CN108350962B - 用于商用车的盘式制动器 - Google Patents

用于商用车的盘式制动器 Download PDF

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CN108350962B
CN108350962B CN201680065377.2A CN201680065377A CN108350962B CN 108350962 B CN108350962 B CN 108350962B CN 201680065377 A CN201680065377 A CN 201680065377A CN 108350962 B CN108350962 B CN 108350962B
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brake
lining
carrier
disk
disc
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CN108350962A (zh
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J·弗里克
M·莫尔纳
M·阿德龙
A·佩特施克
J·施罗普
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Knorr Bremse Systeme fuer Nutzfahrzeuge GmbH
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    • 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
    • F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
    • F16D55/02—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members
    • F16D55/22—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads
    • F16D55/224—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members
    • F16D55/225—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members the braking members being brake pads
    • F16D55/226—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members the braking members being brake pads in which the common actuating member is moved axially, e.g. floating caliper disc brakes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
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    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
    • 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
    • F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
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    • F16D55/22—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads
    • F16D55/224—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members
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    • F16D65/00—Parts or details
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    • F16D65/092—Bands, shoes or pads; Pivots or supporting members therefor for axially-engaging brakes, e.g. disc brakes
    • F16D65/095—Pivots or supporting members therefor
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    • F16D65/097—Resilient means interposed between pads and supporting members or other brake parts
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    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/02—Braking members; Mounting thereof
    • F16D65/04—Bands, shoes or pads; Pivots or supporting members therefor
    • F16D65/092—Bands, shoes or pads; Pivots or supporting members therefor for axially-engaging brakes, e.g. disc brakes
    • F16D65/095—Pivots or supporting members therefor
    • F16D65/097—Resilient means interposed between pads and supporting members or other brake parts
    • F16D65/0973—Resilient means interposed between pads and supporting members or other brake parts not subjected to brake forces
    • F16D65/0974—Resilient means interposed between pads and supporting members or other brake parts not subjected to brake forces acting on or in the vicinity of the pad rim in a direction substantially transverse to the brake disc axis
    • F16D65/0977—Springs made from sheet metal
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    • F16D65/00—Parts or details
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    • F16D65/16—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position arranged in or on the brake
    • F16D65/18—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position arranged in or on the brake adapted for drawing members together, e.g. for disc brakes
    • F16D65/183—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position arranged in or on the brake adapted for drawing members together, e.g. for disc brakes with force-transmitting members arranged side by side acting on a spot type force-applying member
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    • F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
    • F16D2055/0004—Parts or details of disc brakes
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    • F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
    • F16D2055/0004—Parts or details of disc brakes
    • F16D2055/0016—Brake calipers
    • F16D2055/0029—Retraction devices
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    • F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
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Abstract

本发明涉及一种用于商用车的盘式制动器，其包括：骑跨制动盘(4)的制动钳(2)，该制动钳相对于制动盘(4)可轴向移动地保持在车辆侧的制动器支承座(3)上，其中，制动器支承座(3)在制动盘(4)两侧分别具有衬片槽，所述衬片槽在导入侧和导出侧由制动器支承座鞍角(8)限定边界，并且制动衬片(5)定位在该衬片槽中，所述制动衬片具有衬片支承板(6)和紧固在该衬片支承板上的摩擦衬片(7)，所述盘式制动器构造为，使得每个制动衬片(5)在制动时至少在导入侧沿制动盘(4)旋转方向支撑在制动器支承座(3)上。

Description

用于商用车的盘式制动器
技术领域
本发明涉及一种用于商用车的盘式制动器。
背景技术
这样的盘式制动器也被称为滑动钳盘式制动器，已充分为人所知。在此，制动衬片(其分别包括衬片支承板和保持于其上的摩擦衬片)朝制动盘轴线的方向插入到位置固定地保持于车辆上的制动器支承座的衬片槽(Belagschacht)中。
在制动期间，当制动衬片被压向制动盘时，由于相应制动衬片的摩擦衬片与制动盘之间的摩擦锁合，故而有一扭矩沿制动盘旋转方向作用到制动衬片上，该扭矩被导出侧的制动器支承座鞍角
Figure GDA0002137673140000011
吸收。
然而，由此在制动衬片运行期间对制动衬片产生了一种所谓的切向倾斜磨损，使得所述制动衬片沿主制动方向(也就是说在商用车向前行驶时)在导入侧比在导出侧磨损更为严重。
结果便是，一旦制动衬片在较严重受磨损的区域内达到其磨损极限，就必须立刻更换该制动衬片，而在制动衬片或者说摩擦衬片的其余区域中却依然存在可利用的磨损量。
这一情况当然与始终所追求的运行成本优化相悖，之所以如此，特别是还因为商用车通常配备有许多个盘式制动器，它们都分别面临所述的问题。
虽然由现有技术已知这样的盘式制动器，其制动衬片具有形状锁合元件，这些形状锁合元件对应地嵌接到相应的制动器支承座中，但借此所建立的形状锁合却不适于防止倾斜磨损的问题。特别是，制动衬片并未在制动盘的两个旋转方向上均得以形状锁合地保持。
于是，在DE 21 38 776 A中公开了一种盘式制动器，其中，制动衬片以侧向成形的突伸部支承在制动器支承座的导槽中，在制动时，导入侧的突伸部沿径向支撑在导槽的上部壁体上，而制动器支承座在该区域内不能有效地吸收扭矩。DE 22 55 678 A探讨的主题为一种类似设计。
发明内容
本发明的目的是，研发改进一种此类型的盘式制动器，以提高制动衬片的使用寿命和降低运行成本。
该目的通过具有一种盘式制动器得以实现，该用于商用车的盘式制动器包括：骑跨制动盘的制动钳，该制动钳相对于制动盘可轴向移动地保持在安装在车辆上的制动器支承座上，其中，所述制动器支承座在制动盘两侧分别具有衬片槽，所述衬片槽在导入侧和导出侧由制动器支承座鞍角限定边界，并且制动衬片定位在该衬片槽中，所述制动衬片具有衬片支承板和紧固在该衬片支承板上的摩擦衬片，每个制动衬片在制动时沿制动盘旋转方向至少在导入侧支撑在所述制动器支承座上，制动衬片在朝向衬片槽底部的边缘区域上设有至少一个伸出的凸出部，该凸出部嵌接到贴靠着的制动器支承座鞍角的缺口中，并且制动器支承座鞍角和制动衬片以形状锁合的方式耦合，使得制动衬片通过形状锁合被保持在制动器支承座上。
按照本发明对盘式制动器的构造设计，特别是一方面对制动器支承座以及另一方面制动衬片的对应部件的构造设计，导致：在制动时作用于相应制动衬片的有效扭矩作用到制动器支承座的导入侧区域上，特别是作用到导入侧的制动器支承座鞍角上，从而制动衬片在一定程度上起到牵拉件的作用。
制动衬片通过至少一个与制动器支承座(该制动器支承座根据本发明是设置在导入侧)的形状锁合而在制动盘的两个旋转方向上均与制动器支承座以一定程度卡紧。也就是说，作用于制动衬片的扭矩首先只由制动器支承座的(特别是在此制动器支承座鞍角的)导入侧区域吸收。
在制动力矩(制动力矩可以说就是作用到制动衬片上的扭矩)较大的情况下，导入侧的制动器支承座鞍角可能会弯曲变形，而且是弯曲变形到使得制动衬片在导出侧贴靠在所配制动器支承座鞍角上的程度。无论如何，在这样的扭矩吸收作用下终究保证了：杜绝制动衬片的倾斜磨损。
制动衬片与制动器支承座之间的形状锁合可以通过不同结构型式建立。
根据本发明的一种构思，规定：相应的衬片支承板在朝向制动器支承座底部的一侧具有突伸部，该突伸部(沿制动盘旋转方向观察)贴靠在制动器支承座的至少一个支撑面上，所述支撑面由设置在衬片槽底部上的凸起构成。也可以考虑将所配制动器支承座鞍角用作另一支撑面，使得所述突伸部定位在两支撑面之间并贴靠于其上。
这两个彼此相对的支撑面(在它们之间接纳制动衬片的所配置的突伸部)相互平行地设置，并且构造成表面光滑的以及相对于制动盘切向延伸，使得制动衬片可以相对制动盘而言沿径向插入。
根据本发明，虽然制动衬片沿制动盘的两个旋转方向至少在导入侧支撑在制动器支承座上，然而优选的是，既在导入侧也在导出侧设有这种支撑，使得制动衬片可以关于径向中轴线镜像对称地构造。根据制动盘旋转方向，也就是说，根据向前行驶或者向后行驶，导入侧和导出侧发生变换。也就是说，向前行驶时的导入侧在向后行驶时变成导出侧，反之亦然。
本发明的另一变型实施方案规定：通过制动衬片与制动器支承座之间的形状锁合来实现所述支撑，为此在衬片支承板的朝向制动器支承座鞍角的边缘区域中设有卡爪状结构，该卡爪状结构具有一个接纳槽，制动器支承座鞍角的一个与其尺寸匹配的保持销插进该接纳槽之中，从而，由此还实现了制动衬片沿制动盘两个旋转方向在制动器支承座鞍角上的锁止。
替代制动衬片的卡爪状结构和制动器支承座鞍角的保持销，当然也存在如下可能性：将制动器支承座鞍角构造为卡爪状以及为制动衬片设置保持销，该保持销嵌接到制动器支承座鞍角中所构成的凹槽内。
此外，制动衬片的形状锁合元件或者说形状锁合结构是设置在衬片支承板上。
通过使制动衬片沿制动盘旋转方向既在导入侧也在导出侧以一定程度夹紧，若两个衬片槽之一构造为不带有将制动器支承座鞍角相互连接的撑杆，相应的制动衬片便可以承担撑杆的功能。
附图说明
下文将参照附图对本发明的实施例进行说明。
其示出：
图1为现有技术的盘式制动器的俯视图；
图2-23为本发明的一个实施例的不同视图；
图24为另一实施例的不同图示。
具体实施方式
在图1中绘示了按照现有技术的盘式制动器1，其具有骑跨车辆侧制动盘4的制动钳2，该制动钳相对于制动盘4的轴线D可轴向移动地支承在一个位置固定的制动器支承座3上。
在制动器支承座3中，在制动盘4两侧设置有制动衬片5，所述制动衬片分别包括一个衬片支承板6和一个紧固在该衬片支承板上的摩擦衬片7。
在此，制动衬片5定位在衬片槽中，该衬片槽在两侧由制动器支承座鞍角8限定边界。
在图2-21和图24中，分别作为细节示出了本发明的制动器支承座3，其中，图2a)表示制动器支承座3连同置入的制动衬片5的前视图，而图2b)和2c)则表示图2a)所示结构单元的放大的局部A和B。
可以看到：根据本发明，每个制动衬片5至少在导入侧，在本实例中也在导出侧，借助于形状锁合沿制动盘4的两个旋转方向x、y均保持在制动器支承座3上。
为此，制动器支承座3在制动器支承座鞍角8的区域内分别在衬片槽底部上具有一个成形的凸起9，该凸起相对于所配制动器支承座鞍角8以一定距离朝制动衬片5的方向突伸。
制动器支承座鞍角8在其朝向制动衬片5的侧面上分别具有一个支撑面12，该支撑面相对于制动盘4而言沿切向延伸，如同凸起9的支撑面12，该支撑面朝向所述制动器支承座鞍角8的支撑面12并且与之平行地延伸。
由此构成了一个凹部11，制动衬片5的一个突伸部10伸入该凹部中，所述突伸部由于侧向贴靠在制动器支承座鞍角8的和凸起9的两支撑面12上而沿制动盘4的两个旋转方向均通过形状锁合得以保持，其中，支撑面12沿制动盘4的两个旋转方向x、y构成一种支座。
图3表示制动器支承座3的底视图，在该图中可以看到：配置给相应衬片槽的制动器支承座鞍角8分别通过一个撑杆13相互连接。
在图4中可以看到制动器支承座3和制动衬片5单元的透视图，其中在此绘示的是前视图，而图5则表示出后视图，该后视图在装配位置中朝向商用车的轮辋。
图6示出了制动器支承座3连同置入的制动衬片5的俯视图。
图7至10在不同视图中作为细节示出制动器支承座3，其中，每个衬片槽的制动器支承座鞍角8都通过撑杆13相互连接。
在图12至15中绘示出制动器支承座3连同置入的制动衬片5，其中，只有一个衬片槽的制动器支承座鞍角8用撑杆13连接，而另一衬片槽的制动器支承座鞍角8则未用这样的撑杆13连接。
在此，置入的制动衬片5现在接替了撑杆13的功能，该制动衬片于是在一定程度上按照牵杆的方式起作用，更确切地说是通过如下方式，即制动衬片不仅在导入侧而且还在导出侧以成形于其上的突伸部10夹紧在凸起9与制动器支承座鞍角8之间。
图12示出了制动器支承座3的底视图，而图11a)则表示出带有撑杆13的前侧，该前侧在盘式制动器或者说制动器支承座3的装配位置中构成背离轮辋的那侧。
图11b)和11c)分别表示出一个放大的局部A(图11b)和B(图11c)。
图13示出了图11a)图示内容的透视图，而图14同样作为透视图表示出制动器支承座3连同置入的制动衬片5的背侧，该背侧(如已经述及的那样)在工作运行中朝向轮辋，在此可以清楚地看到在衬片槽的区域内没有撑杆13。
图15最后表示出制动器支承座3的俯视图。
图16至21单独示出了图11至15所示的制动器支承座3，其中，图16是按照图13的前侧，图17是制动器支承座3从前侧观察的透视图，以及图19是从背侧观察的透视侧。图18表示出按图14中图示的制动器支承座3的背侧，而图20则示出制动器支承座3的底视图，以及图21示出制动器支承座3的俯视图。
图22a)示出了制动衬片的衬片支承板6的前视图，在该制动衬片上成形有突伸部10。图22b)示出了制动衬片5的侧视图。
图23a)是制动衬片5在摩擦衬片7一方的视图，该摩擦衬片相对于衬片支承板6的外轮廓略微向内缩进，然而在轮廓形状方面是相同的。图23b)最后同样以侧视图表示出制动衬片5。
在图24中示出本发明的另一实施例。在图24a)中可以看到一个置入制动器支承座3中的制动衬片5，其中，对于在衬片支承板6上制动衬片5与制动器支承座3之间的形状锁合，正如特别是在图24c)中可以清楚地看到的那样，在彼此对置的且限定制动衬片5纵向侧面的边缘区域上构造有卡爪16，其分别具有一个凹槽17，背离衬片槽底部成形到制动器支承座鞍角8上的保持销15这样地嵌接到该凹槽中，即：使制动衬片5在制动盘4的两个旋转方向上均得以保持，更确切地说是分别通过两个形状锁合机构中的一个形状锁合机构。
在图24b)中，放大示出了在图24a)的一个局部部分中制动衬片5的连接情况。在此，如同在作为细节表示出制动衬片5的图24c)中那样，可以看到：在衬片支承板6上在与卡爪16相对置的那侧成形有一个凸出部14，该凸出部嵌接到制动器支承座鞍角8的一个与之匹配的接纳部中。
附图标记列表
1 盘式制动器
2 制动钳
3 制动器支承座
4 制动盘
5 制动衬片
6 衬片支承板
7 摩擦衬片
8 制动器支承座鞍角
9 凸起
10 突伸部
11 凹部
12 支撑面
13 撑杆
14 凸出部
15 保持销
16 卡爪
17 凹槽

Claims (2)

1.用于商用车的盘式制动器，其包括：骑跨制动盘(4)的制动钳(2)，该制动钳相对于制动盘(4)可轴向移动地保持在安装在车辆上的制动器支承座(3)上，其中，所述制动器支承座(3)在制动盘(4)两侧分别具有衬片槽，所述衬片槽在导入侧和导出侧由制动器支承座鞍角(8)限定边界，并且制动衬片(5)定位在该衬片槽中，所述制动衬片具有衬片支承板(6)和紧固在该衬片支承板上的摩擦衬片(7)，其特征在于：每个制动衬片(5)在制动时沿制动盘(4)旋转方向至少在导入侧支撑在所述制动器支承座(3)上，制动衬片(5)在朝向衬片槽底部的边缘区域上设有至少一个伸出的凸出部，该凸出部嵌接到贴靠着的制动器支承座鞍角(8)的缺口中，并且制动器支承座鞍角(8)和制动衬片(5)以形状锁合的方式耦合，使得制动衬片(5)通过形状锁合被保持在制动器支承座(3)上。
2.如权利要求1所述的盘式制动器，其特征在于：制动衬片(5)在至少导入侧的边缘区域上具有卡爪(16)，该卡爪带有凹槽(17)，所配制动器支承座鞍角(8)的保持销(15)嵌接到该凹槽中；或者制动器支承座鞍角(8)在其自由端部构造为卡爪，该卡爪带有凹槽，制动衬片(5)的保持销嵌接到该凹槽中。
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US10801565B2 (en) 2020-10-13
US11060573B2 (en) 2021-07-13
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RU2694692C1 (ru) 2019-07-16
WO2017060512A1 (de) 2017-04-13
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US20210277967A1 (en) 2021-09-09
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