CN1806135A - 行星齿轮变速器 - Google Patents
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Abstract
行星齿轮变速器(8)包括齿圈(24),太阳轮(52)和行星齿轮支架(10),在行星齿轮支架上放置了至少一个行星齿轮(20),该行星齿轮变速器具有带接合套(66)的换档装置,该换档装置在一个换档位置实现驱动行星齿轮变速器(8)的轴(44)和行星齿轮变速器(8)输出轴(12)之间的直接连接,在另一个换档位置实现驱动轴(44)和行星齿轮变速器(8)输出轴(12)之间的转速改变。行星齿轮(20)支承在行星齿轮支架(10)上,使得在从一个换档位置向各个其它换档位置转换时,行星齿轮支架(10)上的行星齿轮(20)可轴向移动。
Description
本发明涉及根据权利要求1前序部分的行星齿轮变速器。
档位多的商用汽车通常具有连接在主变速器档位后面的分段式副变速器。通过能够将主变速器的所有档位与分段式副变速器的各个档位一起使用,并且在分段式副变速器的至少一个档位提高或者降低主变速器档位的传动比,可以用分段式副变速器扩大主变速器的总传动比。
例如从DE 41 21 709 A1中已知一种汽车用的分段式副变速器。用这种连接在主变速器之后的行星齿轮变速器能够在其主变速器档位范围内、以两个不同的速度范围驱动汽车。在分段式副变速器的第一减速档位,行星齿轮变速器的齿圈通过换档离合器连接在变速器外壳上,从而分段式副变速器的输出轴具有比主变速器输出轴低的转速。在第二档位实现从主变速器输出轴向分段式副变速器输出轴的直接档传动,其中通过换档离合器在主变速器输出轴和分段式副变速器输出轴之间建立直接连接。换档装置非常昂贵。
DE 198 51 895 A1描述了另一种作为行星齿轮变速器的分段式副变速器。在此行星齿轮变速器的齿圈与变速器外壳不可相对转动地连接。行星齿轮变速器的太阳轮与主变速器的输出轴同轴,并相对主变速器输出轴可自由转动。为在主变速器输出轴和分段式副变速器输出轴之间产生减速比,可将太阳轮与主变速器输出轴不可相对转动地连接。该行星齿轮变速器也是昂贵的并且在单个构件支承情况下有问题。
本发明的任务在于改善行星齿轮变速器和特别是构件支承。
该任务通过具有权利要求1特征的行星齿轮变速器解决。从属权利要求的主题给出了设计方案。
行星齿轮变速器包括齿圈,太阳轮和行星齿轮支架,在行星齿轮支架上放置了至少一个行星齿轮,该行星齿轮变速器具有带接合套的换档装置,该换档装置在一个换档位置实现驱动行星齿轮变速器的轴和行星齿轮变速器输出轴之间的直接连接。在另一个换档位置,换档装置实现驱动轴和行星齿轮变速器输出轴之间的转速改变。行星齿轮支承在行星齿轮支架上,使得在从一个换档位置向各个其它换档位置转换时,行星齿轮支架上的行星齿轮可轴向移动。通常在这种行星齿轮变速器中在圆周上分布三个或五个行星齿轮。
最好行星齿轮相对齿圈和太阳轮轴向固定,从而行星齿轮的轴向移动能够导致齿圈和太阳轮同时轴向移动。
在特别有利的实施形式情况下,在行星齿轮从一个换档位置向各个其它换档位置移动时,行星齿轮通过的移动行程比移动行星齿轮的接合套通过的移动行程小。
在一个有利的设计方案情况下,接合套适合轴向移动太阳轮并从而轴向移动行星齿轮支架上的行星齿轮。
在一个结构形式中,太阳轮带有与接合套共同起作用的压紧螺栓,而在另一个结构中,接合套和太阳轮设计成一体。
最好齿圈和太阳轮都具有贴靠在行星齿轮上的压力环。
在一个设计方案中,换档装置具有空档位置,该空档位置位于两个换档位置之间,在该空档位置行星齿轮变速器的输出轴不被驱动。
在另一个优选的结构形式中,行星齿轮支架上的行星齿轮支承在滚子轴承中。在此滚子轴承最好包括多排轴承。太阳轮和行星齿轮变速器驱动轴的相对支承同样构成了一种设计方案。
特别有利的是,行星齿轮变速器是汽车变速器的分段式副变速器,其在传递扭矩的传动系中连接在主变速器上,并且在该分段式副变速器情况下,主变速器的输出轴是行星齿轮变速器的驱动轴。
同样作为特别有利的结构形式,主变速器包括两个中间轴和一个在中间轴之间浮动支承的主轴,该主轴作为主变速器的输出轴构成行星齿轮变速器的输入轴,并且在其端部支承在行星齿轮变速器的太阳轮内。
有利的是主轴端部的轴承包括带有开槽侧面的轴颈。
下面借助附图更详细地解释本发明。其中:
图1为处于空档位置的、带有第一换档装置的行星齿轮变速器;
图2为处于第一换档位置的、根据图1的换档装置;
图3为处于第二换档位置的、根据图1的换档装置;
图4为处于空档位置的、带有第二换档装置的行星齿轮变速器。
汽车用的变速器2在变速器外壳4内具有主变速器6和行星齿轮变速器8形式的、连接在主变速器6上的分段式副变速器。行星齿轮变速器8包括行星齿轮支架10,该行星齿轮支架与变速器2的输出轴12作为共同的构件。在输出轴12上固定了输出法兰14,输出轴12在变速器外壳4内支承在轴承16内。行星齿轮支架10具有多个在其圆周上分布的行星柱销18,这里仅示出了其中的一个。在行星柱销18上,行星齿轮20支承在滚子轴承22内。通常在行星齿轮支架10的圆周上分布布置三个或五个行星齿轮20。滚子轴承22由两排的圆柱滚子轴承或者滚针轴承构成。行星齿轮20在外侧被齿圈24包围,该齿圈具有换档齿部26,该换档齿部可啮合在支承板30上的换档齿部28内。支承板30在变速器外壳4内被不可转动地支承。在此支承板30可铸入在变速器外壳4内,或者作为单独的板夹在变速器外壳4的单个零件之间。轴32用于可能的驱动动力输出装置并支承在变速器外壳4内的轴承34内。
行星齿轮支架10在行星齿轮变速器8的与输出轴12相对的一侧上具有凸起36,行星齿轮支架10在变速器外壳4内通过滚子轴承38支承在该凸起上。主变速器6的中间轴40也通过轴承42支承在变速器外壳4内。主变速器6的主轴44在其端部支承倒档的齿轮46。齿轮46以微小的径向间隙布置在主轴44上,这对于向两个中间轴分流功率的变速器来说是常见的。在主轴44的端部设置了轴颈45,该轴颈具有开槽的侧面。轴颈45包括被弹簧50径向向外压的压紧螺栓48。在此压紧螺栓穿过行星齿轮变速器8的太阳轮52,该太阳轮布置在主轴44的轴颈45上,其中主轴44支承在太阳轮52内。在太阳轮52和输出轴12或者行星齿轮支架10之间布置了带有盘的套筒54,该盘允许太阳轮52贴靠在输出轴12上并彼此相对滑动,其中太阳轮52和输出轴12的转速可以是不同的。
在太阳轮52上布置了两个压力环56和58,它们防止行星齿轮20相对太阳轮52的轴向运动,但允许行星齿轮20贴靠在压力环上,以接收行星齿轮变速器8的斜齿导致的轴向力。两个另外的压力环60和62布置在齿圈24的径向内部,并同样允许行星齿轮20贴靠。两个压力环60和62防止行星齿轮20相对齿圈24的轴向运动。通过布置压力环56,58,60,62,太阳轮52、行星齿轮20和齿圈24作为一个组件轴向移动,其中通过太阳轮52导入的轴向运动通过行星齿轮20的传递导致齿圈24同向的轴向运动。
在图1中,压紧螺栓48和接合套66内的凹口64共同起作用,并在此接合在凹口64内。由此将接合套66保持在空档位置。接合套66具有第一内齿部68,该内齿部啮合在太阳轮52上的外齿部70内并在接合套66和太阳轮52之间建立不可转动的连接(图2)。为在接合套66和主轴44之间建立不可转动的连接,接合套66具有第二内齿部72,该内齿部啮合在主轴44上的外齿部74内。
为建立主轴44与行星齿轮支架10的可选择的不可转动的连接,以在转速不变的情况下建立主变速器6与输出轴12的直接连接,接合套66具有换档齿部76,该换档齿部可啮合在行星齿轮支架10的凸起36上的换档齿部78内。
图1示出了处于空档位置的行星齿轮变速器8。换档齿部26和28,换档齿部76和78都没有相互啮合。压紧螺栓48啮合在接合套66上的凹口64内。太阳轮52在附图平面内处于其右位置。行星齿轮20在行星柱销18上仅支承在滚子轴承22的一个圆柱滚子轴承上。行星齿轮变速器8空载,所以造成较小损失的简单轴承就足够了。
如果现在这里未示出的致动器向左移动接合套66,则接合套66通过环80在附图平面内同样向左拖拉太阳轮52。在图2中示出了这种情况。行星齿轮20通过太阳轮52上的压力环56和58被一起拖拉,并又通过压力环60和62向左拖拉齿圈24。由此两个换档齿部26和28相互啮合在一起,从而齿圈24被不可转动地固定。因此,行星齿轮支架10以已知的方式相对主轴44以更慢的传动比转动。现在行星齿轮变速器8负载运行,因为现在全部扭矩都通过行星齿轮20传递。为此,行星齿轮20在行星柱销18上的轴承必须被支撑。在通过太阳轮52向左移动行星齿轮20的情况下,行星齿轮也被拖拉到滚子轴承22的第二圆柱滚子轴承上,从而现在可以使用明显增大的滚子轴承22的支承能力。代替多个圆柱滚子轴承,还可以考虑多排轴承,例如两排的滚针轴承。
如果致动器现在使接合套66从图2中所示的换档位置向右移动,则接合套66通过凹口64和压紧螺栓48在附图平面内同样向右移动太阳轮52。行星齿轮20通过太阳轮52上的压力环56和58被一起移动,并又通过压力环60和62向右移动齿圈24,直到达到根据图1的空档位置并且太阳轮52以套筒54贴靠在行星齿轮支架10上为止。
如果从根据图1的空档位置向右移动接合套66,则凹口64压缩顶在压紧螺栓48上的弹簧50,并且接合套66继续向右移动,而在此太阳轮52没有被轴向移动。由此太阳轮52和从而行星齿轮20经过的移动行程比移动太阳轮52和从而移动行星齿轮20的接合套66经过的移动行程小。接合套66上的换档齿部76啮合在行星齿轮支架10的凸起36上的换档齿部78内,由此在主轴44和输出轴12之间实现了不可转动的连接。这在图3中示出。由此行星齿轮支架10以已知方式以相同的转速相对主轴44转动。现在行星齿轮变速器8空载运行,因为全部的扭矩通过行星齿轮支架10传递。不必加强行星齿轮20在行星柱销18上的支承,从而行星齿轮20如在空档位置一样,仅支承在滚子轴承22的一个圆柱滚子轴承上。
图4示出了改变了的接合套66实施形式。这里接合套66与太阳轮是一体的。在该结构中,在向三个可能的换档位置轴向移动接合套66的情况下,太阳轮和从而行星齿轮20和齿圈24始终被一起移动。为此在行星齿轮变速器8内必须有可使用的相应结构空间。
按照关于图2所述,达到慢的传动比。通过一体构成接合套66和太阳轮,取消了压力螺栓和凹口。如果致动器从用于慢传动比的换档位置向右移动接合套66,则接合套66在附图平面内同样向右移动与其一体的太阳轮。行星齿轮20通过太阳轮上的压力环56和58被一起移动,并又通过压力环60和62向右移动齿圈24,直到达到根据图4的空档位置为止。现在太阳轮没有贴靠在行星齿轮支架10上。
如果从根据图4的空档位置继续向右移动接合套66,则接合套66也继续向右轴向移动太阳轮。接合套66上的换档齿部76啮合在行星齿轮支架10的凸起36上的换档齿部78内,由此在主轴44和输出轴12之间建立了不可转动的连接。行星齿轮变速器8再次空载运行,因为全部的扭矩通过行星齿轮支架10传递。不必加强行星齿轮20在行星柱销18上的支承,从而行星齿轮20和在空档位置一样,仅支承在滚子轴承22的一个圆柱滚子轴承上。
为建立稳定的最终位置并发生不希望的相对滑动分离,齿部26,28和68到78备有后卷边。
通过根据本发明的结构,形成了用于行星齿轮变速器的用拨叉操纵的换档装置,该换档装置布置在变速器的主轴上。在直接连接的情况下,无负载地转换到副变速器的快传动比。分段式副变速器齿部的短换档行程导致行星柱销的弯曲力臂短。滚子轴承将行星齿轮可靠在支承在行星柱销上。
原则上根据本发明的换档装置即适用于带有中间轴的变速器,也适用于向多个中间轴分流功率的变速器。
附图标记
2 变速器
4 变速器外壳
6 主变速器
8 行星齿轮变速器
10 行星齿轮支架
12 输出轴
14 输出法兰
16 轴承
18 行星柱销
20 行星齿轮
22 滚子轴承
24 齿圈
26 换档齿部
28 换档齿部
30 支承板
32 轴
34 轴承
36 凸起
38 滚子轴承
40 中间轴
42 轴承
44 主轴
45 轴颈
46 齿轮
48 压紧螺栓
50 弹簧
52 太阳轮
54 套筒
56 压力环
58 压力环
60 压力环
62 压力环
64 凹口
66 接合套
68 内齿部
70 外齿部
72 内齿部
74 外齿部
76 换档齿部
78 换档齿部
80 环
Claims (14)
1.一种行星齿轮变速器(8),包括齿圈(24),太阳轮(52)和行星齿轮支架(10),在行星齿轮支架上放置了至少一个行星齿轮(20),该行星齿轮变速器具有带接合套(66)的换档装置,该换档装置在一个换档位置实现驱动行星齿轮变速器(8)的轴(44)和行星齿轮变速器(8)输出轴(12)之间的直接连接,在另一个换档位置实现驱动轴(44)和行星齿轮变速器(8)输出轴(12)之间的转速改变,其特征在于,行星齿轮(20)这样支承在行星齿轮支架(10)上,使得在从一个换档位置向各个其它换档位置转换时,行星齿轮支架(10)上的行星齿轮(20)可轴向移动。
2.根据权利要求1的行星齿轮变速器(8),其特征在于,行星齿轮(20)相对齿圈(24)和太阳轮(52)轴向固定,从而行星齿轮(20)的轴向移动能够导致齿圈(24)和太阳轮(52)同时轴向移动。
3.根据权利要求1或2的行星齿轮变速器(8),接合套(66)适合轴向移动太阳轮(52)并从而轴向移动行星齿轮支架(10)上的行星齿轮(20)。
4.根据权利要求1至3之一的行星齿轮变速器(8),其特征在于,在行星齿轮(20)从一个换档位置向各个其它换档位置移动时,行星齿轮(20)通过的移动行程比移动行星齿轮(20)的接合套(66)通过的移动行程小。
5.根据权利要求1至4之一的行星齿轮变速器(8),其特征在于,太阳轮(52)包括与接合套(66)共同起作用的压紧螺栓(48)。
6.根据权利要求1至3之一的行星齿轮变速器(8),其特征在于,接合套(66)和太阳轮是一体构成的。
7.根据权利要求1至6之一的行星齿轮变速器(8),其特征在于,齿圈(24)和太阳轮(52)都具有贴靠在行星齿轮(20)上的压力环(56,58,60,62)。
8.根据权利要求1至7之一的行星齿轮变速器(8),其特征在于,换档装置具有空档位置,该空档位置位于两个换档位置之间,在该空档位置行星齿轮变速器(8)的输出轴(12)不被驱动。
9.根据权利要求1至8之一的行星齿轮变速器(8),其特征在于,行星齿轮支架(10)上的行星齿轮(20)支承在滚子轴承(22)中。
10.根据权利要求9的行星齿轮变速器(8),其特征在于,滚子轴承(22)包括多排轴承。
11.根据权利要求1至10之一的行星齿轮变速器(8),其特征在于,太阳轮(52)和行星齿轮变速器(8)的驱动轴(44)相互支承。
12.根据权利要求1至11之一的行星齿轮变速器(8),其特征在于,主轴(44)端部的轴承包括带有开槽侧面的轴颈(45)。
13.根据权利要求1至12之一的行星齿轮变速器(8),其特征在于,行星齿轮变速器(8)是汽车变速器的分段式副变速器,其在传递扭矩的传动系中连接在主变速器(6)上,并且在该分段式副变速器情况下,主变速器(6)的输出轴(44)是行星齿轮变速器(8)的驱动轴。
14.根据权利要求1至8之一的行星齿轮变速器(8),其特征在于,主变速器(6)包括两个中间轴(40)和一个在中间轴(40)之间浮动支承的主轴(44),该主轴作为主变速器(6)的输出轴构成行星齿轮变速器(8)的驱动轴,并且在其端部(46)支承在行星齿轮变速器(8)的太阳轮(52)内。
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CN108291613A (zh) * | 2015-11-27 | 2018-07-17 | Zf 腓德烈斯哈芬股份公司 | 两档传动装置 |
CN109424704A (zh) * | 2017-08-30 | 2019-03-05 | 罗伯特·博世有限公司 | 尤其用于单轮驱动单元的传动机构 |
CN113710925A (zh) * | 2019-04-23 | 2021-11-26 | 采埃孚股份公司 | 可切换的行星齿轮变速器 |
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WO2004111493A1 (de) | 2004-12-23 |
DE10326677A1 (de) | 2005-01-20 |
US7278949B2 (en) | 2007-10-09 |
EP1633994A1 (de) | 2006-03-15 |
JP2006527345A (ja) | 2006-11-30 |
US20060258502A1 (en) | 2006-11-16 |
DE502004001915D1 (de) | 2006-12-14 |
BRPI0411425A (pt) | 2006-07-25 |
EP1633994B1 (de) | 2006-11-02 |
CN100432484C (zh) | 2008-11-12 |
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