WO2022134314A1 - 一种机械自力式恒流量控制组合装置 - Google Patents

一种机械自力式恒流量控制组合装置 Download PDF

Info

Publication number
WO2022134314A1
WO2022134314A1 PCT/CN2021/079195 CN2021079195W WO2022134314A1 WO 2022134314 A1 WO2022134314 A1 WO 2022134314A1 CN 2021079195 W CN2021079195 W CN 2021079195W WO 2022134314 A1 WO2022134314 A1 WO 2022134314A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve core
fine adjustment
fine
adjustment valve
coarse
Prior art date
Application number
PCT/CN2021/079195
Other languages
English (en)
French (fr)
Inventor
宋印东
王洋
郭斌
张钰妮
马旭
徐毅煜
徐静雅
Original Assignee
江苏科技大学
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 江苏科技大学 filed Critical 江苏科技大学
Publication of WO2022134314A1 publication Critical patent/WO2022134314A1/zh

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K17/00—Safety valves; Equalising valves, e.g. pressure relief valves
    • F16K17/20—Excess-flow valves
    • F16K17/22—Excess-flow valves actuated by the difference of pressure between two places in the flow line
    • F16K17/24—Excess-flow valves actuated by the difference of pressure between two places in the flow line acting directly on the cutting-off member
    • F16K17/28—Excess-flow valves actuated by the difference of pressure between two places in the flow line acting directly on the cutting-off member operating in one direction only
    • F16K17/30—Excess-flow valves actuated by the difference of pressure between two places in the flow line acting directly on the cutting-off member operating in one direction only spring-loaded
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K47/00—Means in valves for absorbing fluid energy
    • F16K47/02—Means in valves for absorbing fluid energy for preventing water-hammer or noise
    • F16K47/023—Means in valves for absorbing fluid energy for preventing water-hammer or noise for preventing water-hammer, e.g. damping of the valve movement

Definitions

  • the invention relates to the technical field of self-operated flow control, in particular to a mechanical self-operated constant flow control combined device.
  • the mechanical self-operated constant flow control device belongs to a type of constant flow control valve, which is specially used in the fluid pipe network system that needs to control the flow.
  • the problem to be solved by the present invention is that a mechanical self-operated constant flow control combined device is required to solve the problem of uneven flow transmission and distribution due to the influence of fluid transport pressure changes on the flow during pipeline transportation.
  • a mechanical self-operated constant flow control combined device which includes: a coarse adjustment unit and a fine adjustment unit, the coarse adjustment unit includes a coarse adjustment pressurized chamber, installed in the coarse adjustment unit.
  • the fine adjustment unit is connected with the coarse adjustment unit, including the coarse adjustment pressure chamber A fine-tuned pressurized chamber connected as a whole, a support installed in the fine-tuned pressurized chamber, a pressure equalizing pipe, a second fairing plate and a second elastic piece connected to the support, and a second elastic piece connected to the support Connected fine adjustment spool.
  • one end of the coarse adjustment pressurizing chamber is provided with an inlet, and the other end is connected to the fine adjustment pressurizing chamber, and the fluid is increased by the coarse adjustment.
  • the part of the pressure chamber entering the fine adjustment pressure chamber is the secondary inlet; the diameter of the coarse adjustment pressure chamber is larger than the diameter of the secondary inlet, and the diameter of the secondary inlet is larger than the diameter of the inlet.
  • the first rectifier plate is fixedly installed in the middle of the rough adjustment booster chamber, and the first rectifier plate is provided with several The first flow hole;
  • the coarse adjustment spool is in the shape of a truncated cone, which is installed at the secondary inlet.
  • the larger end of the coarse adjustment spool is located in the coarse adjustment booster chamber, and the other end is located in the fine adjustment booster.
  • the pressure chamber is connected with the first elastic member.
  • the support is a cascade type and is installed at one end of the fine-tuned pressurized chamber close to the secondary inlet, and the support faces the coarse
  • a second rectifying plate is fixedly connected on one side of the pressure regulating chamber, a plurality of second flow holes are arranged on the second rectifying plate, and the second rectifying plate is connected with the first elastic member.
  • a pressure equalizing pipe is installed in the middle of the other side of the support, and the equalizing pressure pipe extends from the side wall of the fine adjustment pressurizing chamber out and communicate with the coarse plenum.
  • the fine adjustment valve includes a fine adjustment valve core, a fine adjustment valve core retaining ring, the fine adjustment valve core and the support
  • a plurality of second elastic members are evenly distributed and connected therebetween.
  • the fine adjustment valve core retaining ring is fixed and sealed with the fine adjustment pressurized inner wall, and the fine adjustment valve core sleeve It is connected in the retaining ring of the fine adjustment valve core, and there are several positioning blocks evenly distributed on the side surfaces of both ends of the fine adjustment valve core, and the fine adjustment valve core can move along the axial direction within a certain range.
  • the fine adjustment valve core is provided with a third flow hole in the middle along the axial direction
  • the fine adjustment valve core side wall is also provided with several Flow groove, the flow groove is evenly distributed on the circumference, and the height of the flow groove is different, showing a uniform gradient change, the upper and lower diameters of the fine adjustment valve core are the same, and the fine adjustment valve core side wall except for the flow
  • the other parts of the groove and the fine adjustment valve core retaining ring are in a sealed state.
  • the sensitivity of the second elastic member is higher than that of the first elastic member, and the coarse adjustment valve core and the support are connected by a The first guide rod is connected, the fine adjustment valve core and the support are connected by a plurality of second guide rods, the first elastic member is sleeved on the first guide rod, and the second elastic member is sleeved on the first guide rod. on the second guide rod.
  • one end of the fine adjustment pressurized chamber is connected to the coarse adjustment pressurized chamber, and the other end is an outlet, and the diameter of the outlet is the same as that of the coarse adjustment pressurized chamber.
  • the diameter of the inlet of one end of the coarse adjustment booster chamber is the same.
  • the present invention controls the fluid flow area with the internal mechanical movement of the pressure change device, realizes a self-operated constant flow control combined device with a relatively constant flow rate, and effectively maintains the accurate and stable flow rate inside the pipeline. It is stable and is not easily affected by uneven distribution; the present invention can be applied to a wide range of pressure fluctuations, has high adaptability to the working conditions that require constant fluid flow under large pressure fluctuation ranges, and achieves high precision
  • the flow rate is constant; after the fluid is adjusted by the traditional constant flow device, the error range of the flow fluctuation is about 5%-8%.
  • the error range of the flow fluctuation after the fluid passes through the device of the present invention is estimated to be between 3% and 5%, and the constant flow control effect of the device will be better than that of the traditional constant flow device; after the fluid flows through the device, the flow fluctuates Compared with the traditional constant flow equipment, it can ensure that the flow of the equipment it serves is stable in the set range, and can effectively reduce the repeated impact on the equipment caused by the fluctuation of the fluid flow, and improve the service life of each part of the system. economy.
  • Figure 1 is a perspective view of the internal structure of a mechanical self-operated constant flow control combination device.
  • FIG. 2 is a cross-section and a fluid flow diagram of a mechanical self-operated constant flow control combination device.
  • FIG. 3 is a perspective view of the internal structure of the mechanical self-operated constant flow control combination device from another perspective.
  • Figure 4 is a schematic diagram of the internal fluid flow area of the mechanical self-operated constant flow control combination device
  • Figure 5 is a diagram showing the connection between the coarse adjustment valve core, the fine adjustment valve core and the spring support inside the mechanical self-operated constant flow control combination device.
  • references herein to "one embodiment” or “an embodiment” refers to a particular feature, structure, or characteristic that may be included in at least one implementation of the present invention.
  • the appearances of "in one embodiment” in various places in this specification are not all referring to the same embodiment, nor are they separate or selectively mutually exclusive from other embodiments.
  • FIGS. 1 to 5 it is the first embodiment of the present invention, which provides a mechanical self-operated constant flow control combined device, which has a higher performance for the working conditions requiring constant fluid flow under a large pressure fluctuation range. Adaptability, can achieve constant flow with high precision.
  • the mechanical self-operated constant flow control combination device includes a coarse adjustment unit 100 that can initially control and adjust the incoming fluid flow, is connected to the coarse adjustment unit 100 as a whole, and can control the fluid flow more precisely so that the flow can reach a stable precision.
  • Tuning unit 200 tuning unit 200.
  • the coarse adjustment unit 100 includes a coarse adjustment pumping chamber 101 , a first rectifying plate 102 installed inside the coarse adjustment pumping chamber 101 , a coarse adjustment valve core 103 , and a first elastic member 104 connected with the coarse adjustment valve core 103 .
  • the first elastic member 104 is a compression spring, which is selected according to the possible change value of the fluid flow in the pipeline.
  • the first elastic member 104 still has a certain amount of compression when the fluid flow is stable, and the pre-compression amount is determined by the pressure The difference range and spring stroke are determined.
  • a certain amount of pre-compression can keep the coarse adjustment spool 103 in a normally open state, preventing the device from failing when the coarse adjustment spool 103 completely fits with the inner wall of the pipeline when the fluid pressure is high.
  • a relatively low-sensitivity spring can be selected in the coarse adjustment device.
  • one end of the coarse adjustment pressurizing chamber 101 is provided with an inlet 101a, and the other end is connected to the fine adjusting pressurizing chamber 201.
  • the part where the fluid enters the fine adjusting pressurizing chamber 201 from the coarse adjusting pressurizing chamber 101 is the secondary inlet 101b;
  • the diameter of the pressurizing chamber 101 is larger than the diameter of the secondary inlet 101b, and the diameter of the secondary inlet 101b is larger than the diameter of the inlet 101a.
  • the first rectifier plate 102 is fixedly installed in the middle of the coarse adjustment pressurizing chamber 101, and the first rectifier plate 102 is provided with a plurality of first flow holes 102a;
  • the larger end of the round surface of the coarse adjustment valve core 103 is located in the coarse adjustment pumping chamber 101 , and the other end is located in the fine adjustment pumping chamber 201 and is connected to the first elastic member 104 .
  • the working principle of the coarse adjustment unit 100 is as follows: when the fluid enters the coarse adjustment pressurized chamber 101 from the inlet 101a, the first rectifier plate 102 can make the fluid evenly distributed in the flow passage of the coarse adjustment pressurized chamber; The change in the size of the 101 caliber makes the fluid flow diameter suddenly expand, converting the kinetic energy of the fluid into pressure energy. When the fluid pressure increases, the flow velocity of the fluid between the coarse adjustment valve core 103 and the valve seat increases, and the flow rate increases.
  • the spool 103 moves in the flow direction under the action of the fluid pressure, the fluid flow cross-sectional area between the coarse adjustment spool 103 and the valve seat decreases, and the flow rate decreases until the fluid pressure acting on the coarse adjustment spool 103 is equal to the first elasticity
  • the pre-compression force of the component 104, the coarse adjustment valve core 103 stops moving, and the flow rate is stable; similarly, when the fluid pressure decreases, the flow velocity between the coarse adjustment valve core 103 and the valve seat decreases, the flow rate decreases, and the fluid acts on the coarse adjustment valve core 103.
  • the pressure on the adjustment valve core 103 is less than the compressive force of the first elastic member 104, the coarse adjustment valve core 103 moves in the opposite direction of the flow under the action of the first elastic element 104, and the fluid between the coarse adjustment valve core 103 and the valve seat circulates As the cross-sectional area increases, the flow rate increases until the fluid pressure acting on the coarse adjustment spool 103 is equal to the compressive force of the first elastic member 104 , the coarse adjustment spool 103 stops moving and the flow is stable.
  • the above-mentioned coarse adjustment unit 100 ensures that the flow rate is initially constant by adjusting the reduction or increase of the flow area between the coarse adjustment valve core 103 and the valve seat when the fluid pressure increases or decreases.
  • the result of the flow control must have a certain adjustment error. There is a certain deviation between the stable flow value and the expected value. Therefore, the flow rate is further controlled by the fine adjustment unit 200 to reduce the deviation.
  • the fine adjustment unit 200 includes a fine adjustment pumping chamber 201 integrally connected with the coarse adjustment pumping chamber 101 , a support 202 installed in the fine adjustment pumping chamber 201 , a pressure equalizing pipe 203 connected to the support 202 , the first Two straightening plates 204 , a second elastic member 205 , and a fine adjustment valve 206 connected with the second elastic member 205 .
  • the support 202 is of a cascade type and is installed at one end of the fine-tuned booster chamber 201 close to the secondary inlet 101b, and a second rectifier plate 204 is fixedly connected to the side of the support 202 facing the coarse-tuned booster chamber 101 , A plurality of second flow holes 204 a are provided on the second rectifying plate 204 , and the second rectifying plate 204 is connected to the first elastic member 104 .
  • a pressure equalizing pipe 203 is installed in the middle of the other side of the support 202 , and the equalizing pressure pipe 203 extends from the side wall of the fine adjustment pressurizing chamber 201 and communicates with the rough adjusting pressurizing chamber 101 .
  • the support 202 is connected to the coarse adjustment pressurizing chamber 101 through the equalizing pressure pipe 203, so that the pressure transmitted by the coarse adjustment valve core 103 to the support 202 through the spring and the pressure in the coarse adjustment pressurizing chamber 101 are balanced and offset each other, and the pressure received by the device is reduced. Flow shock to increase device life.
  • the fine adjustment valve 206 includes a fine adjustment valve core 206a and a fine adjustment valve core retaining ring 206b, and a plurality of second elastic members 205 are evenly distributed and connected between the fine adjustment valve core 206a and the support 202 .
  • the fine adjustment valve core retaining ring 206b is fixed and sealed with the inner wall of the fine adjustment pressurizing chamber 201.
  • the fine adjustment valve core 206a is sleeved in the fine adjustment valve core retaining ring 206b. By positioning the stopper 206a-1, the fine adjustment valve core 206a can move in the axial direction within a certain range.
  • the fine adjustment valve core 206a is provided with a third flow hole 206a-2 in the middle along the axial direction, and the fine adjustment valve core 206a is also provided with a plurality of flow grooves 206a-3 on the side wall.
  • the heights of -3 are different and show a uniform gradient.
  • the upper and lower diameters of the fine adjustment spool 206a are the same, and the fine adjustment spool 206a has a side wall between other parts except the flow groove 206a-3 and the fine adjustment spool stop ring 206b. in a sealed state.
  • the second elastic member 205 adopts a tension spring with high sensitivity, which ensures the precise displacement of the fine adjustment valve core 206a in the axial direction corresponding to the pressure change while ensuring the stability of the fine adjustment valve core 206a, and the positioning block 206a- 1 is arranged at both ends of the fine adjustment spool 206a to ensure that the fine adjustment spool 206a moves within a predetermined range without excessive elongation and loss of spring characteristics; the third flow hole 206a-2 in the middle of the fine adjustment spool 206a allows part of the fluid It can flow through to prevent the fluid from completely flowing out of the flow groove 206a-3 on the side, which affects the flow accuracy of the actual fluid.
  • the size of the hole determines the force area of the finely adjusted valve core, and it should not be too large, and the size of the hole It has a certain relationship with the selection of the fine adjustment spring, which can be determined according to the actual situation.
  • the fine adjustment valve core retaining ring 206b is fixedly connected with the wall of the fluid flow pipe, and it is required to seal between the fine adjustment valve core retaining ring 206a-1 and the pipe wall, and no fluid is allowed from between the retaining ring and the pipe wall. Flow through, while ensuring the relative slip between the fine adjustment valve core 206a and the fine adjustment valve core retaining ring 206b, the sealing performance between the fine adjustment valve core retaining ring 206b and the fine adjustment valve core 206a is required to be good.
  • the fine adjustment valve core retaining ring 206b is at the front end of the fine adjustment valve core 206a, it is required that the fluid can only flow through the third flow hole 206a-2.
  • the quantity, size and shape of the flow grooves 206a-3 on the side of the fine adjustment valve core 206a can be improved according to actual needs.
  • the working principle of the fine adjustment unit 200 is as follows: when the fluid flows into the fine adjustment unit 200 , the second baffle plate 204 can make the fluid evenly distributed in the flow grooves 206 a - 3 of the fine adjustment pressurizing chamber 201 . When the fluid pressure increases, the flow velocity of the fluid in the flow groove 206a-3 increases, and the flow rate increases.
  • the pressure of the fluid acting on the fine adjustment valve core 206a is greater than the initial tension of the second elastic member 205, and the fine adjustment valve core 206a is in the
  • the fluid pressure moves in the direction of flow, the fine adjustment valve core retaining ring 206b blocks part of the flow groove 206a-3, the fluid flow cross-sectional area decreases, and the flow rate decreases until the fluid pressure acting on the fine adjustment valve core 206a is equal to the second elasticity
  • the fine adjustment valve core 206a stops moving, and the flow rate is stable; similarly, when the fluid pressure decreases, the flow velocity of the fluid in the flow groove 206a-3 decreases, the flow rate decreases, and the fluid acts on the fine adjustment valve at the same time.
  • the pressure on the core 206a is less than the pulling force of the second elastic member 205, the fine adjustment valve core 206a moves in the opposite direction of flow under the action of the second elastic member 205, the fine adjustment valve core retaining ring 206b releases part of the flow groove 206a-3, and the flow
  • the flow cross-sectional area of the fluid in the groove 206a-3 increases, and the flow rate increases until the fluid pressure acting on the fine adjustment spool 206a is equal to the pulling force of the second elastic member 205, the fine adjustment spool 206a stops moving and the flow is stable.
  • the above-mentioned fine adjustment unit 200 can change the number of the flow grooves 206a-3 through which the fluid can flow and the same by adjusting the relative position between the fine adjustment valve core retaining ring 206b and the fine adjustment valve core 206a when the fluid pressure increases or decreases.
  • the flow area makes the fine adjustment valve core 206a flow area relatively finely changed to ensure accurate and constant flow.
  • the sensitivity of the second elastic member 205 is higher than that of the first elastic member 104, the coarse adjustment valve core 103 and the support 202 are connected by a first guide rod D-1, and the fine adjustment valve core 206a and the support 202 are connected by a first guide rod D-1.
  • Several second guide rods D-2 are connected, the first elastic member 104 is sleeved on the first guide rod D-1, and the second elastic member 205 is sleeved on the second guide rod D-2.
  • the purpose of arranging the first guide rod D-1 and the second guide rod D-2 is to prevent the coarse adjustment valve core 103 and the fine adjustment valve core 206a from being displaced in the axial direction under the action of pressure. Referring to FIG.
  • the coarse adjustment valve core 103 and the fine adjustment valve core 206a are both provided with round holes for installing the guide rods to prevent When the valve core comes out, the actual length of the first guide rod D-1 and the second guide rod D-2 can be improved according to factors such as the expansion and contraction of the spring, or the first guide rod D-1 and the second guide rod D- A limit block is installed at the end of the Fixed connection. It should be noted that the solutions described in the examples and the drawings are only exemplary, and the actual implementation is not limited to these types.
  • the first rectifying plate 102 and the second rectifying plate 204 are both solid in the middle and holes in the edges.
  • this opening method mainly considers the fluid flow characteristics in the pipe, the fluid flow speed in the middle part is fast, and the solid part in the middle can effectively block the incoming flow, so as to distribute evenly, and at the same time reduce the impact of the fluid flow on the coarse adjustment spool 103.
  • this opening method also considers the flow characteristics, and the solid center can ensure that the flow of the fluid in the fine adjustment pressurizing chamber 201 is dispersed to the edge, so as to prevent the incoming flow from being too fast, from the fine adjustment valve core 206a The middle hole quickly flows through.
  • the diameter of the outlet 201a at one end of the fine adjustment pumping chamber 201 is the same as the diameter of the inlet 101a at one end of the coarse adjustment pumping chamber 101 .
  • the invention can be applied to a wide range of pressure fluctuations, has high adaptability to working conditions with large pressure fluctuations, and achieves constant flow with high precision; the flow fluctuation error range after the fluid is adjusted by the traditional constant flow device is about 5% -8%. Under the same working conditions, the error range of the flow fluctuation after the fluid passes through the device of the present invention is estimated to be between 3% and 5%, and the constant flow control effect of the device will be better than that of the traditional constant flow device; after the fluid flows through the device, the flow fluctuates Smaller, compared with traditional constant flow equipment, it can effectively reduce the repeated impact of fluid pressure fluctuations on the equipment, and the service life of each part of the system will increase, which is more economical.
  • any process or method steps may be varied or re-sequenced according to alternative embodiments.
  • any "mean-plus-function" clause is intended to cover the structures described herein as performing the recited function and not only structural equivalents but also equivalent structures.
  • Other substitutions, modifications, changes and omissions may be made in the design, operation and arrangement of the exemplary embodiments without departing from the scope of the present invention. Therefore, the present invention is not limited to a particular embodiment, but extends to various modifications still falling within the scope of the appended claims.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Flow Control (AREA)
  • Safety Valves (AREA)

Abstract

一种机械自力式恒流量控制组合装置，包括粗调单元(100)和精调单元(200)，粗调单元包括粗调增压室(101)、安装在所述粗调增压室(101)内部的第一整流板(102)和粗调阀芯(103)、与所述粗调阀芯(103)相连的第一弹性件(104)；精调单元(200)与所述粗调单元(100)相连，包括与所述粗调增压室(101)相连为一体的精调增压室(201)，安装在所述精调增压室(201)内的支座(202)，与所述支座(202)相连的衡压管(203)、第二整流板(204)和第二弹性件(205)，以及与第二弹性件(205)相连的精调阀芯。该装置可保证其服务的设备流量稳定在设定区间，有效减少因流体流量波动对设备产生的反复冲击，增加系统各部分设备使用寿命，具有较高的经济性。

Description

一种机械自力式恒流量控制组合装置 技术领域
本发明涉及自力式流量控制技术领域，特别是一种机械自力式恒流量控制组合装置。
背景技术
在供热、空调、供水等复杂管道运输系统中，需要均衡合理地输送和分配流体流量，保持管道内部流量准确和稳定，由于流体输送压力变化对流量产生影响，造成流量分配不均匀，为此人们发明了许多恒流量设备，在航空航天、机床液压、空调、供暖、燃气运输等系统中大量使用此类设备，以确保在输送压力发生变化时，仍然能够维持管道内部流体流量相对恒定，从而保证系统稳定运行。机械自力式恒流量控制装置属于恒流量控制阀的一类产品，专门应用于需要控制流量的流体管网系统。
发明内容
本部分目的在于概述本发明实施例的一些方面以及简要介绍一些较佳实施例。在本部分以及本申请的说明书摘要和发明名称中可能会做些简化或省略以避免使本部分、说明书摘要和发明名称的目的模糊，而这种简化或省略不能用于限制本发明的范围。
鉴于上述和/或现有的自力式恒流量控制装置中存在的问题，提出了本发明。
因此，本发明所要解决的问题在于需要一种机械自力式恒流量控制组合装置，解决管道运输中由于流体的输送压力变化对流量产生影响，造成流量输送及分配不均匀的问题。
为解决上述技术问题，本发明提供如下技术方案：一种机械自力式恒流量控制组合装置，其包括：粗调单元和精调单元，粗调单元包括粗调增压室、安装在所述粗调增压室内部的第一整流板和粗调阀芯、与所述粗调阀芯相连的第一弹性件；精调单元与所述粗调单元相连，包括与所述粗调增压室相连为一体的精调增压室，安装在所述精调增压室内的支座，与所述支座相连的衡压管、第二整流板和第二弹性件，以及与第二弹性件相连的精调阀芯。
作为本发明所述机械自力式恒流量控制组合装置的一种优选方案，其中：所述粗调增压室一端设有进口，另一端与所述精调增压室相连，流体由粗调增 压室进入精调增压室的部分为次级进口；所述粗调增压室直径大于所述次级进口直径，所述次级进口直径大于所述进口直径。
作为本发明所述机械自力式恒流量控制组合装置的一种优选方案，其中：所述第一整流板固定安装在所述粗调增压室内部中间，所述第一整流板上设有若干第一流通孔；所述粗调阀芯为圆台状，其安装于所述次级进口处，所述粗调阀芯圆面较大的一端位于粗调增压室内，另一端位于精调增压室内并与第一弹性件相连。
作为本发明所述机械自力式恒流量控制组合装置的一种优选方案，其中：所述支座为叶栅型并安装在精调增压室内靠近次级进口的一端，所述支座朝向粗调增压室的一面上固定连接有第二整流板，所述第二整流板上设有若干第二流通孔，所述第二整流板与第一弹性件相连。
作为本发明所述机械自力式恒流量控制组合装置的一种优选方案，其中：所述支座另一面中间安装有衡压管，所述衡压管从所述精调增压室侧壁延伸而出并连通到所述粗调增压室。
作为本发明所述机械自力式恒流量控制组合装置的一种优选方案，其中：所述精调阀包括精调阀芯、精调阀芯挡环，所述精调阀芯与所述支座之间均匀分布连接有若干第二弹性件。
作为本发明所述机械自力式恒流量控制组合装置的一种优选方案，其中：所述精调阀芯挡环与所述精调增压室内壁固定且密封连接，所述精调阀芯套接在所述精调阀芯挡环内，所述精调阀芯两端侧面还均匀分布有若干定位挡块,所述精调阀芯可在一定范围内沿轴向移动。
作为本发明所述机械自力式恒流量控制组合装置的一种优选方案，其中：所述精调阀芯中间沿轴向设有第三流通孔，所述精调阀芯侧壁还设有若干流通槽,所述流通槽呈均匀圆周分布，且所述流通槽的高度各不相同，呈均匀梯度变化，所述精调阀芯上下直径一致，且所述精调阀芯侧壁上除了流通槽的其他部分与所述精调阀芯挡环之间为密封状态。
作为本发明所述机械自力式恒流量控制组合装置的一种优选方案，其中：所述第二弹性件的灵敏度高于所述第一弹性件，所述粗调阀芯与支座之间以第一导向杆连接，所述精调阀芯与支座之间以若干第二导向杆连接，所述第一弹性件套接在第一导向杆上，所述第二弹性件套接在第二导向杆上。
作为本发明所述机械自力式恒流量控制组合装置的一种优选方案，其中：所述精调增压室一端与所述粗调增压室相连，另一端为出口,所述出口的直径与粗调增压室一端进口的直径一致。
本发明有益效果为：本发明根据实际生产过程中技术需要，随着压力变化装置内部机械运动控制流体流通面积，实现流量相对恒定的自力式恒流量控制组合装置，有效保持管道内部流量的准确和稳定，不易受到影响而产生分配不均的问题；本发明可应用于较宽的压力波动范围，对较大压力波动范围下需要进行流体流量恒定的工况具有较高适应性，实现精度较高的流量恒定；流体通过传统恒流量装置调节后流量波动误差范围约在5％-8％之间。同工况下，流体通过本发明装置后流量波动误差范围预估约在3％-5％之间，本装置恒定流量控制效果将优于传统恒流量装置；流体流过本装置后，流量波动更小，相比于传统恒流量设备，可以保证其服务的设备流量稳定在设定区间，且能够有效减少因流体流量波动对设备产生的反复冲击，提高系统各部分设备使用寿命，具有较高的经济性。
附图说明
为了更清楚地说明本发明实施例的技术方案，下面将对实施例描述中所需要使用的附图作简单地介绍，显而易见地，下面描述中的附图仅仅是本发明的一些实施例，对于本领域普通技术人员来讲，在不付出创造性劳动性的前提下，还可以根据这些附图获得其它的附图。其中：
图1为机械自力式恒流量控制组合装置的内部结构立体图。
图2为机械自力式恒流量控制组合装置的剖面及流体流通方式图。
图3为机械自力式恒流量控制组合装置的内部结构另一个视角的立体图。
图4为机械自力式恒流量控制组合装置的内部流体流通面积示意图
图5为机械自力式恒流量控制组合装置内部粗调阀芯、精调阀芯与弹簧支座的连接方式图。
具体实施方式
为使本发明的上述目的、特征和优点能够更加明显易懂，下面结合说明书附图对本发明的具体实施方式做详细的说明。
在下面的描述中阐述了很多具体细节以便于充分理解本发明，但是本发明还可以采用其他不同于在此描述的其它方式来实施，本领域技术人员可以在不 违背本发明内涵的情况下做类似推广，因此本发明不受下面公开的具体实施例的限制。
其次，此处所称的“一个实施例”或“实施例”是指可包含于本发明至少一个实现方式中的特定特征、结构或特性。在本说明书中不同地方出现的“在一个实施例中”并非均指同一个实施例，也不是单独的或选择性的与其他实施例互相排斥的实施例。
参照图1～5，为本发明第一个实施例，该实施例提供了一种机械自力式恒流量控制组合装置，其对较大压力波动范围下需要进行流体流量恒定的工况具有较高适应性，能实现精度较高的流量恒定。
所述机械自力式恒流量控制组合装置包括能对进入流体流量进行初步控制调节的粗调单元100，与粗调单元100连接为一体并能对流体流量更精确地控制从而使流量达到稳定的精调单元200。
粗调单元100，包括粗调增压室101、安装在粗调增压室101内部的第一整流板102和粗调阀芯103、与粗调阀芯103相连的第一弹性件104。
其中，第一弹性件104为压缩弹簧，其根据管道内流通的流体流量可能产生的变化值而选择，第一弹性件104在流体流量保持稳定时仍具有一定的压缩量，预压缩量由压差范围及弹簧行程确定。一定的预压缩量可以使得粗调阀芯103保持常开状态，防止流体压力较大时，粗调阀芯103与管道内壁完全贴合导致装置失效。考虑到经济性及实用性，粗调装置中可选择相对较低灵敏度弹簧。
此外，粗调增压室101一端设有进口101a，另一端与精调增压室201相连，流体由粗调增压室101进入精调增压室201的部分为次级进口101b；粗调增压室101直径大于所述次级进口101b直径，次级进口101b直径大于进口101a直径。
进一步的，第一整流板102固定安装在粗调增压室101内部中间，第一整流板102上设有若干第一流通孔102a；粗调阀芯103为圆台状，其安装于次级进口101b处，粗调阀芯103圆面较大的一端位于粗调增压室101内，另一端位于精调增压室201内并与第一弹性件104相连。
基于上述，粗调单元100的工作原理为：当流体从进口101a进入粗调增压室101时，第一整流板102可使流体均匀分布于粗调增压室流通通道；粗调增压室101口径大小的变化使得流体流通直径突然扩大，将流体动能转化为压力 能。当流体压力增大时，粗调阀芯103与阀座之间流体的流速增加，流量增大，同时流体作用于粗调阀芯103上的压力大于第一弹性件104的压缩力，粗调阀芯103在流体压力作用下向流动方向移动，粗调阀芯103与阀座之间的流体流通截面积减小，流量减少，直到作用于粗调阀芯103上的流体压力等于第一弹性件104的预压缩力，粗调阀芯103停止移动，流量稳定；同理，流体压力减小时，粗调阀芯103与阀座之间的流速减小，流量减小，同时流体作用于粗调阀芯103上的压力小于第一弹性件104的压缩力，粗调阀芯103在第一弹性元件104的作用下向流动反方向移动，粗调阀芯103与阀座之间的流体流通截面积增大，流量增大，直到作用于粗调阀芯103上的流体压力等于第一弹性件104的压缩力，粗调阀芯103停止移动，流量稳定。
上述粗调单元100在流体压力增加或减小的工况下，通过调整粗调阀芯103与阀座之间流通面积的减小或增大，保证流量初步恒定。
然而，流体流经粗调增压室101后，由于压力变化范围较大时，以及粗调增压室101和其内部各部件的外形曲线等因素，流量控制的结果必然有一定的调整误差，使得流量稳定值与预期值存在一定的偏差。因此，通过精调单元200对流量进一步控制，缩小偏差。
精调单元200，包括与粗调增压室101相连为一体的精调增压室201，安装在精调增压室201内的支座202，与支座202相连的衡压管203、第二整流板204和第二弹性件205，以及与第二弹性件205相连的精调阀206。
具体的，支座202为叶栅型并安装在精调增压室201内靠近次级进口101b的一端，支座202朝向粗调增压室101的一面上固定连接有第二整流板204，第二整流板204上设有若干第二流通孔204a，第二整流板204与第一弹性件104相连。支座202另一面中间安装有衡压管203，衡压管203从精调增压室201侧壁延伸而出并连通到粗调增压室101。支座202通过衡压管203连接粗调增压室101，使得粗调阀芯103通过弹簧传递给支座202的压力与粗调增压室101内的压力相互平衡抵消，降低装置收到的流动冲击，提高装置寿命。
进一步的，精调阀206包括精调阀芯206a、精调阀芯挡环206b，精调阀芯206a与支座202之间均匀分布连接有若干第二弹性件205。精调阀芯挡环206b与精调增压室201内壁固定并密封连接，精调阀芯206a套接在精调阀芯挡环206b内，精调阀芯206a两端侧面还均匀分布有若干定位挡块206a-1，精调阀芯 206a可在一定范围内沿轴向移动。精调阀芯206a中间沿轴向设有第三流通孔206a-2，精调阀芯206a侧壁还设有若干流通槽206a-3,流通槽206a-3呈均匀圆周分布，且流通槽206a-3的高度各不相同，呈均匀梯度变化，精调阀芯206a上下直径一致，且精调阀芯206a侧壁上除了流通槽206a-3的其他部分与精调阀芯挡环206b之间为密封状态。
其中，第二弹性件205采用灵敏度较高的拉力弹簧，在保证精调阀芯206a稳定性的同时，确保精调阀芯206a在轴向上对应压力变化下的精确位移,定位挡块206a-1设置在精调阀芯206a两端，确保精调阀芯206a在预定范围内移动而不会过度伸长失去弹簧特性；精调阀芯206a中部的第三流通孔206a-2，使部分流体可以流过，避免流体完全从侧面的流通槽206a-3流出，影响实际流体的流量精度，需要注意的是，该孔的大小决定精调阀芯受力面积，不宜过大，且孔的尺寸与精调弹簧的选取有一定关系，可根据实际情况确定。
再进一步的，精调阀芯挡环206b与流体流通管壁相固连，且要求精调阀芯挡环206a-1与管壁之间密封，不允许有流体从挡环与管壁之间流过，在保证精调阀芯206a与精调阀芯挡环206b之间的相对滑移的同时，要求精调阀芯挡环206b与精调阀芯206a壁面之间的密封性能良好，当精调阀芯挡环206b处于精调阀芯206a最前端时，要求流体仅能从第三流通孔206a-2中流过。
为使本装置能够适用于不同流量的不同种类流体流动过程中的流量控制，精调阀芯206a侧面流通槽206a-3的数量、尺寸、形状可根据实际需求改进。
基于上述，精调单元200的工作原理为：当流体流入精调单元200，第二整流板204可使流体均匀分布于精调增压室201的流通槽206a-3。当流体压力增大时，流通槽206a-3中流体的流速增加，流量增大，同时流体作用于精调阀芯206a上的压力大于第二弹性件205的初张力，精调阀芯206a在流体压力作用下向流动方向移动，精调阀芯挡环206b挡住部分流通槽206a-3，流体流通截面积减小，流量减少，直到作用于精调阀芯206a上的流体压力等于第二弹性件205的拉伸弹簧力值，精调阀芯206a停止移动，流量稳定；同理，流体压力减小时，流通槽206a-3中流体的流速减小，流量减少，同时流体作用于精调阀芯206a上的压力小于第二弹性件205的拉力，精调阀芯206a在第二弹性元件205的作用下向流动反方向移动，精调阀芯挡环206b释放部分流通槽206a-3，流通槽206a-3中流体的流通截面积增大，流量增大，直到作用于精调阀芯206a上的 流体压力等于第二弹性件205的拉力，精调阀芯206a停止移动，流量稳定。
上述精调单元200在流体压力增加或减小的工况下，通过调整精调阀芯挡环206b与精调阀芯206a之间相对位置，改变可流通流体的流通槽206a-3数量及其流通面积，使得精调阀芯206a流通面积发生较精细的变化，保证流量精确恒定。
此外，第二弹性件205的灵敏度高于第一弹性件104，粗调阀芯103与支座202之间以第一导向杆D-1连接，精调阀芯206a与支座202之间以若干第二导向杆D-2连接，第一弹性件104套接在第一导向杆D-1上，第二弹性件205套接在第二导向杆D-2上。设置第一导向杆D-1和第二导向杆D-2的目的是防止粗调阀芯103和精调阀芯206a在压力作用下产生轴向上的偏移。参照图5，为第一导向杆D-1和第二导向杆D-2的一种实施方式，粗调阀芯103与精调阀芯206a上均设有用于安装导向杆的圆孔，防止阀芯脱出，第一导向杆D-1和第二导向杆D-2的实际长度可依据弹簧的伸缩量等因素进行改进，也可在第一导向杆D-1和第二导向杆D-2的末端加装限位块等；在其他方案中，第一导向杆D-1和第二导向杆D-2也可设为伸缩杆，分别与粗调阀芯103与精调阀芯206a固定连接。需说明的是，实施例所述及图示中所给的方案仅为例示性的，实际实施方案不限这几种。
在该实施例中，第一整流板102、第二整流板204均采用中部实心，边缘开孔的方式。对于第一整流板102，此开孔方式主要考虑管内流体流动特性，中间部分流体流动速度较快，中部实心能够有效阻挡来流，使均匀分布，同时减少流体流动对于粗调阀芯103的冲蚀；对于第二整流板204，此开孔方式同样考虑流动特性，中部实心能够保证流体在精调增压室201内的流动向边缘分散，避免来流速度过快，从精调阀芯206a中部孔急速流过。为了使流体流通面积不产生过多的变化，以及考虑到配件的实施难度和适用性，精调增压室201一端出口201a的直径与粗调增压室101一端进口101a的直径一致。
本发明可应用于较宽的压力波动范围，对压力波动较大的工况具有较高适应性，实现精度较高的流量恒定；流体通过传统恒流量装置调节后流量波动误差范围约在5％-8％之间。同工况下，流体通过本发明装置后流量波动误差范围预估约在3％-5％之间，本装置恒定流量控制效果将优于传统恒流量装置；流体流过本装置后，流量波动更小，相比于传统恒流量设备，能够有效减少因流体 压力波动对设备产生的反复冲击，系统各部分设备使用寿命均会有所增加，具有较高的经济性。
重要的是，应注意，在多个不同示例性实施方案中示出的本申请的构造和布置仅是例示性的。尽管在此公开内容中仅详细描述了几个实施方案，但参阅此公开内容的人员应容易理解，在实质上不偏离该申请中所描述的主题的新颖教导和优点的前提下，许多改型是可能的(例如，各种元件的尺寸、尺度、结构、形状和比例、以及参数值(例如，温度、压力等)、安装布置、材料的使用、颜色、定向的变化等)。例如，示出为整体成形的元件可以由多个部分或元件构成，元件的位置可被倒置或以其它方式改变，并且分立元件的性质或数目或位置可被更改或改变。因此，所有这样的改型旨在被包含在本发明的范围内。可以根据替代的实施方案改变或重新排序任何过程或方法步骤的次序或顺序。在权利要求中，任何“装置加功能”的条款都旨在覆盖在本文中所描述的执行所述功能的结构，且不仅是结构等同而且还是等同结构。在不背离本发明的范围的前提下，可以在示例性实施方案的设计、运行状况和布置中做出其他替换、改型、改变和省略。因此，本发明不限制于特定的实施方案，而是扩展至仍落在所附的权利要求书的范围内的多种改型。
此外，为了提供示例性实施方案的简练描述，可以不描述实际实施方案的所有特征(即，与当前考虑的执行本发明的最佳模式不相关的那些特征，或于实现本发明不相关的那些特征)。
应理解的是，在任何实际实施方式的开发过程中，如在任何工程或设计项目中，可做出大量的具体实施方式决定。这样的开发努力可能是复杂的且耗时的，但对于那些得益于此公开内容的普通技术人员来说，不需要过多实验，所述开发努力将是一个设计、制造和生产的常规工作。
应说明的是，以上实施例仅用以说明本发明的技术方案而非限制，尽管参照较佳实施例对本发明进行了详细说明，本领域的普通技术人员应当理解，可以对本发明的技术方案进行修改或者等同替换，而不脱离本发明技术方案的精神和范围，其均应涵盖在本发明的权利要求范围当中。

Claims (10)

  1. 一种机械自力式恒流量控制组合装置，其特征在于：包括，
    粗调单元(100)，包括粗调增压室(101)、安装在所述粗调增压室(101)内部的第一整流板(102)和粗调阀芯(103)、与所述粗调阀芯(103)相连的第一弹性件(104)；以及与所述粗调单元(100)相连的精调单元(200)。
    精调单元(200)，包括与所述粗调增压室(101)相连为一体的精调增压室(201)，安装在所述精调增压室(201)内的支座(202)，与所述支座(202)相连的衡压管(203)、第二整流板(204)和第二弹性件(205)，以及与第二弹性件(205)相连的精调阀(206)。
  2. 如权利要求1所述的机械自力式恒流量控制组合装置，其特征在于：所述粗调增压室(101)一端设有进口(101a)，另一端与所述精调增压室(201)相连，流体由粗调增压室(101)进入精调增压室(201)的部分为次级进口(101b)；所述粗调增压室(101)直径大于所述次级进口(101b)直径，所述次级进口(101b)直径大于所述进口(101a)直径。
  3. 如权利要求2所述的机械自力式恒流量控制组合装置，其特征在于：所述第一整流板(102)固定安装在所述粗调增压室(101)内部中间，所述第一整流板(102)上设有若干第一流通孔(102a)；所述粗调阀芯(103)为圆台状，其安装于所述次级进口(101b)处，所述粗调阀芯(103)圆面较大的一端位于粗调增压室(101)内，另一端位于精调增压室(201)内并与第一弹性件(104)相连。
  4. 如权利要求3所述的机械自力式恒流量控制组合装置，其特征在于：所述支座(202)为叶栅型并安装在精调增压室(201)内靠近次级进口(101b)的一端，所述支座(202)朝向粗调增压室(101)的一面上固定连接有第二整流板(204)，所述第二整流板(204)上设有若干第二流通孔(204a)，所述第二整流板(204)与第一弹性件(104)相连。
  5. 如权利要求1～4任一所述的机械自力式恒流量控制组合装置，其特征在于：所述支座(202)另一面中间安装有衡压管(203)，所述衡压管(203)从所述精调增压室(201)侧壁延伸而出并连通到所述粗调增压室(101)。
  6. 如权利要求5所述的机械自力式恒流量控制组合装置，其特征在于：所述精调阀(206)包括精调阀芯(206a)、精调阀芯挡环(206b)，所述精调阀芯(206a)与所述支座(202)之间均匀分布连接有若干第二弹性件(205)。
  7. 如权利要求6所述的机械自力式恒流量控制组合装置，其特征在于：所述精调阀芯挡环(206b)与所述精调增压室(201)内壁固定并密封连接，所述精调阀芯(206a)套接在所述精调阀芯挡环(206b)内，所述精调阀芯(206a)两端侧面还均匀分布有若干定位挡块(206a-1),所述精调阀芯(206a)可在一定范围内沿轴向移动。
  8. 如权利要求7所述的机械自力式恒流量控制组合装置，其特征在于：所述精调阀芯(206a)中间沿轴向设有第三流通孔(206a-2)，所述精调阀芯(206a)侧壁还设有若干流通槽(206a-3),所述流通槽(206a-3)呈均匀圆周分布，且所述流通槽(206a-3)的高度各不相同，呈均匀梯度变化，所述精调阀芯(206a)上下直径一致，且所述精调阀芯(206a)侧壁上除了流通槽(206a-3)的其他部分与所述精调阀芯挡环(206b)之间为密封状态。
  9. 如权利要求8所述的机械自力式恒流量控制组合装置，其特征在于：所述第二弹性件(205)的灵敏度高于所述第一弹性件(104)，所述粗调阀芯(103)与支座(202)之间以第一导向杆(D-1)连接，所述精调阀芯(206a)与支座(202)之间以若干第二导向杆(D-2)连接，所述第一弹性件(104)套接在第一导向杆(D-1)上，所述第二弹性件(205)套接在第二导向杆(D-2)上。
  10. 如权利要求9所述的机械自力式恒流量控制组合装置，其特征在于：所述精调增压室(201)一端与所述粗调增压室(101)相连，另一端为出口(201a),所述出口(201a)的直径与粗调增压室(101)一端进口(101a)的直径一致。
PCT/CN2021/079195 2020-12-23 2021-03-05 一种机械自力式恒流量控制组合装置 WO2022134314A1 (zh)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN202011532206.0A CN112610740B (zh) 2020-12-23 2020-12-23 一种机械自力式恒流量控制组合装置
CN202011532206.0 2020-12-23

Publications (1)

Publication Number Publication Date
WO2022134314A1 true WO2022134314A1 (zh) 2022-06-30

Family

ID=75244255

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CN2021/079195 WO2022134314A1 (zh) 2020-12-23 2021-03-05 一种机械自力式恒流量控制组合装置

Country Status (2)

Country Link
CN (1) CN112610740B (zh)
WO (1) WO2022134314A1 (zh)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN115929961A (zh) * 2023-02-21 2023-04-07 四川旭信阀门制造有限公司 一种自力式压力调节阀及其使用方法
CN116378922A (zh) * 2023-05-31 2023-07-04 德阳市坤炜机电设备有限公司 一种钻井泵送系统及其监测方法

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN117270585B (zh) * 2023-11-21 2024-02-02 深圳市恒永达科技股份有限公司 液体流量控制系统及方法

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102563158A (zh) * 2012-03-07 2012-07-11 广西工学院鹿山学院 动态恒压恒流调节阀
CN102829223A (zh) * 2012-09-08 2012-12-19 环球阀门集团有限公司 多级调节式恒流阀
CN202719232U (zh) * 2012-07-18 2013-02-06 葛景琪 自力式自动控制恒流量阀
EP2690227A2 (en) * 2012-07-23 2014-01-29 "Tecoop-Eng" D.O.O. Pancevo Fire hydrant
WO2014174759A1 (ja) * 2013-04-25 2014-10-30 川崎重工業株式会社 過流防止機能付き弁装置
CN208123541U (zh) * 2018-03-28 2018-11-20 中国广核集团有限公司 自力式流量控制装置

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7255133B2 (en) * 2003-11-17 2007-08-14 In-Well Technologies, Inc. Fluid pressure system including free floating bladder
CN2846936Y (zh) * 2005-06-29 2006-12-13 陈振双 流量自控阀门
US20080271794A1 (en) * 2007-05-01 2008-11-06 Louis Leemhuis Automated mechanical constant flow valve for air ducts
CN201462132U (zh) * 2009-07-09 2010-05-12 上海海事大学 自适应式恒流量控制阀
CN105042152B (zh) * 2015-05-07 2017-07-21 北京航空航天大学 一种高压大流量高精度紧凑型二级减压器
CN105351585B (zh) * 2015-11-25 2017-12-08 徐州工业职业技术学院 变刚度弹簧式恒流阀
CN206093086U (zh) * 2016-07-27 2017-04-12 路达(厦门)工业有限公司 流体开关的恒流装置和流体开关

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102563158A (zh) * 2012-03-07 2012-07-11 广西工学院鹿山学院 动态恒压恒流调节阀
CN202719232U (zh) * 2012-07-18 2013-02-06 葛景琪 自力式自动控制恒流量阀
EP2690227A2 (en) * 2012-07-23 2014-01-29 "Tecoop-Eng" D.O.O. Pancevo Fire hydrant
CN102829223A (zh) * 2012-09-08 2012-12-19 环球阀门集团有限公司 多级调节式恒流阀
WO2014174759A1 (ja) * 2013-04-25 2014-10-30 川崎重工業株式会社 過流防止機能付き弁装置
CN208123541U (zh) * 2018-03-28 2018-11-20 中国广核集团有限公司 自力式流量控制装置

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN115929961A (zh) * 2023-02-21 2023-04-07 四川旭信阀门制造有限公司 一种自力式压力调节阀及其使用方法
CN115929961B (zh) * 2023-02-21 2023-05-12 四川旭信阀门制造有限公司 一种自力式压力调节阀及其使用方法
CN116378922A (zh) * 2023-05-31 2023-07-04 德阳市坤炜机电设备有限公司 一种钻井泵送系统及其监测方法
CN116378922B (zh) * 2023-05-31 2023-08-04 德阳市坤炜机电设备有限公司 一种钻井泵送系统及其监测方法

Also Published As

Publication number Publication date
CN112610740A (zh) 2021-04-06
CN112610740B (zh) 2021-09-10

Similar Documents

Publication Publication Date Title
WO2022134314A1 (zh) 一种机械自力式恒流量控制组合装置
CN110107763B (zh) 一种多级孔板缓冲螺旋型导轨稳压装置及其方法
US9285041B2 (en) Flow control valve and method of use
RU2635176C2 (ru) Выпрямляющее поток седельное кольцо и регулирующий клапан с выпрямляющим поток седельным кольцом
US9068660B2 (en) Valve device with a flow guiding device
CN101248402A (zh) 流体控制装置
CN106051236A (zh) 止回阀设备及方法
CN102695996A (zh) 具有多个阀头和阀座的减压阀
US20080271794A1 (en) Automated mechanical constant flow valve for air ducts
WO2021010830A1 (en) Device for limiting or keeping constant a flowing quantity of liquid
CA3097290C (en) Check valve
US11835142B2 (en) Buffer valve
CN215890649U (zh) 一种液压单向阀
CN110274043B (zh) 流量平衡装置
CN105387242A (zh) 一种压电型薄膜式节流阀
WO2019105336A1 (zh) 一种膨胀阀
WO2018103349A1 (zh) 一种消除粘度影响的恒流量缝隙式进出口
EP1442242A1 (en) Differential pressure valve
CN108050281B (zh) 可变输出压力减压系统
CN109578644B (zh) 一种减压阀
CN220850812U (zh) 一种采用周向可调节嵌套式鼠笼的活塞式调节阀
CN109442072A (zh) 一种自力式压差控制阀
CN115013624B (zh) 减压装置
US20190085988A1 (en) Flow rate control device
WO2024187700A1 (zh) 减压阀、呼吸器及燃料电池车辆

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 21908328

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 21908328

Country of ref document: EP

Kind code of ref document: A1