EP0936356A1 - Selbstansaugende Strahlpumpe mit Durchflusskontrollvorrichtung - Google Patents

Selbstansaugende Strahlpumpe mit Durchflusskontrollvorrichtung Download PDF

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Publication number
EP0936356A1
EP0936356A1 EP99102657A EP99102657A EP0936356A1 EP 0936356 A1 EP0936356 A1 EP 0936356A1 EP 99102657 A EP99102657 A EP 99102657A EP 99102657 A EP99102657 A EP 99102657A EP 0936356 A1 EP0936356 A1 EP 0936356A1
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EP
European Patent Office
Prior art keywords
deflector
pressure chamber
return channel
pump according
centrifugal pump
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Legal status (The legal status 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 status listed.)
Granted
Application number
EP99102657A
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English (en)
French (fr)
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EP0936356B9 (de
EP0936356B1 (de
Inventor
Carlo Serafin
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Calpeda SpA
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Calpeda SpA
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Publication of EP0936356B1 publication Critical patent/EP0936356B1/de
Publication of EP0936356B9 publication Critical patent/EP0936356B9/de
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D9/00—Priming; Preventing vapour lock
    • F04D9/04—Priming; Preventing vapour lock using priming pumps; using booster pumps to prevent vapour-lock
    • F04D9/06—Priming; Preventing vapour lock using priming pumps; using booster pumps to prevent vapour-lock of jet type
    • 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
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/44—Fluid-guiding means, e.g. diffusers
    • F04D29/445—Fluid-guiding means, e.g. diffusers especially adapted for liquid pumps

Definitions

  • the present invention concems a self-priming single-impeller centrifugal pump with a built-in ejector, commonly called shallow-well jet pump, of the type including a diffuser with a return channel downstream the impeller, provided with a device for improving the working efficiency.
  • a solution increasingly used by now for obtaining simultaneously said features, otherwise hardly compatible, is that of eliminating the peripheral tangential component of the flow (or fluid flow) going out from the common diffuser around the impeller periphery, through a diffuser provided with a return channel.
  • Said return channel conveys through guide vanes the fluid from the periphery on a central opening in the pressure chamber (in steady condition) or chamber of calm for the separation of the air from the water (during the self-priming phase). Consequently, said retum channel reduces the rotation and the turbulence of the flow and the centrifugal effect which prevents the separation of the water from the liquid by holding it in the core of the rotating liquid.
  • the outlet of the return channel included in a circular crown around the final part of the ejector or suction duct of the impeller, limits the radial space usable to guide the flow from the peripheral tangential direction toward the axis.
  • a part of the streamlines in the conveying channels come to the outlet through angles which are different from the radial direction, with a consequent residual rotatory component and a residual centrifugal effect in the pressure chamber slowing down the air separation from the liquid during the self-priming phase.
  • the concentrated flow does not use all the surrounding liquid to decrease its own velocity and turbulence and causes the air entrainment together with the liquid. This slows down the air dispersion in the delivery and make its recirculation in the pump easier through the nozzle, the more said outlet of the return channel extends in the axial direction, parallel to the axis, by directing the flow adjacent to the ejector.
  • the device known through the above-mentioned patent, of extending axially the guide vanes beyond said outlet of the return channel, or the more usual device of placing longitudinal baffle walls in the pressure chamber to decrease the fluid residual rotation, are not useful to reduce the flow velocity which causes the air entrainment together with the liquid.
  • the known devices used to make easier the inflow of the driving liquid in the ejector as placing near the nozzle an anti-vortex device or deviating walls to reduce the air recirculation, or placing a duct drawing from below the most deaerated part of the liquid, are not useful to make the air dispersion in the delivery easier, because they do not reduce the fluid turbulence in the separation chamber placed upstream said devices near the nozzle.
  • the return channel can reduce just partially the rotation, the velocity and the turbulence of the flow and does not allow, by itself or coupled to other known elements, the elimination of the residual negative effects for the air separation from the liquid and for a fast pump self-priming with the highest suction lifts. Therefore it is necessary to have a pressure chamber with a liquid reserve suitable for restraining the air entrainment, slowing down the velocity and weaking the flow residual turbulence.
  • Said known embodiment has also the drawback of needing diffuser inlets with a configuration suitable for collecting, at the impeller outlet, as much air as it is separable from the liquid in the pressure chamber.
  • the possibility of a fast air separation from the liquid in the pressure chamber depends, as it will better explained later on, also on the way the air is collected upstream, at the impeller outlet.
  • the possibility of collecting faster the air at the impeller outlet is made conditional on the possibility of allowing the separation from the liquid of the greatest air amount coming in the pressure chamber, when the self-priming phase is extended through the highest suction lifts.
  • Said retum channel can be coupled to an usual radial diffuser around the impeller periphery, producing the same result of reducing the rotation and the flow turbulence in the pressure chamber.
  • a drawback consists in the considerable increase of the pump working noise, due to the interruption of the continuity in the vanes succession through the combination of two separate vaned portions, with a change of direction in the deviation from the centrifugal radial direction in the diffuser at the impeller outlet to the centripetal radial direction in the return channel.
  • the consequent interruption in the guide of the direction and of the flow velocity causes a worse operating efficiency.
  • Said interruption of the guide of the direction and of the flow velocity increases considerably the fluidborne noise during the self-priming process, increasing progressively said noise because of the increase in the amount of the solute air and of the separated air in bubbles, entrained by the liquid in the pump.
  • the noise becomes more considerable if the pump casing is made with a thin sheet steel.
  • a further drawback is that a common radial diffuser around the impeller periphery makes easier the expulsion of the liquid in the delivery at the impeller start, because of its inlet angle configuration.
  • the pump delivers temporarily the greatest operating flow rate with a zero suction lift, since all the chambers and the ducts included wherein are pre-filled with liquid, even, temporarily, the ones on the suction side of the impeller.
  • the kinetic energy and the thrust of the liquid going out from the diffuser cause the expulsion and the dissipation from the delivery port of even a part of the liquid contained in the pressure chamber, that is a part of the driving liquid that must stay in the pump for the self-priming process while the air is dispersed in the delivery.
  • Said liquid expulsion at the start is greater in the pumps having a greater flow rate and larger passages in the ejector and in the impeller, anyhow needing a greater driving liquid reserve.
  • the air pocket present in the pressure chamber after the start because of the dispersed liquid, prevents the following self-priming process. Said self-priming process is even more prevented if a rotation is imparted to said initial air pocket, fed by the air coming from the suction pipe, with the liquid reserve remained in the pressure chamber by a flow coming in said chamber with an excessive residual rotational component and velocity, holding the air through the residual centrifugal force of the liquid and because of the effect of the flow velocity entrainment.
  • a common radial diffuser around the periphery of the impeller collects quickly the air coming out of the impeller and makes it come out more quickly and in a larger amount from the return channel in the pressure chamber. It has been observed that said larger amount of coming air slows down its separation from the liquid in the pressure chamber and its dispersion in the delivery with pumps having a greater flow rate, with an higher flow velocity at the outlet of the return channel or with an insufficient liquid reserve, when the self-priming phase extends with suction lifts higher than the average.
  • the present invention intends to overcome all the above-mentioned limits and the above-mentioned drawbacks of a diffuser with a return channel in a single-impeller shallow-well jet pump.
  • An aim of the present invention is that of improving further the pump self-priming capability with the highest suction lifts allowed by the atmospheric pressure through a further reduction of the velocity, of the residual rotation, and of the fluid turbulence in the pressure chamber.
  • Another aim is that of obtaining the self-priming with a pump casing of smaller dimensions containing a smaller liquid reserve and/or improving the self-priming capability without increasing the pump dimensions and the needed liquid reserve.
  • Another aim is that of reducing the operating noise during the self-priming phase and during the steady condition.
  • Another aim is that of improving the performance in steady condition with the highest suction lifts.
  • a further aim is that of reducing the pump cost.
  • the pump which is the object of the invention is shown in partial views in the drawings and is marked with 1, 100, 101, 102, 103, 104, 105, 106 as a whole.
  • said pump includes a pump casing 2, 20, in which there is the pressure chamber 3, 30 communicating with the delivery port 4, 40 placed on the upper part of said chamber; an ejector 5, 50 connected upstream to the suction port (not visible in the drawings) of the pump and downstream to an impeller 6, 60 keyed on the driving shaft with horizontal axis of rotation 7, 70.
  • Said ejector 5 forms directly the stationary suction duct of the impeller 6 or it may be connected to said impeller 60 through a duct or connection 80 placed between said ejector 50 and said impeller 60, said ejector 5, 50 includes the respective feeding nozzle (not visible in the drawings) fed on its turn by the driving liquid in said pressure chamber 3, 30.
  • the placing of said ejector in the pump can be any: coaxial to the impeller axis of rotation, as shown in the drawings, or parallel or transversal with respect to said axis, said ejector being, with any different placing, anyhow connected, through a duct or connection, to the suction orifice of the impeller.
  • a diffuser Downstream said impeller 6, 60 there is a diffuser with a return channel 9, 90 with at least an interposed guide vane 14, 140 conveying the fluid coming out of said impeller 6, 60 in the central part of said pressure chamber 3, 30.
  • Said return channel 9, 90 substantially radial centripetal is placed between two walls axially spaced.
  • One wall 10, 107 has at least one inlet on the periphery 11, 110.
  • Said wall 10, 107 is placed adjacent to the suction side of said impeller 6, 60 and connected with said stationary suction duct 5, 50, 80 with the possible interposition of a seal means 18. 180.
  • the other wall 12, 120 is inserted inside a peripheral cylindrical surface 200, 201 of said pump casing 2, 20, with at least an outlet 13, 130, placed 360° in a circular crown around said stationary suction duct 5, 50, 80 of said impeller 6, 60.
  • Said diffuser with a return channel can have any combination of the two functions, diffuser and channel for the conveyance from the impeller periphery toward the axis, joined together or coupled, juxtaposed and subsequent so therefore they are distinguishable or combined so as to be not distinguishable, in a course with a continuous guide of the flow velocity and of the flow direction, also in the change of direction in the deviation from the centrifugal radial or tangential peripheral direction to the centripetal radial direction in the return channel.
  • At least one deflector 15, 150 substantially annular so as to direct and distribute toward different directions, marked by the arrows 16-17, 160-170, diverging and converging, to the outside and the inside of said deflector 15, 150, the fluid coming from said retum channel 9, 90.
  • Said at least one deflector 15, 150 is placed in such a way as it prevents a concentrated flow and reduces further the velocity, the residual rotation and the residual turbulence of said fluid in said pressure chamber 3, 30, carrying on the guide of the flow without any additional loss, letting the air contained in the fluid follow the path of least resistance.
  • the invention uses in a jet pump the Principle of Least Resistance, considered in the technical literature of centrifugal pumps for the control of the fluid prerotation in the impeller approach.
  • the present invention applies the principle of the path of least resistance downstream the impeller through a device, formed by at least one deflector, to carry on the control of the direction, of the velocity, of the residual rotation and turbulence of the flow (or fluid current) beyond the return channel in order to advance the start of the air separation from the liquid.
  • Said device provides several outlets from the return channel at the inlet in the pressure chamber, distributing the flow toward different directions, avoiding a concentrated axial flow, in order to let the air follow the path of least resistance independently of the main liquid courses.
  • said at least one deflector 15, forming substantially an annular baffle can have radial outlines with different shapes: truncated cone or bell-shaped, curved or flat.
  • Said at least one deflector 15, 150 can have frontal outlines substantially annular or can have a configuration with sectors which are substantially circular, equidistant or differently placed or spaced angularly and radially, equal or with a different width and/or with different shapes, frontally adjacent as shown in fig. 8 or separated one from the other and defined by substantially radial blades or walls 14, 19, as shown in fig. 2, or a configuration with lobes separated by septa connected to said guide blades.
  • Said at least one deflector with a substantially annular shape 15, 150 is placed with respect to said outlet 13, 130 from said return channel 9, 90 through flow directing means, consisting in a plurality of walls 14, 19 or guide blades 190, suitable to eliminate or reduce the residual rotation and the fluid turbulence coming out from said return channel 9, 90 at the inlet of said pressure chamber 3, 30.
  • a plurality of guide ribs 197, 198 substantially radial placed on said stationary suction duct 5, 50, 80, separated from said deflector 15, 150, can be coupled to said deflector 15, 150.
  • Said substantially circular baffle 157, 158, 159 around said stationary suction duct 54, 81, 82, 84 can be coupled to at least one substantially concentric annular baffle 151, 152, 154 connected through the guide blades 191, 192, 194.
  • a plurality of guide blades 191, 192, 194 or guide ribs 193 can be placed acting as flow directing means suitable for eliminating or reducing the residual rotation and the turbulence of said fluid.
  • said substantially circular baffle 153 facing said outlet 133 of said retum channel 93 and around the terminal part of said stationary suction duct 53, 83, avoids a concentrated axial flow and the consequent air entrainment with the liquid and deviates the flow from the direction toward the nozzle when it is placed in the central part of the pump, decreasing the air recirculation.
  • the opening between said outlet 133 of said retum channel 93 and the terminal part of said deflector 153 increases the outlet section of the return channel and decreases the entry velocity of the flow in said pressure chamber 33.
  • the surrounding liquid is used to restrain the flow turbulence distributing it in the pressure chamber 33.
  • the liquid tends to flow on said deflector 153 with the directions marked by the arrows 173.
  • the air tends to take more internal directions, marked by the arrows 163, flowing on the liquid following the path of least resistance with a temporary or partial separation from the liquid, making the definitive separation easier with the fluid state of calm obtained in the pressure chamber 33.
  • the sectors of said deflector 153 between said guide ribs 193 can have inclinations and/or shapes different from one anothers.
  • said at least one deflector 155 is formed by walls with substantially constant and coincident outlines, independently of the possible different extents of said outlines, on parallel planes with respect to the shape divisional plane, placed preferably on said horizontal axis 75 and with orthogonal outlines perpendicular to said plane 75.
  • Said at least one deflector 155 facing said outlet 135 of said return channel 95 and around the terminal part of said stationary suction duct 55, 85 connected to said impeller 65, has inclined sides connected to the outside of said suction duct 55, 85 on septa 199 turned to the flow source, said at least one deflector 155 suitable to direct and distribute toward laterally opposed directions 165, 175 the fluid coming out from said retum channel 95.
  • Said septa 199, the possible guide ribs 195 as flow directing means and said deflector 155 are placed in such a way as to eliminate or reducing the residual rotation and the flow turbulence coming out from said return channel 95.
  • said at least one deflector 155 let the flow be distributed through other ways along other directions, decreasing its velocity in said pressure chamber 35 and using the surrounding liquid to restrain the residual turbulence and reduce the air entrainment with the liquid, letting the air follow, after said return channel 95, the path of least resistance in order to come in said pressure chamber 35 with a temporary or partial separation from the liquid, making the definitive separation easier with the state of calm of the fluid obtained in said pressure chamber 35.
  • the frontal outline of said at least one deflector 155 can be polygonal, circular or mixtilinear.
  • the outlines of said at least one deflector 155 on parallel planes with respect to a plane on said horizontal axis 75 can have different configurations.
  • the general configuration can be, for example, the one having inclined, flat or concave walls joined toward the flow source on a plane which is perpendicular to said horizontal axis 75.
  • Another general configuration can be the one having a convex deflector or a deflector with an asymmetric outline, or any other configuration suitable for directing and distributing the fluid coming out from said return channel 95 toward different directions and for eliminating or reducing the flow residual rotation, velocity and turbulence in the pressure chamber 35.
  • said deflector 155 can be coupled to other deflectors 215, preferably with a different width and height extent, respectively, parallelly and perpendicularly to said shape divisional plane, placed preferably on said horizontal axis 75.
  • Said deflectors 215 placed laterally to said deflector 155 with said septa 199, as a sort of corolla on a stem, on the terminal part of said stationary suction duct 55, 85, partially connected through the guide ribs 195, are placed in such a way as to direct and distribute toward different directions 165, 167, 175, 177 the fluid coming out from said return channel 95 decreasing its velocity and in such a way as to eliminate or reduce the fluid residual rotation and turbulence in said pressure chamber 35.
  • Said coupled deflectors 155-215 can be at least partially frontally overlapping, or said deflectors 151-157, 152-158, 156-315 can be at least partially radially overlapped, or said deflectors 154-159 can be coupled without any frontal or radial overlap.
  • the configurations of the coupled deflectors can be different according to the preferred molding possibilities. It is also possible to have a spiral and/or helicoidal development of one or more deflectors with the initial and terminal portions 156, 315 being asymmetric, with a shape, dimensions or positions which can be radially, angularly and axially different, as it is shown for example in fig 23.
  • Said flow directing means consisting in said walls or substantially radial guide blades 19, 190, 191, 196, can be connected to the wall 12, 120, 121, 126 having said outlet 13, 130, 131, 136 of said return channel 9, 90, 91, 96. Therefore said at least one deflector 15, 150, 151, 156, 315, said flow directing means 19, 190, 191, 196 and said wall 12, 120, 121, 126 form a single piece.
  • said at least one deflector 15, 150, 151, 156, 157, 315 with said flow directing means 19, 190, 191, 196 or said vanes 14 can have also the function of reinforcing structurally the walls of said diffuser with return channel 9, 90, 91, 96 against the deformations due to temperature and pressure increases.
  • Said deflector 15 can be placed with respect to said outlet 13 through extensions of the said guide vanes 14 of said return channel 9 beyond said outlet 13. Therefore said deflector 15 and said guide vanes 14 form a single piece.
  • the conveying channels 92 can be built through the zigzag course of one of the two walls 109, 122, axially spaced in correspondence with the channels 92 and connected between a conveying channel and the other, forming outlets 132 spaced 360° around said stationary suction duct 52, 82 by the guide blades 142 with the joints 147 between one channel and the other.
  • said at least one deflector 152, 153, 158 the device characterizing the pump of the invention, can be a piece keyed around the terminal part of said stationary suction duct 52, 53, 82, 83, included between said wall 109, adjacent to the impeller 62, or between the collar front 127 or the central part of said wall 210 adjacent to the impeller 63 and a frontal shoulder 28,128 with possible locating elements 29, 129 for the positioning and for preventing angular shifts.
  • said device can be coupled to said stationary suction duct 54, 55, 84, 85. Therefore said deflector 154, 155, 159, 215 and said stationary suction duct 54, 55, 84, 85 form a single piece.
  • the parts forming the diffuser with return channel and the above-described device can be built with the same material, formed by pieces joined through weldings or formed by parts connected with detachable systems or formed by parts of different or dissimilar materials, as metal and plastic or synthetic materials, connected through systems known to join or form pieces of dissimilar materials.
  • Said parts can have a stable shape, built with rigid materials or parts of said device can be flexible, built with deformable elastic materials.
  • Said parts can be realized through different structural shapes and different materials in order to obtain complementary functions, as improving the resistance against the deformations due to temperature and pressure increases, against the thrust of the flow coming out from the return channel, against corrosive liquids, against the wear due to abrasive parts, as improving the efficiency, keeping the adhesion of the return channel walls at the interposed vanes avoiding infiltrations when the vanes separate areas with a different pressure between one channel and the other.
  • the device described above coupled to a diffuser with a return channel improves the self-priming capability of a shallow-well jet pump with the highest suction lifts allowed by the atmospheric pressure.
  • the better self-priming capability is obtained through the reduction of the residual rotation, velocity and turbulence of the flow in the pressure chamber, avoiding the residual centrifugal effect restraining the air in the liquid, the entrainment effect of the air with the liquid due to the velocity of a concentrated flow and reducing the air recirculation through the nozzle.
  • said device allows a quicker air separation from the liquid in the pressure chamber, making the air come out quicker from the pump and feeding the nozzle with a deaerated driving liquid, it allows also to have configurations of the diffuser inlets suitable for collecting quicker the air coming out from the impeller without restraining the greatest air amount coming in the separation chamber and without the recirculation of said air with the liquid when the self-priming phase extends with the highest suction lifts, in addition to configurations of the diffuser and of the return channel suitable to limit the liquid expulsion in the delivery at the start, with small radial dimensions and with a vanes course with a continuous guide of the direction and flow velocity.
  • the better self-priming capability allows the use of a source from extreme suction lifts and grants the self-priming regularity in fixed installations with normal suction lifts, even without the best plant conditions.
  • the best self-priming capability the possibility of using a pump located above ground replacing a pump submersed in the liquid to be lifted eliminating any moving part in the well, even the foot valve with said pump located above ground, is increased.
  • the quicker self-priming reduces the wait time of the continuous liquid flow in the delivery after the start and the permanence time of an air cushion on the contact faces of the mechanical seal on the shaft and this is a further grant against the danger of a failure of the mechanical seal due to lubrication or cooling lack.
  • the self-priming capability is improved through a better use of the liquid reserve in the pump after the prefilling, through the velocity, rotation, turbulence reduction and the distribution of the flow in the pressure chamber, in addition to the reduction of the dispersion of the liquid in the delivery at the start.
  • the device described above allows a functionally less noisy execution with a continuous guide and progressive decrease of the flow velocity and turbulence.
  • This allows the use of the state of calm of the fluid in the pressure chamber in order to muffle the noise from the internal parts with a higher velocity and turbulence, even in a pump casing made with a thin sheet steel.
  • Said device allows to carry on beyond the return channel the reduction of the liquid velocity and turbulence without added losses, improving the operating performance through the nozzle feeding with a laminar driving liquid, increasing the flow rate and decreasing the head loss with the highest suction lifts, slowing down the beginning of cavitation which limit and reduce the highest possible flow rate when the suction lifts increase.
  • the above-mentioned device can be used to reinforce structurally the walls of said diffuser with a return channel against deformations due to temperature and pressure increases.
EP99102657A 1998-02-13 1999-02-12 Selbstansaugende Strahlpumpe mit Durchflusskontrollvorrichtung Expired - Lifetime EP0936356B9 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
IT98VI000028A ITVI980028A1 (it) 1998-02-13 1998-02-13 Pompa autodescante ad eiettore con dispositivo di controllo del flusso
ITVI980028 1998-02-13

Publications (3)

Publication Number Publication Date
EP0936356A1 true EP0936356A1 (de) 1999-08-18
EP0936356B1 EP0936356B1 (de) 2003-07-09
EP0936356B9 EP0936356B9 (de) 2003-10-29

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Application Number Title Priority Date Filing Date
EP99102657A Expired - Lifetime EP0936356B9 (de) 1998-02-13 1999-02-12 Selbstansaugende Strahlpumpe mit Durchflusskontrollvorrichtung

Country Status (5)

Country Link
EP (1) EP0936356B9 (de)
AT (1) ATE244824T1 (de)
DE (2) DE69909347T4 (de)
ES (1) ES2204009T3 (de)
IT (1) ITVI980028A1 (de)

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6168376B1 (en) 1998-02-07 2001-01-02 Brinkmann Pumpen, K.H. Brinkmann Gmbh & Co. Kg Rotary pump with ventilated chamber
EP1178214A1 (de) * 2000-07-08 2002-02-06 Philipp Hilge GmbH Kreiselpumpe
EP1219838A2 (de) * 2000-11-14 2002-07-03 CALPEDA S.p.A. Führungsrad für Kreiselpumpen
WO2016198334A1 (de) * 2015-06-08 2016-12-15 Gea Tuchenhagen Gmbh Selbstansaugende pumpenaggregation
CN106939904A (zh) * 2017-04-01 2017-07-11 江苏大学 一种组合式导叶结构
WO2018045606A1 (zh) * 2016-09-09 2018-03-15 浙江新控泵业有限公司 低噪音自吸复合泵
CN111486128A (zh) * 2019-01-15 2020-08-04 安德烈·斯蒂尔股份两合公司 用于手引导式的吹风设备的鼓风机单元
CN112648242A (zh) * 2021-01-18 2021-04-13 台州市中积智能装备有限公司 一种设有内导流结构的喷射泵

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105937507A (zh) * 2016-06-02 2016-09-14 江苏大学 一种改善射流式离心泵自吸性能的导叶
CN113007101A (zh) * 2021-03-25 2021-06-22 君禾泵业股份有限公司 一种自动调节的射流式自吸离心泵

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DE2249883A1 (de) * 1971-10-15 1973-05-30 Novex Co Ltd Selbstansaugende kreiselpumpe
EP0361328A1 (de) 1988-09-26 1990-04-04 CALPEDA S.p.A. Selbstansaugende Strahlpumpe mit axialem Diffusor
EP0401670A2 (de) 1989-06-07 1990-12-12 Ebara Corporation Selbstansaugende Kreiselpumpe
EP0460597A2 (de) * 1990-06-08 1991-12-11 CALPEDA S.p.A. Einstufige Kreiselpumpe mit einem peripherisch-axialen Diffusor

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2249883A1 (de) * 1971-10-15 1973-05-30 Novex Co Ltd Selbstansaugende kreiselpumpe
EP0361328A1 (de) 1988-09-26 1990-04-04 CALPEDA S.p.A. Selbstansaugende Strahlpumpe mit axialem Diffusor
EP0401670A2 (de) 1989-06-07 1990-12-12 Ebara Corporation Selbstansaugende Kreiselpumpe
US5100289A (en) 1989-06-07 1992-03-31 Ebara Corporation Self-priming centrifugal pump
EP0460597A2 (de) * 1990-06-08 1991-12-11 CALPEDA S.p.A. Einstufige Kreiselpumpe mit einem peripherisch-axialen Diffusor

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6168376B1 (en) 1998-02-07 2001-01-02 Brinkmann Pumpen, K.H. Brinkmann Gmbh & Co. Kg Rotary pump with ventilated chamber
EP1178214A1 (de) * 2000-07-08 2002-02-06 Philipp Hilge GmbH Kreiselpumpe
EP1219838A2 (de) * 2000-11-14 2002-07-03 CALPEDA S.p.A. Führungsrad für Kreiselpumpen
EP1219838A3 (de) * 2000-11-14 2002-07-10 CALPEDA S.p.A. Führungsrad für Kreiselpumpen
US10634145B2 (en) 2015-06-08 2020-04-28 Gea Tuchenhagen Gmbh Self-priming pump assembly
CN107820544A (zh) * 2015-06-08 2018-03-20 基伊埃图亨哈根有限公司 自抽吸的泵组件
CN107820544B (zh) * 2015-06-08 2019-09-10 基伊埃图亨哈根有限公司 自抽吸的泵组件
WO2016198334A1 (de) * 2015-06-08 2016-12-15 Gea Tuchenhagen Gmbh Selbstansaugende pumpenaggregation
WO2018045606A1 (zh) * 2016-09-09 2018-03-15 浙江新控泵业有限公司 低噪音自吸复合泵
CN106939904A (zh) * 2017-04-01 2017-07-11 江苏大学 一种组合式导叶结构
CN111486128A (zh) * 2019-01-15 2020-08-04 安德烈·斯蒂尔股份两合公司 用于手引导式的吹风设备的鼓风机单元
CN111486128B (zh) * 2019-01-15 2024-03-22 安德烈·斯蒂尔股份两合公司 用于手引导式的吹风设备的鼓风机单元
CN112648242A (zh) * 2021-01-18 2021-04-13 台州市中积智能装备有限公司 一种设有内导流结构的喷射泵

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EP0936356B9 (de) 2003-10-29
ITVI980028A1 (it) 1999-08-13
DE69909347D1 (de) 2003-08-14
EP0936356B1 (de) 2003-07-09
DE69909347T4 (de) 2004-09-09
ATE244824T1 (de) 2003-07-15
DE69909347T2 (de) 2004-04-15
ES2204009T3 (es) 2004-04-16

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