CN1115016A - 具锥形帽定位销的同步器 - Google Patents
具锥形帽定位销的同步器 Download PDFInfo
- Publication number
- CN1115016A CN1115016A CN94120712A CN94120712A CN1115016A CN 1115016 A CN1115016 A CN 1115016A CN 94120712 A CN94120712 A CN 94120712A CN 94120712 A CN94120712 A CN 94120712A CN 1115016 A CN1115016 A CN 1115016A
- Authority
- CN
- China
- Prior art keywords
- flange
- axially
- friction
- axial
- pin
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 230000007246 mechanism Effects 0.000 claims abstract description 39
- 230000033001 locomotion Effects 0.000 claims abstract description 26
- 230000000694 effects Effects 0.000 claims description 8
- 210000000078 claw Anatomy 0.000 claims description 7
- 230000001360 synchronised effect Effects 0.000 claims description 6
- 238000006243 chemical reaction Methods 0.000 claims description 3
- 230000008878 coupling Effects 0.000 claims description 3
- 238000010168 coupling process Methods 0.000 claims description 3
- 238000005859 coupling reaction Methods 0.000 claims description 3
- 238000006073 displacement reaction Methods 0.000 claims 6
- 230000015572 biosynthetic process Effects 0.000 claims 1
- 230000002787 reinforcement Effects 0.000 description 13
- 244000161999 Acacia greggii Species 0.000 description 8
- 235000017771 Acacia greggii Nutrition 0.000 description 8
- 230000007935 neutral effect Effects 0.000 description 7
- 230000005540 biological transmission Effects 0.000 description 5
- 230000006872 improvement Effects 0.000 description 4
- 230000002708 enhancing effect Effects 0.000 description 3
- 239000003921 oil Substances 0.000 description 3
- 238000010008 shearing Methods 0.000 description 3
- 230000008859 change Effects 0.000 description 2
- 239000002783 friction material Substances 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000008569 process Effects 0.000 description 2
- 230000004044 response Effects 0.000 description 2
- 208000007038 Dens in Dente Diseases 0.000 description 1
- 244000287680 Garcinia dulcis Species 0.000 description 1
- 240000005373 Panax quinquefolius Species 0.000 description 1
- 235000003140 Panax quinquefolius Nutrition 0.000 description 1
- 230000000712 assembly Effects 0.000 description 1
- 238000000429 assembly Methods 0.000 description 1
- 230000004323 axial length Effects 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 229910003460 diamond Inorganic materials 0.000 description 1
- 239000010432 diamond Substances 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 230000035558 fertility Effects 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 238000009342 intercropping Methods 0.000 description 1
- 230000001050 lubricating effect Effects 0.000 description 1
- 230000001404 mediated effect Effects 0.000 description 1
- 238000012545 processing Methods 0.000 description 1
- 238000012797 qualification Methods 0.000 description 1
- 238000011160 research Methods 0.000 description 1
- 238000005096 rolling process Methods 0.000 description 1
- 239000002689 soil Substances 0.000 description 1
- 230000003068 static effect Effects 0.000 description 1
Images
Classifications
-
- 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
- F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
- F16H55/02—Toothed members; Worms
- F16H55/08—Profiling
-
- 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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D23/00—Details of mechanically-actuated clutches not specific for one distinct type
- F16D23/02—Arrangements for synchronisation, also for power-operated clutches
- F16D23/04—Arrangements for synchronisation, also for power-operated clutches with an additional friction clutch
- F16D23/06—Arrangements for synchronisation, also for power-operated clutches with an additional friction clutch and a blocking mechanism preventing the engagement of the main clutch prior to synchronisation
- F16D23/0606—Arrangements for synchronisation, also for power-operated clutches with an additional friction clutch and a blocking mechanism preventing the engagement of the main clutch prior to synchronisation the blocking mechanism comprising an axially-extending shouldered pin passing through a hole in a radial wall
-
- 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
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/0467—Elements of gearings to be lubricated, cooled or heated
- F16H57/0478—Synchromesh devices
-
- 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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D23/00—Details of mechanically-actuated clutches not specific for one distinct type
- F16D23/02—Arrangements for synchronisation, also for power-operated clutches
- F16D23/04—Arrangements for synchronisation, also for power-operated clutches with an additional friction clutch
- F16D23/06—Arrangements for synchronisation, also for power-operated clutches with an additional friction clutch and a blocking mechanism preventing the engagement of the main clutch prior to synchronisation
- F16D2023/065—Means to provide additional axial force for self-energising, e.g. by using torque from the friction clutch
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Mechanical Operated Clutches (AREA)
- Structure Of Transmissions (AREA)
- Lock And Its Accessories (AREA)
- Input Circuits Of Receivers And Coupling Of Receivers And Audio Equipment (AREA)
Abstract
销式双动同步器机构(18),带有摩擦离合器(20、32与22、24),爪离合器(24、14b和26、16b)和自增力斜面。该斜面在轴(12)和换挡凸缘(28)之间起作用。该凸缘可相对于轴和爪离合器(24、26)转动。凸缘(28)包括齿(48),后者限制由轴花键(12b)形成的杆状部(50)所限定的斜面(50a、50b、50c、50d)的自增力斜面(48a、48b、48c、48d)。与齿轮以花键滑动连接的摩擦元件(20,22)的轴向运动由接销(44)限止。
Description
本发明涉及用于传动***的销式同步器机构。更准确地说,本发明涉及一种用于这种机构的轴向制动锥形摩擦元件。
大家熟知的多传动比传动技术中,同步机构被用来减少全部或部分传动比的换挡时间。也为人们所熟知的是,换挡作用力须由车辆的司机来施加,即将力加在换挡杆上,这样在使用自增力式的同步器机构时就可以省力。具有自增力的销式同步器机构的现有技术的例子可参见美国专利US5,092,439,该专利将作为本发明的参考文件。
在上述专利中所公开的销式同步器机构包括:分别起同步功能及刚性离合功能的摩擦元件与爪式元件,它们与轴上的齿轮轴向分隔开,随着换挡力的作用,爪式元件中之一的初级啮合运动产生的起预增力效应的摩擦元件的初级啮合而引起止动元件的彼此接合,操作这些止动元件以防止爪式元件的异步接合并将换挡力传至摩擦元件以增加其同步力矩,以及自增力效应斜面,该力矩提供一个与换挡力同向并叠加在其上的附加力,以便进一步增加摩擦元件的同步力矩。用于本发明的销式同步器机构可以包括或不包括自增力效应斜面。
许多销式同步器机构包括具有圆锥形摩擦表面的环,该环可以作从同步器机构的中间位置直到与一个固定不转的元件限定的圆锥形摩擦表面相接合为止的轴向运动,这里所有轴向运动都是相对于齿轮进行的。
上述元件的轴向固定最好能保证摩擦表面之间的间隙,即在同步器机构位于中间位置时,保证表面间不接触,而在同步器机构从某一接合位置移向中间位置时,保证或减缓例如是由于摩擦表面间的油类的粘性剪切力所产生的力矩所造成的自增力效应斜面的无意中的接合。
在某些传动设备中,相对于齿轮轴向固定某些元件是困难的和/或成本过高的。但在本文所公开的发明不需使元件固定起来以防任何轴向运动。即使在用于使元件相对于齿轮初步轴向固定的其它装置损坏时,本发明也能保证上述的间隙、脱开及减缓粘性剪切阻力。
本发明的一个目的是改善同步机构的摩擦表面间的功能关系。
按照本发明的特征,销式同步器机构可以选择性地进入摩擦同步啮合状态,并使第一和第二轴向间隔的驱动件的任何一个与轴成刚性连接。这些驱动件设置成可绕同一轴的轴线作相对转动并不会相对于该轴作轴向移动。驱动爪装置固定在每一个驱动件上并可以与轴向运动的爪元件相接合,该爪具有轴向延伸的内花键与设置在轴上的轴向延伸的外花键连续地滑动地配合。第一和第二锥形摩擦面分别是轴向分开的第一和第二元件的一部分,第一和第二元件分别借助于联接件加以紧固,以便随第一和第二驱动件固联转动并限制齿轮之间的离开的间隙的轴向移动。第三与第四圆锥形摩擦表面位于一对与轴装置同心的、在轴向彼此隔开的环上,该环在彼此隔开的驱动件间作轴向运动,以便分别与第一与第二摩擦表面接合,使驱动件与轴达到同步运动。一凸缘经向伸入环之间,以便随施加在凸缘上的轴向双向换挡力(Fo)而轴向推动可轴向移动的环与爪,使它们进入接合状态。固定凸缘的装置防止相对于可轴向运动的爪作轴向运动。止动件用以防止爪在同步运动之前进入接合状态。该止动件包括多个周向彼此隔开并轴向延伸的销,该销与环紧密地固定在一起。销延伸通过凸缘中的开口。每个销具有轴向分开的止动肩,这些肩可以与位于凸缘的两侧呈环绕其上的开口的止动肩接合。随着换挡力的作用,凸缘从中间位置朝向驱动件之一的初步轴向运动,预增力器使第三和第四摩擦表面中的每一个分别与第一和第二摩擦表面相接合,随着摩擦表面的接合,产生一经由销传到凸缘的同步力矩使止动件接合,以及经由接合的止动件将换挡力传送至接合的摩擦表面以增加其接合力。
本发明的特征是:连接件允许第一与第二摩擦件在朝向摩擦环的方向上轴向运动,并有多个周向分隔开的刚性元件轴向地放入第一与第二元件之间以限制或抑制朝向摩擦环的轴向运动。
本发明的同步器机构表示于附图中,其中:
图1是沿图2中的1-1线的双动同步器机构的剖视图;
图2是沿图1中的2-2线的机构局部剖视图;
图3是沿图1中的3-3线的机构的一部分的剖视图;
图4是图1与图2中的元件的透视图。
图5与图6是图1与图2中的柱塞元件与销元件的细部视图;
图7是图1中的机构的局部视图,其中爪离合器处于接合位置;
图8和图9是按图1中8-8线的机构的牙部分的剖视图;
图10是用图表示的作用在同步器的换挡凸缘上的轴向力与力矩;以及
图11是同步器机构的一部分的变化的一个实施例的放大视图。
术语″同步离合器机构″用以表示一种离合器机构,它借助于刚性离合器通过不转动的偶件使轴具有选定的传动比,其中刚性离合器的接合在与其相连的同步摩擦离合器使其元件基本上同步旋转前不会发生。术语″自增力效应″用以表示同步离合器机构中所包括的斜面或凸轮或类似件可以与摩擦离合器的同步力矩成比例地增加同步离合器机构的接合力。
首先主要参见图1与2,其中示出一种齿轮与同步器总成10,它准备用于未示出的陆用车辆,特别是重型卡车的的传动机构。不过总成10也可以在其它应用中使用。该总成包括安装在基本上是共同的轴线11a和12a上的传动输入轴11与主轴12以便绕其转动和彼此隔开的、可转动地安装在轴上的传动比齿轮14、16,齿轮用已知的方式由固定在轴上的环状推力元件阻止其相对于轴作轴向运动,以及双作用销式同步离合器机构18。当总成10是双中间轴传动器、例如在本文中用作参考的美国专利3,648,546与4,788,889中公开的传动器的一部分时,齿轮14上的牙14a将与由齿轮16驱动的未示出的中间轴上的齿轮稳定地啮合,而轴12可连接于或可有选择地连接于某一载荷,轴12也可象现有技术中所熟知地那样稍作自由地径向运动。齿轮16被用花键连接于输入轴11上,齿16a与未示出的中间轴上的齿轮的齿成稳定的啮合。
同步器机构18包括环状摩擦元件或锥形帽20、22和紧固于齿轮14、16与其共同转动的环状爪式接合元件14b、16b,具有内花键齿24a、26a的爪形接合元件24、26,内花键齿24a、26a与轴或其它所附着的元件上制出的外花键齿12b滑配合;一经向伸出的换挡凸缘(28)具有夹在爪形件24、26的轴向表面24b、26b之间的轴向相对的侧面28a、28b;三个H形的定位件30(图4示出其中之一的透视图)用于固定凸缘和爪元件以防止相对的轴向运动的产生,环状摩擦元件或环32、34由三个彼此周向隔开的销36刚性地连接起来,这些销从每个摩擦元件处轴向延伸通过凸缘上的开口28c,三个预增力总成38中每一个都包括有弹簧40与柱塞42,它们作用于销的表面。保持件30,销36与总成38的数量可以比本文公开的多或少些。
轴11、齿轮16与轴承17最好通过变速箱的壳体(部分示出)19上的轴承圈支持孔19a安装成一个总成。因为摩擦元件22的直径大于孔口19a的直径,所以元件22在总成安装完成后再安装在齿轮16上。
摩擦元件20、22具有内锥形摩擦面20a、22a,它们分别与环状摩擦件32、34的外锥形摩擦面相配。不难看出,爪式离合器接合前,摩擦件20、32与22、34对偶组成了使齿轮与轴同步运动的摩擦离合器。摩擦件20、22包括有能与齿轮14、16上的外花键14c、16c相滑配的内花键20b、22b,可用以防止两者之间产生的相对转动。齿轮14、16上的支撑或反应面14d、16d可限止元件20、22作从齿轮之间的间隔离去的轴向移动。元件朝向齿轮间隔方向的轴向运动由多个刚性的长形元件44限制或阻挡,元件44可滑动地延伸穿过与其轴向对准的元件32、34上的开口32b、34b和凸缘28上的开口28c。一个弹簧卡紧件或弹性箍46,例如一个O型卡圈44,来卡紧元件44,并在把元件32、34安装在20、22之间以前就能使每个元件44定位。当可移动的爪24、26中的任一个从啮合位置至中间位置时,元件44也可以确保锥面脱开。
锥角的范围可以是广泛的,在此处所采用的是7度半。摩擦表面可以用已知的摩擦材料中的任一种固定在基底件上形成,本文是采用热解碳摩擦材料,例如美国专利US4,700,823,US4,844,218以及更好的4,778,548中所开的。这些专利用作本文的参考文件。
销36在图6中表示得更为详细。每个销都包括其尺寸略小于凸缘孔28c的直径的较大直径部分36a,位于摩擦环32、34之间的间隙(此处是位于中间)的缩径或凹槽部分36b,从销的轴线径向向外延伸并互相为某一角度,本文是相对于销轴线的法线约成40°角,的锥形止动肩或面36c、36d;最好有但不是必须有的独立的预增力表面36e、36f和延伸的次级中心面369、36h。凹槽部分在其置入它们对应的凸缘开口中时,可限制刚性摩擦环和销总成相对于凸缘的转动以使销止动肩与位于凸缘开口周围的倒角止动肩接合。预增力表面36e、36f弦交或切去锥形止动肩36c、36d的一部分并最好(但不是必需)是平坦的平面并相对于销的轴线成一角度,这一角度最好稍小于止动面的角度。中心面369、36h也是一个平坦的平表面,并在图中很明显地是相对于销的轴线构成了一个角度,该角度显著地小于止动件和预增力件表面的角度。正如在本文中公开的,弦向伸展的平表面是与销中心线与轴中心线同心的圆的切面。可变化的是表面36e、36f也可以取消,于是预增力柱塞124顶住止动表面36c、36d。
螺旋压缩弹簧40位于径向向外朝向销预增力器表面的凸缘偏置柱塞42的缝隙28g中。缝隙的主要延伸方向最好是相对于轴中心径向延伸。该缝也轴向延伸穿过凸缘的侧边28a、28b而进入凸缘开口28c,并以其径向内伸部的端部28h承受弹簧作用力。
如前所述,爪元件24、26具有与固定在轴上的外花键齿12b滑配的内花键齿24a、26a。外花键齿具有与轴中心线平行延伸的渐开线齿侧面12c,该侧面与爪元件的花键齿侧面相配合以限止轴与爪二元件间的相对转动。各H形元件30均具有与爪元件表面24c、26c相抵靠的端部30a、30b以及连接端部的中间部分30c。中间部分延伸,密配地穿过爪元件上的轴向间隙24d、26d并松配地穿过具有经向延伸的止动面28n、28m的开口28k,开口28k与中心部分30c协同限止凸缘相对于爪和轴间的相对转动,其理由在后面叙述。
在图1-2与7-10中清楚看出,轴的若干外齿12b的某些部位在从图1、2与8中所示凸缘28的中间位置上看,在两个轴向方向上加以改进形成一个或多个斜面,这些斜面与数量相似的从凸缘28径向向内延伸并进入轴花键12b之间的轴向延伸的空间的反作用件或内齿48相配。斜面可限止凸缘相对于爪元件24、26和轴12的转动,对锥面离合器与轴之间的同步力矩起反应以提供附加的轴向自增力来增强在施加于凸缘28上的换挡力的作用下锥形离合器初步接合时的接合力以增加由锥面离合器所提供的同步力矩。斜面可以用来提供施于一或两个齿轮的增强的同步力和/或提供增强的同步力以抵抗在向上或向下换挡的情况下所出现的某一方向上的力矩。更具体地说,周向分布于各H形定位件中心部分30c之间的齿12b中的每一个都具有第一和第二轴向分开的凹部,形成多个环形槽,这些槽具有被柱状部50所限定的第一端、轴向相对的端部12d、12e以及最小外径12f。最小外径12f大于花键12b的根径与爪离合器24a、26a的内径24c、26c。同时最小外径12f小于凸缘内齿48的内径。柱状部分50呈菱形,由每个齿在其两个轴向方向上切去部分形成。该已被切去部分的轴向与径向范围选择为易于在柱状部分50上加工增力斜面50a、50b、50c、50d并尽量减小这种切去对齿12b的强度的影响。进一步地,花键齿12b具有足够的径向深度以确保斜面具有足够的面积以最大限度减小作用于其上的力造成的磨损。位于柱状部分50的轴向端50a、50b与齿12的轴向端12d、12e之间的切去部分或凹部的轴向范围可以通过在齿上简单地加工出环形槽来构成。已切去部分的轴向长度足以方便地***刀具以形成斜面。斜面50a、50b分别作用于凸缘齿48上的斜面48a、48b以提供附加力Fa响应任一方向上的力矩来增加或促使齿轮14的同步率。斜面50c、50d分别作用于斜面48c、48d来提供附加的轴向力Fa给齿轮16以响应任一方向上的同步力矩。斜面的角度可以加以变化以提供不同数量的附加轴向力以便上换挡和下换挡以及高速率或低速率。如果没有附加轴向力,建议在一个齿轮或多个的一个方向上,斜面可以平行于花键,即不具有影响的斜面。轴向附加力的大小或值也是摩擦离合器和自增力斜面的平均半径多数的函数,这一点在下文中还要进一步说明。故对于由换挡叉施加于换挡凸缘28上的给定换挡力来说,附加力的大小可以借助于变化斜面的角度和/或平均半径系数来改变。内齿48与柱状部分50可由非增力表面或平面48e与50e在其环形地相对侧形成。非增力表面在凸缘处于中间位置时互相作用以防止由于任何锥形离合器产生的力矩,例如在摩擦表面之间出现油的粘滞剪切力使自增力斜面起作用。
参见图1和8,当凸缘28处于中间位置时,销36的缩径部分36b与其相对应的凸缘开口28c在径向上对准。锥形离合器的摩擦表面稍微地分开并由柱塞42的倾斜的预增力表面42a、42b保持住这种间隔,此时表面42a、42b由弹簧40的力和贴靠于摩擦元件20、22的长形元件44的端开44a、44b作用于销36的预增力表面36e、36f。当需要使二齿轮中之一与轴接合时,可用例如在美国专利US4,920,815中所公开的具参考价值的,适用的但未在本文中示出的以已知方式与凸缘28相连接的换挡机构,使凸缘左向或右向地沿轴12的轴线移动以接合齿轮16或14。换挡机构可以由操作者通过一连杆***手动操作,也可通过一执行机构进行有选择性地推动,或者通过自动启动换挡***并控制换挡***所施加的力的大小的装置来加以推动。当换挡机构被手动时,输出的力与操作者施加于换挡杆的力成比例。无论力是手动地或是自动地被施加,作用在凸缘28上的力是轴向的,在图10中用箭头Fo的长度来表示。
在操作者推动凸缘28作初始的向右的轴向运动时,换挡力Fo借助于预增力柱塞42通过预增力面36f传向销使锥面32a与锥面20a初步摩擦接合。当然锥面的初步接合力是弹簧40的力与预增力面的斜度所作用的结果。初步的摩擦接合(提供了一个异步状态并可在瞬时忽视自增力斜面的作用)产生了一个初步的锥面离合器的接合力与同步力矩To,该力确保了凸缘28和接合的摩擦环之间的有限的相对转动,因而减少了直径的销的部分36b朝向凸缘开口28c的适当侧的运动提供了销止动肩36c与凸缘止动肩28c之间的接合。当止动肩接合后,凸缘28上的全额操作者换挡力Fo经由止动肩传向摩擦环32,而在该全额操作者换挡力Fo作用下锥面离合器接合产生一个最终操作者同步力矩To。该操作者同步力矩To在图10中以箭头To表示。由于止动肩相对于操作者换挡力To的轴线方向成一个角角,故产生了一个反力或反止动力拒,反止动力矩与来自锥面离合器的同步力矩相反,但在异步状态时其量值相对较小。当实质上的同步状态达到时,同步力矩值降至低于反止动力矩值,这样止动肩就把销推至与开口28c同心的位置以使凸缘作连续的轴向运动并使爪元件24的外爪牙24d与齿轮14的内爪牙14b相接合,如图7中所示。就象现有技术中的以及在图7中记载的爪牙16b的参考数值那样,爪牙的导引部分具有倾斜的导缘16c以减轻在最初接触过程中牙所受到的损伤,同时还具有倒角或楔形面16d以使牙部转入对准的配合状态。有导引部分的爪牙在美国专利US4,246,993中作了较详细的公开,该专利还参考了专利US3,265,173中所提出的一种适当的倾斜角教导。该楔形面可以是不对称的,以防止由于牙的导缘的对撞接触而引起的换挡滞后完成。为了促进平滑并相对省力地完成换挡,爪牙最好是在周向上、切实可行地尽量细小,这样就减少了为使爪牙对准所需的转角。同时爪牙也最好尽可能地布置在较大的直径上。
继续忽视自增力斜面的影响,由于Fo提供的圆锥面离合器力矩可以下述等式表达:
To=FoRcμc/sinα
其中:
Rc=锥形摩擦面的平面半径
μc=锥形摩擦面的摩擦系数,而
α=锥形摩擦面角度
现在注意自增力斜面的作用,特别参见图8与9。由于操作者所施加的轴向换挡力Fo所产生的同步力矩To借助于销36传至凸缘28并通过自增力斜面到达轴12。自增力斜面在啮合时限制凸缘相对于轴12与爪元件24、26的转动并产生一轴向分力或轴向附加力Fa在与换挡力Fo相同的方向上作用于凸缘,因而进一步地增强了锥面离合器的接合力而提供了一个附加的同步力矩Ta作为对力矩To的补充。图8示出自增力斜面的位置和爪元件键齿24a、26a啮合于轴键齿12b时的位置,此时换挡凸缘28位于相当于图1中位置的中间位置。图9示出的斜面和键齿的位置是锥面32a、30a接合使齿轮14进入同步状态时的情况。彼此接合的锥面产生一个同步力矩,其方向可使凸缘斜面48a与轴斜面50a相接合。从而使锥角离合器接合的轴向力的量值为Fo加上Fa,而由锥面离合器产生的同步力矩的值为To加上Ta,如图10中的图表所示。对于给定的操作者换挡力Fo与操作者同步力矩To来说,轴向的附加力的数值最好是啮合的自增斜面的角度的函数。该角度最好是大到足以产生能够足以明显增加同步力矩的附加力与降低随操作者产生的给定的适度的换挡作用力而到达同晃状态所费的时间。但该角度也是小到足以产生一个可以随力Fo的增减而增减的轴向附加控地力Fa。如果倾角太大,斜面就会自锁而不是自增力,这样一旦锥面离合器初步接合,力Fa就会独立于力Fo而迅速地及不可控地增长而使圆锥离合器趋于锁闭。自锁而不是自增力还会降低换挡质量或换挡感觉,可能造成过分增强的同步器分力、可能造成圆锥离合器表面的过热与快速磨损,甚至可能造成换挡杆操作者动作过度。
为提供与操作力Fo成比例增减的附加轴向力Fo计算自增力倾斜角所用的主要变量有锥面离合器角度、锥面离合器摩擦系数、锥面离合器与自增力斜面的平均半径系数、斜面摩擦系数以及自增力斜面的压力角。该压力角可以是零。其中斜面具有20度的压力角。计算和控制自增或助推力所需的更多细节可以由前面所述的本文的参考文件美国专利US5,092,439得知。
图11示出长形元件44的一个变化的实例。在这个变化的实例中,每个长形元件标以标号114,对它的改进是在其两端114a、114b设置了减摩元件114c、114d以减缓端部与锥形帽20、22之间的阻力。这种阻力会损害换挡操作的执行并会在端部接触锥形帽时由于磨损与生热而造成损坏。其中减摩元件114c、114d分别是保持在端部114a、114b凹槽中的轴承滚珠。每个凹槽与滚球之间的润滑可以是以已知方式用润滑剂浸润每一个凹槽或使变速器油飞溅到滚珠的各暴露部分上。
公开了两上具有自增力效应与改善的中间位置的同步器机构。相信这些实例的许多变型与改进方案都可以在本发明的精神范围内提出。后面的权利要求试图对所公开的机构以及变型和改进方案的发明部分加以复盖并相信其未脱离本发明的精神。
Claims (7)
1.销式同步器机构(18),有选择地执行摩擦式同步并与轴向上彼此间隔的第一与第二驱动件(14、16)之一形成刚性连接,驱动件安装成可绕轴(12)的轴线(12a)旋转但不能相对于轴作轴向位移,该机构包括:
驱动爪元件(14b、16b)固定在每个驱动件(14、16)上,与可轴向位移的爪元件(24d、26d)接合,爪元件具有轴向延伸的内花键(24a、26a)可连续地与固定在轴(12)上的轴向延伸的外花键(12b)滑配合,外花键(12b)具有一对彼此相对并相互间有间隙的齿侧表面(12c),
第一与第二锥形摩擦表面(20a、22a)分别位于彼此轴向隔开的第一和第二元件(20、22)上,这两个元件分别借助于联接件(14c、16c与14d、16d)加以固定以便随第一和第二驱动件(14、16)一同转动并限制驱动件(14、16)之间离开的间隙的轴向移动,第三与第四圆锥形摩擦表面位于一对与轴中心线(12a)同心的、在轴向彼此隔开的环(32、34)上,该环在彼此隔开的驱动件(14、16)间的间隙中作轴向位移,以分别与第一和第二摩擦表面(20a、22a)接合,使驱动件(14、16)与轴(12)同步;
一凸缘(28)延伸径向伸入环(32、34)之间,以便随施加在凸缘(28)上的轴向双向换挡力(Fo)而轴向推动环与可轴向移动的爪元件(24d、26d),使它们进入接合状态,固定凸缘的装置(30)防止相对于可轴向运动的爪作轴向位移,
止动件(36a、36c与28e、28f)用于防止可轴向移动的爪元件(24d、26d)在同步动作前接合,该止动件包括多个周向彼此隔开并轴向延伸的销(36),该销与环(32、34)紧密地固定在一起,销延伸通过凸缘(28)中的开口(28c),每个销上具有轴向隔开的止动肩(36d、36c),这些肩可以与位于凸缘(28)的两侧并环绕其上的开口(28c)的止动肩(28e、28f)接合,
预增力件(38、36f、36e)随凸缘(28)在换挡力的作用下从中间位置朝向驱动件(14、16)中之一的初步轴向位移,使第三与第四摩擦表面(32a、34a)分别与第一与第二摩擦表面接合,随着摩擦表面(20a、22a、23a、34a)的接合,产生一经由销传到凸缘(28)上的同步力矩使止动件(36d、36c和28e、28f)接合,以及经由接合的止动件将换挡力传送至接合的摩擦表面以增加其接合力,其特征在于:
连接件(14c、16c与14d、16d)允许第一和第二元件(20、22)中的至少一个朝向摩擦环(32、34)中的至少一个作轴向位移;
多个周向上彼此分开的连件元件(44)轴向***到第一与第二元件(20、22)之间,以限制其朝向摩擦环(32、34)的轴向位移。
2.权利要求1的机构,其中:
连接件(14c、16c与14d、16d)包括多组周向上彼此隔开的、在轴向上穿过一对环(32、34)与凸缘(28)的开口(28c、32d、34d)和可滑动地置于一开口组中并具有分别与第一和第二元件(20、22)紧贴的相对端(44a、44b或114c、114d)的呈长形元件状的连接元件(44)。
3.权利要求2的机构,包括用于在将环(32、34)安放在第一与第二元件(20、22)之间从前把长形元件(44)保持在开口(28c、32d、34d)之间的装置(46)。
4.权利要求1或2的同步器机构,包括:具有第一和第二斜面机构(50a、48a)的第一自增力机构(48、50),第一和第二斜面机构随着在摩擦元件(20a、32a)与轴(12)间的起作用的同步力矩的一个方向上的同步力矩和为进一步增加接合第一摩擦表面(32a)的力的轴向附加力而啮合。
5.权利要求1或2的同步机构,进一步包括:
固定凸缘(28)的装置(30),该装置允许凸缘相对于可轴向运动的爪元件(24d、26d)作圆周运动;
至少一个位于具有第一斜面(50a)的外花键齿(12a)之间的间隔,第一斜面是至少在一对齿的侧面(12c)形成的,第一斜面(50a)相对于垂直轴线(12a)的平面和齿侧面(12c)的角度小于90°。
反作用元件(48)从凸缘(48)向内径向延伸并进入一空间,它包括基本上平行于第一斜面(50a)的第二斜面(48a)并与其啮合,该啮合是随着接合摩擦表面(20a、32a)与第一驱动装置(14)连接时某一方向的同步力矩进行的,以便在凸缘(28)上产生一轴向附加力,以增加与第一驱动装置(14)相连的摩擦表面(20a、32a)的接合力。
6.权利要求1、2、4或5的机构,其中:每个长形元件(114)的二相对端具有减摩装置(114c、11d)。
7.权利要求6的机构,其中:减摩机构(114c、114d)包括保持在每个长形元件的各端的槽穴(114a、114b)中的轴承滚珠。
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US311,982 | 1989-03-15 | ||
US17296393A | 1993-12-27 | 1993-12-27 | |
US172,963 | 1993-12-27 | ||
US08/311,982 US5497867A (en) | 1993-12-27 | 1994-09-26 | Synchronizer with cone cup locater pins |
Publications (2)
Publication Number | Publication Date |
---|---|
CN1115016A true CN1115016A (zh) | 1996-01-17 |
CN1062943C CN1062943C (zh) | 2001-03-07 |
Family
ID=26868649
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
CN94120712A Expired - Fee Related CN1062943C (zh) | 1993-12-27 | 1994-12-27 | 具有锥形帽定位销的同步器 |
Country Status (10)
Country | Link |
---|---|
US (1) | US5497867A (zh) |
EP (1) | EP0664411B1 (zh) |
JP (1) | JP3577610B2 (zh) |
KR (1) | KR100272205B1 (zh) |
CN (1) | CN1062943C (zh) |
AT (1) | ATE159569T1 (zh) |
BR (1) | BR9405098A (zh) |
CA (1) | CA2138430C (zh) |
DE (1) | DE69406416T2 (zh) |
ES (1) | ES2109618T3 (zh) |
Cited By (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2018121419A1 (zh) * | 2016-12-30 | 2018-07-05 | 比亚迪股份有限公司 | 锁止装置、动力总成、动力传动***及车辆 |
CN109374521A (zh) * | 2018-11-24 | 2019-02-22 | 福州大学 | 用于测试金属橡胶摩擦耗能性能的装置及其工作方法 |
US11053989B2 (en) | 2016-12-30 | 2021-07-06 | Byd Company Limited | Locking device, power assembly, power transmission system, and vehicle |
CN113389858A (zh) * | 2020-03-13 | 2021-09-14 | 福州锐智新能源科技有限公司 | 行星齿轮变速器 |
CN114017475A (zh) * | 2021-11-10 | 2022-02-08 | 一汽解放汽车有限公司 | 一种变速装置、变速器及车辆 |
CN117570159A (zh) * | 2024-01-15 | 2024-02-20 | 四川艾马仕科技有限公司 | 一种带分离功能的可变速传动总成 |
Families Citing this family (163)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5785162A (en) * | 1997-01-16 | 1998-07-28 | Ford Global Technologies, Inc. | Re-indexing manual transmission synchronizer |
DE19726027C2 (de) * | 1997-06-19 | 1999-05-06 | Memminger Iro Gmbh | Fadenliefergerät und Kupplungseinrichtung |
US6902917B1 (en) * | 1999-08-03 | 2005-06-07 | Archer-Daniels-Midland Company | Process for recovery of organic acids from fermentration broths |
BR9907360A (pt) * | 1999-11-12 | 2001-06-26 | Eaton Corp | Sincronizador tipo anel de bloqueio de ação dupla |
GB2358680A (en) | 2000-01-31 | 2001-08-01 | Eaton Corp | A transmission with low inertia shaft |
US6758787B2 (en) | 2002-10-23 | 2004-07-06 | General Motors Corporation | Family of six-speed dual-clutch transmissions having a stationary planetary gear member |
US6764425B2 (en) | 2002-11-25 | 2004-07-20 | General Motors Corporation | Multi-speed dual-clutch planetary transmissions having four fixed interconnecting members |
US6746363B1 (en) | 2002-11-25 | 2004-06-08 | General Motors Corporation | Multi-speed dual-clutch planetary transmission mechanisms having a stationary gear member and one brake |
US6716132B1 (en) | 2002-11-25 | 2004-04-06 | General Motors Corporation | Family of multi-speed dual-clutch transmissions having four interconnected planetary gear sets |
US6755765B2 (en) | 2002-11-25 | 2004-06-29 | General Motors Corporation | Multi-speed dual-clutch planetary transmissions having three gear members continuously interconnected with output shaft |
US6764426B2 (en) | 2002-11-25 | 2004-07-20 | General Motors Corporation | Multi-speed dual-clutch transmissions having three interconnecting members and four brakes |
US6743142B1 (en) | 2002-11-25 | 2004-06-01 | General Motors Corporation | Multi-speed dual-clutch planetary transmission mechanisms having three interconnecting members |
US6811512B2 (en) | 2002-11-25 | 2004-11-02 | General Motors Corporation | Multi-speed dual-clutch planetary transmission mechanisms having a stationary gear member and two brakes |
US6743143B1 (en) | 2002-11-25 | 2004-06-01 | General Motors Corporation | Multi-speed dual-clutch planetary transmission mechanisms having four gear sets and a stationary member |
US6743144B1 (en) | 2002-11-26 | 2004-06-01 | General Motors Corporation | Multi-speed dual-clutch planetary transmissions having three continuously interconnected gear members |
US6743139B1 (en) | 2002-11-26 | 2004-06-01 | General Motors Corporation | Multi-speed dual-clutch planetary transmissions having output shaft interconnected with three gear members |
US6752736B1 (en) | 2002-12-06 | 2004-06-22 | General Motors Corporation | Multi-speed dual-clutch planetary transmissions having a stationary fourth gear set member |
US6758784B2 (en) | 2002-12-06 | 2004-07-06 | General Motors Corporation | Family of six-speed dual-clutch transmissions having a stationary planetary member and two brakes |
US6736751B1 (en) | 2002-12-06 | 2004-05-18 | General Motors Corporation | Family of multi-speed dual-clutch transmissions having three interconnected planetary gear members |
US6783477B2 (en) * | 2002-12-18 | 2004-08-31 | General Motors Corporation | Family of six-speed dual-clutch transmissions having three planetary gear sets |
US6746357B1 (en) | 2002-12-18 | 2004-06-08 | General Motors Corporation | Family of six-speed dual-clutch transmissions having four planetary gear sets and three brakes |
US6743140B1 (en) | 2002-12-18 | 2004-06-01 | General Motors Corporation | Family of six-speed dual-clutch transmissions having two stationary planetary gear members |
US6837823B2 (en) | 2002-12-19 | 2005-01-04 | General Motors Corporation | Six-speed dual-clutch transmissions having four planetary gear sets and two brakes |
US6764424B1 (en) | 2003-01-03 | 2004-07-20 | General Motors Corporation | Six-speed dual-clutch transmissions having planetary gear sets with three interconnecting members |
US6852059B2 (en) | 2003-01-03 | 2005-02-08 | General Motors Corporation | Six-speed dual-clutch transmissions having planetary gear sets with two interconnecting members |
US6767307B1 (en) * | 2003-01-06 | 2004-07-27 | General Motors Corporation | Family of multi-speed dual-clutch transmissions having four planetary gear sets and four brakes |
US7090610B2 (en) * | 2004-02-10 | 2006-08-15 | General Motors Corporation | Wide ratio transmissions with three interconnected planetary gear sets |
US6949048B2 (en) * | 2004-02-10 | 2005-09-27 | General Motors Corporation | Wide ratio transmissions with three planetary gear sets and two brakes |
US6962548B2 (en) * | 2004-02-10 | 2005-11-08 | General Motors Corporation | Wide ratio transmissions with a stationary planetary gear member and at least five clutches |
EP1566573A1 (en) | 2004-02-19 | 2005-08-24 | General Motors Corporation | Family of multi-speed dual-clutch transmissions having three interconnected planetary gear members |
EP1566574A1 (en) | 2004-02-19 | 2005-08-24 | General Motors Corporation | Family of six speed dual clutch transmissions having two stationary planetary gear members |
US6994649B2 (en) * | 2004-03-24 | 2006-02-07 | General Motors Corporation | Wide ratio transmissions having three gear sets and a stationary planetary member |
US6988972B2 (en) * | 2004-03-24 | 2006-01-24 | General Motors Corporation | Wide ratio transmissions having three planetary gear sets and three brakes |
US7001304B2 (en) * | 2004-03-24 | 2006-02-21 | General Motors Corporation | Wide ratio transmissions having three planetary gear sets and at least six clutches |
US7004880B2 (en) * | 2004-03-24 | 2006-02-28 | General Motors Corporation | Wide ratio transmissions with three interconnected planetary gear sets and at least one brake |
US6997844B2 (en) * | 2004-03-24 | 2006-02-14 | General Motors Corporation | Wide ratio transmissions with three interconnected planetary gear sets and a stationary member |
US6991577B2 (en) * | 2004-03-24 | 2006-01-31 | General Motors Corporation | Wide ratio transmissions with three planetary gear sets and a stationary interconnecting member |
US6997846B2 (en) * | 2004-03-24 | 2006-02-14 | General Motors Corporation | Wide ratio transmissions with three planetary gear sets and two interconnecting members |
US7056257B2 (en) * | 2004-04-07 | 2006-06-06 | General Motors Corporation | Wide ratio transmissions with two fixed interconnecting members |
US7041027B2 (en) * | 2004-05-03 | 2006-05-09 | General Motors Corporation | Wide ratio transmissions with a fixed interconnecting member and at least six clutches |
US7059994B2 (en) * | 2004-05-10 | 2006-06-13 | General Motors Corporation | Wide ratio transmissions with a fixed interconnecting member and a stationary planetary member |
US7086986B2 (en) * | 2004-06-04 | 2006-08-08 | General Motors Corporation | Wide ratio transmissions with two fixed interconnecting members and at least three clutches |
US7094173B2 (en) * | 2004-06-04 | 2006-08-22 | General Motors Corporation | Wide ratio transmissions having a stationary planetary member and at least four clutches |
US7033299B2 (en) * | 2004-06-16 | 2006-04-25 | General Motors Corporation | Planetary transmissions having three interconnected gear sets and clutched input |
US7101302B2 (en) * | 2004-07-14 | 2006-09-05 | General Motors Corporation | Planetary transmissions having a stationary member and input clutches |
US7056258B2 (en) * | 2004-07-23 | 2006-06-06 | General Motors Corporation | Planetary transmissions having one interconnecting member and an input member |
US7066861B2 (en) * | 2004-07-23 | 2006-06-27 | General Motors Corporation | Planetary transmissions having a stationary member and at least two input clutches |
US7150695B2 (en) * | 2004-07-23 | 2006-12-19 | General Motors Corporation | Planetary transmissions having input clutches and three interconnected gear sets |
US7118510B2 (en) * | 2004-07-23 | 2006-10-10 | General Motors Corporation | Planetary transmissions having input clutches and two interconnecting members |
US7118508B2 (en) * | 2004-07-28 | 2006-10-10 | General Motors Corporation | Planetary transmissions having three interconnected gear members and clutched input members |
US7153232B2 (en) * | 2004-07-28 | 2006-12-26 | General Motors Corporation | Planetary transmissions having a stationary member and an input member |
US7074152B2 (en) * | 2004-08-18 | 2006-07-11 | General Motors Corporation | Planetary transmissions having a stationary member and three interconnected gear members |
US7081066B2 (en) * | 2004-08-18 | 2006-07-25 | General Motors Corporation | Planetary transmissions having three non-continuously interconnected gear sets |
US7074153B2 (en) * | 2004-08-18 | 2006-07-11 | General Motors Corporation | Planetary transmissions having three gear sets and input clutches |
US7150696B2 (en) * | 2004-08-24 | 2006-12-19 | General Motors Corporation | Planetary transmissions having a stationary gear member and clutched input members |
US7104914B2 (en) * | 2004-09-14 | 2006-09-12 | General Motors Corporation | Planetary transmissions having two fixed interconnections and a stationary gear member |
US7104916B2 (en) * | 2004-09-23 | 2006-09-12 | General Motors Corporation | Planetary transmissions having a stationary fixed interconnection and providing at least eight speed ratios |
US7108627B2 (en) * | 2004-10-13 | 2006-09-19 | General Motors Corporation | Planetary transmissions having two interconnecting members and at least two input clutches |
US7128684B2 (en) * | 2004-11-01 | 2006-10-31 | General Motors Corporation | Planetary transmissions having a stationary fixed interconnection and up to three input clutches |
US7166053B2 (en) * | 2004-12-10 | 2007-01-23 | General Motors Corporation | Planetary transmissions having four interconnecting members and clutched input members |
US7153231B2 (en) * | 2005-01-04 | 2006-12-26 | General Motors Corporation | Planetary transmissions having two interconnecting members and clutched input members |
US7163484B2 (en) * | 2005-01-24 | 2007-01-16 | General Motors Corporation | Eight-speed transmissions with four planetary gear sets |
US7192378B2 (en) * | 2005-01-24 | 2007-03-20 | General Motors Corporation | Planetary transmissions having three interconnecting members and clutched input members |
US7175561B2 (en) * | 2005-02-10 | 2007-02-13 | General Motors Corporation | Planetary transmissions having two non-continuously interconnected gear members |
US7226381B2 (en) * | 2005-03-03 | 2007-06-05 | General Motors Corporation | Nine-speed transmissions with four planetary gear sets |
US7226382B2 (en) * | 2005-05-06 | 2007-06-05 | Gm Global Technology Operations, Inc. | Multi-speed planetary transmissions having three interconnected gear members and multiple input clutches |
US7341537B2 (en) * | 2005-05-25 | 2008-03-11 | General Motors Corporation | Multi-speed transmission |
US7204780B2 (en) * | 2005-05-25 | 2007-04-17 | General Motors Corporation | Multi speed transmission |
US7250019B2 (en) * | 2005-07-08 | 2007-07-31 | Gm Global Technology Operations, Inc. | Multi-speed planetary transmissions having a stationary member and seven torque-transmitting devices |
US7247120B2 (en) * | 2005-07-08 | 2007-07-24 | Gm Global Technology Operations, Inc. | Multi-speed planetary transmissions having seven torque-transmitting devices engaged in combinations of two |
US7261666B2 (en) * | 2005-07-08 | 2007-08-28 | Gm Global Technology Operations, Inc. | Multi-speed planetary transmissions having seven torque transmitting devices engaged in combinations of five |
US7303501B2 (en) * | 2005-07-08 | 2007-12-04 | Gm Global Technology Operations, Inc. | Multi-speed planetary transmissions having seven torque-transmitting devices and two fixed interconnections |
US7300378B2 (en) * | 2005-07-08 | 2007-11-27 | Gm Global Technology Operations, Inc. | Multi-speed planetary transmissions having clutched input members and providing at least eight speed ratios |
US7311635B2 (en) * | 2005-09-23 | 2007-12-25 | General Motors Corporation | Seven speed transmissions with all positive rotation components in forward speeds |
US7396312B2 (en) * | 2005-09-29 | 2008-07-08 | General Motors Corporation | Six speed transmission with a single carrier |
US7354376B2 (en) * | 2005-12-07 | 2008-04-08 | Gm Global Technology Operations, Inc. | Multi speed transmission |
US7384365B2 (en) * | 2006-01-27 | 2008-06-10 | Gm Global Technology Operations, Inc. | Multi speed transmission |
US7429229B2 (en) * | 2006-05-25 | 2008-09-30 | Gm Global Technology Operations, Inc. | Multi-speed transmissions with a long pinion and four fixed interconnections |
US7699745B2 (en) * | 2006-05-25 | 2010-04-20 | Gm Global Technology Operations, Inc. | Multi-speed transmissions with a long pinion and one fixed interconnection |
US7442145B2 (en) * | 2006-06-02 | 2008-10-28 | Gm Global Technology Operations, Inc. | Multi-Speed transmissions with a long pinion |
US7452302B2 (en) * | 2006-06-27 | 2008-11-18 | Gm Global Technology Operations, Inc. | Multi-speed transmissions with three interconnected gearsets |
US7727102B2 (en) * | 2007-03-30 | 2010-06-01 | Gm Global Technology Operations, Inc. | 8-speed transmission |
US7811197B2 (en) * | 2007-03-30 | 2010-10-12 | Gm Global Technology Operations, Inc. | 8-speed transmission |
US8057350B2 (en) * | 2007-03-30 | 2011-11-15 | GM Global Technology Operations LLC | 8-speed transmission |
US7798934B2 (en) * | 2007-03-30 | 2010-09-21 | Gm Global Technology Operations, Inc. | 8-speed transmission |
US7699742B2 (en) * | 2007-03-30 | 2010-04-20 | Gm Global Technology Operations, Inc. | 8-speed transmission with two fixed interconnections and on grounded member |
US7749126B2 (en) * | 2007-03-30 | 2010-07-06 | Gm Global Technology Operations, Inc. | 8-speed transmission |
US7862468B2 (en) * | 2007-03-30 | 2011-01-04 | Gm Global Technology Operations, Inc. | 8-speed transmission |
US7736259B2 (en) * | 2007-03-30 | 2010-06-15 | Gm Global Technology Operations, Inc. | 8-Speed Transmission |
US7766783B2 (en) * | 2007-03-30 | 2010-08-03 | Gm Global Technology Operations, Inc. | 8-speed transmission |
US7811196B2 (en) * | 2007-03-30 | 2010-10-12 | Gm Global Technology Operations, Inc. | 8-speed transmission with two fixed interconnections |
US7824298B2 (en) * | 2007-03-30 | 2010-11-02 | Gm Global Technology Operations, Inc. | 8-speed transmission with two fixed interconnections |
US7749129B2 (en) * | 2007-03-30 | 2010-07-06 | Gm Global Technology Operations, Inc. | 8-speed transmission |
US7854679B2 (en) * | 2007-03-30 | 2010-12-21 | Gm Global Technology Operations, Inc. | 8-speed transmission with three fixed interconnections |
US7998014B2 (en) * | 2007-04-04 | 2011-08-16 | GM Global Technology Operations LLC | 8-speed transmission |
US7883441B2 (en) * | 2007-04-04 | 2011-02-08 | GM Global Technology Operations LLC | 8-speed transmission |
US7811195B2 (en) * | 2007-04-06 | 2010-10-12 | Gm Global Technology Operations, Inc. | 8-speed transmission |
US7678011B2 (en) * | 2007-04-20 | 2010-03-16 | Gm Global Technology Operations, Inc. | 8-speed transmission |
US7892138B2 (en) * | 2007-04-20 | 2011-02-22 | GM Global Technology Operations LLC | 8-speed transmission |
US7678010B2 (en) * | 2007-04-20 | 2010-03-16 | Gm Global Technology Operations, Inc. | 8-speed transmission |
US7736261B2 (en) * | 2007-04-20 | 2010-06-15 | Gm Global Technology Operations, Inc. | 8-speed transmission |
US7749127B2 (en) * | 2007-04-20 | 2010-07-06 | Gm Global Technology Operations, Inc. | 8-speed transmission |
US7803084B2 (en) * | 2007-04-20 | 2010-09-28 | Gm Global Technology Operations, Inc. | 8-speed transmission |
US7670247B2 (en) * | 2007-04-20 | 2010-03-02 | Gm Global Technology Operations, Inc. | 8-speed transmission |
US7678009B2 (en) * | 2007-05-21 | 2010-03-16 | Gm Global Technology Operations, Inc. | 8-speed transmission |
US7695397B2 (en) * | 2007-06-04 | 2010-04-13 | Gm Global Technology Operations, Inc. | 8-speed transmission |
US7637837B2 (en) * | 2007-06-04 | 2009-12-29 | Gm Global Technology Operations, Inc. | 8-speed transmission |
US7628724B2 (en) * | 2007-06-04 | 2009-12-08 | Gm Global Technology Operations, Inc. | 8-speed transmission |
US7691024B2 (en) * | 2007-06-04 | 2010-04-06 | Gm Global Technology Operations, Inc. | 10-speed transmission |
US7670245B2 (en) * | 2007-06-04 | 2010-03-02 | Gm Global Technology Operations, Inc. | 8-speed transmission |
US7691022B2 (en) * | 2007-07-09 | 2010-04-06 | Gm Global Technology Operations, Inc. | 9-speed transmission |
US7749125B2 (en) * | 2007-07-09 | 2010-07-06 | Gm Global Technology Operations, Inc. | 8-speed transmission |
US7731620B2 (en) * | 2007-07-09 | 2010-06-08 | Gm Global Technology Operations, Inc. | 8-speed transmission |
US7651431B2 (en) * | 2007-07-09 | 2010-01-26 | Gm Global Technology Operations, Inc. | 10-speed transmission |
US7731625B2 (en) * | 2007-07-09 | 2010-06-08 | Gm Global Technology Operations, Inc. | 9-speed transmission |
US7695398B2 (en) * | 2007-07-09 | 2010-04-13 | Gm Global Technology Operations, Inc. | 9-speed transmission |
US7628725B2 (en) * | 2007-07-09 | 2009-12-08 | Gm Global Technology Operations, Inc. | 8-speed transmission |
US7828688B2 (en) * | 2007-07-09 | 2010-11-09 | Gm Global Technology Operations, Inc. | 10-speed transmission |
US7766786B2 (en) * | 2007-07-11 | 2010-08-03 | Gm Global Technology Operations, Inc. | 8-speed transmission |
US7771306B2 (en) * | 2007-07-11 | 2010-08-10 | Gm Global Technology Operations, Inc. | 9-speed transmission |
US7736258B2 (en) * | 2007-07-19 | 2010-06-15 | Gm Global Technology Operations, Inc. | 8-speed transmission |
US8021262B2 (en) * | 2007-07-19 | 2011-09-20 | GM Global Technology Operations LLC | 8-speed transmission |
US7785227B2 (en) * | 2007-07-19 | 2010-08-31 | Gm Global Technology Operations, Inc. | 8-speed transmissions |
US7811198B2 (en) * | 2007-07-20 | 2010-10-12 | Gm Global Technology Operations, Inc. | 8-speed transmission |
US7731621B2 (en) * | 2007-07-20 | 2010-06-08 | Gm Global Technology Operations, Inc. | 8-speed transmission |
US7731622B2 (en) * | 2007-07-20 | 2010-06-08 | Gm Global Technology Operations, Inc. | 8-speed transmissions |
US7722496B2 (en) * | 2007-07-31 | 2010-05-25 | Gm Global Technology Operations, Inc. | 10-speed transmission |
US7946950B2 (en) * | 2007-08-01 | 2011-05-24 | GM Global Technology Operations LLC | 8-speed transmissions |
US7513846B2 (en) * | 2007-08-01 | 2009-04-07 | Gm Global Technology Operations, Inc. | 8-speed transmission |
US7736263B2 (en) * | 2007-08-15 | 2010-06-15 | Gm Global Technology Operations, Inc. | 9-speed transmission |
US7695395B2 (en) * | 2007-08-15 | 2010-04-13 | Gm Global Technology Operations, Inc. | 8-speed transmission |
US7766782B2 (en) * | 2007-08-16 | 2010-08-03 | Gm Global Technology Operation, Inc. | 8-speed transmission |
US7691023B2 (en) * | 2007-08-17 | 2010-04-06 | Gm Global Technology Operations, Inc. | 8-speed transmission |
US7828689B2 (en) * | 2007-08-24 | 2010-11-09 | Gm Global Technology Operations, Inc. | 8-speed transmission |
US7717819B2 (en) * | 2007-09-21 | 2010-05-18 | Gm Global Technology Operations, Inc. | 8-speed transmission |
US7695391B2 (en) * | 2007-09-21 | 2010-04-13 | Gm Global Technology Operations, Inc. | 8-speed transmission |
US7883440B2 (en) * | 2007-09-21 | 2011-02-08 | GM Global Technology Operations LLC | 8-speed transmission |
US7824303B2 (en) * | 2007-09-21 | 2010-11-02 | Gm Global Technology Operations, Inc. | 8-speed transmission |
US7887453B2 (en) * | 2008-01-31 | 2011-02-15 | GM Global Technology Operations LLC | 9-speed transmission |
US7946948B2 (en) * | 2008-01-31 | 2011-05-24 | GM Global Technology Operations LLC | 9-speed transmission |
US8052567B2 (en) * | 2008-12-04 | 2011-11-08 | GM Global Technology Operations LLC | Multi-speed transmissions |
US8113984B2 (en) * | 2009-01-12 | 2012-02-14 | GM Global Technology Operations LLC | 8-speed transmissions |
US8123649B2 (en) * | 2009-01-14 | 2012-02-28 | GM Global Technology Operations LLC | 7-speed transmissions |
US8002662B2 (en) * | 2009-01-26 | 2011-08-23 | GM Global Technology Operations LLC | Multi-speed transmissions |
US7771305B1 (en) | 2009-02-16 | 2010-08-10 | Gm Global Technology Operations, Inc. | Ten-speed transmission |
US8052566B2 (en) * | 2009-02-16 | 2011-11-08 | GM Global Technology Operations LLC | Multi-speed transmissions |
US8016713B2 (en) * | 2009-02-19 | 2011-09-13 | GM Global Technology Operations LLC | Multi-speed transmissions |
US7963877B2 (en) * | 2009-03-04 | 2011-06-21 | GM Global Technology Operations LLC | Eight-speed transmissions |
US7828690B2 (en) * | 2009-03-04 | 2010-11-09 | Gm Global Technology Operations, Inc. | Ten-speed transmissions |
US8167753B2 (en) * | 2009-03-25 | 2012-05-01 | GM Global Technology Operations LLC | 8-speed hybrid transmission |
RU2010107092A (ru) * | 2010-02-25 | 2011-08-27 | Джи Эм Глоубал Текнолоджи Оперейшнз, Инк. (Us) | Многоступенчатая планетарная коробка передач с двумя блоками двухступенчатых планетарных зубчатых передач |
RU2010107090A (ru) * | 2010-02-25 | 2011-08-27 | Джи Эм Глоубал Текнолоджи Оперейшнз, Инк. (Us) | Многоступенчатая планетарная коробка передач с двумя планетарными зубчатыми передачами и имеющая до десяти отношений скоростей переднего хода |
RU2010107093A (ru) * | 2010-02-25 | 2011-08-27 | Джи Эм Глоубал Текнолоджи Оперейшнз, Инк. (Us) | Многоступенчатая планетарная коробка передач, имеющая до десяти передаточных отношений переднего хода |
RU2010107475A (ru) * | 2010-03-01 | 2011-09-10 | Джи Эм Глоубал Текнолоджи Оперейшнз, Инк. (Us) | Многоскоростная коробка передач с двухступенчатой и простой планетарными передачами и с промежуточными валами |
RU2010107928A (ru) * | 2010-03-03 | 2011-09-10 | Джи Эм Глоубал Текнолоджи Оперейшнз, Инк. (Us) | Многоступенчатая планетарная трансмиссия с тремя тормозами и четырьмя муфтами (варианты) |
RU2010110530A (ru) * | 2010-03-19 | 2011-09-27 | Джи Эм Глоубал Текнолоджи Оперейшнз, Инк. (Us) | Коробка передач смешанного типа с планетарным механизмом и промежуточными валами |
RU2010110533A (ru) * | 2010-03-19 | 2011-09-27 | Джи Эм Глоубал Текнолоджи Оперейшнз, Инк. (Us) | Многоскоростная трансмиссия с планетарными зубчатыми передачами и промежуточными валами (варианты) |
RU2010110532A (ru) * | 2010-03-19 | 2011-09-27 | Джи Эм Глоубал Текнолоджи Оперейшнз, Инк. (Us) | Многоступенчатая коробка передач с восемью механизмами передачи крутящего момента |
RU2010112594A (ru) | 2010-03-31 | 2011-12-10 | Джи Эм Глоубал Текнолоджи Оперейшнз, Инк. (Us) | Многоступенчатая трансмиссия (варианты) |
RU2010112596A (ru) | 2010-03-31 | 2011-12-10 | Джи Эм Глоубал Текнолоджи Оперейшнз, Инк. (Us) | Многоступенчатая трансмиссия (варианты) |
RU2010112592A (ru) | 2010-03-31 | 2011-12-10 | Джи Эм Глоубал Текнолоджи Оперейшнз, Инк. (Us) | Многоступенчатая трансмиссия (варианты) |
JP6666825B2 (ja) | 2016-10-27 | 2020-03-18 | トヨタ自動車株式会社 | 車両用変速機 |
CN112610772B (zh) * | 2020-12-16 | 2022-08-02 | 大庆石油管理局有限公司 | 一种快速接头 |
Family Cites Families (13)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1909644A (en) * | 1931-06-05 | 1933-05-16 | Gen Motors Corp | Synchronizing device for transmissions |
US2221899A (en) * | 1938-06-11 | 1940-11-19 | Borg Warner | Blocker synchronizer |
US2515270A (en) * | 1946-06-26 | 1950-07-18 | Borg Warner | Synchronizing transmission |
US3078975A (en) * | 1961-06-19 | 1963-02-26 | Clark Equipment Co | Synchronizer |
US3109317A (en) * | 1961-12-01 | 1963-11-05 | Chrysler Corp | Countershaft gearing noise eliminator |
US4462489A (en) * | 1981-07-31 | 1984-07-31 | Eaton Corporation | Synchronizer spring pin |
FR2556437B1 (fr) * | 1983-12-13 | 1989-03-31 | Renault Vehicules Ind | Dispositif de synchronisation triple |
SE448182B (sv) * | 1986-03-20 | 1987-01-26 | Saab Scania Ab | Synkroniseringsmekanism vid en vexellada |
DE69111586T2 (de) * | 1990-12-24 | 1996-03-21 | Eaton Corp | Bolzenartige Synchronisiereinrichtung. |
US5092438A (en) * | 1990-12-24 | 1992-03-03 | Eaton Corporation | Synchronizer with self-energizing |
US5111922A (en) * | 1990-12-24 | 1992-05-12 | Eaton Corporation | Pre-energizer for a synchronizer |
US5161423A (en) * | 1990-12-24 | 1992-11-10 | Eaton Corporation | Self-energizing synchronizer for equalizing shift time and effort of a multi-ratio transmission |
US5078244A (en) * | 1990-12-24 | 1992-01-07 | Eaton Corporation | Self-energizing synchronizer |
-
1994
- 1994-09-26 US US08/311,982 patent/US5497867A/en not_active Expired - Fee Related
- 1994-12-19 DE DE69406416T patent/DE69406416T2/de not_active Expired - Fee Related
- 1994-12-19 ES ES94309513T patent/ES2109618T3/es not_active Expired - Lifetime
- 1994-12-19 CA CA002138430A patent/CA2138430C/en not_active Expired - Fee Related
- 1994-12-19 AT AT94309513T patent/ATE159569T1/de not_active IP Right Cessation
- 1994-12-19 EP EP94309513A patent/EP0664411B1/en not_active Expired - Lifetime
- 1994-12-22 BR BR9405098A patent/BR9405098A/pt not_active IP Right Cessation
- 1994-12-27 KR KR1019940037412A patent/KR100272205B1/ko not_active IP Right Cessation
- 1994-12-27 CN CN94120712A patent/CN1062943C/zh not_active Expired - Fee Related
- 1994-12-27 JP JP33814094A patent/JP3577610B2/ja not_active Expired - Fee Related
Cited By (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2018121419A1 (zh) * | 2016-12-30 | 2018-07-05 | 比亚迪股份有限公司 | 锁止装置、动力总成、动力传动***及车辆 |
US11053989B2 (en) | 2016-12-30 | 2021-07-06 | Byd Company Limited | Locking device, power assembly, power transmission system, and vehicle |
US11359697B2 (en) | 2016-12-30 | 2022-06-14 | Byd Company Limited | Locking device, power assembly, power transmission system, and vehicle |
CN109374521A (zh) * | 2018-11-24 | 2019-02-22 | 福州大学 | 用于测试金属橡胶摩擦耗能性能的装置及其工作方法 |
CN109374521B (zh) * | 2018-11-24 | 2024-04-16 | 福州大学 | 用于测试金属橡胶摩擦耗能性能的装置及其工作方法 |
CN113389858A (zh) * | 2020-03-13 | 2021-09-14 | 福州锐智新能源科技有限公司 | 行星齿轮变速器 |
CN113389858B (zh) * | 2020-03-13 | 2022-06-21 | 福州锐智新能源科技有限公司 | 行星齿轮变速器 |
CN114017475A (zh) * | 2021-11-10 | 2022-02-08 | 一汽解放汽车有限公司 | 一种变速装置、变速器及车辆 |
CN114017475B (zh) * | 2021-11-10 | 2023-11-21 | 一汽解放汽车有限公司 | 一种变速装置、变速器及车辆 |
CN117570159A (zh) * | 2024-01-15 | 2024-02-20 | 四川艾马仕科技有限公司 | 一种带分离功能的可变速传动总成 |
CN117570159B (zh) * | 2024-01-15 | 2024-03-19 | 四川艾马仕科技有限公司 | 一种带分离功能的可变速传动总成 |
Also Published As
Publication number | Publication date |
---|---|
BR9405098A (pt) | 1995-12-19 |
CN1062943C (zh) | 2001-03-07 |
ES2109618T3 (es) | 1998-01-16 |
US5497867A (en) | 1996-03-12 |
KR950019310A (ko) | 1995-07-22 |
CA2138430C (en) | 2000-10-03 |
JP3577610B2 (ja) | 2004-10-13 |
ATE159569T1 (de) | 1997-11-15 |
EP0664411B1 (en) | 1997-10-22 |
CA2138430A1 (en) | 1995-06-28 |
EP0664411A1 (en) | 1995-07-26 |
DE69406416D1 (de) | 1997-11-27 |
JPH07293584A (ja) | 1995-11-07 |
DE69406416T2 (de) | 1998-05-28 |
KR100272205B1 (ko) | 2000-12-01 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
CN1115016A (zh) | 具锥形帽定位销的同步器 | |
CN1070587C (zh) | 同步离合器 | |
JP3082043B2 (ja) | 二段変速歯車列組立体 | |
EP1574734B1 (en) | Synchronizer for transmission | |
CN1095950C (zh) | 同步器 | |
US20120006643A1 (en) | Double-acting synchronizer | |
CN1059491C (zh) | 自增力的摩擦环式同步器 | |
US8567582B2 (en) | Synchronizer assembly | |
EP3325854B1 (en) | Shifting apparatus | |
US4823631A (en) | Transmission synchronizer | |
JPH0457895B2 (zh) | ||
EP2682643A1 (en) | Reverse synchronizing device for manual transmission | |
US6571927B2 (en) | Transmission synchronizer pin arrangement | |
US4280370A (en) | Clutch assembly for gear-type transmission system | |
EP0897069B1 (en) | Synchronizer | |
US6467598B2 (en) | Synchronizer | |
CA2141018C (en) | Blocking mechanism for splitter type auxiliary transmission section | |
CN2312367Y (zh) | 带同步器的重型汽车变速箱 | |
JP2724742B2 (ja) | 変速機の同期噛合装置 | |
KR100314605B1 (ko) | 자활동기장치 | |
RU2627911C1 (ru) | Самозатягивающийся синхронизатор | |
KR19980034448U (ko) | 수동 변속기용 시프트 포크 결합부 윤활 구조 | |
JPH0612259Y2 (ja) | 手動変速機の同期装置 | |
CN113280113A (zh) | 一种变挡组件 | |
JPS6034520A (ja) | 同期伝動アセンブリ |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
C06 | Publication | ||
PB01 | Publication | ||
C10 | Entry into substantive examination | ||
SE01 | Entry into force of request for substantive examination | ||
C14 | Grant of patent or utility model | ||
GR01 | Patent grant | ||
C19 | Lapse of patent right due to non-payment of the annual fee | ||
CF01 | Termination of patent right due to non-payment of annual fee |