CN107387499A - A kind of hydraulic means suitable for underwater sound emission Burning rate testing system - Google Patents
A kind of hydraulic means suitable for underwater sound emission Burning rate testing system Download PDFInfo
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- 238000012360 testing method Methods 0.000 title claims abstract description 32
- 239000003921 oil Substances 0.000 claims abstract description 57
- 238000002485 combustion reaction Methods 0.000 claims abstract description 56
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims abstract description 50
- 239000010720 hydraulic oil Substances 0.000 claims abstract description 21
- 229910001220 stainless steel Inorganic materials 0.000 claims abstract description 13
- 239000010935 stainless steel Substances 0.000 claims abstract description 13
- 230000000087 stabilizing effect Effects 0.000 claims description 25
- IJGRMHOSHXDMSA-UHFFFAOYSA-N Atomic nitrogen Chemical compound N#N IJGRMHOSHXDMSA-UHFFFAOYSA-N 0.000 claims description 22
- 239000007788 liquid Substances 0.000 claims description 16
- 239000007789 gas Substances 0.000 claims description 14
- 229910052757 nitrogen Inorganic materials 0.000 claims description 11
- 230000035939 shock Effects 0.000 claims description 7
- 239000002828 fuel tank Substances 0.000 claims description 5
- 238000006243 chemical reaction Methods 0.000 claims description 3
- 238000011084 recovery Methods 0.000 claims description 3
- 230000000712 assembly Effects 0.000 abstract 1
- 238000000429 assembly Methods 0.000 abstract 1
- 239000004449 solid propellant Substances 0.000 description 12
- 230000006837 decompression Effects 0.000 description 6
- 238000000034 method Methods 0.000 description 6
- 238000011056 performance test Methods 0.000 description 6
- 239000010729 system oil Substances 0.000 description 4
- 230000008569 process Effects 0.000 description 3
- 230000006641 stabilisation Effects 0.000 description 3
- 238000011105 stabilization Methods 0.000 description 3
- 230000001276 controlling effect Effects 0.000 description 2
- 238000011156 evaluation Methods 0.000 description 2
- 230000006872 improvement Effects 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 239000003380 propellant Substances 0.000 description 2
- 238000011160 research Methods 0.000 description 2
- 238000012827 research and development Methods 0.000 description 2
- 230000035945 sensitivity Effects 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 238000013461 design Methods 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 229910001873 dinitrogen Inorganic materials 0.000 description 1
- 238000005008 domestic process Methods 0.000 description 1
- 239000003344 environmental pollutant Substances 0.000 description 1
- 238000005259 measurement Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 231100000719 pollutant Toxicity 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
Classifications
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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
- F15B19/00—Testing; Calibrating; Fault detection or monitoring; Simulation or modelling of fluid-pressure systems or apparatus not otherwise provided for
- F15B19/007—Simulation or modelling
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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
- F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
- F15B1/02—Installations or systems with accumulators
- F15B1/027—Installations or systems with accumulators having accumulator charging devices
- F15B1/033—Installations or systems with accumulators having accumulator charging devices with electrical control means
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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
- F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
- F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
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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
- 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
- F15B13/06—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with two or more servomotors
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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
- F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
- F15B21/04—Special measures taken in connection with the properties of the fluid
- F15B21/041—Removal or measurement of solid or liquid contamination, e.g. filtering
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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
- F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
- F15B21/04—Special measures taken in connection with the properties of the fluid
- F15B21/042—Controlling the temperature of the fluid
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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
- F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
- F15B21/08—Servomotor systems incorporating electrically operated control means
- F15B21/087—Control strategy, e.g. with block diagram
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- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
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- Analytical Chemistry (AREA)
- Fluid-Pressure Circuits (AREA)
- Investigating Strength Of Materials By Application Of Mechanical Stress (AREA)
Abstract
本发明属于水下声发射燃速测试相关技术领域，其公开了一种适用于水下声发射燃速测试系统的液压装置，所述液压装置包括增压系统，所述增压系统包括增压组件，所述增压组件包括一次通过管道相连接的油箱、柱塞泵、第二单向阀、压油精滤器、第一比例减压阀、第二电磁换向阀、水增压器、不锈钢高压水阀及燃烧室、连接于所述柱塞泵的变频电机及连接于所述水增压器的水箱；所述水增压器包括两个串联的等径、同心、共用一个活塞杆的液压缸，两个液压缸分别为液压油入口液压缸及出口液压缸，所述液压油入口液压缸连接于所述第二电磁换向阀；所述出口液压缸与所述水箱相连通。本发明成本较低，通用性较好，精度较高，且适用于水下高压环境。
The invention belongs to the related technical field of underwater acoustic emission combustion rate test, and discloses a hydraulic device suitable for underwater acoustic emission combustion rate test system, the hydraulic device includes a booster system, and the booster system includes a booster Assemblies, the pressurization assembly includes an oil tank connected by a pipeline, a plunger pump, a second one-way valve, an oil pressure filter, a first proportional pressure reducing valve, a second electromagnetic reversing valve, a water booster, A stainless steel high-pressure water valve and a combustion chamber, a variable frequency motor connected to the plunger pump, and a water tank connected to the water booster; The two hydraulic cylinders are respectively a hydraulic oil inlet hydraulic cylinder and an outlet hydraulic cylinder, the hydraulic oil inlet hydraulic cylinder is connected to the second electromagnetic reversing valve; the outlet hydraulic cylinder communicates with the water tank. The invention has lower cost, better versatility, higher precision and is suitable for underwater high pressure environment.
Description
技术领域technical field
本发明属于水下声发射燃速测试相关技术领域，更具体地，涉及一种适用于水下声发射燃速测试系统的液压装置。The invention belongs to the technical field related to underwater acoustic emission burning rate testing, and more specifically relates to a hydraulic device suitable for an underwater acoustic emission burning rate testing system.
背景技术Background technique
在固体推进剂研发、试样、批量生产的过程中，需要对燃烧性能作出评价，以衡量新工艺下的推进剂是否符合设计要求。在评价燃烧性能中，推进剂燃速、燃速压强指数、温敏系数是重要参考指标。这些参数中，燃速是最关键的评价指标。无论是压强指数还是温敏系数的求取都最终反映在燃速的测量中，而在燃速的测试过程中一个稳定的水下高压环境的实现是至关重要的。In the process of solid propellant research and development, samples, and mass production, it is necessary to evaluate the combustion performance to measure whether the propellant under the new process meets the design requirements. In the evaluation of combustion performance, propellant burning rate, burning rate pressure index and temperature sensitivity coefficient are important reference indicators. Among these parameters, burning rate is the most critical evaluation index. Whether it is the pressure index or the temperature sensitivity coefficient, it is finally reflected in the measurement of the burning rate, and the realization of a stable underwater high-pressure environment is very important during the burning rate test.
目前，国内用于实现稳定的水下高压环境的方式多为泵压式，然而泵压式采用的是电磁阀控制水的压力，高压水阀存在高压时易泄漏、难密封、控制精度远远不能满足测试要求、研发成本高、通用性差等问题，现有的燃速测试系统已远不能满足实际测试需求，尤其在15MPa以上的中高压压强范围内。相应地，为适应固体推进剂生产研制需要，建立一套满足高压燃速测试的液压系统至关重要。At present, most of the domestic methods used to achieve a stable underwater high-pressure environment are pump pressure types. However, the pump pressure type uses solenoid valves to control the water pressure. High-pressure water valves are prone to leakage and difficult to seal when there is high pressure. Unable to meet the test requirements, high R&D costs, and poor versatility, the existing burning rate test system is far from meeting the actual test requirements, especially in the range of medium and high pressures above 15MPa. Correspondingly, in order to meet the needs of solid propellant production and development, it is very important to establish a hydraulic system that meets the high-pressure burning rate test.
发明内容Contents of the invention
针对现有技术的以上缺陷或改进需求，本发明提供了一种适用于水下声发射燃速测试系统的液压装置，其基于现有水下声发射燃速测试系统的稳压方式的特点，研究及设计了适用于水下声发射燃速测试系统的液压装置，所述液压装置能够为固体推进剂燃烧性能测试提供一个高精度的高压环境，解决了目前固体推进剂燃速性能测试系统无法满足实际测试需求的问题，通过反馈控制可以精确地实现一个稳定的水下高压环境，以更好地实现固体推进剂燃烧性能测试。Aiming at the above defects or improvement needs of the prior art, the present invention provides a hydraulic device suitable for the underwater acoustic emission burning rate test system, which is based on the characteristics of the pressure stabilization mode of the existing underwater acoustic emission burning rate test system, Researched and designed a hydraulic device suitable for the underwater acoustic emission burning rate test system. The hydraulic device can provide a high-precision high-pressure environment for the solid propellant combustion performance test, which solves the problem that the current solid propellant burning rate performance test system cannot To meet the actual test requirements, a stable underwater high-pressure environment can be accurately realized through feedback control, so as to better realize the combustion performance test of solid propellants.
为实现上述目的，本发明提供了一种适用于水下声发射燃速测试系统的液压装置，其包括增压系统及与所述增压系统相连通的稳压系统，其特征在于：In order to achieve the above object, the present invention provides a hydraulic device suitable for an underwater acoustic emission combustion rate test system, which includes a booster system and a voltage stabilization system connected to the booster system, characterized in that:
所述增压系统包括增压组件及连接于所述增压组件的增压系统反馈组件，所述增压系统反馈组件用于检测及反馈所述增压系统的温度、液位及压强；所述增压组件包括一次通过管道相连接的油箱、柱塞泵、第二单向阀、压油精滤器、第一比例减压阀、第二电磁换向阀、水增压器、不锈钢高压水阀及燃烧室、连接于所述柱塞泵的变频电机及连接于所述水增压器的水箱；所述水增压器包括两个串联的等径、同心、共用一个活塞杆的液压缸，两个液压缸分别为液压油入口液压缸及出口液压缸，所述液压油入口液压缸为双作用加载液压缸，其连接于所述第二电磁换向阀；所述出口液压缸通过一个单向阀与所述水箱相连通，其为单作用负载液压缸；所述稳压系统用于稳定所述燃烧室内的压强。The booster system includes a booster component and a booster system feedback component connected to the booster component, the booster system feedback component is used to detect and feed back the temperature, liquid level and pressure of the booster system; The pressurized assembly includes a fuel tank connected by a pipeline, a plunger pump, a second one-way valve, a pressure oil filter, a first proportional pressure reducing valve, a second electromagnetic reversing valve, a water booster, a stainless steel high-pressure water valve and combustion chamber, the variable frequency motor connected to the plunger pump and the water tank connected to the water booster; the water booster includes two hydraulic cylinders connected in series with the same diameter, concentricity, and a common piston rod , the two hydraulic cylinders are respectively a hydraulic oil inlet hydraulic cylinder and an outlet hydraulic cylinder, the hydraulic oil inlet hydraulic cylinder is a double-acting loading hydraulic cylinder, which is connected to the second electromagnetic reversing valve; the outlet hydraulic cylinder passes through a The one-way valve communicates with the water tank, which is a single-acting load hydraulic cylinder; the pressure stabilizing system is used to stabilize the pressure in the combustion chamber.
进一步地，所述液压油入口液压缸通过所述第二电磁换向阀的换向来实现所述活塞杆的推进及回收；所述出口液压缸基于所述活塞杆受力平衡来实现油压转换为水压。Further, the hydraulic oil inlet hydraulic cylinder realizes the advancement and recovery of the piston rod through the reversing of the second electromagnetic reversing valve; the outlet hydraulic cylinder realizes oil pressure conversion based on the force balance of the piston rod for water pressure.
进一步地，所述增压组件还包括溢流阀、第一电磁换向阀、球阀、冷却器、第一单向阀及回油精滤器，所述回油精滤器设置在所述油箱上；所述冷却器与所述球阀串联后连接于所述回油精滤器，所述第一电磁换向阀的一端连接于所述球阀，另一端连接于所述第二单向阀与所述柱塞泵之间的管路上；所述第一单向阀的入口连接于所述球阀与所述第一电磁换向阀之间的管路，其出口连接于所述冷却器与所述回油精滤器之间的管路；所述溢流阀的两端分别连接于所述球阀的入口及所述第二单向阀与所述压油精滤器之间的管路。Further, the pressurization assembly also includes an overflow valve, a first electromagnetic reversing valve, a ball valve, a cooler, a first one-way valve, and an oil return fine filter, and the oil return fine filter is arranged on the oil tank; The cooler and the ball valve are connected in series to the oil return fine filter, one end of the first electromagnetic reversing valve is connected to the ball valve, and the other end is connected to the second one-way valve and the column On the pipeline between the plug pumps; the inlet of the first check valve is connected to the pipeline between the ball valve and the first electromagnetic reversing valve, and its outlet is connected to the cooler and the oil return The pipeline between the fine filter; the two ends of the overflow valve are respectively connected to the inlet of the ball valve and the pipeline between the second one-way valve and the pressure oil fine filter.
进一步地，所述增压系统反馈组件包括液位传感器、温度传感器、第一测压接头及第一耐震轴向压力表，所述液位传感器及所述温度传感器分别间隔设置在所述油箱上；所述第一测压接头的一端连接于所述柱塞泵与所述第二单向阀之间的管路，另一端连接于所述第一耐震轴向压力表。Further, the booster system feedback component includes a liquid level sensor, a temperature sensor, a first pressure measuring joint, and a first shock-resistant axial pressure gauge, and the liquid level sensor and the temperature sensor are separately arranged on the oil tank ; One end of the first pressure measuring joint is connected to the pipeline between the plunger pump and the second one-way valve, and the other end is connected to the first shock-resistant axial pressure gauge.
进一步地，所述稳压系统包括第一电磁阀及连接于所述第一电磁阀的第三蓄能器，所述第一电磁阀连接于所述油箱。Further, the pressure stabilizing system includes a first solenoid valve and a third accumulator connected to the first solenoid valve, and the first solenoid valve is connected to the oil tank.
进一步地，所述稳压系统还包括连接于所述油箱的第二电磁阀、连接于所述第二电磁阀的第三电磁阀及连接于所述第三电磁阀的第一蓄能器。Further, the pressure stabilizing system further includes a second solenoid valve connected to the oil tank, a third solenoid valve connected to the second solenoid valve, and a first accumulator connected to the third solenoid valve.
进一步地，所述稳压系统还包括第四电磁阀及连接于所述第四电磁阀一端的第二蓄能器，所述第四电磁阀的另一端还分别连接于所述第二电磁阀与所述第三电磁阀之间的管路及所述第一比例减压阀与所述第二电磁换向阀之间的管路。Further, the pressure stabilizing system also includes a fourth solenoid valve and a second accumulator connected to one end of the fourth solenoid valve, and the other end of the fourth solenoid valve is also respectively connected to the second solenoid valve The pipeline between the third electromagnetic valve and the pipeline between the first proportional pressure reducing valve and the second electromagnetic reversing valve.
进一步地，所述稳压系统还包括一端连接于所述水增压器与所述不锈钢高压水阀之间的管路的第四蓄能器、连接于所述第四蓄能器另一端的气增压器及连接于所述气增压器的氮气源。Further, the pressure stabilizing system also includes a fourth accumulator with one end connected to the pipeline between the water booster and the stainless steel high-pressure water valve, and a fourth accumulator connected with the other end of the fourth accumulator. A gas booster and a nitrogen source connected to the gas booster.
进一步地，所述稳压系统还包括连接于所述第四蓄能器入口的电控气动球阀、连接于所述电控气动球阀的气控背压阀、连接所述电控气动球阀及所述气控背压阀的电气比例阀及连接所述氮气源及所述电控气动球阀与所述电气比例阀之间的管路的减压表。Further, the pressure stabilizing system also includes an electro-pneumatic ball valve connected to the inlet of the fourth accumulator, an air-controlled back pressure valve connected to the electro-pneumatic ball valve, an electro-pneumatic ball valve connected to the The electric proportional valve of the air control back pressure valve and the decompression meter connecting the nitrogen source and the pipeline between the electric control pneumatic ball valve and the electric proportional valve.
进一步地，所述稳压系统还包括第二比例减压阀及连接所述第二比例减压阀及所述气增压器的第四电磁换向阀，所述第二比例减压阀连接于所述压油精滤器与所述第一比例减压阀之间的管路。Further, the pressure stabilizing system also includes a second proportional pressure reducing valve and a fourth electromagnetic reversing valve connected to the second proportional pressure reducing valve and the gas supercharger, and the second proportional pressure reducing valve is connected to A pipeline between the pressure oil fine filter and the first proportional pressure reducing valve.
总体而言，通过本发明所构思的以上技术方案与现有技术相比，本发明提供的适用于水下声发射燃速测试系统的液压装置主要具有以下有益效果：Generally speaking, compared with the prior art through the above technical solutions conceived by the present invention, the hydraulic device suitable for the underwater acoustic emission combustion rate testing system provided by the present invention mainly has the following beneficial effects:
1.所述液压装置通过柱塞泵来提供高压液压油，通过蓄能器组来实现比例减压阀、减压阀和电磁换向阀入口压力的稳定，通过水增压器来实现对燃烧室的增压，最后通过蓄能器对燃烧室内的压力进行保压，从而实现高精度的稳定水下高压环境；1. The hydraulic device provides high-pressure hydraulic oil through the plunger pump, realizes the stability of the inlet pressure of the proportional pressure reducing valve, the pressure reducing valve and the electromagnetic reversing valve through the accumulator group, and realizes the combustion control through the water supercharger. The pressurization of the chamber, and finally the pressure in the combustion chamber is maintained by the accumulator, so as to achieve a high-precision and stable underwater high-pressure environment;
2.所述液压装置的成本较低，通用性较强，可用于各种型号的固体推进剂进行水下燃速性能测试，并且可用于大多数需要水下高压环境的场合；2. The cost of the hydraulic device is low, and it has strong versatility. It can be used for various types of solid propellants for underwater burning rate performance tests, and can be used for most occasions that require underwater high-pressure environments;
3.采用液压增压的方式可实现对燃烧室的快速增压，同时通过蓄能器对燃烧室内的压强进行保压，实现了高精度的稳定水下高压环境，且效率较高。3. The rapid pressurization of the combustion chamber can be realized by adopting the hydraulic pressure boosting method, and at the same time, the pressure in the combustion chamber is maintained by the accumulator, which realizes a high-precision and stable underwater high-pressure environment with high efficiency.
附图说明Description of drawings
图1是本发明较佳实施方式提供的适用于水下声发射燃速测试系统的液压装置的示意图。Fig. 1 is a schematic diagram of a hydraulic device suitable for an underwater acoustic emission burning rate test system provided by a preferred embodiment of the present invention.
在所有附图中，相同的附图标记用来表示相同的元件或结构，其中：21A-油箱，22A-空滤器，23A-变频电机，24A-柱塞泵，25A-电加热器，26A-放油阀，27A-冷却器，28A-球阀，29A-第一单向阀，21B-压油精滤器，22B-溢流阀，23B-第一电磁换向阀，24B-第二单向阀，25B-第一比例减压阀，26B-减压阀，27B-第二电磁换向阀，28B-水增压器，29B-不锈钢高压水阀，21C-回油精滤器，22C-排水阀，23C-燃烧室，24C-第三电磁换向阀，25C-液位计，26C-水箱，31A-液位传感器，32A-温度传感器，33A-第一测压接头，34A-第二测压接头，35A-第三测压接头，36A-第一耐震轴向压力表，37A-第二耐震轴向压力表，38A-第三耐震轴向压力表，39A-第一压力变送器，31B-第二压力变送器，32B-第三压力变送器，33B-第四压力变送器，34B-第五压力变送器，41-第一电磁阀，42-第二电磁阀，43-第三电磁阀，44-第四电磁阀，45-第一蓄能器，46-第二蓄能器，47-第三蓄能器，51A-第二比例减压阀，52A-第四电磁换向阀，53A-氮气源，54A-气增压器，55A-第四蓄能器，56A-第三单向阀，57A-蓄能器充气工具，58A-电控气动球阀，59A-减压表，51B-电气比例阀，52B-气控背压阀。In all drawings, the same reference numerals are used to represent the same elements or structures, among which: 21A-oil tank, 22A-air filter, 23A-inverter motor, 24A-piston pump, 25A-electric heater, 26A- Oil drain valve, 27A-cooler, 28A-ball valve, 29A-first one-way valve, 21B-pressure oil fine filter, 22B-overflow valve, 23B-first electromagnetic reversing valve, 24B-second one-way valve , 25B-first proportional pressure reducing valve, 26B-pressure reducing valve, 27B-second electromagnetic reversing valve, 28B-water booster, 29B-stainless steel high pressure water valve, 21C-return oil fine filter, 22C-drainage valve , 23C-combustion chamber, 24C-third electromagnetic reversing valve, 25C-liquid level gauge, 26C-water tank, 31A-liquid level sensor, 32A-temperature sensor, 33A-first pressure measuring joint, 34A-second pressure measuring Connector, 35A-the third pressure measuring joint, 36A-the first shockproof axial pressure gauge, 37A-the second shockproof axial pressure gauge, 38A-the third shockproof axial pressure gauge, 39A-the first pressure transmitter, 31B - second pressure transmitter, 32B - third pressure transmitter, 33B - fourth pressure transmitter, 34B - fifth pressure transmitter, 41 - first solenoid valve, 42 - second solenoid valve, 43 -Third solenoid valve, 44-Fourth solenoid valve, 45-First accumulator, 46-Second accumulator, 47-Third accumulator, 51A-Second proportional pressure reducing valve, 52A-Fourth Electromagnetic reversing valve, 53A-nitrogen source, 54A-gas booster, 55A-fourth accumulator, 56A-third one-way valve, 57A-accumulator charging tool, 58A-electrically controlled pneumatic ball valve, 59A- Pressure reducing table, 51B-electric proportional valve, 52B-pneumatic control back pressure valve.
具体实施方式detailed description
为了使本发明的目的、技术方案及优点更加清楚明白，以下结合附图及实施例，对本发明进行进一步详细说明。应当理解，此处所描述的具体实施例仅仅用以解释本发明，并不用于限定本发明。此外，下面所描述的本发明各个实施方式中所涉及到的技术特征只要彼此之间未构成冲突就可以相互组合。In order to make the object, technical solution and advantages of the present invention clearer, the present invention will be further described in detail below in conjunction with the accompanying drawings and embodiments. It should be understood that the specific embodiments described here are only used to explain the present invention, not to limit the present invention. In addition, the technical features involved in the various embodiments of the present invention described below can be combined with each other as long as they do not constitute a conflict with each other.
请参阅图1，本发明较佳实施方式提供的适用于水下声发射燃速测试系统的液压装置，所述液压装置通过柱塞泵来提供高压液压油，通过蓄能器组来实现比例减压阀、减压阀和电磁换向阀入口压力的稳定，通过水增压器来实现对燃烧室的增压，最后通过蓄能器对燃烧室内的压力进行保压，从而实现高精度的稳定水下高压环境。所述液压装置在固体推进剂燃烧性能测试过程中将保持燃烧室内的压力稳定在±0.05MPa浮动范围内，对于测试固体推进剂的燃烧性能参数及后续研究固体推进剂能量释放速度具有重要意义。Please refer to Fig. 1, the hydraulic device suitable for the underwater acoustic emission combustion rate test system provided by the preferred embodiment of the present invention, the hydraulic device provides high-pressure hydraulic oil through the plunger pump, and realizes proportional reduction through the accumulator group. The inlet pressure of the pressure reducing valve, pressure reducing valve and electromagnetic reversing valve is stabilized, the pressure of the combustion chamber is realized through the water booster, and finally the pressure in the combustion chamber is maintained through the accumulator, so as to achieve high precision stability Underwater high pressure environment. The hydraulic device will keep the pressure in the combustion chamber stable within the floating range of ±0.05MPa during the solid propellant combustion performance test, which is of great significance for testing the combustion performance parameters of the solid propellant and subsequent research on the energy release rate of the solid propellant.
所述液压装置包括增压系统和稳压系统，所述稳压系统与所述增压系统相连通。所述增压系统采用液压增压方式，其包括增压组件及与所述增压组件相连通的增压系统反馈组件。The hydraulic device includes a pressure boosting system and a voltage stabilizing system, and the voltage stabilizing system communicates with the boosting system. The pressurization system adopts a hydraulic pressurization method, which includes a pressurization assembly and a pressurization system feedback assembly communicated with the pressurization assembly.
所述增压组件包括油箱21A、空滤器22A、变频电机23A、柱塞泵24A、电加热器25A、放油阀26A、冷却器27A、球阀28A、第一单向阀29A、压油精滤器21B、溢流阀22B、第一电磁换向阀23B、第二单向阀24B、第一比例减压阀25B、减压阀26B、第二电磁换向阀27B、水增压器28B、不锈钢高压水阀29B、回油精滤器21C、排水阀22C、燃烧室23C、第三电磁换向阀24C、液位计25C及水箱26C。The booster assembly includes a fuel tank 21A, an air filter 22A, a variable frequency motor 23A, a plunger pump 24A, an electric heater 25A, an oil drain valve 26A, a cooler 27A, a ball valve 28A, a first one-way valve 29A, and an oil pressure fine filter 21B, overflow valve 22B, first electromagnetic reversing valve 23B, second one-way valve 24B, first proportional pressure reducing valve 25B, pressure reducing valve 26B, second electromagnetic reversing valve 27B, water booster 28B, stainless steel High pressure water valve 29B, oil return fine filter 21C, drain valve 22C, combustion chamber 23C, third electromagnetic reversing valve 24C, liquid level gauge 25C and water tank 26C.
所述油箱21A用于储存液压油，所述放油阀26A设置在所述油箱21A的左侧壁上。所述液位计25C设置在所述油箱21A上，其用于测量所述油箱21A内的液压油的液位。所述空滤器22A、所述柱塞泵24A、所述电加热器25A及所述回油精滤器21C间隔设置在所述油箱21A上，所述变频电机23A连接于所述柱塞泵24A，其用于驱动所述柱塞泵24A转动以供压。本实施方式中，通过变频器控制所述变频电机23A的转速以调节所述柱塞泵24A的输出流量，使得系统流量可调。The oil tank 21A is used to store hydraulic oil, and the oil drain valve 26A is arranged on the left side wall of the oil tank 21A. The liquid level gauge 25C is arranged on the oil tank 21A, and is used to measure the liquid level of the hydraulic oil in the oil tank 21A. The air filter 22A, the plunger pump 24A, the electric heater 25A and the oil return fine filter 21C are arranged at intervals on the fuel tank 21A, the frequency conversion motor 23A is connected to the plunger pump 24A, It is used to drive the plunger pump 24A to rotate to supply pressure. In this embodiment, the output flow of the plunger pump 24A is adjusted by controlling the rotation speed of the variable frequency motor 23A through a frequency converter, so that the system flow can be adjusted.
所述第二单向阀24B的入口及出口分别连接于所述柱塞泵24A的出口及所述压油精滤器21B的入口。所述第一比例减压阀25B连接所述压油精滤器21B的出口及所述第二电磁换向阀27B。本实施方式中，所述第二电磁换向阀27B是三位四通电磁阀。The inlet and outlet of the second one-way valve 24B are respectively connected to the outlet of the plunger pump 24A and the inlet of the pressure oil fine filter 21B. The first proportional decompression valve 25B is connected to the outlet of the pressure oil fine filter 21B and the second electromagnetic reversing valve 27B. In this embodiment, the second electromagnetic reversing valve 27B is a three-position four-way electromagnetic valve.
所述水增压器28B由两个等径、同心、共用一个活塞杆的液压缸串联而成，两个液压缸分别为液压油入口液压缸及出口液压缸，所述液压油入口液压缸为双作用加载液压缸，其连接于所述第二电磁换向阀27B。所述液压油入口液压缸通过所述第二电磁换向阀27B的换向来实现活塞杆的推进及回收。所述出口液压缸通过一个单向阀与所述水箱26C相连通，其为单作用负载液压缸，基于所述活塞杆受力平衡实现油压转换为水压。The water booster 28B is formed by connecting two equal-diameter, concentric hydraulic cylinders sharing one piston rod in series. The two hydraulic cylinders are hydraulic oil inlet hydraulic cylinder and outlet hydraulic cylinder respectively. The hydraulic oil inlet hydraulic cylinder is A double-acting loading hydraulic cylinder is connected to the second electromagnetic reversing valve 27B. The hydraulic oil inlet hydraulic cylinder realizes the advancement and recovery of the piston rod through the reversing of the second electromagnetic reversing valve 27B. The outlet hydraulic cylinder communicates with the water tank 26C through a one-way valve, which is a single-acting load hydraulic cylinder, and converts oil pressure into water pressure based on the force balance of the piston rod.
所述不锈钢高压水阀29B连接所述出口液压缸及所述燃烧室23C，所述排水阀22C设置在所述燃烧室23C上。所述减压阀26B连接所述压油精滤器21B的出口及所述第三电磁换向阀24C，所述第三电磁换向阀24C连接于所述不锈钢高压水阀29B。本实施方式中，所述第三电磁换向阀24C可将其出口处的压力控制在10MPa。The stainless steel high-pressure water valve 29B is connected to the outlet hydraulic cylinder and the combustion chamber 23C, and the drain valve 22C is arranged on the combustion chamber 23C. The pressure reducing valve 26B is connected to the outlet of the pressure oil fine filter 21B and the third electromagnetic reversing valve 24C, and the third electromagnetic reversing valve 24C is connected to the stainless steel high-pressure water valve 29B. In this embodiment, the pressure at the outlet of the third electromagnetic reversing valve 24C can be controlled at 10 MPa.
所述冷却器27A与所述球阀28A串联后连接于所述回油精滤器21C，所述第一电磁换向阀23B的一端连接于所述球阀28A，另一端连接于所述第二单向阀24B与所述柱塞泵24A之间的管路上。所述第一单向阀29A的入口连接于所述球阀28A与所述第一电磁换向阀23B之间的管路，其出口连接于所述冷却器27A与所述回油精滤器21C之间的管路。所述溢流阀22B的两端分别连接于所述球阀28A的入口及所述第二单向阀24B与所述压油精滤器21B之间的管路。The cooler 27A is connected in series with the ball valve 28A to the oil return fine filter 21C, one end of the first electromagnetic reversing valve 23B is connected to the ball valve 28A, and the other end is connected to the second one-way valve. On the pipeline between the valve 24B and the plunger pump 24A. The inlet of the first one-way valve 29A is connected to the pipeline between the ball valve 28A and the first electromagnetic reversing valve 23B, and its outlet is connected between the cooler 27A and the oil return fine filter 21C. pipelines between. Both ends of the overflow valve 22B are respectively connected to the inlet of the ball valve 28A and the pipeline between the second one-way valve 24B and the fine oil pressure filter 21B.
所述增压系统反馈组件包括液位传感器31A、温度传感器32A、第一测压接头33A、第二测压接头34A、第三测压接头35A、第一耐震轴向压力表36A、第二耐震轴向压力表37A、第三耐震轴向压力表38A、第一压力变送器39A、第二压力变送器31B、第三压力变送器32B、第四压力变送器33B及第五压力变送器34B。所述液位传感器31A及所述温度传感器32A分别间隔设置在所述油箱21A上。所述第一测压接头33A的一端连接于所述柱塞泵24A与所述第二单向阀24B之间的管路，另一端连接于所述第一耐震轴向压力表36A。所述第二测压接头34A的一端连接于所述压油精滤器21B与所述第一比例减压阀25B之间的管路，另一端连接于所述第二耐震轴向压力表37A。所述第一压力变送器39A设置在所述第二测压接头34A与所述压油精滤器21B之间的管路上。所述第三测压接头35A的一端连接于所述第一比例减压阀25B与所述第二电磁换向阀27B之间的管路，另一端连接于所述第三耐震轴向压力表38A。所述第二压力变送器31B设置在所述第一比例减压阀25B与所述第三测压接头35A之间的管路上。所述第三压力变送器32B设置在所述不锈钢高压水阀29B与所述出口液压缸之间的管路上，所述第五压力变送器34B设置在所述燃烧室23C与所述不锈钢高压水阀29B之间的管路上。所述第四压力变送器33B设置于所述稳压系统。The booster system feedback assembly includes a liquid level sensor 31A, a temperature sensor 32A, a first pressure measuring joint 33A, a second pressure measuring joint 34A, a third pressure measuring joint 35A, a first shockproof axial pressure gauge 36A, a second shockproof Axial pressure gauge 37A, third shockproof axial pressure gauge 38A, first pressure transmitter 39A, second pressure transmitter 31B, third pressure transmitter 32B, fourth pressure transmitter 33B and fifth pressure transmitter Transmitter 34B. The liquid level sensor 31A and the temperature sensor 32A are separately arranged on the oil tank 21A at intervals. One end of the first pressure measuring joint 33A is connected to the pipeline between the plunger pump 24A and the second one-way valve 24B, and the other end is connected to the first shock-resistant axial pressure gauge 36A. One end of the second pressure measuring joint 34A is connected to the pipeline between the pressure oil fine filter 21B and the first proportional pressure reducing valve 25B, and the other end is connected to the second shock-resistant axial pressure gauge 37A. The first pressure transmitter 39A is arranged on the pipeline between the second pressure measuring joint 34A and the pressure oil fine filter 21B. One end of the third pressure measuring joint 35A is connected to the pipeline between the first proportional pressure reducing valve 25B and the second electromagnetic selector valve 27B, and the other end is connected to the third shock-resistant axial pressure gauge 38A. The second pressure transmitter 31B is arranged on the pipeline between the first proportional pressure reducing valve 25B and the third pressure measuring joint 35A. The third pressure transmitter 32B is set on the pipeline between the stainless steel high pressure water valve 29B and the outlet hydraulic cylinder, and the fifth pressure transmitter 34B is set between the combustion chamber 23C and the stainless steel On the pipeline between the high pressure water valve 29B. The fourth pressure transmitter 33B is arranged in the pressure stabilizing system.
所述液压装置的液压系统的压力由所述变频电机23A驱动所述柱塞泵24A提供，所述燃烧室23C内的压力由所述水增压器28B提供。所述液压油入口油缸的入口压力通过所述第一比例减压阀25B进行调节，压强控制精度在0.5％以上。所述水增压器28B的理论增压比为1，通过控制器入口压力即可实现精确控制其输出压力。所述不锈钢高压水阀29B控制增压回路的通断，所述排水阀22C用于更换所述燃烧室23C内的水。通过所述第五压力变送器34B实时反馈所述燃烧室23C内的压力，并根据其压力来对所述第一比例减压阀25B进行微调以保证所述燃烧室23C内的压力稳定可靠。所述溢流阀22B是系统油压强在不正常增高且超过30MPa时可用实现安全溢流以保证系统安全。通过所述第一电磁换向阀23B的开闭可使系统油压保持在一个比较合理的范围内。所述压油精滤器21B及所述回油精滤器21C都是对液压油进行过滤以保证液压油的干净。此外，当系统持续保持高压运行时，系统油温可能会升高，通过所述冷却器27A可以将系统油温降低到液压油的工作范围内。所述减压阀26B是保持其出口压强为10MPa来控制所述第三电磁换向阀24C的通断进而控制所述不锈钢高压水阀29B的开断，所述回油精滤器21C用于把系统内产生或者侵入的污染物在返回所述油箱21A前捕获到以确保流回所述油箱21A的液压油是干净的、在试验完成后打开所述排水阀22C以将所述燃烧室23C中的液体排出。所述液位计25C用于实时监测所述油箱21A中液压油的液位，而所述水箱26C是为所述水增压器28B提供水源。The pressure of the hydraulic system of the hydraulic device is provided by the variable frequency motor 23A driving the plunger pump 24A, and the pressure in the combustion chamber 23C is provided by the water booster 28B. The inlet pressure of the hydraulic oil inlet cylinder is regulated by the first proportional pressure reducing valve 25B, and the pressure control precision is above 0.5%. The theoretical boost ratio of the water booster 28B is 1, and the output pressure can be precisely controlled by controlling the inlet pressure. The stainless steel high-pressure water valve 29B controls the on-off of the booster circuit, and the drain valve 22C is used to replace the water in the combustion chamber 23C. The pressure in the combustion chamber 23C is fed back in real time through the fifth pressure transmitter 34B, and the first proportional pressure reducing valve 25B is fine-tuned according to the pressure to ensure that the pressure in the combustion chamber 23C is stable and reliable . The overflow valve 22B can be used to realize safe overflow when the system oil pressure increases abnormally and exceeds 30MPa to ensure system safety. The system oil pressure can be maintained within a reasonable range through the opening and closing of the first electromagnetic reversing valve 23B. Both the pressure oil fine filter 21B and the oil return fine filter 21C filter the hydraulic oil to ensure that the hydraulic oil is clean. In addition, when the system continues to operate at high pressure, the temperature of the system oil may rise, and the cooler 27A can reduce the temperature of the system oil to within the working range of the hydraulic oil. The decompression valve 26B keeps its outlet pressure at 10MPa to control the on-off of the third electromagnetic reversing valve 24C and then controls the on-off of the stainless steel high-pressure water valve 29B. The oil return fine filter 21C is used to The pollutants generated or intruded in the system are captured before returning to the oil tank 21A to ensure that the hydraulic oil flowing back into the oil tank 21A is clean. After the test is completed, the drain valve 22C is opened to discharge liquid discharge. The liquid level gauge 25C is used to monitor the liquid level of the hydraulic oil in the oil tank 21A in real time, and the water tank 26C provides water source for the water booster 28B.
所述稳压系统包括入口稳压组件及连接于所述入口稳压组件的出口稳压组件。所述入口稳压组件包括第一电磁阀41、第二电磁阀42、第三电磁阀43、第四电磁阀44、第一蓄能器45、第二蓄能器46及第三蓄能器47。所述第一电磁阀41连接于所述油箱21A，所述第三蓄能器47连接于所述第一电磁阀41。本实施方式中，所述第三蓄能器47的容积为6.3L，充气压强为8MPa。所述第一电磁阀41与所述第三蓄能器47之间的管路及所述第二测压接头34A与所述第一压力变送器39A之间的管路相连通。所述第二电磁阀42的一端连接于所述第一电磁阀41与所述油箱21A之间的管路，另一端连接于所述第三电磁阀43。所述第一蓄能器45连接于所述第三电磁阀43。本实施方式中，所述第一蓄能器45的容积为2.5L，充气压强为2.5MPa。所述第四电磁阀44的一端连接所述第三电磁阀43与所述第二电磁阀42之间的管路及所述第三测压接头35A与所述第二压力变送器31B之间的管路。The voltage stabilizing system includes an inlet stabilizing component and an outlet stabilizing component connected to the inlet stabilizing component. The inlet pressure stabilizing assembly includes a first solenoid valve 41, a second solenoid valve 42, a third solenoid valve 43, a fourth solenoid valve 44, a first accumulator 45, a second accumulator 46 and a third accumulator 47. The first solenoid valve 41 is connected to the oil tank 21A, and the third accumulator 47 is connected to the first solenoid valve 41 . In this embodiment, the volume of the third accumulator 47 is 6.3L, and the charging pressure is 8MPa. The pipeline between the first solenoid valve 41 and the third accumulator 47 and the pipeline between the second pressure measuring joint 34A and the first pressure transmitter 39A are connected. One end of the second solenoid valve 42 is connected to the pipeline between the first solenoid valve 41 and the oil tank 21A, and the other end is connected to the third solenoid valve 43 . The first accumulator 45 is connected to the third solenoid valve 43 . In this embodiment, the volume of the first accumulator 45 is 2.5L, and the charging pressure is 2.5MPa. One end of the fourth solenoid valve 44 is connected to the pipeline between the third solenoid valve 43 and the second solenoid valve 42 and between the third pressure measuring joint 35A and the second pressure transmitter 31B. pipelines between.
所述出口稳压组件包括第二比例减压阀51A、第四电磁换向阀52A、氮气源53A、气增压器54A、第四蓄能器55A、第三单向阀56A、蓄能器充气工具57A、电控气动球阀58A、减压表59A、电气比例阀51B及气控背压阀52B。所述第二比例减压阀51A的一端连接于所述减压阀26B与所述压油精滤器21B之间的管路，另一端连接于所述第四电磁换向阀52A。所述第四电磁换向阀52A连接于所述气增压器54A的中部。四个所述第三单向阀56A两两分别连接于所述气增压器54A的两端，且其中两个所述第三单向阀56A的出口分别连接于所述气增压器54A的两端，出口均连接于所述氮气源53A；另外两个所述第三单向阀56A的入口分别连接于所述气增压器54A的两端，出口相连接通后连接于所述蓄能器充气工具57A。所述蓄能器充气工具57A连接于所述第四蓄能器55A的入口，所述第四蓄能器55A的出口连接于所述水增压器28B与所述第三压力变送器32B之间的管路。本实施方式中，所述第四蓄能器55A的容积为10L。所述电控气动球阀58A连接于所述第四压力变送器33B与所述蓄能器充气工具57A之间的管路，所述电气比例阀51B连接所述电控气动球阀58A及所述气控背压阀52B。所述气控背压阀52B连接于所述电控气动球阀58A，气体通过所述气控背压阀52B排出。所述减压表59A的一端连接于所述电控气动球阀58A与所述电气比例阀51B之间的管路，另一端连接于所述氮气源53A。本实施方式中，所述减压表59A可将其出口氮气压强控制到0.8MPa。The outlet pressure stabilization assembly includes a second proportional pressure reducing valve 51A, a fourth electromagnetic reversing valve 52A, a nitrogen source 53A, a gas booster 54A, a fourth accumulator 55A, a third one-way valve 56A, an accumulator Inflatable tool 57A, electric control pneumatic ball valve 58A, decompression gauge 59A, electric proportional valve 51B and air control back pressure valve 52B. One end of the second proportional pressure reducing valve 51A is connected to the pipeline between the pressure reducing valve 26B and the fine pressure oil filter 21B, and the other end is connected to the fourth electromagnetic reversing valve 52A. The fourth electromagnetic reversing valve 52A is connected to the middle of the gas supercharger 54A. Two of the four third one-way valves 56A are respectively connected to both ends of the gas supercharger 54A, and the outlets of two of the third one-way valves 56A are respectively connected to the gas supercharger 54A The two ends of the outlet are connected to the nitrogen source 53A; the inlets of the other two third check valves 56A are respectively connected to the two ends of the gas booster 54A, and the outlets are connected and connected to the nitrogen source. Accumulator inflation tool 57A. The accumulator inflation tool 57A is connected to the inlet of the fourth accumulator 55A, and the outlet of the fourth accumulator 55A is connected to the water booster 28B and the third pressure transmitter 32B pipeline between. In this embodiment, the volume of the fourth accumulator 55A is 10L. The electric control pneumatic ball valve 58A is connected to the pipeline between the fourth pressure transmitter 33B and the accumulator charging tool 57A, and the electric proportional valve 51B is connected to the electric control pneumatic ball valve 58A and the Air-operated back pressure valve 52B. The air control back pressure valve 52B is connected to the electric control pneumatic ball valve 58A, and the gas is discharged through the air control back pressure valve 52B. One end of the decompression gauge 59A is connected to the pipeline between the electro-pneumatic ball valve 58A and the electric proportional valve 51B, and the other end is connected to the nitrogen source 53A. In this embodiment, the decompression gauge 59A can control the outlet nitrogen pressure to 0.8 MPa.
所述入口稳压组件主要作用是稳定所述第一比例减压阀25B、所述减压阀26B、所述第二比例减压阀51A及所述第二电磁换向阀27B的入口压力。开始工作的时候，关闭所述第一电磁阀41及所述第二电磁阀42；当所述燃烧室23C需要的压强低于8MPa的时候打开所述第三电磁阀43，关闭所述第四电磁阀44；当所述燃烧室23C需要的压强高于8MPa的时候打开所述第四电磁阀44，关闭所述第三电磁阀43。The main function of the inlet pressure stabilizing component is to stabilize the inlet pressure of the first proportional pressure reducing valve 25B, the pressure reducing valve 26B, the second proportional pressure reducing valve 51A and the second electromagnetic reversing valve 27B. When starting to work, close the first electromagnetic valve 41 and the second electromagnetic valve 42; when the pressure required by the combustion chamber 23C is lower than 8MPa, open the third electromagnetic valve 43 and close the fourth electromagnetic valve. Solenoid valve 44: when the pressure required by the combustion chamber 23C is higher than 8 MPa, the fourth solenoid valve 44 is opened, and the third solenoid valve 43 is closed.
所述出口稳压组件主要作用是稳定所述燃烧室23C内的压力。根据所述燃烧室23C所需压强，设定所述第二比例减压阀51A的压强，并打开所述氮气源53A及所述第四电磁换向阀52A，通过所述气增压器54A向所述第四蓄能器55A中充入氮气。当所述第四蓄能器55A内的压强达到要求后，关闭所述第四电磁换向阀52A。在所述燃烧室23C的增压过程中，当所述燃烧室23C内压强超过所述第四蓄能器55A中的压强时，所述第四蓄能器55A开始工作以保持所述燃烧室23C内压力稳定增加，直到达到所需压力。在燃烧室23C内的压强达到所需压强后，所述第四蓄能器55A能使所述燃烧室23C内的压强保持。当所述第四蓄能器55A内的压强高于所述燃烧室23C所需的压强时，需要对所述第四蓄能器55A进行泄压处理，具体地，打开所述电控气动球阀58A，并给所述电气比例阀51B一个设定压强，通过所述电气比例阀51B来控制所述气控背压阀52B的开闭，从而达到对所述第四蓄能器55A进行泄压的目的，泄压完成后关闭所述电控气动球阀58A。The main function of the outlet pressure stabilizing component is to stabilize the pressure in the combustion chamber 23C. According to the required pressure of the combustion chamber 23C, the pressure of the second proportional pressure reducing valve 51A is set, and the nitrogen source 53A and the fourth electromagnetic reversing valve 52A are opened to pass through the gas booster 54A. Charge nitrogen gas into the fourth accumulator 55A. When the pressure in the fourth accumulator 55A reaches the requirement, the fourth electromagnetic reversing valve 52A is closed. During the pressurization process of the combustion chamber 23C, when the pressure in the combustion chamber 23C exceeds the pressure in the fourth accumulator 55A, the fourth accumulator 55A starts to work to keep the combustion chamber The pressure within 23C increases steadily until the desired pressure is reached. After the pressure in the combustion chamber 23C reaches the desired pressure, the fourth accumulator 55A can maintain the pressure in the combustion chamber 23C. When the pressure in the fourth accumulator 55A is higher than the pressure required by the combustion chamber 23C, it is necessary to perform pressure relief on the fourth accumulator 55A, specifically, open the electro-pneumatic ball valve 58A, and give the electrical proportional valve 51B a set pressure, and control the opening and closing of the air-controlled back pressure valve 52B through the electrical proportional valve 51B, so as to release the pressure of the fourth accumulator 55A The purpose is to close the electro-pneumatic ball valve 58A after pressure relief is completed.
本发明提供的适用于水下声发射燃速测试系统的液压装置，所述液压装置通过柱塞泵来提供高压液压油，通过蓄能器组来实现比例减压阀、减压阀和电磁换向阀入口压强的稳定，通过水增压器来实现对燃烧室的增压，最后通过蓄能器对燃烧室内的压力进行保压，从而实现高精度的稳定水下高压环境。所述液压装置在固体推进剂燃烧性能测试过程中将保持燃烧室内的压强稳定在±0.05MPa浮动范围内，对于测试固体推进剂的燃烧性能参数及后续研究固体推进剂能量释放速度具有重要意义。The hydraulic device provided by the present invention is applicable to the underwater acoustic emission combustion rate testing system. To stabilize the pressure at the inlet of the valve, the water booster is used to pressurize the combustion chamber, and finally the accumulator is used to maintain the pressure in the combustion chamber, thereby achieving a high-precision and stable underwater high-pressure environment. The hydraulic device will keep the pressure in the combustion chamber stable within the floating range of ±0.05MPa during the solid propellant combustion performance test, which is of great significance for testing the combustion performance parameters of the solid propellant and subsequent research on the energy release rate of the solid propellant.
本领域的技术人员容易理解，以上所述仅为本发明的较佳实施例而已，并不用以限制本发明，凡在本发明的精神和原则之内所作的任何修改、等同替换和改进等，均应包含在本发明的保护范围之内。It is easy for those skilled in the art to understand that the above descriptions are only preferred embodiments of the present invention, and are not intended to limit the present invention. Any modifications, equivalent replacements and improvements made within the spirit and principles of the present invention, All should be included within the protection scope of the present invention.
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