马达)(2)的实际工作进油口，高压蓄能器(14)通过液压控制阀块(12)接通行星差动轮系齿轮泵(6)和通轴式液压变量泵(马达)(2)的实际工作出油口，行星差动轮系齿轮泵(6)和通轴式液压变量泵(马达)(2)工作在泵状态，将低压蓄能器(11)中的液压油泵入高压蓄能器(14)把负载的惯性动能转换为液压势能储存。汽车起动时，摩擦制动器(9)贴合制动，高压蓄能器(11)通过液压控制阀块(12)接通行星差动轮系齿轮泵(6)和通轴式液压变量泵(马达)(2)的实际工作进油口，行星差动轮系齿轮泵(6)和通轴式液压变量泵(马达)(2)工作在马达状态，高压蓄能器(11)释放液压能，行星差动轮系齿轮泵(6)和通轴式液压变量泵(马达)(2)将液压能转换为机械扭矩输出，驱动汽车，低压蓄能器(14)通过液压控制阀块(12)接通行星差动轮系齿轮泵(6)和通轴式液压变量泵(马达)(2)的实际工作出油口，储存液压油。

Claims (3)

1.一种油液混合动力汽车功率分流能量再生无极变速器，行星差动轮系齿轮泵(6)的三大运动元件中心太阳轮、行星架、内齿圈的任何一件为动力输入轴(10)，其余2件中任何一件与通轴式液压变量泵(马达)(2)动力输出轴(1)轴相联接，通轴式液压变量泵(马达)(2)动力输出轴(1)与动力输入轴是同一轴，这种联接方式轮流变换共有6种变化型式，行星差动轮系齿轮泵(6)的三大运动元件心太阳轮、行星架、内齿圈都没有与泵壳固定，行星差动轮系齿轮泵(6)的输出扭矩等于输入扭矩，行星轮系齿轮泵(6)的作用有两个，一是将动力输入轴(10)的机械扭矩传递给动力输出轴(1)，二是将部分机械能转变为液压流体静压能，通过液压控制阀块(12)输送给通轴式液压变量泵(马达)(2)，由通轴式液压变量泵(马达)(2)将液压流体静压能转变为旋转机械扭矩与输入扭矩叠加在动力输出轴(1)，摩擦制动器(9)静止部分与泵壳固定，运动部分与动力输入轴(10)固定，通轴式液压变量泵(马达)进油口(3)、通轴式液压变量泵(马达)出油口(4)、行星差动轮系齿轮泵进油口(7)两个、行星差动轮系齿轮泵出油口(8)两个、低压蓄能器(11)、高压蓄能器(14)都接入液压控制阀块(12)，压力传感器(15)接在高压蓄能器(14)的进出油口，检测高压蓄能器(14)压力，速度传感器(13)接在动力输出轴(1)处，检测动力输出轴(1)转速，其特征是：在行星差动轮系齿轮泵(6)的输出端同轴联接通轴式液压变量泵(2)的动力输入轴，由这两个功能元件组成具有机械、液压功率分流功能的分速型液压机械无极变速器基本单元。
2.根据权利要求1所述的油液混合动力汽车功率分流能量再生无极变速器，其特征是：在行星差动轮系齿轮泵(6)的输入端同轴联接通轴式液压变量泵(2)的动力输出轴，由这两个功能元件组成具有机械、液压功率分流功能的汇速型液压机械无极变速器基本单元。
3.根据权利要求1所述的油液混合动力汽车功率分流能量再生无极变速器，其特征是：汽车及其它形式负载减速及制动时，摩擦制动器(9)贴合制动，低压蓄能器(11)通过液压控制阀块(12)接通行星差动轮系齿轮泵(6)和通轴式液压变量泵(马达)(2)的实际工作进油口，高压蓄能器(14)通过液压控制阀块(12)接通行星差动轮系齿轮泵(6)和通轴式液压变量泵(马达)(2)的实际工作出油口，行星差动轮系齿轮泵(6)和通轴式液压变量泵(马达)(2)工作在泵状态，将低压蓄能器(11)中的液压油泵入高压蓄能器(14)，回收负载的惯性动能，并转换为液压势能储存，汽车起动时，摩擦制动器(9)贴合制动，高压蓄能器(11)通过液压控制阀块(12)接通行星差动轮系齿轮泵(6)和通轴式液压变量泵(马达)(2)的实际工作进油口，行星差动轮系齿轮泵(6)和通轴式液压变量泵(马达)(2)工作在马达状态，高压蓄能器(11)释放液压能，行星差动轮系齿轮泵(6)和通轴式液压变量泵(马达)(2)将液压能转换为机械扭矩输出，低压蓄能器(14)通过液压控制阀块(12)接通行星差动轮系齿轮泵(6)和通轴式液压变量泵(马达)(2)的实际工作出油口，储存液压油。
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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN106051108A (zh) * 2016-05-04 2016-10-26 陈金祥 一种可变量齿轮泵式汽车无级变速器
CN106895140A (zh) * 2015-12-17 2017-06-27 Zf腓德烈斯哈芬股份公司 运行有带次级联接部分流无级传动装置车辆传动系的方法
CN107407405A (zh) * 2015-03-20 2017-11-28 日产自动车株式会社 车辆的再生变速控制装置

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2995014B1 (fr) * 2012-09-06 2014-09-12 Peugeot Citroen Automobiles Sa Dispositif de thermomanagement d'un groupe motopropulseur d'un vehicule automobile hybride hydraulique
FR2995012B1 (fr) * 2012-09-06 2014-09-12 Peugeot Citroen Automobiles Sa Dispositif de thermomanagement d'un groupe motopropulseur d'un vehicule automobile hybride hydraulique
CN105605183B (zh) * 2016-03-08 2018-04-17 南京农业大学 一种用于大马力拖拉机的机液协驱无级变速箱

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN1363479A (zh) * 2001-10-31 2002-08-14 南京理工大学 车轮独立驱动制动与回收制动能量的电控液驱车辆
CN1379186A (zh) * 2002-05-17 2002-11-13 浙江大学 定流网络二次调节液压***
CN2559811Y (zh) * 2002-08-12 2003-07-09 大庆石油管理局 液力驱动无级调速双作用升压泵
JP2004176921A (ja) * 2002-11-25 2004-06-24 General Motors Corp <Gm> 無段変速機用のベルト比率制御システム
US20040177610A1 (en) * 2003-03-11 2004-09-16 Hendrickson Barry M. Broad range speed control for hydraulic motors
CN101067447A (zh) * 2007-06-11 2007-11-07 赵宏坚 机械－液压复合传动机构和机械－液力复合传动机构

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102005060990A1 (de) * 2005-12-20 2007-06-28 Bosch Rexroth Aktiengesellschaft Antrieb und hydrostatische Kolbenmaschine mit Rückgewinnung von Bremsenergie
US20090036248A1 (en) * 2006-03-13 2009-02-05 Bosch Rexroth Ag Drive with a torque split transmission
US8454469B2 (en) * 2006-09-12 2013-06-04 Purdue Research Foundation Power split transmission with energy recovery
US7744499B2 (en) * 2007-01-22 2010-06-29 Southwest Research Institute Hydro-mechanical transmission

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN1363479A (zh) * 2001-10-31 2002-08-14 南京理工大学 车轮独立驱动制动与回收制动能量的电控液驱车辆
CN1379186A (zh) * 2002-05-17 2002-11-13 浙江大学 定流网络二次调节液压***
CN2559811Y (zh) * 2002-08-12 2003-07-09 大庆石油管理局 液力驱动无级调速双作用升压泵
JP2004176921A (ja) * 2002-11-25 2004-06-24 General Motors Corp <Gm> 無段変速機用のベルト比率制御システム
US20040177610A1 (en) * 2003-03-11 2004-09-16 Hendrickson Barry M. Broad range speed control for hydraulic motors
CN101067447A (zh) * 2007-06-11 2007-11-07 赵宏坚 机械－液压复合传动机构和机械－液力复合传动机构

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107407405A (zh) * 2015-03-20 2017-11-28 日产自动车株式会社 车辆的再生变速控制装置
US10253876B2 (en) 2015-03-20 2019-04-09 Nissan Motor Co., Ltd. Vehicle regenerative speed control device
CN107407405B (zh) * 2015-03-20 2019-04-19 日产自动车株式会社 车辆的再生变速控制装置
CN106895140A (zh) * 2015-12-17 2017-06-27 Zf腓德烈斯哈芬股份公司 运行有带次级联接部分流无级传动装置车辆传动系的方法
CN106895140B (zh) * 2015-12-17 2020-03-03 Zf腓德烈斯哈芬股份公司 运行有带次级联接部分流无级传动装置车辆传动系的方法
CN106051108A (zh) * 2016-05-04 2016-10-26 陈金祥 一种可变量齿轮泵式汽车无级变速器

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