CN211835928U - Proportional mixer - Google Patents

Abstract

The application discloses a proportioner, comprising a shell; a first fluid passage for flowing water therethrough; a second fluid passage for flowing foam concentrate therethrough; a communication port provided to communicate the first fluid passage and the second fluid passage; a regulating valve disposed in the second fluid passage, the regulating valve configured to be adjustable based on a flow rate of water into the first fluid passage, thereby changing a flow rate of foam from the second fluid passage into the first fluid passage. This application can automatically regulated's governing valve through providing the aperture for when the scope of discharge is great, change the flow area of the governing valve of fluid flow through, and influence foam liquid flow from this, make foam liquid flow obtain changing under the dual influence of adsorption pressure and governing valve aperture, satisfy the mixed proportion requirement of foam liquid and water.

Description

Proportional mixer

Technical Field

The application relates to the field of fire-fighting equipment, in particular to a proportional mixer.

Background

The proportioner is a common device in the field of fire-fighting equipment, and is used for mixing foam concentrate and fire-fighting water according to a certain proportion range to obtain mixed liquid for extinguishing fire.

A venturi proportioner is a commonly used proportioner that creates a negative pressure (or a vacuum) that adsorbs the foam concentrate as the fire fighting water flows through the diminishing flow cross-section in the proportioner, which can affect the flow of the foam concentrate into the proportioner. Generally, when the flow rate of fire fighting water is in a certain range, the fire fighting water and the fire fighting water foam concentrate are influenced by fluid turbulence and boundary conditions to a certain extent, and the negative pressure and the flow rate of fire fighting water can be approximately in a linear relationship, so that the flow rate of the fire fighting water and the flow rate of the foam concentrate are in a certain proportion range. However, when the flow range of fire fighting water is too large, the fire fighting water and foam concentrate are affected by fluid turbulence and boundary conditions to an increased extent, and the negative pressure may not be in a completely linear relationship with the flow of fire fighting water, resulting in a ratio range where the flow of foam concentrate and the flow of fire fighting water cannot meet the requirements.

SUMMERY OF THE UTILITY MODEL

In order to solve the above problems, at least one object of the present application in a first aspect is to provide a proportioner that can be adapted for mixing fire water and foam concentrate in a large flow range, the proportioner comprising: a housing; a first fluid passage formed in the housing for passing water therethrough, the first fluid passage including: a convergent section, a throat section and a divergent section, the throat section being disposed between the convergent section and the divergent section; a second fluid passage formed in the housing for circulating a foam concentrate; a communication port provided on the housing at a throat portion of the first fluid passage and provided to communicate the first fluid passage and the second fluid passage so that the foam circulating in the second fluid passage can enter the first fluid passage; a regulating valve disposed in the second fluid passage, the regulating valve configured to be adjustable based on a flow rate of water into the first fluid passage, thereby changing a flow rate of foam from the second fluid passage into the first fluid passage.

According to the above first aspect, the regulator valve includes: the pore plate is connected in the second fluid channel, at least two through holes are formed in the pore plate, and an inlet of the second fluid channel is in fluid communication with the communication port through the at least two through holes; and a stopper configured to be movable relative to the orifice plate to open or close at least a portion of the at least two through-holes to vary a flow rate of the foam in the second fluid passage as a function of pressure at the communication port; wherein the pressure at the communication port reflects the flow rate of the water into the first fluid channel.

According to the first aspect described above, the orifice plate is vertically connected within the second fluid passage.

According to the above first aspect, the regulator valve further includes: a float assembly movably connected with the orifice plate; the blocking piece is arranged on the floating assembly and moves along with the movement of the floating assembly; wherein the float assembly is movable relative to the orifice plate along the second fluid pathway based on the pressure at the communication port to move the obstruction into or out of the at least two through-holes.

According to the first aspect described above, the float assembly comprises: the upper supporting plate is arranged on one side of the pore plate; the lower supporting plate is arranged on the other side of the pore plate; a connecting rod passing through the orifice plate to connect the upper support plate and the lower support plate such that the upper support plate and the lower support plate move together, wherein the connecting rod is perpendicular to the upper support plate and the lower support plate; and wherein the pressure at the inlet of the second fluid channel is reflected on the upper support plate and the pressure at the communication port is reflected on the lower support plate.

According to the above first aspect, the regulator valve further includes: an elastic member having one end fixed with respect to the orifice plate and the other end supported to the upper support plate or the lower support plate, the elastic member being capable of applying an elastic force to the upper support plate or the lower support plate.

According to the first aspect, the blocking member comprises at least one ejector pin, each of the at least one ejector pin extends from the surface of the upper support plate and/or the lower support plate and is aligned with one of the at least two through holes.

According to the first aspect described above, the at least one jack bar comprises at least two jack bars, the at least two jack bars having different lengths.

According to the first aspect, the elastic member includes a spring disposed between the orifice plate and the upper support plate or the lower support plate, wherein a top end of the spring is connected to the orifice plate, and a bottom end of the spring abuts against the upper support plate or the lower support plate.

According to the first aspect described above, the at least two through holes include at least two circles of through holes, and the stopper is configured to be able to open or close the through hole of an inner circle of the at least two circles of through holes.

The application provides an opening can automatically regulated's governing valve for when the scope of discharge is great, change the flow area of fluid flow through governing valve 120, and influence foam liquid flow from this, make foam liquid flow obtain changing under the dual influence of the pressure of intercommunication mouth department and governing valve opening, satisfy the mixed proportion requirement of foam liquid and water.

Drawings

FIG. 1A is a perspective view of one embodiment of the proportioner of the present application;

FIG. 1B is an axial cross-sectional view of the proportioner shown in FIG. 1A;

FIG. 2A is a perspective cross-sectional view of the portion of FIG. 1B outside the dashed box;

FIG. 2B is an enlarged partial view of the dashed box portion of FIG. 1B;

FIG. 3 is a perspective view of the float assembly and orifice plate of FIG. 2B;

FIG. 4 is a top view of the orifice plate of FIG. 3;

5A-5C are cross-sectional views of one embodiment of the regulator valve of FIG. 2B to illustrate an automatic adjustment process of the regulator valve;

FIG. 6 is a cross-sectional view of another embodiment of the regulator valve of FIG. 2B;

FIG. 7 is a cross-sectional view of yet another embodiment of the regulator valve of FIG. 2B.

Detailed Description

Various embodiments of the present application will now be described with reference to the accompanying drawings, which form a part hereof. It should be understood that although directional terms, such as "front," "rear," "upper," "lower," "left," "right," "top," "bottom," "inner," "outer," and the like may be used herein to describe various example structural portions and elements of the application, these terms are used herein for convenience of description only and are intended to be based on the example orientations shown in the figures. Because the embodiments disclosed herein can be arranged in a variety of orientations, these directional terms are used for purposes of illustration only and are not to be construed as limiting. Wherever possible, the same or similar reference numbers used in this application refer to the same or like parts.

Fig. 1A shows a perspective view of the proportional mixer 100 of the present application, and fig. 1B shows an axial cross-sectional view of the proportional mixer 100 shown in fig. 1A.

As shown in fig. 1A, the proportioner mixer 100 comprises a hollow housing 150, the housing 150 comprising a cylindrical section 151 and a flared section 152 connected to each other, and a branch section 153 extending from the cylindrical section 151. The flared section 152 has a smaller diameter end connected to a bottom surface of the cylindrical section 151, and the branch section 153 extends from a side surface of the cylindrical section 151.

As shown in fig. 1B, a first fluid passage 112 and a second fluid passage 113 are formed in the housing 150. The first fluid channel 112 extends through the cylindrical section 151 and the flared section 152, and the second fluid channel 113 extends through the branch section 153 anda cylindrical section 151 and communicates with the first fluid passage 112. The inlet of the first fluid channel 112 is the water inlet 102. The inlet of second fluid passage 113 is foam concentrate inlet 101. The outlet of first fluid channel 112 is mixed liquor outlet 103. Fire water (i.e., water) and foam concentrate flow into first fluid passage 112 and second fluid passage 113 of proportioner 100 from water inlet 102 and foam concentrate inlet 101, respectively, and then foam concentrate in second fluid passage 113 flows into first fluid passage 112 again, mixing with fire water in first fluid passage 112 and flowing out from mixed liquor outlet 103. The proportioner 100 further comprises a regulating valve 120 disposed in the second fluid passage 113, the regulating valve 120 being capable of being based on a flow rate Q of fire water into the first fluid passage 112₁Is adjusted so as to change the flow rate Q of the foam entering the first fluid passage 112 from the second fluid passage 113₂This will be described in detail later. In the embodiment shown in figure 1B, in use, the first fluid passage 112 is arranged transversely and the second fluid passage 113 is arranged longitudinally. In other embodiments, in use, the first fluid passage 112 may be arranged longitudinally and the second fluid passage 113 transversely.

As also shown in fig. 1B, the first fluid passage 112 includes a converging section 106, a throat 107, and a diverging section 108, which are connected in series. The cross-section (i.e., fluid flow area) of the convergent section 106 gradually decreases from the end forming the water inlet 102 to the end connected to the throat 107, and the fluid flow area of the divergent section 108 gradually increases from the end connected to the throat 107 to the end forming the mixed liquid outlet 103. The fluid flow area of the throat 107 remains substantially constant and is equal to the minimum flow area of the convergent section 106 and the minimum flow area of the divergent section 108.

Fig. 2A is a perspective cross-sectional view of a portion other than the dashed line frame in fig. 1B, for illustrating how the first fluid passage 112 and the second fluid passage 113 communicate with each other. As shown in FIG. 2A, the diverging section 108 of the first fluid passageway 112 is formed in the flared section 152, while the converging section 106 and throat 107 are formed by an inner shell structure 255 located in the cylindrical section 151. Inner housing structure 255 is also flared, forming an annular volume 210 surrounding inner housing structure 155 between inner housing structure 255 and cylindrical section 151, and second fluid passage 113 extends into volume 210. A communication port 209 is provided in the inner housing structure 255 at the throat 107, the communication port 209 extending through the inner housing structure 255 to communicate the second fluid passage 113 with the first fluid passage 112. The communication port 209 is provided as an annular opening provided around the circumference of the throat portion 107. By providing the annular communication port 209 and the annular volume 210, the foam concentrate in the second fluid passage 113 can enter the first fluid passage 112 along the circumferential direction of the first fluid passage 112, so that the foam concentrate and the water are more uniformly mixed.

As shown in fig. 1B and 2A, the fire water at the water inlet 102 typically has a certain supply pressure P1 from the water source, and the foam water at the foam inlet typically has a certain supply pressure P3 from the foam source. The above-described arrangement of the first fluid passage 112 causes a venturi effect to occur in the first fluid passage 112. According to the venturi effect, fire water entering first fluid passage 112 from water inlet 102, when flowing through constriction 106 to throat 107, increases in flow velocity in throat 107 due to the reduction in fluid flow area, but decreases in pressure, thereby creating a negative pressure P2 near communication port 209 of throat 107 (i.e., the inlet of foam concentrate from second fluid passage 113 into first fluid passage 112). The negative pressure P2 reflects the amount of pressure loss (i.e., pressure reduction) of the fire fighting water and is related to the flow rate of the fire fighting water. This negative pressure P2, which we refer to herein as the suction pressure P2, is capable of producing an adsorptive effect on the foam concentrate in the second fluid passage 113, thereby affecting the flow of foam concentrate from the second fluid passage 113 into the first fluid passage 112. It should be noted that P1, P2, and P3 actually refer to the pressure at the corresponding cross section of the fluid, i.e. the force of the fluid acting on the unit area perpendicularly.

Flow rate Q of water in the first fluid channel 112 at the water inlet 102₁(hereinafter referred to as "water flow rate Q₁") and the flow rate Q of the foam concentrate at the communication port 209 from the second fluid passage 113 into the first fluid passage 112₂(hereinafter referred to as "foam liquid flow rate Q₂") determines the proportion of foam concentrate in the mixed liquor provided by proportioner 100. It is usually necessary to mixThe proportion of the foam concentrate in the mixed solution is kept in a certain range of about 3 percent or a certain range of about 6 percent so as to meet the optimal fire extinguishing proportion of the standard requirement. Foam liquid flow rate Q₂Is determined by the supply pressure P3 of the foam, the suction pressure P2, and the fluid flow area of the regulator valve 120. Since the supply pressure P3 of the foam is controllable, the foam liquid flow Q is maintained if the fluid flow area of the regulator valve 120 is maintained constant₂It is substantially only affected by the suction pressure P2. Whereas if the adsorption pressure P2 and the water flow rate Q are₁In a predictable (e.g., linear) relationship, then foam concentrate flow rate Q₂Can receive the water flow Q₁Under the influence of (2) on the water flow rate Q₁When the foam liquid is changed, the foam liquid is automatically changed according to an expected formula, so that the proportion of the foam liquid in the mixed liquid can always meet the requirement.

However, the adsorption pressure P2 is not always equal to the water flow rate Q₁In a predictable relationship. Typically the adsorption pressure P2 will be affected by fluid turbulence and boundary conditions at the foam inlet end (i.e., communication port 209). Under ideal conditions, i.e., without completely considering the effects of fluid turbulence and boundary conditions at the foam inlet end (i.e., communication port 209), at P2 and Q₁Can establish a desired linear relationship according to which Q is known₁The expected value of P2 was calculated. When water flow rate Q₁Within a certain range, the adsorption pressure P2 is less affected by the fluid turbulence and the boundary condition of the foam inlet port (i.e., the communication port 209), and even if there is a slight difference between the actual value and the expected value of the adsorption pressure P2, it can be regarded as the water flow rate Q₁Approximately keeping the expected linear relation with the adsorption pressure P2 can ensure that the mixing ratio of the foam concentrate and the fire fighting water is within the range of fire fighting requirements. While the water flow rate Q₁Is larger, the adsorption pressure P2 is more influenced by the fluid turbulence and the boundary conditions of the foam inlet end (i.e., the communication port 209), and therefore the water flow rate Q is larger₁The mixing ratio of the foam concentrate and the fire fighting water cannot meet the fire fighting requirement due to the fact that the mixing ratio cannot be in a linear relation with the adsorption pressure P2 and the difference between the actual value and the expected value of the adsorption pressure P2 is large.

To this end, the present application provides a degree of opennessWith self-regulating valve 120 for regulating the water flow rate Q₁Is greater, the flow area of the fluid through the regulating valve 120 is changed and the foam concentrate flow Q is thereby influenced₂So that the flow rate Q of the foam concentrate is set₂The adsorption pressure P2 and the opening degree of the regulating valve 120 are changed under the double influence, and the mixing ratio requirement of the foam concentrate and the water is met.

Fig. 2B is a partially enlarged view of a dotted frame portion in fig. 1B for illustrating a specific structure of the regulator valve 120. As shown in fig. 2B, the regulator valve 120 includes an orifice plate 221, a float assembly 244, and a blocking member 229. At least two through holes 222 are formed in the orifice plate 221, and the orifice plate 221 and the branch section 153 are perpendicular to each other, so that the orifice plate 221 is vertically connected in the second fluid passage 113, so that the foam liquid entering from the inlet of the second fluid passage 113 (i.e., the foam liquid inlet 101) can flow through the orifice plate 221 only from the through holes 222 on the orifice plate 221, and then flows into the first fluid passage 112. A float assembly 244 is connected to the orifice plate 221 in an up and down movable manner, and a stopper 229 is provided on the float assembly 244 and is movable in response to movement of the float assembly 244 to open or close at least a portion of at least two of the through-holes 222 in the orifice plate 221 to reduce or increase a flow area for foam concentrate to flow through on the orifice plate 221.

The floating assembly 244 includes an upper support plate 226, a lower support plate 227, and a connecting rod 225, wherein the connecting rod 225 connects the upper support plate 226 and the lower support plate 227 through the orifice plate 221 such that the upper support plate 226 and the lower support plate 227 are movable together. Floating assembly 244 is subjected to a foam feed pressure P3 and an adsorption pressure P2 in secondary fluid passage 113, both of which act downwardly on floating assembly 244, causing floating assembly 244 to be subjected to two downward forces. Specifically, the supply pressure P3 of the foam concentrate acts on the upper support plate 226, and the upper support plate 226 is subjected to the force F₁And the suction pressure P2 acts on the lower support plate 227 to subject the lower support plate 227 to the force F₂. As one example, the surface area of the upper support plate 226 is equal to the surface area of the lower support plate 227.

The blocking member 229 includes at least one push rod formed to extend from the upper surface of the lower support plate 227 toward the through-hole 222 of the orifice plate 221. When the upper support plate 226 and the lower support plate 227 move up and down together, the lift pin can be inserted into the through-hole 222 to close at least a portion of the through-hole, or the lift pin can be moved away from the through-hole 222 to open the portion of the through-hole. As an example, the ejector pin of the blocking member 229 can be provided with different lengths. It should be noted that the blocking member 229 may also include at least one push rod extending from the lower surface of the upper support plate 226 toward the through hole 222 of the orifice plate 221, or the lower surface of the upper support plate 226 and the upper surface of the lower support plate 227 may be provided with push rods.

The adjusting valve 120 further includes a spring 243, and the spring 243 is fitted over the connecting rod 225, and has one end fixed to the lower surface of the orifice plate 221 and the other end connected to the upper surface of the lower support plate 227. As described above, floating assembly 244 is subjected to a downward fluid force from the fluid (i.e., force F exerted by suction pressure P2 on lower support plate 227₂And the force F of the foam concentrate supply pressure P3 acting on the upper support plate 226₁And) the spring 243 applies an upward pulling force to the floating assembly 244 so that the floating assembly 244 is floatingly coupled in the orifice plate 221 without the upper and lower support plates 226 and 227 abutting against the orifice plate 221. When water flow rate Q₁When held constant, the float assembly 244 is in a steady state and does not move relative to the orifice plate 221, and the fluid force experienced by the float assembly 244 is balanced with the spring force of the spring 243. When water flow rate Q₁When the adsorption pressure P2 changes, the fluid force applied to the floating assembly 244 also changes, and the floating assembly 244 moves upward or downward due to the spring 243 until the floating assembly 244 is balanced again between the fluid force applied to the floating assembly and the elastic force of the spring 243. As the floating assembly 244 moves up and down, the length of the spring 243 can be decreased or increased, so that the elastic force of the spring 243 is decreased or increased. By presetting the elastic coefficient of the spring 243 and the height of the ejector pin, it is possible to make Q proper₁When the amount is increased or decreased, the moving stroke of the spring 243 makes the rod open or close a part of the through hole 222, so that the adjusting process of the adjusting valve 120 is based on the water flow rate Q₁Is automatically performed according to the size ofIn (1).

It should be understood by those skilled in the art that the spring 243 may be other elastic members capable of applying an elastic force to the floating assembly 244. And since the upper support plate 226 and the lower support plate 227 move together, the spring 243 may also have one end fixed to the upper surface of the orifice plate 221 and the other end connected to the lower surface of the upper support plate 226.

Due to the flow rate Q of the fire water entering the first fluid channel 112₁The adsorption pressure P2 is affected, so the pressure differential between the foam concentrate supply pressure P3 and the adsorption pressure P2 (i.e., the sum of the absolute values of the pressures between the foam concentrate supply pressure P3 and the adsorption pressure P2) can reflect the flow rate of the fire fighting water. According to the flow Q of the fire water₁In contrast, the force F of foam concentrate supply pressure P3 on upper support plate 226₁Force F of the adsorption pressure P2 acting on the lower support plate 227₂And the spring force of the spring 243 will cause the upper support plate 226 and the lower support plate 227 to move up and down together relative to the orifice plate 221, and drive the rod to move up and down to open or close at least a part of the through holes 222.

When the adsorption pressure P2 is greatly different from the expected value, the inflow amount of the foam liquid is greatly different from the expected value, and the fire fighting water and the foam liquid cannot meet the requirement of proportional mixing. At this time, the inflow amount of the foam concentrate can be changed by opening or closing at least a part of the through-holes 222 so that the ratio of the foam concentrate and the fire water can meet the requirement. When a part of the through-holes 222 on the orifice plate 221 is opened, the flow area of the foam concentrate flowing through the orifice plate 221 is increased, enabling an increase in the inflow amount of the foam concentrate; when a part of the through-holes 222 on the orifice plate 221 is closed, the flow area of the foam concentrate flowing through the orifice plate 221 is reduced, and the inflow amount of the foam concentrate can be reduced.

The regulator valve 120 may be disposed within the second fluid passage 113 by any structure known in the art. In the embodiment shown in fig. 2B, a valve mounting structure 250 similar to a valve seat is provided at an upper portion of the branch section 153 of the proportional mixer 100, the valve mounting structure 250 is detachably mounted on a lower portion of the branch section 153, and the regulating valve 120 is detachably mounted in the valve mounting structure 250. The fluid passage in the valve mounting structure 250 forms the second fluid passage 113 together with the fluid passage in the lower portion of the branch section 153. Specifically, the valve mounting structure 250 includes a lower sleeve 232, an upper sleeve 231, and an outer sleeve 233, the outer sleeve 233 connecting the lower sleeve 232 and the upper sleeve 231 together by a fastening structure, such as threads. Lower bushing 232 is attached to the lower portion of branch section 153 by a fastening structure, such as threads. The orifice plate 221 of the regulator valve 120 is connected to the upper sleeve 231 and/or the lower sleeve 232 such that the regulator valve 120 is stationary inside the valve mounting structure 250. As a specific example, the interior of the lower bushing 232 has a ring of inwardly projecting bosses 239, the top edge of the orifice plate 221 of the regulator valve 120 has a ring of flanges 236, the lower surface of the flanges 236 abuts from above against the bosses 239 of the lower bushing 232 via sealing rings 238, and the upper surface of the flanges 236 abuts from below against the upper bushing 231. Thus, when the outer sleeve 233 couples the lower sleeve 232 and the upper sleeve 231 together, the upper sleeve 231 and the lower sleeve 232 can sandwich the orifice plate 221 from both the top and bottom directions to secure the orifice plate 221, thereby coupling the regulator valve 120 in the valve mounting structure 250. As an alternative example, the joints between the upper sleeve 231, the lower sleeve 232 and the outer sleeve 233 are further provided with sealing rings 237.

It should be noted that in other examples, the first fluid passage 112 may be longitudinally disposed and the second fluid passage 113 may be transversely disposed, with the regulator valve 120 being longitudinally coupled in the second fluid passage 113 and the float assembly 244 and the obstruction 229 moving transversely (left and right) relative to the orifice plate 221.

Fig. 3 is a perspective view of the control valve 120 without the spring 243 for more clearly showing the specific structure of the control valve 120. As shown in FIG. 3, the orifice plate 221 of the regulator valve 120 is a generally circular plate with an upper edge that projects outwardly to form a flange 236. The orifice plate 221 is provided with eight through holes 222 (see fig. 4) penetrating the orifice plate 221. The connecting rod 225 passes through the orifice plate 221 to connect the upper support plate 226 and the lower support plate 227 together. Wherein, the lower support plate 227 is provided with four top rods 229 extending to the hole plate 221, and the four top rods 229 have different lengths. Albeit as shown in the figureThe perspective view of fig. 3 shows only three push rods 229, but those skilled in the art will appreciate that one push rod 229 is covered by the connecting rod 225 at the rear side of fig. 3. In the embodiment shown in fig. 3, the top bar 229 comprises two long top bars 342 and two short top bars 341. When the upper and lower support plates 226 and 227 move relative to the orifice plate 221 in a certain stroke, the long push rods 342 can be inserted into two of the through holes to close the two through holes, while the short push rods 341 cannot be inserted into the other two through holes to open the two through holes. Thus, by providing the push rods 229 having different lengths, the number of open or closed through holes 222 can be changed twice, and the flow rate of the foam concentrate can be adjusted twice. Specifically, when the elastic coefficient k of the spring 243 is constant, the flow rate Q of fire fighting water is preset to be one of the flow rates Q₁(e.g., by comparison to a proportioner that does not include the regulator valve 120 to determine the preset fire water flow Q₁Value) that can be measured to obtain the actual value of the corresponding preset adsorption pressure P2, according to formula F₁+F₂Kx, the force F acting on the upper support plate 226 by the foam concentrate supply pressure P3₁And the force F of the actual value of the suction pressure P2 acting on the lower support plate 227₂In sum, a preset moving stroke (i.e., a stretched length x) of the spring 243 can be calculated, and the length of the short ejector pin 341 or the long ejector pin 342 is set with the preset moving stroke of the spring 243 as a threshold value so that a part of the inner race through-hole 482 or the entire inner race through-hole 482 can be just opened when the amount of deformation by the downward stretching deformation of the spring 243 reaches the preset moving stroke. For example, when the amount of deformation of the spring 243 reaches a preset first movement stroke (i.e., a first stretched length), the short ejector 341 can open two through holes, and when the amount of deformation of the spring 243 reaches a preset second movement stroke (i.e., a second stretched length), the long ejector 342 can open the other two through holes.

Fig. 4 is a plan view of the orifice plate 221 for explaining a specific structure of the through-holes 222 in the orifice plate 221. As shown in fig. 4, the at least two through holes 222 include eight through holes arranged in two circles of four through holes. Among them, the four inner ring through holes 482 can be opened or closed by the push rod 229 of the regulator valve 120, while the outer ring through hole 481 remains open. It will be appreciated by those skilled in the art that to ensure that the ejector pin 229 can open or close the inner ring through-hole 482, the inner ring through-hole 482 needs to be aligned with the ejector pin 229. It should be noted that the through holes 222 may be arranged in other numbers or in other manners, and only the number and the positions of the push rods 229 need to be correspondingly arranged.

A mounting hole 483 is further formed at the center of the orifice plate 221, and the connecting rod 225 passes through the mounting hole 483 to connect the upper support plate 226 and the lower support plate 227 to the upper and lower sides of the orifice plate 221. As an example, four clamping grooves are uniformly formed at the edge of the mounting hole 483, and a rib (not shown in the drawings) protruding outward in the radial direction of the connecting rod 225 may be at least partially formed on the connecting rod 225, and the clamping grooves and the rib are cooperatively arranged to prevent the connecting rod 225 from rotating relative to the orifice plate 221. Of course, other rotation preventing structures may be disposed between the orifice plate 221 and the connecting rod 225, so that the connecting rod 225 can be limited to move (i.e., move up and down or move longitudinally) only along the axial direction of the connecting rod 225 with respect to the orifice plate 221.

Fig. 5A-5C show cross-sectional views of a regulating valve 120 according to an embodiment of the present application in three different operating states, the regulating valve 120 being used in a proportional mixer in a proportional mixing device. With the proportioner used for such a proportioner, when the flow Q1 of fire water (i.e., the flow rate of fire water) is wide, the actual value of the suction pressure P2 is always larger than the expected value (i.e., the actual value of the absolute value of the negative pressure P2 is always smaller than the expected value), so that the actual flow of the foam concentrate tends to be smaller than the expected value (if the regulating valve 120 of the present application is not provided). As one example, a proportional mixer including a regulator valve 120 as shown in FIGS. 5A-5C may be suitable for use in a balanced proportional mixing device.

FIGS. 5A-5C are diagrams illustrating the flow Q of fire water as a proportioner₁(i.e., the flow rate of the fire water) is varied from small to large over a wide range (e.g., 4-100L/S), automatically adjusting the flow area of the foam through the regulator valve 120. In the operating state shown in fig. 5A-5C, the floating assembly 244 is subjected to fluid forces and springsThe elastic force of the spring 243 is balanced. Fig. 5A shows the state of the regulator valve 120 when the outer ring through hole 481 is open and the inner ring through holes 482 are all closed, fig. 5B shows the state of the regulator valve 120 when the outer ring through hole 481 is open, a part of the inner ring through holes 482 is open, and another part of the inner ring through holes 482 is closed, and fig. 5C shows the state of the regulator valve 120 when the inner ring through holes 482 and the outer ring through holes 481 are all open.

In the state shown in fig. 5A, the flow rate Q of fire water₁The minimum pressure loss of fire water is the minimum, the adsorption pressure P2 at the communication port reaches the maximum (namely the absolute value of the negative pressure P2 is the minimum), and the acting force F on the supporting plate 227 under the action of the adsorption pressure P2₂And minimum. Since the force of foam concentrate supply pressure P3 on upper support plate 226 remains constant, the tensile spring force of spring 243 is at a minimum at this time, i.e., the amount of downward tensile deflection of spring 243 is at a minimum, and floating assembly 244 is at an uppermost position relative to orifice plate 221. The long post rod 342 and the short post rod 341 are inserted into the inner ring through holes 482 to close all the inner ring through holes 482. At this time, only the outer ring through hole 481 on the orifice plate 221 is opened, and the inner ring through hole 482 is completely closed, so that the foam concentrate flow rate Q is increased₂And correspondingly minimal.

In the state shown in fig. 5B, the flow rate Q of fire water is compared with the state shown in fig. 5A₁The pressure loss of the fire water increases, the adsorption pressure P2 decreases (i.e., the absolute value of the negative pressure P2 increases), and the force F of the adsorption pressure P2 acting on the lower support plate 227 increases₂And is increased. Force F acting on upper support plate 226 due to foam concentrate supply pressure P3₁The tensile elastic force of the spring 243 is maintained as compared with that of FIG. 5A due to F₂Increasing, the amount of downward-extending deformation of the spring 243 increases to reach a first travel stroke (i.e., a first extended length), the floating assembly 244 moves downward a distance relative to the orifice plate 221, but the long push rod 342 is still inserted into a portion of the inner ring through-hole 482 to close the portion of the inner ring through-hole 482, and the short push rod 341 leaves another portion of the inner ring through-hole 482 to open the portion of the inner ring through-hole 482.

At this time, since the fire-fighting water and the foam concentrate are affected by the fluid turbulence and the boundary conditions, the fire-fighting water and the foam concentrate are mixed with each otherIf the suction pressure P2 is different from the expected value, the floating assembly 244 will not move downwards to open a part of the inner ring through holes 482, and the flow rate Q of the foam concentrate is obtained₂Will be less than expected. At this time, a part of the inner-ring through holes 482 of the orifice plate 221 is opened, so that the flow rate Q of the foam concentrate is increased₂Can be compensated, and the requirement of the mixing proportion of the fire-fighting water and the foam liquid can be met.

In the state shown in fig. 5C, the flow rate Q of fire water is compared with the state shown in fig. 5A and 5B₁The maximum pressure loss of the fire water is achieved, the adsorption pressure P2 is the minimum (i.e. the absolute value of the negative pressure P2 is the maximum), and the acting force F of the adsorption pressure P2 acting on the lower support plate 227 is the maximum₂And max. Force F acting on upper support plate 226 due to froth supply pressure P3₁While the tension elastic force of the spring 243 is maximized, the downward tension deformation of the spring 243 is maximized to reach the second moving stroke (i.e., the second tension length), the floating assembly 244 is at the lowermost position with respect to the orifice plate 221, and the long lift pins 342 and the short lift pins 341 are separated from the inner ring through holes 482 to open all the inner ring through holes 482.

At this time, since the fire water and the foam concentrate are affected by the fluid turbulence and the boundary conditions such that the adsorption pressure P2 has a larger difference from the expected value, if the floating assembly 244 does not move down to open all of the inner-ring through-holes 482, the flow rate Q of the foam concentrate is increased₂Will be less than expected. At the moment, all inner ring through holes 482 on the pore plate 221 are opened together, so that the flow of the foam concentrate is compensated to a greater extent, and the requirement of the mixing ratio of the fire fighting water and the foam concentrate is met.

FIG. 6 illustrates a cross-sectional view of a regulator valve 620 according to another embodiment of the present application. In this embodiment, the push rods 651 and 652 are provided to extend from the lower surface of the upper support plate 626 toward the through hole of the orifice plate 221, while the push rods are not provided on the lower support plate 627.

The regulating valve 620 in the embodiment shown in fig. 6 is used for a proportional mixer in another proportional mixing device in which the actual value of the adsorption pressure P2 is always smaller than the expected value (i.e., the actual value of the absolute value of the negative pressure P2 is always smaller than the expected value)Large value), if the regulating valve 620 of the present embodiment is not provided, the actual flow rate Q of the foam concentrate₂And the mixing ratio of the fire-fighting water and the foam concentrate is larger than the expected value, so that the fire-fighting requirement cannot be met.

In the present embodiment, when the amount of deformation of the downward tensile deformation of the spring 243 reaches a predetermined displacement stroke (i.e., a tensile length), a part of the inner-ring through-hole 482 can be closed, thereby reducing the flow rate of the foam concentrate. In this embodiment, the lift pins include a long lift pin 652 and a short lift pin 651, so that the flow rate Q of the foam concentrate can be reduced twice as well₂。

As a more specific example, a proportional mixer including a regulator valve 620 as shown in FIG. 6 may be adapted for use with a pressure-type proportional mixing device.

FIG. 7 illustrates a cross-sectional view of a regulator valve 720 according to another embodiment of the present application. In this embodiment, a part of the lift pins 751 is provided to extend from the lower surface of the upper support plate 726 toward the through-hole of the orifice plate 221, and the other parts of the lift pins 341 and 342 are provided to extend from the upper surface of the lower support plate 727 toward the through-hole of the orifice plate 221.

The regulating valve 720 in the embodiment shown in fig. 7 is used for a proportioner in another proportional mixing device in which the water flow rate Q is set₁In the first range, the actual value of the adsorption pressure P2 is greater than the expected value (i.e., the actual value of the absolute value of the negative pressure P2 is less than the expected value), and if the control valve 720 of the present application is not provided, the actual flow rate Q of the foam concentrate is set₂And the mixing ratio of the fire-fighting water and the foam concentrate can be smaller than the expected value, so that the fire-fighting requirement can not be met. While the water flow rate Q₁In a second range greater than the first range, the actual value of the suction pressure P2 is again smaller than expected (i.e., the actual value of the absolute value of the negative pressure P2 is greater than expected), and if the regulating valve 720 of the present application is not provided, the actual flow rate Q of the foam concentrate is again reduced₂And the mixing ratio of the fire-fighting water and the foam concentrate can not meet the fire-fighting requirement.

In the present embodiment, when the water flow rate Q is high₁When increased to allow downward movement of the floating assembly 744, i.e. when the floating assembly 744 is moved downwardThe flow area of the foam through the regulator valve 720 may be increased or the flow area of the foam through the regulator valve 720 may be decreased. When water flow rate Q₁Within the first range, the floating member 744 moves downward, and the spring 243 is stretched downward to a predetermined amount corresponding to the movement strokes (i.e., stretching lengths) of the lift rods 341 and 342, so that at least a part of the inner-ring through-hole 482 can be opened to increase the foam concentrate flow rate Q₂。

While the water flow rate Q₁When the flow rate increases to be within the second range, the floating assembly 744 continues to move downwards, and the spring 243 is stretched downwards to be deformed to close at least a part of the inner ring through hole 482 when the deformation reaches a predetermined moving stroke (i.e. stretching length) corresponding to the push rod 751, so as to reduce the foam liquid flow rate Q₂。

The proportioner 100 of the present application can be based on the flow rate Q of fire water entering the first fluid passage 112 by providing the regulating valve 120 in the second fluid passage 113₁While automatically regulating the flow rate Q of foam concentrate from second fluid passage 113 into first fluid passage 112₂Thereby ensuring that the mixing ratio of the fire-fighting water and the foam concentrate is within the ratio range required by fire fighting. Accordingly, the proportioner 100 of the present application is particularly suited for use in situations where the fire water flow range is large. Moreover, the proportioner 100 of the application has the advantages of little change to the existing proportioner, low improvement cost and strong practicability.

Although the present application will be described with reference to the particular embodiments shown in the drawings, it should be understood that many variations of the proportioner of the application can be made without departing from the spirit and scope of the teachings of the application. Those of ordinary skill in the art will also realize that there are different ways of varying the details of the structures in the embodiments disclosed in this application that fall within the spirit and scope of the application and the claims.

Claims (10)

1. A proportioner, characterized by: the proportioner comprises:

a housing;

a first fluid passage formed in the housing for passing water therethrough, the first fluid passage including:

a convergent section, a throat section and a divergent section, the throat section being disposed between the convergent section and the divergent section;

a second fluid passage formed in the housing for circulating a foam concentrate;

a communication port provided on the housing at a throat portion of the first fluid passage and provided to communicate the first fluid passage and the second fluid passage so that the foam circulating in the second fluid passage can enter the first fluid passage;

a regulating valve disposed in the second fluid passage, the regulating valve configured to be adjustable based on a flow rate of water into the first fluid passage, thereby changing a flow rate of foam from the second fluid passage into the first fluid passage.

2. The proportioner of claim 1 wherein: the regulating valve includes:

the pore plate is connected in the second fluid channel, at least two through holes are formed in the pore plate, and an inlet of the second fluid channel is in fluid communication with the communication port through the at least two through holes; and

a stopper configured to be movable relative to the orifice plate to open or close at least a portion of the at least two through-holes to vary a flow rate of foam in the second fluid passage as a function of pressure at the communication port;

wherein the pressure at the communication port reflects the flow rate of the water into the first fluid channel.

3. The proportioner of claim 2 wherein:

the orifice plate is vertically connected within the second fluid passage.

4. The proportioner of claim 3 wherein: the governing valve still includes:

a float assembly movably connected with the orifice plate;

the blocking piece is arranged on the floating assembly and moves along with the movement of the floating assembly;

wherein the float assembly is movable relative to the orifice plate along the second fluid pathway based on the pressure at the communication port to move the obstruction into or out of the at least two through-holes.

5. The proportioner of claim 4 wherein: the float assembly includes:

the upper supporting plate is arranged on one side of the pore plate;

the lower supporting plate is arranged on the other side of the pore plate;

a connecting rod passing through the orifice plate to connect the upper support plate and the lower support plate such that the upper support plate and the lower support plate move together, wherein the connecting rod is perpendicular to the upper support plate and the lower support plate; and

wherein a pressure at the inlet of the second fluid channel is reflected on the upper support plate and a pressure at the communication port is reflected on the lower support plate.

6. The proportioner of claim 5 wherein: the governing valve still includes:

an elastic member having one end fixed with respect to the orifice plate and the other end supported to the upper support plate or the lower support plate, the elastic member being capable of applying an elastic force to the upper support plate or the lower support plate.

7. The proportioner of claim 6 wherein:

the blocking member comprises at least one ejector rod, each of the at least one ejector rod extends out from the surface of the upper supporting plate and/or the lower supporting plate and is aligned with one of the at least two through holes.

8. The proportioner of claim 7 wherein:

the at least one ejector pin comprises at least two ejector pins, and the at least two ejector pins have different lengths.

9. The proportioner of claim 6 wherein:

the elastic component comprises a spring, the spring is arranged between the pore plate and the upper supporting plate or the lower supporting plate, the top end of the spring is connected to the pore plate, and the bottom end of the spring is abutted to the upper supporting plate or the lower supporting plate.

10. The proportioner of claim 2 wherein:

the at least two through holes include at least two circles of through holes, and the stopper is configured to be able to open or close the through hole of an inner circle of the at least two circles of through holes.

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