CN112703137B - 制动控制阀装置 - Google Patents
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Abstract
本发明涉及一种被配置为提供紧急制动的电动气动轨道制动系统,其包括控制气流进入到紧急调节阀(15)中的紧急电磁阀(19),该阀具有紧急备用室。紧急调节器提供额定等于可变负载压力且不低于皮重备用的输出压力。电磁阀(19)在通电时关闭,并且在断电时压力被允许进入到紧急备用室。在紧急施加期间持续调节制动缸压力,从而在紧急停止期间所施加的制动缸压力不会下降低于预定水平。在紧急制动停止期间如果失去动力,则对制动缸施加额定紧急制动压力。
Description
技术领域
本发明涉及一种用于铁路车辆制动系统的轨道车辆用的电动气动制动系统,并且尤其涉及一种用于使用在远程释放和紧急制动功能中的排气阀装置。
背景技术
在诸如EP1588913和GB2359599中公开的已知系统中,设定了可用的气动制动力,从而利用其当前负载来支持车辆的最大减速所需的制动力是可用的,并且可以对制动缸施加该制动力以提供全气动紧急制动停止。在行车制动期间,根据实际制动需求(例如选定的制动踏板)和由其他制动子系统(例如电动制动器或轨道制动器)提供的制动力,所施加的制动压力(即制动缸中的压力)被调节到低于可用压力的水平。
该系统已实地进行了验证,但遭受到在制动施加过程中可能发生的制动衬块摩擦变化以及可能使任何转向架上的制动致动产生与根据制动系统规格计算出的制动力不同的制动力的任何机械因素的影响。这些机械效应会导致列车的制动不足和过度制动。
WO2011086029公开了一种铁路车辆的具有紧急制动器的制动装置,该紧急制动器包括以断电原理工作以进行关闭的螺线管,该螺线管在正常操作时被供电并保持在打开位置。尚未商业化的这种系统遇到类似的问题。
发明内容
本发明的任务在于提供一种能够实现更精确控制制动压力的制动系统,从而导致制动不足或过度制动的较小的可能性,特别是但并非排他性地在紧急制动期间。
根据本发明,提供了一种用于轨道车辆的电动气动制动系统,所述电动气动制动系统被配置为提供紧急制动并具有用于施加制动力的制动缸,所述制动系统包括控制气流进入到紧急调节阀中的紧急电磁阀,该紧急调节阀具有紧急备用室,所述紧急调节阀适于提供额定等于可变负载压力且不低于皮重备用设定的输出压力,并且所述紧急电磁阀由第一电子控制单元控制,该第一电子控制单元能够调节制动缸压力,并且所述紧急电磁阀在通电时关闭,其特征在于,当所述紧急电磁阀断电时允许压力进入到所述紧急备用室,在紧急施加期间所述第一电子控制单元持续调节制动缸压力,从而在紧急停止期间所施加的制动缸压力不会下降低于预定水平,并且如果在紧急制动停止期间失去电力,则对所述制动缸施加额定紧急制动压力。
对于给定的制动踏板,本构思有利地提供了所期望的车辆减速率,而独立于在制动施加过程中可能发生的制动衬块摩擦变化以及可能使任何转向架上的制动致动产生与根据制动系统规格计算出的制动力不同的制动力的任何机械因素。
附图说明
现在将参照附图详细地描述本发明的示例性实施例,在附图中:
图1显示了制动阀装置的气动示意图;
图2显示了远程释放阀17和关联的压力控制器的示意图。
具体实施方式
为了允许对气动制动(紧急制动和行车制动)进行减速控制,可用的制动力必须被设定在高于从制动规格推导出的制动力的水平,以便在制动施加过程中能够增大制动力,以弥补由制动系统的机械部件(包括制动衬块)引起的制动力的任何减小。根据控制算法,制动力的减小可以是列车范围的或节段范围的。同样,减速控制可能需要减小制动力,因此需要减小所施加的制动压力,从而抵消由制动系统的机械性能引起的任何过度制动。
图1显示了制动阀装置的气动示意图,其包括歧管1,歧管1接收主制动供应压力2并提供与制动缸3、4的气动连接。该歧管提供来自可选的外部负载连接部5和分配阀7的进一步气动连接。负载重量输入在标准使用中由一个或两个辅助传感器测量。
气动阀单元8容纳主继动调节器9,该主继动调节器从制动供应压力2接收输入压力。主继动调节器9的出口经由在下面更详细描述的配置模块14连接到控制阀12、13的相应入口10、11。
主继动调节器9由来自提供皮重备用设定水平的紧急调节器15和挤压调节器16的压力主导。各调节器限制先导压力水平。双止回阀18和紧急调节器的输出主导主继动调节器9。皮重备用设定是在可变负载控制压力(VLCP)的压力小于皮重设定的紧急情况下可用的最小压力。挤压调节器的设定水平是VLCP控制阀可用的最大压力。紧急调节器15经由紧急制动回路螺线管19连接到主供应压力2和主继动调节器9的先导输入。
挤压调节器16从主制动供应压力2接收气动输入,出口连接到进气排气阀装置,该进气排气阀装置控制到远程释放阀17的实际压力,该远程释放阀连接到主继动调节器9的出口。因此,挤压调节器经由远程释放阀17连接到主继动调节器9。可选的低重量连接部设有通往远程释放阀17入口的路径。在远程释放阀17和主继动调节器9之间的路径中设有双止回阀18,该双止回阀也气动地连接到间接制动输入7上。
控制阀12、13分别包括由相应的螺线管和另一个螺线管控制的进气排气膜片阀,这两个螺线管被布置成使得排气膜片上的压力均衡。控制阀12和13的出口连接到相应的制动缸。包括膜片阀和螺线管的联接阀在各个控制阀12、13的出口之间提供气动连接。
如上所述,主继动调节器9的出口连接到配置模块14。配置模块14在从主继动调节器9到相应的入口膜片的入口的气动路径20、21中设有相应的节流部。入口膜片的出口经由配置模块14中的相应的节流部22、23气动地连接到排气膜片。排气膜片经由配置模块对制动缸进行排气。
在使用时,制动施加时间和排气时间由节流孔的尺寸决定,这些节流孔能够实现标准的或所期望的要实现的施加和释放时间,而与制动缸容积无关。这确保了可预测的制动缸压力控制和车轮防滑保护性能。
在本发明中,为了提供减速控制功能,在紧急施加期间(通过微控制器)持续调节制动缸压力。然而,制动控制器必须确保在紧急停止期间施加的制动缸压力不会下降到最小水平以下,并且在紧急制动停止期间失去电力的情况下确保额定紧急制动压力(在为车辆当前负载提供所需的紧急减速时根据制动计算确定的压力)施加到制动缸上。
此外,为了确保制动阀装置(理想情况下对于紧急制动为SIL3)在由微控制器(通常为SIL2)调节制动缸压力的同时提供最小水平的紧急制动力,制动缸压力由电子设备或电子逻辑设备(FPGA)独立监控,电子设备或电子逻辑设备(FPGA)将检测制动缸压力下降低于预配置的百分比的额定紧急制动压力的情况。
同样,该监控系统还可以确保所施加的制动压力不会超过预定上限,从而提供过度制动保护。制动不足保护只有在紧急制动施加期间才激活;否则,制动释放和低制动踏板在行车制动模式中是不可能的。过度制动保护在紧急制动模式和行车制动模式中均激活。
在紧急制动模式中,制动缸的监控电子设备或逻辑设备禁止微控制器对制动缸压力调节(因此也禁用头端设备的控制),并以类似于标准已知的紧急制动施加的方式在制动缸处施加额定紧急压力水平。
在行车制动操作中,制动缸的监控电子设备或逻辑设备将操作以释放制动缸压力(在检测到过压时)。这与下面描述的释放功能兼容。
如果WSP在紧急制动施加期间保持操作(如果该单元被供电),则在受控紧急制动激活时可发生WSP操作。为了控制车轮滑动并在紧急制动停止期间优化可用的附着力,WSP控制活动可能导致制动缸压力下降低于针对受控紧急制动限定的最小压力。可以提供监控电子设备,以防止在检测到欠压的情况下立即中断功能。由于这种压力降低是可以接受的,因此通过WSP系统控制制动缸压力将防止监控电子设备/逻辑设备强行欠压跳闸。由监控电子设备/逻辑设备使用的WSP活动在致动阀时被检测到,因此由WSP控制对压力进行的任何调节(保持或排气)都会禁用欠压跳闸。WSP操作本身由高完整性(SIL3)电子设备(或电子逻辑设备)监控,以防止由WSP控制长时间降低制动缸压力。这些电子设备的操作将确保由WSP操作无法持续驱动阀以维持低压,从而确保不会永久防止监视电子设备/逻辑设备在欠压条件下工作。
图2示出了远程释放阀17和关联的压力控制器的示意图。远程释放阀具有以下端口连接:端口1:压力控制器;端口2:继动阀控制室;连接到大气的端口3。
当远程释放阀17(螺线管)断电时:端口2连接到端口3,端口1阻塞;当该远程释放阀通电时,端口1连接到端口2,端口3阻塞。等效于图1中的继动阀9的气动继动阀具有的控制输入输出比=1:1。
阀装置提供或实现以下功能:
如果失去对制动控制阀的电力供应,则应释放行车制动(如果施加的话),并进一步防止重新施加。在正常运行条件下,这是通过在电磁阀17通电从而通过阀的端口2至端口1将控制室连接到VLCP压力控制器上时可用的电力实现的。继动阀提供的输出等于行车制动进行控制的VLCP。
如果失去电力,螺线管17会断电并脱离,从而通过阀的端口2至端口3将控制室压力排放到大气。继动阀现在将输出压力排放至零;任何制动缸压力现在将反馈通过行车制动控制膜片,因为如果去除了供应压力,这些膜片将无法保持压力。因此实现了制动释放,并且去除了对保持阀中的膜片的供应压力,从而防止任何随后的行车制动施加。
如果受控紧急制动超过安全范围,则FPGA将超越受控紧急制动,并仅施加气动受控负载加权紧急制动。这是通过禁用行车制动器(即打开保持阀和关闭排气阀)并对控制室排气电磁阀17断电来实现的。这通过电磁阀端口2至端口3将控制室压力排放到大气。该压力可以被设定为负载加权水平的增强值,以便能够实现紧急制动功能。所述增强值的示例值是125%。
控制室膜片有效面积在控制室和输出压力之间提供1:1的比率。如果控制室没有排气,则至制动缸的输出压力将为所需的负载加权水平的125%,即25%为过度制动。
在启动紧急制动施加时,受控的紧急制动将变为激活的,在通电时关闭的紧急电磁阀将会脱离,从而允许压力进入紧急备用室。压力水平由紧急调节器设定。紧急调节器被设计成用于提供额定等于可变负载压力VLCP且不低于皮重备用设定的输出压力。
紧急备用室膜片的有效面积在紧急备用室和输出压力之间提供0.8:1的比率——0.8是负载重量水平的增强值的倒数。但是,它与控制室的比率为1:1。在受控紧急制动期间,在控制室和紧急备用室中的压力相等。因此,对膜片堆没有叠加的向下力。
如果FPGA决定超越受控紧急制动并从控制室排出VLCP压力,则现在去除在紧急备用室膜片的底侧上的平衡力。
当控制室排气螺线管断电时,VLCP压力被锁定。这确保用于维持紧急备用室压力的紧急调节器的参考压力为额定负载加权水平的125%。
在控制室压力排气的情况下,从紧急室膜片施加的力现在通过膜片堆激活。该力由作用在控制膜片的底侧上的制动缸压力进行平衡。由于紧急备用室膜片与制动缸膜片之比为0.8:1.0,这将制动缸中的输出压力校正为额定负载加权值,即1.25x 0.8=1。
如果在制动控制阀内检测到故障,例如“拉曳制动”,则允许释放行车制动(如果施加的话),并进一步防止重新施加。该功能是通过直接输入到FPGA的外部数字输入来实现的。当FPGA接收到该信号时,它禁止对断电的螺线管17进行驱动。
当螺线管17断电时,控制室排气。继动阀现在将输出压力排放至零;任何制动缸压力现在将反馈通过行车制动控制膜片,因为如果去除了供应压力,这些膜片将无法保持压力。因此实现了制动释放,并且去除了对膜片的供应压力,从而防止任何随后的行车制动施加。
进一步的操作模式允许列车中具有故障的直接制动或电力供应问题的车辆由救援机车或应急列车移动。
当控制室电磁阀断电时,控制室排气。继动阀现在将输出压力排放至零;任何制动缸压力现在将反馈通过行车制动控制膜片,并且将实现制动释放。
现在,第一间接制动压力施加将切换双止回阀18,从而关闭通过电磁阀(端口2至端口3)排气的路径,并将间接制动输入端口连接至控制室。
紧急制动回路(EBL)19必须高,以便在此操作模式中实现制动释放。如果EBL下降到低水平,则在制动缸中产生的输出将取决于两个室(控制室或紧急备用室)中的哪一个室提供最大的力。
Claims (6)
1.一种用于轨道车辆的电动气动制动系统,所述电动气动制动系统被配置为提供紧急制动并具有用于施加制动力的制动缸,所述制动系统包括控制气流进入到紧急调节阀(15)中的紧急电磁阀(19),该紧急调节阀具有紧急备用室,所述紧急调节阀(15)适于提供额定等于可变负载压力且不低于皮重备用设定的输出压力,并且所述紧急电磁阀(19)由第一电子控制单元控制,该第一电子控制单元能够调节制动缸压力,并且所述紧急电磁阀在通电时关闭,
其特征在于,当所述紧急电磁阀断电时允许压力进入到所述紧急备用室,在紧急施加期间所述第一电子控制单元持续调节制动缸压力,从而在紧急停止期间所施加的制动缸压力不会下降低于预定水平,并且如果在紧急制动停止期间失去电力,则对所述制动缸施加额定紧急制动压力。
2.根据权利要求1所述的电动气动制动系统,其中,所述系统包括第二电子控制单元,用以在所述第一电子控制单元调节所述制动缸压力的同时提供预定水平的紧急制动力,所述制动缸压力由所述第二电子控制单元独立监控,该第二电子控制单元适于检测所述制动缸压力何时下降低于预定量或百分比的所述额定紧急制动压力。
3.根据权利要求2所述的电动气动制动系统,其中,所述第二电子控制单元适于确保所施加的制动压力不会超过预定上限。
4.根据权利要求1至3任一项所述的电动气动制动系统,其中,制动不足保护仅在紧急制动施加期间激活。
5.根据权利要求1至3任一项所述的电动气动制动系统,其中,过度制动保护在紧急制动模式和行车制动模式中均激活。
6.根据权利要求2所述的电动气动制动系统,其中,在紧急制动期间,所述第二电子控制单元禁止所述第一电子控制单元进行制动缸压力调节并且对所述制动缸施加所述额定紧急制动压力。
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