CN107642582A - 用于混合动力车辆的变速器 - Google Patents
用于混合动力车辆的变速器 Download PDFInfo
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- CN107642582A CN107642582A CN201611011851.1A CN201611011851A CN107642582A CN 107642582 A CN107642582 A CN 107642582A CN 201611011851 A CN201611011851 A CN 201611011851A CN 107642582 A CN107642582 A CN 107642582A
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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
- B60K6/50—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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- 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
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- 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
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- 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
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Abstract
本发明涉及一种用于混合电动车辆的变速器,该变速器可以包括:第一输入轴,其持续地接收来自发动机的动力;第二输入轴,其经由离合器而选择性地接收来自发动机的动力;中间轴,其联接至第一输入轴;输出轴,其联接至第二输入轴;第一单向离合器,其设置在沿着动力从发动机传递至输出轴的路径上;电机输入轴,其接收来自电机的动力;电机侧换挡单元,其包括具有不同传动比的多个齿轮对,其中,利用接合/断开器来选择多个齿轮对中的能够适合于行驶速度的一个齿轮对;以及第二单向离合器,其设置在沿着动力从电机传递至输出轴的路径上。
Description
技术领域
本发明涉及一种用于混合动力车辆的变速器,该变速器通过在发动机的低效率的驱动范围内操作电机,来改善混合动力车辆的燃料效率和市场竞争力。
背景技术
类似于自动变速器,自动手动变速器(automated manual transmission)通过允许在车辆行驶中经由致动器来自动地改变挡位,从而提供驾驶便利性。由于动力传动效率优于自动变速器的传动效率,自动手动变速器会有助于燃料效率的提高。
自动手动变速器包括在手动变速器中使用的液压致动器,借此通过控制挡位来改变挡位的过程能够通过变速器控制单元(transmission control unit,TCU)来自动地执行,这样就代替了由驾驶员手动地执行换挡。
然而,在基于同步换挡机构的自动手动变速器中,在通过致动器自动地执行换挡的过程中,会不可避免地出现来自发动机的动力停止供应的时刻,由此引起的扭矩减小会导致换挡感变差,即,驾驶员会感到车辆被向后拉拽的现象。
就此而言,提出了将电机增加到由发动机提供动力的车辆的方案。当来自发动机的动力停止供应时,该方案将通过电机产生的动力提供给输出轴,从而解决了在换挡过程中发生的扭矩减小的现象。
为了改善车辆的燃料效率和市场竞争力,所期望的是在车辆行驶时,加强避免换挡感下降的操作,并且增加利用电机来驱动车辆的操作的频率。就此而言,需要增加在发动机的低效率驱动范围内的电机操作的频率。
公开于该本发明背景技术部分的信息仅仅旨在加深对本发明的一般背景技术的理解,而不应当被视为承认或以任何形式暗示该信息构成已为本领域技术人员所公知的现有技术。
发明内容
本发明的各个方面致力于提供一种用于混合动力车辆的变速器,这种变速器通过在发动机的低效率的驱动范围内操作电机,来提高混合动力车辆的燃料效率和市场竞争力。
根据本发明的各个方面,一种用于混合电动车辆的变速器,该变速器可以包括:第一输入轴,其持续地接收来自发动机的动力;第二输入轴,其经由离合器而选择性地接收来自发动机的动力;中间轴,其经由具有不同传动比的多个副换挡齿轮对而联接至第一输入轴,所述多个副换挡齿轮对中的每一对副换挡齿轮彼此啮合,其中,利用接合/断开器来可以选择多个副换挡齿轮对中的一个副换挡齿轮对,使得中间轴传递动力;输出轴,其经由具有不同传动比的多个主换挡齿轮对而联接至第二输入轴,所述多个主换挡齿轮对中的每一对主换挡齿轮彼此啮合,其中,利用接合/断开器来可以选择多个主换挡齿轮对中的一个主换挡齿轮对,使得输出轴传递动力;第一单向离合器,其设置在沿着动力从发动机传递至输出轴的路径上,使得动力仅在从中间轴到输出轴的方向上传递;电机输入轴,其接收来自电机的动力;电机侧换挡单元,其包括具有不同传动比的多个齿轮对,所述多个齿轮对中的每一对齿轮设置在电机输入轴和输出轴上,并且彼此啮合,其中,利用接合/断开器来选择多个齿轮对中的可以适合于行驶速度的一个齿轮对;以及第二单向离合器,其设置在沿着动力从电机传递至输出轴的路径上,使得动力仅在从电机输入轴到输出轴的方向上传递。
所述第一输入轴和第二输入轴可以同轴心地设置;所述第二输入轴可以为中空轴,使得所述第一输入轴容纳在第二输入轴中;离合器可以设置在定位于更接近发动机的第二输入轴的第一端上。
所述输出轴可以包括第一输出轴和第二输出轴;所述第一输入轴可以设置为平行于中间轴,使得副换挡齿轮对中的每一对副换挡齿轮彼此啮合;所述第二输入轴可以设置为平行于第二输出轴,使得主换挡齿轮对中的每一对主换挡齿轮彼此啮合。
所述多个副换挡齿轮对中的至少一个副换挡齿轮对可以具有与所述多个主换挡齿轮对中的至少一个主换挡齿轮对相同的传动比。
所述多个副换挡齿轮对和所述多个主换挡齿轮对可以包括:除了最低挡位的齿轮对和最高挡位的齿轮对之外的齿轮对。
所述第二输出轴和中间轴可以同轴心地设置;所述第一单向离合器可以设置在经由第二输出轴从中间轴延伸至第一输出轴的动力传递路径中间。
所述第二输出轴上可以设置有动力传递输入齿轮;所述第一单向离合器可以设置在动力传递输入齿轮和中间轴之间;所述第一输出轴上可以设置有动力传递输出齿轮;动力传递中间齿轮可以啮合在动力传递输入齿轮和动力传递输出齿轮之间。
所述电机侧换挡单元可以包括:设置在电机输入轴和第一输出轴上的低挡位齿轮对和高挡位齿轮对,在低挡位齿轮对和高挡位齿轮对中的每一对齿轮彼此啮合;所述第二单向离合器可以设置在从低挡位齿轮对延伸至第一输出轴的动力传递路径中间。
该种变速器可以进一步包括:同步装置,该同步装置将低挡位齿轮对的输出齿轮与第一输出轴选择性地联接;其中,所述第二单向离合器可以设置在同步装置和第一输出轴之间。
所述输出轴和中间轴可以同轴心地设置;所述第一单向离合器可以设置在中间轴和输出轴之间。
所述输出轴上可以设置有动力传递构件;所述第一单向离合器可以设置在动力传递构件和中间轴之间。
所述电机侧换挡单元的多个齿轮对可以包括设置在电机输入轴和输出轴上的低挡位齿轮对和高挡位齿轮对,在低挡位齿轮对和高挡位齿轮对中的每一对齿轮彼此啮合;所述第二单向离合器可以设置在从低挡位齿轮对延伸至输出轴的动力传递路径中间。
该种变速器可以进一步包括:同步装置,所述同步装置将低挡位齿轮对的输出齿轮与输出轴选择性地联接;其中,所述第二单向离合器可以设置在同步装置和输出轴之间。
根据本发明的各个实施方案,能够从停止状态、在低速驾驶范围或在高速驾驶范围利用电机来驱动车辆。由此通过在发动机的低效率驾驶范围内操作电机,能够提高混合动力车辆的燃料效率和市场竞争力。另外,当电机的驱动转变到发动机的驱动时,在低速驱动范围的换挡点,扭矩的变化被吸收至单向离合器,去除了扭矩中断感觉,从而提高了换挡感觉。
应当理解,此处所使用的术语“车辆”或“车辆的”或其它类似术语一般包括机动车辆,例如包括运动型多用途车辆(SUV)、大客车、卡车、各种商用车辆的乘用汽车,包括各种舟艇、船舶的船只,航空器等,并且包括混合动力车辆、电动车辆、可插式混合动力电动车辆、氢动力车辆以及其它替代性燃料车辆(例如源于非石油的能源的燃料)正如此处所提到的,混合动力车辆是具有两种或更多动力源的车辆,例如具有汽油动力和电力动力两者的车辆。
本发明的方法和装置具有其它的特性和优点,这些特性和优点从并入本文中的附图和随后的具体实施方案中将是显而易见的,或者将在并入本文中的附图和随后的具体实施方案中进行详细陈述,这些附图和具体实施方案共同用于解释本发明的特定原理。
附图说明
图1示出了根据本发明的各个实施方案的用于混合动力车辆的变速器的配置;
图2示出了根据本发明的各个实施方案的用于混合动力车辆的变速器的配置;
图3示出了根据本发明的各个实施方案,在利用变速器进行升挡和降挡的情形下,在各个挡位位置的换挡操作的示意图。
应当了解,所附附图并不必须是按比例绘制的,其呈现了某种程度上经过简化的说明本发明的基本原理的各个特征本文所公开的本发明的具体设计特征包括例如具体尺寸、方向、位置和外形将部分地由具体所要应用和使用的环境来确定。
具体实施方式
下面将详细说明本发明的各个实施方案,其示例将在附图中示出并且在下文进行描述虽然本发明与示例性实施方案相接合进行描述,但是应当了解,本说明书并非旨在将本发明限制为那些示例性实施方案相反,本发明旨在不但覆盖这些示例性实施方案,而且覆盖可以包括在由所附权利要求所限定的本发明的精神和范围之内的各种替换形式、修改形式、等效形式以及其它实施方案。
根据本发明的各个实施方案的用于混合动力车辆的变速器大体上包括:第一输入轴IP1、第二输入轴IP2、中间轴CNT、输出轴、第一单向离合器OWC1,电机输入轴IPM、电机侧换挡单元、以及第二单向离合器OWC2。
下面将参考附图1和附图2并根据本发明的各个实施方案对该种变速器进行具体描述。第一输入轴IP1凭借来自发动机E的动力而持续地旋转。
第二输入轴IP2响应于离合器CL的选择性的接合和释放操作,凭借选择性地供应自发动机E的动力而可以旋转。
例如,第一输入轴IP1和第二输入轴IP2可以设置在偏心圆上,或者第二输入轴IP2可以实现为中空轴,从而将第一输入轴IP1容纳在其中。
离合器CL可以设置在第二输入轴IP2的一端(该端与第二输入轴IP2的另一端相比更接近于发动机E),发动机E直接地或经由减震器(damper)而联接至第一输入轴IP1的一端,使得第一输入轴IP1可以通过来自发动机E的动力而旋转。
具有不同传动比的多个副换挡齿轮对GS2和GS3设置在中间轴CNT和第一输入轴IP1上,使得多个副换挡齿轮对中的每一对齿轮彼此啮合。副换挡齿轮对GS2和GS3中的一对由接合/断开单元SS2&3的选择而传递动力。
例如,副换挡齿轮对GS2和GS3中的一对可以由设置在副换挡齿轮对GS2和GS3之间的接合/断开单元SS2&3进行选择,所述接合/断开单元SS2&3可以实现为用于允许和禁止动力的传输的设备,该设备选自而不限于:同步啮合式同步装置、爪型离合器、改进的爪型离合器、干式/湿式离合器、电动/电子-干式/湿式电磁离合器、联轴器、液力离合器、以及基于花键的联接结构。
另外,具有不同传动比的多个主换挡齿轮对GM2和GM3设置在输出轴和第二输入轴IP2上,使得主换挡齿轮对中的每一对齿轮彼此啮合。多个主换挡齿轮对GM2和GM3中的一对由接合/断开单元SM2&3进行选择而传递动力。
例如,主换挡齿轮对GM2和GM3中的一对可以由设置在主换挡齿轮对GM2和GM3之间的接合/断开器SM2&3选择,该接合/断开器SM2&3可以实现为用于允许和禁止动力传输的设备,接合/断开器SM2&3选自但不限于:同步啮合式同步装置、爪型离合器、改进的爪型离合器、干式/湿式离合器、电动/电子-干式/湿式电磁离合器、联轴器、液力离合器、以及基于花键的联接结构。
第一单向离合器OWC1可以设置在沿着动力从发动机E传递至输出轴的路径上,使得动力仅在从中间轴CNT到输出轴的方向上传递。
在此,用于机械地允许和禁止动力传输的第一单向离合器OWC1可以实施为选自但不限于下面一种:以如上所述的相同原理操作的机械设备、使用液压力进行操作的部件、具有液力-机械复合结构的设备、以及使用电动/电子力的设备等。
电机输入轴IPM能够利用来自电机M的动力旋转。电机输入轴IPM设置为平行于输出轴。电机输入轴IPM的一端可以直接地连接至电机M。
电机侧换挡单元包括具有不同传动比的多个齿轮对,每一对齿轮包括设置在电机输入轴IPM上的齿轮和设置在输出轴上的齿轮,以彼此啮合,使得可以通过接合/断开器SL&H来选择适合于驾驶速度的齿轮对。
例如,多个齿轮对中的一对可以由接合/断开器SL&H选择。接合/断开器SL&H可以实现为用于允许和禁止动力的传输的设备,该接合/断开器SL&H选自但不限于:同步啮合式同步装置、爪型离合器、改进的爪型离合器、干式/湿式离合器、电动/电子-干式/湿式电磁离合器、联轴器、液力离合器、以及基于花键的联接结构。
第二单向离合器OWC2可以设置在沿着动力从电机M传递至输出轴的路径上,使得动力仅在从电机输入轴IPM到输出轴的方向上传递。
在此,用于机械地允许和禁止动力传输的第二单向离合器OWC2可以实施为选自但不限于下面一种:以如上所述的相同原理操作的机械设备、使用液压力操作的部件、具有液力-机械复合结构的设备、以及使用电动/电子力的设备等。
根据如前面所述的配置,能够从停止状态、在低速驾驶范围内或在高速驾驶范围内,利用电机M来驱动车辆。由此能够通过在发动机E的低效率驾驶范围内操作电机M,来提高混合动力车辆的燃料效率和市场竞争力。
另外,通过利用第一单向离合器OWC1和第二单向离合器OWC2来吸收扭矩的改变,这样能够去除扭矩的中断感,从而提高换挡感觉。
图1示出了根据本发明的各个实施方案的用于混合动力车辆的变速器的配置,其中,输出轴包括:第一输出轴OP1和第二输出轴OP2。
例如,第一输入轴IP1设置为平行于中间轴CNT,使得多个副换挡齿轮对GS2和GS3中的一对齿轮在彼此啮合的情况下,多个副换挡齿轮对GS2和GS3可以分别地联接至第一输入轴IP1和中间轴CNT。
另外,第二输入轴IP2设置为平行于第二输出轴OP2,使得主换挡齿轮对GM2和GM3中的一对齿轮在彼此啮合的情况下,多个主换挡齿轮对GM2和GM3可以分别地联接至第二输入轴IP2和第二输出轴OP2。
特别地,副换挡齿轮对GS2和GS3与主换挡齿轮对GM2和GM3配置为:使得副换挡齿轮对GS2和GS3中的至少一对齿轮具有与主换挡齿轮对GM2和GM3中的至少一对齿轮相同的传动比。
具体而言,当设置副换挡齿轮对GS2具有第二传动比,而副换挡齿轮对GS3具有第三传动比时,可以设置主换挡齿轮对GM2具有第二传动比,而主换挡齿轮对GM3具有第三传动比。
另外,副换挡齿轮对GS2和GS3以及主换挡齿轮对GM2和GM3可以是不具有最低挡位的齿轮对和不具有最高挡位的齿轮对的齿轮对。
例如,根据本发明的各个实施方案,第二齿轮的齿轮对和第三齿轮的齿轮对可以设置为副换挡齿轮对GS2和GS3以及主换挡齿轮对GM2和GM3。第二/第三副换挡齿轮接合/断开器SS2&3设置在第二副换挡齿轮对GS2和第三副换挡齿轮对GS3之间,以选择能够被选择使用的两个副换挡齿轮对GS2和GS3中的一对。第二/第三主换挡齿轮接合/断开器SM2&3设置在第二主换挡齿轮对GM2和第三主换挡齿轮对GM3之间,以选择两个主换挡齿轮对GM2和GM3中的一对。
根据各个实施方案,连接至差速器的后减速齿轮(following reduction gear)FGR设置在第一输出轴OP1上。
另外,第二输出轴OP2和中间轴CNT同轴心地设置,以朝向彼此。第一单向离合器OWC1设置在经由第二输出轴OP2从中间轴CNT延伸至第一输出轴OP1的动力传递路径中间。由此,可以进一步地设置用于将动力从中间轴CNT传递至第一输出轴OP1的配置。
例如,动力传递输入齿轮TG_IN设置在第二输出轴OP2的一端,第一单向离合器OWC1设置在动力传递输入齿轮TG_IN和中间轴CNT之间。另外,动力传递输出齿轮TG_OUT设置在第一输出轴OP1上,并且动力传递中间齿轮TG_ID啮合在动力传递输入齿轮TG_IN和动力传递输出齿轮TG_OUT之间。
具体而言,供应至中间轴CNT的来自发动机E的驱动力传递至动力传递中间齿轮TG_ID。随后,驱动力经由动力传递中间齿轮TG_ID和动力传递输出齿轮TG_OUT,并且随后通过设置在第一输出轴OP1上的后减速齿轮FGR而传递至差速器。当中间轴CNT的旋转速度大于动力传递中间齿轮TG_ID的旋转速度时,第一单向离合器OWC1吸收中间轴CNT和动力传递中间齿轮TG_ID之间的速度差,由此中间轴CNT能够相对旋转。
参见图1,电机侧换挡单元包括:低挡位齿轮对G1和高挡位齿轮对G4。
例如,低挡位齿轮对G1和高挡位齿轮对G4设置在电机输入轴IPM和第一输出轴OP1上,使得齿轮对中的每一对齿轮彼此啮合。
在此,电机侧接合/断开器SL&H提供在设置在低挡位齿轮对G1中的输出齿轮G1_OUT和设置在高挡位齿轮对G4中的输出齿轮G4_OUT之间。低挡位齿轮对G1可以是第一挡位的齿轮对,高挡位齿轮对G4可以是第四挡位的齿轮对。电机侧接合/断开器SL&H可以是第一/第四挡位接合/断开器。
另外,高挡位齿轮对G4可以用作电力产生齿轮对,其中电机M可以用作发电机。尽管电机M可以是能够同时执行电动机所独有的旋转功能和发电机功能的电动机发动机,但是为了清楚和简要的考虑,本文使用术语“电机”。
第二单向离合器OWC2设置在从低挡位齿轮对G1延伸至第一输出轴OP1的动力传递路径中间。
例如,提供有同步单元S1-1,所述同步单元S1-1允许低挡位齿轮对G1的输出齿轮G1_OUT选择性地联接至第一输出轴OP1。就此而言,第二单向离合器OWC2设置在同步单元S1-1和第一输出轴OP1之间。
也即,低挡位齿轮对G1的输出齿轮G1_OUT可以经由同步单元S1-1联接至第一输出轴OP1。
另外,图2示出了根据本发明的各个实施方案的用于混合动力车辆的变速器的配置。第一输入轴IP1设置为平行于中间轴CNT,使得在每一个副换挡齿轮对GS2和GS3彼此啮合的情况下,多个副换挡齿轮对GS2和GS3联接至第一输入轴IP1和中间轴CNT。
另外,第二输入轴IP2设置为平行于输出轴OP,使得在每一主换挡齿轮对GM2和GM3彼此啮合的情况下,多个主换挡齿轮对GM2和GM3联接至第二输入轴IP2和输出轴OP。
此外,连接至差速器的后减速齿轮FGR设置在输出轴OP上。
输出轴OP和中间轴CNT同轴心地设置,以朝向彼此。第一单向离合器OWC1设置在从中间轴CNT延伸至输出轴OP的动力传递路径中间。
例如,动力传递构件TG设置在输出轴OP的一端,第一单向离合器OWC1设置在动力传递构件TG和中间轴CNT之间。动力传递构件TG可以为齿轮形状。
从发动机E供应至中间轴CNT的动力经由第一单向离合器OWC1而传递至动力传递构件TG。动力可以经由设置在输出轴OP上的后减速齿轮FGR而传递至差速器。在此时,当中间轴CNT的旋转速度大于动力传递构件TG的旋转速度时,第一单向离合器OWC1吸收在中间轴CNT和动力传递构件TG之间的速度差,由此使中间轴CNT能够相对旋转。
参见图2,电机侧换挡单元包括低挡位齿轮对G1和高挡位齿轮对G4。
例如,低挡位齿轮对G1和高挡位齿轮对G4设置在电机输入轴IPM和第一输出轴OP1上,使得每个齿轮对中的齿轮彼此啮合。
在此,电机侧接合/断开器SL&H提供在设置在低挡位齿轮对G1中的输出齿轮G1_OUT和设置在高挡位齿轮对G4中的输出齿轮G4_OUT之间。低挡位齿轮对G1可以是第一挡位的齿轮对,而高挡位齿轮对G4可以是第四挡位的齿轮对。电机侧接合/断开器SL&H可以是第一/第四挡位接合/断开器。
第二单向离合器OWC2设置在从低挡位齿轮G1延伸至输出轴OP的动力传递路径中间。
例如,提供同步单元S1-1,所述同步单元S1-1允许低挡位齿轮对G1的输出齿轮G1_OUT选择性地联接至输出轴OP。就此而言,第二单向离合器OWC2设置在同步单元S1-1和输出轴OP之间。
即是,低挡位齿轮对G1的输出齿轮G1_OUT可以经由同步单元S1-1联接至输出轴OP。
在下文中,根据本发明的各个实施方案,将对使用变速器在特定换挡点的换挡操作进行描述。
参见图1至图3,当车辆在第一挡位运行时,其中设置有第二单向离合器OWC2的同步单元S1-1操作为选择低挡位齿轮对G1的输出齿轮G1_OUT。
当电机M在该状态下运行时,第二单向离合器OWC2在牵引第一输出轴OP1的同时,引起低挡位齿轮对G1的输出齿轮G1_OUT旋转,使得车辆能够利用电机M的驱动力而在第一挡位行驶。
随后,在从第一挡位至第二挡位的升挡的情形中,利用第二/第三主换挡齿轮接合/断开器SM2&3来选择第二主换挡齿轮对GM2,并且随后离合器CL转变到接合位置,由此车辆可以利用来自发动机E的驱动力而在第二挡位行驶。在离合器CL转变到接合位置的时刻,以第二主换挡齿轮对GM2的传动比传递至第二输出轴OP2的发动机的旋转速度大于低挡位齿轮对G1的输出齿轮G1_OUT的旋转速度。第二单向离合器OWC2吸收速度之间的差,从而防止互锁。
另外,在从第二挡位至第三挡位的升挡的情形中,利用第二/第三副换挡齿轮接合/断开器SS2&3来选择第二副换挡齿轮对GS2。在此,第二主换挡齿轮对GM2的传动比等于第二副换挡齿轮对GS2的传动比,从而旋转能够传递而不会发生互锁。
随后,离合器CL转变到断开位置,并且第二/第三主换挡齿轮接合/断开器SM2&3选择性地从第二主换挡齿轮对GM2转变到断开位置。即便其中在离合器CL和第二/第三主换挡齿轮接合/断开器SM2&3转变到断开位置的情况下,发动机E的驱动力仍然经由第二副换挡齿轮对GS2而传递。特别地,中间轴CNT在牵引动力传递中间齿轮TG_ID的同时经由第一单向离合器OWC1而导致旋转,由此,车辆能够利用发动机E的驱动动力而继续以第二挡位行驶。
其后,利用第二/第三主换挡齿轮接合/断开器SM2&3选择第三主换挡齿轮对GM3,并且离合器转变到接合位置,由此车辆可以利用发动机E的驱动力而以第三挡位行驶。
特别地,在离合器CL转变到接合位置时,以第三主换挡齿轮对GM3的传动比传递至动力传递中间齿轮TG_ID的旋转速度大于以第二副换挡齿轮对GS2的传动比传递至中间轴CNT的旋转速度。第一单向离合器OWC1吸收速度之间的差,从而防止互锁。
然后,利用第二/第三副换挡齿轮接合/断开器SS2&3选择和接合第三副换挡齿轮对GS3。在此时,第三主换挡齿轮对GM3的传动比等于第三副换挡齿轮对GS3的传动比,从而旋转能够传递,而不会发生互锁。
在从第三挡位至第四挡位的升挡的情形中,电机M的旋转速度设定为:以第三副换挡齿轮对GS3的传动比传递至第一输出轴OP1的旋转速度,然后利用第一/第四挡位接合/断开器SL&H选择高挡位齿轮对。然后,在离合器CL转变到断开位置的同时,控制电机M,由此,车辆能够利用电机M的驱动力而以第四或更高挡位行驶。
在以第四或更高挡位行驶的过程中,第二/第三主换挡齿轮接合/断开器SM2&3和第二/第三副换挡齿轮接合/断开器SS2&3都被控制为转变到断开位置。
在从第四挡位至第三挡位的降挡的情形中,利用第二/第三主换挡齿轮接合/断开器SM2&3选择第三主换挡齿轮对GM3,并且电机M的旋转速度设定为:以第三主换挡齿轮对GM3的传动比传递至第一输出轴OP1的发动机的旋转速度。然后,在第一/第四挡位接合/断开器SL&H从高挡位齿轮对G4断开的同时,离合器CL转变到接合位置,由此,车辆可以利用发动机E的驱动力而以第三挡位行驶。可以利用第二/第三副换挡齿轮接合/断开器SS2&3来选择第三换挡齿轮对GS3。
另外,在从第三挡位至第二挡位的降挡的情形中,利用单个离合器执行换挡。具体而言,离合器转变到断开位置,然后第二/第三主换挡齿轮接合/断开器SM2&3和第二/第三副换挡齿轮接合/断开器SS2&3从第三主换挡齿轮对GM3和第三副换挡齿轮对GS3断开。在第二/第三主换挡齿轮接合/断开器SM2&3和第二/第三副换挡齿轮接合/断开器SS2&3与第二主换挡齿轮对GM2和第二副换挡齿轮对GS2接合之后,离合器CL转变到接合位置,由此形成第二挡位。由此,车辆可以以第二挡位行驶。
随后,在从第二挡位至第一挡位的降挡的情形中,电机M的旋转速度设定为:以第二齿轮G2的齿轮对的传动比传递至第一输出轴OP1的发动机E的旋转速度,并且利用第一/第四挡位接合/断开器SL&H而选择低挡位齿轮对G1。然后,在离合器CL转变到断开位置的同时,控制电机M的运行,由此车辆可以以第一挡位行驶。
在下文中,将描述为何利用第一/第四挡位接合/断开器SL&H来选择低挡位齿轮对G1的原因。当利用同步单元S1-1而选择低挡位齿轮对G1时,由于从第二挡位至第一挡位的降挡的行驶特性,第一输出轴OP1旋转得比低挡位齿轮对G1的输出齿轮G1_OUT快。于是,第二单向离合器OWC2吸收速度之间的差。因此,来自电机M的驱动力并未传递至第一输出轴OP1,即,动力的供应停止。
就此而言,根据本发明的各个实施方案,利用第一/第四挡位接合/断开器SL&H来选择低挡位齿轮对G1,使得第一输出轴OP1的减速能够通过控制电机M而受到控制。因而能够根据第一传动比使车辆快速地减速。
根据如前所述的本发明的各个实施方案,能够从停止状态、在低速驱动范围、或者在高速驱动范围利用电机M来驱动车辆。由此能够在发动机E的低效率的驱动范围内利用电机M来提高混合动力车辆的燃料效率和市场竞争性。另外,在低速驱动范围的换挡点,变化的扭矩被吸收至第一单向离合器OWC1或第二单向离合器OWC2,从而去除了扭矩中断感,由此改善了换挡感觉。
为了方便解释和精确限定所附权利要求,将参考附图中所显示的特征的位置使用术语“上”或“下”、“内”或“外”等来描述示例性实施方案的这些特征。
前面对本发明具体示例性实施方案所呈现的描述是出于说明和描述的目的前面的描述并不想要成为毫无遗漏的,也不是想要把本发明限制为所公开的精确形式,显然,根据上述教导很多改变和变化都是可能的选择示例性实施方案并进行描述是为了解释本发明的特定原理及其实际应用,从而使得本领域的其它技术人员能够实现并利用本发明的各种示例性实施方案及其各种选择形式和修改形式本发明的范围意在由所附权利要求书及其等效形式所限定。
Claims (13)
1.一种用于混合电动车辆的变速器,该变速器包括:
第一输入轴,其持续地接收来自发动机的动力;
第二输入轴,其经由离合器而选择性地接收来自发动机的动力;
中间轴,其经由具有不同传动比的多个副换挡齿轮对而联接至第一输入轴,所述多个副换挡齿轮对中的每一对副换挡齿轮彼此啮合,其中,利用接合/断开器来选择多个副换挡齿轮对中的一个副换挡齿轮对,使得中间轴传递动力;
输出轴,其经由具有不同传动比的多个主换挡齿轮对而联接至第二输入轴,所述多个主换挡齿轮对中的每一对主换挡齿轮彼此啮合,其中,利用接合/断开器来选择多个主换挡齿轮对中的一个主换挡齿轮对,使得输出轴传递动力;
第一单向离合器,其设置在沿着动力从发动机传递至输出轴的路径上,使得动力仅在从中间轴到输出轴的方向上传递;
电机输入轴,其接收来自电机的动力;
电机侧换挡单元,其包括具有不同传动比的多个齿轮对,所述多个齿轮对中的每一对齿轮设置在电机输入轴和输出轴上,并且彼此啮合,其中,利用接合/断开器来选择多个齿轮对中的能够适合于行驶速度的一个齿轮对;以及
第二单向离合器,其设置在沿着动力从电机传递至输出轴的路径上,使得动力仅在从电机输入轴到输出轴的方向上传递。
2.根据权利要求1所述的用于混合电动车辆的变速器,其中,
所述第一输入轴和第二输入轴同轴心地设置;
所述第二输入轴包括中空轴,使得所述第一输入轴容纳在第二输入轴中;
离合器设置在定位于更接近发动机的第二输入轴的第一端上。
3.根据权利要求1所述的用于混合电动车辆的变速器,其中,
所述输出轴包括第一输出轴和第二输出轴;
所述第一输入轴设置为平行于中间轴,使得副换挡齿轮对中的每一对副换挡齿轮彼此啮合;
所述第二输入轴设置为平行于第二输出轴,使得主换挡齿轮对中的每一对主换挡齿轮彼此啮合。
4.根据权利要求1所述的用于混合电动车辆的变速器,其中,所述多个副换挡齿轮对中的至少一个副换挡齿轮对具有与所述多个主换挡齿轮对中的至少一个主换挡齿轮对相同的传动比。
5.根据权利要求4所述的用于混合电动车辆的变速器,其中,所述多个副换挡齿轮对和所述多个主换挡齿轮对包括:除了最低挡位的齿轮对和最高挡位的齿轮对之外的齿轮对。
6.根据权利要求3所述的用于混合电动车辆的变速器,其中,
所述第二输出轴和中间轴同轴心地设置;
所述第一单向离合器设置在经由第二输出轴从中间轴延伸至第一输出轴的动力传递路径中间。
7.根据权利要求6所述的用于混合电动车辆的变速器,其中,
所述第二输出轴上设置有动力传递输入齿轮;
所述第一单向离合器设置在动力传递输入齿轮和中间轴之间;
所述第一输出轴上设置有动力传递输出齿轮;
动力传递中间齿轮啮合在动力传递输入齿轮和动力传递输出齿轮之间。
8.根据权利要求3所述的用于混合电动车辆的变速器,其中,
所述电机侧换挡单元包括:设置在电机输入轴和第一输出轴上的低挡位齿轮对和高挡位齿轮对,低挡位齿轮对和高挡位齿轮对中的每一对齿轮彼此啮合;
所述第二单向离合器设置在从低挡位齿轮对延伸至第一输出轴的动力传递路径中间。
9.根据权利要求8所述的用于混合电动车辆的变速器,进一步包括:同步装置,该同步装置将低挡位齿轮对的输出齿轮与第一输出轴选择性地联接;
其中,所述第二单向离合器设置在同步装置和第一输出轴之间。
10.根据权利要求1所述的用于混合电动车辆的变速器,其中,
所述输出轴和中间轴同轴心地设置;
所述第一单向离合器设置在中间轴和输出轴之间。
11.根据权利要求10所述的用于混合电动车辆的变速器,其中,
所述输出轴上设置有动力传递构件;
所述第一单向离合器设置在动力传递构件和中间轴之间。
12.根据权利要求1所述的用于混合电动车辆的变速器,其中,所述电机侧换挡单元的多个齿轮对包括设置在电机输入轴和输出轴上的低挡位齿轮对和高挡位齿轮对,低挡位齿轮对和高挡位齿轮对中的每一对齿轮彼此啮合;
所述第二单向离合器设置在从低挡位齿轮对延伸至输出轴的动力传递路径中间。
13.根据权利要求12所述的用于混合电动车辆的变速器,进一步包括:同步装置,所述同步装置将低挡位齿轮对的输出齿轮与输出轴选择性地联接;
其中,所述第二单向离合器设置在同步装置和输出轴之间。
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