CN101184923B - 液压系统及其操作方法以及使用该液压系统的工作机器 - Google Patents

液压系统及其操作方法以及使用该液压系统的工作机器 Download PDF

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CN101184923B
CN101184923B CN2006800184757A CN200680018475A CN101184923B CN 101184923 B CN101184923 B CN 101184923B CN 2006800184757 A CN2006800184757 A CN 2006800184757A CN 200680018475 A CN200680018475 A CN 200680018475A CN 101184923 B CN101184923 B CN 101184923B
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valve
fluid
actuator
pressure
fluid actuator
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CN101184923A (zh
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章佼
马鹏飞
M·R·施瓦布
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Caterpillar Japan Ltd
Caterpillar Inc
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Shin Caterpillar Mitsubishi Ltd
Caterpillar Inc
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
    • F15B11/044—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the return line, i.e. "meter out"
    • F15B11/0445—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the return line, i.e. "meter out" with counterbalance valves, e.g. to prevent overrunning or for braking
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2221—Control of flow rate; Load sensing arrangements
    • E02F9/2225—Control of flow rate; Load sensing arrangements using pressure-compensating valves
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/226—Safety arrangements, e.g. hydraulic driven fans, preventing cavitation, leakage, overheating
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2278—Hydraulic circuits
    • E02F9/2296—Systems with a variable displacement pump
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/003—Systems with load-holding valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/006—Hydraulic "Wheatstone bridge" circuits, i.e. with four nodes, P-A-T-B, and on-off or proportional valves in each link
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
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    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
    • F15B11/05—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed specially adapted to maintain constant speed, e.g. pressure-compensated, load-responsive
    • 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
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20546—Type of pump variable capacity
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30505—Non-return valves, i.e. check valves
    • F15B2211/3051—Cross-check valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • F15B2211/3053—In combination with a pressure compensating valve
    • F15B2211/3055—In combination with a pressure compensating valve the pressure compensating valve is arranged between directional control valve and return line
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/3056—Assemblies of multiple valves
    • F15B2211/30565—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve
    • F15B2211/3057—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve having two valves, one for each port of a double-acting output member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • 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
    • F15B2211/3111—Neutral or centre positions the pump port being closed in the centre position, e.g. so-called closed centre
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3144—Directional control characterised by the positions of the valve element the positions being continuously variable, e.g. as realised by proportional valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/327—Directional control characterised by the type of actuation electrically or electronically
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • 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
    • F15B2211/41581—Flow control characterised by the connections of the flow control means in the circuit being connected to an output member and a return line
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/42—Flow control characterised by the type of actuation
    • F15B2211/426—Flow control characterised by the type of actuation electrically or electronically
    • 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
    • F15B2211/46—Control of flow in the return line, i.e. meter-out control
    • 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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/605—Load sensing circuits
    • F15B2211/6051—Load sensing circuits having valve means between output member and the load sensing circuit
    • F15B2211/6054—Load sensing circuits having valve means between output member and the load sensing circuit using shuttle valves
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    • F15B2211/7058—Rotary output members

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Abstract

本发明揭示一用于工作机器(10)的液压系统(22)。该液压系统具有一构造成容纳供应流体的贮器(34)以及一构造成加压流体的加压源(18)。液压系统还具有一流体致动器(20)、一第一阀(27)，以及一第二阀(32)。第一阀构造成有选择地将加压源与流体致动器流体连通以利于流体致动器沿第一方向的运动。第二阀构造成有选择地将流体致动器与贮器流体连通以利于流体致动器沿第一方向的运动。液压系统还具有一比例压力补偿阀(36)，其构造成对在流体致动器和贮器之间被引导的流体的压力进行控制。

Description

液压系统及其操作方法以及使用该液压系统的工作机器
技术领域
本发明总的涉及一液压系统，具体来说，涉及一具有回压补偿器的液压系统。 
背景技术
诸如推土机、装载机、挖掘机、自动平路机和其它类型重型机械的工作机器使用一个或多个液压致动器来完成各种任务。这些致动器流体地连接到工作机器的泵上，其对致动器内的腔室提供加压流体。一电动液压阀结构通常流体地连接在泵和致动器之间，以控制加压流体流入和流出致动器腔室的流速和方向。 
在致动器运动过程中，作用在工作机器上的重力会迫使流体以比流体填充致动器更快的速度从致动器流出。在此情形中，由于填充腔室在致动器内膨胀(空穴化)可形成空穴或真空。空穴化可导致工作机器不理想和/或不希望的运动，并可损坏液压致动器。此外，在这些情形中，致动器可能超速或比预期或期望的移动得更快。 
2000年10月17日授予Poorman的美国专利No.6,131,391(’391专利)描述了一种将空穴化和超速现象减到最小的方法。’391专利描述了一种液压回路，该回路具有一贮箱、一泵、一马达、四个独立操作的电动液压计量阀、一马达输入压力传感器、一马达输出压力传感器，以及一泵供应压力传感器。当马达输出处测得的压力大于马达和泵供应的输入处测得的压力时，就可确定超速的状态。当确定出一超速状态时，其中一个电动液压计量阀被致动而限制从马达流出的液压流体的流动，以减慢马达的转动和流出马达的流体的流速。 
尽管’391专利中描述的液压回路可减少超速和空穴化的可能性，但它可能响应缓慢并且会变得复杂和昂贵。尤其是，因为减慢马达的机构包括一电磁阀，液压回路的响应时间可以是5-15hz的量级。对于这样的结构，在确定出超速状态并已平衡之时，空穴化或超速的效应已经被工作机器所经历。此外，因为’391专利的超速保护是基于检测到的信息，所以，系统会很复杂。为提供检测信息所需要的附加的传感器也会增加系统的成本。     
本发明揭示的液压系统旨在克服一个或多个以上所阐述的问题。 
发明内容
在一个方面，本发明针对一种液压系统。该液压系统包括一构造成容纳供应流体的贮器以及一构造成加压流体的加压源。该液压系统还包括一流体致动器、一第一阀和一第二阀。第一阀构造成有选择地将加压源与流体致动器流体连通以利于流体致动器沿第一方向的运动。第二阀构造成有选择地将流体致动器与贮器流体连通以利于流体致动器沿第一方向的运动。该液压系统还包括一比例压力补偿阀，其构造成对在流体致动器和贮器之间被引导的流体的压力进行控制。 
在另一方面，本发明针对一种操作一液压系统的方法。该方法包括加压一流体和通过一第一阀将加压流体引导到一流体致动器以利于流体致动器沿第一方向的运动。该方法还包括通过一第二阀从流体致动器中排出流体以利于流体致动器沿第一方向的运动。该方法还包括用比例压力补偿阀来控制从致动器中排出的流体压力。 
附图说明
图1是根据本发明一示范实施例的工作机器的示意侧视图；以及 
图2是用于图1工作机器的本发明示范的液压回路的示意图。 
具体实施方式
图1示出一示范的工作机器10。工作机器10可以是执行某种类型操作的机器，这种类型的操作与诸如开矿、建筑、农业之类的行业或本技术领域内所公知的任何其它行业相关。例如，工作机器10可以是诸如推土机、装载机、锄耕机、挖掘机、自动平路机、自动倾斜卡车之类的移动泥土的机器，或任何其它移动泥土的机器。工作机器10可包括一动力源12和一相连接的传动机构 14以驱动多个拖拉装置16(图1中仅示出一个)。 
动力源12可以是一发动机，例如，柴油机、汽油机、诸如天然气发动机的气体燃料发动机，或本技术领域内的技术人员所熟知的任何其它的发动机。动力源12还可包括诸如燃料电池、动力储存装置的其它动力源，或本技术领域内公知的任何其它动力源。 
传动机构14可以是一静液压传动机构，用来将动力从动力源12传递到拖拉装置16。静液压的传动机构通常由一泵18、一马达20和一比例控制器(未示出)组成。比例控制器可操纵泵18和马达20的排量，由此，控制传动结构14的输出转动。马达20可通过管道流体地连接到泵18，管道将流体来回地供应和返回到泵18和马达20，允许泵18通过流体压力有效地驱动马达20。可以构思工作机器10可在一双路径的结构中包括一个以上连接到动力源12的传动机构14。 
泵18和马达20可以是变排量、变输送量、固定排量，或本技术领域内公知的任何其它构造。泵18可以通过一输入轴26直接连接到动力源12。或者，泵18可通过一转矩转换器、一齿轮箱、一电路或本技术领域内公知的任何其它方式连接到动力源12。泵18可以是专门仅对马达20供应加压流体，或者可以是对工作机器10内的其它液压系统(未示出)供应加压流体。 
传动机构14还可包括一将马达20连接到拖拉装置16的输出轴21。工作机器10可以包括或不包括一减速齿轮结构，例如，一设置在马达20和拖拉装置16之间的行星结构。 
拖拉装置16可包括一位于工作机器10每一侧上的履带24(图中仅示出一侧)。或者，拖拉装置16可包括轮子、传动带或其它被驱动的拖拉装置。拖拉装置16可以被马达20驱动从而根据输出轴21的转动而转动。 
如图2所示，泵18和马达20可在一液压系统22内发挥功能而移动拖拉装置16(参见图1)。液压系统22可包括一向前供应阀27、一反向排放阀28、一反向供应阀30、一向前排放阀32、一贮箱34，以及一比例压力补偿阀36。可以构思液压系统22可包括附加的和/或不同的部件，例如，压力传感器、温度传感器、位置传感器、控制器、蓄能器、补充阀(make-up valve)、卸压阀，以及本技术领域内公知的其它部件。还可构思液压系统22可与一不是马达20 或除马达20之外的液压致动器连接，例如，一液压缸。 
向前供应阀27可以设置在泵18和马达20之间，并构造成调节流入马达20的加压流体的流量，以帮助沿向前方向驱动马达20。具体来说，向前供应阀27可包括一弹簧偏压的比例阀机构，其是电磁驱动阀并构造成在一第一位置和一第二位置之间移动，在第一位置，允许流体流入马达20，而在第二位置，流体与马达20阻塞。可以构思向前供应阀27替换为液压致动的、机械致动的、气动致动的，或任何其它合适方式致动的。还可构思向前供应阀27可以构造成：当马达20内的压力超过从泵18引入马达20的压力时，在一重建过程中，允许流体从马达20流过向前供应阀27。 
反向排放阀28可以设置在马达20和贮箱34之间，并构造成调节从马达20的流入贮箱34的加压流体的流量，以帮助沿向前方向驱动马达20。具体来说，反向排放阀28可包括一弹簧偏压的比例阀机构，其是电磁驱动阀并构造成在一第一位置和一第二位置之间移动，在第一位置，允许流体从马达20流出，而在第二位置，阻塞流体从马达20流出。可以构思反向排放阀28替换为液压致动的、机械致动的、气动致动的，或任何其它合适方式致动的。 
反向供应阀30可以设置在泵18和马达20之间，并构造成调节流入马达20的加压流体的流量，以帮助沿与向前方向相对的反向方向驱动马达20。具体来说，反向供应阀30可包括一弹簧偏压的比例阀机构，其是电磁驱动阀并构造成在一第一位置和一第二位置之间移动，在第一位置，允许流体流入马达20，而在第二位置，流体与马达20阻塞。可以构思反向供应阀30替换为液压致动的、机械致动的、气动致动的，或任何其它合适方式致动的。还可构思反向供应阀30可以构造成：当马达20内的压力超过从泵18引入到反向供应阀30的压力时，在一重建过程中，允许流体从马达20流过反向供应阀30。 
向前排放阀32可以设置在马达20和贮箱34之间，并构造成调节从马达20流入贮箱34的加压流体的流量，以帮助沿反向方向驱动马达20。具体来说，向前排放阀32可包括一弹簧偏压的比例阀机构，其是电磁驱动阀并构造成在一第一位置和一第二位置之间移动，在第一位置，允许流体从马达20流出，而在第二位置，阻塞流体从马达20流出。还可以构思向前排放阀32替换为液压致动的、机械致动的、气动致动的，或任何其它合适方式致动的。 
向前和反向供应和排放阀27、28、30、32可以流体地互连。尤其是，向前和反向供应阀27、30可平行于一上游公共的流体通道60进行连接。向前和反向排放阀32、28可平行于一公共的信号通道62和一公共的排放通道64进行连接。向前供应阀27和反向排放阀28可平行于一第一马达通道61进行连接。反向供应阀30和向前排放阀32可平行于一第二马达通道63进行连接。 
液压系统22可包括一附加的部件来控制流体压力和液压系统22内的流量。具体来说，液压系统22可包括一设置在公共信号通道62内的滑阀74。滑阀74可构造成流体地将具有较高流体压力的向前和反向排放阀32、28中的一个阀连接到比例压力补偿阀36。因为滑阀74允许较高的压力来影响比例压力补偿阀36，比例压力补偿阀36的功能可维持恒定的排放流，并响应于由重力或惯性力造成的马达内过度的压力水平，将空穴化和/或超速减到最小。 
贮箱34可构成一贮器，其构造成容纳供应的流体。流体可以包括专用液压油、发动机润滑油、传动机构润滑油，或本技术领域内公知的任何其它流体。工作机器10内的一个或多个液压系统可从贮箱34中抽取流体以及将流体返回到贮箱34。还可构思将液压系统22连接到多个分离的流体贮箱。 
比例压力补偿阀36可以是设置在公共排放通道64和贮箱34之间的液压-机械致动的比例控制阀以控制从马达20流出的流体压力。具体来说，比例压力补偿阀36可包括一阀元件，其被弹簧偏压和液压偏压朝向一流动通过的位置，并通过液压的压差可移动朝向流体阻塞的位置。在一实施例中，比例压力补偿阀36可通过从滑阀74经一流体通道78引出的流体而朝向流动阻塞位置移动。一节流孔板80可以设置在流体通道78内以将流体通道78内的压力和/或流量波动减到最小。比例压力补偿阀36可通过一流体通道82从就在比例压力补偿阀36上游的一点朝向流动通过的位置移动到比例压力补偿阀36的一端。一节流孔板84可以设置在流体通道82内以将流体通道82内的压力和/或流量波动减到最小。可以构思比例压力补偿阀36的阀元件也可选择用弹簧偏压朝向流动阻塞位置，且从流体通道82流出的流体可选择将比例压力补偿阀36的阀元件偏压朝向流动通过的位置，和/或从流体通道78流出的流体可选择将比例压力补偿阀36的阀元件移向流动阻塞的位置。还可构思，如果需要的话，节流孔板80和84可以省略。 
液压系统22还可包括一备用设备，在工作机器10运行期间，如果第一或第二马达通道61、63破裂，则该备用设备用来防止超速和空穴化。尤其是，第一止回阀86可以设置在邻近于马达20的第一马达通道61内，而一第二止回阀88可以设置在邻近于马达20的第二马达通道63内。第一信号通道90可从第一马达通道61延伸到第二止回阀88，而第二信号通道92可从第二马达通道63延伸到第一止回阀86。第一信号通道90内的流体压力或第二马达通道63内的流体压力足以克服弹簧偏压力和与第二止回阀88相关的背压，以在正常操作过程中移动第二止回阀88朝向流动通过的位置。类似地，第二信号通道92内的流体压力或第一马达通道61内的流体压力足以克服弹簧偏压力和与第一止回阀86相关的背压，以在正常操作过程中移动第一止回阀86朝向流动通过的位置。在马达沿反向方向运动过程中，如果第二马达通道63破裂，则第二信号通道92内的流体压力可能不足以将第一止回阀86移至流动通过的位置。类似地，在马达沿向前方向运动过程中，如果第一马达通道61破裂，则第一信号通道90内的流体压力可能不足以将第二止回阀88移至流动通过的位置。当第一或第二止回阀86和88中的任何一个处于流动阻塞的位置时，可阻止马达20转动。 
工业应用性 
本发明的液压系统可以适用于任何工作机器，该种工作机器包括其中没有空穴化和超速的液压致动器。本发明的液压系统可提供高度响应的压力调节，该种调节保护液压系统的部件并在低成本和简单的结构中提供相同的致动器特性。现将解释液压系统22的操作。 
马达20可通过流体压力响应于操作者的输入而移动。流体可被泵18加压并引导到向前和反向供应阀27和30。响应于操作者的输入而沿向前或反向方向移动拖拉装置16，向前和反向供应阀27和30之一的阀元件可移动到打开位置以将加压流体引导到马达20。基本上同时地，向前和反向排放阀32和28之一的阀元件移动到打开位置以将流体从马达20引导到贮箱34而横贯马达20两端形成一压差，该压差致使马达20转动。例如，如果要求马达20向前转动，那么，向前供应阀27可移至打开位置而引导加压流体从泵18流到马达 20。基本上在引导加压流体流入马达20的同时，向前排放阀32可移至打开位置以允许流体从马达20流到贮箱34。如果要求马达20反向转动，那么，反向供应阀30可移至打开位置而引导加压流体从泵18流到马达20。基本上在引导加压流体流入马达20的同时，反向排放阀28可移至打开位置以允许流体从马达20流到贮箱34。 
因为重力可影响马达20的转动以及流出马达20的相关的流体流，所以，马达20会在某些情形中趋于超速或空穴化。例如，当倾斜向下移动时，作用在工作机器10上的重力会造成拖拉装置比所要求的更快地转动马达20。如果任其不加控制，那么，会导致马达20和拖拉装置16不一致的和/或不希望的运动，并可能导致缩短液压系统22的部件寿命。通过比例压力补偿阀36的阀元件响应于从马达20排出的流体的压力在流动通过位置和流动阻塞位置之间的移动，比例压力补偿阀36可解决这些影响以横贯马达20两端提供最大可接受的压降。 
当向前和反向排放阀32、28之一的阀元件移动到流动通过位置时，流过流动通过阀进入滑阀74的信号流体的压力可高于流过处于流动阻塞位置的阀的信号流体的压力。其结果，较高的压力可偏压滑阀74而将从流动通过阀流出的较高的压力连通到比例压力补偿阀36。然后，该较高的压力可作用而抵抗比例压力补偿阀的弹簧力和来自流体通道82的压力。该合力随后可将比例压力补偿阀36的阀元件移向流动阻塞位置或流动通过位置。当流出马达20的流体响应于重力载荷而使压力增加时，比例压力补偿阀36的阀元件可朝向流动阻塞位置移动而限制从马达20流出的流体，由此，提高马达20的背压并使马达20保持一可接受的速度。类似地，当流出马达20的流体压力减小时，比例压力补偿阀36可朝向流动通过位置移动，由此使马达20保持一可接受的速度。以此方式，比例压力补偿阀36可调节液压系统22内的流体压力而将空穴化和超速减到最小。 
因为比例压力补偿阀36是液压-机械致动的，所以，在液压系统22内的压力波动可显著地影响马达20的运动或液压系统22的部件寿命之前，该压力波动就可快速地得到调和。尤其是，比例压力补偿阀36的响应时间可以约为200hz或更长，这远大于响应时间约为5-15hz的典型的电磁阀。此外，因为比 例压力补偿阀36可以是液压-机械致动的而不是电子致动的，所以，液压系统22的成本可降到最小。而且，因为液压系统22不依赖于检测到的信息，所以，可减小液压系统22的复杂性和部件成本。 
本技术领域内的技术人员将会明白对于本发明揭示的液压系统可作出各种修改和变化。考虑到本说明书和对所揭示的液压系统的实践，本技术领域内的技术人员将会明白其它的实施例。本说明书和实例应被认为只是示范的，真正的范围由下面的权利要求书和其等价物予以指明。 

Claims (9)

1.一种液压系统(22)，其包括：
一构造成容纳供应流体的贮器(34)；
一构造成加压流体的加压源(18)；
一流体致动器(20)；
一第一阀(27)，其构造成有选择地将加压源(18)与流体致动器(20)流体连通以利于流体致动器(20)沿第一方向的运动；
一第二阀(32)，其构造成有选择地将流体致动器(20)与贮器流体连通以利于流体致动器沿第一方向的运动；
一第三阀(30)，其构造成有选择地将加压源(18)与流体致动器(20)流体连通以利于流体致动器沿一第二方向运动；
一第四阀(28)，其构造成有选择地将流体致动器(20)与贮器(34)流体连通以利于流体致动器(20)沿第二方向运动；
一滑阀(74)，其设置在一公共信号通道(62)内，所述公共信号通道(62)设置在第二阀(32)和第四阀(28)的上游，并与第二阀(32)和第四阀(28)流体连通，所述滑阀可在一第一位置和一第二位置之间移动，在第一位置，从第二阀(32)流出的加压流体通过滑阀(74)，而在第二位置，从第四阀(28)流出的加压流体通过滑阀(74)；以及
一比例压力补偿阀(36)，其构造成对在流体致动器(20)和贮器(34)之间被引导的流体的压力进行控制。
2.如权利要求1所述的液压系统，其特征在于，比例压力补偿阀包括一阀元件，其响应于超过预定压力的流过第二阀的流体压力朝向一流动阻塞位置移动，由此减慢液压致动器的运动。
3.如权利要求1所述的液压系统，其特征在于，还包括
一设置在流体致动器(20)与第一阀(27)和第四阀(28)之间的第一马达通道(61)；
一设置在流体致动器与第二阀(32)和第三阀(30)之间的第二马达通道(63)；
一设置在第一马达通道(61)内的第一止回阀(86)，其在流体致动器(20)沿第二方向运动过程中，被弹簧偏压而有选择地阻止流体从流体致动器(20)流到第一阀(27)和第四阀(28)；以及
一设置在第二马达通道(63)内的第二止回阀(88)，其构造成在流体致动器(20)沿第一方向运动过程中，有选择地阻止流体从流体致动器(20)流到第二阀(32)和第三阀(30)；
一第一信号通道(90)，其构造成连通第一马达通道(61)和第二止回阀(88)；以及
一第二信号通道(92)，其构造成连通第二马达通道(63)和第一止回阀(86)。
4.如权利要求1所述的液压系统，其特征在于，还包括设置在贮器(34)与第二阀(32)和第四阀(28)之间的公共排放通道(64)，其中，第二阀(32)和第四阀(28)平行地连接到公共排放通道(64)，而比例压力补偿阀(36)设置在公共排放通道(64)和贮器(34)之间。
5.如权利要求4所述的液压系统，其特征在于，还包括：
一第一流体通道(82)，其中，比例压力补偿阀(36)包括一在流动通过位置和流动阻塞位置之间移动的阀元件，第一流体通道(82)构造成将流体从比例压力补偿阀(36)和公共排放通道(64)之间引导到比例压力补偿阀(36)，以偏压阀元件朝向流动通过位置和流动阻塞位置中的一个位置；以及
一第二流体通道(78)，其构造成通过滑阀(74)将加压流体从第二阀(32)和第四阀(28)之一引导到比例压力补偿阀(36)，以偏压比例压力补偿阀的阀元件朝向流动通过位置和流动阻塞位置中的另一个位置。
6.一种操作一液压系统(22)的方法，该方法包括：
加压一流体；
通过一第一阀(27)将加压流体引导到一流体致动器(20)以利于流体致动器沿第一方向的运动；
通过一第二阀(32)从流体致动器(20)中排出流体以促进流体致动器(20)沿第一方向的运动；
通过一第三阀(30)引导加压流体到流体致动器(20)以利于沿第二方向的运动；
通过一第四阀(28)从流体致动器(20)中排出流体以促进沿第二方向的运动；
用比例压力补偿阀(36)来控制从致动器(20)中排出的流体压力；以及
引导加压流体到一滑阀(74)，所述滑阀设置在一公共信号通道(62)内，所述公共信号通道(62)设置在第二阀(32)和第四阀(28)的上游，并与第二阀(32)和第四阀(28)流体连通，其中，当所述滑阀移动至一第一位置时，从第二阀(32)流出的加压流体通过滑阀(74)，当所述滑阀移动至一第二位置时，从第四阀(28)流出的加压流体通过滑阀(74)。
7.如权利要求6所述的方法，其特征在于，还包括：
在流体致动器(20)沿第一方向运动过程中，响应于超过预定值的横贯流体致动器的压差而有选择地阻止流体从流体致动器(20)流到第二阀(32)和第三阀(30)；以及
在流体致动器(20)沿第二方向运动过程中，响应于超过预定值的横贯流体致动器(20)的压差而有选择地阻止流体从流体致动器(20)流到第一阀(27)和第四阀(28)。
8.如权利要求7所述的方法，其特征在于，还包括：
引导加压流体从就在比例压力补偿阀(36)上游的地方流向比例压力补偿阀(36)的一端，以推动比例压力补偿阀的阀元件朝向一流动通过位置；以及
引导加压流体从第二阀(32)和第四阀(28)流向比例压力补偿阀(36)的一端，以推动比例压力补偿阀的阀元件朝向一流动阻塞位置。
9.一工作机器(10)，其包括：
一动力源(12)；
一拖拉装置(16)；
如权利要求1-5中任何一项所述的液压系统(22)被动力源驱动并构造成使拖拉装置移动。
CN2006800184757A 2005-05-31 2006-04-25 液压系统及其操作方法以及使用该液压系统的工作机器 Expired - Fee Related CN101184923B (zh)

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US11/139,689 US7302797B2 (en) 2005-05-31 2005-05-31 Hydraulic system having a post-pressure compensator
US11/139,689 2005-05-31
PCT/US2006/015363 WO2006130267A1 (en) 2005-05-31 2006-04-25 Hydraulic system having a return pressure compensator

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