CN115542742A - Jet flow channel window design method, self-operated quick-adjustment control valve and control system - Google Patents
Jet flow channel window design method, self-operated quick-adjustment control valve and control system Download PDFInfo
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Abstract
The invention belongs to the technical field of self-operated valves, and particularly relates to a jet flow channel window design method, a self-operated fast-adjusting control valve and a control system. The jet flow channel window design method comprises the following steps: s1, obtaining the window area A of a single-group jet flow channel under different opening degrees through the following formula j : s2, calculating theoretical calculation flow Q of the control valve under different opening degrees through the following formula j . The design method has the advantage of high design precision, and can effectively improve the product research and development efficiency; the valve core with the jet flow channel window manufactured by the design method can realize accurate feedback regulation of the control valve; meanwhile, by matching with a rotary window type valve core structure component, the unbalanced force borne by the valve core can be greatly improved or even avoided.
Description
Technical Field
The invention belongs to the technical field of self-operated valves, and particularly relates to a jet flow channel window design method, a self-operated fast-adjusting control valve and a control system.
Background
The gas turbine, briefly called as a combustion engine, is a power device for reliable and stable operation of ships and warships, and when the combustion engine is switched among different working condition modes such as normal operation, full-speed propulsion, emergency deceleration and the like, the important precondition is that rapid and accurate automatic feedback adjustment is required to be performed through a self-operated control valve positioned at an inlet of the combustion engine so as to ensure that the pressure at an oil inlet of the combustion engine is stabilized within a specified range value; obviously, the harsh requirements of quick response, accurate adjustment, sensitive action and the like are imposed on the matched control valve.
The structure of the existing control valve is basically a straight-through type, the valve core is coaxial with the valve rod, and the valve core can move up and down along the vertical direction to open and close and adjust the valve, so as to adjust the flow, which is described in patents CN 208687047U, CN 204942674U, CN 213512104U and CN 214037017U. However, as shown in fig. 1, since the flow channel structure of the valve is "S", when the valve is in operation, fluid directly impacts the bottom end face of the valve core, so that the valve core assembly is subjected to a large unbalanced medium force, and the unbalanced force tends to fluctuate irregularly with the change of the opening degree of the valve, so that the fluid state inside the control valve and the force applied to the valve core are unstable and uncertain. Under certain conditions, the adverse factors are even further superposed, so that the existing self-operated control valve is low in design efficiency and low in precision, and meanwhile, a series of problems of severe feedback pressure fluctuation, poor regulation performance, reaction lag, slow regulation and the like exist in practical application, the interlocking shutdown fault of the combustion engine is even caused under extreme working conditions, the service life of the combustion engine is shortened, and the development of a ship power device is severely restricted. In addition, the valve also has the defects of large size and heavy weight, easily causes the problems of large load of an installation pipeline, waste of installation space and the like, and cannot meet the application requirements of miniaturization and light weight of ship equipment. Therefore, a solution is urgently needed.
Disclosure of Invention
One of the purposes of the invention is to overcome the defects of the prior art and provide a jet flow channel window design method, which has the advantage of high design precision and can effectively improve the product research and development efficiency; the valve core with the jet flow channel window manufactured by the design method can realize accurate feedback regulation of the control valve; meanwhile, the valve core is matched with a rotary window type valve core structural component, so that unbalanced force borne by the valve core can be greatly improved and even avoided. Another objective of the present invention is to provide a self-operated fast-adjusting control valve with a compact and reasonable structure, which can specifically and effectively improve or even eliminate the unbalanced force applied to the valve core, thereby greatly simplifying the actual stress condition of the valve core, and finally ensuring the fluid state inside the valve and the stability of the stress of the valve core; the last purpose of the present invention is to provide a control system using the self-operated fast-adjusting control valve, which has the advantages of precise adjustment, fast feedback and stable response.
In order to achieve the purpose, the invention adopts the following technical scheme:
a jet flow channel window design method is characterized by comprising the following steps:
s1, obtaining the window area A of a single-group jet flow channel under different opening degrees through the following formula j ：
In the formula:
j is the opening degree of a single group of jet flow channel window, j =0, 10%, 20%, \ 8230, 100%;
n represents the number of jet holes in the single group of jet flow channel windows;
ɑ j representing the termination angle of each layer of jet hole when the control valve is at different opening degrees;
r i the center line inner diameter of each layer of jet hole is shown;
Δ r represents the width of each layer of jet holes;
s2, calculating theoretical calculation flow Q of the control valve under different opening degrees through the following formula j ：
In the formula:
A 0 denotes the inlet end area of the control valve in cm 2 ；
m represents the number of jet flow channel windows;
Δ P represents the pressure difference between the inlet and outlet of the control valve in kgf/cm 2 ；
ρ represents the density of the medium in g/cm 3 ；
g represents the acceleration of gravity in cm/s 2 。
Preferably, the jet holes are waist-shaped holes with equal width penetrating through the surface of the static valve core, and the jet holes are sequentially arranged along the radial direction of the static valve core, and the axis of a hole pattern curve of each jet hole is coaxial with the static valve core; each jet hole with the hole pattern length sequentially increased from inside to outside is taken as a group of jet flow channel windows which are uniformly distributed around the axis of the static valve core in sequence; the material receiving surface of the static valve core is coaxial and is in fit with a movable valve core in an attaching mode in a rotating mode, the movable valve core is arranged on the static valve core and is used for generating a staggered action with a jet flow channel window so as to open, close and adjust the flow channel fan-shaped holes, and the number of the jet flow channel windows is equal to the number of the fan-shaped holes; on the same group of jet flow channel windows, the end part of the jet hole which is firstly contacted with the fan-shaped hole is taken as the front end of the jet hole, the front end of each jet hole and the contacted fan edge of the fan-shaped hole are positioned on the same radial line of the static valve core, and the rear end of each jet hole is gradually elongated from inside to outside along the radial direction of the static valve core.
Preferably, the self-operated quick-adjusting control valve using the jet flow channel window design method is characterized in that: the valve comprises a valve body, wherein the valve body is provided with a straight cylindrical valve cavity for forming a flow passage, and a static valve core as a static piece is coaxially fixed in the valve cavity; the movable valve core as a movable part is coaxially arranged in the direction of the material receiving surface of the static valve core, and the movable valve core generates an attaching type coaxial rotation action relative to the static valve core under the driving of a power source.
Preferably, a rotating shaft is coaxially and convexly arranged at the material feeding surface of the static valve core, so that coaxial splicing matching is formed between the rotating shaft and a coaxial counter bore concavely arranged at the movable valve core.
Preferably, an arc-shaped guide groove is concavely arranged on the material feeding surface of the static valve core, the extension direction of the arc-shaped guide groove is the same as the hole type length direction of the jet hole, and the axes of curves formed by the arc-shaped guide groove and the hole type length direction are coaxial with each other; the movable valve core is convexly provided with a guide post and axially extends into the arc-shaped guide groove.
Preferably, the feeding surface of the movable valve core is provided with a thrust ball bearing, a bearing seat, an axial spring, a spring seat, a retainer ring and a side cover in sequence from near to far along the axial direction, the coaxial threads of the side cover are matched with the feeding end of the valve cavity, and the side cover and the spring seat as well as the spring seat and the inner wall of the valve cavity are sealed by sealing rings.
Preferably, the power source is used for driving the valve rod to generate reciprocating linear motion along the direction vertical to the axis of the movable valve core; the power source comprises a shell and a diaphragm positioned in the shell, the axis of the valve rod is vertical to the membrane surface of the diaphragm, the top end of the valve rod is fixed on the diaphragm, and the bottom end of the valve rod is provided with a rack so as to form a meshing relationship with the gear-shaped movable valve core; the diaphragm divides the inner cavity of the shell into an upper pressure cavity and a lower pressure cavity, so that the diaphragm is driven to reciprocate by the pressure change of the upper pressure cavity and the lower pressure cavity, and the valve rod is driven to drive the movable valve core to rotate.
Preferably, the top end of the valve rod is provided with a small-diameter section, a shaft shoulder formed by the small-diameter section and the top end of the valve rod is tightly propped against the lower membrane surface of the diaphragm from bottom to top, and the small-diameter section penetrates through the diaphragm and then is sequentially compressed by the diaphragm disc and the fastening nut; the top end of the pressure spring is tightly propped against the top wall of the upper pressure cavity, the bottom of the pressure spring is tightly propped against the spring adjusting seat, and the adjusting screw rod penetrates through the top wall of the upper pressure cavity from outside to inside and is coaxially matched with the screw thread on the spring adjusting seat.
Preferably, the pressure springs are in three groups and are coaxially and uniformly distributed from inside to outside in sequence.
Preferably, the control system of the self-operated quick-adjustment control valve is characterized in that: and a pressure-taking interface is arranged at the lower pressure cavity and is communicated with fluid at a flow passage in the feeding direction through a feedback pipe.
The invention has the beneficial effects that:
1) The design method has very high design precision, greatly improves the product research and development efficiency, fills the blank of theoretical calculation of the valve with the novel structure, and can provide data basis for subsequent research of engineers. The valve core with the jet flow channel window manufactured by the design method can greatly improve the feedback regulation precision of the control valve, and has remarkable effect.
2) Specifically, the valve holes of the movable valve core and the static valve core can be staggered to form an overflowing area, so that the pressure is adjusted. During the design, quiet valve element adopts multilayer efflux runner equipartition structural design, each efflux runner of single runner window department is along radial direction proportional radiation amplification and evenly arranged in proper order from the runner center, overall structure is similar to the wifi shape, the medium jets out from the crisscross hole in edge of wifi distal end during little aperture, the efflux effect of porous equipartition can offset external force each other and make the case atress more even, it is more stable to flow, the crisscross hole of wifi near-end plays flow compensation effect during big aperture, can quick accurate regulated pressure, make the feedback in time, the emergence of phenomena such as combustion engine import department pressure fluctuation, hysteresis has been avoided to stability. In addition, compared with the existing control valve, the multilayer jet flow channel structure has a multilayer flow dividing effect and further generates a porous jet effect, the medium is sucked and mixed behind the valve to form a plurality of strong shearing energy dissipation areas, so that the scouring of the medium to the internal parts of the valve is greatly reduced, the phenomenon is more obvious in small opening degree, the medium is seriously eroded to a valve seat and a valve core in the existing control valve in small opening degree, even cavitation occurs under extreme working conditions, and the service life of the valve is shortened.
3) The invention realizes the structural design of self-tightening sealing by arranging the movable valve core on the material feeding surface of the static valve core. When the valve is in a closed state, the pressure of the fluid medium tightly attaches the movable valve core to the static valve core to generate a self-tightening sealing effect, so that the leakage amount of the closed control valve is extremely small. Simultaneously, in the control process, the movable valve core slides around the axis of the flow passage and the static valve core in a rotating way just like doing self-grinding, so that the leakage amount can be ensured for a long time, and the movable valve core has the advantages of good sealing property, simple structure and small maintenance workload.
4) The two valve cores of the invention are both designed by adopting a structure with multiple jet flow channel windows uniformly distributed, so that the motion of the valve rod in unit stroke can trigger the linkage of the multiple strokes of the valve cores. Taking four groups of jet flow channel windows as an example, the movable valve cores of the four fan-shaped holes can be linked with the static valve cores of the four groups of jet flow channel windows at the moment, and the four windows can be adjusted simultaneously; compared with the traditional control valve, the adjusting stroke of the invention only accounts for 1/4 of the prior structure under the condition of the same parameters, and the invention has the advantages of short adjusting stroke, high response speed, accuracy and stability, and can realize quick response and accurate adjustment under the working condition of small opening.
5) On the basis of the valve core structure, the valve core of the existing self-operated control valve is considered to be complex in stress, and the valve core assembly is subjected to unbalanced force and instantaneous impact of unsteady fluctuation in the whole movement process besides the self gravity and friction of the valve core assembly; during design, engineers usually ignore transient impact action and simplify fluctuating unbalanced force into a constant value for processing, so that a series of problems of poor regulating performance, serious pressure fluctuation, reaction lag and the like exist in the actual working process of the control valve. Compared with the prior art, the valve adopts a direct-flow structural design, the movable valve core rotates around the center of the flow channel in a reciprocating manner, the whole set of valve core is not interfered by gravity in the motion process, the porous surrounding and uniformly distributed structures of the valve hole can also mutually counteract the acting force of fluid, the fluid is prevented from being impacted, and the unbalanced force is 0; that is to say, the dynamic valve core and the static valve core of the invention only need to be acted by a small friction force in the whole movement process, thereby greatly simplifying the stress condition of the corresponding valve core, ensuring the fluid state in the valve and the stability of the stress of the valve core, and having the advantages of accurate adjustment, rapid feedback and stable response.
6) The valve rod and the movable valve core are designed in an eccentric structure, the valve rod and the movable valve core are not on the same plumb line, and the height of the valve is greatly reduced after the valve rod and the movable valve core are comprehensively accumulated and overlapped by matching with the multi-window design. In addition, the whole valve can adopt a compact butt clamp type structure for connection, has the advantages of small volume and light weight, is easy to install, and can further meet the design requirements of miniaturization and light weight.
7) The valve rod drives the movable valve core to do rotary motion around the axis of the flow passage in a gear-rack meshing mode, and the controllability of the action stroke of the movable valve core can be ensured by matching the guide post and the arc-shaped guide groove. Meanwhile, in the whole movement process of the movable valve core, only the rotary friction force caused by the spring force of the medium and the axial spring is applied to the movable valve core, the sealing surfaces of the movable valve core and the static valve core can be ground before assembly, the thrust ball bearing ensures that the movable valve core is not interfered by other external force when rotating, and the self-lubricating property of the fuel medium is added, so that the rotary friction force is very little, the actual service life of the control valve can be greatly prolonged, and the effect is remarkable.
Drawings
FIG. 1 is a schematic diagram of a conventional self-operated control valve;
FIG. 2 is a schematic structural diagram of a self-operated quick-adjustment control valve according to the present invention;
FIG. 3 is a schematic view of the engagement of the movable valve core, the movable valve core and the valve rod;
FIG. 4 is a diagram of the matching state of the movable valve core and the static valve core when the flow channel is in the fully opened state;
FIG. 5 is a diagram showing the engagement of the movable valve element and the stationary valve element in the half-open state of the flow passage;
FIG. 6 is a diagram showing the engagement of the movable valve element and the stationary valve element when the flow passage is closed;
FIG. 7 is a force diagram of the self-operated quick-adjustment control valve of the present invention;
FIG. 8 is an assembly view of the components within the valve chamber;
FIG. 9 is a schematic diagram of the control system of the present invention;
FIG. 10 is a graph of the comparative analysis of the opening degree and the unbalanced force applied to the valve core of the conventional self-operated control valve and the present invention under DN200 caliber;
FIG. 11 is a theoretical model of the jet flow channel window of the present invention;
fig. 12 is a pressure cloud and a velocity cloud with the control valve at 80% open.
The actual correspondence between each label and the part name of the invention is as follows:
a-an upper pressure chamber; b-a lower pressure chamber;
10-a valve body; 20-a static valve core; 21-jet hole; 22-arc guide groove;
30-a movable valve core; 31-a fan-shaped hole; 32-a guide post;
40-a power source; 41-a housing; 42-a membrane sheet; 43-a membrane disc; 44-a fastening nut;
45-pressure spring; 46-a spring adjustment seat; 47-adjusting screw; 48-pressure taking interface;
49-a feedback tube;
50-a rotating shaft; 61-thrust ball bearing; 62-a bearing seat; 63-an axial spring;
64-spring seats; 65-a retainer ring; 66-side cover; 67-sealing ring;
70-a valve stem; 71-rack.
Detailed Description
For ease of understanding, the specific construction and operation of the present invention is further described herein with reference to FIGS. 1-12:
the design method of the present invention is embodied by the following example 1:
example 1:
in this embodiment 1, a DN100 aperture control valve is taken as an example, and is matched with a wifi-shaped jet hole 21 shown in fig. 11, and a jet flow channel window formed by the jet hole 21 is a four-window uniform distribution structure.
At this time, the number of the jet holes of the single group of jet flow channel windows is 7, that is, m =4, n =7, the width Δ r of the jet hole 21 =5mm, and three typical opening degrees of j =20%, j =50%, and j =80% are selected for flow calculation of the control valve.
When the opening is 20%, that is, j =20%, the flow area of the window of the single-group jet flow channel is calculated according to fig. 11 and the following formula, where the upper and lower limit ranges of the double integral interval are respectively as follows:
substituting the boundary condition into an equation to obtain:
i.e. 20% open, the single set of fluidic channel window areas a of the control valve 20％ ＝0.52cm 2 。
Subsequently, the flow calculation formula for the control valve at different opening degrees is obtained as follows:
in the formula:
Q j m represents the theoretical calculated flow of the control valve under different opening degrees 3 /h；
A 0 Denotes the area of the inlet end of the control valve in cm 2 ；
m represents the number of control valve multilayer jet flow channel groups (m =1, 2, 3 \8230; etc.);
Δ P represents the pressure difference between the inlet and outlet of the control valve, and is 100kgf/cm 2 ；
Rho represents the density of the medium and is 1g/cm 3 ；
g represents gravity acceleration, and is 981cm/s 2 ；
According to the design parameters, A 0 ＝Π/4*DN 2 ＝78.5cm 2 Obtaining:
establishing three-dimensional flow channel modeling for the control valve with the opening degree of 20%, and performing numerical simulation calculation by adopting a fluid mechanics method to obtain a simulated flow value of 3.5m 3 /h。
Similarly, the calculated flow and the simulated flow of the control valve at the opening degrees of 50% and 80% are respectively calculated according to the above process, and the pressure cloud chart and the speed cloud chart at the opening degree of 80% of the control valve are shown in fig. 12, which are not described again here; the relative error between theoretical and simulated flow was calculated simultaneously and the results are shown in table 1:
TABLE 1DN100 orifice control valve typical opening degree lower flow coefficient and error
And (4) conclusion: as can be seen from table 1, the calculated flow and the simulated flow of the control valve gradually increase with the increase of the opening, and the simulated flow value at the typical opening is larger than the calculated flow value, which is caused by the local simplification of the model during the numerical simulation and neglecting the influence of the factors such as roughness on the flow. In addition, the relative error between the calculated flow and the simulated flow is about 8%, and the correctness of theoretical design is verified within the range allowed by engineering error and technical requirements.
Therefore, the design method provided by the invention has very high design precision, greatly improves the product research and development efficiency, fills the gap of theoretical calculation of the valve with the novel structure, and provides a data basis for subsequent research of engineers.
On the basis of the above design method, the present invention provides an improved control valve structure, specifically as shown in fig. 2 to 9, in which the main body portion includes an adjustment mechanism and a control mechanism constituting the power source 40, wherein:
the adjusting structure is a main valve component and comprises a valve body 10, a valve rod 70, a movable valve core 30, a static valve core 20, a corresponding pressure adjusting unit and the like. During assembly, as shown in fig. 2-3, the valve rod 70 and the movable valve core 30 are in meshing transmission through a gear and a rack; when the valve rod 70 reciprocates up and down along the axial direction, the movable valve core 30 is driven to reciprocate and rotate around the axis of the flow passage. In practical design, as shown in fig. 2, an O-ring is sleeved on the valve rod 70 to ensure that the pressure between the lower pressure chamber b and the valve chamber does not interfere with each other.
As for the pressure adjusting unit, as shown in fig. 7 to 8, it includes a side cover 66, a retainer ring 65, a spring seat 64, an axial spring 63, a bearing seat 62 and a thrust ball bearing 61 arranged in this order from left to right. As can be seen from fig. 8, the stationary valve element 20 is fixed in the valve chamber by the positioning pin, and the stationary valve element 20 and the thrust ball bearing 61 cooperate with each other to hold the movable valve element 30, with the movable valve element 30 closely attached to the stationary valve element 20. To avoid media leakage, sealing rings 67 are arranged between the outer annular surface of the spring seat 64 and the inner wall of the valve chamber and between the side cover 66 and the inner annular surface of the spring seat 64.
During assembly, the static valve core 20 is arranged in the middle of the valve cavity and fixedly connected with the valve body 10 into a whole through a positioning pin, and the movable valve core 30 is coaxially attached to the static valve core 20 through the rotating shaft 50 and is meshed with the rack 71 at the valve rod 70 through a gear and a rack. The thrust ball bearing 61 is arranged in the bearing seat 62 and is abutted with the material coming surface of the movable valve core 30. The axial springs 63 are uniformly distributed in the spring seat 64, and the spring seat 64 is coaxially arranged in the valve cavity and sealed by means of an O-shaped ring. The retainer ring 65 can be an elastic retainer ring and is clamped into a groove preset at the material inlet end of the valve body 10, so that the spring seat 64 is attached to the bearing seat 62, and an initial pre-tightening force can be provided for the movable valve element 30. The side cover 66 is threadedly coupled to the valve body 10.
As shown in fig. 3, when the present invention is operated, the valve rod 70 reciprocates in the vertical axial direction to drive the movable valve element 30 to reciprocate around the fluid passage rotating shaft 50, and the windows of the movable valve element 30 and the stationary valve element 20 are staggered to form a fluid passage for realizing flow rate regulation. The static valve core 20 is provided with a semi-countersink-shaped arc-shaped guide groove 22 on one surface attached to the dynamic valve core 30, namely the material feeding surface of the static valve core 20, so that the motion stroke of the dynamic valve core 30 is limited through the guide action of a guide post 32 on the dynamic valve core 30, and the dynamic valve core 30 is ensured to work in a preset stroke.
Taking the four-window structure shown in fig. 2-6 as an example, in the whole movement process of the present invention, the moving valve core 30 is not affected by gravity, because the valve hole uniform distribution scheme of the present invention can make the impact effect of the fluid converge at the fan-shaped holes 31 of the moving valve core 30, and mutually collide and offset due to the matching action of one set of fan-shaped holes 31 and multiple sets of jet holes 21, and the moving valve core 30 only receives the friction force generated when the medium force and the spring force act on the end surface and rotate with the static valve core 20; meanwhile, multi-window designs such as four windows also have multi-level flow distribution effects, so that a porous jet effect is generated, the medium is sucked and mixed behind the valve to form a plurality of strong-shearing energy dissipation areas, and the scouring effect of the medium on the rear inner wall of the valve is effectively reduced.
During specific design, on the same group of jet flow channel windows, the end part of the jet hole 21 which is firstly contacted with the fan-shaped hole 31 is the front end of the waist-shaped hole-shaped jet hole 21, the front end of each jet hole 21 and the contacted fan edge of the fan-shaped hole 31 are both positioned on the same radial line of the static valve core 20, and the rear end of each jet hole 21 is gradually elongated from inside to outside along the radial direction of the static valve core 20; that is, the hole widths and the intervals of the jet holes 21 are not changed, but the lengths thereof are sequentially increased in the rotation direction of the movable valve body 30, and the overall structure is formed in a shape similar to a shape in which wifi is inclined to one side. When the guide post 32 of the movable valve core 30 moves in the arc-shaped guide groove 22 of the static valve core 20, the valve holes at the two groups of valve cores naturally generate an interlaced fluid channel, and finally, the adjusting effect as shown in fig. 4-6 is realized.
The control mechanism mainly comprises a diaphragm 42, a pressure spring 45, an adjusting screw 47, a pressure taking port 48 and the like. During assembly, as shown in fig. 2, the whole set of control structure may be disposed in a cavity of the housing 41 formed by flange-fitting the upper cover and the valve body 10, and the cavity of the housing 41 may be divided into an upper pressure chamber a and a lower pressure chamber b by the diaphragm 42, and the lower pressure chamber b is communicated with a flow passage in the incoming material direction, that is, an inlet of the combustion engine, through the pressure tapping port 48 and the feedback pipe 49. The top end of the valve rod 70 is provided with a small diameter section, the small diameter section and a shaft shoulder formed at the top end of the valve rod 70 tightly support the lower membrane surface of the diaphragm 42 from bottom to top, and the small diameter section penetrates through the diaphragm 42 and then is sequentially compressed by the diaphragm disc 43 and the fastening nut 44. The top end of the pressure spring 45 abuts against the top wall of the upper pressure cavity a, the bottom of the pressure spring 45 abuts against the spring adjusting seat 46, the adjusting screw 47 penetrates through the top wall of the upper pressure cavity a from outside to inside and is coaxially in threaded fit with the spring adjusting seat 46, and online control of the spring force of the control mechanism can be achieved by rotating the adjusting screw 47. The spring adjustment seat 46 itself may be formed from multiple pieces and will not be described in detail herein.
In practice, the diaphragm 42 is stressed as shown in FIG. 9, and the valve core is stressed as shown in FIG. 7. At this time, the pressure P1 at the inlet of the internal combustion engine is introduced to the lower pressure chamber b of the control mechanism through the feedback pipe 49, the pressure acting below the diaphragm 42 generates a vertically upward medium force F1 as shown in fig. 9, and a spring force F2 is exerted above the diaphragm 42.
When the pressure P1 at the inlet of the combustion engine is reduced, F1 is less than F2, the pressure spring 45 drives the diaphragm 42 and the valve rod 70 to move downwards, at the moment, the movable valve core 30 rotates around the axis of the flow channel, the valve holes are staggered, and the area of staggered windows is gradually reduced, so that the purpose of increasing the pressure P1 at the inlet of the combustion engine is achieved;
vice versa, when the pressure P1 at the inlet of the combustion engine increases, and F1 is greater than F2, the pressure spring 45 drives the diaphragm 42 and the valve rod 70 to move upwards, at the moment, the movable valve core 30 rotates around the axis of the flow channel, and the valve holes are staggered and gradually increase the area of staggered windows, so that the purpose of reducing the pressure P1 at the inlet of the combustion engine is achieved;
the system has the advantages of repeated and quick response and accurate adjustment, and can ensure that the pressure at the inlet of the combustion engine is stabilized within a designed range value, thereby ensuring the safe, reliable and stable operation of the system.
Fig. 7 is a schematic diagram of unbalanced force stress according to the present invention, the movable valve element 30 rotates around the center of the flow channel in a reciprocating manner, the fluid medium goes straight in and goes straight out, the movable valve element 30 is not disturbed by gravity in the movement process, the multi-layer jet flow channel structure can mutually counteract the acting force of the fluid, so as to avoid the impact of the fluid, and the unbalanced force Fb' =0 applied to the control valve greatly simplifies the stress condition of the valve element, and has the advantages of accurate adjustment, rapid response, and stable feedback.
For comparison, fig. 1 also shows a force diagram of a conventional self-operated control valve; the valve flow channel structure is in an S shape, fluid directly impacts and acts on the end face of the bottom of the valve core, so that the valve core assembly is subjected to large medium unbalanced force, and the unbalanced force is in an unsteady fluctuation trend along with the change of the valve opening. At present, when an engineering technician calculates an unbalanced force Fb, the unbalanced force Fb is calculated by simplifying the unbalanced force Fb into a constant value according to an industry design manual, and errors caused by fluctuation of front and rear differential pressures of a control valve under different opening degrees are not considered, so that a series of problems such as severe pressure fluctuation, reaction lag, poor regulation performance and the like often exist in the actual working process of the control valve; the calculation formula is shown as follows:
in the formula:
fb represents the unbalanced force, in N;
ds represents the stem diameter in mm;
dg represents spool diameter in mm;
p1 represents the upstream pressure in mPa;
p2 represents the downstream pressure in mPa.
Further, for illustration, the present invention shown in fig. 7 and the existing control valve shown in fig. 1 are compared and analyzed for unbalanced force of the valve core under DN200 caliber, so as to obtain an intuitive comparison under the same parameter caliber, which is specifically shown in fig. 10.
In fig. 10, it is evident that:
the unbalanced force of the existing control valve in the whole adjusting stroke tends to fluctuate unsteadily. As shown in fig. 10, the low-inlet and high-outlet type, that is, the existing flow-off type, gradually reduces the unbalanced force and then becomes stable as the opening degree increases; the high-inlet low-outlet type also has the advantages that the existing flow-opening type is increased along with the opening, the unbalanced force is gradually reduced to 0, then the direction is changed and is gradually increased, the unbalanced force interferes with the motion of the valve core, the feedback pressure fluctuation is caused, and the adjusting performance is poor.
According to the invention, the valve internal part structure is balanced by changing the relationship between the motion mode of the valve core and the fluid acting force, and the fluid acting force is counteracted by energy dissipation, as shown in fig. 10, at the moment, the unbalanced force borne by the valve core in the motion process is always 0, obviously, the stress condition of the valve core is greatly simplified, and the adjustment is effective and accurate.
It will, of course, be evident to those skilled in the art that the invention is not limited to the details of the foregoing illustrative embodiments, but rather includes the same or similar structures that may be embodied in other specific forms without departing from the spirit or essential characteristics thereof. The present embodiments are therefore to be considered in all respects as illustrative and not restrictive, the scope of the invention being indicated by the appended claims rather than by the foregoing description, and all changes which come within the meaning and range of equivalency of the claims are therefore intended to be embraced therein. Any reference sign in a claim should not be construed as limiting the claim concerned.
Furthermore, it should be understood that although the present description refers to embodiments, not every embodiment may contain only a single embodiment, and such description is for clarity only, and those skilled in the art should integrate the description, and the embodiments may be combined as appropriate to form other embodiments understood by those skilled in the art.
The techniques, shapes, and configurations not described in detail in the present invention are all known techniques.
Claims (10)
1. A jet flow channel window design method is characterized by comprising the following steps:
s1, obtaining the window area A of a single group of jet flow channels under different opening degrees through the following formula j ：
In the formula:
j is the opening degree of a single-group jet flow channel window, and j =0, 10%, 20%, 8230100%;
n represents the number of jet holes (21) in the single group of jet flow channel windows;
ɑ j representing the termination angle of each layer of jet holes (21) of the control valve under different opening degrees;
r i represents the center line inner diameter of each layer of jet holes (21);
Δ r represents the width of each layer of jet holes (21);
s2, calculating theoretical calculation flow Q of the control valve under different opening degrees through the following formula j ：
In the formula:
A 0 denotes the area of the inlet end of the control valve in cm 2 ；
m represents the number of jet flow channel windows;
Δ P represents the pressure difference between the inlet and outlet of the control valve in kgf/cm 2 ；
ρ represents the density of the medium in g/cm 3 ；
g represents the acceleration of gravity in cm/s 2 。
2. The method of claim 1 for designing a fluidic flow channel window, wherein: the jet holes (21) are waist-shaped holes with equal width and penetrate through the surface of the static valve core (20), the jet holes (21) are sequentially arranged along the radial direction of the static valve core (20), and the axis of a hole pattern curve of each jet hole (21) is coaxial with the static valve core (20); each jet hole (21) with the hole type length sequentially increased from inside to outside is used as a group of jet flow channel windows which are sequentially and uniformly distributed around the axis of the static valve core (20); the feeding surface of the static valve core (20) is coaxially and in a fit type, a movable valve core (30) is in rotary fit with the feeding surface, the movable valve core (30) is arranged and used for generating a mismatch action with a jet flow channel window so as to open, close and adjust a flow channel fan-shaped hole (31), and the number of the jet flow channel windows is equal to that of the fan-shaped holes (31); on the same group of jet flow channel windows, the end part of the jet hole (21) which is firstly contacted with the fan-shaped hole (31) is taken as the front end of the jet hole (21), the front end of each jet hole (21) and the contacted fan edge of the fan-shaped hole (31) are positioned on the same radial line of the static valve core (20), and the rear end of each jet hole (21) is gradually elongated from inside to outside along the radial direction of the static valve core (20).
3. The self-operated fast-adjusting control valve using the jet flow channel window design method of claim 2, characterized in that: the valve comprises a valve body (10), wherein the valve body (10) is provided with a straight cylindrical valve cavity for forming a flow passage, and a static valve core (20) as a static piece is coaxially fixed in the valve cavity; the moving valve core (30) which is used as a moving piece is coaxially arranged in the direction of the material feeding surface of the static valve core (20), and the moving valve core (30) generates a joint type coaxial rotating action relative to the static valve core (20) under the driving of a power source (40).
4. The self-operated fast-adjusting control valve of the jet flow channel window design method according to claim 3, characterized in that: a rotating shaft (50) is coaxially and convexly arranged at the feeding surface of the static valve core (20), so that coaxial splicing matching is formed between the rotating shaft and a coaxial counter bore concavely arranged at the movable valve core (30).
5. The self-operated fast-adjusting control valve of the jet flow channel window design method according to claim 3, characterized in that: an arc-shaped guide groove (22) is concavely arranged on the feeding surface of the static valve core (20), the extension direction of the arc-shaped guide groove (22) is in the same direction with the hole type length direction of the jet hole (21), and the axes of curves formed by the arc-shaped guide groove and the hole type length direction are coaxial with each other; the movable valve core (30) is convexly provided with a guide post (32) and axially extends into the arc-shaped guide groove (22).
6. The self-operated fast-adjusting control valve of the jet flow channel window design method according to claim 3, 4 or 5, characterized in that: the feeding surface of the movable valve core (30) is provided with a thrust ball bearing (61), a bearing seat (62), an axial spring (63), a spring seat (64), a retainer ring (65) and a side cover (66) in sequence from near to far along the axial direction, the coaxial threads of the side cover (66) are matched with the feeding end of the valve cavity, and the side cover (66) and the spring seat (64) and the inner wall of the valve cavity are sealed by sealing rings (67).
7. The self-operated fast-adjusting control valve of the jet flow channel window design method according to claim 3, 4 or 5, characterized in that: the power source (40) is used for driving the valve rod (70) to generate reciprocating linear motion along the axial direction of the vertical movable valve core (30); the power source (40) comprises a shell (41) and a diaphragm sheet (42) positioned in the shell (41), the axis of the valve rod (70) is vertical to the membrane surface of the diaphragm sheet (42), the top end of the valve rod is fixed on the diaphragm sheet (42), and the bottom end of the valve rod (70) is provided with a rack (71) so as to form a meshing relation with the gear-shaped movable valve core (30); the diaphragm (42) divides the inner cavity of the shell (41) into an upper pressure chamber (a) and a lower pressure chamber (b), so that the diaphragm (42) is driven to reciprocate by means of pressure changes of the upper pressure chamber (a) and the lower pressure chamber (b), and the valve rod (70) is driven to drive the movable valve core (30) to rotate.
8. The self-operated fast-adjusting control valve of the jet flow channel window design method according to claim 7, characterized in that: the top end of the valve rod (70) is provided with a small-diameter section, a shaft shoulder formed by the small-diameter section and the top end of the valve rod (70) is tightly propped against the lower membrane surface of the diaphragm (42) from bottom to top, and the small-diameter section penetrates through the diaphragm (42) and then is sequentially compressed by the diaphragm disc (43) and the fastening nut (44); the top end of the pressure spring (45) abuts against the top wall of the upper pressure cavity (a), the bottom of the pressure spring (45) abuts against the spring adjusting seat (46), and the adjusting screw rod (47) penetrates through the top wall of the upper pressure cavity (a) from outside to inside and is in threaded fit with the spring adjusting seat (46) coaxially.
9. The self-operated fast-adjusting control valve of the jet flow channel window design method according to claim 8, characterized in that: the pressure springs (45) are divided into three groups and are coaxially and uniformly distributed from inside to outside in sequence.
10. The control system of the self-operated quick-adjustment type control valve according to claim 7, wherein: and a pressure taking interface (48) is arranged at the lower pressure cavity (b), and the pressure taking interface (48) is communicated with fluid at a flow passage in the feeding direction through a feedback pipe (49).
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202211277548.1A CN115542742A (en) | 2022-10-19 | 2022-10-19 | Jet flow channel window design method, self-operated quick-adjustment control valve and control system |
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| CN202211277548.1A CN115542742A (en) | 2022-10-19 | 2022-10-19 | Jet flow channel window design method, self-operated quick-adjustment control valve and control system |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN116756855A (en) * | 2023-08-14 | 2023-09-15 | 中国空气动力研究与发展中心低速空气动力研究所 | Design method of airborne jet control valve, control valve and jet actuating system |
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2022
- 2022-10-19 CN CN202211277548.1A patent/CN115542742A/en active Pending
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN116756855A (en) * | 2023-08-14 | 2023-09-15 | 中国空气动力研究与发展中心低速空气动力研究所 | Design method of airborne jet control valve, control valve and jet actuating system |
| CN116756855B (en) * | 2023-08-14 | 2023-10-20 | 中国空气动力研究与发展中心低速空气动力研究所 | Design method of airborne jet control valve, control valve and jet actuating system |
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