WO2013078878A1 - 基于液压集成技术的小型调速器综合调节装置 - Google Patents

基于液压集成技术的小型调速器综合调节装置 Download PDF

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Publication number
WO2013078878A1
WO2013078878A1 PCT/CN2012/079473 CN2012079473W WO2013078878A1 WO 2013078878 A1 WO2013078878 A1 WO 2013078878A1 CN 2012079473 W CN2012079473 W CN 2012079473W WO 2013078878 A1 WO2013078878 A1 WO 2013078878A1
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Prior art keywords
way
valve
port
coil
reversing valve
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PCT/CN2012/079473
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English (en)
French (fr)
Inventor
何林波
许栋
蔡晓峰
蔡卫江
荣红
朱祥
陈登山
陈晓勇
Original Assignee
国网电力科学研究院
南京南瑞集团
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Publication of WO2013078878A1 publication Critical patent/WO2013078878A1/zh

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Classifications

    • 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
    • F15B20/00—Safety arrangements for fluid actuator systems; Applications of safety devices in fluid actuator systems; Emergency measures for fluid actuator systems
    • 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
    • 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
    • F15B2211/80—Other types of control related to particular problems or conditions
    • F15B2211/875—Control measures for coping with failures
    • F15B2211/8755—Emergency shut-down

Definitions

  • the invention relates to a small speed governor integrated adjusting device based on hydraulic integration technology. Background technique
  • the speed control system plays a very important role in ensuring the safe and stable operation of the unit.
  • the design of the speed control system for small and medium-sized hydropower stations also fully considers the safety. Both the accidental pressure distribution and the sectional shutdown are designed.
  • the small and medium-sized hydropower stations are limited by the plant, and the speed control system cannot occupy too much space.
  • the small hydropower station The comprehensive technical strength is limited, and it is difficult to maintain a speed control system with complex structures.
  • the device makes full use of the hydraulic integration technology, and integrates the basic adjustment function of the governor, the accidental pressure regulating valve and the sectional closing device on one hydraulic manifold, which is simple and convenient to use.
  • the prior art governor integrated adjusting device is composed of three independent devices: a main adjusting device, an accident regulating valve and a segment closing device.
  • the main adjustment device has 4 externally operated oil pipes, the accidental pressure regulating valve is externally connected to the main operation. There are 6 oil pipes, and the sectional closing device has 2 external operating oil pipes.
  • the three sets of devices are connected intricately, resulting in increased leakage points, increased installation space, and increased costs.
  • the main object of the invention is to adopt a highly integrated integrated adjustment device, the function of the speed control system is sound, and the installation is convenient, and the external interface pipeline is small, whether built-in or external.
  • the type of relay is very convenient to arrange.
  • the operation of the pressure oil is eliminated, the governor operation is more stable and reliable, and the "hydraulic differential" is eliminated, thus ensuring the safe and stable operation of the power station and the production of the standard.
  • a small governor comprehensive adjusting device based on hydraulic integration technology comprising: main oil inlet P, main oil return port 1 ⁇ a three-position four-way proportional valve, first single-coil two-way four-way reversing valve, Two single coil two-way four-way reversing valve, one double-coil three-position four-way electromagnetic reversing valve, one two-position four-way reversing valve, one two-six six-way double-end hydraulic reversing valve, one adjustable type Throttle valve, an adjustable one-way throttle valve, a servo opener, and a servo-closed chamber;
  • the oil return port ⁇ 5 , the port 2 of the adjustable throttle valve is connected;
  • the mouth of the three-position four-way proportional valve is respectively connected to the oil inlet P 2 and the oil return port T 2 of the first single-rotor two-way four-way selector valve; the mouth and the mouth are respectively the left of the three-position four-way proportional valve , right control port, three-position four-way proportional valve is located at the left end of the mouth ⁇ and mouth ⁇ ⁇ connected, mouth and mouth Pi connected; three four-way proportional valve is located at the right end ⁇ and mouth Pi connected, mouth ⁇ and mouth ⁇ ⁇ connected
  • the three-position four-way proportional valve is in the middle position, and the mouth, mouth and mouth are separated; the first single-coil two-way four-way reversing valve port A 2 , port B 2 and two-six six-way double-end hydraulic control valve Port d 2 and port C 2 are connected; port A 2 and port B 2 are respectively the left and right control ports of the first single-coil two-way four-way reversing valve, and the first single-
  • port A 4, B 4 are dual port coil three-way solenoid valve of the left and right control port, dual three-way solenoid valve coil at the left end sad communication port a 4 T 4 and the port, port 4 communicates with the port ⁇ [rho] 4;
  • lane Three-position four-way electromagnetic reversing valve position At the right end, the mouth A 4 is connected to the mouth P 4 , and the mouth B 4 is connected to the mouth T 4 ;
  • the double-coil three-position four-way electromagnetic reversing valve is located at the middle position, and the mouth ⁇ 4 , the mouth ⁇ 4 and the mouth ⁇ 4 ⁇ 4 are cut off. ;
  • port A 5, B 5 are two port
  • the left and right control ports of the four-way mechanically-positioned electromagnetic reversing valve, the two-position four-way electromagnetic reversing valve with mechanical positioning are located at the left end of the port A 5 and the port T 5 , port 5 and port 5 Connected;
  • two-way four-way electromagnetic reversing valve with mechanical positioning is located at the right end of the port ⁇ 5 is connected to the port 5 , and the port is connected to the port 5 ;
  • the port C 6 of the two-position six-way double-end hydraulically controlled reversing valve is connected to the servo-closed chamber;
  • the port C 5 of the two-position six-way double-end hydraulically controlled reversing valve is connected to the port T 3 of the second single-coil two-way four-way reversing valve, and the port 2 of the adjustable one-way throttle valve is connected;
  • the port of the second single-coil two-way four-way reversing valve 3 , the port 1 of the adjustable one-way throttle valve is connected to the opener of the servomotor.
  • the mouthpiece 3 and the mouthpiece 3 are the left and right control ports of the second single-coil two-way four-way reversing valve, and the second single-coil two-way four-way reversing valve is located at the left end of the mouth ⁇ 3 , ⁇ 3 and the mouth ⁇ 3, ⁇ 3 partition; a second single coil two four-way valve positioned at the right ⁇ 3 griefful port in communication with port ⁇ 3, port in communication with port ⁇ 3 ⁇ 3.
  • the above two-position six-way double-end hydraulic control reversing valve is a two-way six-way plate-mounted hydraulic control reversing valve at both ends.
  • adjustable throttle valve and adjustable one-way throttle valve respectively adjust the accident stop time and the segmentation closing time.
  • the second single-coil two-way four-way reversing valve described above realizes a two-position two-way electromagnetic reversing valve.
  • the above two-position four-way reversing valve and the second single-coil two-way four-way reversing valve are two-position four-way electromagnetic reversing valves with mechanical positioning, or two-position four-way hydraulically controlled reversing valves.
  • the present invention has at least the following advantages:
  • the invention adopts a two-six-way plate type hydraulic control reversing valve as an accidental pressure regulating valve, and the pressure exchange of the control oil Qi and Q 2 realizes normal work and accident shutdown action, and the action is reliable.
  • the electromagnetic valve, the liquid control valve and the throttle valve used in the invention are all plate-mounted, integrated in one body, small in size, simple in structure, convenient in installation and low in cost, and the phenomenon of "hydraulic differential" is eliminated, and the pressure oil is prevented from leaking.
  • FIG. 1 is a schematic diagram of a conventional governor integrated adjustment device
  • Figure 2 is a schematic diagram of the present invention.
  • a small governor comprehensive adjustment device based on hydraulic integration technology, including: main oil inlet P, main oil return port T, a three-position four-way proportional valve 1, the first single coil two Four-way reversing valve 2, second single-coil two-way four-way reversing valve 3, one double-coil three-position four-way electromagnetic reversing valve 4, one two-position four-way electromagnetic reversing valve with mechanical positioning 5, one Two-six six-way double-end hydraulic control reversing valve 6, an adjustable throttle valve 7, an adjustable one-way throttle valve 8, a servo opener 9, and a servo-closed chamber 10;
  • the oil inlet P 3 is connected to the C 4 port of the two-way six-way double-end hydraulic control valve 6;
  • the three-position four-way proportional valve 1 is respectively connected to the oil inlet P 2 and the oil return port T 2 of the first single-coil two-way four-way switching valve 2;
  • Two-way electromagnetic valve 5 with mechanical positioning of A 5, B 5, respectively, and two six-port two-terminal Qi 6 of the hydraulic control valve, is connected to port Q 2;
  • the C 6 port of the two-way six-way double-ended hydraulic control reversing valve 6 is connected to the servo-closed chamber 10; the C 5 port of the two-six-way double-end hydraulically controlled reversing valve 6 and the second single-coil two-way four-way exchange To the T 3 port of the valve 3, the two ports of the adjustable one-way throttle valve 8 are connected;
  • the second single-coil two-way four-way reversing valve 3, the adjustable one-way throttle valve 8 The port is connected to the servo opener 9.
  • Two-position six-way double-end hydraulic control reversing valve 6 is a two-way six-way plate-mounted hydraulic control reversing valve at both ends.
  • Adjustable throttle valve 7 The adjustable one-way throttle valve 8 adjusts the accident downtime and the segmentation closing time respectively.
  • the second single-coil two-way four-way reversing valve 3 realizes a two-position two-way electromagnetic reversing valve.
  • Two-position four-way electromagnetic reversing valve with mechanical positioning 5 The second single-coil two-way four-way reversing valve 3 can be replaced by a two-position four-way hydraulically controlled reversing valve with the same valve position function.
  • Two-way six-way hydraulic control reversing valve at both ends two positions refer to the left position and the right position of the working position; the six-way means that the valve has d, C 2 , C 3 , C 4 , C 5 , C 6 six ports.
  • the hydraulic control at both ends means that there are two hydraulic terminals of Q 2 .
  • the liquid control reversing valve works in the left position (ie, the port C 5 port, the C 2 port C 6 port, the C 3 , C 4 ports are closed) .
  • the liquid control reversing valve works in the right position (ie C 3 port C 5 port, C 4 port C 6 port, d, C 2 port) Closed).
  • the a-terminal electromagnet of the two-position four-way mechanically-positioned electromagnetic reversing valve 5 is energized, and the two-position four-way mechanically-positioned electromagnetic reversing valve 5 operates at the 3 ⁇ 4 end.
  • the chamber of the two-way six-way double-end hydraulic control valve 6 is pressure oil, the Q 2 chamber is oil return, and the two-way six-way double-end hydraulic control valve 6 is operated at the A 6 end, the two-way six-way double-end liquid
  • the control of the reversing valve 6 is connected, ( 2 and ( 6) .
  • the control signal can be adjusted after d, C 5 , C 2 , C 6 to adjust the vane opening.
  • the first single-coil two-way four-way reversing valve 2 When the automatic adjustment is made, the first single-coil two-way four-way reversing valve 2 is de-energized. Under the action of the spring force, the first single-coil two-way four-way reversing valve 2 works at the b 2 end, three four
  • the adjustment signal of the proportional valve 1 passes through the first single-coil two-way four-way reversing valve 2 and the two-position six-way double-end hydraulically controlled reversing valve 6, and communicates with the servomotor opening chamber 9, the servomotor closing chamber 10, and automatically adjusts the guide. The opening of the leaf.
  • the first single-coil two-way four-way reversing valve 2 When the manual adjustment is made, the first single-coil two-way four-way reversing valve 2 is energized. Under the action of electromagnetic force, the first single-coil two-way four-way reversing valve 2 works at the 3 ⁇ 4 end, and the three-fourth is cut off. The control signal of the proportional valve 1 is passed. At this time, the control signal of the double-coil three-position four-way electromagnetic reversing valve 4 passes through the two-six-way two-terminal hydraulically controlled reversing valve 6 and the servo open chamber 9 and the relay close chamber 10 Connect, manually adjust the vane opening.
  • the b 4 terminal of the two-way four-way solenoid-operated solenoid-operated valve 5 The magnet is energized, and the two-position four-way electromagnetically directional control valve 5 with mechanical positioning operates at the b 5 end.
  • the QJ of the two-way six-way double-end hydraulic control valve 6 is oil return, the Q 2 chamber is pressure oil, and the two-way six-way double-end hydraulic control valve 6 is operated at the B 6 end, two-six-way double-end C 3 of the pilot-operated directional control valve 6 is in communication with C 5 , and C 4 is in communication with C 6 .
  • the pressure oil passes through the C 4 and C 6 of the two-way six-way double-end hydraulic control reversing valve 6 and directly communicates with the servo-closed chamber 10, and the oil returns through the 2, 1 port of the adjustable throttle valve 7, two-six Through the C 3 of the double-end hydraulic control reversing valve 6, ( 5 is connected with the servo opener 9 to realize the function of rapid accident stop, the accident downtime can be adjusted by adjusting the opening degree of the adjustable throttle valve 7.
  • the terminal electromagnet of the second single-turn two-way four-way reversing valve 3 is energized, and under the action of the electromagnetic force, the second single-coil two-way four-way reversing valve 3 is operated at the end, from the relay
  • the oil coming back from the open chamber 9 can only be returned to the total oil return through the second single coil two-way four-way reversing valve 3 of 1, 2 .
  • the second closing time of the segment closing can be adjusted, and the stepless adjustment can be realized.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
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Abstract

一种基于液压集成技术的小型调速器综合调节装置，该装置包括：主进油口Ρ、主回油口T、一个三位四通比例阀（1）、第一单线圈两位四通换向阀（2）、第二单线圈两位四通换向阀（3）、一个双线圈三位四通电磁换向阀（4）、一个两位四通带机械定位的电磁换向阀（5）、一个两位六通双端液控换向阀（6）、一个可调型节流阀（7）、一个可调型单向节流阀（8）、接力器开腔（9）、接力器关腔（10）。该装置采用两位六通板式安装液控换向阀为事故配压阀，由控制油Q1、Q2压力交换来实现正常工作与事故停机动作，动作可靠。所采用的电磁阀、液控阀、节流阀均为板式安装，集成于一体，体积小，结构简单，安装方便、成本低，避免了"液压差动"现象和压力油跑冒滴漏。

Description

说 明 书 案件编号 基于液压集成技术的小型调速器综合调节装置 技术领域
本发明涉及一种基于液压集成技术的小型调速器综合调节装置。 背景技术
调速系统作为水电站主要的控制设备之一， 对保证机组安全、稳 定运行起着非常重要的作用。目前中小型水电站调速系统的设计也充 分考虑到了安全性， 均设计了事故配压， 分段关闭等装置， 但中小型 水电站受到厂房的限制， 调速系统不能占据过大空间， 同时小型水电 站的综合技术实力有限， 对维护复杂结构的调速系统比较困难。
基于以上问题，需要一种高度集成且功能齐全的调速系统综合液 压装置来满足小型水电站的要求。该装置充分利用液压集成技术， 将 调速器主配基本调节功能， 事故配压阀、分段关闭装置集成在一个液 压集成块上， 使用简单方便。
现有技术的调速器综合调节装置，如图 1所示，由主配调节装置、 事故配压阀、 分段关闭装置为三个独立的装置组成。
主配调节装置对外主操作油管有 4根，事故配压阀对外接主操作 油管有 6根， 分段关闭装置外接主操作油管有 2根。三套装置连接起 来配管错综复杂， 导致系统的漏点增多、 安装空间增大、 成本增加。
目前， 国内小型调速器的液压调节装置不足有：
(1)调速器主配压阀、 事故配压阀、 分段关闭装置相对独立， 配 管十分复杂， 容易出现跑冒滴漏现象， 对于电站达标投产将产生极其 不良的影响。
(2)部分中小型电站缺失事故保护与分段关闭的功能， 当出现事 故时， 不能保证机组及时停机， 容易造成更大的损失。
(3)插装阀型液压调节装置容易出现液压差动问题， 造成水轮机 接力器失控， 严重时会导致压力钢管爆裂， 造成水淹厂房。
(4)如电站采用内置式接力器， 调速器布置更加复杂、 困难。
发明内容
本发明的主要目的是采用高度集成式综合调节装置后，调速系统 的功能健全， 且安装方便， 对外接口管路少， 不管是内置式还是外置 式接力器， 布置起来都十分方便， 同时， 杜绝了压力油的跑冒滴漏现 象， 调速器运行更加稳定可靠， 杜绝 "液压差动"， 从而保障电站安 全稳定运行和达标投产。
解决国内中小型水电站调速系统多种功能难以集成实现， 安装复杂， 维护困难的问题， 进而保障中小水电站的安全稳定运行， 减少投资。
本发明的主要技术内容如下：
一种基于液压集成技术的小型调速器综合调节装置， 包括： 主进 油口 P、 主回油口 1\ 一个三位四通比例阀、 第一单线圈两位四通换 向阀、第二单线圈两位四通换向阀、一个双线圈三位四通电磁换向阀、 一个两位四通换向阀、一个两位六通双端液控换向阀、一个可调型节 流阀、 一个可调型单向节流阀、 接力器开腔、 接力器关腔；
主进油口 P与三位四通比例阀的进油口 Pi、双线圈三位四通电磁 换向阀的进油口 P4、两位四通带机械定位的电磁换向阀的进油口 P5、， 两位六通双端液控换向阀的 c4口相连；
主回油口 T与三位四通比例阀的回油口 Ί\，双线圈三位四通电磁 换向阀的回油口 Τ4、 两位四通带机械定位的电磁换向阀的回油口 Τ5、 可调型节流阀的口 2相连；
三位四通比例阀的口 口 分别与第一单线圈两位四通换向阀 的进油口 P2、 回油口 T2相连； 口 、 口 ^分别是三位四通比例阀的 左、 右控制油口， 三位四通比例阀位于左端恻口 ^与口 Ί\连通， 口 与口 Pi连通； 三位四通比例阀位于右端恻 与口 Pi连通， 口^ 与口 Ί\连通；三位四通比例阀位于中位则口 、口 与口 隔断； 第一单线圈两位四通换向阀的口 A2，口 B2分别与两位六通双端液 控换向阀的口 d、 口 C2相连； 口 A2、 口 B2分别是第一单线圈两位四 通换向阀的左、右控制油口， 第一单线圈两位四通换向阀 2位于左端 恻口 A2、 口 与口 P2 T2,隔断； 阀 2位于右端恻口 Α2与口 Ρ2连通， 口 Β2与口 Τ2连通；
双线圈三位四通电磁换向阀的口 Α4, 口 Β4分别与两位六通双端 液控换向阀的 d、 C2口相连； 口 A4、 口 B4分别是双线圈三位四通电 磁换向阀的左、右控制油口， 双线圈三位四通电磁换向阀位于左端恻 口 A4与口 T4连通， 口 Β4与口 Ρ4连通； 双线圈三位四通电磁换向阀位 于右端恻口 A4与口 P4连通， 口 B4与口 T4连通； 双线圈三位四通电磁 换向阀位于中位则口 Α4、 口 Β4与口 Ρ4 Τ4隔断；
两位四通带机械定位的电磁换向阀的口 Α5、口 Β5分别与两位六通 双端液控换向阀的 、 Q2口相连； 口 A5、 口 B5分别是两位四通带机 械定位的电磁换向阀的左、右控制油口， 两位四通带机械定位的电磁 换向阀位于左端恻口 A5与口 T5连通， 口 Β5与口 Ρ5连通； 两位四通带 机械定位的电磁换向阀位于右端恻口 Α5与口 Ρ5连通， 口 与口 Τ5连 通；
两位六通双端液控换向阀的口 C6与接力器关腔相连；
两位六通双端液控换向阀的口 C5与第二单线圈两位四通换向阀 的口 T3， 可调型单向节流阀的口 2相连；
第二单线圈两位四通换向阀的口 Β3、可调型单向节流阀的口 1与 接力器开腔相连。口 Α3、口 Β3分别是第二单线圈两位四通换向阀的左、 右控制油口， 第二单线圈两位四通换向阀位于左端恻口 Α3、 Β3与口 Τ3, Ρ3隔断;第二单线圈两位四通换向阀位于右端恻口 Α3与口 Ρ3连通， 口 Β3与口 Τ3连通。
上述的两位六通双端液控换向阀为两端液控两位六通板式安装 液控换向阀。
上述的可调型节流阀、可调型单向节流阀上分别调节事故停机时 间与分段关闭时间。
上述的第二单线圈两位四通换向阀实现两位两通电磁换向阀。 上述的两位四通换向阀、第二单线圈两位四通换向阀为两位四通 带机械定位的电磁换向阀、 或两位四通液控换向阀。
借由上述技术方案， 本发明至少具有下列优点：
本发明采用两位六通板式安装液控换向阀为事故配压阀，由控制 油 Qi、 Q2压力交换来实现正常工作与事故停机动作， 动作可靠。 本发 明采用的电磁阀、 液控阀、 节流阀均为板式安装， 集成于一体， 体积 小， 结构简单， 安装方便、 成本低， 杜绝 "液压差动"现象， 杜绝压 力油跑冒滴漏。
本发明的具体实施方式由以下实施例及其附图详细给出。
附图说明 图 1为现有调速器综合调节装置的原理图；
图 2为本发明的原理图。
具体实施方式
为更进一步阐述本发明为达成预定发明目的所采取的技术手段 及功效，以下结合附图及较佳实施例， 对依据本发明提出的其具体实 施方式、 结构、 特征及其功效， 详细说明如后。
如图 2 所示， 一种基于液压集成技术的小型调速器综合调节装 置， 包括： 主进油口 P、 主回油口 T、 一个三位四通比例阀 1、 第一 单线圈两位四通换向阀 2、 第二单线圈两位四通换向阀 3、 一个双线 圈三位四通电磁换向阀 4、一个两位四通带机械定位的电磁换向阀 5、 一个两位六通双端液控换向阀 6、 一个可调型节流阀 7、 一个可调型 单向节流阀 8、 接力器开腔 9、 接力器关腔 10;
主进油口 Ρ与三位四通比例阀 1的进油口 Pi、第一单线圈两位四 通换向阀 2的进油口 P2、 第二单线圈两位四通换向阀 3的进油口 P3， 两位六通双端液控换向阀 6的 C4口相连；
主回油口 T与三位四通比例阀 1的回油口 Ί\，双线圈三位四通电 磁换向阀 4的回油口 Τ4、两位四通带机械定位的电磁换向阀 5的回油 口 Τ5、 可调型节流阀 7的 2口相连；
三位四通比例阀 1的 分别与第一单线圈两位四通换向阀 2的进油口 P2、 回油口 T2相连；
第一单线圈两位四通换向阀 2的 Α2， Β2口分别与两位六通双端液 控换向阀 6的 d、 C2口相连；
双线圈三位四通电磁换向阀 4的口 A4, 口 B4分别与两位六通双 端液控换向阀 6的 d、 C2口相连；
两位四通带机械定位的电磁换向阀 5的 A5、 B5口分别与两位六通 双端液控换向阀 6的 Qi、 Q2口相连；
两位六通双端液控换向阀 6的 C6口与接力器关腔 10相连； 两位六通双端液控换向阀 6的 C5口与第二单线圈两位四通换向 阀 3的 T3口， 可调型单向节流阀 8的 2口相连；
第二单线圈两位四通换向阀 3的 口、可调型单向节流阀 8的 1 口与接力器开腔 9相连。
两位六通双端液控换向阀 6为两端液控两位六通板式安装液控 换向阀。
可调型节流阀 7、 可调型单向节流阀 8上分别调节事故停机时间 与分段关闭时间。
第二单线圈两位四通换向阀 3实现两位两通电磁换向阀。
两位四通带机械定位的电磁换向阀 5、 第二单线圈两位四通换向 阀 3可以采用相同阀位机能的两位四通液控换向阀替代。
两端液控两位六通液控换向阀：两位是指工作位置有左位和右卫 二个位置； 六通是指阀有 d、 C2、 C3、 C4、 C5、 C6六个油口。 两端液控 是指有 、 Q2两个液控端。 当 端液控端通压力油， Q2端为回油时， 液控换向阀工作于左位（即 口通 C5口， C2口通 C6口， C3， C4口封闭）。 当^端液控端通回油， Q2端为压力油时， 液控换向阀工作于右位（即 C3口通 C5口， C4口通 C6口， d， C2口封闭）。
本发明工作原理及过程如下：
如图 2所示， 正常调节状态时， 两位四通带机械定位的电磁换向 阀 5的 a端电磁铁得电，两位四通带机械定位的电磁换向阀 5工作于 ¾端。 两位六通双端液控换向阀 6的 腔为压力油， Q2腔为回油， 两 位六通双端液控换向阀 6工作于 A6端， 两位六通双端液控换向阀 6 的 与 相通， （2与（6相通。 控制信号经过 d， C5， C2， C6后可调节 导叶开度。
(1)、 自动调节时， 第一单线圈两位四通换向阀 2失电， 在弹簧 力的作用下第一单线圈两位四通换向阀 2工作于 b2端，三位四通比例 阀 1的调节信号经过第一单线圈两位四通换向阀 2与两位六通双端液 控换向阀 6后与接力器开腔 9、 接力器关腔 10相通， 自动调节导叶 的开度。
(2)、 手动调节时， 第一单线圈两位四通换向阀 2得电， 在电磁 力的作用下第一单线圈两位四通换向阀 2工作于 ¾端，截断三位四通 比例阀 1的控制信号，此时双线圈三位四通电磁换向阀 4的控制信号 通过两位六通双端液控换向阀 6后与接力器开腔 9、 接力器关腔 10 相通， 手动调节导叶开度。
事故停机状态时，两位四通带机械定位的电磁换向阀 5的 b5端电 磁铁得电，两位四通带机械定位的电磁换向阀 5工作于 b5端。两位六 通双端液控换向阀 6的 QJ空为回油， Q2腔为压力油， 两位六通双端液 控换向阀 6工作于 B6端，两位六通双端液控换向阀 6的 C3与 C5相通， C4与 C6相通。压力油经过两位六通双端液控换向阀 6的 C4， C6后直接 与接力器关腔 10相通， 回油经过可调型节流阀 7的 2、 1口， 两位六 通双端液控换向阀 6的 C3， （5后与接力器开腔 9相通， 实现了快速事 故停机的功能，事故停机时间可以通过调节可调型节流阀 7的开度来 调整。
分段关闭投入时，第二单线圈两位四通换向阀 3的 端电磁铁得 电， 在电磁力的作用下， 第二单线圈两位四通换向阀 3工作于 端， 从接力器开腔 9回来的油只能通过第二单线圈两位四通换向阀 3的 1， 2后回到总回油。 同过调节可调型单向节流阀 8的开度就可以调整分 段关闭的第二段关闭时间， 可实现无极调节。
以上所述， 仅是本发明的较佳实施例而已， 并非对本发明作任何 形式上的限制， 虽然本发明已以较佳实施例揭露如上， 然而并非用以 限定本发明，任何熟悉本专业的技术人员， 在不脱离本发明技术方案 范围内，当可利用上述揭示的技术内容作出些许更动或修饰为等同变 化的等效实施例,但凡是未脱离本发明技术方案的内容， 依据本发明 的技术实质对以上实施例所作的任何简单修改、等同变化与修饰， 均 仍属于本发明技术方案的范围内。

Claims

权 利 要 求 书 案件编号
1、 一种基于液压集成技术的小型调速器综合调节装置， 其特征 在于： 包括： 主进油 Π Ρ、 主回油口 1\ 一个三位四通比例阀、 第一 单线圈两位四通换向阀、第二单线圈两位四通换向阀、一个双线圈三 位四通电磁换向阀、一个两位四通换向阀、一个两位六通双端液控换 向阀、 一个可调型节流阀、 一个可调型单向节流阀、 接力器开腔、 接 力器关腔；
主进油口 Ρ与三位四通比例阀的进油口 Pi、双线圈三位四通电磁 换向阀的进油口 P4、两位四通带机械定位的电磁换向阀的进油口 P5、， 两位六通双端液控换向阀的 c4口相连；
主回油口 T与三位四通比例阀的回油口 Ί\，双线圈三位四通电磁 换向阀的回油口 τ4、 两位四通带机械定位的电磁换向阀的回油口 τ5、 可调型节流阀的口 2相连；
三位四通比例阀的口 口 分别与第一单线圈两位四通换向阀 的进油口 P2、 回油口 T2相连；
第一单线圈两位四通换向阀的口 Α2，口 Β2分别与两位六通双端液 控换向阀的口 d、 口 C2相连；
双线圈三位四通电磁换向阀的口 A4, 口 B4分别与两位六通双端 液控换向阀的 d、 C2口相连；
两位四通带机械定位的电磁换向阀的口 A5、口 B5分别与两位六通 双端液控换向阀的 、 Q2口相连；
两位六通双端液控换向阀的口 C6与接力器关腔相连；
两位六通双端液控换向阀的口 C5与第二单线圈两位四通换向阀 的口 T3， 可调型单向节流阀的口 2相连；
第二单线圈两位四通换向阀的口 Β3、可调型单向节流阀的口 1与 接力器开腔相连。
2、 根据权利要求 1所述的基于液压集成技术的小型调速器综合 调节装置， 其特征在于： 所述两位六通双端液控换向阀为两端液控两 位六通板式安装液控换向阀。
3、 根据权利要求 1所述的基于液压集成技术的小型调速器综合 调节装置， 其特征在于： 所述的两位四通换向阀、 第二单线圈两位四 通换向阀为两位四通带机械定位的电磁换向阀、或两位四通液控换向 阀。
PCT/CN2012/079473 2011-11-29 2012-08-01 基于液压集成技术的小型调速器综合调节装置 WO2013078878A1 (zh)

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