WO2009081465A1 - 加圧遠心ポンプ - Google Patents

加圧遠心ポンプ Download PDF

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Publication number
WO2009081465A1
WO2009081465A1 PCT/JP2007/074642 JP2007074642W WO2009081465A1 WO 2009081465 A1 WO2009081465 A1 WO 2009081465A1 JP 2007074642 W JP2007074642 W JP 2007074642W WO 2009081465 A1 WO2009081465 A1 WO 2009081465A1
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WO
WIPO (PCT)
Prior art keywords
blade
fluid
chamber
impeller
pump
Prior art date
Application number
PCT/JP2007/074642
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
Ryoichi Yonehara
Original Assignee
Yonehara Giken Co., Ltd.
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Yonehara Giken Co., Ltd. filed Critical Yonehara Giken Co., Ltd.
Priority to CN2007801019836A priority Critical patent/CN101903661A/zh
Priority to KR1020107013332A priority patent/KR20100097165A/ko
Priority to US12/808,773 priority patent/US20110280718A1/en
Priority to PCT/JP2007/074642 priority patent/WO2009081465A1/ja
Priority to EP07851048A priority patent/EP2233749A4/de
Publication of WO2009081465A1 publication Critical patent/WO2009081465A1/ja

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/18—Rotors
    • F04D29/22—Rotors specially for centrifugal pumps
    • F04D29/2261—Rotors specially for centrifugal pumps with special measures
    • F04D29/2288—Rotors specially for centrifugal pumps with special measures for comminuting, mixing or separating
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D23/00—Other rotary non-positive-displacement pumps
    • F04D23/008—Regenerative pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/18—Rotors
    • F04D29/188—Rotors specially for regenerative pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/18—Rotors
    • F04D29/22—Rotors specially for centrifugal pumps
    • F04D29/2261—Rotors specially for centrifugal pumps with special measures
    • F04D29/2272—Rotors specially for centrifugal pumps with special measures for influencing flow or boundary layer
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/18—Rotors
    • F04D29/22—Rotors specially for centrifugal pumps
    • F04D29/2261—Rotors specially for centrifugal pumps with special measures
    • F04D29/2294—Rotors specially for centrifugal pumps with special measures for protection, e.g. against abrasion
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/18—Rotors
    • F04D29/22—Rotors specially for centrifugal pumps
    • F04D29/24—Vanes
    • F04D29/242—Geometry, shape
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D5/00—Pumps with circumferential or transverse flow
    • F04D5/002—Regenerative pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D5/00—Pumps with circumferential or transverse flow
    • F04D5/002—Regenerative pumps
    • F04D5/008—Details of the stator, e.g. channel shape
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D7/00—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts
    • F04D7/02—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts of centrifugal type
    • F04D7/04—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts of centrifugal type the fluids being viscous or non-homogenous
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2250/00—Geometry
    • F05D2250/50—Inlet or outlet
    • F05D2250/51—Inlet

Definitions

  • the present invention relates to a pressurized centrifugal pump that rotates an impeller inside a pump case to suck and send out liquid or the like.
  • a pressurized centrifugal pump that sucks, pressurizes, and delivers a fluid such as water, oil, air, or the like is already known as disclosed in Patent Document 1 related to the proposal of the present applicant.
  • This pressurizing centrifugal pump is a drum-shaped case having a suction port and a delivery port, and a pressure chamber converged from the suction port side toward the delivery port side on an impeller having blades projecting radially on the side surface.
  • the pressurizing surface to be formed and the pressurizing part that forms a pressurizing partition wall that prevents the fluid in the vane chamber from leaking close to the side surface of the blade are opposed to each other, and the fluid sucked from the suction port is transferred between the impeller and the pressurizing unit. Pressurize in the formed pump chamber and send it out from the delivery port.
  • the pressure centrifugal pump shown in the above-mentioned patent document 1 is provided with a blade forward tilt angle (scratching angle) on a blade projecting radially from the boss portion on the side surface of the blade plate, the leading blade outer end is pressurized.
  • a blade forward tilt angle tilt angle
  • the blade formed with a flat surface having a blade front tilt angle freely pressurizes the leakage of the fluid scraped into the blade chamber to the side, the boundary between the side surface of the impeller and the pressure chamber Have the disadvantage of producing intense turbulence.
  • the blade chamber connects the blade front and back of adjacent blades with a flat blade valley surface on the blade plate side, the fluid that is scooped in the blade front and forms a vortex in the center of the blade chamber There is a drawback in that turbulent flow is generated at the corners and the pump efficiency is impaired.
  • each impeller protrudes with the same diameter as the diameter of the impeller, the outer peripheral surface of the impeller is brought close to the inner peripheral wall of the pump case, and the fluid that tries to leak to the back side of the impeller is discharged.
  • the blade tip when a fluid regulating interval of about 0.3 mm is formed, the blade tip also forms the same gap as the fluid regulating interval.
  • a pressurized centrifugal pump includes a drum-shaped case (4) having a suction port (2) and a delivery port (3), and a blade plate (14).
  • An impeller (5) rotating in the case (4) formed by projecting a plurality of blades (12) radially from the boss portion (15) with a receding angle in the rotational direction on the side surface of the boss portion (15),
  • a pressurizing part (22) having a pressurizing partition wall (25) that is close to the side surface of the blade (12) and prevents leakage of fluid in the blade chamber (16), and the impeller (5) )
  • the tip of the blade (12) is formed low by providing a step (36) in the center direction from the outer periphery of the blade plate (14), and the blade plate (11) is formed on the inner peripheral wall (11) of the case (4). 14), the fluid control interval (h) that restricts the movement of fluid to the blade back side is formed by bringing the outer periphery close to each other, and a fluid is provided between the inner peripheral wall (11) and the tip of the blade (12). It is characterized in that a fluid passage interval (H) that promotes passage of foreign matter (X) therein is formed.
  • the blade chamber (16) formed by the blade (12) protruding from the blade plate (14) with a predetermined adjacent interval is curved toward the upper side in the rotational direction.
  • an arcuate blade valley surface (37) that curves toward the blade plate (14) side.
  • the valley depth of the blade chamber 16 is gradually formed deeper from the bottom side toward the tip side.
  • the valley depth of the blade chamber 16 is gradually formed deeper from the bottom side toward the middle part on the front end side, and the valley depth from the middle part to the front end side is formed to be substantially constant.
  • a pressure guide surface 27b substantially parallel to the side surface of the impeller 5 is formed on the start end side of the pressure surface 27 connected to the suction port 2.
  • the pressurized centrifugal pump of the present invention configured as described above has the following effects.
  • the tip of the blade low by providing a step inside the outer periphery of the blade plate, the outer peripheral surface of the blade plate can be as close as possible to the inner peripheral wall, and the movement of the fluid from the fluid regulation interval to the back side is restricted. Pump efficiency can be improved. Further, from the fluid passage interval formed between the inner peripheral wall and the tip of the blade, it is possible to facilitate the passage of the foreign matter (X) mixed in the fluid and to reduce the generation of noise.
  • the fluid supplied from the suction port with the rotation is introduced so as to scoop into the blade chamber along the shape of the blade front surface, and the fluid sequentially introduced from the pressure chamber through the pressure surface is introduced into the blade front surface and the blade valley.
  • a vortex flow is smoothly formed in the blade chamber along the surface to reach the delivery outlet, so that the pump pressure can be increased and released vigorously by the centrifugal force and kick action of the blade.
  • Fluid moves along the blade front and blade valley surfaces from the bottom side to the tip side in the blade chamber to prevent turbulent flow and form an orderly vortex to increase the blade chamber pressure.
  • a swirl flow from the bottom of the blade chamber to the delivery port is formed in an orderly manner, so that the fluid is sent out vigorously from the delivery port. be able to.
  • the valley depth of the blade chamber gradually deeper from the bottom side toward the middle of the tip, and forming the valley depth from the middle to the tip side substantially constant, the bottom side of the blade chamber with respect to the delivery port It is possible to form the slope of the valley without reducing the depth of the valley and to direct the fluid to the delivery port reliably.
  • the fluid supplied from the suction port is directed to the impeller side through the pressure guide surface, and the fluid is guided in parallel along the impeller from the initial stage of suction.
  • the generation of negative pressure can be prevented and pump efficiency can be increased.
  • FIG. 3 is a left side view of the pressurized centrifugal pump according to the present invention, partially broken away. It is sectional drawing which shows the structure in the pump chamber of FIG. It is an expanded sectional view which expands and shows composition of a pump room of Drawing 1. It is a front view which shows the structure of a pressurization case.
  • FIG. 5 is a sectional view taken along line AA in FIG. 4.
  • FIG. 5 is a sectional view taken along line BB in FIG. 4.
  • FIG. 8 is a sectional view taken along line AA in FIG. 7.
  • FIG. 8 is a sectional view taken along line BB in FIG.
  • reference numeral 1 denotes a pressure centrifugal pump, and a drum-type case 4 having a suction port 2 and a delivery port 3, and is rotatably supported in the case 4.
  • the gas supply part 6 which consists of an impeller 5 and supplies gas, such as air, in the case 4 as needed is installed.
  • This pump 1 drives one side of a pump shaft 7 provided with an impeller 5 from the prime mover side, rotates the impeller 5 in the direction of the arrow shown in FIG.
  • Arbitrary gases such as gas or powders such as drugs are sucked into the pump chamber 9 in the case 4 from the suction port 2 side, pressurized and energized while stirring and mixing the above gases etc. in the fluid, and sent out from the delivery port 3 To do.
  • the fluid is water
  • the mixed gas is air
  • the case 4 in the illustrated example forms an airtight pump chamber 9 in which a pressure case 4a having a suction port 2 and an impeller case 4b having a delivery port 3 are paired on the left and right sides so as to be separable. .
  • the impeller case 4b is formed in a saddle shape that internally fits the impeller 5 and a pressurizing portion 22 of a pressurizing case 4a described later.
  • a predetermined length straddling a plurality of blades 12 that are formed to project is formed at a delivery position that faces the blade width.
  • a delivery pipe 13 curved in the fluid delivery direction is integrally connected to the delivery port 3.
  • the impeller case 4 b is integrally provided with a support portion that pivotally supports the pump shaft 7 at the center portion of the pump chamber 9 on the other side of the inner peripheral wall 11.
  • the pump shaft 7 has an impeller 5 provided with a plurality of blades 12 protruding from a shaft end in the pump chamber 9 and fixed by a mounting screw and a nut.
  • the impeller 5 has the other side surface of the impeller plate 14 protruding from the impeller 12 approaching the side wall of the impeller case 4b, and the impeller 12 has a fluid passage interval H described later with reference to FIG. Provided.
  • the impeller 5 is integrally formed with a cylindrical boss portion 15 that also serves as an attachment portion to the pump shaft 7 from a central portion of a disc-like blade plate 14 serving as a blade sidewall. Further, the impeller 5 is formed so that the side ends of the boss portion 15 and the blade 12 have substantially the same height, and when the impeller 5 is attached to the impeller case 4b, the end surface of the boss portion 15 is formed at the center of the pressure case 4a. It is made to adjoin with the end surface of the flat surface-shaped pressurization partition wall 25 (refer FIG. 4) mentioned later.
  • the impeller 5 causes each blade 12 to project radially from the blade plate 14 and the boss portion 15 with a predetermined interval, and the space formed by each adjacent blade 12, the blade plate 14 and the boss portion 15.
  • the blade chamber 16 (see FIG. 3) for containing fluid is used.
  • the vane chamber 16 is formed with vanes 12 as will be described later with reference to FIGS. 7 to 11, thereby improving the pump efficiency.
  • the pressurizing case 4a is integrally formed with a case lid portion 21 having a suction pipe 19 and a pressurizing portion 22, and is formed in the opening of the inner peripheral wall 11 of the impeller case 4b in a state where the impeller 5 is assembled.
  • the pressurizing part 22 is inserted and the pressurizing case 4a and the impeller case 4b are fixed with bolts, and the case 4 can be configured in a closed state.
  • a pump chamber (pressurizing chamber) 9 is formed between the pressurizing unit 22 and the impeller 5 to pressurize the fluid scooped from the suction port 2 through the impeller 5 and send it out from the delivery port 3. .
  • the pump chamber 9 includes a suction chamber 23 that promotes the suction of fluid, and a pressurizing chamber 24 that communicates with the suction chamber 23 and pressurizes the fluid. Further, between the end of the pressurizing chamber 24 and the suction port 2, a pressurizing partition wall 25 that is close to the side surface of the plurality of blades 12 and restricts fluid leakage in the blade chamber 16 is flush with the central partition wall 26. A flat surface is formed. As a result, a suction chamber 23, a pressurizing chamber 24, and a pressurizing partition wall 25 are formed in series around the central partition wall 26 facing the end face of the boss portion 15 of the impeller 5.
  • the pressurizing surface 27 formed with a smooth inclined surface in the range from the suction port 2 side to the pressurization partition wall 25 forms the pressurization chamber 24 gradually approaching the blade 12 from the suction chamber 23 side in a convergent manner. .
  • the fluid sucked into the pump chamber 9 from the suction port 2 is sequentially scraped and held in each blade chamber 16 by the rotation of the impeller 5, and the plurality of blades 12 through the pressurizing chamber 24 of the long passage. Is gradually pressurized.
  • the pressurization surface 27 is formed up to a pressurization end point 29 located at the start end of the pressurization partition wall 25, and a fluid moving from the suction chamber 23 toward the lower side is applied to the blade chamber 16 along the inclination of the pressurization surface 27. Induct pressure. Further, it is possible to pressurize the fluid in the pump chamber 9 without causing sudden pressure fluctuations, and to efficiently push out the fluid pressurized to the maximum pressure at the pressurization end point 29 from the outlet 3.
  • the pressurizing surface 27 of the present embodiment allows the flow of the pressurized fluid to the blade chamber 16 in the vicinity of the pressurization end point 29 on the near side facing the start end of the delivery port 3.
  • a turning pressure surface 31 that promotes the turning is formed in a stepped shape, and a second pressure surface 27 a is formed between the turning pressure surface 31 and the pressurization end point 29.
  • the diverting pressure surface 31 is preferably formed on the upper side of the pressurization end point 29 from the vicinity of the lower side of the starting end portion of the delivery port 3, and the fluid in the pressurizing chamber 24 is impregnated immediately before the second pressure surface 27a.
  • the direction is changed to the delivery port 3 side through the chamber 16. Thereby, the pressurization of the fluid is promoted at the portion where the delivery port 3 is located in the pump chamber 9, and the pressure drop due to the delivery is prevented.
  • the fluid is sequentially pressurized along the pressure surface 27 while being stirred by the blades 12 in the converging pressure chamber 24 to form a violent vortex, but in the case of a pump that mixes air, Bubble miniaturization is promoted in a pressurized vortex. Then, the fluid and air bubbles that move to the lower side are diverted and transferred into the blade chamber 16 without causing shocking contact resistance in the middle of the pressurizing surface 27 due to the shape of the diverting and pressing surface 31. Can be quickly discharged.
  • supply of gas, such as air, into the pump chamber 9 can mix gas in the liquid in the suction inlet 2 with the gas supply apparatus 6 which consists of the same structure as the conventional one.
  • the suction chamber 23 of the pump 1 of the embodiment forms a pressure guide surface 27b substantially parallel to the side surface of the impeller 5 on the start end side of the pressure surface 27 connected to the suction port 2 as shown by a dotted line in FIG. ing. Accordingly, it is possible to improve the suction performance by promoting the supply of fluid from the suction port 2 without causing a negative pressure of the fluid in the suction chamber 23, corresponding to the suction capability accompanying the shape improvement of the blade chamber 16 described later. it can.
  • the pressurizing guide surface 27b is a corner portion formed so as to project smoothly so as to restrict the end of the suction port 2 with respect to the inclined surface having the conventional shape formed from the starting end portion of the pressurizing surface 27 shown by the solid line in FIG. From the curved surface, the flat surface substantially parallel to the side surface of the blade 12 of the impeller 5 and the inclined surface of the pressure surface 27 are connected.
  • the pump 1 vigorously directs the fluid supplied from the suction port 2 to the impeller 5 side via the start end corner portion of the pressurizing guide surface 27b, and sucks the fluid by the pressurizing guide surface 27b from the initial stage. Can be guided to the side. And, since the supply of fluid corresponding to the suction of the impeller 5 can prevent the generation of negative pressure on the start end side of the suction chamber 23, the pump efficiency can be increased as compared with the conventional one and the cavitation is suppressed. And it can be made a pump with high quietness.
  • the delivery port 3 formed in the impeller case 4b is located on the inner peripheral wall 11 of the impeller case 4b at a portion facing the second pressurizing surface 27a and the pressurizing partition wall 25 on the terminal end side of the pressurizing chamber 24. Opposed to the blade width, it is opened in the shape of a long hole.
  • a plate-shaped guide member 32 that guides fluid delivery is installed in the middle of the length direction of the delivery port 3 with a predetermined fluid guiding angle.
  • the blade 12 is disposed on one side of a disk-shaped blade 14 from the boss portion 15 toward the upper side in the impeller rotation direction (hereinafter simply referred to as “upper side”). Projecting in the radial direction, the blade piece is smoothly bent and inclined backward from the middle of the length in front view.
  • the impeller 5 scrapes fluid from the suction port 2 as it rotates and holds the fluid in the blade chamber 16. Then, when each blade 12 reaches the delivery port 3 site, it pushes and urges it as if kicking it while applying centrifugal force with the blade shape in which the fluid in the blade chamber 16 is retreated and inclined, and the flow pressure in the centrifugal direction is reduced. Increase.
  • the impeller 5 is configured such that the diameter of the tip rotation locus of the blade 12 is smaller than the diameter of the blade plate 14, and the gap between the inner peripheral wall 11 formed by both of them is different.
  • the blade 12 of the pump 1 in the illustrated example has, for example, only 12 blades 12 having a tip plate thickness of about 3 mm on the boss portion 15 having an outer diameter of 125 mm and a diameter of 55 mm.
  • the base interval between adjacent blades 12 is set to about 10 mm.
  • each blade 12 restricts the bending of the blade base side so as not to narrow the base interval, thereby increasing the amount of fluid contained in the blade chamber 16 so as not to prevent the inflow of the fluid on the base side.
  • the blade 12 has a flat surface 5 a that is parallel to the pressure partition wall 25 from the blade front surface 33 side formed in an arc surface within the thickness of the blade outer end, and a blade rear surface.
  • a chamfered inclined surface 5b reaching 35 is formed.
  • the thickness of the blade 12 is about 3 mm, it is desirable to form the inclined surface 5b with the width of the flat surface 5a being about 1 mm, and the inclined surface 5b has a shape substantially following the shape of the blade front surface 33.
  • the blade back surface 35 may be curved.
  • the blade 12 is subjected to surface treatment with a wear-resistant material such as titanium or a surface slidable member, if necessary.
  • the impeller 5 of the pump 1 in the illustrated example has a step 36 at the tip of each blade 12 from the outer periphery of the blade plate 14 toward the center so that the rotation diameter of the blade tip is smaller by several millimeters than the diameter of the blade plate 14. Is formed low.
  • the step 36 is a pump for fresh water (normal water)
  • the above-described step 36 is about 0.05 mm above the fluid regulating interval h formed by the cylindrical surface of the inner peripheral wall 11 and the outer periphery of the blade 14.
  • the fluid passage interval H formed by the inner peripheral wall 11 and the tip of the blade 12 is preferably set to about 0.35 mm.
  • the pump 1 can form a fluid passage interval H between the tip of the blade 12 and the inner peripheral wall 11 by the step 36 while making the outer periphery of the blade plate 14 as close as possible to the inner peripheral wall 11.
  • the pressure loss can be suppressed by restricting the leakage of the fluid that is about to leak from the fluid regulation interval h.
  • the fluid passage interval H formed larger than the fluid regulation interval h is about 0.3 mm of small particles (foreign matter (X)) such as sand and other minerals and organic substances mixed in the fluid. Can be passed easily.
  • small particles foreign matter (X)
  • the foreign matter (X) is vigorously brought into contact with the inner peripheral wall 11 as in the conventional case, and the foreign matter (X) is rotated between the tip of the blade and the opening end of the delivery port 3 in a state where it is caught or bitten. Etc. can be solved.
  • the impeller 5 smoothly moves and moves the foreign matter (X) in the pump chamber 9 through the fluid passage interval H, and prevents the inner peripheral wall 11 and the blades 12 from being damaged and discharged from the delivery port 3.
  • the fluid passage interval H is a gap that allows the foreign matter (X) to pass therethrough, the pump efficiency is not significantly impaired. If such a function is exhibited, the step 36 does not necessarily have to be a “step” in a strict sense.
  • the blade 12 that rotates at high speed can accommodate a large amount of fluid around the entire circumference and can be smoothly moved and sent out from the delivery port 3 by the fluid passage interval H formed low through the step 36. At this time, cavitation that tends to occur between the tip and the inner peripheral wall 11 is suppressed, and the fluid is moved through a large gap between the tip and the inner peripheral wall 11, so that noise such as water draining noise at the blade tip can be simultaneously reduced.
  • the fluid passage interval H can be a gap corresponding to the size of the foreign matter (X) in the case of a pump that sends large foreign matter (X) together with the fluid.
  • Each blade 12 protruding from the blade plate 14 with a predetermined blade pitch and blade width has an arcuate blade front surface 33 curved toward the upper side (upstream side) in the rotational direction on the front surface, and a rear surface.
  • An arcuate blade valley surface that smoothly connects the blade front surface 33 and the blade back surface 35 of the adjacent blades 12 and curves toward the blade plate 14 side, and has a curved surface that substantially follows the shape of the blade front surface 33. 37.
  • the blade chamber 16 formed by forming the blade front surface 33, the blade back surface 35, and the blade valley surface 37 in series is the width of the blade 12 (protrusion) from the blade tip width to the bottom portion, which is substantially equal to the opening width of the delivery port 3.
  • the valley depth of the blade chamber 16 is gradually increased from the bottom side toward the tip side.
  • the cross-sectional shapes at each position of the blade chamber 16 are formed so as to be substantially similar.
  • the impeller 5 configured as described above introduces the fluid supplied from the suction port 2 as it rotates to scoop into the blade chamber 16 along the shape of the blade front surface 33. Then, the vortex around the center of the blade chamber cross section along the blade front surface 33 and the blade valley surface 37 is disturbed by the fluid sequentially introduced from the pressure chamber 24 through the pressure surface 27 as shown by arrows in FIG. It is possible to prevent the generation of a flow and form it in an orderly and accelerated manner to increase the blade chamber pressure.
  • the valley depth of the blade chamber 16 is changed from the bottom side to the tip side when being discharged from the tip by the centrifugal force and kick action by the blade 12. Since it is formed so as to gradually become deeper, a swirling flow from the bottom of the vane chamber 16 toward the delivery port 3 can be formed in an orderly manner, and it can be smoothly and smoothly moved from the delivery port 3 with increased pressurization energy. To send.
  • the blade 12 formed as described above can be thickened by the flat surface 5a without the outer end being thin and sharp, and the base side is thickened by the curvature of the blade valley surface 37.
  • it has strength and durability and can be brought close to the pressure partition wall 25.
  • wing 12 can be adjoined to the pressurization partition wall 25, and leakage of fluid, a bubble, etc. is suppressed from both.
  • a small amount of fluid flowing out of the gap vigorously flows into the next blade chamber 16 and is scooped by the blade front surface 33 while forming a vortex along the inclined surface 5b and the blade rear surface 35. Promotes pressurization without causing it.
  • the blade back surface 35 and the blade front surface 33 can be connected and formed in series with a curved surface larger than the curved surface shown by the dotted line. In this case as well, it is desirable to form the step 36 on a tangent to the valley of the blade chamber 16.
  • the slope of the valley formed on the valley surface of the blade chamber 16 in an inclined manner from the bottom to the tip side is not limited to the example shown in the figure, and is approximately half the valley length. It is also possible to adopt a configuration in which the front end side is not inclined toward the delivery port 3 from the midway portion of 1 (see dotted line 37). In this case, with respect to the delivery port 3 of an arbitrary diameter installed at a predetermined position of the impeller case 4b, a trough surface is formed without reducing the valley depth on the bottom side of the blade chamber 16, and the fluid is sent and received. 3 can be reliably directed. Therefore, by selecting the blade chamber 16 as described above corresponding to the use of the pump 1, there is an advantage that it can be easily adapted to various pump specifications.
  • each blade 12 sucks and sucks fluid into the blade chamber 16 from the suction port 2 via the suction chamber 23, and each blade chamber 16.
  • the fluid accommodated in the gas is pumped around the pump chamber 9 and continuously delivered to the delivery outlet 3 and delivered from the delivery pipe 13.
  • the impeller 5 is formed so that the tip of the blade 12 is lowered by providing a step 36 on the inside from the outer periphery of the blade plate 14, the foreign matter (X) mixed in the fluid is separated from the inner peripheral wall 11 and the tip of the blade 12.
  • the flow passage interval H that is formed between the two, the passage is encouraged to escape in the circumferential direction, and the contact of the foreign matter (X) against the inner peripheral wall 11 is buffered.
  • the movement of the foreign matter (X) by the tip of the blade 12 is prevented, it is possible to make the pump excellent in durability, and to reduce cavitation, draining sound, etc. generated at the tip of the blade by the fluid passage interval H. Can do.
  • the impeller 5 can reduce the fluid regulating interval h to the approximate limit of the allowable machining accuracy in a state where the fluid passage interval H is secured, even if the fluid pressure in the pressurizing chamber 24 is increased, the impeller plate There is an advantage that the movement of the fluid to the back side of 14 can be restricted and the pump efficiency can be improved.
  • the air mixed with the fluid in the pressurizing chamber 24 and the application is compressed along the pressurizing surface 27 to be microbubbled by the blades 12 and uniformly dispersed within the fluid passage interval H, and the pressurizing partition. It reaches the wall 25, reaches a maximum pressure state, and is smoothly fed out from the delivery port 3 by applying an extrusion force and a centrifugal force due to the rotation of the blade 12.
  • the gas mixed in the pump 1 can mix various gas bodies and a granular material, without being limited to air.
  • any liquid such as a chemical solution, a fire extinguishing solution, and a nutrient solution can be supplied and mixed, so that convenience can be enhanced and pump applications can be expanded.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Geometry (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
PCT/JP2007/074642 2007-12-21 2007-12-21 加圧遠心ポンプ WO2009081465A1 (ja)

Priority Applications (5)

Application Number Priority Date Filing Date Title
CN2007801019836A CN101903661A (zh) 2007-12-21 2007-12-21 增压离心泵
KR1020107013332A KR20100097165A (ko) 2007-12-21 2007-12-21 가압 원심 펌프
US12/808,773 US20110280718A1 (en) 2007-12-21 2007-12-21 Pressurizing centrifugal pump
PCT/JP2007/074642 WO2009081465A1 (ja) 2007-12-21 2007-12-21 加圧遠心ポンプ
EP07851048A EP2233749A4 (de) 2007-12-21 2007-12-21 Zentrifugaldruckpumpe

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2007/074642 WO2009081465A1 (ja) 2007-12-21 2007-12-21 加圧遠心ポンプ

Publications (1)

Publication Number Publication Date
WO2009081465A1 true WO2009081465A1 (ja) 2009-07-02

Family

ID=40800784

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2007/074642 WO2009081465A1 (ja) 2007-12-21 2007-12-21 加圧遠心ポンプ

Country Status (5)

Country Link
US (1) US20110280718A1 (de)
EP (1) EP2233749A4 (de)
KR (1) KR20100097165A (de)
CN (1) CN101903661A (de)
WO (1) WO2009081465A1 (de)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6283928B2 (ja) * 2013-10-03 2018-02-28 三浦工業株式会社 インペラ及びカスケードポンプ
CN114294259B (zh) * 2021-12-30 2024-10-22 福建省福安市力德泵业有限公司 一种高效低噪音泵
CN115233715B (zh) * 2022-08-07 2024-06-14 黑龙江省六建建筑工程有限责任公司 一种建筑工程排水装置及排水方法

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JPS63138199A (ja) * 1986-11-28 1988-06-10 Nikko Eng Kk 気液混合移送用ポンプ
JPH04159493A (ja) * 1990-10-19 1992-06-02 Hitachi Ltd 渦流ポンプ
JPH09177693A (ja) * 1995-12-26 1997-07-11 Asmo Co Ltd 液体ポンプ
JP2000240584A (ja) * 1999-02-18 2000-09-05 Ebara Corp ボルテックスポンプ
JP2004060470A (ja) 2002-07-25 2004-02-26 Yonehara Giken Kk 加圧遠心ポンプの気体等の混入構造
JP2005240629A (ja) * 2004-02-25 2005-09-08 Tsurumi Mfg Co Ltd 水中遠心ポンプの拘束防止構造
JP2005240628A (ja) * 2004-02-25 2005-09-08 Tsurumi Mfg Co Ltd 水中遠心ポンプの拘束防止構造
JP2005270245A (ja) * 2004-03-24 2005-10-06 Hitachi Home & Life Solutions Inc 食器洗い機の洗浄兼排水ポンプ
WO2005098239A1 (ja) * 2004-03-31 2005-10-20 Yonehara Giken Co., Ltd. 加圧遠心ポンプ
JP2006307859A (ja) * 2005-04-29 2006-11-09 Sulzer Pumpen Ag 遠心ポンプ及びそのインペラ

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JPS63138199A (ja) * 1986-11-28 1988-06-10 Nikko Eng Kk 気液混合移送用ポンプ
JPH04159493A (ja) * 1990-10-19 1992-06-02 Hitachi Ltd 渦流ポンプ
JPH09177693A (ja) * 1995-12-26 1997-07-11 Asmo Co Ltd 液体ポンプ
JP2000240584A (ja) * 1999-02-18 2000-09-05 Ebara Corp ボルテックスポンプ
JP2004060470A (ja) 2002-07-25 2004-02-26 Yonehara Giken Kk 加圧遠心ポンプの気体等の混入構造
JP2005240629A (ja) * 2004-02-25 2005-09-08 Tsurumi Mfg Co Ltd 水中遠心ポンプの拘束防止構造
JP2005240628A (ja) * 2004-02-25 2005-09-08 Tsurumi Mfg Co Ltd 水中遠心ポンプの拘束防止構造
JP2005270245A (ja) * 2004-03-24 2005-10-06 Hitachi Home & Life Solutions Inc 食器洗い機の洗浄兼排水ポンプ
WO2005098239A1 (ja) * 2004-03-31 2005-10-20 Yonehara Giken Co., Ltd. 加圧遠心ポンプ
JP2006307859A (ja) * 2005-04-29 2006-11-09 Sulzer Pumpen Ag 遠心ポンプ及びそのインペラ

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See also references of EP2233749A4

Also Published As

Publication number Publication date
CN101903661A (zh) 2010-12-01
EP2233749A1 (de) 2010-09-29
KR20100097165A (ko) 2010-09-02
US20110280718A1 (en) 2011-11-17
EP2233749A4 (de) 2012-12-19

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