CN1693719A - 具有改进响应特性闭锁阀的液压控制阀 - Google Patents
具有改进响应特性闭锁阀的液压控制阀 Download PDFInfo
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- F16L—PIPES; JOINTS OR FITTINGS FOR PIPES; SUPPORTS FOR PIPES, CABLES OR PROTECTIVE TUBING; MEANS FOR THERMAL INSULATION IN GENERAL
- F16L25/00—Constructive types of pipe joints not provided for in groups F16L13/00 - F16L23/00 ; Details of pipe joints not otherwise provided for, e.g. electrically conducting or insulating means
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- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
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- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
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- F16L—PIPES; JOINTS OR FITTINGS FOR PIPES; SUPPORTS FOR PIPES, CABLES OR PROTECTIVE TUBING; MEANS FOR THERMAL INSULATION IN GENERAL
- F16L13/00—Non-disconnectible pipe-joints, e.g. soldered, adhesive or caulked joints
- F16L13/14—Non-disconnectible pipe-joints, e.g. soldered, adhesive or caulked joints made by plastically deforming the material of the pipe, e.g. by flanging, rolling
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- F16L13/142—Non-disconnectible pipe-joints, e.g. soldered, adhesive or caulked joints made by plastically deforming the material of the pipe, e.g. by flanging, rolling by crimping or rolling from the outside with a sealing element inserted into the female part before crimping or rolling
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- F15B2211/305—Directional control characterised by the type of valves
- F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
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- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
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- F15B2211/00—Circuits for servomotor systems
- F15B2211/30—Directional control
- F15B2211/31—Directional control characterised by the positions of the valve element
- F15B2211/3105—Neutral or centre positions
- F15B2211/3116—Neutral or centre positions the pump port being open in the centre position, e.g. so-called open centre
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- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
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- F15B2211/315—Directional control characterised by the connections of the valve or valves in the circuit
- F15B2211/31523—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source and an output member
- F15B2211/31529—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source and an output member having a single pressure source and a single output member
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- F15B2211/3157—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source, an output member and a return line
- F15B2211/31576—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source, an output member and a return line having a single pressure source and a single output member
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- F15B2211/00—Circuits for servomotor systems
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
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- F15B2211/00—Circuits for servomotor systems
- F15B2211/40—Flow control
- F15B2211/405—Flow control characterised by the type of flow control means or valve
- F15B2211/40515—Flow control characterised by the type of flow control means or valve with variable throttles or orifices
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
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- F15B2211/40—Flow control
- F15B2211/41—Flow control characterised by the positions of the valve element
- F15B2211/413—Flow control characterised by the positions of the valve element the positions being continuously variable, e.g. as realised by proportional valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
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- F15B2211/00—Circuits for servomotor systems
- F15B2211/40—Flow control
- F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
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- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
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- F15B2211/00—Circuits for servomotor systems
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- F15B2211/505—Pressure control characterised by the type of pressure control means
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- F15B2211/50581—Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure using counterbalance valves
- F15B2211/5059—Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure using counterbalance valves using double counterbalance valves
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- F15B2211/6355—Circuits providing pilot pressure to pilot pressure-controlled fluid circuit elements having valve means
Abstract
公开了一种具有改进响应特性闭锁阀的液压控制阀。液压控制阀包括:阀套,其包括与液压泵连通的泵通道,与油箱连接的箱的通道,和与液压缸连接的第一和第二汽缸通道;可移动地设置在阀套中的控制阀芯,在中立状态下将泵通道切断于第一和第二汽缸端口,并且如果控制信号压力作用到其上而沿左右方向移动时,选择性地将泵通道和油箱通道连接于第一和第二汽缸端口;设置在第二汽缸端口和控制阀芯之间的闭锁阀,当控制阀芯处在中立状态时切断第二汽缸端口并且保持液压缸的负载,从而不会引起液压缸的自然下落;以及闭锁阀的启动通道,当控制阀芯处在中立状态时该启动通道将第二汽缸端口的液压油连接到油箱通道。
Description
技术领域
本发明涉及一种液压控制阀,特别涉及一种具有改进响应特性闭锁阀的液压控制阀,其中提供有闭锁阀的启动通道以改进闭锁阀的响应特性,从而减小液压缸的自然下降。
背景技术
通常,诸如挖土机的重型建筑设备设置有工作装置,例如吊杆、臂、和铲斗。重型建筑设备由液压缸驱动并且能进行多种操作。液压缸由液压泵供给的液压油操作。液压控制阀设置在液压泵和液压缸之间,用来将液压油从液压泵供给到液压缸。工作装置的驱动方式为,当驾驶员操纵控制杆时,操作液压控制阀以控制向液压缸供给的液压油的压力、方向、和流量。
工作装置被制造得庞大以承受巨大的载荷和恶劣的工作条件。在工作装置空置的中立状态中,由于大量工作装置负载和货物负载,一些液压油通过液压控制阀阀芯和阀套的间隙泄漏。为此,工作装置可能自然下落(natural drop)。因此,固定于重型建筑设备的液压系统包括能防止在中立状态下由于负载而发生自然下落的闭锁阀。
图1是示出相关技术的具有闭锁阀的液压控制阀的线路图,图2是示出相关技术的具有闭锁阀的液压控制阀的部分剖视图。
相关技术液压控制阀100包括阀套110,设置在阀套110中的控制阀芯120,其能被控制信号压力‘a’与‘b’切换以控制液压油的流量和方向,和闭锁阀130。阀套110包括与液压泵2连通的泵通道111,与油箱4连通的油箱通道112,和与液压缸3连通的第一和第二汽缸端口113和114。
如图所示,如果控制阀芯120处于中立状态,液压泵2的液压油被喷射到油箱4。闭锁阀130包括设置在第二汽缸端口114和控制阀芯120之间的闭锁提升阀(holding poppet)131,和向闭锁提升阀131的后压力腔134提供液压油或者切断闭锁提升阀131的后压力腔134的液压油的排泄阀132。在控制阀芯120处于中立的状态下,液压缸3的液压油通过汽缸端口114和闭锁提升阀131的孔133流入到闭锁提升阀131的后压力腔134内。因此,从图中可以看出,闭锁提升阀131被上下施压,从而液压缸3的液压油不会泄漏到油箱4中。
在这种状态下,如果控制信号压力‘a’和‘b’作用在控制阀芯120左右侧的控制端口120a和120b上,那么控制阀芯120被切换到左侧或右侧,从而液压泵2的液压油可以流入到第一汽缸端口113或第二汽缸端口114以驱动液压缸3。
如果当控制信号压力‘a’作用在控制阀芯120右侧的控制端口120a从而控制阀芯120被切换到左侧时,液压泵2的液压油流入到第一汽缸端口113内以驱动液压缸3。同时,控制信号压力‘c’作用在排泄阀132上,从而排泄阀132可以被切换到右侧并且闭锁提升阀131可以被打开以向油箱4喷射液压缸3的液压油。
然而,在这种情况下,如果控制阀芯120切换到中立状态,连接于闭锁提升阀131的连接管路115被切断。因此,连接管路115和第二汽缸端口114受到相同的压力。这时,由于通过打开的闭锁提升阀131从液压缸3提供的液压油通过第二汽缸端口114和连接管路115作用在控制阀芯120上,因此由于液压缸3的负载,液压油会通过控制阀芯120和阀套110泄漏。由于泄漏的油不是小量而是大量的,因此它作用使得工作装置的自然下落。
如果由于在工作装置自然下落时连接管路115的液压油泄漏,连接管路115的压力变得比第二汽缸端口114中的压力小,闭锁提升阀131被关闭以防止发生油的泄漏。然而,在连接管路115的压力变得比第二汽缸端口114中的压力小后,在闭锁提升阀131关闭之前发生时间延迟。在时间延迟段内发生油的泄漏。
如上所述,由于在相关技术的液压控制阀100中闭锁阀130的响应速度低,因此传统上通过增加闭锁提升阀131的孔133的截面积来增加供给到后压力腔134中的液压油,从而避免液压缸3过度的自然下落。然而,这对从根本上解决闭锁阀130的时间延迟来说是失败的。同样,如果孔133的截面积增加,当工作装置开始操作或者由于后压力腔134中液压油的增加而后压增加时,发生振荡,从而导致不稳定的工作压力。
发明内容
因此,本发明涉及具有改进响应特性闭锁阀的液压控制阀,完全消除了由于相关技术的局限和缺点导致的一个或多个问题。
本发明的一个目的是提供一种具有改进响应特性闭锁阀的液压控制阀,其中通过改进闭锁阀的响应特性减小液压缸的自然下落,从而改进稳定性和可靠性。
本发明的另一个目的是提供一种具有改进响应特性闭锁阀的液压控制阀,其中设置有闭锁阀的启动通道以减小液压缸的自然下落。
为了实现这些目的和其他的优点并且根据本发明的目的,如这里实施并宽泛描述的,一种具有改进响应特性闭锁阀的液压控制阀包括:阀套,其包括与液压泵连通的泵通道,与油箱连通的油箱通道,和与液压缸连通的第一和第二汽缸端口;可移动地设置在阀套中的控制阀芯,在中立状态下切断泵通道与第一和第二汽缸端口,并且如果控制信号压力作用到其上而沿左右方向移动时,选择地将泵通道和油箱通道连接于第一和第二汽缸端口;设置在第二汽缸端口和控制阀芯之间的闭锁阀,当控制阀芯处在中立状态时切断第二汽缸端口并且保持液压缸的负载,以便不引起液压缸的自然下落;以及闭锁阀的启动通道,当控制阀芯处在中立状态时该启动通道将第二汽缸端口的液压油连接到油箱通道。
优选地,启动通道是形成在控制阀芯表面上的具有预定长度和宽度的槽或者孔。
优选地,启动通道是成形为穿过第二汽缸端口和油箱通道的排泄孔。
优选地,启动通道由设置在第二汽缸端口和控制阀芯之间的单独的侧阀形成。
附图说明
通过参考附图描述本发明特定的实施例,可以更加明了本发明上述的方面和特征,其中:
图1是示出相关技术的液压控制阀的线路图;
图2是示出相关技术的液压控制阀的部分剖视图;
图3是示出根据本发明具有改进响应特性闭锁阀的液压控制阀的线路图;和
图4是示出根据本发明具有改进响应特性闭锁阀的液压控制阀的部分剖视图。
具体实施方式
现在将详细地参考本发明的优选实施例,它们的例子在附图中示出。尽可能地,在整个附图中相同的标号将表示相同或类似的部分。
图3是示出根据本发明具有改进响应特性闭锁阀的液压控制阀的线路图,图4是示出根据本发明具有改进响应特性闭锁阀的液压控制阀的部分剖视图。
根据本发明的液压控制阀1包括阀套10,设置在阀套10中的控制阀芯20,闭锁阀30,和闭锁阀的启动通道40。
阀套10包括泵通道11,油箱通道12,以及第一汽缸端口13和第二汽缸端口14。泵通道11与喷射液压油的液压泵2连通。油箱通道12与存储液压油的油箱4连通。第一汽缸端口13和第二汽缸端口14与液压缸3连通。
控制阀芯20可移动地设置在阀套10中。如果控制信号压力‘a’与‘b’输入到控制阀芯20,则控制阀芯20抵着阀套10向左侧或右侧移动,从而泵通道11和油箱通道12可以选择地连接于第一和第二汽缸端口13和14。如果控制信号压力没有输入到控制阀芯20而控制阀芯20处在中立状态,那么第一和第二汽缸端口13和14从泵通道11切断。在该情况下,由于液压油没有供给到汽缸端口,因此液压缸3处在空置状态。
如上所述,控制阀芯20向液压缸3提供从液压泵2供给的液压油或切断向液压缸3提供由液压泵2所供给的液压油。可选地,控制阀芯20收集液压缸3的液压油向油箱4中喷射。因此,控制阀芯20用于控制液压缸3的驱动、停止、和切换。
闭锁阀30包括设置在阀套10的第二汽缸端口14上的闭锁提升阀31,和向闭锁提升阀31的后压力腔34供给液压油或切断闭锁提升阀31的后压力腔34的液压油的排泄阀32。在控制阀芯20处于中立的状态下,闭锁阀30通过切断第二汽缸端口14来保持液压缸3的负载。结果,不发生液压缸3的自然下落。
闭锁阀的启动通道40用来将第二汽缸端口14的液压油连接到油箱通道12,从而在控制阀芯20中立时改进闭锁阀30的响应特性。优选地,通过在控制阀芯20的表面上加工具有预定长度和宽度的槽或洞形成启动通道40。利用控制阀芯,槽或洞将第二汽缸端口连接于重现芯部。当控制阀芯20中立时,第二汽缸端口14的液压油能够通过重现芯部喷射到油箱通道12。在这种情况下,虽然未示出,但重现芯部通过处理提升阀连接于油箱通道。
同样,虽然未示出,但启动通道40可以通过加工从第二汽缸端口以预定距离通到油箱通道的排泄孔而形成。或者,启动通道40可以通过在第二汽缸端口14和控制阀芯20之间加工单独的侧阀形成。
下面将描述上述具有改进响应特性闭锁阀的液压控制阀的操作。
如在图3和图4中所示,当控制信号压力‘a’和‘b’没有输入控制阀芯40从而控制阀芯40处于中立时,第一和第二汽缸端口13和14切断于泵通道11。在这种情况下,由于液压泵2的液压油没有供给到液压缸3,所以液压缸3不工作。
液压缸3的液压油通过第二汽缸端口14和闭锁提升阀31的孔33流入到闭锁提升阀31的后压力腔34内。因此,闭锁提升阀31向下加压以切断第二汽缸端口14,从而液压缸3的液压油不会被喷射到油箱4中。结果,闭锁阀30保持液压缸3的负载,从而不会导致液压缸3的自然下落。
如果控制信号压力‘a’作用到控制阀芯20右侧的控制端口21上,控制阀芯20被切换到左侧,从而泵通道11可以与第一汽缸端口13连结并且液压泵2的液压油可以供给到液压缸3以驱动液压缸3。
当控制信号压力‘a’应用于控制阀芯20时,控制信号压力‘c’作用在排泄阀32上,从而排泄阀32可以切换到右侧以打开闭锁提升阀31,从而通过闭锁提升阀31将液压缸3的液压油喷射到油箱4。
在这种状态下,如果控制阀芯20被切换到中立状态,连接控制阀芯20和第二汽缸端口14的连接管路15通过启动通道40连接于油箱通道12。因此,如果控制阀芯20切换到中立状态,连接管路15的液压油被迅速地喷射到油箱4。在这种状态下,由于连结管路15的压力变得比第二汽缸端口14的压力小,因此闭锁阀30的闭锁提升阀31向下移动以保持液压缸3的负载。
换句话说,通过启动通道40的作用可以无时间延迟地驱动闭锁提升阀31,所以闭锁阀30可以保持液压缸3的负载。这样,由于可以显著地改进闭锁阀30的响应特性,因此不会发生由于时间延迟产生的液压缸3过多的自然下落。
如上所述,具有改进响应特性的闭锁阀的液压控制阀有如下的优点。
由于通过闭锁阀的启动通道改进了闭锁阀的响应特性,因此减小了液压缸的自然下落,从而改进了液压控制阀的稳定性和可靠性。
前述的实施例和优点仅仅是说明性的,不应认为是对本发明的限制。本发明能够容易地应用于其他类型的装置。而且,本发明实施例的说明的目的是示意性的,不是限制权利要求书的范围,并且许多改变、修改和变型对本领域的技术人员来说是显而易见的。
Claims (4)
1.一种具有改进响应特性闭锁阀的液压控制阀,包括:
阀套,其包括与液压泵连通的泵通道,与油箱连通的油箱通道,和与液压缸连通的第一和第二汽缸端口;
可移动地设置在阀套中的控制阀芯,在中立状态下将泵通道切断于第一和第二汽缸端口,并且如果控制信号压力作用到其上而沿左右方向移动时,选择性地将泵通道与油箱通道连接于第一和第二汽缸端口;
设置在第二汽缸端口和控制阀芯之间的闭锁阀,当控制阀芯处在中立状态时切断第二汽缸端口并且保持液压缸的负载,从而不会引起液压缸的自然下落;以及
闭锁阀的启动通道,当控制阀芯处在中立状态时该启动通道将第二汽缸端口的液压油连接于油箱通道。
2.根据权利要求1所述的具有改进响应特性的闭锁阀的液压控制阀,其中启动通道是形成在控制阀芯表面上的具有预定长度和宽度的槽或者孔。
3.根据权利要求1所述的具有改进响应特性的闭锁阀的液压控制阀,其中启动通道是形成为穿过第二汽缸端口和油箱通道的排泄孔。
4.根据权利要求1所述的具有改进响应特性的闭锁阀的液压控制阀,其中启动通道通过设置在第二汽缸端口和控制阀芯之间的单独的侧阀形成。
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EP1593855A2 (en) | 2005-11-09 |
KR100631067B1 (ko) | 2006-10-02 |
US20050247188A1 (en) | 2005-11-10 |
US7162946B2 (en) | 2007-01-16 |
DE602005006884D1 (de) | 2008-07-03 |
JP2005321094A (ja) | 2005-11-17 |
CN100387851C (zh) | 2008-05-14 |
EP1593855B1 (en) | 2008-05-21 |
EP1593855A3 (en) | 2005-12-07 |
KR20050106233A (ko) | 2005-11-09 |
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