CN113108070A - Multistage pressure reduction string type liquid level regulating valve structure - Google Patents
Multistage pressure reduction string type liquid level regulating valve structure Download PDFInfo
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- CN113108070A CN113108070A CN202110499992.7A CN202110499992A CN113108070A CN 113108070 A CN113108070 A CN 113108070A CN 202110499992 A CN202110499992 A CN 202110499992A CN 113108070 A CN113108070 A CN 113108070A
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- 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
- F16K1/00—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces
- F16K1/32—Details
- F16K1/34—Cutting-off parts, e.g. valve members, seats
- F16K1/36—Valve members
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- 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
- F16K1/00—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces
- F16K1/32—Details
- F16K1/52—Means for additional adjustment of the rate of flow
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- 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
- F16K47/04—Means in valves for absorbing fluid energy for decreasing pressure or noise level, the throttle being incorporated in the closure member
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Abstract
The invention discloses a multistage pressure reduction string type liquid level regulating valve structure. A valve seat is arranged in the vertical cavity of the valve body, the valve seat is vertically divided into a throttling valve core cylindrical cavity and a buffering cylindrical cavity, a valve core sleeve is arranged in the throttling valve core cylindrical cavity, the valve core is sleeved with the valve seat, the valve core sleeve is provided with a valve core, and a multi-stage serial pressure reduction structure is arranged between the valve core and the valve core sleeve; the valve body is provided with a valve cover, and the valve cover axially compresses the valve core sleeve on the valve seat; fluid medium flows into the buffer cylindrical cavity from the inlet of the valve body, flows into the cylindrical cavity of the throttling valve core after passing through the central through hole of the valve seat, flows out from the through hole on the side wall of the upper end of the valve core sleeve to the reversing gap between the valve body and the valve core sleeve, and flows out from the outlet of the valve body after converging. The invention optimizes the valve structure aiming at the service environment and the structural characteristics of the high-pressure-difference liquid level control valve, and is beneficial to prolonging the service life and the safe and stable operation period of the high-pressure-difference liquid control valve.
Description
Technical Field
The invention relates to the structural design of a flow industrial regulating valve, in particular to a multi-stage pressure reduction string type liquid level regulating valve structure.
Background
Energy resources in China present the current situation of 'more coal, less oil and less gas', so the development of the modern coal chemical industry is an important measure for ensuring the safety of national energy strategy and ensuring that China reaches the development level of moderately developed countries in the middle of the century. The liquid level regulating valve is a key special device in the major process industry, a complex flowing state exists in the regulation and control process, the fault probability is high in the actual operation process, and prediction, prevention and control are difficult. For example, the wear failure of a high-pressure-difference regulating valve in the operation of a world first megaton coal liquefaction demonstration project is very serious. Despite the adoption of the high-end product of SchuF company in germany and the addition of more than 2 hundred million investments to design a single channel as four parallel, the service life of the actual single valve is still short. The abrasion failure of the liquid level regulating valve seriously restricts the production safety and economic benefit of the coal chemical industry device and the popularization of national demonstration engineering.
The abrasion failure process of the high-temperature-high-pressure-difference hydraulic control valve is closely related to factors such as a valve body structure, the physical properties of multi-component fluid, the structural characteristics of a fluid domain, material performance, the characteristics of particles and the like, the research on gas-liquid phase change, energy transfer and material response under the transient condition of the liquid level regulating valve is extremely complex, and the development of related theoretical modeling and experimental research is extremely complex. For a high-temperature and high-pressure-difference hydraulic control regulating valve, if the wear characteristics of an internal flow channel of the high-temperature and high-pressure-difference hydraulic control regulating valve cannot be accurately grasped, and a corresponding quantitative wear characteristic prediction method is established, the dynamic regulation and control of the flow wear characteristics of the liquid level regulating valve based on the flow wear characteristic prediction are difficult to realize. The structure optimization design of the high-temperature high-pressure-difference liquid level regulating valve is one of key ways for improving the abrasion resistance of the high-temperature high-pressure-difference liquid level regulating valve, and although the angle valve structure of the liquid level regulating valve is adjusted to be a multi-stage pressure reduction series regulating valve, the throttling capacity of the regulating valve can be effectively improved, higher requirements are provided for the abrasion resistance between a valve core and a valve sleeve, even between the valve core and a valve seat. The existing research results carry out more researches on the internal cavitation and cavitation erosion characteristics of the high-pressure-difference hydraulic control valve, and also clearly illustrate that the cavitation and cavitation erosion characteristics in the calculation domain of the regulating valve are closely related to the pressure difference between an inlet and an outlet, the cavitation number, the cavitation intensity and the like. In addition, for a coal chemical industry system, particularly a direct coal liquefaction system, the whole process from raw material preparation and reaction separation to residue treatment relates to multiphase flow transmission of pulverized coal solid particles, and the throttling process of the high-temperature high-pressure-difference hydraulic control valve also has a serious flow wear problem.
In conclusion, in the face of the problem of failure of the high differential pressure hydraulic control regulating valve in a complex flowing and corrosive environment, the internal flow channel of the high differential pressure hydraulic control valve is subjected to a multistage pressure reduction series design according to the internal flowing characteristic of the high differential pressure hydraulic control valve, so that the internal cavitation and cavitation characteristics can be remarkably reduced. On the basis, the flow wear characteristics of the internal flow channel of the multistage pressure reduction serial liquid level regulating valve are researched, and the correlation relation between the flow wear position and strength, the pressure difference between the inlet and the outlet of the hydraulic control valve and the opening of the regulating valve is determined, so that important theoretical support and technical support are provided for accurately regulating and controlling the flow corrosion resistance of the hydraulic control valve.
The invention content is as follows:
in order to solve the problems existing in the prior art, the invention aims to provide a multistage pressure reduction series type liquid level regulating valve structure, aiming at the service environment and the structural characteristics of a high-pressure-difference liquid level control valve, the multistage pressure reduction series structure optimization of the high-pressure-difference liquid control valve is realized, and the service life and the safe and stable operation period of the high-pressure-difference liquid control valve are prolonged.
In order to achieve the aim of the invention, the technical scheme adopted by the invention is as follows:
a multistage pressure reduction string type liquid level regulating valve structure:
the structure comprises a valve body, a valve seat, a valve core sleeve, a valve cover and a valve core; a vertical cavity is arranged in the valve body, a valve seat is arranged in the vertical cavity, the vertical cavity in the valve body is divided into a throttling valve core cylindrical cavity at the upper part and a buffering cylindrical cavity at the lower part by the valve seat, a central through hole is formed in the valve seat and communicates the throttling valve core cylindrical cavity with the buffering cylindrical cavity, an inlet and an outlet are respectively arranged on two sides of the valve body, the inlet is communicated with the bottom of the buffering cylindrical cavity, and the outlet is communicated with the bottom of the throttling valve core cylindrical cavity; a valve core sleeve is fixedly arranged in the throttle valve core cylindrical cavity, an annular gap is formed between the outer wall of the valve core sleeve and the wall surface of the throttle valve core cylindrical cavity, and the annular gap is communicated with the outlet of the valve body; the bottom of the valve core sleeve is connected to the valve seat, a valve core with a plurality of notches is coaxially arranged in a cavity inside the valve core sleeve, and a flow passage is arranged between the valve core and the valve core sleeve to form a multi-stage serial pressure reduction structure; the upper port of the valve body is fixedly provided with a valve cover, the center of the valve cover is provided with a central hole which is coaxially communicated with the cylindrical cavity of the throttling valve core, and the end surface around the central hole of the valve cover axially compresses the valve core sleeve on the valve seat through a nut; a plurality of through holes are uniformly distributed on the side wall of the upper end of the valve core sleeve far away from the valve seat along the circumferential direction, fluid medium flows into the buffer cylindrical cavity from the inlet of the valve body and flows into the throttle valve core cylindrical cavity after passing through the central through hole of the valve seat, and the fluid medium after throttling and pressure reduction in the throttle valve core cylindrical cavity flows out of the through holes uniformly distributed on the side wall of the upper end of the valve core sleeve into the annular gap between the valve body and the valve core sleeve and flows out of the outlet of the valve body after converging in the annular gap.
The valve cover is characterized in that a valve rod is installed in a center hole of the valve cover, and the upper end of the valve core is fixedly connected with the lower end of the valve rod after penetrating into the center hole of the valve cover.
The valve core at the joint of the valve cover and the valve core sleeve is sleeved with a guide sleeve.
The annular gap between the valve rod and the valve cover central hole is sequentially provided with a packing bottom pad, packing and a packing gland from bottom to top, the part of the upper end of the packing gland, which extends out of the valve cover central hole, is provided with an outer flange, a flange plate is arranged on the packing gland and is fixedly connected to the upper end part of the valve cover through a screw rod, and the flange plate is tightly pressed on the packing gland through the screw rod.
The multistage string type pressure reduction structure between the valve core and the valve core sleeve specifically comprises: a step cavity is arranged in the valve core sleeve below the through hole at the upper end of the valve core sleeve, a plurality of inner flanges serving as throttling rings are axially arranged in the step cavity from top to bottom at intervals, and the step cavity is integrally divided into a plurality of small cavities by the plurality of throttling rings; the valve core in the valve core sleeve is characterized in that a plurality of symmetrical groove structures are axially arranged from top to bottom, each symmetrical groove structure comprises two grooves which are respectively and symmetrically arranged at two sides of the valve core along a symmetrical direction, and the symmetrical directions of the two grooves of two adjacent symmetrical groove structures are vertical; the inner diameter of the throttle ring is consistent with the outer diameter of the valve core, and the width of the groove is larger than the thickness of the throttle ring.
The disk seat all seted up annular groove at up terminal surface and lower terminal surface, all install the flange winding in the annular groove and fill up and seal.
The lower end of the valve rod is coaxially connected with the upper end of the valve core through a connecting sheath, and the valve rod drives the valve core to move up and down in the valve core sleeve in the axial direction.
The valve inner flow channel abrasion characteristic prediction regulation and control treatment process comprises the following steps:
1) the method comprises the following steps of building a circulating pipeline loop, arranging liquid-phase oil and particles in the circulating pipeline loop, arranging opposite flanges in the middle area of the circulating pipeline loop, mounting a multi-stage pressure-reducing string-type liquid level regulating valve between the opposite flanges, conveying and pressurizing the liquid-phase oil and the particles in the circulating pipeline loop by using a circulating pump and a pressurizing pump, and regulating the pressure of an inlet and an outlet of the multi-stage pressure-reducing string-type liquid level regulating valve;
2) defining the throttling times of the fluid in the fluid domain between the valve core and the valve core sleeve as the number of stages;
3) in the test process, aluminum sheets are fixedly adhered to different positions of the inner wall of the valve core sleeve and the outer wall of the valve core at each stage in the multistage pressure reduction serial liquid level regulating valve respectively, n pressure strain gauges and m flow rate meters are adhered to the positions near each aluminum sheet, and m flow rate distribution values and n pressure distribution values of different positions of the inner wall of the valve core sleeve and the outer wall of the valve core at different moments are acquired and converted in real time; after each group of experiment tests are completed, the wear rate KE of the aluminum sheet is tested based on the scanning of the laser displacement sensorC；
4) Adjusting the inlet pressure of the multistage pressure reduction serial liquid level adjusting valve to 11.7MPa, and converting by utilizing the step 3) to obtain n pressure distribution values and m flow velocity distribution values at different positions at different moments to obtain the distribution characteristics of a pressure field and a velocity field in a flow field; establishing a wear rate KE based on the aluminum sheet wear depth obtained by scanning a laser displacement sensorCCorrelation with pressure distribution and flow velocity distribution;
5) sequentially increasing and adjusting inlet pressure P of multistage pressure reduction string type liquid level adjusting valve at fixed pressure intervalinRepeating the experimental method of the step 4), and respectively drawing the wear rates KE of the aluminum sheets in different stagesCWith inlet pressure PinA varying discrete data curve;
6) wear rate KE for aluminum sheetCWith inlet pressure PinCarrying out data fitting to obtain a continuous data change curve of the wear rate of the aluminum sheet along with the inlet pressure;
7) the height positions of different valve rods are dynamically regulated and controlled, so that the valve core is driven to move up and down, namely the position of the valve core sleeve is relative to the valve core, and the opening degree of the multistage pressure reduction serial liquid level regulating valve is adjusted; under the condition of different openness, testing the wear rate of the aluminum sheet along with the change of the openness to obtain a discrete data change curve of the wear rate of the aluminum sheet along with the openness of the valve core, and further obtaining a continuous data change curve of the wear rate of the aluminum sheet along with the openness of the valve core through data fitting; expanding and obtaining an incidence relation atlas of the aluminum sheet wear rate, the inlet pressure and the valve core openness by utilizing a continuous data change curve of the aluminum sheet wear rate along with the inlet pressure and combining a continuous data change curve of the aluminum sheet wear rate along with the valve core openness;
8) similarly, repeating the step 7), changing the particle size and the particle concentration, and continuously expanding to obtain an incidence relation map of the wear rate of the aluminum sheet and the inlet pressure, the opening degree of the valve core, the particle size and the particle concentration;
9) in the dynamic adjustment process, the critical wear rate [ epsilon ] is preset based on the wear-resistant characteristic and the wear setting margin of the aluminum sheet material]And based on real-time dynamic actual wear rate KE of aluminum sheetCAnd critical wear rate value [ epsilon ]]And (3) comparison:
if KEC＜0.95[ε]The position of the valve rod, the inlet pressure and the opening degree of the valve core are kept unchanged;
if KEC≥0.95[ε]Adjusting the opening degree of the valve core, the inlet pressure, the particle size and the particle concentration, and dynamically updating the actual wear rate value KE of the aluminum sheet material in real timeCUp to KEC＜0.95[ε]To avoid the valve coreRapid wear failure.
The invention has the beneficial effects that:
the invention provides a multistage pressure reduction string type liquid level regulating valve structure aiming at the service environment and the structural characteristics of a high pressure difference liquid level control valve in the flow type industrial fields of petrochemical engineering, coal chemical engineering, nuclear power engineering and the like. In addition, through the optimization of a multistage depressurization series structure, the adaptability of the regulating valve for resisting higher differential pressure is improved, the service life of the high differential pressure hydraulic control valve is prolonged, the safe and stable operation period is prolonged, and the expansion transformation and the design optimization of a process equipment system are supported.
The invention is suitable for the optimized design and the optimized operation of the multistage pressure reduction string type liquid level regulating valve with high pressure difference, such as petrochemical engineering, coal chemical engineering, nuclear power engineering and the like, has high prediction regulation and control precision, and has important practical value for pressure reduction optimization and liquid level precision adjustment.
Drawings
Fig. 1 is a schematic structural diagram of an embodiment of the present invention.
Fig. 2 is an enlarged view of the area a in fig. 1.
Fig. 3 is an enlarged view of region B in fig. 1.
Fig. 4 is an isometric view of the valve cartridge of the present invention.
FIG. 5 is a view showing the fitting relationship between the spool and the spool housing according to the present invention.
Fig. 6 is a cut-away view of the mating 1/4 of the valve core and the valve core sleeve of the present invention.
FIG. 7 is a cut-away view 1/4 of the valve core and the valve core sleeve and a schematic flow direction diagram of the inner flow channel.
Fig. 8 is a schematic diagram of the positional relationship between the spool and the spool sleeve when the spool opening is 50%.
Fig. 9 is a schematic diagram of the positional relationship between the spool and the spool cover when the spool opening is 0%.
Fig. 10 is a schematic diagram of the positional relationship between the spool and the spool cover when the opening of the spool is 100%.
FIG. 11 is a two-dimensional cross-sectional view of the assembly of the valve cartridge and the valve cartridge sleeve of the present invention.
Fig. 12 is a three-dimensional schematic view of the assembly of the valve cartridge and the cartridge sleeve of the present invention.
FIG. 13 shows a valve element opening C according to the present invention1And (3) a wear depth distribution characteristic diagram of the cylindrical expansion surface.
FIG. 14 is the corresponding C obtained from the test1The maximum abrasion depth of the cylindrical surface is shown along with the change of the opening degree of the valve core.
FIG. 15 is the corresponding C obtained from the test1The maximum abrasion depth of the cylindrical surface is shown as the change of the particle diameter of the particles.
FIG. 16 is the corresponding C obtained from the test1The maximum abrasion depth of the cylindrical surface is plotted along with the change of the inlet pressure.
The reference numbers in the figures illustrate: 1. a valve body; 2. a valve seat; 3. a valve core sleeve; 4. a guide sleeve; 5. a nut; 6. a packing press pad; 7. a filler; 8. a screw; 9. a valve stem; 10. a packing gland; 11. a connecting sheath; 12. a valve cover; 13. a valve core; 14. an inlet flange; 15. a flange winding pad; 16. a flange plate; 17. a fluid inlet flow passage; 18. a fluid outlet flow passage.
Detailed Description
The invention is further explained below with reference to the drawings and examples.
As shown in fig. 1, 2 and 3, the present invention includes a valve body 1, a valve seat 2, a valve core sleeve 3, a valve cover 12 and a valve core 13; a vertical cavity is arranged in the valve body 1, a valve seat 2 is arranged in the vertical cavity, and the valve seat 2 divides the vertical cavity in the valve body 1 into a throttling valve core cylindrical cavity at the upper part and a buffering cylindrical cavity at the lower part; the valve seat 2 is provided with a central through hole which communicates the throttling valve core cylindrical cavity with the buffer cylindrical cavity, and the two sides of the valve body 1 are respectively provided with an inlet and an outlet, wherein an inlet flow passage is communicated with the bottom of the buffer cylindrical cavity, and an outlet flow passage is communicated with the bottom of the throttling valve core cylindrical cavity; annular grooves are formed in the upper end face and the lower end face of the cylindrical valve seat 2, and flange winding gaskets 15 are installed in the annular grooves for sealing connection between the valve seat 2 and the valve core sleeve 3 and the valve body 1 through the flange winding gaskets 15 in the annular grooves in the upper end face and the flange winding gaskets 15 in the annular grooves in the lower end face.
A valve core sleeve 3 is fixedly arranged in the throttling valve core cylindrical cavity, an annular gap is formed between the outer wall of the valve core sleeve 3 and the wall surface of the throttling valve core cylindrical cavity, and the lower part of the annular gap is communicated with an outlet of the valve body 1; the bottom of the valve core sleeve 3 is connected to the valve seat 2, and the annular valve seat 2 and the valve core sleeve 3 are coaxially arranged; a valve core 13 with a plurality of notches is coaxially arranged in a cavity inside the valve core sleeve 3, and a flow passage is arranged between the valve core 13 and the valve core sleeve 3 to form a multi-stage serial pressure reduction structure.
The cylindrical cavity of the throttling valve core penetrates through the upper port of the valve body 1, the upper port of the valve body 1 is fixedly provided with a valve cover 12, the center of the valve cover 12 is provided with a central hole which is coaxially communicated with the cylindrical cavity of the throttling valve core, and the end surface around the central hole of the valve cover 12 axially compresses the valve core sleeve 3 on the valve seat 2 through a nut 5; in the specific embodiment shown in fig. 3, the central hole of the valve cover 12 is a tapered multi-stage hole formed from bottom to top in the axial direction, the upper part of the valve core 13 is embedded into the lower part of the central hole of the valve cover 12, the guide sleeve 4 with the supporting and guiding functions is embedded in the annular gap between the valve core sleeve 3 and the central hole at the upper end of the valve body and the central hole at the lower end of the valve cover, and the upper end surface of the valve body 1 and the lower end surface of the valve cover 12 are fixedly connected.
The side wall of the upper end of the valve core sleeve 3 far away from the valve seat 2 is uniformly provided with a plurality of through holes, generally four through holes along the circumferential direction. The fluid medium flows into the buffer cylindrical cavity from the fluid inlet flow channel 17 of the valve body 1, flows into the throttle valve core cylindrical cavity after passing through the central through hole of the valve seat 2, and thus the throttling and pressure reduction are realized. The fluid medium after throttling and pressure reduction in the cylindrical cavity of the throttling valve core flows out from the through hole on the side wall of the upper end of the valve core sleeve 3 to the annular gap between the valve body 1 and the valve core sleeve 3, and flows out from the fluid outlet flow channel 18 of the valve body 1 through the annular gap in confluence.
The fluid inlet channel 17 and the fluid outlet channel 18 of the valve body 1 are respectively provided with an inlet flange 14 and an outlet flange, and the fluid inlet channel 17 and the fluid outlet channel 18 are respectively communicated with an inlet and an outlet of the valve body 1.
The valve rod 9 is arranged in the central hole of the valve cover 12, and the upper end of the valve core 13 is fixedly connected with the lower end of the valve rod 9 after penetrating into the central hole of the valve cover 12. Wherein the lower end of the valve rod 9 is coaxially connected with the upper end of the valve core 13 through the connecting sheath 11, and the valve rod 9 drives the valve core 13 to move up and down in the valve core sleeve 3 in the axial direction. The valve core 13 at the joint of the valve cover 12 and the valve core sleeve 3 is externally sleeved with a guide sleeve 13 for supporting the valve core 13 to move up and down in the axial direction, so that the smoothness of the up and down movement of the valve core is ensured.
As shown in fig. 3, a packing bottom pad 6, a packing 7 and a packing gland 10 are sequentially installed in an annular gap between a valve rod 9 and a central hole of a valve cover 12 from bottom to top, an outer flange is arranged at a part of the upper end of the packing gland 10, which extends out of the central hole of the valve cover 12, a flange 16 is arranged on the packing gland 10, and the flange 16 is pressed on the packing gland 10 through a screw 8.
As shown in fig. 4, the valve core 13 located in the valve core sleeve 3 is characterized in that a plurality of symmetrical groove structures are axially arranged from top to bottom, and the symmetrical groove structures are arranged at intervals along the axial direction; each symmetrical groove structure comprises two grooves which are respectively and symmetrically arranged at two sides of the valve core 13 along the symmetrical direction, and the symmetrical directions of the two grooves of the two adjacent symmetrical groove structures are vertical. As can be seen from fig. 5, 6 and 7, the multistage tandem type pressure reducing structure between the valve core 13 and the valve core sleeve 3 specifically includes: a step cavity is arranged in the valve core sleeve 3 below the through hole at the upper end of the valve core sleeve 3, a plurality of inner flanges are arranged in the step cavity from top to bottom at certain intervals in the axial direction and serve as throttling rings, and the step cavity is integrally divided into a plurality of small cavities by the throttling rings. The inner diameter of the throttle ring is the same as the outer diameter of the valve core 13, and the width of the groove is larger than the thickness of the throttle ring.
As shown in fig. 5, three inner flanges are axially and equidistantly arranged from top to bottom in the stepped cavity inside the valve core sleeve 3, and the three inner flanges divide the whole stepped cavity into four small cavities; as can be seen from fig. 4, the valve core 13 located in the valve core sleeve 3 is characterized in that three symmetrical groove structures are axially formed from top to bottom, the three symmetrical groove structures are axially arranged at intervals, each symmetrical groove structure comprises two grooves which are respectively and symmetrically arranged on two sides of the valve core 13 along a symmetrical direction, and the symmetrical directions of the two grooves of two adjacent upper and lower symmetrical groove structures are perpendicular to each other; the upper groove wall of each groove is a transition inclined surface, the peripheral surface of the valve core 13 above the uppermost symmetrical groove structure is provided with an annular groove which is complete along the annular shape, and the annular groove is positioned near the through hole at the upper end of the valve core sleeve 3.
Fig. 4 is an isometric view of the valve cartridge of the present invention. As can be seen from the figure, the structure of the valve core is in a shape of a sugarcoated haw, and the valve core is in a multi-stage series structure. The lower end of the valve core is cylindrical and is provided with a chamfer, two grooves with the same size and size are symmetrically formed in the upward cylindrical tail end at certain intervals, two grooves with the same size and size are symmetrically formed in the upward equidistant interval at certain intervals, 90-degree direction torsion is performed at certain intervals, two grooves with the same size and size are formed in the upward equidistant interval at certain intervals, three pairs of grooves are sequentially formed in the outer wall surface of the lower portion of the whole valve core 13, and the phase difference between.
Fig. 5 shows a fitting relationship between the spool and the spool case. 3 sets of throttling rings with holes in the middle are sequentially arranged in the internal cavity of the valve core sleeve 3 at intervals from top to bottom, and the outer wall surface of each throttling ring is welded and fixed with the inner wall surface of the internal cavity of the valve core sleeve 3; the valve core 13 passes through the inner cavity of the valve core sleeve from bottom to top from the bottom of the valve core sleeve 3. Wherein, the diameter of the cylindrical end at the tail end of the valve core 13 is slightly larger than the middle hole diameter of the lowest throttling ring in the inner cavity of the valve core sleeve 3. The distance from the lower surface of the lowest throttling ring of the cavity in the valve core sleeve 3 to the upper surface of the valve seat 2 is defined as H, the height of the cylindrical end at the tail end of the valve core 13 is defined as H, the maximum stroke of the valve core 13 in the valve core sleeve 3 is defined as H-H, namely the opening range of the valve core is defined as 0 to (H-H). The height direction center of a throttle ring of an inner cavity of the valve core sleeve 3 from bottom to top is defined as a horizontal section, and the horizontal section is respectively defined as a first stage of the regulating valve, a second stage of the regulating valve and a third stage of the regulating valve and is represented as a section I, a section II and a section III. Accordingly, the number of stages of the regulating valve represents the number of times the fluid medium inside the regulating valve is throttled.
Fig. 6 and 7 are respectively a cutaway view (isometric view) of the valve core and the valve core sleeve matching 1/4, a cutaway view 1/4 of the valve core and the valve core sleeve matching 1/4 and a schematic flow direction of the inner flow channel. The valve rod 9 drives the valve core 13 to move axially up and down in the valve core sleeve 3, and the symmetrical groove structures are arranged on the valve core 13 in a non-aligned mode, so that the symmetrical groove structures of the valve core 13 reciprocate in the throttle rings of the valve core sleeve 3, the throttle area is changed, and different valve core opening degree control and adjustment are realized. The axial position of the valve core 13 relative to the valve core sleeve is different, the gaps between the symmetrical groove structures and the throttling rings are different, so that the flow areas of fluid media are different, the flow areas and the flow rates in the flow areas are different due to the different opening degrees of the trigger valve cores, and the multi-stage pressure reduction serial liquid level regulation is realized. Fig. 6 and 7 only illustrate the valve core structure with 3 symmetrical grooves, and more valve core structures with symmetrical grooves can be arranged in engineering practice, so that higher-pressure reduction regulation is realized. With reference to the opening definition of fig. 5, when the lower end surface of the valve element 13 is tightly pressed and connected to the upper end surface of the central through hole of the valve seat 2, the valve opening is zero, and is in a closed state, and at this time, the fluid medium in the buffer cylindrical cavity cannot flow into the cylindrical cavity of the throttle valve element, and the structural schematic diagram of the valve element is shown in fig. 9, which shows a schematic diagram of a positional relationship between the valve element and the valve element sleeve when the valve element opening is 0%. Similarly, when the lower end surface of the valve element 13 is at a distance (H-H) from the upper end surface of the central through hole of the valve seat 2, the opening is 100% opening, and as shown in fig. 10, the throttle chamber fluid does not flow.
Fig. 8 is a schematic diagram showing a positional relationship between the spool and the spool cover when the spool opening is 50%. When the valve core 13 is at the middle position of the movable opening, the opening is at the middle position, namely 50% (H-H). At this time, the fluid medium in the buffer cylindrical cavity flows into the small cavity at the lowest end of the valve core sleeve 3 after passing through the central through hole of the valve seat 2, and then enters the next small cavity of the valve core sleeve 3 through a symmetrical groove of the valve core 13. The valve core sleeve 3 is pushed into the last small cavity at the uppermost end of the valve core sleeve 3 in sequence, then flows into the through hole in the side wall of the upper end of the valve core sleeve 3 from the annular groove of the valve core 13, flows out of the through hole in the side wall of the upper end of the valve core sleeve 3 to the annular gap between the valve body 1 and the valve core sleeve 3, and finally flows out of the outlet of the valve body 1.
The valve inner flow channel abrasion characteristic prediction regulation and control process specifically implemented by the invention comprises the following steps:
1) constructing a circulating pipeline loop, arranging liquid phase oil and particles in the circulating pipeline loop, and arranging opposite positions in the middle area of the circulating pipeline loopThe system comprises flanges, a circulating pump, a pressure pump, a circulating pump, a; inlet pressure P with multistage pressure reduction string type liquid level regulating valveinThe pressure is more than or equal to 11.7MPa, and the outlet pressure is 3 MPa;
2) the number of times the fluid in the fluid region between the spool 13 and the spool housing 3 is throttled is defined as a number of stages. The height direction center of a throttle ring of an inner cavity of the valve core sleeve 3 from bottom to top is defined as a horizontal section, and the horizontal section is respectively defined as a first stage of the regulating valve, a second stage of the regulating valve and a third stage of the regulating valve and is represented as a section I, a section II and a section III. Accordingly, the number of stages of the regulating valve represents the number of times the fluid medium inside the regulating valve is throttled. And after throttling from the area above the section III, the fluid flows to four through holes which are circumferentially arranged at the upper part of the valve core sleeve.
3) In the test process, bonding aluminum sheets are respectively fixed at different positions of the inner wall of the valve core sleeve 3 and the outer wall of the valve core 13 at the stage of each regulating valve in the multistage pressure reduction serial liquid level regulating valve, the aluminum sheets are in an annular structure and are arranged on the same circumference, n pressure strain gauges and n flow rate meters are bonded near each aluminum sheet, m flow rate distribution values and n pressure distribution values at different positions of the inner wall of the valve core sleeve 3 and the outer wall of the valve core 13 at different moments are obtained through real-time acquisition and conversion, and a speed field and a pressure field distribution characteristic in a fluid circulation area are obtained; after each group of experiment tests are completed, the wear rate KE of the aluminum sheet is tested based on the scanning of the laser displacement sensorC。
Fig. 11 and 12 show a two-dimensional sectional view of the assembly of the spool and the spool case, and a three-dimensional schematic view of the assembly of the spool and the spool case, respectively. Wherein 3 cylindrical surfaces C are marked on the inner cylindrical surface of the valve core sleeve1、C2、C3The first stage of the regulating valve, the second stage of the regulating valve and the third stage of the regulating valve are respectively corresponding to the first stage of the regulating valve, the second stage of the regulating valve and the third stage of the regulating valve. And annular aluminum sheets are fixedly bonded on the inner wall of the valve core sleeve 3 and the outer wall of the valve core 13 respectively.
4) Adjusting the inlet pressure of the multistage pressure reduction string type liquid level adjusting valve to 11.7MPa, and converting by utilizing the step 3) to obtain n pressure distribution values and m flow velocity components at different positions of different moments of a basin in the adjusting valveDistributing values to obtain the distribution characteristics of a pressure field and a velocity field in the flow field; based on the aluminum sheet abrasion depth obtained by scanning of the laser displacement sensor, the abrasion rate KE is established by combining the density and the abrasion volume of the aluminum sheet for conversionCAnd (4) correlation with pressure distribution and flow velocity distribution. FIG. 13 shows C at a certain opening of the valve core obtained by the test1The profile of the wear depth of the cylindrical surface along its circumferential development. Wherein the length ratio of the ordinate is defined as along C1Height value H in height directionCAnd C1The ratio of the perimeter of the faces is used for determining the height position of the wear failure; the abscissa is the phase angle matched with the end face of the valve core in FIG. 12, and the abrasion failure C is determined1Phase position of the circumferential region of the cylindrical surface.
5) Based on the step 4), keeping the inlet pressure value of the constant regulating valve at 11.7MPa, respectively regulating the opening degrees of different valve cores, such as 0-100% (H-H), and respectively testing the critical areas C when the opening degrees of 10%, 20% and 30% reach 100%1、C2、C3A wear rate distribution map corresponding to the cylindrical expansion surface;
6) sequentially increasing and adjusting inlet pressure P of multistage pressure reduction string type liquid level adjusting valve at fixed pressure intervalinE.g. by mixing PinGradually increasing the pressure to 13.7MPa, 15.7MPa, 17.7MPa and 19.7MPa, and repeating the step 4) and the step 5), respectively drawing key areas C of the inner cylindrical surface of the valve core sleeve in the fluid domains of different levels1、C2、C3Wear rate KE of adhesively bonded aluminum sheetCWith inlet pressure PinA varying discrete data curve;
7) wear rate KE for aluminium sheetCWith inlet pressure PinCarrying out data fitting to obtain a continuous data change curve of the wear rate of the aluminum sheet along with the inlet pressure;
8) the different height positions of the control valve rod 9 are dynamically adjusted, so that the valve core 13 is driven to move up and down, namely the position of the valve core sleeve 3 is opposite to that of the valve core sleeve, and the opening adjustment of the multistage pressure reduction serial liquid level adjusting valve is realized; repeating the step 5), and under the condition of different valve core opening degrees, matching the key area C of the inner cylindrical surface of the valve core sleeve1、C2、C3Testing the wear rate of the bonded and fixed aluminum sheet along with the change of the openness to obtain a discrete data change curve of the wear rate of the aluminum sheet along with the openness of the valve core 13, and further obtaining a continuous data change curve of the wear rate of the aluminum sheet along with the openness of the valve core through data fitting; expanding and obtaining an incidence relation map of the wear rate of the aluminum sheet, the inlet pressure and the valve core opening; FIG. 14 is the corresponding C obtained from the test1The change rule of the maximum abrasion depth of the cylindrical surface along with the opening degree of the valve core, and FIG. 16 is the corresponding C obtained by the test1The maximum abrasion depth of the cylindrical surface is along with the change rule of the inlet pressure.
9) Similarly, repeating the step 7), changing the particle size and the particle concentration, and continuously expanding to obtain an incidence relation map of the wear rate of the aluminum sheet and the inlet pressure, the opening degree of the valve core, the particle size and the particle concentration; FIG. 15 is the corresponding C obtained from the test1The maximum abrasion depth of the cylindrical surface is in accordance with the change rule of the particle size of the particles.
10) Aluminum sheet wear rate KE based on C1 cylindrical surface bonding fixation obtained in step 9)COpening degree X of valve core1Particle diameter X of the particles2Inlet pressure X3The correlation equation of the wear rate and the opening degree of the valve core, the particle size of the particles and the inlet pressure is obtained by fitting, and is expressed as follows:
KEC＝-0.0189X1 2+1.7472X1+0.2571X2+2.5503X3-71.4857
in the formula X2Is particle size in microns, X3Is the inlet pressure in MPa.
Similarly, cylinder C can be solved for2、C3And an incidence relation equation between the wear rate of the aluminum sheet fixed by the cylindrical surface in a bonding way and the openness, particle size and inlet pressure of the valve core.
11) In the dynamic adjustment process, the wear rates tested in the steps 1) to 10) are all corresponding aluminum sheet wear rates, so that the actual valve core materials, such as carbon steel and stainless steel, are respectively subjected to the aluminum sheet wear rate KECOn the basis of the method, a material coefficient W is set to represent the corresponding wear rates of different materials, for example, the wear rate of carbon steel is represented as W1KECThe wear rate of stainless steel is represented by W2KEC(ii) a The present embodiment is described by taking an aluminum sheet as an example. Based on the wear-resistant characteristics (related to material properties) and wear design margin of the aluminum sheet material, a critical wear rate [ epsilon ] is preset]And based on real-time dynamic actual wear rate KE of aluminum sheetCAnd critical wear rate value [ epsilon ]]And (3) comparison:
if KEC＜0.95[ε]The position of the valve rod, the inlet pressure and the opening degree of the valve core are kept unchanged;
if KEC≥0.95[ε]Adjusting the opening degree of the valve core, the inlet pressure, the particle size and the particle concentration, and dynamically updating the actual wear rate value KE of the aluminum sheet material in real timeCUp to KEC＜0.95[ε]To avoid rapid wear failure of the valve core.
Through the valve combined with the processing of the abrasion characteristic prediction regulation process, a correlation relation model between the flow abrasion characteristic of the flow channel in the high-pressure-difference liquid level regulating valve and the influence factors such as the valve core opening, the inlet pressure, the particle size, the particle concentration and the like can be calibrated through variable working condition experimental tests, a dynamic monitoring and regulation of the anti-flow abrasion of the multi-stage pressure-reducing serial liquid level regulating valve based on the critical flow abrasion rate is formed, the dynamic monitoring and regulation of the flow abrasion state of the multi-stage pressure-reducing serial liquid level regulating valve are suitable for the dynamic regulation and control of the flow abrasion state of the multi-stage pressure-reducing serial liquid level regulating valve, and the self-elimination of the flow.
Claims (7)
1. The utility model provides a multistage pressure reduction string formula liquid level control valve structure which characterized in that:
comprises a valve body (1), a valve seat (2), a valve core sleeve (3), a valve cover (12) and a valve core (13); a vertical cavity is arranged in the valve body (1), a valve seat (2) is arranged in the vertical cavity, the vertical cavity in the valve body (1) is divided into a throttling valve core cylindrical cavity at the upper part and a buffering cylindrical cavity at the lower part by the valve seat (2), a central through hole is formed in the valve seat (2), the throttling valve core cylindrical cavity is communicated with the buffering cylindrical cavity by the central through hole, an inlet and an outlet are respectively arranged on two sides of the valve body (1), the inlet is communicated with the bottom of the buffering cylindrical cavity, and the outlet is communicated with the bottom of the throttling valve core cylindrical cavity; a valve core sleeve (3) is fixedly arranged in the throttling valve core cylindrical cavity, an annular gap is formed between the outer wall of the valve core sleeve (3) and the wall surface of the throttling valve core cylindrical cavity, and the annular gap is communicated with an outlet of the valve body (1); the bottom of the valve core sleeve (3) is connected to the valve seat (2), a valve core (13) with a plurality of notches is coaxially arranged in a cavity inside the valve core sleeve (3), and a flow passage is arranged between the valve core (13) and the valve core sleeve (3) to form a multistage series type pressure reduction structure; a valve cover (12) is fixedly installed at the upper port of the valve body (1), a central hole which is coaxially communicated with the throttle valve core cylindrical cavity is formed in the center of the valve cover (12), and the valve core sleeve (3) is axially pressed on the valve seat (2) by the end face around the central hole of the valve cover (12); keep away from case cover (3) upper end lateral wall of disk seat (2) and set up a plurality of through-holes along circumference equipartition, fluid medium flows into the buffering cylinder cavity from valve body (1) entry, flows into throttle case cylinder cavity behind the central through-hole of disk seat (2), fluid medium after throttle step-down in the throttle case cylinder cavity flows out to the annular gap between valve body (1) and case cover (3) in the through-hole of case cover (3) upper end lateral wall equipartition to flow to the export of valve body (1) in the annular gap and flow.
2. The multistage pressure reducing tandem liquid level regulating valve structure according to claim 1, wherein: a valve rod (9) is installed in a center hole of the valve cover (12), and the upper end of the valve core (13) penetrates into the center hole of the valve cover (12) and then is fixedly connected with the lower end of the valve rod (9).
3. The multistage pressure reducing tandem liquid level regulating valve structure according to claim 2, wherein: the guide sleeve (4) is sleeved outside the valve core (13) at the joint of the valve cover (12) and the valve core sleeve (3).
4. The multistage pressure reducing tandem liquid level regulating valve structure according to claim 2, wherein:
annular clearance from the bottom up between valve rod (9) and valve gap (12) centre bore install packing heelpiece (6), filler (7), gland (10) in proper order, the part that gland (10) upper end stretches out behind valve gap (12) centre bore sets up the outward flange, be equipped with ring flange (16) on gland (10), ring flange (16) are through screw rod (8) fixed connection to valve gap (12) upper end, ring flange (16) are compressed tightly on gland (10) through screw rod (8).
5. The multistage pressure reducing tandem liquid level regulating valve structure according to claim 2, wherein:
the multistage tandem type pressure reduction structure between the valve core (13) and the valve core sleeve (3) specifically comprises the following components: a step cavity is arranged in the valve core sleeve (3) below the through hole at the upper end of the valve core sleeve (3), a plurality of inner flanges serving as throttling rings are axially arranged in the step cavity from top to bottom at intervals, and the step cavity is integrally divided into a plurality of small cavities by the throttling rings; the valve core (13) positioned in the valve core sleeve (3) is characterized in that a plurality of symmetrical groove structures are axially arranged from top to bottom, each symmetrical groove structure comprises two grooves which are respectively and symmetrically arranged at two sides of the valve core (13) along a symmetrical direction, and the symmetrical directions of the two grooves of two adjacent symmetrical groove structures are vertical; the inner diameter of the throttle ring is consistent with the outer diameter of the valve core (13), and the width of the groove is larger than the thickness of the throttle ring.
6. The multistage pressure reducing tandem liquid level regulating valve structure according to claim 1, wherein: the valve seat (2) is provided with annular grooves on the upper end surface and the lower end surface, and flange winding pads (15) are installed in the annular grooves for sealing.
7. The multistage pressure reducing tandem liquid level regulating valve structure according to claim 2, wherein: the lower end of the valve rod (9) is coaxially connected with the upper end of the valve core (13) through a connecting sheath (11), and the valve rod (9) drives the valve core (13) to move up and down in the valve core sleeve (3) in the axial direction.
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| CN202110499992.7A CN113108070A (en) | 2021-05-08 | 2021-05-08 | Multistage pressure reduction string type liquid level regulating valve structure |
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| CN202110499992.7A CN113108070A (en) | 2021-05-08 | 2021-05-08 | Multistage pressure reduction string type liquid level regulating valve structure |
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Cited By (2)
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| WO2022237185A1 (en) * | 2021-05-08 | 2022-11-17 | 浙江理工大学 | Method for predicting, regulating and controlling wear characteristic of flow channel in valve |
| CN118009097A (en) * | 2024-04-10 | 2024-05-10 | 蓝帕控制阀门(江苏)有限公司 | Multistage pressure reducing regulating valve |
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Application publication date: 20210713 |