CN117807725A - Design and flow calculation method of parabolic valve core in flow regulating valve - Google Patents
Design and flow calculation method of parabolic valve core in flow regulating valve Download PDFInfo
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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
- F16K1/02—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 with screw-spindle
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
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- 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
- F16K1/38—Valve members of conical shape
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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
- F16K1/42—Valve seats
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Abstract
The invention belongs to the technical field of fluid regulating valves, and discloses a design and flow calculation method of a parabolic valve core in a flow regulating valve. The method comprises the following steps: s1, constructing a relational expression of flow areas of corresponding flow regulating valves under different valve core displacements; s2, constructing a geometric relation of the flow area according to the geometric structures of the throttle valve and the valve core, and obtaining a relation satisfied by the cross section molded line of the valve core; s3, dispersing the displacement ratio into a plurality of values, calculating to obtain corresponding flow areas of different displacement ratios, calculating coordinates of points on the valve core molded surface at different displacement ratios, fitting the points on the valve core molded surface at all displacement ratios into parabolas, and rotating the parabolas around the central axis of the valve core for one circle to obtain the required revolution paraboloid curve of the valve core. The invention also discloses application of the method. The invention solves the problem of deformation of the valve rod under the radial impact force of fluid and the problem of inconsistent flow adjustment resolution of different valve rod positions of the regulating valve.
Description
Technical Field
The invention belongs to the technical field related to fluid regulating valves, and particularly relates to a design and flow calculation method of a parabolic valve core in a flow regulating valve.
Background
In the field of fluid control, it is common to refer to devices for regulating the flow of a fluid, such as a refrigerant in an industrial plant refrigeration system. The refrigerant plays a key heat exchange role in the refrigeration system, the size of the refrigerant flow is required to be changed according to different equipment temperatures so as to adjust the refrigeration effect, equipment is prevented from being invalid or even damaged due to high temperature, and the adjustment and control precision of the refrigerant flow directly influence the safety of industrial equipment. Carbon dioxide is used as a natural medium, is environment-friendly, nontoxic and pollution-free, has the advantages of high density, low viscosity, small flow loss, good heat transfer effect and the like in a supercritical state, and more importantly, the supercritical carbon dioxide has large latent heat and high phase-to-phase heat exchange, so that higher heat exchange efficiency and better cooling performance can be realized. Carbon dioxide is therefore widely used in refrigeration systems as a new refrigerant.
In the patent publication CN101655173a, a regulating valve, particularly for regulating the flow of a fluid of a refrigeration system, is disclosed, which inserts a valve body into a connection opening of a pipe, and a piston is driven by a motor to adjust between an open position and a blocking position of the connection opening, while having a plurality of small holes in a front surface of the piston to balance the pressure of the fluid applied to the front surface. The flow passage of the flow regulating valve is complex, and turbulence is easy to generate when carbon dioxide flows through the small hole at the piston of the regulating valve, so that larger pressure loss is caused, uncontrollable phase change of the carbon dioxide is caused, and the flow regulating precision and the refrigerating effect are affected. And thus is not suitable for flow regulation of carbon dioxide media.
An adjustable cavitation venturi for a flow-regulating device is disclosed in patent CN113175532a, such a flow-regulating valve comprising a venturi, a differential pressure displacement sensor, a driving mechanism and a controller. The valve core passes through the flow channel and is abutted against the induction end of the differential pressure variable displacement sensor, and the driving mechanism is arranged at the other end of the valve core. The controller enables the driving mechanism to drive the valve core to move, and meanwhile, the displacement sensor is utilized to acquire the position information of the valve core in real time, so that closed-loop control of valve core displacement is realized. The invention patent CN112211751A also discloses an adjustable venturi pipe device, the adjustable venturi pipe divides the valve body into two parts, the first valve body is used for fixing the driving motor, the first section of the valve rod is connected with the driving motor, the second section of the valve rod is cylindrical, the valve rod passes through the first valve body to enter the flow passage, the third section of the valve rod is conical and can be inserted into the venturi pipe of the second valve body, and the valve core is axially moved by the driving motor to realize the control of the fluid flow.
The venturi flow regulator reduces the pressure of fluid in the throat through the contraction and expansion structure to produce cavitation area, which can isolate the influence of downstream pressure fluctuation on upstream pressure and maintain stable flow. However, in the above two kinds of adjustable venturi flow rate adjusting devices, firstly, the device only depends on the limiting mechanism or the through hole on the valve body to support the valve rod, so that when fluid flows in from the inlet on the side surface of the valve body, a relatively slender structure of the valve rod can generate relatively large radial impact force on the valve rod, so that the valve rod is deformed, and further the valve rod deviates from the axis position at the venturi throat, the symmetry of the valve port flow area and the flow channel is changed, and even the valve rod is blocked and cannot work. Secondly, the valve rod of the adjusting device is designed into a cone shape, the minimum flow area of the valve port of the venturi tube and the displacement of the valve rod are in nonlinear relation, so that the flow adjustment resolutions of different valve rod positions are inconsistent, the high-precision adjustment of the flow adjusting device is not facilitated, and therefore, the flow adjusting valve with the flow area linearly changed along with the displacement of the valve core is required to be designed so as to improve the flow control precision. The flow calculation formula of the existing flow regulating valve is as follows:
wherein Q is m For mass flow, C d The flow coefficient, A, is the flow area, ΔP is the difference between the inlet pressure and the saturated vapor pressure, ρ is the fluid density. Therefore, when the flow area is linearly changed along with the valve core displacement, the mass flow is also in a linear relation with the valve core displacement, and the accurate control of the flow is facilitated. However, the flow formula is only suitable for ideal incompressible fluid, and for carbon dioxide, the medium has strong compressibility in a supercritical state, physical properties of the medium can also change drastically when the medium flows through a venturi-type pipeline flow regulating valve, and a traditional mass flow calculation method is not suitable for the flow regulating valve, so that the control accuracy of the flow regulating valve is greatly influenced. Accordingly, there is a need for an apparatus and method that addresses the above-described problems.
Disclosure of Invention
Aiming at the defects or improvement demands of the prior art, the invention provides a design and flow calculation method of a parabolic valve core in a flow regulating valve, which solves the problem of deformation of a valve rod under the radial impact force of fluid and the problem of inconsistent flow regulating resolution of different valve rod positions of the regulating valve.
In order to achieve the above object, according to one aspect of the present invention, there is provided a design method of a parabolic valve spool in a flow rate adjusting valve, the method comprising the steps of:
s1, setting the displacement ratio of a valve core in a regulating valve, and constructing a relational expression between the flow area and the valve core displacement in the flow regulating valve and boundary conditions met when the valve core is at the maximum displacement and the minimum displacement in the flow regulating valve, so as to obtain relational expressions of the flow areas of the corresponding flow regulating valves under different valve core displacements;
s2, constructing a geometric relation of the flow area according to the geometric structures of the throttle valve and the valve core, and obtaining a relation satisfied by the cross section molded line of the valve core from the geometric relation of the flow area;
s3, dispersing the displacement ratio into a plurality of values, calculating by utilizing a relational expression of the corresponding flow area under the displacement of the valve core obtained in the step S1 to obtain the corresponding flow area of different displacement ratios, carrying the flow area into the cross section molded line calculation of the valve core in the step S2 to obtain the coordinates of points on the molded surface of the valve core at different displacement ratios, fitting the points on the molded surface of the valve core under all displacement ratios into parabolas, and obtaining the required revolution paraboloid curve of the valve core by rotating the parabolas around the central axis of the valve core for one circle.
Further preferably, in step S1, the relation between the flow area and the spool displacement is performed as follows:
wherein A is the flow area; x is the displacement of the valve core; k. b are all linear characteristic parameters, A max Is the maximum flow area.
Further preferably, in step S1, the boundary conditions are performed as follows:
wherein A is min 、A max 、x min 、x max The valve is respectively a minimum flow area, a maximum flow area, a minimum valve core displacement and a maximum valve core displacement.
Further preferably, in step S1, the relationship between the flow areas of the corresponding flow rate regulating valves at different spool displacements is as follows:
A＝[(t-1)·k+1]·A max
wherein A is the flow area; t is the displacement ratio, i.e. the ratio of the current valve core displacement to the maximum valve core displacement; k is a linear characteristic parameter, amax is a maximum flow area.
Further preferably, the expression that the envelope satisfies is performed as follows:
where f (l, α) is an equal area curve equation,l is the radial distance between the point on the valve core molded surface and the throat; alpha is the included angle between the perpendicular line formed by any point on the intersection line of the contraction section of the venturi flow channel and the throat and the valve core molded surface and the plane where the intersection line is located; d is the throat diameter; a is the flow area.
According to another aspect of the present invention, there is provided a valve core obtained by the method described above, the front end of the valve core being a paraboloid of revolution.
According to a further aspect of the present invention, there is provided a flow regulating valve having the valve core described above, the flow regulating valve comprising a linear motor, a main body, a valve core and a venturi, wherein,
the linear motor, the main valve body and the venturi are sequentially connected, the valve core is arranged in the main valve body, one end of the valve core is connected with an output shaft of the linear motor, the other end of the valve core is matched with the venturi, the main valve body is provided with a fluid inlet and a fluid channel, the fluid channel is connected with the venturi, and fluid enters the fluid channel from the fluid inlet and flows out of the venturi;
the valve core is matched with the venturi tube in the fluid channel, the linear motor drives the valve core to do linear motion to adjust the gap between the venturi tube and the valve core, so that the opening of the fluid outflow position is adjusted, and further the control of the fluid flow is realized.
According to still another aspect of the present invention, there is provided a method for calculating a mass flow rate of the flow rate regulating valve described above, the method comprising the steps of:
(a) Constructing a flow model of the flow regulating valve according to a mass flow formula and a fluid flow velocity formula at a valve port interface;
(b) And constructing a relation between the density and the pressure of the cross-section fluid at the inlet or the outlet of the venturi according to the geometry of the venturi, and introducing the relation between the density and the pressure of the fluid into the flow model to obtain the required mass flow.
Further preferably, in step (a), the flow model is performed according to the following relation:
wherein Qm is the mass flow; cd is the flow coefficient; ρ is the fluid density; a (x) is the flow area and is a function of the displacement x of the valve core; p1 is the fluid pressure at the inlet; t1 is the fluid temperature at the inlet; p2 is the fluid pressure at the valve port; t2 is the temperature of the fluid at the valve port; f (P, T) is the inverse of fluid density as a function of pressure.
Further preferably, in step (b), the relationship between fluid density and pressure is performed as follows:
wherein ρ is the fluid density; e is a natural index; k. a and b are fitting parameters of a fluid density-pressure relation, and specific values are determined by fitting according to the corresponding fluid temperature at the inlet of the flow regulating valve.
In general, compared with the prior art, the above technical solution conceived by the present invention has the following beneficial effects:
1. the front end of the valve core is designed into a paraboloid of revolution, and the valve core of the paraboloid of revolution can enable the flow area to be in linear relation with the displacement of the valve core. The flow formula can show that when the pressure and temperature working conditions are fixed, if the flow area is linearly changed along with the displacement of the valve core, the mass flow is also linearly changed along with the displacement of the valve core, and the design reduces the flow control difficulty, is favorable for high-precision control of the flow, and solves the problem that the flow adjustment resolutions of the existing conical valve core in different displacement ranges are inconsistent.
2. According to the linear flow regulating valve for the carbon dioxide venturi provided by the invention, the valve core axially moves through the linear motor, so that the minimum flow area between the curved surface part of the valve core and the throat is changed, the regulating function of the carbon dioxide flow is realized, the flow passage in the flow regulating valve is designed as the venturi, the flow resistance is reduced, the pressure loss is reduced, the carbon dioxide cavitation occurs at the throat of the venturi, the upstream pressure cannot be influenced by the downstream pressure fluctuation, and the influence of the pressure fluctuation of the downstream load on the flow regulation is avoided.
3. The linear flow regulating valve of the carbon dioxide venturi is internally provided with the valve sleeve structure, so that additional supporting and guiding effects are provided for the valve core, the displacement precision of the valve core is improved, the valve core regulating section profile of the flow regulating valve is calculated to obtain a paraboloid of revolution through an envelope curve method, and specific calculation steps are provided.
4. Aiming at the characteristics of severe change of physical properties of carbon dioxide in liquid and supercritical states and strong compressibility, the invention applies the Euler equation to deduce a universal Bernoulli equation, thereby obtaining a mass flow formula applicable to compressible fluid, and obtaining a flow model applicable to carbon dioxide media by fitting and integrating the relationship between carbon dioxide density and pressure. The model can calculate and predict the mass flow through the regulating valve according to the flow area, the pressure, the temperature and other state parameters, and the control accuracy of the regulating valve is improved.
Drawings
FIG. 1 is a schematic perspective view of a carbon dioxide venturi linear flow regulator valve constructed in accordance with an embodiment of the present invention;
FIG. 2 is a cross-sectional view of the carbon dioxide venturi line flow regulator valve of FIG. 1 constructed in accordance with an embodiment of the present invention;
FIG. 3 is a schematic perspective view of a main valve housing of a linear flow regulator valve for a carbon dioxide venturi constructed in accordance with an embodiment of the present invention;
FIG. 4 is an enlarged schematic view of a portion of FIG. 2A constructed in accordance with an embodiment of the invention;
FIG. 5 is an enlarged partial schematic view at B of FIG. 2 constructed in accordance with an embodiment of the invention;
FIG. 6 is a schematic diagram of a valve port structure of a carbon dioxide venturi linear flow regulator valve constructed in accordance with an embodiment of the present invention;
FIG. 7 is a schematic diagram of the physical parameters of the inlet, throat and outlet of a carbon dioxide venturi linear flow regulator valve constructed in accordance with an embodiment of the present invention.
The same reference numbers are used throughout the drawings to reference like elements or structures, wherein:
10-a linear motor; 20-limiting valve sleeve; 30-a main valve body; 31-a first sealing ring; 32-a first sealing collar; 40-valve core; 41-valve core curved surface portion; 50-main valve sleeve; a 60-venturi; 61-a constriction; 62-throat; 63-an expansion section; 64-a second seal ring; 65-a second sealing retainer ring; d-throat diameter; d-valve port valve core diameter; the radial distance between the point M on the profile of the l-valve core and the throat; the angle between alpha-PM and PQ; x-spool displacement; x' -MN and the right end of the curved surface part.
Detailed Description
The present invention will be described in further detail with reference to the drawings and examples, in order to make the objects, technical solutions and advantages of the present invention more apparent. It should be understood that the specific embodiments described herein are for purposes of illustration only and are not intended to limit the scope of the invention. In addition, the technical features of the embodiments of the present invention described below may be combined with each other as long as they do not collide with each other.
Referring to fig. 1 to 7, the present embodiment provides a carbon dioxide venturi linear flow regulator valve, which is applied to the field of fluid control and is used for regulating the flow of carbon dioxide refrigerant in a refrigeration system.
See fig. 1-3. The carbon dioxide venturi linear flow regulating valve provided by the embodiment comprises a linear motor 10, a limiting valve sleeve 20, a main valve body 30, a valve core 40, a main valve sleeve 50 and a venturi 60. The linear motor 10 and the limit valve sleeve 20 are sequentially fixed at the upper end of the main valve body 30, the venturi tube 60 is fixed at the lower end of the main valve body 30, the linear motor 10 is provided with an output shaft, the valve core 40 is fixedly connected with the output shaft of the linear motor 10 through threads, the other end of the valve core 40 penetrates through a through hole of the main valve body 30 to enter an internal flow passage, and when the output shaft of the linear motor 10 moves linearly, the valve core 40 moves axially along with the linear motor, so that the flow of the regulating valve is controlled. The main valve housing 50 is mounted within the main valve body and the valve core 40 passes through a central through hole in the main valve housing 50 and into the flow passage of the venturi 60.
Referring to fig. 1 and 2, a square flange is provided at the upper end of a main valve body 30, and a limit valve sleeve 20 and a linear motor 10 are sequentially fixed to the main valve body. The lower side of the square flange is a cylindrical cavity which can accommodate the limit valve sleeve 20 and the output shaft of the linear motor 10, and can meet the space requirement of axial displacement of the valve core 40. One side of the outer circumferential surface of the main valve body 30 is provided with an inlet pipe joint and an inlet runner, carbon dioxide medium flows into the flow regulating valve through the inlet runner, the outer circumferential surface of the inlet pipe joint is provided with threads, the inner side of the inlet pipe joint is provided with a circular table surface, and the circular table surface can be matched with a spherical joint of a pipeline of a refrigerating system to realize surface sealing and avoid carbon dioxide leakage. The upper side of the inlet flow passage of the main valve body 30 is provided with a through hole, the valve core 30 can pass through the through hole to enter the inner flow passage of the regulating valve, and the through hole has supporting, radial positioning and guiding functions on the valve core 30. The main valve body 30 is internally provided with an upper section and a lower section of cylindrical flow channels, the upper section of cylindrical flow channels are connected with the inlet flow channels, the flow direction of carbon dioxide is changed from radial to axial, the diameter of the lower section of cylindrical flow channels is slightly larger than that of the upper section, and the lower section of cylindrical flow channels has a stepped structure, so that the main valve sleeve 50 can be positioned, and the main valve sleeve 50 is inserted into the lower section of cylindrical flow channels from the lower side opening of the main valve body 30. The lower end of the main body 30 is provided with a circular flange by which the venturi 60 is secured to the main body 30.
Further, in this embodiment, as shown in fig. 4, a sealing groove is provided on the circumferential surface of the through hole of the main valve body 30, and a first sealing ring 31 and a first sealing ring 32 are installed in the sealing groove, so that dynamic sealing in the axial movement process of the valve core 40 can be realized; the first sealing ring 31 is installed on one side close to the inner flow passage of the main valve body 30, namely, the pressure-bearing side, and the first sealing retainer ring 32 is installed on one side far away from the inner flow passage of the main valve body 30, namely, the non-pressure-bearing side, so that the first sealing ring 31 can be prevented from extruding out due to the fact that the first sealing ring 31 is subjected to larger fluid pressure, and the maximum sealing pressure of the sealing structure is improved.
In this embodiment, the material of the first sealing collar 32 may be polytetrafluoroethylene.
As an alternative embodiment, referring to fig. 1 and 2, a fixing plate is further provided on the circumferential surface of the main valve body 30 on the side close to the square flange, and a mounting hole is provided on the fixing plate. When the carbon dioxide venturi tube linear flow regulating valve is assembled in the refrigerating system, the flow regulating valve can be fixed on other table boards or supports through the fixing plate, so that the pipeline is prevented from bearing the whole weight of the flow regulating valve.
The limiting valve sleeve 20 has a stepped cylindrical structure and can be divided into a first cylindrical section on the upper side and a second cylindrical section on the lower side. The upper end of the limit valve housing 20 is provided with a square flange which can be fixed on the main valve body 30. The bottom of the second cylindrical section of the limit valve housing 20 is provided with a through hole, from which the output shaft of the linear motor 10 protrudes for axial movement. The lower end surface of the second cylindrical section has a limiting function, so that on one hand, the upward displacement of the valve core 40 can be limited not to exceed the maximum opening displacement; on the other hand, when the valve core 40 is at the maximum opening displacement position and the flow regulating valve discharges excessive upstream carbon dioxide at the maximum working pressure, the lower end surface can bear the vertical upward fluid pressure borne by the valve core 40 and transmit the vertical upward fluid pressure to the main valve body 30, so that the fluid pressure is prevented from directly acting on the linear motor 10 through the valve core 40 to cause overload damage of the linear motor 10;
specifically, in this embodiment, when the flow rate regulating valve is assembled, the lower end face of the second cylindrical section of the limiting valve sleeve 20 faces the main valve body 30 and is inserted into the main valve body, and at this time, the outer circumferential face of the first cylindrical section is in interference fit with the inner circumferential face of the cylindrical cavity of the main valve body 30, so as to limit the radial displacement of the limiting valve sleeve 20.
The linear motor 10 plays a role in driving and controlling in the carbon dioxide venturi linear flow regulating valve. The linear motor 10 is provided at its lower end with a square flange surface which can be connected to the stop valve sleeve 20 and thereby indirectly fixed to the main valve body 30. The linear motor 10 has a cylindrical output shaft at one end near the square flange face, and the output shaft can perform linear motion along the axis direction. The outer circumference of the output shaft is provided with external threads, and the external threads can be connected with the valve core 40, so that the valve core 40 is fixedly connected to the output shaft of the linear motor 10. When the output shaft of the linear motor 10 moves, the valve core 40 is driven to do axial linear motion, and the valve core 40 is controlled to stop and keep at the required valve core displacement, so that the minimum flow area at the valve port is changed to a certain specific value, and the flow regulation function is realized.
In this embodiment, as shown in fig. 2, 5 and 6, a through flow passage is provided in the venturi 60 along the axial direction, and the through flow passage can be sequentially divided into four parts of a contraction section 61, a throat 62, an expansion section 63 and an outlet section along the flow direction of carbon dioxide, and the flow passages of the sections are sequentially communicated. The contraction section 61 is a circular-table-shaped flow passage, the cone angle of the contraction section is set to be 60 degrees, the diameter of the contraction section gradually decreases along the flow direction of the carbon dioxide until the diameter of the contraction section is the same as the diameter of the initial part of the throat, and when the carbon dioxide flows through the flow passage of the contraction section, the flow speed is increased, and the pressure is reduced; the throat 62 is a cylindrical flow passage, the diameter of the flow passage is kept unchanged, and carbon dioxide forms a cavitation zone in the flow passage, which is a key area of the flow regulating valve; the expansion section 63 is also a circular-table-shaped flow passage, the cone angle of the expansion section is set to be 6 degrees, the diameter of the expansion section is gradually increased along the flow direction of the carbon dioxide, when the carbon dioxide flows through the flow passage of the section, the flow speed is reduced, the pressure is increased, the cavitation zone disappears, and the expansion section is restored to a liquid state or a supercritical state; the outlet section is the transition section of the venturi 60 and the downstream pipeline, the section is provided with an outlet pipe joint, carbon dioxide flows out of the flow regulating valve from the section flow passage, and the circular truncated surface of the outlet section can also be matched with the pipeline joint to realize surface sealing.
Specifically, in the present embodiment, when the flow rate regulating valve is assembled, the constricted section 61 of the venturi 60 is directed toward and inserted into the main valve body 30, which causes the internal flow passage of the venturi 60 to communicate with and be on the same axis as the internal flow passage of the main valve body 30. The carbon dioxide fluid flows from the constriction 61 into the venturi 60, sequentially through the flow passages of each section and out of the venturi 60 through the outlet section. The venturi 60 is provided with a circular flange on its outer circumferential surface and can be fixed to the main body 30.
Further, in this embodiment, as shown in fig. 2 and 5, a sealing groove is provided on one side of the outer circumferential surface of the venturi tube 60 near the contraction section 61, and a second sealing ring 64 and a second sealing ring 65 are installed in the sealing groove to prevent carbon dioxide from leaking into the external environment; the second sealing ring 64 is installed on the side close to the venturi constriction section, namely the pressure-bearing side, and the second sealing retainer ring 65 is installed on the side far away from the venturi constriction section, namely the non-pressure-bearing side, so that the second sealing ring 64 can be prevented from extruding out due to the larger fluid pressure, and the maximum sealing pressure of the sealing structure is improved.
In this embodiment, the material of the second sealing collar 65 may be polytetrafluoroethylene.
In this embodiment, referring to fig. 2 and 3, the main valve housing 50 has a cylindrical structure, and a cylindrical flow passage is formed inside the main valve housing, and the diameter of the flow passage is the same as that of the upper cylindrical flow passage of the main valve body 30, so that the large local pressure loss of carbon dioxide caused by abrupt change of the flow passage cross section can be avoided. The upper end of the main valve housing 50 is provided with a Y-shaped bracket, a through hole along the axial direction is arranged in the center of the Y-shaped bracket, so that the radial positioning of the valve core and the auxiliary valve core 40 can be supported, and meanwhile, a certain guiding function is provided, and the valve core 40 can extend into the venturi tube 60 in a clearance fit manner through the through hole.
Further, in this embodiment, as shown in fig. 2 and 5, a main valve sleeve limiting groove is provided on the outer circumferential surface of the venturi 60 near the contraction section 61, and the limiting groove has a certain width and depth, so that the main valve sleeve 50 can be fixed in the axial direction and the radial direction. When the flow regulating valve is assembled, the lower end of the main valve sleeve 50 is inserted into the main valve sleeve limiting groove in an interference fit manner; the main valve housing 50 is then inserted into the main valve body 30 with a clearance fit in the venturi 60. The inlet flow passage of the main valve body 30, the upper section cylindrical flow passage of the main valve body 30, the cylindrical flow passage of the main valve sleeve 50 and the flow passage inside the venturi 60 are completely communicated, and are combined together to form a complete flow passage inside the flow regulating valve.
In this embodiment, referring to fig. 2 to 6, the valve core 40 is sequentially a connection section, a first support section, a second support section, and an adjustment section in the axial direction. The end surface of the connecting section is provided with an internal threaded hole which can be connected with external threads of the output shaft of the linear motor 10, so that the valve core 40 can be fixed on the output shaft of the linear motor 10, and the valve core 40 can generate axial displacement along with the movement of the output shaft; the outer circumferential surface of the connecting section is provided with a hexagonal boss, and the structure can play a role in fastening the threaded connection of the valve core 40 and the output shaft of the linear motor 10; an end surface perpendicular to the axial direction is arranged between the connecting section and the first supporting section of the valve core 40, and when the end surface contacts with the outer end surface of the through hole side of the main valve body 30, the end surface is the displacement zero point of the valve core 40. The first support section is cylindrical and passes through the through hole of the main valve body 30 in a clearance fit. The second support section is also cylindrical and is connected to the first support section by a 45 chamfer and passes through the bore of the main valve housing 50 in a clearance fit.
Referring to fig. 2 and 3, the valve body 40 is supported at two places in the flow regulating valve, the first place is supported by the through hole of the main valve body 30 at the first support section of the valve body 40, and the second place is supported by the Y-shaped bracket of the main valve housing 50 at the second support section of the valve body 40. The two supports are respectively positioned at the upper side and the lower side of the inlet runner. This configuration can prevent the valve core 40 from being deformed and deflected greatly when the carbon dioxide flows into the inlet flow passage to cause radial fluid impact on the valve core 40, and can also guide the valve core 40. And after the carbon dioxide flows through the two supporting sections, the flow direction of the carbon dioxide in the regulating valve is changed from radial flow to uniform axial flow due to the influence of the cylindrical flow channel in the regulating valve, so that the valve core 40 is hardly impacted by radial fluid outside the two supporting sections, the valve core 40 is favorably kept on the flow channel axis, the symmetry of the flow channel is ensured, and the problems of valve port flow area errors and clamping stagnation are reduced.
Further, the adjusting section is connected with the second supporting section through a 60-degree chamfer, the adjusting section sequentially comprises a cylindrical portion and a curved surface portion along the fluid flow direction, the diameter of the cylindrical portion is the same as that of the venturi throat 62, clearance fit is formed between the cylindrical portion and the venturi throat 62, and when the valve core 40 is at a displacement zero point, the cylindrical portion can be partially inserted into the venturi throat 62. The diameter of the upper end of the curved surface part is the same as that of the cylindrical part, and then the diameter of the curved surface part is gradually reduced to 0 along the axial fluid flow direction; the outer profile of the curved surface portion is a paraboloid of revolution which cooperates with the venturi throat 62 to form a minimum flow area for the flow regulator valve which is in linear relationship with the linear displacement of the valve core 40, and changing the displacement of the valve core 40 can change the flow area linearly to achieve an accurate flow regulation function.
In this embodiment, the material of the valve metal member may be PH 17-4 stainless steel.
Further, in this embodiment, referring to fig. 2, 5 and 6, the design method of the paraboloid of revolution of the curved surface portion of the valve core 40 uses the flow characteristic and the mathematical characteristic of the envelope curve of the regulating valve, and mainly includes the following steps:
step one, the valve core displacement x and the flow area A are in a linear relation, so that the flow regulating valve has linear area characteristics, and the expression satisfied by the linear area characteristics in the maximum stroke range of the valve core is as follows:
wherein A is the flow area; x is the displacement of the valve core; k. b are linear characteristic parameters and are unknown quantities. To obtain the values of k and b, substituting the conditions at which the spool 40 is at the minimum and maximum displacements can obtain the boundary conditions satisfied by equation (1) at the minimum and maximum displacements of the spool 40:
wherein A is min 、A max 、x min 、x max All are known design parameters of the regulating valve, and are specific values.
Solving the equation set of the formula (2) to obtain values of the linear characteristic parameters k and b:
wherein R is an adjustable ratio:when the pressure difference before and after the regulating valve is kept unchanged and the flow coefficient is constant, the flow of the regulating valve is related to the flow area, and the flow of the regulating valve and the flow area are in direct proportion, namely R meets the following conditions:
step two, in order to simplify the calculation and the solution of the equation, the valve core displacement x and the maximum valve core displacement x of the flow regulating valve are calculated max The ratio of (2) is defined as the displacement ratio t of the flow regulating valve, and the expression satisfied by the displacement ratio t can be obtained by the geometric relationship:
wherein x' is the axial distance between MN and the right end of the curved surface part; l is the radial distance between the point M on the valve core molded surface and the throat; alpha is the angle between PM and PQ. From formulas (1) to (5), expressions of the flow area A of the flow regulating valve under different valve core displacements x are obtained, and the expressions are another expression of linear area characteristics of the formula (1):
A＝[(t-1)·k+1]·A max (6)
in this embodiment, referring to fig. 6, the flow area a is the side area of the circular truncated cone PMNQ, thereby obtaining an expression of the geometric form thereof:
wherein A is the flow area, alpha is the included angle between PM and PQ, PM is the bus of the truncated cone PMNQ in the cross section of the valve port, PQ is the diameter of the throat in the cross section of the valve port; l is the radial distance between the point M on the valve core molded surface and the throat; d is the throat diameter. By the formula (7), the constant area curve equation can be obtained in the cross section of the valve port through transformation:
all points (l, alpha) on the equal area curve determined by the equation can be calculated to obtain the same flow area A, namely the curved surface area formed by one rotation of a line segment formed by connecting the point P and the point (l, alpha) around the axis of the valve core 40 is constant.
From the mathematical relationship, the cross section profile of the valve core is obtained, namely, the expression that the envelope curve of the valve core meets:
the cross section profile of the curved surface of the valve core 40 is the envelope curve of the equal area curve corresponding to the flow area A under different displacement ratios t. Therefore, the displacement ratio t is set at [0,1]Uniformly discretized into n+1 values t in interval 0 ，t 1 ，...，t n Index number is i, and each discrete displacement ratio t is obtained according to the linear area characteristic obtained by the formula (6) i Corresponding flow area A i Thereby obtaining the displacement ratio t of the n+1 group i And flow area A i Is a value of (2). From equation (9), a point set { l ] consisting of n+1 points is obtained i ，α i Point on this point set }Are located on the envelope, i.e., the cross-sectional profile of the curved portion of spool 40.
Step three, for the envelope curve point set { l } i ，α i Performing secondary fitting to obtain a parabola; the parabola is rotated for one circle about the axis of the valve core 40 to obtain a rotating parabola of the curved surface part of the valve core 40, the rotating parabola enables the valve core displacement x and the flow area A to be in a linear relation, the linear flow characteristic expressed in the formula (1) is met, the flow regulation resolution in the working range of the regulating valve can be kept consistent through the molded surface obtained through the method, and the flow regulation precision of the flow regulating valve is improved.
In this embodiment, a flow model for compressible media is provided, which can be used for mass flow calculation of a flow regulating valve, including a general bernoulli equation and an improved mass flow formula.
Preferably, the flow model in this embodiment is adapted to calculate the mass flow of the carbon dioxide medium through the flow regulating valve. So as to meet the special working conditions that the physical properties of the medium are changed drastically when the carbon dioxide flows through the flow regulating valve, and the carbon dioxide has stronger compressibility in a supercritical state.
In this embodiment, referring to fig. 7, where P is the fluid pressure, v is the fluid flow rate, z is the relative height, subscript 1 indicates the flow channel inlet cross section, subscript 2 indicates the valve port cross section at the junction of the constriction 61 and throat 62, and subscript 3 indicates the flow channel outlet cross section.
Based on physical property data of carbon dioxide, carbon dioxide is considered to be an ideal fluid having no viscosity because the viscosity of carbon dioxide in liquid and supercritical states is only about one tenth of that of water. When the ideal fluid is subjected to steady flow, the differential equation satisfied by each fluid particle on the flow line is obtained by using the Euler equation and the fluid streamline equation of the ideal fluid, and is shown as follows:
wherein ρ is the fluid density; p is the fluid pressure; v is the fluid flow rate; g is gravity acceleration; z is the relative height. Equation (10) is a generalized Bernoulli equation that applies to both compressible and incompressible ideal fluids and thus carbon dioxide media in this embodiment.
Integrating the equation (10) along the streamline from the flow channel inlet section to the valve port section. The integration ignores the change in height of the carbon dioxide as it flows within the flow regulating valve and approximates the flow rate of the carbon dioxide at the flow channel inlet cross section of the flow regulating valve to 0.
Further, in this embodiment, considering the characteristic that the carbon dioxide medium has strong compressibility in the supercritical state, the density is regarded as a function of pressure and temperature, expressed as: ρ (P, T). The expression of the fluid flow rate at the valve port cross section is as follows:
wherein v is the fluid flow rate; ρ is the fluid density; p is the fluid pressure; t is the fluid temperature; the subscript 1 indicates a physical parameter of the flow passage inlet cross section, and the subscript 2 indicates a physical parameter of the valve port cross section. In the formula (11), the result of the indefinite integration of the integral term is:another form of fluid flow velocity expression at the valve port cross-section is obtained:
substituting a mass flow formula: q (Q) m Let ρva, and consider the flow coefficient C d The following flow model was obtained:
wherein Q is m Is mass flow; c (C) d Is the flow coefficient; ρ is the carbon dioxide density; a (x) is the flow area; is aboutA function of spool displacement x; p is the fluid pressure; t is the fluid temperature; referring to fig. 7, a subscript 1 indicates a physical parameter of a flow passage inlet cross section, and a subscript 2 indicates a physical parameter of a valve port cross section; f (P, T) is the inverse of fluid density as a function of pressure.
Since the integral object in the expression (11) is only pressure, it can be considered that the temperature T is at the inlet cross section 1 The relationship between density and pressure is fitted under known conditions. Based on the physical properties of carbon dioxide, the following carbon dioxide density-pressure relationship is obtained:
wherein e is a natural index; ρ is the carbon dioxide density; p is the pressure of carbon dioxide; k. a and b are fitting parameters of a carbon dioxide density-pressure relation, and specific values are determined according to the corresponding medium temperature at the inlet of the flow regulating valve. The meaning and the value of the parameter symbol in the formula (14) are not related to the symbol in the design method of the rotary paraboloid of the valve core curved surface part 41. Substituting the density-pressure relation expression represented by the formula (14) into the formula (13) and integrating to obtain a flow rate model suitable for the flow of the carbon dioxide medium in the flow rate regulating valve:
wherein Q is m Is mass flow; c (C) d Is the flow coefficient; ρ is the carbon dioxide density; a (x) is the flow area and is a function of the displacement x of the valve core; p is the fluid pressure; t is the fluid temperature; referring to fig. 7, a subscript 1 indicates a physical parameter of a flow passage inlet cross section, and a subscript 2 indicates a physical parameter of a valve port cross section; e is a natural index; k. a and b are constants, and are fitting parameters of a carbon dioxide density-pressure relation.
According to the flow model, when the flow regulating valve is in a certain specific working condition, the flow area can be changed by changing the valve core displacement, and then the flow regulating function is realized.
The flow model provided in the embodiment can calculate the mass flow of the carbon dioxide medium flowing through the flow regulating valve in a liquid state or a supercritical state under different working conditions such as pressure, temperature, valve core displacement and the like.
It will be readily appreciated by those skilled in the art that the foregoing description is merely a preferred embodiment of the invention and is not intended to limit the invention, but any modifications, equivalents, improvements or alternatives falling within the spirit and principles of the invention are intended to be included within the scope of the invention.
Claims (10)
1. The design method of the parabolic valve core in the flow control valve is characterized by comprising the following steps of:
s1, setting the displacement ratio of a valve core in a regulating valve, and constructing a relational expression between the flow area and the valve core displacement in the flow regulating valve and boundary conditions met when the valve core is at the maximum displacement and the minimum displacement in the flow regulating valve, so as to obtain relational expressions of the flow areas of the corresponding flow regulating valves under different valve core displacements;
s2, constructing a geometric relation of the flow area according to the geometric structures of the throttle valve and the valve core, and obtaining a relation satisfied by the cross section molded line of the valve core from the geometric relation of the flow area;
s3, dispersing the displacement ratio into a plurality of values, calculating by utilizing a relational expression of the corresponding flow area under the displacement of the valve core obtained in the step S1 to obtain the corresponding flow area of different displacement ratios, carrying the flow area into the cross section molded line calculation of the valve core in the step S2 to obtain the coordinates of points on the molded surface of the valve core at different displacement ratios, fitting the points on the molded surface of the valve core under all displacement ratios into parabolas, and obtaining the required revolution paraboloid curve of the valve core by rotating the parabolas around the central axis of the valve core for one circle.
2. The design method according to claim 1, wherein in step S1, the relation between the flow area and the spool displacement is performed as follows:
wherein A is the flow area; x is the displacement of the valve core; k. b are all linear characteristic parameters, A max Is the maximum flow area.
3. The design method according to claim 2, wherein in step S1, the boundary conditions are performed as follows:
wherein A is min 、A max 、x min 、x max The valve is respectively a minimum flow area, a maximum flow area, a minimum valve core displacement and a maximum valve core displacement.
4. The design method according to claim 1 or 3, wherein in step S1, the relation between the flow areas of the corresponding flow rate regulating valves at different spool displacements is performed as follows:
A＝[(t-1)·k+1]·A max
wherein A is the flow area; t is the displacement ratio, i.e. the ratio of the current valve core displacement to the maximum valve core displacement; k is a linear characteristic parameter, amax is a maximum flow area.
5. The design method according to claim 1, wherein the expression that the envelope satisfies is performed as follows:
where f (l, α) is an equal area curve equation,l is the radial distance between the point on the valve core molded surface and the throat; alpha is the included angle between the perpendicular line formed by any point on the intersection line of the contraction section of the venturi flow channel and the throat and the valve core molded surface and the plane where the intersection line is located; d is the throat diameter; a is the flow area.
6. A valve cartridge obtainable by the method of any one of claims 1 to 5, wherein the front end of the valve cartridge is a paraboloid of revolution.
7. A flow rate regulating valve comprising the valve core according to claim 6, wherein the flow rate regulating valve comprises a linear motor, a main valve body, the valve core and a venturi tube,
the linear motor, the main valve body and the venturi are sequentially connected, the valve core is arranged in the main valve body, one end of the valve core is connected with an output shaft of the linear motor, the other end of the valve core is matched with the venturi, the main valve body is provided with a fluid inlet and a fluid channel, the fluid channel is connected with the venturi, and fluid enters the fluid channel from the fluid inlet and flows out of the venturi;
the valve core is matched with the venturi tube in the fluid channel, the linear motor drives the valve core to do linear motion to adjust the gap between the venturi tube and the valve core, so that the opening of the fluid outflow position is adjusted, and further the control of the fluid flow is realized.
8. A method of calculating a mass flow rate of a flow regulating valve as claimed in claim 7, the method comprising the steps of:
(a) Constructing a flow model of the flow regulating valve according to a mass flow formula and a fluid flow velocity formula at a valve port interface;
(b) And constructing a relation between the density and the pressure of the cross-section fluid at the inlet or the outlet of the venturi according to the geometry of the venturi, and introducing the relation between the density and the pressure of the fluid into the flow model to obtain the required mass flow.
9. The computing method of claim 8, wherein in step (a), the flow model is performed according to the following relationship:
wherein Qm is the mass flow; cd is the flow coefficient; ρ is the fluid density; a (x) is the flow area and is a function of the displacement x of the valve core; p1 is the fluid pressure at the inlet; t1 is the fluid temperature at the inlet; p2 is the fluid pressure at the valve port; t2 is the temperature of the fluid at the valve port; f (P, T) is the inverse of fluid density as a function of pressure.
10. The computing method of claim 8 or 9, wherein in step (b), the relationship between fluid density and pressure is performed according to the following:
wherein ρ is the fluid density; e is a natural index; k. a and b are fitting parameters of a fluid density-pressure relation, and specific values are determined by fitting according to the corresponding fluid temperature at the inlet of the flow regulating valve.
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