JP3192927U - Jet pump - Google Patents

Abstract

To provide a jet pump capable of increasing the efficiency of pressure fluid energy conversion and selecting the head and discharge amount of a water-absorbing material according to the capacity of a pressure pump.
A pressure flow injected from an air layer forming tube 58 passes through a suction chamber space 68 that is approximately the same distance as the inner diameter of the suction tube 63 until reaching the energy conversion tube 61, but air is contained in the outer periphery of the pressure flow. Since it is covered with a pressure flow and is constricted and compressed by a rectifying groove of the air layer forming tube to become a high-speed fluid, it goes straight into the energy conversion tube having the same shape as the hole diameter of the air layer forming tube without increasing diffusion. Since the pressure flow inlet end face of the energy conversion tube has a wide angle, the pressure flow that enters and leaks into the energy conversion tube is extremely reduced.
[Selection] Figure 4

Description

  The present invention relates to an air-jet jet pump that pumps individual liquids indispensable for a contaminated soil purification system. More specifically, the present invention sucks and pumps a solid mass containing a fluid, or reduces the negative pressure of a suction dehydrator. The present invention relates to a pressure fluid energy conversion device of a jet pump for forming or transferring from a low position to a high position.

  A conventional Venturi-type negative pressure forming device, which is a conventional jet pump, injects pressurized fluid from an injection nozzle and causes the pressure fluid to flow through the Venturi or throat at approximately sonic speed, and this part is subjected to Bernoulli's theorem. The jet pump is very susceptible to turbulence and cavitation in the venturi or throat because it has a structure in which negative pressure is generated and the generated negative pressure is taken out and used. It was.

  Therefore, the diameter of the venturi section or the throat section and the flow diameter of the pressure fluid that flows them are not always kept in a constant relationship, and the good efficiency of the jet pump cannot be maintained. Therefore, when setting the diameter of the venturi section or the throat section, the flow velocity of the pressure fluid that flows these, and the diameter of the flow, the settings of the diameter of the injection nozzle that injects the pressure fluid and the pressure of the pressure pump are also individually set. There was a problem that it had to be done at the same time according to the work.

  Even if the venturi part or throat part diameter, the diameter of the injection nozzle that injects the pressure fluid, and the pressure of the pressurizing pump for forming the pressure fluid are individually set according to the work, the negative pressure is still in the venturi part. Or, since it is formed only at the throat part, the suction negative pressure acting as a back pressure on the venturi part or the throat part constantly fluctuates due to the change in the amount of suction, and the good negative pressure formation efficiency of the jet pump cannot be maintained. .

  Therefore, it is difficult to set the flow diameter of the pressurized fluid that flows the bore diameter of the venturi section or the throat section. Or just rely on accumulated experience.

  In addition, since the negative pressure is formed at the venturi or throat part, the pipe diameter through which the pressure fluid flows when calculating the negative pressure formed at the part away from the venturi or throat part. In addition to the taper shape, the flow diameter of the pressure fluid that flows is gradually expanding, the reference position for the calculation of both is not fixed, and the calculation formula for the work amount for practical use is not established . Therefore, as described above, it is the present situation that the experimental values and empirical rules must be relied upon as materials for designing the jet pump.

  More specifically, when the slurry containing solid agglomerates is used for suction / conveyance, etc., surpassing a jet pump, the specific gravity of the slurries containing the solid agglomerates increases, and cavitation occurs, Damage due to contact with or collision with the throat portion is severe, and as the injection pressure is increased, the degree of damage increases exponentially.

  Therefore, the jet pump has a problem that the negative pressure for suction and the pressure for conveyance can be used only in a relatively low pressure range in order to prevent damage due to cavitation and damage due to solid mass. In the structure of the conventional jet pump limited to such a certain condition, as described above, any one of the injection pressure of the injection nozzle, the diameter of the injection nozzle, the throat diameter, and the distance between the injection nozzle and the throat opening start end is selected. Even if it is changed, performance will be unstable.

  Furthermore, when the injection pressure of the pressure fluid is increased, the flow diameter of the pressure fluid immediately expands by cavitation due to the pressure fluid, exceeds the throat opening cross-sectional area, and a part of the pressure fluid flows backward in the decompression chamber, Damage to the open end of the throat becomes significant due to the solid mass contained in the backflowing pressure fluid. For this reason, the balance between the diameter of the opening end of the throat and the diameter of the injection nozzle is very delicate, resulting in a limited range of use for a jet pump having a single structure.

  There exists patent document 1 as a method which improved said point.

Japanese Laid-Open Patent Publication No. 10-9216

  In FIG. 2 of the patent document 1, a water storage tank 32, a pressure pump 34 for pressurizing water 33 stored in the water storage tank 32, and an injection nozzle 35 for injecting pressure water pressurized by the pressure pump 34, The injection nozzle 35 includes an air layer forming pipe 36 on the lower side of the injection direction and an energy conversion tube 38 disposed on the lower side of the air layer forming pipe 36 with a conversion energy first extraction space 37 interposed therebetween.

  The injection nozzle 35 and the air layer forming pipe 36 are integrally formed with a casing 39. That is, the injection nozzle 35 is formed by inserting a small-diameter injection port 40 from one end of a round bar-shaped casing 39 to a substantially intermediate position of the casing 39, and the air layer forming pipe 36 is formed from the other end of the casing 39. A jet flow hole 52 having a diameter larger than that of the 35 injection ports 40 is formed, and an intake port 42 provided with an intake pipe 43 is provided at an end of the jet flow hole 52 on the injection nozzle 35 side.

  The energy conversion tube 38 is formed in a straight tubular shape having a diameter larger than that of the air layer forming tube 36, and the straight tube portion has a length three times or more the diameter of the inlet side. A portion on the air layer forming tube 36 side becomes 44, and a converted energy second extraction port 45 is formed on the discharge side on the lower side of a virtual continuous piston described later of the energy conversion tube 38.

Next, the operation of the jet pump formed as described above will be described.
First, the pressure pump 34 is driven to suck and pressurize the water 33 stored in the water storage tank 32 from the strainer 50, and this pressurized high-pressure fluid is injected from the injection nozzle 35 into the air layer forming pipe 36. Spray. When the high-pressure fluid is thus injected from the injection nozzle 35 into the air layer forming pipe 36, the jet stream 51 in the air layer forming pipe 36 has a velocity in the jet flow hole 52 in the air layer forming pipe 36. Becomes negative pressure by Bernoulli's theorem, and the outside air is sucked into the air layer forming pipe 36 from the intake pipe 42 through the intake port 43.

  Since the air sucked into the air layer forming pipe 36 is adsorbed by the jet stream 51 flowing therethrough and flows together with the jet stream 51, the jet stream 51 is surrounded by air as shown by an imaginary line in FIG. The layer 41 is formed and enters the energy conversion tube 38. The jet flow 51 that has entered the energy conversion tube 38 reduces friction between the outer stationary air layer and the inner peripheral surface portion of the energy conversion tube 38 by the air layer 41 formed around the jet flow 51. The flow diameter of the jet stream 51 is prevented from being attenuated while the flow diameter is not widened and the thickness of the surrounding air layer 41 is gradually reduced.

  In this way, when the jet stream 51 flows in the energy conversion tube 38, it flows while overcoming the resistance 55 indicated by the black arrow in the energy conversion tube 38 in FIG. When the resistance 55 in the energy conversion tube 38 is strong and the jet flow 51 is spread at once, a virtual piston 56 that continuously acts in the direction of the outlet is formed in the energy conversion tube 38 at the dotted line mesh pattern portion. .

  A negative pressure is formed in the upper side portion of the virtual piston 56, and the space portion of the lower side portion of the virtual piston 56 in the jet flow is compressed. The negative pressure formed in the upper portion of the virtual piston 56 is taken out as a suction negative pressure from the converted energy first take-out port 54 and used as suction negative pressure sludge and a suction negative pressure of the dehydrator. Further, the applied pressure compressed by the lower side portion of the jet flow 51 of the virtual piston 56 pumps the sucked sludge from the conversion energy second take-out port 45 to the solid-gas-liquid separator or the dehydration installed at a high place. It is used to fry to the device.

  Next, a method for calculating the head pressure at the time of frying from the converted energy second outlet 45 to the dehydrator installed at a high place will be described. The head pressure from the converted energy second outlet 45 is expressed by dividing the pressure fluid pressure by the area ratio between the area of the energy conversion tube 38 and the area of the injection nozzle and multiplying this by the density change rate.

This is expressed by the following formula.
When the unit of jet injection pressure P as a driving source is input in kg / cm 2, the head h = [p × 10 / (m / a)] × av, and the unit of the head ph of the driving pump is input as m. In this case, the head ph = [p / (m / a)] × av.

The symbol m used in the above formula is the cross-sectional area of the energy conversion tube, and its unit is m.
2, av is the density change rate of the mixed jet taking into account the gas expansion due to compression release in the energy conversion tube and the velocity energy inertia force.

  Using the above formula, for example, the pressure fluid of a pressure fluid having a head height p = 300 m (3000 kg / cm 2 in terms of jet flow injection pressure) and an injection nozzle diameter a = 5 mmφ and an energy conversion tube diameter m = 100 mmφ is used. When the head h of the energy conversion device is calculated, [300 × 10 / (0.00785 / 0.000019625)] × 1.85 = 13.875 m. That is, a lifting force of 13.875 m can be obtained. Incidentally, the calculation of the pumping amount q in this case is expressed by the pumping amount q = [(m−a) × (√ (h × 19.6)] × qx.

  In the above calculation formula, qx is a liquid slip ratio in consideration of resistance in the flow pipe and the like, and in this example, qx = 0.5556. Therefore, the pumping amount q = [(0.0078304) × (√ (13.875 × 19.6))] × 60 × 0.556 = 4.30747 m 3 / min in this example. Based on these, the numerical values of the structure and function of the energy conversion device for pressure fluid are calculated as follows.

(1) Injection nozzle diameter ... 5.00mm
(2) Jet injection pressure: 300.00kg / cm2
(3) Amount of jet water used: 285.36 l / min
(4) Energy conversion tube diameter: 100.00mm
(5) Maximum head ... 13.88m
(6) Maximum pumping volume ... 4.30m3 / min
(7) True specific gravity ... 2.60
(8) Porosity ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ 0.60
(9) Apparent specific gravity: 1.56
(10) Total specific gravity ... 1.96
(11) Suction sand content: 30.00%
(12) Emission sand content rate: 28.13%
(13) Specific gravity loss: 2.95m
(14) Amount of jet water: 0.29m3 / min
(15) Total water volume and total flow volume ... 3.67m3 / min
(16) Flow pipe length ... 50.00m
(17) Flow pipe diameter ... 200.00mm
(18) In-pipe friction coefficient ... 0.80
(19) Flow velocity in the flow pipe ... 1.95m / sec
(20) Loss head due to resistance in flow pipe ... 0.87m
(21) Total actual lifting head ... 3.82m
(22) Available head [(5)-(21)] 10.05m
(23) Head balance ... 0.05m
(24) Final pumping volume ... 3.12m3 / min
(25) Unloading sand volume per minute ... 0.94m3 / min
(26) 1 day (8 hours continuous) amount of unloading sand ... 449.03 m3 / day

  Next, an energy conversion device for pressure fluid of a pressure fluid with a lift pressure p = 50 m (5 kg / cm 2 in terms of jet flow injection pressure) and an injection nozzle diameter a = 50 mmφ and an energy conversion tube diameter m = 100 mmφ is shown. When the head h is calculated, [5 × 10 / (0.00005 / 0.000019625)] × 1.85 = 23.125 m. That is, a lifting force of 23.125 m can be obtained. Incidentally, the pumping amount q in this case is the watering amount q = [(0.0058875) × (√ (23.125 × 19.6))] × 60 × 0.556 = 4.1784 m 3 / min. Based on these, the numerical values of the structure and function of the energy conversion device for pressure fluid are calculated as follows.

(1) Injection nozzle diameter ... 50.00mm
(2) Jet injection pressure ... 5.00kg / cm2
(3) Amount of jet water used ... 368.92 l / min
(4) Energy conversion tube diameter: 100.00mm
(5) Maximum head: 23.13m
(6) Maximum pumping volume ... 4.18m3 / min
(7) True specific gravity ... 2.60
(8) Porosity ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ 0.60
(9) Apparent specific gravity: 1.56
(10) Total specific gravity ... 1.96
(11) Suction sand content: 30.00%
(12) Emission sand content rate: 15.94%
(13) Specific gravity loss: 3.07m
(14) Amount of jet water ... 3.68m3 / min
(15) Total water volume and total flow rate ... 7.31 m3 / min
(16) Flow pipe length ... 100.00m
(17) Flow pipe diameter ... 200.00mm
(18) In-pipe friction coefficient ... 0.80
(19) Flow velocity in the flow pipe ... 3.88 m / sec
(20) Loss head due to resistance in the flow pipe, etc. 6.91m
(21) Total lift head: 9.98m
(22) Available head [(5)-(21)] 13.15m
(23) Head balance ... 3.15m
(24) Final pumping amount ... 2.38m3 / min
(25) Unloading sand amount per minute ... 0.71m3 / min
(26) 1 day (8 hours continuous) amount of unloading sand ... 340.80m3 / day

  As is apparent from the above, in the fluid energy conversion device of this example, when the lifting force of the pressurizing pump, that is, when the pressure of the injection nozzle is high, the diameter of the injection nozzle is reduced, and when the pressure is low, the diameter of the injection nozzle is increased. It is possible to secure a sufficient lifting force and pumping capacity simply by doing.

  FIG. 2 shows an embodiment of the jet pump. In the figure, 23 is a nozzle, 24 is a cabless tube, 25 is a high pressure water mounting flange, 26 is an air introduction valve, 27 is a delivery, 28 is a water supply outer cylinder, 29 is a solid lump suction port, and 30 is a water supply outer cylinder. It is a mounting flange.

  By the way, in the conventional jet pump, the diameter of the energy conversion tube is made larger than the diameter of the injection nozzle to fill the pressure in consideration of the diffusion of the jet flow injected from the air layer forming pipe. Therefore, a gap is generated in the energy conversion tube. For this reason, the negative pressure generated by the Venturi effect causes a reverse flow resistance in the energy conversion tube, and the pressure fluid energy conversion efficiency is lowered.

  According to the description of the conventional jet pump, the energy injection pressure is 300.00 kg / cm 2 (pressure pump lift 3000 m), the lift is 10.05 m, the pumping amount is 3.12 m 3 / min, When the injection pressure is 5.00 kg / cm 2 (pressurizing pump 50 m), the head is 13.15 m and the pumping amount is 2.38 m 3 / min, and the pump is used regardless of the capacity of the energy injection pressure, that is, the capacity of the pressurizing pump. It is shown that there is almost no change in the head and the pumping amount (discharge amount). In other words, it is to change the diameter of the injection nozzle according to the capacity of the pressurizing pump to be used, and is independent of the water discharge amount and the head required at the work site, and the work content is naturally limited. It will be.

  The present invention seeks to solve the problems of such a conventional jet pump configuration, and enhances the pressure fluid energy conversion efficiency and raises the water absorption object according to the capacity of the pressure pump. An object of the present invention is to realize a jet pump capable of selecting a discharge amount.

  In order to solve the above-mentioned conventional problems, the present invention is applied to a jet pump having a hole that penetrates an injection nozzle, an air layer forming tube, and an energy conversion tube on the same straight line from the upper direction of pressure flow inside a sealed casing. The hole diameter of the injection nozzle connected to the pipe extending from the pressure pump has substantially the same diameter as the pipe inner diameter, and the diameter of the hole is tapered toward the lower side in the pressure flow direction from the hole diameter connected to the pipe to the middle part of the injection nozzle. The so-called trumpet shape is made smaller in size, extending from the substantially middle part of the injection nozzle toward the lower side of the pressure flow, extending the hole having the same diameter as the above-mentioned in parallel to the injection nozzle outlet end, and cross-sectioning the inner wall of the parallel hole diameter part A rectifying groove is provided at the same position and at equal intervals radially from the center portion of the upper hole diameter, and the rectifying groove is extended in parallel with the hole center line from the position of the taper minimum diameter to the injection nozzle outlet end. Have that structure.

  In the above structure, the piping is connected by various curved pipes from the pressure pump to the injection nozzle, and if there is no rectifying groove, the pressure flow passing through the inside of the pipe has the inertia of this curved pipe. Although the pressure flow is diffused when discharged from the nozzle, the straightening property is maintained even after the discharge from the spray nozzle by the rectifying groove. The principle is the same as that of a current plate applied in a so-called water tap.

  An air layer forming pipe having a hole diameter larger than the injection nozzle outlet end hole diameter on the same line as the injection nozzle hole diameter center line in the pressure flow down direction from the injection nozzle, and the hole diameter of the air layer forming pipe is a pressure inflow end And the pressure outflow end portion are penetrated in parallel with the same diameter, and the inner wall of the hole diameter portion is provided with a rectifying groove radially at the same position and at equal intervals from the center of the hole diameter on the cross section, from the pressure flow end portion of the air layer forming pipe An air inlet having a structure extending in parallel with the hole center line to the pressure outflow end portion of the air layer forming pipe and penetrating the casing in the gap between the injection nozzle and the air layer forming pipe Connected to the intake port, an intake pipe is provided outside the casing, and a control valve is provided in the intake pipe.

  With this structure, when the pressure flow rectified straight by the injection nozzle flows into the air layer forming pipe, the outside air is sucked from the intake port to cover the outer periphery of the pressure flow, and the diffusion of the pressure flow is prevented. Since the pressure flow including the outside air is constricted and compressed by the rectifying groove inside the air layer forming pipe, the pressure flow that is higher than the pressure flow that passes through the air layer forming pipe and the pressure flow injected from the air layer forming pipe is It becomes a pressure flow with straightness.

  An air intake pipe penetrating the casing is provided in the downstream direction of the pressure flow from the air layer forming pipe, and an energy conversion tube is provided on the same line as the center line of the air layer forming pipe with a distance substantially equal to the inner diameter of the air intake pipe. The hole diameter of the pressure conversion side end face of the energy conversion tube is larger than the hole diameter of the air layer forming tube and is tapered in the pressure flow downstream side direction, that is, constricted in a trumpet shape, and the minimum hole diameter of the energy conversion tube is equal to that of the injection nozzle. The minimum hole diameter of the energy conversion tube penetrates in parallel from the pressure flow upper direction to the lower direction, and the total length of the minimum hole diameter is the same as the total length of the air layer forming pipe. It is a structure having a longer length.

  As a result, the pressure flow injected from the air layer forming tube passes through the suction chamber space of the same distance as the inner diameter of the suction tube until reaching the energy conversion tube, but the pressure flow outer peripheral portion contains air. Since it is covered with a pressure flow and constricted and compressed at the rectifying groove of the air layer forming tube to achieve high-speed rectification, the straightness is increased, and it flows into the energy conversion tube without diffusing. In addition, since the pressure flow inlet end face of the energy conversion tube has a wide angle, the pressure flow that enters and leaks into the energy conversion tube is extremely reduced.

  With the above structure, the pressure flow filled in the air layer forming tube is mixed with the suction material sucked from the suction tube and enters the energy conversion tube, and the energy conversion tube is filled with pressure flow, which meets the Venturi effect theory. In this way, negative pressure in the suction chamber is continuously generated. Therefore, assuming that the diameter of the injection nozzle is the same, the higher the head pressure of the pressurizing pump, the higher the pressure flow passing through the suction chamber and the higher negative pressure will be generated, resulting in a stronger suction force. It will be.

  According to the jet pump of the present invention, when the nozzle diameter of the jet nozzle of the jet pump is the same, the suction force and discharge force of the jet pump according to the discharge amount and lift force of the pressurizing pump can be obtained. Suction according to the site by changing the capacity of the pressure pump and the diameter of the jet nozzle of the jet pump according to the type of product, the suction amount per hour, the discharge amount, and the distance required to discharge the suction product・ Discharge work is possible.

It is a figure which shows a contaminated soil purification system. It is sectional drawing of the conventional jet pump. It is a figure which shows the effect | action of the conventional jet pump. It is a correlation perspective view of a tank remaining amount and a rotation rod. It is sectional drawing of the jet pump which concerns on this invention. It is a hole sectional view of a jet pump concerning the present invention. It is a schematic diagram of a venturi effect.

  Embodiments of the present invention will be described below with reference to the drawings.

  FIG. 1 shows an example of a contaminated soil purification system. The contaminated soil 1 is pulverized by a crusher 2 and sent to a jet pump 6 according to the present invention through a cyclone 5. Water is sucked from the water tank 4 by the pressurizing pump 23, and the pressure flow is pressed into the jet pump 6. The jet pump 6 sucks the contaminated soil crushed from the cyclone 5 by the venturi effect and conveys it to the cyclone 12.

  Currently, there is little work with the jet pump according to the present invention, and the work content is systematized as shown in Fig. 1, and the contaminated soil is separated into clean water and gravel using sludge separator etc. and restored to nature. Is partly obligatory. For this reason, it is expected that the distance from the jet pump 6 to the cyclone 12 will be 2000 m. Therefore, it is necessary that the lifting capacity of the pressurizing pump 23 is reliably transmitted via the jet pump 6. However, the jet pump 6 of the present invention can reliably connect the lifting capacity of the pressurizing pump 23 to the lifting head from the jet pump 6 to the cyclone 12 by the venturi effect described later in detail.

  In FIG. 1, a precipitation tank 8, a kneading machine 10, a particle sorting device 13, a sludge separation tank 14, a fresh water tank 17, and an electrode tank 19 are not included in the gist of the present invention, and detailed description thereof is omitted. To do.

  Here, the Venturi effect that is the basis of the present invention and the most important principle will be described. FIG. 7 is a schematic diagram of a venturi meter. In FIG. 7, when the flow cross-sectional area is narrowed when the flow rate is constant, the flow velocity increases. When the fluid is incompressible, that is, when the density is constant, v2 = A1 / A2 × V1. Here, the fluid is incompressible, the density is P = constant, and it is a steady flow. The cross-sectional area, flow velocity, pressure, and head of the pipe before squeezing are A1, v1, p1, and z1, respectively, and the cross-sectional area, flow velocity, pressure, and water head of the throttle section are A2, v2, p2, z2, and the flow rate are Q, When the gravitational acceleration is g, the following equation is established. p1 / p + (v1 × v1) / 2 + gz1 = p2 / p + (v2 × v2) / 2 + gz2. Therefore, from the Bernoulli theorem, the pressure decreases as the flow velocity increases. To repeat the explanation, in order to reliably apply the Venturi effect, a structure in which the thick pipes before and after the throttle pipe are filled with incompressible running water or the like is necessary.

  FIG. 4 shows an example of an embodiment of a jet pump according to the present invention. An injection nozzle 57, an air layer forming pipe 58, an energy conversion tube 61, and a discharge pipe 62 are arranged in a casing 69 that hermetically covers the entire apparatus, with the center position of the hole diameter provided on the same line from the upward direction of pressure flow. The hole diameter of the injection nozzle 57 connected to the pipe extended from the pressurizing pump (not shown) has substantially the same diameter as the pipe inner diameter, and the hole diameter is reduced to the lower side in the pressure flow direction. The diameter of the hole connected to the pipe is tapered to a so-called trumpet shape, and the hole having the same diameter as the hole diameter from the substantially middle part of the injection nozzle 57 toward the lower side of the pressure flow is parallel to the outlet end of the injection nozzle 57. The inner wall of the parallel hole diameter portion is extended, and a straightening groove 65 is provided at the same position and at equal intervals radially from the center of the hole diameter on the cross section, and the straightening groove 65 extends from the position of the smallest taper diameter to the injection nozzle outlet end. It has a structure extending in parallel with the hole center line. FIG. 5 is a cross-sectional view in the upward direction of the pressure flow viewed from the direction of arrow A in FIG. Rectifying grooves 65 are provided at equal intervals radially from the center of the injection nozzle 57. The rectifying groove 65 has a U-shape in this embodiment, but may be a semi-elliptical or semi-circular shape.

  In FIG. 4, an air layer forming pipe 58 is provided on the extension line of the center position of the injection nozzle 57, which is larger in diameter than the pressure flow outlet end face hole diameter of the injection nozzle 57 in the lower pressure direction of the injection nozzle 57. The air diameter of the air layer forming tube 58 is such that the pressure inflow end and the pressure outflow end are penetrated in parallel with the same diameter, and the inner wall of the hole diameter is radially radiated from the center of the hole diameter in the cross section at equal intervals and at equal intervals. 66, and has a structure extending from the pressure inflow end portion of the air layer forming tube 58 to the pressure outflow end portion of the air layer forming tube 58 in parallel with the center line of the air layer forming tube 58. FIG. 5 is a cross-sectional view from the direction of arrow A in FIG. Rectifying grooves 66 are provided at equal intervals radially from the center of the air layer forming tube 58. The rectifying groove 66 has a U-shape in this embodiment, but may be a semi-elliptical or semi-circular shape.

  FIG. 6 is a three-dimensional cross-sectional view of the injection nozzle 57 and the air layer forming pipe 58. The pressure flow A is press-fitted into a wide-angle injection nozzle 57 that is substantially the same as the inner diameter of a pipe (not shown) to which an inlet surface is connected, but is tapered from the injection flow surface of the injection nozzle 57, that is, in a trumpet shape. The pressure flow A is accelerated because the diameter of the passing hole is reduced by the diameter of the hole narrowed to a substantially middle part of the injection nozzle 57 and reduced in diameter. The accelerated pressure flow A becomes straight by the rectifying grooves 66 that are radially arranged at the same position and at the same interval on the same line as the hole diameter center line of the injection nozzle 57.

  An air inlet (not shown) is provided in the gap between the injection nozzle 57 and the air layer forming pipe 58, and the pressure flow A that has been accelerated and increased in straightness is covered with a pressure flow including air on the outer periphery of the pressure flow A. And then flows into the air layer forming pipe 58. The hole diameter of the air layer forming pipe 58 is larger than the hole diameter of the pressure flow surface of the injection nozzle 57 and is provided on the center line extension of the hole diameter of the injection nozzle 57. The flow surface has the same hole diameter. The pressure flow A, which includes air on the outer periphery and is accelerated to increase straightness, further travels straight by passing through the rectifying grooves 66 that are radially arranged at equal intervals on the same line as the hole diameter center line of the air layer forming tube 58. It will increase the nature.

  In FIG. 4, an intake port 70 penetrating the casing 69 is provided in the gap between the injection nozzle 57 and the air layer forming tube 58, an intake tube 71 is provided outside the casing 69 connected to the intake port 70, and the intake tube 71. Has a structure in which a regulating valve 60 connected to a sealed chamber or a conduit is provided.

  With this structure, when the pressure flow rectified straight by the injection nozzle 57 flows into the air layer forming pipe 58, the outside air is sucked from the intake port 70 to cover the outside of the pressure flow and prevent the pressure flow from being diffused. Since the pressure flow including the outside air is constricted and compressed by the rectifying groove 66 inside the layer forming tube 58, the pressure flow that is higher than the inside of the pressure flow passing through the air layer forming tube 58 and the pressure flow injected from the air layer forming tube 58 is It becomes a pressure flow with straightness.

  A suction pipe 63 penetrating the casing 69 is provided in the direction of pressure flow lower than the air layer formation pipe 58, and is substantially collinear with the center line of the air layer formation pipe 58 with the inner diameter of the suction pipe 63 being substantially the same distance as the pressure flow lower direction. An energy conversion tube 61 is provided, and the hole diameter of the pressure inflow side end face of the energy conversion tube 61 is larger than the hole diameter of the air layer forming tube 58 and is narrowed in a taper shape, that is, a trumpet shape in the downstream direction of the pressure flow. The minimum hole diameter of 61 has a structure of the sum of the hole diameter of the injection nozzle 57 and the inner diameter of the suction pipe 63, and the minimum hole diameter of the energy conversion tube 61 penetrates in parallel from the upper direction of the pressure flow to the lower direction. The total length of the air layer forming tube 58 is equal to or longer than the total length of the air layer forming tube 58.

  As a result, the pressure flow injected from the air layer forming tube 58 passes through the space of the suction chamber 68 that is substantially the same distance as the inner diameter of the suction tube 63 until reaching the energy conversion tube 61, but the pressure flow outer peripheral portion contains air. Covered with a pressure flow and constricted and compressed by the rectifying groove 66 of the air layer forming tube 58 to achieve high-speed rectification, so that straightness is increased and mixed with the sucked material sucked from the suction tube 63 without diffusing, and the energy conversion tube 61 will be poured into. Since the pressure flow inlet end surface 67 of the energy conversion tube 61 has a wide angle, the pressure flow that enters and leaks into the energy conversion tube 61 is extremely reduced.

  The pressure flow filled in the air layer forming pipe 58 with the above structure is mixed with the suctioned matter sucked from the suction pipe 63 and enters the energy conversion tube 61 to fill the energy conversion tube 61 with the pressure flow. Thus, the negative pressure in the suction chamber 68 is generated in a form consistent with the above theory. Therefore, assuming that the diameter of the injection nozzle 57 is the same, the higher the head pressure of the pressurizing pump, the higher the pressure flow passing through the suction chamber 68 and the higher negative pressure can be generated. As a result, a strong suction force is generated.

57 injection nozzle 58 air layer forming pipe 60 intake valve 61 energy conversion tube 62 discharge pipe 63 suction pipe 65 injection nozzle rectifying groove 66 air layer forming pipe rectifying groove 67 wide angle pressure flow port 68 suction chamber 69 casing 70 air intake port

In order to solve the above-mentioned conventional problems, the present invention is applied to a jet pump having a hole that penetrates an injection nozzle, an air layer forming tube, and an energy conversion tube on the same straight line from the upper direction of pressure flow inside a sealed casing. The hole diameter of the injection nozzle connected to the pipe extending from the pressure pump has substantially the same diameter as the pipe inner diameter, and the diameter of the hole is tapered toward the lower side in the pressure flow direction from the hole diameter connected to the pipe to the middle part of the injection nozzle. The so-called trumpet shape is made smaller in size, extending from the substantially middle part of the injection nozzle toward the lower side of the pressure flow, extending the hole having the same diameter as the above-mentioned in parallel to the injection nozzle outlet end, and cross-sectioning the inner wall of the parallel hole diameter part upper hole diameter central portion is provided at equal intervals in the rectification groove and at the same position radially from, the rectification groove is parallel to the extension and the hole center line from the position of the tapered minimum diameter to the injection nozzle outlet end Have that structure.

An air intake pipe penetrating the casing is provided in the downstream direction of the pressure flow from the air layer forming pipe, and an energy conversion tube is provided on the same line as the center line of the air layer forming pipe with a distance substantially equal to the inner diameter of the air intake pipe. the energy conversion tube fluid inlet-side end surface of the pore diameter fluid downstream side direction tapered large diameter than the hole diameter of the air layer forming tube, that is, narrowing like a trumpet is the minimum diameter of the energy conversion tube the injection nozzle the total length of the pore diameter and have pore size of the sum of the inner diameter of the suction tube, the total length of the minimum pore diameter in parallel to the through minimum pore size from fluid good direction in poor direction of the energy conversion tube of the air layer forming pipe The structure has the same or longer length.

FIG. 4 shows an example of an embodiment of a jet pump according to the present invention. An injection nozzle 57, an air layer forming pipe 58, an energy conversion tube 61, and a discharge pipe 62 are arranged in a casing 69 that hermetically covers the entire apparatus, with the center position of the hole diameter provided on the same line from the upward direction of pressure flow. The hole diameter of the injection nozzle 57 connected to the pipe extended from the pressurizing pump (not shown) has substantially the same diameter as the pipe inner diameter, and the hole diameter is reduced to the lower side in the pressure flow direction. The diameter of the hole connected to the pipe is tapered to a so-called trumpet shape, and the hole having the same diameter as the hole diameter from the substantially middle part of the injection nozzle 57 toward the lower side of the pressure flow is parallel to the outlet end of the injection nozzle 57. is extended, at regular intervals to the rectifying groove 65 and at the same position radially inner wall of the parallel opening part from a cross-sectional the hole diameter central portion is provided, the rectifying groove 65 is the injection nozzle outlet end from the position of the tapered minimum diameter And has a structure extending in parallel with the hole center line. FIG. 5 is a cross-sectional view in the upward direction of the pressure flow viewed from the direction of arrow A in FIG. Rectifying grooves 65 are provided at equal intervals radially from the center of the injection nozzle 57. The rectifying groove 65 has a U-shape in this embodiment, but may be a semi-elliptical or semi-circular shape.

A suction pipe 63 penetrating the casing 69 is provided in the direction of pressure flow lower than the air layer formation pipe 58, and is substantially collinear with the center line of the air layer formation pipe 58 with the inner diameter of the suction pipe 63 being substantially the same distance as the pressure flow lower direction. An energy conversion tube 61 is provided, and the hole diameter of the pressure inflow side end face of the energy conversion tube 61 is larger than the hole diameter of the air layer forming tube 58 and is narrowed in a taper shape, that is, a trumpet shape in the downstream direction of the pressure flow. 61 minimum diameter of has the structure of pore size of the sum of the pore diameter and the inner diameter of the suction tube 63 of the injection nozzle 57, the minimum diameter of the energy conversion tube 61 in parallel to penetrate the poor direction from fluid good direction, the total length of the minimum pore size is a structure that has an overall length the same as or more in length of the air layer forming tube 58.

Claims (2)

  In a jet pump having a hole through which an injection nozzle, an air layer forming tube, and an energy conversion tube penetrate on the same line from the direction of pressure flow on the piping side extended from the pressurizing pump inside the sealed casing, it is extended from the pressurizing pump. The diameter of the nozzle of the injection nozzle connected to the pipe to be connected is approximately the same as the inner diameter of the pipe, and the diameter of the hole toward the lower side of the pressure flow is made smaller than the diameter of the hole connected to the pipe to the substantially middle part of the pressure nozzle, so that the diameter is smaller. The hole has the same diameter as the small diameter from the substantially intermediate portion of the injection nozzle toward the lower side of the pressure flow, and extends to the injection nozzle outlet end in parallel with the injection nozzle hole diameter center line. The inner wall of the hole diameter part is provided with a rectifying groove that is radially equidistant from the center part of the hole diameter on the cross section, and the rectifying groove is located at the end of the injection nozzle from the position of the smallest taper diameter. And a hole diameter that is larger than the injection nozzle outlet end hole diameter on the same line extension as the injection nozzle hole diameter center line from the injection nozzle in the downstream direction of the pressure flow. The air layer forming tube has a hole diameter of the pressure inflow end portion and the pressure outflow end portion of the same diameter in parallel, and the inner wall of the hole diameter portion radiates from the center of the hole diameter on the cross section. A rectifying groove is provided at the same position and at equal intervals, and extends from the pressure end of the air layer forming tube to the pressure outflow end of the air layer forming tube in parallel with the hole diameter center line. An intake port penetrating the casing is provided in a gap between the injection nozzle and the air layer forming pipe, and an intake pipe is provided outside the casing connected to the intake port. A control valve is provided on the intake pipe. The structure is provided, and the pressure flow is lower than the air layer forming pipe. In the direction, a suction pipe penetrating the casing is provided, and an energy conversion tube is provided on the same line extension line as the center line of the air layer forming pipe at a distance substantially equal to the inner diameter of the suction pipe. The hole diameter of the pressure inflow side end surface is larger than the hole diameter of the air layer forming pipe and is narrowed in a taper shape or a trumpet shape in the pressure flow downstream side, and the minimum hole diameter of the energy conversion tube is the hole diameter of the injection nozzle and the water absorption pipe. The energy conversion tube has a structure of a total pore diameter with the inner diameter, and the minimum pore diameter of the energy conversion tube penetrates in parallel from the pressure flow upper direction to the lower direction, and the total length of the minimum hole diameter is equal to or greater than the total length of the air layer forming tube. A jet pump characterized by a structure having a length of 2. The jet pump according to claim 1, wherein the shape of the rectifying groove of the injection nozzle and the rectifying groove of the air layer forming tube is U-shaped, semi-elliptical, semi-circular in cross section with respect to the hole diameter center line. A jet pump characterized by not restricting the cross-sectional shapes of the rectifying groove of the injection nozzle and the rectifying groove of the air layer forming tube.

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