CN108340910B - 用于运行用于机动车的动力系统的方法以及相应的动力系统 - Google Patents

用于运行用于机动车的动力系统的方法以及相应的动力系统 Download PDF

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CN108340910B
CN108340910B CN201810060330.8A CN201810060330A CN108340910B CN 108340910 B CN108340910 B CN 108340910B CN 201810060330 A CN201810060330 A CN 201810060330A CN 108340910 B CN108340910 B CN 108340910B
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rotational speed
combustion engine
internal combustion
shaft
clutch
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CN108340910A (zh
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M·施耐德
H·卡尔托梅特沙
B·布吕克尔
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Audi AG
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Audi AG
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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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Abstract

本发明涉及一种用于运行机动车的动力系统的方法，动力系统具有内燃机、电机及换档变速器，内燃机的驱动轴能借助于切换离合器与电机的电机轴耦合，电机轴(17)与换档变速器(11)的变速器输入轴(15)耦合，动力系统(2)的输出轴(5)与换档变速器(11)的变速器输出轴(10)耦合或能耦合，切换离合器(18)在第一切换状态中为使内燃机(3)与电机(4)脱耦而打开，在第二切换状态中为使内燃机(3)与电机(4)耦合而闭合。当在第一运行方式中从第一切换状态变换到第二切换状态中时，如果驱动轴(19)的转速梯度与电机轴(17)的转速梯度之间的差超过转速梯度阈值和/或转速梯度具有不同符号则使切换离合器(18)延迟闭合。此外，本发明还涉及一种机动车的动力系统。

Description

用于运行用于机动车的动力系统的方法以及相应的动力系统
技术领域
本发明涉及一种用于运行动力系统的方法，所述动力系统用于机动车，所述动力系统具有内燃机、电机以及换档变速器，其中，所述内燃机的驱动轴可借助于切换离合器与所述电机的电机轴耦合并且所述电机轴与所述换档变速器的变速器输入轴耦合，其中，所述动力系统的输出轴与所述换档变速器的变速器输出轴耦合或可耦合，其中，所述切换离合器在第一切换状态中为了使所述内燃机与所述电机脱耦而打开，并且在第二切换状态中为了使所述内燃机与所述电机耦合而闭合。此外，本发明还涉及一种动力系统。
背景技术
动力系统用于驱动机动车，即就此而言用于提供旨在驱动机动车的转矩。动力系统具有多个驱动单元，其中，驱动单元中的第一驱动单元构造成内燃机并且驱动单元中的第二驱动单元构造成电机。动力系统就此而言作为混合动力系统存在。附加于驱动单元，动力系统具有换档变速器，所述换档变速器又具有变速器输入轴和变速器输出轴。借助于换档变速器可在变速器输入轴与变速器输出轴之间调整不同的传动比或者说调整从多个不同传动比选择的传动比。
内燃机具有驱动轴，所述驱动轴例如相应于内燃机的曲轴或与所述曲轴耦合，优选刚性地和/或持久地耦合。而电机具有电机轴，所述电机轴又与电机的转子耦合，优选也刚性地和/或持久地耦合。内燃机的驱动轴和电机的电机轴可借助于切换离合器耦合。这意味着，在切换离合器的第一切换状态中驱动轴与电机轴耦合，优选刚性地耦合，即无相对转动地或者说无滑转地耦合。为此，可在第一切换状态中在切换离合器被相应构造、例如构造成片式离合器的情况下设置有切换离合器的离合器过压，由此，在动力系统运行期间通常产生的转矩下不产生切换离合器的离合器滑转。
而在第二切换状态中，切换离合器至少部分地、尤其是完全地打开。即优选在第二切换状态中驱动轴与电机轴完全脱耦。电机的电机轴与换档变速器的变速器输入轴耦合，优选刚性地和/或持久地耦合，或至少可耦合。换档变速器的变速器输出轴又与动力系统的输出轴耦合，尤其是刚性地和/或持久地耦合，和/或至少可耦合。
对于动力系统的输出轴应理解为这样的轴，动力系统在所述轴上提供可用于驱动机动车的驱动转矩。就此而言，输出轴例如与机动车的车轮桥或机动车的至少一个车轮耦合，尤其是刚性地和/或持久地耦合，或至少可耦合。例如电机轴在电机的一侧连接在切换离合器上并且在电机的另一侧连接在变速器输入轴上。电机可与变速器输入轴同轴线地布置。但也可实现电机的其它布置。
发明内容
本发明的目的在于，提出一种用于运行用于机动车的动力系统的方法，所述方法相对于公知方法具有优点，尤其是可实现内燃机可靠且舒适地与电机耦合，优选在内燃机启动期间。
根据本发明，这通过具有本发明特征的方法来实现。在此提出，当在第一运行方式中从第一切换状态变换到第二切换状态中时，如果驱动轴的转速梯度与电机轴的转速梯度之间的差超过转速梯度阈值和/或转速梯度具有不同符号，则使切换离合器的闭合延迟。对于转速梯度应理解为转速关于时间的梯度。在此，在转速增大时存在正的符号，在转速减小时存在负的符号。
在从第一切换状态变换到第二切换状态中时，要将内燃机与电机耦合，即从脱耦的状态转移到至少部分耦合的状态、但尤其是刚性地耦合的状态中。在变换开始时，内燃机与电机相应地是脱耦的，即完全脱耦的。而在变换之后，内燃机与电机耦合。相应地，在变换期间需要闭合切换离合器，以便实现内燃机与电机之间的耦合。
但当符合至少一个确定的条件时，将切换离合器的这种闭合延迟或者说推迟。这种确定的条件例如可以是，转速梯度之间、即驱动轴的转速梯度与电机轴的转速梯度之间的差超过转速梯度阈值，即大于所述转速梯度阈值。另一个条件是，转速梯度、即驱动轴的转速梯度和电机轴的转速梯度具有不同符号。如果满足所述条件中的刚好一个或至少一个，则将闭合延迟，即暂时不执行切换离合器的闭合。不言而喻也可提出，仅当满足所述条件中的多个时才将闭合延迟。
例如在从第一切换状态变换到第二切换状态中时提出，将内燃机或者说驱动轴的转速适配于电机的转速或者说电机轴的转速并且接着将切换离合器闭合。但即使转速彼此一致或转速至少近似彼此一致，当同时转速梯度过强烈地彼此偏离或者说具有不同符号时，切换离合器的闭合可能对于机动车的乘员或者说驾驶员显得不舒适。最后所述情况例如可能当驱动轴的转速提高并且同时电机轴的转速减小时出现。驱动轴的转速提高以及电机轴的转速减小现在完全可使得驱动轴和电机轴的转速彼此一致。
但如果现在将切换离合器闭合，则尽管转速彼此一致仍必须首先使转速梯度彼此适配。这可在转速梯度彼此偏差过大时导致可明显察觉的转速变化。出于此原因首先提出，将切换离合器的闭合延迟，即不执行。尤其是在延迟期间将离合器的当前存在的切换状态保持恒定，尤其是将切换离合器保持在第一切换状态中，即不从第一切换状态中置出。
在本发明的另一个构型的范围内提出，在启动内燃机期间执行从第一切换状态到第二切换状态的变换。对于启动内燃机应理解为，将所述内燃机从小于最低转速和/或怠速转速的转速置于最低转速或怠速转速。对于最低转速优选应理解为内燃机的这样的转速，从所述转速起所述内燃机可自动地即在无外部转矩影响的情况下自动地在点燃运行下提高其转速。而怠速转速是内燃机的这样的转速，当内燃机不应为在输出轴上提供驱动转矩做贡献时通常在所述内燃机上调整所述转速。怠速转速在此通常高于最低转速并且优选这样选择，使得存在内燃机的尽可能平稳且低噪声的运行。
内燃机的启动不仅可在冷启动的范围内而且可在热启动或重新启动的范围内进行。内燃机的启动也可从任意初始转速出发来进行，例如从为零的初始转速出发，即从内燃机静止出发来进行。内燃机的启动不言而喻也可从不同于零的初始转速出发来进行。尤其是如果启动相对于直接在该启动之前的内燃机关闭以这样短的时间间隔来进行，使得内燃机仍未完全静止，则情况即如此。
在内燃机启动期间，内燃机的转速提高，驱动轴的转速梯度因此大于零。现在例如当电机的转速减小与内燃机的启动重合、即同时发生时执行切换离合器的闭合的延迟。在此情况下，转速梯度具有不同符号，由此，在转速彼此一致时通常也不可舒适地闭合切换离合器。
本发明的一个扩展构型提出，在从第一切换状态变换到第二切换状态中期间借助于换档变速器执行从初始档位到目标档位的档位转换。初始档位和目标档位具有不同的传动比，由此，在变速器输出轴与变速器输入轴并且因此电机的电机轴之间在档位转换之前与在档位转换之后相比存在不同传动比。
现在如果从第一切换状态到第二切换状态的变换与所述档位转换重合，则尽管机动车的行驶速度基本上保持不变并且因此变速器输出轴的转速基本上保持不变但仍可存在变速器输入轴的转速的突然变化以及相应地存在电机轴的大的转速梯度。在此情况下应将切换离合器的闭合暂时延迟。此外，尤其是当档位转换与内燃机的启动重合并且档位转换在降档、即借助于换档变速器挂入的行驶档位降低的范围内进行，由此初始档位大于目标档位时，情况即如此。在此情况下变速器输入轴以及相应地电机轴的转速增大。
本发明的另一个构型提出，在延迟切换离合器的闭合的情况下在内燃机上调整由变速器输出轴的转速和目标档位求得的给定转速。即首先确定变速器输出轴的转速和目标档位。接着由这些参量确定给定转速。给定转速在此优选相应于变速器输入轴的转速，所述转速在存在变速器输出轴的转速时在挂入目标档位之后得到。给定转速相应地是由变速器输出轴的转速和目标档位的传动比得到的转速。
在内燃机上调整给定转速并且将内燃机的实际转速控制或调节到给定转速。这尤其是这样来进行，使得内燃机在借助于换档变速器进行档位转换结束之后已经在相应于给定转速的实际转速下运行。因此预见性地求得变速器输入轴以及相应地电机轴的可能在档位转换之后存在的转速并且内燃机通过调整相应的给定转速已经为切换离合器的闭合做好准备。
本发明的另一个构型提出，当实际转速相应于给定转速和/或差小于或等于转速梯度阈值和/或转速梯度具有相同符号时，结束延迟并且将切换离合器闭合。就此而言当符合所述条件中的刚好一个或至少一个时结束延迟。但优选必须符合所述条件中的多个，以便结束延迟。尤其是提出，总是实际转速与给定转速必须彼此一致并且符合另外的条件中的至少一个。
本发明的一个优选构型提出，当在第二运行方式中从第一切换状态变换到第二切换状态中时，立即执行切换离合器的闭合，尤其是与转速梯度之间的差和/或符号无关地执行。切换离合器的闭合的延迟因此仅在第一运行方式中、但不在第二运行方式中执行。在第二运行方式中，当变换时立即、即无延迟地执行切换离合器的闭合。切换离合器的闭合因此与转速梯度之间的差或者说转速梯度的符号无关。
本发明的另一个优选实施形式提出，如果在动力系统上调整的预给定转矩超过转矩阈值和/或驱动轴的转速与电机轴的转速之间的转速差小于转速差阈值和/或换档变速器的变矩器的变矩器滑转率未知和/或速度信号无效，则从第一运行方式转换到第二运行方式中。例如提出，通常执行第一运行方式并且仅当符合所述条件中的刚好一个、至少一个或多个或者说全部时转换到第二运行方式中。换言之，如果符合所述条件的一个选择，则从第一运行方式转换到第二运行方式中。但如果不符合选择，则从第二运行方式变回到第一运行方式中。
预给定转矩例如是由机动车的驾驶员和/或驾驶员辅助装置预给定的转矩。例如在动力系统上调整的给定转矩相应于预给定转矩。如果预给定转矩超过转矩阈值，即如果存在特别高的转矩要求，则有利的是，立即执行内燃机与电机的耦合。附加地或作为替换方案可检验，是否转速阈值被转速差低于。转速差阈值原则上可任意确定，尤其是这样选择转速差阈值，使得在所述转速差阈值被转速差低于时可将内燃机与电机舒适地耦合。另外可检验，变矩器的变矩器滑转率是已知还是未知。尤其是当变矩器的变矩器跨接离合器打开，由此不可计算变矩器中出现的滑转率时，存在未知的变矩器滑转率。另外可检验，速度信号是有效还是无效。速度信号例如是与转速或行驶速度相对应的信号。
最后，在本发明的另一个实施形式的范围内可提出，在第二运行方式中在借助于换档变速器执行档位转换之前使切换离合器闭合。如果从第一切换状态到第二切换状态的变换与档位转换重叠，则在第二运行方式中尽可能快速地闭合切换离合器，即在执行档位转换之前。以此方式和方法可在输出轴上特别快速地提供由内燃机产生的转矩。
本发明的另一个构型提出，内燃机的启动通过借助于启动机拖曳内燃机和/或通过仅仅部分地闭合切换离合器来执行。内燃机的启动在此可分别或者在点火的情况下或者在不点火的情况下来执行。在每种情况下，内燃机被拖曳。这可借助于启动机、例如带式启动机或通过仅仅部分地闭合切换离合器来实现。在启动内燃机的范围内仅仅部分地闭合切换离合器在此不同于在从第一切换状态变换到第二切换状态中时闭合切换离合器。在变换时执行的闭合在很大程度上作为用于拖曳内燃机的闭合来进行，尤其是在第一种情况下比在后一种情况中调整更高的离合器转矩。
本发明的扩展构型提出，用于启动内燃机的在切换离合器上待调整的离合器给定转矩由温度和/或内燃机的尤其是在内燃机静止时存在的曲轴位置求得。离合器给定转矩是应借助于切换离合器传递的转矩。实际上通过切换离合器传递的离合器实际转矩优选调整到离合器给定转矩，尤其是控制性地和/或调节性地。
离合器给定转矩现在借助于温度和/或内燃机的曲轴位置来确定。例如温度越低，则离合器给定转矩越高。作为温度例如考虑内燃机的内燃机温度、例如润滑剂温度。附加地或作为替换方案考虑在尤其是在内燃机静止时进行启动之前存在的曲轴位置。
曲轴位置例如描述这样的转动角度，内燃机的曲轴必须转过该转动角度，直到对于首先进行压缩和/或燃料喷射的缸达到上止点。在转动角度小时比在转动角度大时必然压缩少的混合物，因为待点火的第一缸紧处于其上止点之前。相应地，转动角度越小，则离合器给定转矩选择得越小。
本发明的另一个优选构型提出，如果内燃机的转速在启动开始时大于零或在关闭之后的时间间隔低于预给定时间间隔，则向上校正离合器给定转矩，其中，时间间隔低于预给定时间间隔越多，则离合器给定转矩选择得越大。前文已经描述，内燃机的启动可从任意的初始转速出发来进行。如果内燃机的在启动之前的关闭恰恰经过短的时间，则转速大于零。相应地，在应进行压缩的下一个缸中已经存在预压缩的混合物。
这使得必须提高离合器给定转矩。例如离合器给定转矩的提高在内燃机的确定的转速范围内进行。所述转速范围作为下极限例如具有大于零的转速，尤其是无穷小地大于零的转速，在该转速下内燃机在其惯性下刚好仍处于运动中。作为上极限，转速范围可具有小于最低转速和/或怠速转速的转速。尤其是转速取值为最低转速的至多75％、至多50％、至多40％、至多30％或至多25％。如果内燃机的转速超过转速范围，即如果处于所述转速范围之上，则可取消离合器给定转矩的提高，因为内燃机的仍旋转的质量支持启动。
如果在内燃机的惯性下节气门是打开的，则内燃机的缸仍被供应以完全的空气填充。相应地，预压缩的空气填充存在于待压缩的第一缸中。所述提高的填充在内燃机停止之后缓慢地通过缸的不密封性、例如缸密封装置的不密封性而减低。在待压缩的第一缸中提高的填充应在计算离合器给定转矩时予以考虑。如果时间间隔低于预给定时间间隔，则相应地考虑在启动之前的关闭之后的时间间隔并且向上校正离合器给定转矩。在此提出，时间间隔低于预给定时间间隔越多，则离合器给定转矩选择得越大。例如离合器给定转矩在内燃机关闭之后的时间上呈线性减小。
本发明的另一个实施形式提出，将可借助于电机提供的驱动转矩限制到由电机的最大驱动转矩和转矩储备求得的转矩极限值。最大驱动转矩相应于可借助于电机提供的最大转矩。最大驱动转矩在此优选相应于额定转矩，在所述额定转矩下电机可持久地且连贯地运行。
由最大驱动转矩和转矩储备确定转矩极限值。转矩极限值在此相应于最大驱动转矩减去转矩储备。通过设置转矩储备而保证，总是可借助于电机可靠地启动内燃机。相应地，将可由电机产生的驱动转矩限制到转矩极限值。
在本发明的另一个有利实施形式的范围内提出，转矩储备由启动内燃机所需的拖曳转矩求得。拖曳转矩相应于拖曳内燃机、尤其是拖曳到最低转速和/或怠速转速所需的转矩。转矩储备现在例如等于拖曳转矩。
本发明的另一个构型提出，如果电机的实际转矩小于最大驱动转矩减去拖曳转矩，则使转矩储备等于拖曳转矩，否则等于最大驱动转矩减去实际转矩并且接着提高。由此可对于机动车的驾驶员不可察觉地提供转矩储备，即其方式是首先这样选择转矩储备，使得所述转矩储备不影响实际转矩并且接着缓慢提高，由此电机的实际转矩缓慢下降。
此外，本发明还涉及一种动力系统，用于机动车，尤其是用于执行上文所述的方法，所述动力系统具有内燃机、电机以及换档变速器，其中，内燃机的驱动轴可借助于切换离合器与电机的电机轴耦合并且电机轴与换档变速器的变速器输入轴耦合，其中，动力系统的输出轴与换档变速器的变速器输出轴耦合或可耦合，其中，切换离合器在第一切换状态中为了使内燃机与电机脱耦而打开，并且在第二切换状态中为了使内燃机与电机耦合而闭合。
在此提出，动力系统被构造用于，当在第一运行方式中从第一切换状态变换到第二切换状态中时，如果驱动轴的转速梯度与电机轴的转速梯度之间的差超过转速梯度阈值和/或转速梯度具有不同符号则将切换离合器的闭合延迟。
已经指明了动力系统的这种处理方式以及相应构型的优点。不仅动力系统而且用于运行动力系统的方法可根据上述实施形式来扩展构造，由此就此而言参见上述实施形式。
附图说明
下面借助于附图中所示实施例详细描述本发明，而不限制本发明。在此，
图1示出了未进一步示出的机动车的动力总成系统1的示意性视图。
具体实施方式
动力总成系统1具有动力系统2，所述动力系统又具有内燃机3、电机以及输出轴5。动力系统2用于驱动机动车的至少一个车轮桥6，所述车轮桥由两个分桥7和8组成，所述分桥通过差速器9与动力系统2的输出轴5耦合。输出轴5与动力系统2的换档变速器11的变速器输出轴10耦合，尤其是可刚性地和/或持久地和/或借助于可选择的切换离合器12耦合。
换档变速器11例如可具有变矩器13，所述变矩器可具有变矩器跨接离合器14。换档变速器11具有变速器输入轴15，所述变速器输入轴优选持久地与变矩器13耦合。变速器输入轴15可直接地或如在此所示通过减振装置16、例如扭振减振器与电机4的电机轴17耦合，尤其是刚性地和/或持久地耦合。电机4可相对于变速器输入轴15和/或变速器输出轴10同轴线地布置。
内燃机3与电机4之间的作用连接可借助于切换离合器18来调整。切换离合器18在此处于内燃机3的驱动轴19与电机4的电机轴17之间。此外，在内燃机3与切换离合器18之间的作用连接中可以可选地设置有另外的减振装置20。减振装置20优选构造成双质量飞轮。
在切换离合器18的第一切换状态中，内燃机3与电机4脱耦。而在第二切换状态中，所述内燃机与所述电机耦合。相应地，切换离合器18在第一切换状态中打开，尤其是完全地打开，在第二切换状态中至少部分地、优选完全地闭合。对于完全地闭合可理解为切换离合器18在具有或不具有离合器过压的情况下闭合。
如果要从第一切换状态变换到第二切换状态中，即如果内燃机3与电机4暂时是彼此脱耦的，则当驱动轴19的转速梯度与电机轴17的转速梯度之间的差超过转速梯度阈值和/或转速梯度具有不同符号时将切换离合器18的为此所需的闭合延迟。这特别优选当在启动内燃机3期间执行所述变换并且同时借助于换档变速器11进行档位转换、即从初始档位转换到目标档位时进行。通过这种处理方式，可使内燃机3与电机4特别舒适地耦合。

Claims (6)

1.一种用于运行机动车的动力系统(2)的方法，所述动力系统具有内燃机(3)、电机(4)以及换档变速器(11)，所述内燃机(3)的驱动轴(19)能借助于切换离合器(18)与所述电机(4)的电机轴(17)耦合，电机轴(17)与换档变速器(11)的变速器输入轴(15)耦合，动力系统(2)的输出轴(5)与换档变速器(11)的变速器输出轴(10)耦合或能耦合，切换离合器(18)在第一切换状态中为了使内燃机(3)与电机(4)脱耦而打开，而在第二切换状态中为了使内燃机(3)与电机(4)耦合而闭合，当在第一运行方式中从第一切换状态变换到第二切换状态时，如果驱动轴(19)的转速梯度与电机轴(17)的转速梯度之间的差超过转速梯度阈值和/或驱动轴(19)的转速梯度与电机轴(17)的转速梯度具有不同符号，则使切换离合器(18)延迟闭合，其特征在于：当在第二运行方式中从第一切换状态变换到第二切换状态中时，立即执行切换离合器(18)的闭合，如果在所述动力系统(2)上调整出的预给定转矩超过转矩阈值和/或驱动轴(19)的转速与电机轴(17)的转速之间的转速差小于转速差阈值和/或换档变速器(11)的变矩器(13)的变矩器滑转率未知和/或速度信号无效，则从第一运行方式转换到第二运行方式中，在第一运行方式中在从第一切换状态变换到第二切换状态期间借助于换档变速器(11)执行从初始档位到目标档位的档位转换，在第二运行方式中在切换离合器(18)闭合之后借助于换档变速器(11)执行从初始档位到目标档位的档位转换。
2.根据权利要求1所述的方法，其特征在于：在启动内燃机(3)期间执行从第一切换状态到第二切换状态的变换。
3.根据权利要求1或2所述的方法，其特征在于：在使切换离合器(18)延迟闭合的情况下，在内燃机(3)上调整出由变速器输出轴(10)的转速和目标档位求得的给定转速。
4.根据权利要求1或2所述的方法，其特征在于：所述延迟一直被执行到内燃机(3)的实际转速与给定转速相当和/或在驱动轴(19)的转速梯度与电机轴(17)的转速梯度之间的差小于或等于转速梯度阈值和/或驱动轴(19)的转速梯度与电机轴(17)的转速梯度具有相同符号。
5.根据权利要求1或2所述的方法，其特征在于：当实际转速与给定转速相当和/或在驱动轴(19)的转速梯度与电机轴(17)的转速梯度之间的差小于或等于转速梯度阈值和/或驱动轴(19)的转速梯度与电机轴(17)的转速梯度具有相同符号时，结束所述延迟并且将切换离合器(18)闭合。
6.一种机动车的动力系统(2)，该动力系统用于执行根据权利要求1-5中任一项所述的方法，所述动力系统具有内燃机(3)、电机(4)以及换档变速器(11)，所述内燃机(3)的驱动轴(19)能借助于切换离合器(18)与电机(4)的电机轴(17)耦合，电机轴(17)与换档变速器(11)的变速器输入轴(15)耦合，动力系统(2)的输出轴(5)与换档变速器(11)的变速器输出轴(10)耦合或能耦合，切换离合器(18)在第一切换状态中为了使内燃机(3)与电机(4)脱耦而打开，而在第二切换状态中为了使内燃机(3)与电机(4)耦合而闭合，所述动力系统(2)被构造用于，当在第一运行方式中从第一切换状态变换到第二切换状态中时，如果驱动轴(19)的转速梯度与电机轴(17)的转速梯度之间的差超过转速梯度阈值和/或驱动轴(19)的转速梯度与电机轴(17)的转速梯度具有不同符号，则使切换离合器(18)延迟闭合，其特征在于：当在第二运行方式中从第一切换状态变换到第二切换状态中时，立即执行切换离合器(18)的闭合，如果在所述动力系统(2)上调整出的预给定转矩超过转矩阈值和/或驱动轴(19)的转速与电机轴(17)的转速之间的转速差小于转速差阈值和/或换档变速器(11)的变矩器(13)的变矩器滑转率未知和/或速度信号无效，则从第一运行方式转换到第二运行方式中，在第一运行方式中在从第一切换状态变换到第二切换状态期间借助于换档变速器(11)执行从初始档位到目标档位的档位转换，在第二运行方式中在切换离合器(18)闭合之后借助于换档变速器(11)执行从初始档位到目标档位的档位转换。
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