CN115397688A - 在混合动力总成中换挡鼓的学习的方法 - Google Patents

在混合动力总成中换挡鼓的学习的方法 Download PDF

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Publication number
CN115397688A
CN115397688A CN202180027417.5A CN202180027417A CN115397688A CN 115397688 A CN115397688 A CN 115397688A CN 202180027417 A CN202180027417 A CN 202180027417A CN 115397688 A CN115397688 A CN 115397688A
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China
Prior art keywords
shift
shifting
shift drum
rotational speed
electric machine
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延斯·萨贝里
马里厄斯·赫梅尔
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Magna Pt & CoKg GmbH
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Magna Pt & CoKg GmbH
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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
    • 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
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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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    • F16H—GEARING
    • F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
    • F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
    • F16H63/08—Multiple final output mechanisms being moved by a single common final actuating mechanism
    • F16H63/16—Multiple final output mechanisms being moved by a single common final actuating mechanism the final output mechanisms being successively actuated by progressive movement of the final actuating mechanism
    • F16H63/18—Multiple final output mechanisms being moved by a single common final actuating mechanism the final output mechanisms being successively actuated by progressive movement of the final actuating mechanism the final actuating mechanism comprising cams
    • 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
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  • Transportation (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • General Engineering & Computer Science (AREA)
  • Automation & Control Theory (AREA)
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Abstract

本发明涉及一种用于混合动力总成(10)中的换挡鼓(100)的学习的方法，其中所述混合动力总成(10)具有呈内燃机(12)形式的第一驱动机和呈电机(16)形式的第二驱动机以及变速器装置(18)，所述变速器装置能够经由换挡元件(K0)与所述第一驱动机(12)连接，并且所述变速器装置能够与所述第二驱动机(12)连接或者已经与所述第二驱动机连接，其中所述变速器装置(18)包括输入轴(26)和输出轴(34)以及设置在其之间的多个挡位(40、46、56)，所述挡位构成为能够经由相关联的换挡元件(K1、K2、K4)换挡，其中所述换挡元件(K0、K1、K2、K4)经由可旋转360度的换挡鼓(100)切换，所述方法具有以下方法步骤：将换挡鼓(100)旋转到第一换挡状态中，所述第一换挡状态对应于变速器装置(18)的空挡位置；借助于所述电机(16)产生低的转速，由此在所述变速器装置(18)的至少两个换挡元件(K0，K2)上产生转速差；将所述换挡鼓(100)沿着第一旋转方向旋转到第二换挡状态中，其中第一换挡元件(K0)以所述转速差切换，使得所述电机(16)突然制动到零，其中产生所述电机(16)的转速信号，并且将所述转速信号与作为虚拟的端部止挡件的第一参考位置/旋转角度相关联；将所述换挡鼓(100)转回所述第一换挡状态中；并且将换挡鼓(100)沿着第二旋转方向旋转到另一换挡状态中，其中第二换挡元件(K2)以所述转速差切换，使得使所述电机(16)突然制动到零，其中产生所述电机(16)的转速信号，并且将所述转速信号与作为虚拟的端部止挡件的第二参考位置/旋转角度相关联。

Description

在混合动力总成中换挡鼓的学习的方法
技术领域
本发明涉及一种用于在混合动力总成中换挡鼓的学习的方法。
背景技术
用于机动车辆的混合动力总成近年来变得流行起来。混合动力总成在此能够以不同的方式方法实现。
一个示例是所谓的串联混合动力总成，其中内燃机的输出端与发电机连接，其中混合动力总成的从动器与电动机连接，并且其中电动机和发电机连接到公共电池上。
并联混合动力总成能够用于将内燃机的驱动功率和电动机的驱动功率传输到从动器上。在此，在一些情况下，电机围绕曲轴设置，并且曲轴可经由启动离合器与从动器连接，更确切地说，通常经由多挡变速器。
混合动力总成通常是已知的(分轴式)，其中内燃机驱动车辆的一个车桥并且电机驱动车辆的另一个车桥。
此外，已知具有双离合变速器的并联混合动力总成，其中电机能够连接到子变速器之一的输入端上或者能够与双离合变速器的输出端连接。使用双离合变速器能够在不中断牵引力的情况下进行换挡。
变速器装置为了设立不同挡位具有多个换挡离合器。换挡离合器用于将轮组带入功率流中(在这种情况下，轮组的活动轮与相关联的轴连接)。对换挡离合器的操控在此例如经由包括换挡鼓的换挡设备来进行。在此必须准确已知换挡鼓的旋转角。
换挡鼓以及用于参考换挡鼓的旋转位置的方法原则上是已知的。在这种情况下，换挡鼓通常构成有所谓的端部止挡件，其中位置传感器能够检测端部止挡件的相应的角位置。
文献WO2015/149797A1例如公开了一种用于操作变速器的操作设备，其具有可旋转的换挡鼓，其中与换挡鼓抗扭地连接的端部止挡件与信号指示装置一起作用，使得在信号指示装置和端部止挡件在换挡鼓的特定的旋转位置中相对移动时可产生位置信号。位置信号可由改变驱动马达在特定的旋转位置中的驱动力的机械阻力产生。
从文献EP1286088A1中已知将磁环固定在换挡鼓上，所述磁环构成用于借助于适合的传感器进行相应的换挡鼓的旋转位置检测。
如上所述，为了参考旋转位置，能够将转动的端部止挡件集成到换挡鼓中。然而，在这种情况下，换挡鼓的可旋转性是有限的。宽且实心的止挡件会部分地显著降低换挡鼓的可用的旋转角。
在具有与换挡鼓体牢固连接的止挡件的已知的换挡鼓装置中，由360°减去止挡元件的圆周角并减去参考元件的圆周角产生换挡鼓体的最大可旋转性，所述参考元件例如能够是固定于壳体的元件，例如壳体止挡件。在此，如果例如止挡元件在35°上延伸并且如果壳体止挡件同样延伸35°，那么现有技术中的最大的旋转角仅为290°。
尤其地，变速器的上述的混动化产生对换挡设备的新的挑战。在某些情况下有利的是，换挡鼓能够在两个旋转方向上任意/连续地旋转。
如果换挡鼓装置需要超过360°的旋转，那么从现有技术中已知的用于需要末端止挡件的换挡鼓的学习的方法以这种方式方法是不可行的。
发明内容
在此背景下，本发明的目的是实现一种用于在混合动力总成中换挡鼓的学习的方法，所述方法能够在如下换挡鼓中使用，所述换挡鼓能够在两个旋转方向上连续地旋转。
上述目的通过在权利要求1中提出的方法实现。
通过上述用于换挡鼓的学习的方法，可以简单的方式方法出于参考换挡角度的目的来确定在可连续旋转的换挡鼓中的虚拟的端部止挡件。
这由此是可行的是，因为从混合动力总成的变速器装置的、对应于换挡鼓的第一换挡状态的空挡位置开始，借助于电机产生小的转速，由此在变速器装置的至少两个换挡元件处产生转速差。
其中紧接着在另一方法步骤中，换挡鼓沿着第一旋转方向旋转到另一换挡状态中，并且第一换挡元件以转速差切换，使得电机突然制动到零，其中产生电机的转速信号并且将该转速信号与作为虚拟的端部止挡件的第一参考位置相关联。
其中在另一方法步骤中，换挡鼓在此旋转回到空挡位置中。
然后重新借助于电机产生小的转速。
其中在最后的方法步骤中，换挡鼓沿着第二旋转方向旋转到又一换挡状态中，并且第二换挡元件以转速差切换，使得电机突然制动到零，其中产生电机的转速信号，并且将该转速信号与作为虚拟的端部止挡件的第二参考位置相关联。
附图说明
本发明的实施例在附图中示出并且在以下描述中详细阐述。附图示出：
图1示出机动车辆的混合动力总成的示意图，其中混合动力总成设计用于执行根据本发明的方法。
图2示出换挡鼓的一部分的视图
图3a-3d示出根据矩阵在换挡鼓沿着第一旋转方向旋转时离合器K0和K2的不同的换挡状态
图4示出具有不同的换挡状态S1-S4的换挡鼓的示意图；以及
图5a-5d以示意图形式示出用于执行根据本发明的方法的方法步骤。
具体实施方式
在图1中以示意形式示出用于机动车辆的混合动力总成并且通常用10表示。
混合动力总成10具有呈内燃机12形式的第一驱动机。内燃机12能够与起动器14连接。此外，混合动力总成10包括呈电机16形式的第二驱动机。
混合动力总成10还具有与内燃机12和电机16连接的变速器装置18。
变速器装置18具有变速器输入轴26。变速器输入轴26的端部区域在此包括支承在变速器输入轴26上的空心轴54。在变速器输入轴26与可旋转地支承在变速器输入轴上的空心轴54之间的连接，如下面将更详细描述的那样可经由换挡装置K4建立。
此外，惯性飞轮32的输入元件28(内燃机的输出轴)与内燃机12的曲轴连接。惯性飞轮32的输出元件30可经由换挡元件K0与变速器输入轴26连接，所述换挡元件能够构成为爪式离合器。换挡元件K0能够占据两个换挡位置。第一换挡位置是空挡位置，在所述空挡位置中在内燃机12和变速器输入轴26之间不建立连接。第二换挡位置是如下位置，所述位置在内燃机12和变速器输入轴26之间建立连接。换挡元件K0的换挡由双箭头PF0示出。
变速器装置18还具有变速器输出轴34，所述变速器输出轴相对于变速器输入轴26平行错开地定向。
在输出侧，变速器装置18与差速器20连接，借助于所述差速器可将驱动功率分配到被驱动的车轮22L、22R上。为此，从动器齿轮36在端侧固定在变速器输出轴34上，所述从动器齿轮与差速器齿轮38接合。差速器齿轮38抗扭地与差速器20的差速器壳连接。
变速器装置18包括三个齿轮级，所述齿轮级如接下来所描述的那样经由三个轮组形成。
变速器输入轴26和变速器输出轴34经由第一轮组40彼此连接，所述第一轮组包括支承在变速器输入轴26上的固定轮42和与变速器输出轴34连接的活动轮44。活动轮44的齿与固定轮42的齿啮合地接合。第一轮组40与前进挡1相关联，所述前进挡形成变速器装置18的最低的前进挡。
变速器输入轴26还经由第二轮组46与变速器输出轴34连接，其中第二轮组46具有可旋转地支承在变速器输入轴26上的固定轮48和固定到变速器输出轴34上的活动轮50。活动轮48的齿与固定轮50的齿啮合地接合。第二轮组46与前进挡3相关联。
出于建立活动轮44或活动轮50的抗扭的连接的目的，换挡元件K1在这两个活动轮之间设置在变速器输出轴34上。换挡元件K1能够占据以下三个换挡位置。
空挡位置，在所述空挡位置中这两个活动轮44、50中的任何一个都不与变速器输出轴34抗扭地连接。换挡位置，在所述换挡位置中，换挡元件K1切换到轴向向右移置的位置中，由此在活动轮44和变速器输出轴34之间建立抗扭的连接。由此，变速器输入轴26经由第一轮组40与变速器输出轴34连接并且实现任选的扭矩传输路径。
还有换挡位置，在所述换挡位置中，换挡元件K1切换到轴向向左移置的位置中，由此在活动轮50和变速器输出轴34之间建立抗扭的连接。由此，变速器输入轴26经由第二轮组46与变速器输出轴34连接。换挡元件K1的轴向移置通过双箭头PF1表示。换挡元件K1是双侧的形状配合的离合器。由于其实施方案为本领域技术人员所熟知，因此关于这一点不再赘述。换挡元件通常构成为同步单元。
在本文中，术语“连接”意味着：能够经由该连接传输驱动功率。因此，连接能够是可行的(例如可经由换挡离合器产生的)连接，但也能够是如下连接，所述连接例如使所连接的元件置于固定的转速比。
在将换挡元件K0调节到第二换挡位置中时，能够借助于第一轮组40设立内燃机式的运行，其中挂入前进挡1。替选地，能够经由换挡元件K0设立借助于内燃机12的行驶运行，其中第二轮组46被切换到功率流中，以便挂入前进挡3。
变速器输入轴26可经由桥式离合器BR与空心轴54连接。
变速器装置18还包含呈行星变速器64形式的叠加齿轮组。这种行星变速器原则上是已知的并且关于这一点不再进一步描述。所述行星变速器基本上包括齿圈66、支承在行星架上的行星轮83和太阳轮82。
作为行星变速器64的第一输入元件的太阳轮82与空心轴54抗扭地连接。
作为第二输入元件的齿圈66连接在端侧设置的空心轴部段68上，其中空心轴部段68与变速器输入轴26同轴地构成并且相对于变速器输入轴26是可旋转的。
行星轮83支承在行星架上，所述行星架形成另一输入元件。
第三轮组56的第一活动轮58可旋转地支承在行星架上。第三轮组56还具有可旋转地支承在变速器输出轴34上的第二活动轮60。第三轮组56形成第二挡位。
第一活动轮58能够借助于锁止离合器BL与空心轴54抗扭地耦联。第二活动轮60能够借助于换挡元件K2与变速器输出轴34抗扭地耦联。换挡元件K2能够占据以下两个换挡位置。
空挡位置，在所述空挡位置中活动轮60可旋转地支承在变速器输出轴34上。第二换挡位置，在所述第二换挡位置中，换挡元件K2切换到轴向向左移置的位置中，由此在第二活动轮60和变速器输出轴34之间建立抗扭的连接。由此，变速器输入轴26或空心轴54能够经由第三轮组56与变速器输出轴34相连接并且实现另一任选的扭矩传输路径。
换挡元件K2的轴向移置通过箭头PF2表示。换挡元件K2是单侧的形状配合的离合器。
桥式离合器和锁止离合器集成在换挡装置K4中，所述换挡装置具有三个换挡位置并且可借助于单个操作元件例如单个换挡套筒来操作。
在换挡装置K4切换到向左移置的位置中的第一换挡位置中，锁止离合器BL闭合而桥式离合器BR断开。其结果是第一活动轮58与行星架抗扭地耦联并且与变速器输入轴26的连接被断开。行星变速器64处于闭锁状态中。
在换挡装置K4的向右移置的第二位置中，桥式离合器BR闭合而锁止离合器BL断开。其结果是第一活动轮58可旋转地支承在行星架上，并且空心轴54与变速器输入轴26抗扭地连接。
此外，能够通过换挡装置K4设立中间的换挡位置。在中间的换挡位置中，锁止离合器和桥式离合器闭合。在这种情况下，行星变速器64处于闭锁位置中。此外，建立在空心轴54与变速器输入轴26之间的连接。
空心轴部段68经由齿轮级70与电机16耦联。齿轮级70具有抗扭地设置在空心轴部段68上的第一齿轮72和与第一齿轮72接合的第二齿轮74。第二齿轮74与电机16的驱动小齿轮76接合。
第二齿轮74可旋转地支承在中间轴78上，所述中间轴相对于变速器输入轴26同轴偏移地定向并且优选也相对于变速器输出轴34同轴偏移地定向。
电机16具有机器轴80，所述机器轴与驱动小齿轮76同轴地定向并且与其抗扭地连接。机器轴80相对于变速器输入轴26和变速器输出轴34平行地偏移。
如上面已经讨论的那样，换挡元件K0、K1和K2以及换挡装置K4借助于换挡套筒切换到所述换挡位置中。
为了使这些换挡套筒轴向运动从而切换这些换挡套筒，变速器装置18包括具有可旋转地支承的换挡鼓的换挡装置。在所示出的适用于执行根据本发明的方法的实施例中，在图2中示出的换挡鼓100切换这两个换挡元件K0和K2。
换挡鼓100具有换挡鼓体102，所述换挡鼓体沿着两个旋转方向围绕旋转轴线104可旋转地支承，更确切地说，相对于壳体可旋转。例如，壳体能够是变速器装置18的壳体。
换挡鼓体102与未示出的驱动元件连接。驱动元件例如能够由具有外齿部的齿轮形成。例如，驱动元件的外齿部能够与换挡鼓马达的驱动小齿轮接合。例如，换挡鼓马达能够是电动机。因此，通过操控换挡鼓马达，换挡鼓体102能够相对于壳体旋转。
在换挡鼓体102的外环周上构成有至少一个呈换挡鼓槽106形式的换挡轮廓，其如能够从图2中所看到的那样是轴向地成型的。换挡鼓槽106连续地构成，使得换挡鼓100的沿着两个旋转方向的在360度的旋转角上的任意旋转都是可行的。
换挡拨叉相应地接合到该换挡鼓槽106中，所述换挡拨叉也作用在相关联的换挡套筒上。换挡拨叉在此具有滑块，所述滑块接合到换挡鼓槽106中。在换挡鼓槽106的适合的构成方案中，换挡鼓体102的旋转因此导致换挡杆的轴向偏移从而导致换挡套筒的轴向偏移，这引起换挡元件K0和K2调节到已经描述的换挡位置中。
如从根据图3a-3d的换挡元件K0和K2的换挡状态的矩阵中所看到的那样，在换挡鼓100旋转360度时，可按照以下给出的顺序在环周上分布式地切换4种换挡状态：
-换挡状态1(S1)：换挡元件K0和K2处于空挡位置中(图3a)，
-换挡状态2(S2)：换挡元件K0在第二换挡位置(内燃机12通过换挡元件K0与变速器输入轴26耦联)而K2在空挡位置中(图3b)，
-换挡状态3(S3)：换挡元件K0在第二换挡位置中而换挡元件K2在第二换挡位置(第二活动轮60与变速器输出轴34抗扭地连接)中(图3c)
-换挡状态4(S4)：换挡元件K0处于空挡位置中而换挡元件K2处于第二换挡位置中(图3d)。
在换挡鼓100沿着相同的旋转方向进一步旋转时，在换挡状态4(S4)之后再次达到换挡状态1(S1)。
下面根据图5a-5d的示意图详细描述根据本发明的用于换挡鼓100的学习，即用于确定对应于旋转角度0的旋转角度的方法。
在图5a中示出的初始位置在第一方法步骤中首先是换挡状态1(S1)，在所述初始位置中，这两个换挡元件K0和K2处于空挡位置中。上述其他换挡元件或换挡装置在此具有以下换挡状态：
-换挡装置K4在中间换挡位置中，
-换挡元件K1在空挡位置中。
在混合动力总成的这种状态下，对应于内燃机12的输出轴的输入元件28以及曲轴具有转速0。这与电机16的机器轴80具有何种转速无关。
在图5b中示出的随后的方法步骤中，为了在电机16的转速低时确定第一参考位置，换挡鼓100进一步朝向换挡状态2(S2)旋转。恰好在换挡元件K0已经克服惯性飞行阶段(Freiflugphase)的时刻，这能够在电机16的转速信号中看到。电机16保持停止，因为其现在经由换挡元件K0、输入轴26、处于中间换挡位置中的换挡装置K4，即在桥式离合器接通和锁止离合器接通时，经由叠加齿轮组、齿轮级70、驱动小齿轮76与静止的内燃机12连接。这种情况在换挡鼓100的相应的旋转角中限定第一参考位置。
在确定第一参考位置之后，换挡鼓100在此旋转回到第一换挡状态S1中，所述第一换挡状态如在第一方法步骤中已经阐述的那样对应于空挡。这在图5c中示出。
从换挡状态1(S1)开始，换挡鼓100然后在电机16的转速低的情况下进一步旋转到换挡状态4(S4)中以确定第二参考位置。这在图5d中示出。恰好在换挡元件K2已经克服惯性飞行阶段的时刻，这能够在电机16的转速信号中看到。电机16保持停止，因为其现在经由换挡元件K2、第三轮组56、叠加轮组、齿轮级70和驱动小齿轮76与停止的变速器输出轴34连接。这种情况在换挡鼓100的相应旋转角中限定第二参考位置。
在此时在换挡鼓100的相关联的旋转角中对应于虚拟的端部止挡件的这两个参考位置已经被确定并且存储在所属的控制单元中之后，结束学习过程。
附图标记列表
10 混合动力总成
12 内燃机
14 起动器
16 电机
18 变速器装置
20 差速器
22R 被驱动的车轮
22L 被驱动的车轮
26 变速器输入轴
28 输入元件
30 输出元件
32 惯性飞轮
34 变速器输出轴
36 从动器齿轮
38 差速器齿轮
40 第一轮组
42 固定轮
44 活动轮
46 第二轮组
48 固定轮
50 活动轮
56 第三轮组
58 第一活动轮
60 第二活动轮
54 空心轴
64 行星变速器
66 齿圈
68 空心轴部段
70 齿轮级
72 第一齿轮
74 第二齿轮
76 驱动小齿轮
80 机器轴
83 行星轮
82 太阳轮
100 换挡鼓
102 换挡鼓体
104 旋转轴线
106 换挡鼓槽
BL 锁止离合器
BR 桥式离合器
K0 换挡元件
K1 换挡元件
K2 换挡元件
K4 换挡装置

Claims (4)

1.一种用于混合动力总成(10)中的换挡鼓(100)的学习的方法，其中所述混合动力总成(10)具有呈内燃机(12)形式的第一驱动机和呈电机(16)形式的第二驱动机以及变速器装置(18)，所述变速器装置能够经由换挡元件(K0)与所述第一驱动机连接，并且所述变速器装置能够与所述第二驱动机连接或者已经与所述第二驱动机连接，其中所述变速器装置(18)包括变速器输入轴(26)和变速器输出轴(34)以及设置在其之间的多个呈轮组(40、46、56)形式的齿轮级，所述齿轮级构成为能够经由相关联的换挡元件(K1、K2、K4)换挡，其中所述换挡元件(K0、K1、K2、K4)经由至少一个换挡设备切换，所述换挡设备包括换挡鼓(100)，并且其中所述至少一个换挡鼓(100)包括换挡鼓体(102)，所述换挡鼓体围绕换挡鼓轴线(104)沿着第一和第二旋转方向能够连续地旋转，并且具有在外表面的环周上伸展的环绕的换挡轮廓，所述方法具有以下方法步骤：
-将换挡鼓(100)旋转到第一换挡状态(S1)中，所述第一换挡状态对应于变速器装置(18)的空挡位置，
-借助于所述电机(16)产生低的转速，由此在所述变速器装置(18)的至少两个换挡元件(K0，K2)上产生转速差，
-将所述换挡鼓(100)沿着第一旋转方向旋转到第二换挡状态(S2)中，其中第一换挡元件(K0)以所述转速差切换，使得所述电机(16)突然制动到零，其中产生所述电机(16)的转速信号，并且将所述转速信号与作为虚拟的端部止挡件的第一参考位置/旋转角度相关联，
-将所述换挡鼓(100)转回到所述第一换挡状态(S1)中，
-借助于所述电机(16)产生低的转速，由此在所述变速器装置(18)的至少两个换挡元件(K0、K2)上产生转速差；以及
-将所述换挡鼓(100)沿着第二旋转方向旋转到另一换挡状态中，其中第二换挡元件(K2)以所述转速差切换，使得使所述电机(16)突然制动到零，其中产生所述电机(16)的转速信号，并且将所述转速信号与作为虚拟的端部止挡件的第二参考位置/旋转角度相关联。
2.根据权利要求1所述的用于混合动力总成(10)中的换挡鼓(100)的学习的方法，其特征在于，经由所述第一换挡元件(K0)在内燃机(12)和变速器输入轴(26)之间建立可切换的连接并且所述换挡元件(K0)能够切换到以下换挡位置中：
-空挡位置，在所述空挡位置中在内燃机(12)和变速器输入轴(26)之间不建立连接，
-换挡位置，在所述换挡位置中，所述内燃机(12)与所述变速器输入轴(26)连接。
3.根据权利要求2所述的用于混合动力总成(10)中的换挡鼓(100)的学习的方法，其特征在于，所述第二换挡元件(K2)与形成所述第二挡位的第三轮组(56)相关联，所述第三轮组包括支承在所述变速器输出轴(34)上的活动轮(60)，所述活动轮能够借助于所述第二换挡元件(K2)切换到以下换挡位置中：
-空挡位置，在所述空挡位置中，所述活动轮(60)可旋转地支承在所述输出轴(34)上，
-换挡位置，在所述换挡位置中，所述第二换挡元件(K2)切换到轴向移置的位置中，由此在活动轮(60)和变速器输出轴(34)之间建立抗扭的连接，由此所述变速器输入轴(26)能够经由所述第三轮组(56)与所述变速器输出轴(34)连接，并且能够实现另一任选的扭矩传输路径。
4.根据上述权利要求中任一项所述的用于混合动力总成(10)中的换挡鼓(100)的学习的方法，其特征在于，在所述换挡鼓(100)沿着第一旋转方向旋转360度时，借助于换挡轮廓能够按照以下给出的顺序在环周上分布式地切换4种换挡状态：
-换挡状态1(S1)：第一和第二换挡元件(K0和K2)处于空挡位置中，
-换挡状态2(S2)：第一换挡元件(K0)处于第二换挡位置中(内燃机与变速器输入轴26耦联)并且第二换挡元件(K2)处于空挡位置中，
-换挡状态3(S3)：第一换挡元件(K0)处于第二换挡位置中并且第二换挡元件(K2)处于第二换挡位置中，
-换挡状态4(S4)：第一换挡元件(K0)处于空挡位置中并且第二换挡元件(K2)处于第二换挡位置中。
CN202180027417.5A 2020-04-06 2021-03-31 在混合动力总成中换挡鼓的学习的方法 Pending CN115397688A (zh)

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