• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    The liquid injector according to the first embodiment of the present invention has a fluid passage channel formed by sequentially combining an inlet portion 2 formed as a converging tube, a cylindrical portion 3 and an outlet portion 4 formed as a conical diffuser. Casing 1 is included. The length of the cylindrical portion 3 is not smaller than its radius. The cone angle of the diffuser constituting the outlet 4 of the fluid passage channel is greater than the cone angle of the converging tube constituting the inlet 2 of the same channel. According to a second embodiment of the invention, the converging tube constituting the inlet of the fluid passage channel is made conical. The use of the present invention makes it possible to produce a steady, finely dispersed liquid stream with minimal energy consumption.
    公开号:KR20030090685A
    申请号:KR10-2003-7012373
    申请日:2002-03-21
    公开日:2003-11-28
    发明作者:안드레이 엘 두쉬킨；알렉산더 브이 칼피쉐브
    申请人:안드레이 엘 두쉬킨；알렉산더 브이 칼피쉐브；
    IPC主号:
    专利说明:

    Liquid Sprayers
    [2] Various types of liquid injectors are currently used as fire extinguishers in various fields, including fire suppression facilities.
    [3] As an example, US Pat. No. 5,125,582 (IPC B05B 1/00, published June 30, 1992) discloses the manufacture of a liquid injector designed to produce a cavitation liquid flow. The prior art includes a casing having a flow-through channel formed by a nozzle and a cylindrical chamber. The nozzles are made in the form of converging tubes in communication with the conical diffuser and their surfaces do not join continuously. The length of the cylindrical chamber is at least three times the diameter of the minimum section of the nozzle. When a constant pressure of liquid is supplied to the inlet opening of the converging tube of the nozzle, the liquid flow section contracts and the outflow rate increases. Sudden expansion of the liquid flow in the diffuser causes a liquid cavity. The liquid cavity is augmented in the passage of a liquid jet through the cylindrical chamber, where the liquid jet is expanded and a return vortex flow is created. An annular vacuum zone is formed around the cone jet to initiate the liquid flow dispersion process associated with the cavitation process.
    [4] However, despite the possibility of strengthening the cavity process, the prior art liquid injectors do not provide for the formation of a fixed, finely dispersed liquid flow which can maintain the shape and section size of the liquid flow in lengths up to 10 m. This is especially important when the injector is used to control the source of fire.
    [5] Vacuum injector heads (author's proof, USSR 994022, IPC B05B 1/00, published February 7, 1983) are also known and comprise a nozzle consisting of a converging tube and a cylindrical head coaxially located with the nozzle. The cylindrical head is provided with a discharge hole formed in the side of its outlet opening to allow the atmosphere to enter the vacuum zone of the cylindrical head cavity. As a result, the air being sucked saturates the moving liquid stream, causing the stream to separate into droplets.
    [6] Russian Patent No. 2123871 (IPC A62C 31/02, published December 27, 1998) describes a head for forming aerosol-type liquid jets, which allows the dispersion of gas droplet jets to be improved. The prior art injector (head) is a casing having a fluid passage channel formed by a Laval nozzle, an inlet pipe coupling for supplying a liquid with pressure and between the pipe coupling and an inlet section of the Laval nozzle. It includes a distribution grid located. The size of the distribution grid hole is 0.3 to 1.0 of the diameter of the Laval nozzle critical section. While passing through the holes of the distribution grid, the liquid flow is separated into separate flows, which are continuously concentrated in the nozzle holes and accelerated at high speed. This embodiment provides a sufficient distance to release for fire suppression and fine spraying.
    [7] Closest to the claimed version of the injector is the liquid ejection device described in German Democratic Republic (DDR) Patent No. 233490 (IPC A62C 1/00, published March 5, 1986), which provides extinguishing agent to the source of the fire. It is applied to supply. The apparatus consists of a casing having a fluid passage channel, in which the working fluid, including water, is supplied under constant pressure. The fluid passage channel of the device consists of an inlet formed by a converging tube, a cylindrical part and an outlet formed by a conical diffuser, each of which is sequentially coupled to be axially aligned with each other. The device also includes a reservoir for containing the extinguishing agent, which reservoir communicates with the diffuser through the radial passage.
    [8] During operation of the device the liquid (water) is supplied to the inlet opening of the fluid passage channel at a pressure of 1.5 to 2.0 bar and is accelerated sequentially in a nozzle formed by a converging tube, a cylinder and a diffuser. The extinguishing agent is released to the diffuser through a radial passage and further mixed with the liquid stream. When known extinguishing agents are used, the use of the device inevitably increases the extinguishing agent, thereby improving fire extinguishing efficiency. However, the example given does not produce a high velocity, finely dispersed gas droplet jet. In most cases the liquid flow is used in devices as carriers for additionally introduced extinguishing agents such as, for example, foam generating additives.
    [1] The present invention relates to liquid spraying technology, which can be used in fire protection systems as part of a processing facility for the combustion of fuels in thermal engineering and transportation, as well as for humidifying the surroundings and spraying disinfectants and pesticides.
    [26] The invention is illustrated by examples of specific embodiments and by the application drawings described below.
    [27] 1 is a view schematically showing a liquid injector formed according to a first embodiment of the present invention.
    [28] 2 is a schematic cross sectional view of a liquid injector formed in accordance with a first embodiment of the present invention having a rounded corner fluid passage channel;
    [29] 3 is a schematic cross-sectional view of a liquid injector formed in accordance with a first embodiment of the present invention having a chamber with a cylindrical channel.
    [30] 4 is a cross-sectional view in the A-A plane of a chamber with a cylindrical chamber used in two embodiments of the present invention (see FIGS. 3 and 6).
    [31] 5 is a schematic cross-sectional view of a liquid injector formed in accordance with a first embodiment of the present invention having a chamber located on the same axis as the casing so that an annular passage is formed.
    [32] 6 is a schematic view of a liquid injector formed in accordance with a second embodiment of the present invention.
    [33] 7 is a schematic cross-sectional view of a liquid injector formed in accordance with a second embodiment of the present invention having a chamber with a cylindrical channel.
    [34] 8 is a schematic cross-sectional view of a liquid injector formed in accordance with a first embodiment of the present invention having a chamber arranged on the same axis as the casing to form an annular passageway.
    [9] The claimed invention aims at producing a steady state finely dispersed liquid jet which must maintain the shape and size of the jetting section at a distance of up to 10 m and to increase the energy efficiency consumed for the production of gas droplet jets. There is this. In addition, the distribution of droplet concentrations should be homogeneous for the intervals of the finely dispersed gas droplet jets. The solution for the purpose described above is particularly important in the application of liquid injectors to extinguish fire sources.
    [10] The technical results achievable through the solution of the above described work are to increase the fire extinguishing efficiency when liquids containing extinguishing agents are used, to increase the effective use of working fluids and to consume the energy to generate gas bubble jets. It is to reduce.
    [11] The above object comprises a casing having a fluid passage channel consisting of an inlet portion formed as a converging tube, a cylindrical portion and an outlet portion formed as a conical diffuser, each of which is sequentially coupled to each other and arranged on the same axis. By providing a liquid injector according to an example. According to the invention, the length of the cylinder is not smaller than its radius, and the cone angle of the diffuser constituting the outlet of the fluid passage channel is greater than the cone angle of the converging tube constituting the inlet of the fluid passage channel.
    [12] Preferably, a liquid injector is used in which the vertex angle of the cone constituting the converging tube is between 6 and 20 degrees and the vertex angle of the cone constituting the diffuser is between 8 and 90 degrees. Specifically, the vertex angle of the cone constituting the converging tube may be equal to 13 degrees, and the vertex angle of the cone constituting the diffuser may be equal to 20 degrees.
    [13] In order to remove the stationary and vibrating fluctuations from a predetermined direction to improve the steady flow of the gas droplet jet, the inlet edge of the converging tube constituting the inlet of the fluid passage channel and the outlet of the fluid passage channel are configured. The exit edge is rounded.
    [14] The radius of the rounded corner is 1 to 2.5 times the radius of the cylindrical portion of the fluid passage channel.
    [15] The liquid injector is provided with a chamber having a cylindrical channel whose inlet end is coupled with the outlet section of the diffuser, the diameter of the cylindrical channel of the chamber not being smaller than the diameter of the outlet section of the diffuser. Using the chamber described above, it is possible to consume and generate a minimum amount of fine jet finely dispersed gas droplet jets. The diameter of the cylindrical channel of the chamber is approximately 4 to 6 times the diameter of the cylindrical portion of the fluid passage channel, and the length of the channel is 10 to 30 times the diameter of the cylindrical portion of the fluid passage channel.
    [16] A grid or perforated plate may be located in the outlet section of the cylindrical channel of the chamber. In this case, the gas droplet jets generated in the cylindrical chamber of the chamber are additionally separated. In order to reduce energy loss in the process of producing finely dispersed flows, the total cross sectional area of the perforated plate or grid hole is chosen to be 0.4 to 0.7 times the cross sectional area of the cylindrical channel of the chamber.
    [17] The chamber wall may be provided with at least one tangential opening for blowing gas (eg air) from the outside into the cylindrical channel of the chamber. This embodiment makes it possible for the gas droplet jet to stabilize and the kinetic energy loss of the liquid droplets to be reduced due to the swirl of the air flow around the jet generated. In view of this purpose, at least four tangential openings may be provided in the chamber wall of the preferred embodiment, which openings are symmetrically arranged in pairs in two cross sections of the cylindrical channel of the chamber, the first plane being It extends near the diffuser exit section and the second plane extends near the exit section of the chamber.
    [18] According to another embodiment of the invention, the liquid injector may consist of a chamber arranged on the same axis as the casing on the outside of the casing. At least one passage is formed between the casing outer surface and the chamber inner surface to supply a gas flow under pressure to the outlet section of the outlet of the fluid passage channel of the injector. The chamber may comprise a nozzle consisting of a converging tube and a diffuser arranged sequentially. The nozzle inlet section communicates with the outlet of the fluid passage channel of the injector. The use of a chamber with a nozzle allows the energy of the gas flow in the same direction to be used to further separate the liquid droplets and increase the reaching of the finely dispersed gas droplet jets.
    [19] The accomplishment of the object comprises a casing having a fluid passage channel consisting of an inlet portion formed as a converging tube, a cylindrical portion and an outlet portion formed as a conical diffuser, each of which is sequentially coupled to each other and arranged on the same axis. It is possible by providing a liquid injector according to the embodiment. According to the invention, the length of the cylindrical portion is not smaller than its radius, and the converging tube constituting the inlet of the fluid passage channel is made in the shape of a cone, and the radius of the rounded portion of the side surface is the cylindrical portion of the fluid passage channel. Not smaller than the radius.
    [20] The vertex angle of the cone constituting the converging tube is preferably between 8 degrees and 90 degrees. The surface of the conical converging tube is preferably engaged with the surface of the cylindrical portion of the fluid passage channel at an angle of at least 2 degrees.
    [21] In order to further stabilize the steady state flow of the gas droplet flow, the outlet edge of the diffuser constituting the outlet of the fluid passage channel is rounded. The radius of the rounded portion of the corner is approximately one to two times the diameter of the cylindrical portion of the fluid passage channel.
    [22] The liquid injector may be provided with a chamber having a cylindrical channel to which the outlet section of the diffuser is coupled at the inlet end, the diameter of the cylindrical channel of the chamber not being smaller than the diameter of the outlet section of the diffuser. As in the first embodiment of the present invention, the use of the chamber enables finely dispersed gas droplet jets to be produced with minimal energy consumption. The diameter of the cylindrical channel of the chamber is approximately 4 to 6 times the diameter of the cylindrical portion of the fluid passage channel, and the length thereof is 10 to 30 times the diameter of the cylindrical portion of the fluid passage channel.
    [23] As in the first embodiment of the invention, a grid or perforated plate may be located in the outlet section of the cylindrical channel of the chamber. In order to reduce energy loss while producing finely dispersed flow, the cross-sectional area of the perforated plate or grid hole is chosen to be 0.4 to 0.7 times the cross-sectional area of the cylindrical channel of the chamber.
    [24] As in the first embodiment of the invention, the chamber wall may be provided with at least one tangential opening for blowing gas from the outside into the cylindrical channel of the chamber. This embodiment makes it possible for the gas bubble jet to be stabilized and to be reduced due to the vortex of the air flow around the flow in which the kinetic energy loss of the fluid flow is generated. In view of this object, at least four tangential openings may be provided in the chamber wall in a preferred embodiment of the invention, the tangential openings being symmetrically paired in two cross sections of the cylindrical channel of the chamber. The first plane extends near the outlet section of the diffuser and the second plane extends near the outlet section of the chamber.
    [25] Further, a preferred embodiment of the liquid injector may comprise a chamber arranged on the same axis as the casing on the outside of the casing instead of the chamber described above. At least one passage is formed between the outer surface of the casing and the inner surface of the chamber for supplying gas under pressure to the outlet section of the fluid passage channel of the injector. The chamber may comprise a nozzle consisting of a converging tube and a diffuser arranged sequentially. The nozzle inlet section communicates with the outlet of the fluid passage channel of the injector. As in the first embodiment of the present invention, the use of a chamber with nozzles allows the energy of the gas flow in the same direction to be used to further separate the liquid droplets and increase the arrival to the finely dispersed gas droplet flow. do.
    [35] The liquid injector formed according to the first embodiment of the invention (see FIGS. 1 to 5) comprises a casing 1 having a fluid passage channel consisting of axially aligned portions joined together. The inlet part 2 is made in the form of a converging tube in which the outlet opening is combined with the inlet opening of the cylindrical part 3. The outlet portion 4 made in the form of a conical diffuser comprises an inlet opening coupled with the outlet opening of the cylindrical portion 3. The length of the cylinder is 0.7 of its diameter. The corner angle of the cone constituting the converging tube is 13 degrees and the corner angle of the cone constituting the diffuser is 20 degrees.
    [36] The casing 1 is connected to the pipe joint 5 of the pipeline of the liquid supply system at the side of the inlet opening of the converging tube. The liquid supply system comprises a pump or a pressure type liquid supercharger 6.
    [37] In a preferred embodiment (see FIG. 2), the inlet edge of the converging tube constituting the inlet portion 2 of the fluid passage channel and the outlet edge of the diffuser constituting the outlet portion 4 are rounded, of which the rounded circle is formed. The radius is made equal to the diameter of the cylindrical portion 3.
    [38] The liquid injector may comprise a chamber 7 (see FIG. 3) in which the inlet opening has a cylindrical channel 8 which communicates with the outlet section of the diffuser (outlet 4). The diameter of the cylindrical channel 8 is equal to four times the diameter of the cylindrical portion 3 of the fluid passage channel. The length of the cylindrical channel 8 measured from the outlet section of the diffuser to the outlet section of the chamber 7 is equal to ten times the diameter of the cylindrical section 3 of the fluid passage channel. The perforated plate 9 is located at the outlet opening of the cylindrical channel 8 and is attached to the end of the chamber 7 by means of a special nut 10. The total cross-sectional area of the hole in the perforated plate 9 is 0.5 times the cross-sectional area of the cylindrical channel 8. The maximum size "d" of each fluid passage hole in the perforated plate 9 is selected depending on the diameter "D" of the cylindrical portion 3 according to the following condition (0.2 <d / D <0.7).
    [39] Eight tangential openings 11 are formed in the wall of the chamber 7 to blow air from the outside into the cylindrical channel 8 (see FIGS. 3 and 4). The tangential opening 11 is arranged in two sections of the cylindrical channel 8. Four openings 11 are arranged symmetrically in the cross section of the channel 8 near the outlet section of the diffuser (outlet 4), and four other openings 11 are located near the outlet section of the chamber 7. It is arranged in the cross section of the channel 8.
    [40] The injector may be provided with a cylindrical chamber 12 axially aligned with the casing on the outside of the casing 1 (see FIG. 5). An annular passageway is formed between the outer surface of the casing 1 and the inner surface of the chamber 12 to communicate with the high pressure gas source 13. The annular passage is applied for supplying gas to the section of the outlet 4 of the fluid passage channel. The nozzle located at one end of the chamber consists of a converging tube 14 and a diffuser 15.
    [41] The liquid injector according to the second embodiment of the present invention (see FIGS. 6 to 8) comprises a casing 16 having a fluid passage channel consisting of continuously coupled portions axially aligned with each other. The inlet 17 is made in the form of a conical converging tube in which the radius of the rounded circle on the side surface is equal to the diameter of the cylinder 18. The length of the cylindrical portion 18 engaged with the inlet portion 17 is 0.7 times its diameter. The outlet portion 19 formed by the conical diffuser has an inlet opening coupled with the outlet opening of the cylindrical portion 18. The corner angle of the cone forming the diffuser is 20 degrees. The conical surface of the converging tube (entrance 17) is coupled with the surface of the cylindrical portion 18 at an angle of 2 degrees. The outlet edges of the diffuser constituting the outlet portion 19 of the fluid passage channel are rounded, and the radius of the rounded circle of the corner is the same as that of the cylinder portion 18.
    [42] The casing 16 is connected to a pipe joint 20 of a pipeline of a liquid supply system comprising a liquid supercharger 21.
    [43] The outlet edges of the diffuser constituting the outlet portion 19 are rounded, and the radius of the rounded circle of the edge is the same as that of the cylindrical portion 18.
    [44] In a preferred embodiment of the injector (see FIG. 7), the outlet opening of the diffuser (outlet 19) is in communication with a chamber 22 having a cylindrical channel 23. The geometric size of the cylindrical portion 18 is chosen to be the same as that of the first embodiment of the injector (see FIG. 3). The perforated plate 24 is located in the outlet opening of the cylindrical channel 23 and attached to the end of the chamber 22 by a special nut 25. The size of the hole in the perforated plate 24 is selected the same as that of the first embodiment of the injector (see FIG. 3).
    [45] Eight tangential openings 26 are formed in the wall of the chamber 22 to blow air from the outside into the cylindrical chamber 23 (see FIGS. 7 and 4). The tangential opening 26 is arranged and positioned in the same way as in the first embodiment of the injector.
    [46] Another example of an injector in accordance with a second embodiment of the invention may include a cylindrical chamber 27 (see FIG. 8) arranged on the same axis as the gasket 16 on the outside of the casing 16. An annular passageway formed between the outer surface of the casing and the inner surface of the chamber 27 communicates with the high pressure gas source 28. The annular passage is adapted to supply cocurrent gas flow to the outlet section of the outlet 19 of the fluid passage channel. The nozzle at the end of the chamber consists of a converging tube 29 and a diffuser 30.
    [47] Operation of the injector designed according to the first embodiment of the present invention is performed in the following manner.
    [48] The liquid is supplied under constant pressure to a pipe joint 5 connected to the outlet opening of the casing 1 of the injector by means of a supercharger 6 through the pipeline of the liquid supply system. The liquid is moved to the inlet opening of the converging tube (inlet 2), producing a high velocity fluid flow with a constant velocity profile in that section. The liquid flow proceeds from the region with higher static pressure and lower dynamic pressure in the converging tube to the region with lower static pressure and higher dynamic pressure. This enables the conditions for the creation of the vortex flow and prevents the liquid flow from separating from the channel wall.
    [49] The outlet end up to a liquid flow rate of the liquid outlet end value of the saturated vapor pressure is the static pressure at the initial temperature at the convergence of the converging tube of the tube (in 20 for the liquid P sv 2.34 and 10 -3 MPa). The upstream of the initial static liquid pressure of the converging tube is maintained at a level not lower than the critical pressure (P in 0.23 MPA) required for the development of the cavitation during the output flow to the atmosphere. The loss of kinetic energy that occurs while the liquid flow passes through the converging tube depends on the cone angle of the cone forming the conical surface of the converging tube. When the cone angle increases from 6 degrees, the energy consumption initially increases and reaches a maximum when the angle reaches 13 degrees, then decreases at an angle of 20 degrees. Therefore, the optimal vertex angle of the cone constituting the converging tube is chosen between 6 and 20 degrees.
    [50] After passing through the inlet 2 of the fluid passage channel of the injector, the liquid flow is transferred to the cylinder 3, where the hollow bubbles develop for a time of 10 −4 to 10 −5 seconds. . Foaming while the liquid flows through the cylinder 3 is ensured if the length of the cylinder exceeds its radius to provide some time sufficient for a stationary cavity. However, fluid friction losses are known to increase at generally increased lengths of cylindrical channels. Thus, under the service conditions of an applicable injector, the length of the cylindrical channel can be limited to a value corresponding to the diameter of the fluid passage channel.
    [51] During the passage of liquid through the outlet 4, which consists of a diffuser, the cavity bubbles grow and propagate violently, and the liquid flow separates from the diffuser wall. The flow is accelerated in the diffuser due to the reduced density of the liquid stream containing the vapor and air bubbles. Since the static pressure at the inlet area of the diffuser is low and comparable to the cavity pressure, a directional air stream enters the cavity section between the gas jet and the diffuser wall from the outside. Vortex flows, caused by gas and liquid flows in opposite directions, cause the liquid flow to be pushed out of the diffuser wall to reduce frictional energy losses. In addition, the creation of the vortex flow results in the actual separation of the liquid flow, which is further augmented by the propagation of hollow bubbles while the flow expands in the diffuser. This process occurs when the cone angle of the diffuser constituting the outlet 2 of the fluid passage channel exceeds the cone angle of the converging tube constituting the inlet 4 of the fluid passage channel of the injector. The optimal vertex angle of the cone constituting the diffuser is between 8 degrees and 90 degrees. The generation of the vortex flow does not occur at the vertex angle above 90 degrees. At a vertex lower than 8 degrees, there is practically a lack of gas covering between the liquid flow and the diffuser walls.
    [52] With the proper selection of the optimal cone angle for the converging tube and the diffuser, the diameter of the diffuser outlet opening is important for the effective separation of the liquid flow. It is reasonable to use a diameter of the diffuser outlet opening that is more than 4-6 times the diameter of the cylindrical part 3. Smaller diameters of the diffuser outlet openings exhibit only minimal effect of the vortex flow on the liquid flow, with larger diameters generally increasing the size of the injector.
    [53] Injectors with fluid passage channels of the size described above provide for the generation of high velocity finely dispersed gas droplet jets with minimal loss of kinetic energy.
    [54] When the diameter of the outlet opening of the pipe joint 5 is essentially larger than the diameter of the cylindrical part 3 of the fluid passage channel, the use of a converging tube with a rounded inlet edge (see FIG. 2) takes place.
    [55] This embodiment of the injector makes it possible to reduce the dimensions of the injector with minimal loss of kinetic energy for the generation of friction and vortex flow. The optimum radius of the rounded circle at the corner of the converging tube is between 1 and 2.5 times the radius of the cylinder portion of the fluid passage channel. Since the increase in the rounded corner radius results in an increase in the dimensions of the overall device, it is preferable to select the radius equal to the diameter of the cylindrical portion 3. In the outflow of liquid through a converging tube with rounded corners, the mode of operation of the injector does not change as a whole and the cavity zone is located at the inlet of the diffuser. The operating characteristics given above enhance the cavitation in the liquid flow upon acceleration of the liquid flow.
    [56] The use of a diffuser (outlet 4 of the fluid passage channel) with a rounded outlet edge (see FIG. 2) makes it possible to improve the static state of the gas droplet jet flow from the injector. In this embodiment of the injector, the resulting jet is fixed from the longitudinal axial symmetry of the fluid passage channel and the oscillating fluctuations are eliminated.
    [57] The radius of the rounded circle of the diffuser outlet edge is also chosen between 1 and 2.5 times the radius of the cylindrical part 3 of the fluid passage channel of the injector. Increasing the radius of the rounded circle at the corner of the diffuser outlet reduces the effect of air vortex flow entering the diffuser during the process of separating the droplets from the resulting gas droplet jet. As a result, the droplet size of the resulting gas droplet jet increases. Based on the limitations described above, in the preferred embodiment the radius of the rounded circle of the corner is chosen to be equal to the diameter of the cylindrical part 3 of the fluid passage channel.
    [58] As the accelerated liquid-gas jet flows through the outlet section of the diffuser with an optimally shaped outlet edge, an axially symmetric annular vortex air stream is formed in the diffuser. This annular structure extends axially and does not cause disturbance at the diffuser outlet.
    [59] When a chamber 7 having a cylindrical channel 8 (see FIG. 3) is used in the preferred embodiment of the injector, the gas droplet jet is expanded and the small droplets are secondaryly separated by the perforated plate 9. The jet extends during passage through the channel 8 and stabilizes along the length of the channel, which is 10 to 30 times the diameter of the cylindrical portion 3 of the fluid passage channel of the injector. In a given length range for the cylindrical channel 8, velocity leveling is provided on the one hand over the section of the gas droplet jet, and on the other hand the required jet velocity is maintained. On impingement with the perforated plate 9, the droplet size of the gas droplet jet decreases on average 2 to 3 times.
    [60] The effect of the perforated plate 9 on the gas droplet jet structure produced in the fluid passage channel of the injector is eliminated by having air freely access the diffuser outlet section from the outside. This possibility is provided by selecting the total area of the holes in the perforated plate 9 in the range between 0.5 and 0.6 times the cross-sectional area of the cylindrical channel 8. As the area of the pores increases, the non-uniform droplet size is distributed in the resulting finely dispersed flow section, and the phenomenon of the inclusion of a separate liquid flow and gas (discontinuity of the liquid flow) may occur around the flow.
    [61] Optimal selection of the diameter "d" of the aperture of the perforated plate 9 (depending on the condition of 0.2 <d / D <0.7, where D is the diameter of the cylindrical part 3) gives time and the liquid flows into small droplets. Ensure even separation in space. If you choose a hole size smaller than the optimum value, the surface tension effect causes the liquid to stick into the aperture of the drilled plate. On the other hand, an increase in pore diameter “d” above the optimum value results in an increase in the size of the droplets in the resulting liquid-gas flow.
    [62] When the liquid supply pressure fluctuates over a wide range (increased by more than 10 times the initial normal level), the tangential openings 11 (see FIG. 3) formed in the chamber 7 are formed in the process of forming finely dispersed gas droplet jets. Provide additional vortex stabilization.
    [63] During operation of the injector air is blown out from the outside through four tangential openings 11 into the cylindrical channel 8, which tangential openings 11 are provided in two cross-sections of the cylindrical channel 8 of the chamber 7. Paired and symmetrically arranged. The ejection is caused by a decrease in vacuum (vacuum) at the diffuser outlet end when the gas droplet jet is accelerated. A chamber composed of an opening 11 formed in the chamber 7 in a tangential direction, a first plane extending near the diffuser outlet section, and a second plane extending near the exit section of the chamber 7. The symmetrical arrangement of the openings 11 in the two cross sections of (7) allows the ejected air to swirl evenly around the gas droplet jet. The vortex swirling of the inhaled air reduces the effect of the perforated plate 9 in the flow of the cylindrical channel 8 and minimizes the sticking of liquid in the aperture of the perforated plate 9. In addition, the operating mode of the injector enhances the process of mixing liquid droplets and air in the flow section, and consequently, increases the homogeneity of the droplet concentration upstream of the perforated plate 9. This eliminates the possibility of generating a separate liquid stream which affects the formation of homogeneous finely dispersed gas droplet jets.
    [64] Many studies have found that the optimum conditions for stabilizing gas droplet jets are made by setting a specific ratio of the cross-sectional area of the tangential opening between 0.5 and 0.9 with respect to the total area of the effective section of the perforated plate 9. The number and arrangement of tangential openings formed along the chamber 7 depends on the requirement for uniform mixing of the liquid gas flow.
    [65] The use of the chamber 12 (see FIG. 5) in the manufacture of the injector allows for further separation of droplets in the same direction of gas flow produced, and increases the arrival of the resulting finely dispersed gas droplet jets. The gas flow is produced through the output flow of gas from the high pressure gas source 13 to the annular passage formed between the outer surface of the injector casing 1 and the inner surface of the chamber 12 under excessive pressure of 0.25 to 0.35 MPa. . The optimum ratio of the liquid flow rate through the fluid passage channel of the injector and the gas flow rate through the annular passage of the chamber is between 90 and 25.
    [66] When the same direction of gas flow and pre-dispersed gas droplet jets are accelerated simultaneously in the nozzles of the chamber 12 consisting of the converging tube 14 and the diffuser 15, a narrow directional finely dispersed gas droplet jet is finally obtained. Is formed. While the gas droplet jet stream flows through the nozzle of chamber 12, large liquid droplets are separated due to the action of the surrounding gas flow and are secondaryly accelerated by the gas flow. At an initial liquid velocity of 45 m / s and an initial gas velocity of chamber 12 up to 80 m / s, the average velocity of the droplets in the resulting gas droplet jet is 30 m at a position 3.5 m away from the outlet section of the chamber nozzle. / s. The resulting gas droplet jet had a distribution of sufficiently homogeneous droplet sizes over the jet flow section. That is, the droplet size at the center of the jet was 190 to 200 μm, 175 to 180 μm in the annular zone, and 200 μm or more around the annular zone.
    [67] The operation of the injector designed according to the second embodiment of the present invention (see FIGS. 6 to 8) is performed in the same manner as that of the first embodiment of the present invention. The only difference is that the longitudinal dimension of the injector is reduced so that the gas jet is further optimized. The inlet portion 17 of the fluid passage channel of the injector is made conical and the radius of the rounded circle of the side surface is not smaller than the radius of the cylinder portion 18 of the fluid passage channel. This configuration of the inlet allows the kinetic energy loss of the gas droplet jet for generation of vortex flow in the converging tube to be reduced. The surface of the converging tube is continuously coupled to the surface of the cylinder 18 to provide acceleration of liquid flow and to preclude premature formation of the vortex flow upstream of the diffuser inlet end. In addition, the continuous reduction in the effective section of the short cone-shaped inlet section 17 of the channel allows the cavity center to be located near the diffuser inlet section. As a result, homogeneous concentration of finely dispersed gas droplet jets occurs with minimal energy loss.
    [68] Much research supports the possibility of producing a fixed, finely dispersed liquid stream with minimal energy consumption by the present invention. Improved identity of the droplet concentration distribution is provided over the flow sections so that the resulting flow maintains the shape and size of the flow sections at distances up to 10 m.
    [69] The claimed invention can be used in fire protection systems as part of a treatment facility for the combustion of fuels in thermal engineering and transportation, as well as for humidifying the surroundings and spraying disinfectants and pesticides. The invention can be used as part of fire extinguishing means in stationary and mobile units, and not only extinguish fire sources such as air, but also in different types of objects, ie hospitals, libraries and water pipes, and ships. To extinguish fire.
    [70] The claimed invention is illustrated by way of example of the preferred embodiments described above. However, it should be understood by those skilled in the art that minor modifications may be made in the industry when compared to the illustrated embodiments without departing substantially from the gist of the claimed invention.
    权利要求:
    Claims (29)
    [1" claim-type="Currently amended] Liquid injector comprising a casing (1) having a fluid passage channel consisting of an inlet (2) formed as a converging tube, a cylinder (3) and an outlet (4) formed as a conical diffuser, aligned on the same axis and sequentially joined To
    The length of the cylinder 3 is not smaller than its radius and not larger than the diameter, and the cone angle of the diffuser that constitutes the outlet 4 of the fluid passage channel constitutes the inlet 2 of the fluid passage channel. Liquid injector, characterized in that exceeding the cone angle of the converging tube.
    [2" claim-type="Currently amended] The liquid injector of claim 1, wherein the vertex angle of the cone forming the converging tube is between 6 degrees and 20 degrees, and the vertex angle of the cone constituting the diffuser is between 8 degrees and 90 degrees.
    [3" claim-type="Currently amended] 3. The liquid injector of claim 2, wherein the vertex angle of the cone constituting the converging tube is 13 degrees and the vertex angle of the cone constituting the diffuser is 20 degrees.
    [4" claim-type="Currently amended] 2. Liquid injector according to claim 1, characterized in that the inlet edges of the converging tubes constituting the inlet (2) of the fluid passage channel are rounded.
    [5" claim-type="Currently amended] 2. Liquid injector according to claim 1, characterized in that the outlet edges of the diffuser constituting the outlet (4) of the fluid passage channel are rounded.
    [6" claim-type="Currently amended] 6. Liquid injector according to claim 4 or 5, characterized in that the radius of the rounded part of the corner is 1 to 2.5 times the radius of the cylindrical part (3) of the fluid passage channel.
    [7" claim-type="Currently amended] 2. The liquid injector of claim 1, wherein the liquid injector comprises a chamber (7) having an inlet end connected to an outlet section of the diffuser, the diameter of the cylinder channel (8) of the chamber (7) being the diffuser outlet section. Liquid injector, characterized in that at least equal to the diameter of.
    [8" claim-type="Currently amended] 8. Liquid injector according to claim 7, characterized in that the diameter of the cylindrical channel (8) of the chamber (7) is 4 to 6 times the diameter of the cylindrical portion (3) of the fluid passage channel.
    [9" claim-type="Currently amended] 8. Liquid injector according to claim 7, characterized in that the length of the cylindrical channel (8) of the chamber (7) is 10 to 30 times the diameter of the cylindrical portion (3) of the fluid passage channel.
    [10" claim-type="Currently amended] 8. Liquid injector according to claim 7, characterized in that the grid or perforated plate (9) is located in the outlet section of the cylindrical channel (8) of the chamber (7).
    [11" claim-type="Currently amended] 11. Liquid injector according to claim 10, characterized in that the total cross-sectional area of the aperture of the perforated plate (9) or grid is 0.4 to 0.7 times the cross-sectional area of the cylindrical channel (8) of the chamber (7).
    [12" claim-type="Currently amended] 8. Liquid injector according to claim 7, characterized in that at least one tangential opening (11) is formed in the wall of the chamber (7) for blowing gas from the outside into the cylindrical channel (8) of the chamber (7).
    [13" claim-type="Currently amended] At least four tangential openings (11) are made in the wall of the chamber (7), the openings (11) being paired in two planes of the cylindrical channel (8) of the chamber (7). Arranged in a symmetrical manner, the first plane extending near the diffuser exit section and the second plane extending near the exit section of the chamber (7).
    [14" claim-type="Currently amended] 2. The liquid injector of claim 1, wherein the liquid injector comprises a chamber arranged on the same axis as the casing 1 on the outside of the casing 1, the gas under pressure being connected to the outlet 4 section of the fluid passage channel of the injector. Liquid injector, characterized in that at least one passage is formed between the outer surface of the casing and the inner surface of the chamber for feeding.
    [15" claim-type="Currently amended] 15. The chamber (12) according to claim 14, wherein the chamber (12) comprises a nozzle consisting of a converging tube (14) and a diffuser (15) arranged sequentially, the nozzle inlet section communicating with the outlet (4) of the fluid passage channel of the injector. Liquid injector, characterized in that.
    [16" claim-type="Currently amended] To a liquid injector comprising a casing 16 having a fluid passage channel consisting of an inlet 17 formed as a converging tube, a cylinder 18 and an outlet 19 formed as a diffuser, aligned on the same axis and sequentially joined. In
    The length of the cylindrical portion 18 is not at least smaller than its radius and not larger than its diameter, and the radius of the rounded portion of its side surface is at least equal to the radius of the cylindrical portion 18 of the fluid passage channel. A converging tube constituting the inlet portion (17) of the fluid passage channel is made of a conical shape.
    [17" claim-type="Currently amended] 17. The liquid injector of claim 16, wherein the vertex angle of the cone constituting said diffuser is between 8 degrees and 90 degrees.
    [18" claim-type="Currently amended] 17. The liquid injector of claim 16, wherein the conical shaped surface of the converging tube engages the surface of the cylindrical portion (18) of the fluid passage channel at an angle not exceeding two degrees.
    [19" claim-type="Currently amended] 17. The liquid injector according to claim 16, wherein the outlet edge of the diffuser constituting the outlet portion (19) of the fluid passage channel is rounded.
    [20" claim-type="Currently amended] 20. The liquid injector of claim 19, wherein the radius of the rounded portion of the diffuser outlet edge is one to two times the radius of the cylindrical portion (18) of the fluid passage channel.
    [21" claim-type="Currently amended] 17. The liquid injector of claim 16, wherein the liquid injector comprises a chamber 22 having a cylindrical channel 23 whose inlet is connected with a diffuser outlet section, the diameter of the cylindrical channel 23 of the chamber 22 being defined by the diffuser outlet section. Liquid injector, characterized in that at least equal to the diameter.
    [22" claim-type="Currently amended] 22. The liquid injector of claim 21, wherein the diameter of the cylindrical channel (23) of the chamber (22) is 4 to 6 times the diameter of the cylindrical portion (18) of the fluid passage channel.
    [23" claim-type="Currently amended] 22. The liquid injector of claim 21, wherein the length of the cylindrical channel (23) of the chamber (22) is 10 to 30 times the diameter of the cylindrical portion (18) of the fluid passage channel.
    [24" claim-type="Currently amended] 22. The liquid injector according to claim 21, wherein the grid or perforated plate (24) is located in the outlet section of the cylindrical channel (23) of the chamber (22).
    [25" claim-type="Currently amended] 25. The liquid injector of claim 24, wherein the total cross sectional area of the perforated plate (24) or grid is 0.4 to 0.7 times the cross sectional area of the cylindrical channel (23) of the chamber (22).
    [26" claim-type="Currently amended] 17. Liquid injector according to claim 16, characterized in that at least one tangential opening (26) is formed in the wall of the chamber for ejecting gas from the outside into the cylindrical channel (23) of the chamber (22).
    [27" claim-type="Currently amended] 27. A chamber according to claim 26, wherein at least four tangential openings 26 are paired in two cross sections of the cylindrical channel 23 of the chamber 22 symmetrically arranged on the wall of the chamber 22, Is extended near the outlet section of the diffuser and the second plane extends near the outlet section of the chamber (22).
    [28" claim-type="Currently amended] 17. The liquid injector according to claim 16, wherein the liquid injector comprises a chamber (27) arranged on the same axis as the casing (16) on the outside of the casing (16), the section of the outlet section (19) of the fluid passage channel under pressure At least one passage is formed between the outer surface of the casing (16) and the inner surface of the chamber (27) for supplying to the liquid injector.
    [29" claim-type="Currently amended] 29. The chamber (27) according to claim 28, wherein the chamber (27) comprises nozzles consisting of converging tubes (29) and diffusers (30) arranged sequentially, the nozzle inlet section communicating with an outlet portion (19) of said fluid passage channel. Liquid injector made.
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    同族专利:
    公开号 | 公开日
    NZ528574A|2005-03-24|
    CN1498137A|2004-05-19|
    SI1370367T1|2006-02-28|
    AU2002251620B8|2005-11-24|
    AP200302880A0|2003-12-31|
    DE60204857T2|2006-05-18|
    DK1370367T3|2005-10-17|
    CA2441405A1|2002-10-03|
    DE60204857D1|2005-08-04|
    AT298634T|2005-07-15|
    EP1370367A1|2003-12-17|
    WO2002076624B1|2002-12-27|
    ES2244766T3|2005-12-16|
    OA12593A|2006-06-08|
    MXPA03008600A|2005-03-07|
    HK1066186A1|2006-08-25|
    CN1236858C|2006-01-18|
    AP1570A|2006-02-08|
    RU2184619C1|2002-07-10|
    AU2002251620B2|2005-11-03|
    KR100555747B1|2006-03-03|
    BR0208293A|2004-04-13|
    JP2004532721A|2004-10-28|
    US7059543B2|2006-06-13|
    ZA200307341B|2004-07-14|
    EP1370367B1|2005-06-29|
    PT1370367E|2005-11-30|
    WO2002076624A1|2002-10-03|
    US20040124269A1|2004-07-01|
    JP4065410B2|2008-03-26|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    法律状态:
    2001-03-22|Priority to RU2001107433
    2001-03-22|Priority to RU2001107433/12A
    2002-03-21|Application filed by 안드레이 엘 두쉬킨, 알렉산더 브이 칼피쉐브
    2002-03-21|Priority to PCT/RU2002/000108
    2003-11-28|Publication of KR20030090685A
    2006-03-03|Application granted
    2006-03-03|Publication of KR100555747B1
    优先权:
    申请号 | 申请日 | 专利标题
    RU2001107433|2001-03-22|
    RU2001107433/12A|RU2184619C1|2001-03-22|2001-03-22|Liquid sprayer |
    PCT/RU2002/000108|WO2002076624A1|2001-03-22|2002-03-21|Liquid sprayers|
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