WO2017185885A1 - 一种温差能驱动海洋剖面运动系统 - Google Patents

一种温差能驱动海洋剖面运动系统 Download PDF

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Publication number
WO2017185885A1
WO2017185885A1 PCT/CN2017/076252 CN2017076252W WO2017185885A1 WO 2017185885 A1 WO2017185885 A1 WO 2017185885A1 CN 2017076252 W CN2017076252 W CN 2017076252W WO 2017185885 A1 WO2017185885 A1 WO 2017185885A1
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WO
WIPO (PCT)
Prior art keywords
phase change
valve
oil
bladder
temperature difference
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Application number
PCT/CN2017/076252
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English (en)
French (fr)
Inventor
杨灿军
夏庆超
陈燕虎
金波
李德骏
Original Assignee
浙江大学
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Application filed by 浙江大学 filed Critical 浙江大学
Publication of WO2017185885A1 publication Critical patent/WO2017185885A1/zh

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03G—SPRING, WEIGHT, INERTIA OR LIKE MOTORS; MECHANICAL-POWER PRODUCING DEVICES OR MECHANISMS, NOT OTHERWISE PROVIDED FOR OR USING ENERGY SOURCES NOT OTHERWISE PROVIDED FOR
    • F03G7/00—Mechanical-power-producing mechanisms, not otherwise provided for or using energy sources not otherwise provided for
    • F03G7/04—Mechanical-power-producing mechanisms, not otherwise provided for or using energy sources not otherwise provided for using pressure differences or thermal differences occurring in nature
    • F03G7/05—Ocean thermal energy conversion, i.e. OTEC
    • 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
    • F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
    • F15B1/02—Installations or systems with accumulators
    • 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
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • 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
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/027—Check valves
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E10/00—Energy generation through renewable energy sources
    • Y02E10/30—Energy from the sea, e.g. using wave energy or salinity gradient

Definitions

  • the present invention relates to a marine profile motion system, and more particularly to an energy-saving temperature difference capable of driving a marine profile motion system.
  • Marine profile motion equipment is an important tool for people to study and detect the ocean.
  • lithium batteries are traditionally used for power supply.
  • a considerable part of the energy consumption of lithium batteries is used for driving and controlling the equipment, which greatly reduces the profile motion equipment.
  • Service life At present, there is a motion system driven by a temperature difference, and the control of the movement of the device is performed by a solenoid valve.
  • the energy consumption of the solenoid valve of several tens of watts is still too large for such a long-term profile motion device in the ocean.
  • sufficient ocean observation data is a necessary condition for people to deeply understand the ocean.
  • the profile monitoring equipment is limited by the battery power and cannot increase the number of section movements.
  • the motion of the cross-section monitoring device is generally electrically controlled by the microcontroller. Once a problem occurs, the device will malfunction and the reliability of the device will be reduced.
  • the object of the present invention is to solve the defects of the existing marine profile motion system in terms of control mode and energy consumption, and propose an energy-saving temperature difference capable of driving the ocean profile motion system with simple structure and reliable operation.
  • An energy-saving temperature difference can drive a marine profile motion system, including:
  • phase change cavity containing a solid phase change material and a sealing liquid
  • phase change hydraulic oil bladder disposed in a phase change chamber covered with a sealing liquid
  • an accumulator connected to the phase change hydraulic oil bladder by an oil discharge path with a first one-way valve
  • an outer oil bladder connected to the accumulator by an oil inlet passage having a first sequence valve and a first reversing valve; [0009] passing through a second sequence valve and a second reversing valve An internal oil bladder connected to the outer oil bladder; [0010] the phase change hydraulic oil bladder is connected to the inner oil bladder through a second oil return passage with a second one-way valve; [0011] The outer oil bladder and the phase change cavity are disposed outside a sealed cavity, and the remaining components and the oil passage are disposed in the sealed cavity; [0012] the first sequential valve and the second reversing valve are both subjected to Controlled by the outer oil bladder; the first diverter valve is controlled by an inner oil pocket; the second sequence valve is controlled by the accumulator.
  • the oil inlet is provided with a throttle valve.
  • the first oil return road is provided with a throttle valve.
  • the first sequence valve, the first reversing valve and the throttle valve on the oil passage have relatively independent functions, and the connection sequence on the oil inlet path is not strictly required; the same second sequence valve The second reversing valve and the throttle valve connection sequence on the oil line are also not strictly required to meet the function realization.
  • the solid phase change material is selected from n-hexadecane having a phase transition temperature of 18.2 ° C or a temperature sensitive hydrogel having a phase transition temperature of 18 ⁇ 2 ° C.
  • the phase transition temperature is between 8% and 10 ⁇ 3 ⁇ 4 in the solid-liquid phase change between the upper seawater and the bottom seawater.
  • the phase change material is n-hexadecane quinone, the sealing liquid is water, and the phase change material is solidified and shrinks.
  • the density of n-hexadecane is less than water, so the phase change hydraulic oil bladder is installed on the lower side of the phase change chamber; the phase change material is temperature sensitive hydrogel, and the solidification point of the seal liquid is -9.6. °C n-dodecane, phase change material solidification shrinkage ⁇ filled by n-dodecane, the temperature sensitive hydrogel density is greater than n-dodecane, so the phase change hydraulic oil capsule is installed in the phase change chamber The upper side of the body.
  • the solid-liquid phase change material is selected from n-hexadecane having a phase transition temperature of 18.2 ° C; and the sealing liquid is water.
  • the first sequence valve and the second sequence valve are externally controlled sequence valves; and the first directional control valve and the second directional control valve are hydraulically controlled directional control valves.
  • the external control pressure of the sequence valve is large, and can reach several tens of MPa.
  • the control pressure of the hydraulic control type directional control valve is generally several bar to several MPa but can withstand the pressure of several tens of MPa, which can be selected and set according to needs.
  • the spring pre-compression amount of the first sequence valve, the second sequence valve, the first reversing valve, and the second reversing valve are both adjustable. Both are adjusted according to the water depth range of the equipment before being placed. If the first sequence valve is replaced by a similarly functioned hydraulic control check valve, the accumulator pressure should be reasonably set and the hydraulic control check valve should be properly selected so that the hydraulic control check valve pressure is slightly lower than the corresponding water pressure at the deepest dive of the equipment. .
  • first and second are used merely to distinguish two or more components, and have no limiting effect on the function, order, and the like of these components.
  • the inner oil bladder is surrounded by a sealed cavity, and the inner wall of the sealed cavity is filled with the outer wall of the inner oil bladder.
  • nitrogen There is nitrogen, and the nitrogen pressure varies with the volume of the inner oil pocket. The amount of nitrogen gas is satisfied: After the oil of the outer oil bladder enters the inner oil bladder, the pressure of the inner oil bladder is greater than the spring force of the first reversing valve; after the inner oil bladder fluid is absorbed by the phase change hydraulic oil bladder, the inner oil bladder The pressure is less than the spring force of the first reversing valve.
  • the spring force setting value of the second sequence valve is slightly lower than the pressure of the accumulator after the solid liquid phase material is completely melted (if the spring force setting value is too low, the accumulator pressure is very high)
  • the low-lying equipment will sink, which will cause the accumulator at the lowest point to not fill the outer oil bladder. If the spring force setting is too high, the accumulator pressure will not hit the second sequence valve, and the equipment will not move.
  • the spring force setting value of the second reversing valve is slightly larger than the pressure value of the outer oil bladder at the highest point of the movement of the device profile (the spring force is set such that the second reversing valve at the highest point is smashed, and the device is lowered by several meters)
  • the rear spring force is equal to less than the outer oil bladder pressure, and the second reversing valve is gradually closed.
  • the spring force setting value of the first sequence valve is slightly smaller than the pressure value of the outer oil bladder at the lowest point of the device profile movement (the spring force is set like this) At the lowest point, the outer oil bladder pressure is greater than the spring force of the first sequence valve, and the first sequence valve is turned on.
  • the first change Spring to valve The force setting value is slightly higher than the pressure value of the inner oil bladder after the solid-liquid phase change material is completely condensed and contracted (the spring force is set to ensure that the solid-liquid phase change material is almost completely condensed, and the inner oil bladder fluid enters the phase change hydraulic oil to the maximum extent.
  • the capsule which produces high pressure preparation conditions for the next cycle of phase change material melting).
  • the throttle valve on the oil returning passage is a common throttle valve; the pressure difference on the oil inlet road is relatively high, and preferably, the throttle valve is a precision throttle valve.
  • both the phase change hydraulic oil bladder and the accumulator are hydraulic oil.
  • the accumulator can be selected from a diaphragm accumulator or a capsule accumulator.
  • the sealing liquid and the hydraulic oil are separated by a hydraulic oil capsule, and the phase change hydraulic oil bladder is installed on the phase change cavity through the sealing ring, and the sealing method is that the static sealing has better performance than the traditional piston type dynamic sealing. Sealing performance.
  • the phase change hydraulic oil bladder is installed in the phase change chamber, and the vacant portion of the phase change chamber is filled with the solid liquid phase change material and the sealing liquid, and the outer oil bladder and the phase change chamber are exposed to the sea water.
  • the other parts and pipelines are sealed in the sealed chamber; in the oil outlet and the oil inlet, the phase change hydraulic oil bladder is connected to the accumulator through the first one-way valve, and the accumulator is connected with the sequence valve of the oil inlet passage.
  • the oil path sequence valve is connected with the hydraulic control type directional control valve, and the hydraulic control type directional control valve is connected with the outer oil sac through a precision throttle valve; in the first oil return passage and the second return oil passage, the outer oil sac passage passage section
  • the flow valve is connected to the externally controlled sequence valve, and the externally controlled sequence valve is passed through the hydraulically controlled shut-off valve.
  • the inner oil bladder is connected, and the inner oil bladder is connected to the phase change hydraulic oil bladder through a one-way valve; in the control oil passage: the accumulator is connected to the control chamber of the external control type sequence valve on the oil circuit, and the oil port of the outer oil bladder is connected to the oil inlet.
  • the control chamber of the external control type sequence valve on the road is connected to the control chamber of the hydraulic control cut-off type reversing valve on the oil return line, and the inner oil tank port is connected to the control chamber of the hydraulic control cut-off type reversing valve.
  • the second sequence valve In the absence of external force, the second sequence valve is a normally closed valve, and the external force is greater than the spring force to close; the second reversing valve is a normally closed valve, and the external force is greater than the spring force to break;
  • the sequence valve is a normally closed valve, and the external force is greater than the spring force to close; the first reversing valve is a normally closed valve, and the external force is greater than the spring force to break.
  • the valve closing means that the oil can flow through the valve
  • the valve breaking means that the oil cannot flow through the valve
  • the normal closing and the normally closing means that the valve is only subjected to the spring force, often Closed means that the oil can flow through the valve. Normally, it means that the oil cannot flow through the valve.
  • the motion system is at the upper limit point, the second sequence valve is closed under the control of the accumulator, and the lower limit position is reached; the second reversing valve is lowered to the uniform speed in the motion system.
  • the falling point is broken, and the moving system rises to a constant speed drop point ⁇ closed; the first sequence valve closes when the motion system drops to a constant speed rising point, rises to a constant speed rising point, and breaks; the first reversing valve is at the upper limit point After the process of the constant speed drop point is interrupted, it is closed at the lower limit point.
  • the one-way valve of the present invention is a differential pressure control one-way valve.
  • the first one-way valve is turned on, and vice versa; the inner oil bladder pressure is greater than the phase change.
  • the hydraulic oil bladder pressure is ⁇ , the second check valve is turned on, and vice versa.
  • the solid-liquid phase change material provides a power source for the system through solidification shrinkage in the deep water low temperature zone and melting and expansion in the shallow water high temperature zone, and the accumulator stores energy and releases energy under the control of the hydraulic valve, the hydraulic valve
  • the control completely adopts the oil pressure of the external oil tank generated by the internal oil pressure and external water pressure of the system, no electric energy is required, and the high pressure to the set value due to the melting of the material, the equipment automatically sinks, and the internal oil bladder caused by the condensation of the material After the low pressure reaches the set value, the device automatically floats up. It does not need to be manually set according to its own movement. It makes full use of the temperature difference energy and maximizes the number of single day movements.
  • the invention has the advantages ofaki design, high temperature difference energy utilization, no need of any electromagnetic valve for control, no power consumption, no external human control, and improved equipment life and reliability.
  • FIG. 1 is a schematic diagram of an energy-saving temperature difference energy driven ocean profile motion system of the present invention.
  • FIG. 2 is a schematic diagram of the state of the system at the top of the motion range.
  • FIG. 3 is a schematic view showing the state of the liquid absorbing system from the outer oil sac.
  • FIG. 4 is a schematic diagram showing the state of a sinking system at a constant speed.
  • FIG. 5 is a schematic view showing the state of a liquid filling system for an external oil bladder.
  • FIG. 6 is a schematic diagram of a state of a floating system at a constant speed.
  • FIG. 7 is a schematic view showing the arrangement of the device in the sea.
  • phase change cavity 1, solid-liquid phase change material; 3, phase change hydraulic oil bladder; 4, check valve; 5, throttle valve; 6, external control sequence valve; 7, hydraulic control Cut-off reversing valve; 8, inner oil bladder; 9, sealed cavity; 10, outer oil bladder; 11, precision throttle valve; 12, hydraulic control cut-off reversing valve; 13, external control sequence valve; , check valve; 15, hydraulic oil; 16, accumulator; 17, oil inlet; 18a, return road; 18b, return road; 19, control oil circuit; 20, oil circuit; .
  • an energy-saving temperature difference capable driving marine profile motion system of the present invention includes: a phase change cavity 1, a phase change hydraulic oil bladder 3, a check valve 4, a throttle valve 5, and an external control sequence.
  • Valve 6 hydraulically controlled shut-off valve 7, inner oil bladder 8, sealed chamber 9, outer oil bladder 10, precision throttle valve 11, hydraulically controlled shut-off valve 12, externally controlled sequence valve 13, one-way
  • the phase change cavity 1 is two.
  • the phase change hydraulic oil bladder 3 is installed in the phase change chamber 1, and the vacant portion in the phase change chamber 1 is filled with the solid liquid phase change material 2 and the sealing liquid 21, and the phase change hydraulic oil bladder 3 is surrounded by the sealing liquid 21,
  • the oil bladder 10 and the phase change chamber 1 are exposed to seawater, and other parts and pipelines are sealed within the sealed cavity.
  • both the externally controlled sequence valve and the cut-off type reversing valve adopt a liquid-controlled structure, and the control of the working state thereof is realized by the liquid pressure change of the peripheral device.
  • oil outlet 20 phase change hydraulic oil bladder 3 through the check valve 14 connected to the accumulator 16;
  • the oil inlet 17 the accumulator 16 is connected to the externally controlled sequence valve 13, the externally controlled sequence valve 13 is connected to the hydraulically controlled directional control valve 12, and the hydraulically controlled directional control valve 12 is passed through the precision throttle valve 11 is connected to the outer oil bladder 10; the precision throttle valve 1 1 , the external control type sequence valve 13 and the liquid control cut-off type reversing valve 12 are not strictly required on the inlet circuit 17 , and can be adjusted according to actual needs;
  • the oil return passage 18a the outer oil bladder is connected to the external control type sequence valve 6 through the throttle valve 5, and the external control type sequence valve 6 is connected to the inner oil bladder 8 through the hydraulic control cut-off valve 7; the throttle valve 5, The relative installation sequence of the externally controlled sequence valve 6 and the hydraulically controlled shut-off valve 7 on the oil return passage 18a is also not strictly limited, and can be adjusted according to actual needs; [0050] the oil return passage 18b: the inner oil bladder 8 is connected to the phase change hydraulic oil bladder 3 through the check valve 4;
  • the control oil passage 19 the accumulator 16 is connected to the control chamber of the external control type sequence valve 6 on the return oil passage 18a, and the outer oil bladder 10 is connected to the control chamber of the externally controlled sequence valve 13 on the oil passage 17
  • the other circuit is connected to the control chamber of the hydraulically controlled shut-off type reversing valve 7 on the oil returning circuit 18a, and the oil port 8 is connected to the control chamber of the hydraulically controlled shut-off type reversing valve 12 on the oil passage 17.
  • the solid-liquid phase change material adopts n-hexadecane with a phase transition temperature of 18.2 ° C, and the phase transition temperature is between the temperature of the upper seawater and the bottom seawater, the solid phase density is 835 Kg/m 3 , and the liquid phase density is 770.1 Kg. /m3, the solid-liquid phase change volume changes by 8%, the sealing liquid uses water, the phase change material solidifies, and the water creates a space for solidification; [0054] The sealing liquid and the hydraulic oil are separated by hydraulic oil capsule, hydraulic oil The bladder is mounted on the phase change chamber by a sealing ring
  • the sealing method is static sealing, which has better sealing performance than the traditional piston type dynamic sealing.
  • the external control type sequence valve 6 on the oil returning path 18a, the hydraulic control cut-off reversing valve 7 on the returning oil path 18a, the externally controlled sequence valve 13 on the oil inlet path 17, and the hydraulically controlled cut-off type reversing valve on the oil inlet path The spring pre-compression amount of 12 is adjustable, and it is adjusted according to the water depth range of the cloth before the equipment is placed.
  • the upper pressure difference is higher, and the throttle valve 11 on the oil inlet 17 is a precision throttle valve having a high throttling accuracy.
  • the inside of the sealed chamber 9 enclosing the oil bladder is nitrogen gas, and the nitrogen pressure varies with the volume of the inner oil bladder.
  • the amount of nitrogen gas to be inflated should ensure that the oil in the outer oil bladder 10 enters the inner oil bladder 8, the pressure of the inner oil bladder 8 is greater than the spring force of the hydraulic control shut-off valve 12 on the oil inlet 17; the inner oil bladder 8 oil After the liquid is absorbed by the phase change hydraulic oil bladder 3, the pressure of the inner oil bladder 8 is smaller than the spring force of the hydraulic control cut-off type reversing valve 12 of the inlet oil passage.
  • the spring force setting value of the externally controlled sequence valve 6 on the return oil passage 18a is slightly lower than the pressure of the accumulator 16 after the phase change material is completely melted, and the spring of the hydraulic control cutoff reversing valve 7 on the return oil passage 18a
  • the force setting value is slightly larger than the highest point of the device profile movement (corresponding position of the upper limit position in Fig. 7).
  • the pressure value of the oil tank 10 oil, the spring force setting value of the external control type sequence valve 13 on the oil inlet 17 is slightly It is less than the lowest point of the section movement of the equipment (corresponding position of the lower limit in Fig. 7).
  • the pressure value of the oil tank 10, the spring force setting value of the hydraulic control type shut-off valve 12 on the inlet 17 Slightly higher than the pressure value of the inner oil bladder 8 after the complete condensation of the phase change material.
  • An energy-saving temperature difference can drive the ocean profile motion system as follows:
  • the device is physically limited to the upper and lower positions according to the required range of motion depth, as shown in FIG. 7: the anchor block is fixed to the sea bottom, and the guiding cable is fixed between the anchor block and the buoyancy material; the energy-saving temperature difference of the invention
  • the marine profile motion system can be driven to slide on the cable; the upper and lower limit points are set according to actual requirements.
  • the device In the initial state, the device is in a positive buoyancy state and is limited to the upper limit of the range of motion. Since the device is at the highest position, the pressure of the outer oil bladder 10 is much lower than the spring force of the externally controlled sequence valve 13, so the externally controlled sequence valve 13 is in the closed state; due to the spring force setting value of the hydraulically controlled shut-off type switching valve 7 Slightly larger than the pressure of the outer oil bladder 10 at the highest position, so the hydraulically controlled shut-off type reversing valve 7 is turned on; since the oil tank 8 in this crucible has the least oil, the pressure is lower than the spring force of the hydraulically controlled shut-off type reversing valve 12, Therefore, the hydraulically controlled shut-off type reversing valve 12 is turned on, as shown in FIG.
  • the phase change material melts and expands and pressures up, so the check valve 4 is closed, the check valve 14 is turned on, and the high pressure oil in the phase change hydraulic oil bladder 3 is filled to In the accumulator 16, as the phase change material melts, the pressure of the accumulator 16 gradually rises, and when the pressure rises to the set value of the externally controlled sequence valve 6, the externally controlled sequence valve 6 is snoring and returning to oil.
  • the road 18a is turned on, and the oil in the outer oil bladder 10 enters the inner oil bladder 8, and the device changes from a positive buoyancy state to a negative buoyancy state, and the device sinks, as shown in FIG.
  • the inward oil bladder 8 As the inward oil bladder 8 is filled, the internal oil bladder pressure rises to the set spring value ⁇ of the hydraulically controlled shut-off type reversing valve 12, the reversing valve 12 is closed; after sinking for a short distance, The oil bladder pressure is greater than the spring force setting value of the hydraulically controlled shut-off type directional control valve ⁇ , the hydraulic control cut-off type directional control valve 7 is closed, the return oil passage 18a is broken, reaches the uniform speed drop point, and the device sinks at a constant speed, as shown in Fig. 4 Shown.
  • the value is slightly less than the pressure value of the outer oil pocket fluid at the lowest point of the profile movement, so the equipment sinks to the lowest point, and the externally controlled sequence valve 13 is turned on; the above two conditions are satisfied, and the accumulator is charged to the outer oil bladder.
  • the liquid, the accumulator pressure is reduced, the outer oil bladder volume is increased, and the equipment is gradually floating as shown in Fig. 5.
  • the accumulator pressure is lower than the spring force of the externally controlled sequence valve 6, and the externally controlled sequence valve 6 is closed; after the small distance is raised, when the external oil bladder pressure is lower than the spring setting of the externally controlled sequence valve 13
  • the value ⁇ the external control sequence valve 13 is closed, the oil inlet circuit is closed, and reaches the uniform rising point, and the device floats at a constant speed, as shown in Fig. 6.
  • the invention does not require any electromagnetic valve to control, saves electric energy; can use the temperature difference of seawater to self-float and sink; can adaptively change the phase change according to the seawater temperature, and immediately rise or sink after the phase change is completed.
  • the number of cross-section movements is greatly improved; the control in the present invention all directly comes from the hydraulic pressure of the hydraulic pipeline, and the conventional pressure sensor and the electric control device are not used, which saves the cost and improves the reliability of the system.

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  • Mechanical Engineering (AREA)
  • Fluid Mechanics (AREA)
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  • Supply Devices, Intensifiers, Converters, And Telemotors (AREA)
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Abstract

一种节能型温差能驱动海洋剖面运动系统，包括：相变腔体(1)；设置在相变腔体(1)内的相变液压油囊(3)；通过出油路(20)与相变液压油囊(3)连接的蓄能器(16)；通过进油路(17)与蓄能器(16)连接的外油囊(10)；通过第一回油路与外油囊(10)连接的内油囊(8)；相变液压油囊(3)同时通过第二回油路与内油囊(8)连接；外油囊(10)和相变腔体(1)设于一密封腔外，其余部件和油路均设于该密封腔内。该系统不需要任何电磁阀进行控制，节省了电能；能够利用海水的温差能自行上浮下沉；能够根据海水温度自适应的改变相变时间，相变完成后立即上浮或下沉，极大提高了剖面运动次数；其控制全部直接来自液压管路的油压，没有采用传统的压力传感器，节省了成本并提高了系统的可靠性。

Description

说明书 发明名称：一种温差能驱动海洋剖面运动系统 技术领域
[0001] 本发明涉及海洋剖面运动系统， 尤其是一种节能型温差能驱动海洋剖面运动系 统。
背景技术
[0002] 海洋剖面运动设备是人们研究和探测海洋的重要工具。 对于需要长期持续地在 海洋中工作的监测设备， 传统上都是采用锂电池的供电方式， 然而锂电池的能 耗有相当一部分用于设备的驱动与控制， 极大的降低了剖面运动设备的使用寿 命。 目前已经有应用温差能驱动的运动系统， 其对设备运动的控制靠电磁阀来 完成， 然而电磁阀几十瓦的能耗对于这种在海洋中长期值守的剖面运动设备来 说依然过大。 另一方面， 充足的海洋观测数据是人们深入认识海洋的必要条件 ， 传统上的剖面监测设备受电池电量的限制无法提高剖面运动次数。 最后， 剖 面监测设备的运动一般都由单片机进行电气控制， 一旦发生问题便会导致设备 故障， 降低了设备的可靠性。
技术问题
[0003] 本发明的目的是针对现有海洋剖面运动系统在控制方式以及能耗上的缺陷， 提 出一种结构简洁、 运行可靠的节能型温差能驱动海洋剖面运动系统。
问题的解决方案
技术解决方案
[0004] 一种节能型温差能驱动海洋剖面运动系统， 包括：
[0005] 盛放有固液相变材料和密封液体的相变腔体；
[0006] 设置在相变腔体内被密封液体包覆的相变液压油囊；
[0007] 通过带有第一单向阀的出油路与所述相变液压油囊连接的蓄能器；
[0008] 通过带有第一顺序阀、 第一换向阀的进油路与所述蓄能器连接的外油囊； [0009] 通过带有第二顺序阀、 第二换向阀的第一回油路与所述外油囊连接的内油囊； [0010] 所述相变液压油囊同吋通过带有第二单向阀的第二回油路与内油囊连接； [0011] 所述外油囊和相变腔体设于一密封腔外， 其余部件和油路均设于该密封腔内； [0012] 所述第一顺序阀、 第二换向阀均受控于所述外油囊； 所述第一换向阀受控于内 油囊； 所述第二顺序阀受控于所述蓄能器。
[0013] 作为优选， 所述进油路上设有节流阀。
[0014] 作为优选， 所述第一回油路上设有节流阀。
[0015] 本发明中， 所述第一顺序阀、 第一换向阀和该油路上的节流阀其功能相对独立 ， 在进油路上连接顺序无严格要求； 同样的所述第二顺序阀、 第二换向阀和该 油路上的节流阀连接顺序也无严格要求， 以满足功能实现为准。
[0016] 作为优选， 所述固液相变材料选用相变温度为 18.2°C的正十六烷或相变温度为 18±2°C的温度敏感性水凝胶。 其相变温度处于上层海水与底层海水温度之间固 液相变吋体积变化 8%-10<¾， 相变材料为正十六烷吋， 密封液体选用水， 相变材 料凝固收缩吋由水填补凝固所产生的空间， 正十六烷密度小于水， 因此相变液 压油囊安装在相变腔体的下侧； 相变材料为温敏性水凝胶吋， 密封液体选用凝 固点为 -9.6°C的正十二烷， 相变材料凝固收缩吋由正十二烷填补凝固所产生的空 间， 温敏性水凝胶密度大于正十二烷， 因此相变液压油囊安装在相变腔体的上 侧。 作为更进一步优选， 所述固液相变材料选用相变温度为 18.2°C的正十六烷； 密封液体选用水。
[0017] 作为优选， 所述第一顺序阀、 第二顺序阀为外控式顺序阀； 所述第一换向阀、 第二换向阀为液控截止式换向阀。 顺序阀的外控压力较大， 能到几十 MPa， 液控 截止式换向阀的控制压力一般在几 bar到几 MPa但是能承受几十 MPa的压力， 可 根据需要进行选择和设定。
[0018] 作为优选， 所述第一顺序阀、 第二顺序阀、 第一换向阀、 第二换向阀的弹簧预 压缩量均可调。 且均在设备布放前根据布放的水深范围调节好。 若第一顺序阀 由类似功能的液控单向阀替代， 应合理设置蓄能器压力及合理选择液控单向阀 使液控单向阀幵启压力略小于设备最深下潜处对应水压。
[0019] 本发明中， 涉及到的"第一""第二"仅仅是用于区别两个或多个部件， 对这些部 件的功能和顺序等均没有限定作用。
[0020] 作为优选， 所述内油囊外包围有密封腔体， 密封腔体内壁与内油囊外壁之间充 有氮气， 氮气压力随内油囊体积而变化。 氮气的充气量满足： 外油囊的油液进 入内油囊后， 内油囊的压力大于第一换向阀的弹簧力； 内油囊油液被相变液压 油囊吸收后， 内油囊的压力小于第一换向阀的弹簧力。
[0021] 作为优选， 所述第二顺序阀的弹簧力设定值略低于固液相变材料完全融化后蓄 能器的压力 （若弹簧力设定值太低， 则蓄能器压力很低吋设备便下沉， 会导致 设备在最低点处蓄能器无法给外油囊充液； 若弹簧力设定值太高， 则蓄能器压 力打不幵第二顺序阀， 设备无法运动） ； 所述第二换向阀的弹簧力设定值略大 于设备剖面运动最高点处外油囊的压力值 （弹簧力这样设置可以使最高点处第 二换向阀打幵， 设备下降几米后弹簧力等于直至小于外油囊压力， 第二换向阀 逐渐关闭） ， 第一顺序阀的弹簧力设定值略小于设备剖面运动最低点处外油囊 的压力值 （弹簧力这样设置可使在最低点处外油囊压力大于第一顺序阀的弹簧 力， 第一顺序阀导通。 同吋若设备不下降到接近最低点， 第一顺序阀不通， 设 备继续下降） ， 第一换向阀的弹簧力设定值略高于固液相变材料完全冷凝收缩 后内油囊的压力值 （弹簧力这样设置可确保固液相变材料几乎完全冷凝， 内油 囊油液最大限度进入相变液压油囊， 为下一循环相变材料融化产生高压准备条 件） 。
[0022] 由于回油路上压差较小， 因此回油路上节流阀为普通节流阀； 进油路上压差较 高， 作为优选， 所述节流阀为精密节流阀。
[0023] 本发明中， 相变液压油囊与蓄能器内均为液压油。 蓄能器可选择隔膜式蓄能器 或者囊式蓄能器。 其中密封液体与液压油之间由液压油囊隔断， 相变液压油囊 通过密封圈安装在相变腔体上， 其密封方式为静密封与传统的活塞式的动密封 相比具有更好的密封性能。
[0024] 本发明中， 相变液压油囊安装在相变腔体内， 相变腔体内的空余部分装满固液 相变材料与密封液体， 外油囊、 相变腔体暴露在海水中， 其他零件及管路密封 在密封腔之内； 在出油路和进油路， 相变液压油囊通过第一单向阀连接蓄能器 ， 蓄能器与进油路的顺序阀连接， 进油路上顺序阀与液控截止式换向阀连接， 液控截止式换向阀通过精密节流阀与外油囊连接； 在第一回油路和第二回油路 ， 外油囊通过节流阀与外控式顺序阀连接， 外控式顺序阀通过液控截止换向阀 连接内油囊， 内油囊通过单向阀与相变液压油囊相连； 在控制油路： 蓄能器连 接回油路上外控式顺序阀的控制腔， 外油囊的油口连接进油路上外控式顺序阀 的控制腔， 另一路连接回油路上液控截止式换向阀的控制腔， 内油囊油口连接 进油路液控截止式换向阀的控制腔。
[0025] 本发明中， 通过各个阀门的配合工作， 实现对油路的控制， 最终实现对运动系 统的控制。 我们假设， 运动系统运动过程中， 根据运动位置和运动性质的不同 ， 自上而下， 分别具有上限位点、 匀速下降点、 匀速上升点、 下限位点， 如图 7 所示， 在这些点位及点位之间， 各阀动作顺序如表 1所示：
[0026] 表 1各阀动作顺序表
[0027]
Figure imgf000006_0001
[0028] 在没有外力作用吋， 第二顺序阀为常幵阀门， 外力大于弹簧弹力吋才会闭合； 第二换向阀则为常闭阀门， 外力大于弹簧弹力吋才会断幵； 第一顺序阀为常幵 阀门， 外力大于弹簧弹力吋才会闭合； 第一换向阀为常闭阀门， 外力大于弹簧 弹力吋才会断幵。
[0029] 本发明中： 阀门闭合是指油液可以流通此阀， 阀门断幵是指油液不可以流通此 阀； 常幵、 常闭是指阀在只受弹簧力作用吋的状态， 常闭是指油液可以流通此 阀， 常幵是指油液无法流通此阀。 [0030] 在运动系统运行过程中， 运动系统在上限位点处， 第二顺序阀在蓄能器控制下 闭合， 在到达下限位点吋断幵； 第二换向阀在运动系统下降到匀速下降点吋断 幵， 在运动系统上升到匀速下降点吋闭合； 第一顺序阀在运动系统下降到匀速 上升点吋闭合， 上升到匀速上升点吋断幵； 第一换向阀在上限位点到匀速下降 点过程中断幵， 在下限位点吋闭合。
[0031] 本发明单向阀为压差控制单向阀， 当相变处液压油囊压力大于蓄能器压力吋， 第一单向阀导通， 反之关闭； 内油囊压力大于相变处液压油囊压力吋， 第二单 向阀导通， 反之关闭。
发明的有益效果
有益效果
[0032] 与现有技术相比， 本发明的优势如下：
[0033] 本发明中固液相变材料通过深水低温区的凝固收缩与浅水高温区的融化膨胀为 系统提供动力来源， 蓄能器储存能量并在液压阀的控制下进行能量的释放， 液 压阀的控制完全采用系统内部油压及外部水压所产生的外油囊油压， 不需电能 ， 同吋由于材料融化产生的高压至设定值吋设备自动下沉， 材料冷凝导致的内 油囊低压至设定值后设备自动上浮， 完全根据自身状况运动不需要进行人为设 定， 充分利用了温差能， 最大限度提高了单日运动次数。 本发明设计精巧， 温 差能利用率高， 不需要任何电磁阀进行控制， 无需耗电， 无需外部人为控制， 提高了设备的寿命及可靠性。
对附图的简要说明
附图说明
[0034] 图 1为本发明的节能型温差能驱动海洋剖面运动系统示意图。
[0035] 图 2为处于运动范围最上位吋系统状态示意图。
[0036] 图 3为从外油囊吸液吋系统状态示意图。
[0037] 图 4为匀速下沉吋系统状态示意图。
[0038] 图 5为给外油囊充液吋系统状态示意图。
[0039] 图 6为匀速上浮吋系统状态示意图。
[0040] 图 7为设备在海中布置方式示意图。 [0041] 上述附图中：
[0042] 1、 相变腔体； 2、 固液相变材料； 3、 相变液压油囊； 4、 单向阀； 5、 节流阀 ； 6、 外控式顺序阀； 7、 液控截止式换向阀； 8、 内油囊； 9、 密封腔体； 10、 外油囊； 11、 精密节流阀； 12、 液控截止式换向阀； 13、 外控式顺序阀； 14、 单向阀； 15、 液压油； 16、 蓄能器； 17、 进油路； 18a、 回油路； 18b、 回油路 ； 19、 控制油路； 20、 出油路； 21、 密封液体。
本发明的实施方式
[0043] 以下结合附图进一步说明本发明。
[0044] 参照图 1， 本发明的一种节能型温差能驱动海洋剖面运动系统包括： 相变腔体 1 、 相变液压油囊 3、 单向阀 4、 节流阀 5、 外控式顺序阀 6、 液控截止换向阀 7、 内 油囊 8、 密封腔体 9、 外油囊 10、 精密节流阀 11、 液控截止式换向阀 12、 外控式 顺序阀 13、 单向阀 14、 蓄能器 16; 以及将这些部件连接的油路： 出油路 20、 进 油路 17、 回油路 18a、 回油路 18b和多条控制油路 19。
[0045] 图 1中， 相变腔体 1为两个。 相变液压油囊 3安装在相变腔体 1内， 相变腔体 1内 的空余部分装满固液相变材料 2与密封液体 21， 相变液压油囊 3被密封液体 21包 围， 外油囊 10、 相变腔体 1暴露在海水中， 其他零件及管路密封在密封腔体之内
[0046] 本发明中， 外控式顺序阀和截止式换向阀均采用液控式结构， 通过外设的液体 压力变化实现对其工作状态的控制。
[0047] 出油路 20: 相变液压油囊 3通过单向阀 14连接蓄能器 16;
[0048] 进油路 17: 蓄能器 16连接外控式顺序阀 13， 外控式顺序阀 13与液控截止式换向 阀 12连接， 液控截止式换向阀 12通过精密节流阀 11连接外油囊 10; 精密节流阀 1 1、 外控式顺序阀 13与液控截止式换向阀 12在进油路 17上的相对安装顺序没有严 格要求， 可根据实际需要调整确定；
[0049] 回油路 18a: 外油囊通过节流阀 5与外控式顺序阀 6连接， 外控式顺序阀 6通过液 控截止换向阀 7连接内油囊 8 ; 节流阀 5、 外控式顺序阀 6与液控截止换向阀 7在回 油路 18a上的相对安装顺序也无严格限制， 可根据实际需要调整； [0050] 回油路 18b: 内油囊 8通过单向阀 4与相变液压油囊 3相连；
[0051] 控制油路 19: 蓄能器 16连接回油路 18a上外控式顺序阀 6的控制腔， 外油囊 10— 路连接进油路 17上外控式顺序阀 13的控制腔， 另一路连接回油路 18a上液控截止 式换向阀 7的控制腔， 内油囊 8油口连接进油路 17上液控截止式换向阀 12的控制 腔。
[0052] 其中：
[0053] 固液相变材料选用相变温度为 18.2°C的正十六烷， 其相变温度处于上层海水与 底层海水温度之间， 其固相密度 835Kg/m3,液相密度为 770.1 Kg/m3， 固液相变吋 体积变化 8%， 密封液体选用水， 相变材料凝固吋由水填补凝固所产生的空间； [0054] 密封液体与液压油之间由液压油囊隔断， 液压油囊通过密封圈安装在相变腔上
， 其密封方式为静密封， 与传统的活塞式的动密封相比具有更好的密封性能。
[0055] 回油路 18a上外控式顺序阀 6、 回油路 18a上液控截止换向阀 7、 进油路 17上外控 式顺序阀 13、 进油路上液控截止式换向阀 12的弹簧预压缩量可调， 且均在设备 布放前根据布放的水深范围调节好。
[0056] 由于回油路 18a上压差较小， 因此回油路 18a上节流阀 5为普通节流阀； 进油路 1
7上压差较高， 进油路 17上的节流阀 11为具有很高节流精度的精密节流阀。
[0057] 对于单向阀 4， 当内油囊 8压力大于相变液压油囊 3内压力吋， 单向导通； 对于 单向阀 14， 当相变液压油囊 3内压力大于蓄能器 16内液压油 15吋， 单向阀 14单向 导通。
[0058] 包裹内油囊的密封腔体 9内为氮气， 氮气压力随内油囊 8体积而变化。 设计吋， 氮气的充气量应保证外油囊 10油液进入内油囊 8后， 内油囊 8压力大于进油路 17 上液控截止式换向阀 12的弹簧力； 内油囊 8油液被相变液压油囊 3吸收后， 内油 囊 8压力小于进油路液控截止式换向阀 12的弹簧力。
[0059] 回油路 18a上外控式顺序阀 6的弹簧力设定值略微低于相变材料完全融化后蓄能 器 16的压力， 回油路 18a上液控截止换向阀 7的弹簧力设定值略微大于设备剖面运 动最高点处 （图 7中上限位对应位置） 夕卜油囊 10油液的压力值， 进油路 17上外控 式顺序阀 13的弹簧力设定值略小于设备剖面运动最低点处 （图 7中下限位对应位 置） 夕卜油囊 10油液的压力值， 进油路 17上液控截止式换向阀 12的弹簧力设定值 略高于为相变材料完全冷凝收缩后内油囊 8的压力值。
[0060] 一种节能型温差能驱动海洋剖面运动系统的工作原理如下：
[0061] 首先根据所需的运动深度范围将设备进行上下位的物理限制， 如图 7所示： 锚 块固定于海底， 锚块与浮力材料之间固定有导向缆绳； 本发明的节能型温差能 驱动海洋剖面运动系统在该缆绳上滑动； 按照实际要求设置好上限位点和下限 位点。
[0062] 初始状态吋， 设备处于正浮力状态且被限位在运动范围的上限。 由于设备处于 最高位， 外油囊 10压力远低于外控式顺序阀 13的弹簧力， 因此外控式顺序阀 13 处于关闭状态； 由于液控截止式换向阀 7的弹簧力设定值稍微大于处于最高位的 外油囊 10压力， 因此液控截止式换向阀 7导通； 由于此吋内油囊 8油液最少， 压 力低于液控截止式换向阀 12的弹簧力， 因此液控截止式换向阀 12导通， 如图 2所 示。
[0063] 由于浅层海水温度高于材料相变温度， 相变材料融化膨胀升压， 因此单向阀 4 关闭， 单向阀 14导通， 相变液压油囊 3中的高压油充液至蓄能器 16中， 随着相变 材料融化， 蓄能器 16压力逐渐升高， 当压力升高到外控式顺序阀 6的设定值吋， 外控式顺序阀 6打幵， 回油路 18a导通， 外油囊 10中的油液进入内油囊 8， 设备从 正浮力状态变为负浮力状态， 设备下沉， 如图 3所示。
[0064] 随着往内油囊 8充液， 内油囊压力升高至液控截止式换向阀 12的设定弹簧值吋 ， 换向阀 12关闭； 下沉一小段距离后， 当外油囊压力大于液控截止式换向阀 7的 弹簧力设定值吋， 液控截止式换向阀 7关闭， 回油路 18a断幵， 到达匀速下降点， 设备匀速下沉， 如图 4所示。
[0065] 当深水区水温低于相变材料的相变温度吋， 材料冷凝收缩， 相变液压油囊 3内 逐渐产生真空， 内油囊 8的低压油通过单向阀 4为相变液压油囊 3补油， 油囊 8油 压降至液控截止式换向阀 12的弹簧设定值吋， 液控截止式换向阀 12导通； 由于 外控式顺序阀 13的弹簧力设定值略小于剖面运动最低点处外油囊油液的压力值 ， 因此设备下沉到最低点吋， 外控式顺序阀 13导通； 以上两条件都满足吋， 蓄 能器给外油囊充液， 蓄能器压力降低， 外油囊体积增大， 设备逐渐上浮如图 5所 示。 [0066] 蓄能器压力低于外控式顺序阀 6的弹簧力吋， 外控式顺序阀 6关闭； 上浮小段距 离后， 当外油囊压力低于外控式顺序阀 13的弹簧设定值吋， 外控式顺序阀 13关 闭， 进油路关闭， 到达匀速上升点， 设备匀速上浮， 如图 6所示。
[0067] 随着上浮， 外油囊压力降低， 压力小于液控截止式换向阀 7的弹簧力吋， 液控 截止式换向阀 7导通， 由于此吋外控式顺序阀 6依然关闭， 回油路 18a不通， 设备 依然上浮直至最上位， 如图 2所示， 至此一个循环完成。
[0068] 本发明不需要任何电磁阀进行控制， 节省了电能； 能够利用海水的温差能自行 上浮下沉； 能够根据海水温度自适应的改变相变吋间， 相变完成后立即上浮或 下沉， 极大提高了剖面运动次数； 本发明中的控制全部直接来自液压管路的油 压， 没有采用传统的压力传感器及电控设备， 节省了成本并提高了系统的可靠 性。

Claims

权利要求书
[权利要求 1] 一种温差能驱动海洋剖面运动系统， 其特征在于， 包括：
盛放有固液相变材料和密封液体的相变腔体；
设置在相变腔体内被密封液体包覆的相变液压油囊；
通过带有第一单向阀的出油路与所述相变液压油囊连接的蓄能器； 通过带有第一顺序阀、 第一换向阀的进油路与所述蓄能器连接的外油 通过带有第二顺序阀、 第二换向阀的第一回油路与所述外油囊连接的 内油囊；
所述相变液压油囊同吋通过带有第二单向阀的第二回油路与内油囊连 接；
所述外油囊和相变腔体设于一密封腔外， 其余部件和油路均设于该密 封腔内；
所述第一顺序阀、 第二换向阀均受控于所述外油囊； 所述第一换向阀 受控于内油囊； 所述第二顺序阀受控于所述蓄能器。
[权利要求 2] 根据权利要求 1所述的温差能驱动海洋剖面运动系统， 其特征在于， 所述进油路上设有节流阀。
[权利要求 3] 根据权利要求 1所述的温差能驱动海洋剖面运动系统， 其特征在于， 所述第一回油路上设有节流阀。
[权利要求 4] 根据权利要求 1所述的温差能驱动海洋剖面运动系统， 其特征在于， 所述固液相变材料选用相变温度为 18.2°C的正十六烷或者相变温度为
18±2°C的温度敏感性水凝胶。
[权利要求 5] 根据权利要求 1所述的温差能驱动海洋剖面运动系统， 其特征在于， 所述第一顺序阀、 第二顺序阀为外控式顺序阀； 所述第一换向阀、 第 二换向阀为液控截止式换向阀； 所述第一顺序阀、 第二顺序阀、 第一 换向阀、 第二换向阀的弹簧预压缩量均可调。
[权利要求 6] 根据权利要求 1或 5所述的温差能驱动海洋剖面运动系统， 其特征在 于， 所述内油囊外包围有密封腔体， 密封腔体内壁与内油囊外壁之间 充有氮气， 氮气的充气量满足： 外油囊的油液进入内油囊后， 内油囊 的压力大于第一换向阀的弹簧力； 内油囊油液被相变液压油囊吸收彻 底后， 内油囊的压力小于第一换向阀的弹簧力。
[权利要求 7] 根据权利要求 1或 5所述的温差能驱动海洋剖面运动系统， 其特征在于 ， 所述第二顺序阀的弹簧力设定值略低于固液相变材料完全融化后蓄 能器的压力； 所述第二换向阀的弹簧力设定值略大于设备剖面运动最 高点处外油囊的压力值， 第一顺序阀的弹簧力设定值略小于设备剖面 运动最低点处外油囊的压力值， 第一换向阀的弹簧力设定值略高于固 液相变材料完全冷凝收缩后内油囊的压力值。
[权利要求 8] 根据权利要求 2所述的温差能驱动海洋剖面运动系统， 其特征在于， 所述节流阀为精密节流阀。
[权利要求 9] 根据权利要求 1或 4所述的温差能驱动海洋剖面运动系统， 其特征在于 ， 相变材料为正十六烷吋， 密封液体为水， 相变材料为温度敏感性水 凝胶吋， 密封液体为正十二烷。
[权利要求 10] 根据权利要求 9所述的温差能驱动海洋剖面运动系统， 相变材料为正 十六烷吋相变液压油囊安装在相变腔体的下侧， 相变材料为温度敏感 性水凝胶吋相变液压油囊安装在相变腔体的上侧。
[权利要求 11] 根据权利要求 1或 5或 7所述的温差能驱动海洋剖面运动系统， 第一顺 序阀由液控单向阀替代， 第二顺序阀由卸荷阀替代。
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