EP3519699A1 - Arrangement de pompage - Google Patents

Arrangement de pompage

Info

Publication number
EP3519699A1
EP3519699A1 EP17832366.3A EP17832366A EP3519699A1 EP 3519699 A1 EP3519699 A1 EP 3519699A1 EP 17832366 A EP17832366 A EP 17832366A EP 3519699 A1 EP3519699 A1 EP 3519699A1
Authority
EP
European Patent Office
Prior art keywords
pump
impeller
housing cavity
pump housing
pump unit
Prior art date
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
EP17832366.3A
Other languages
German (de)
English (en)
Other versions
EP3519699B1 (fr
Inventor
Christian Wagler
Klaus-Detlef Krüger
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Pf Pumpen und Feuerloschtechnik GmbH
Original Assignee
Pf Pumpen und Feuerloschtechnik GmbH
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 Pf Pumpen und Feuerloschtechnik GmbH filed Critical Pf Pumpen und Feuerloschtechnik GmbH
Priority to PL17832366T priority Critical patent/PL3519699T3/pl
Publication of EP3519699A1 publication Critical patent/EP3519699A1/fr
Application granted granted Critical
Publication of EP3519699B1 publication Critical patent/EP3519699B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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
    • F04D1/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal 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
    • F04D13/00—Pumping installations or systems
    • F04D13/12—Combinations of two or more 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
    • F04D15/00—Control, e.g. regulation, of pumps, pumping installations or systems
    • F04D15/0072—Installation or systems with two or more pumps, wherein the flow path through the stages can be changed, e.g. series-parallel
    • 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
    • F04D29/426—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for liquid 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
    • F04D29/70—Suction grids; Strainers; Dust separation; Cleaning
    • F04D29/708—Suction grids; Strainers; Dust separation; Cleaning specially for liquid 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
    • 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
    • F04D5/007—Details of the inlet or outlet
    • 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
    • F04D7/045—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 with means for comminuting, mixing stirring or otherwise treating

Definitions

  • the present invention relates to a pump assembly, especially a fire-extinguishing water pump, having at least one first fluid pump unit generating a first fluid pressure having at least one first impeller rotatable in a first pump housing cavity connected to a fluid supply and one downstream of the first fluid pump unit in the fluid delivery direction of the pump assembly; a second fluid pressure higher than the first fluid pressure generating second fluid pump unit having at least one second impeller rotatable in a second pump housing cavity, a pressure output of the first fluid pump unit being connected to the second fluid pump unit via at least one connection.
  • Pump assemblies of this type are known as combined fire pumps with a functioning as a normal or low pressure stage first fluid pump unit and acting as a high-pressure stage second fluid pump unit, for example, from the document GB 2 338 747 A.
  • a normal or low pressure stage at a relatively low pressure of about 10 to 15 bar, a large volume of liquid per time, such. B. 750 to 6000 l / min, are provided, while the high-pressure stage at high pressure of about 40 bar, a lower flow rate of liquid such. B. 250 to 400 l / min, is provided. Both applications can occur separately and also simultaneously.
  • the normal or low-pressure stage and / or the high-pressure stage can / can be coupled, for example, with a water and foam-utilizing foam generator or a compressed air foam generator.
  • a single or multi-stage centrifugal pump is usually used in practice, while for the realization of the high-pressure stage either multi-stage centrifugal pumps or single or multi-stage peripheral pumps are used.
  • the well-known fire pumps are suitable for both mobile and stationary applications.
  • the drive of the pump arrangement can be controlled by a secondary drive a vehicle engine or with a separate drive motor done.
  • the first liquid pump unit, with the normal or low pressure is generated, and the second liquid pump unit, so the high-pressure stage can be located on a common drive shaft, be connected to each other via an optionally shiftable transmission or be installed as separate pumps. Both in the normal or low pressure stage and in the high pressure stage, one or more wheels can be used in each case.
  • the liquid set by the normal or low-pressure stage under a first liquid pressure or a partial flow of this liquid can be fed via a connecting line to a high-pressure stage inlet, ie the suction inlet of the high-pressure stage, the high-pressure stage outlet being connected via a second connecting line, in which a break valve is provided, also connected to the normal or low pressure stage.
  • a filter is provided between the normal or low-pressure stage output and the high-pressure stage input.
  • the document GB 2 338 747 A proposes, instead of a conventional through-hole, cylindrical filter which can easily clog, to use a long slot-shaped filter with a support structure wound in the form of a helix and which can be easily cleaned by means of water rinsing ,
  • a pump arrangement of the type indicated above in which between at least one fixed inner wall of the first Pumpengeophurraumraumes and the first impeller at least a first cross-sectional constriction is formed to form at least one outer gap for a liquid passage between the inner wall and the first impeller wherein the connection is formed by at least one provided in the liquid conveying direction after the outer gap, between the first pump housing cavity and the second pump housing cavity extending connecting channel.
  • the outer gap can be formed with such a small cross-section that reliably particles are retained on it and can not be conveyed further to the second liquid pump unit, that is to say the high-pressure pump unit or high-pressure stage, and can not damage them.
  • one or more outer gaps can be provided.
  • the outer gap may be annular, elliptical, corrugated, serrated, having angles or turns or formed in any other suitable shape. It is preferably provided so that the entire, can be traversed by the liquid cross-section, so all too large particles can be collected at the at least one outer gap.
  • the outer gap has the advantage that it is integrated directly into the pump interior and does not have to be realized by an outer component. A sieve or filter and an associated maintenance accounted for. It is also no interruption of an insert of the pump assembly according to the invention, such as a firefighter, necessary to make a screen or filter cleaning. Due to the inventive design of the pump assembly, this also has a more compact design than known pump assemblies.
  • the outer gap is formed between the fixed inner wall, that is, a pump housing part, and the rotating first impeller.
  • the inner wall may be composed of a plurality of mutually straight or angularly connected wall parts.
  • the first liquid pump unit has a plurality of impellers, also between a plurality of these impellers and inner walls located opposite them or between a plurality of the impellers outer gaps may be formed in the sense of the present invention.
  • the inner wall located opposite the impeller can be opposed not only to the impeller surface but also to the radially outer edge of the impeller or, for example, to a tangentially extending projection on the radially outer edge of the impeller.
  • outer gap Through the outer gap is formed radially inwardly by the outer gap outwardly limited outer annular space.
  • This outer annular space may extend radially inwardly to the impeller hub or a drive shaft of the first impeller.
  • the outer annular space is connected via the connecting channel with a suction inlet of the second liquid pump unit.
  • a portion of the delivery flow of the first fluid pump unit ie the normal or low pressure stage, flows radially inward from the impeller outlet on a rear wall of the first impeller, thereby passing the outer gap.
  • Solid or dirt larger than the gap of the outer gap is prevented from passing through the outer gap. They remain in the first pump housing cavity of the first liquid pump unit and are conveyed out via the pressure outlet of the first liquid pump unit or after completion of the use of the pump assembly via the drainage connection to the outside.
  • the distance of the outer gap from the axis of rotation of the first pump unit is less than or equal to the outer radius of the first impeller. In this embodiment of the invention, therefore, there is the outer gap between a side surface of the first impeller and the fixed inner wall of the first pump housing cavity.
  • the outer gap is thus formed according to the invention on a relatively large diameter, whereby in the annular space formed by the outer gap a high delivery pressure remains and a good feed to the second liquid pump unit is realized.
  • the pump arrangement according to the invention can have first and second liquid pump units with different drive speeds. These fluid pump units have different impeller blades in dependence on the drive speed, wherein usually the remaining pump components can be used identically. With a smaller impeller diameter, the respective fluid pump unit will provide the same delivery at a higher input speed as a larger impeller diameter fluid pump unit and lower input speed.
  • the split ring diameter is chosen so small that Even at the smallest usable diameter of the first impeller still results in a gap, so the outer gap between the first impeller and the fixed inner wall of the first pump housing cavity.
  • the present invention can be used largely independently of the diameter of the at least one first impeller of the first liquid pump unit used in each case.
  • the gap ring diameter of the outer gap can also be chosen so small that even wacky first wheels, so wheels of the normal or low pressure stage, can still be used.
  • the outer gap may be formed, for example, on a rear wall of the impeller of the first liquid pump unit.
  • the diameter of the outer gap then corresponds to a value between the hub outer diameter of the first impeller and the impeller outer diameter of the first impeller.
  • the outer gap between the rotating first impeller and a fixed pump housing part is formed.
  • the outer gap can be formed by additional parts which are connected to the first impeller or the pump housing part.
  • Within the usually annular outer gap is a closed annulus.
  • the outer gap can also run around the outer radius of the first impeller.
  • support and / or cover plate of the first impeller have an example C-shaped cross section and the outer gap then extends around the projecting from the outer radius of the first impeller regions of the first impeller.
  • the connecting channel extends at the level of the first and the second pump housing cavity.
  • the connecting channel leads in this embodiment of the invention within the pump housing through at least one of its inner walls from the first into the second pump housing cavity.
  • the at least one outer gap may be arranged and aligned in the pump arrangement according to the invention such that a direction of flow of the liquid through the at least one outer gap extends axially and / or radially and / or diagonally to the axis of rotation of the first impeller.
  • the specified flow directions can be used individually or in combination depending on the training and purpose of each selected embodiment of the pump assembly according to the invention. By appropriate gap combinations can be achieved a particularly good filtering effect. If the outer gap flows radially or diagonally through the liquid, this has the advantage that solids penetrating into the outer gap are again conveyed radially outwards by the centrifugal force and thus do not clog the outer gap. Is the outer gap arranged so that he If the liquid flows through axially, any existing assembly tolerances have less effect on the gap function or can be compensated more easily by simple mechanical measures.
  • the connecting channel between the first and the second liquid pump unit via external connecting lines can also be through at least one pump housing inner wall and / or between Pump housing interior walls run.
  • the connecting channel can, for example, also pass into a pump housing inner wall and then radially outwardly into a connecting line.
  • the latter variant is a simple structural solution in order to be able to connect a venting pump unit to the connecting line.
  • the at least one pump housing inner wall through which the connecting passage extends, or the pump housing inner walls between which the connecting passage runs lies between the outer gap and an inner gap located radially further inwardly than the outer gap forming the second cross-sectional constriction.
  • the outer gap between a support disk and / or a cover disk of the first impeller and an inner wall of the first pump housing cavity is provided.
  • the outer gap has a gap between 0.2 mm and 3.0 mm.
  • the gap dimension of the outer gap is between 0.5 mm and 2.5 mm.
  • the gap of the outer gap is 0.8 mm ⁇ 0.3 mm.
  • the gap size of the outer gap is selected so that only solids of such a size can pass through the outer gap, which can lead to no damage to the second liquid pump unit, so the high-pressure pump unit.
  • the gap size of the outer gap is in turn chosen to be as large as possible so that the smallest possible throttling losses occur and a sufficient ensuring adequate supply of liquid to the second liquid pump unit.
  • the defined by the outer gap closed annulus may extend radially inwardly to the impeller hub or the drive shaft of the first impeller.
  • the closed annulus can also be delimited radially inward by a second, inner annular gap.
  • an inner annular space is provided between a hub region of the first impeller and a second cross-sectional constriction of the first pump housing cavity that is located radially further inside than the outer gap, in which bores are provided in a support disk of the adjacent first impeller, wherein in a formed between the inner gap and the outer gap outer annular space no holes in the support disk of the adjacent first impeller are provided.
  • the second, inner gap in conjunction with the holes in the support disc creates a pressure relief required for centrifugal pumps for axial thrust relief. Since the support disk of the first impeller is closed in the region of the outer annulus and the outer annulus is sealed radially inwardly by the inner annulus defining inner gap, no solids can pass to the second liquid pump unit other than through the outer gap. Due to the design with the outer and the second, inner gap, the advantage of the high feed pressure to the second liquid pump unit in the outer gap can be combined with the advantage of axial thrust relief through the inner gap.
  • the outer gap is formed by at least one provided on the inner wall of the first pump housing cavity and / or on the first impeller spacer.
  • the at least one spacer element may be provided on a surface and / or on a circumference of the first impeller.
  • centrifugal pumps and peripheral pumps which can be used for the formation of the pump arrangement according to the invention are not self-priming. For a quick and safe pressure build-up in the centrifugal pump and in the peripheral pump, it is important that as much air as possible can be sucked off before the inflowing fluid is swirled by the respective pump impeller.
  • the point of connection where the decision Ventilation pump unit air sucks for example, at the highest point of the Pumpensaugeingangs, in the pump chamber of the first liquid pump unit or within an annulus behind the last impeller of the first liquid pump unit, so the normal or low pressure stage lie.
  • the pump arrangement according to the invention has a venting pump unit connected to the suction inlet of the second liquid pump unit and / or to the connection channel.
  • the vent pump unit can be vented, for example, at the beginning of an insert of the pump assembly according to the invention, such as a Löscheinsatzes, suction line and pump chamber of the first and second liquid pump unit.
  • a connection of the venting pump unit is arranged on a side of the second impeller facing away from the liquid conveying direction in the connecting channel.
  • connection of the venting pump unit is located at a transition from a breaker for separating the suction side and pressure side of the second pump housing cavity to the suction side of the second pump housing hollow space. At this transition, there is a reduced pressure and thus there is a lower pressure load for the venting pump unit when conveying liquids.
  • the liquid first flows into the first liquid pump unit and is fluidized by the rotating first impeller. Only relatively late does much liquid pass through the radially inner outer gap and the connecting channel into the second liquid pump unit. The penetrating liquid is deflected by the rotating second impeller. There is hardly any liquid to the connection point of the venting pump unit. In this way, the entire pump assembly can be vented almost completely. There remains only very little air in the second liquid pump unit.
  • the delivery pressure may still drop for a short time. Within a few seconds, however, the desired high pressure is permanently generated.
  • the venting pump unit is also protected by the outer gap from contamination.
  • connection point of the venting pump unit even when the second liquid pump unit is operating, only the feed pressure from the first to the second liquid pump unit is present, so that the connection line of the venting pump unit can be shut off with conventional low-pressure fittings.
  • the combination of the first and second liquid pump units used in the pump arrangement according to the invention usually works in the form that the second impeller, ie the peripheral impeller, runs permanently. If no liquid removal takes place at the high-pressure outlet, the second liquid pump unit conveys via a bypass connecting line back into the pressure outlet or the suction inlet of the first liquid pump unit. In order to use the high-pressure outlet, the bypass connecting line is closed by a shut-off and a possibly present at the high-pressure outlet of the second liquid pump unit obturator is opened.
  • a shut-off device in the form of a ball valve with at least one with the first pump housing cavity and / or the second Pump housing cavity connected inlet and outlet channel receiving receptacle provided for a spherical member.
  • this embodiment of the invention uses a ball valve as a shut-off device for the outlet of the second fluid pump unit, so that when high-pressure fluid is not used, it can flow back into the first fluid pump unit.
  • the ball valve is adjusted so that high pressure fluid is applied to the high pressure outlet of the pump assembly.
  • liquid can repeatedly penetrate between a spherical component of the ball valve and the housing component in which the spherical component is mounted. There is a risk that this liquid can freeze in frost and cause damage to the pump assembly.
  • the ball valve is designed so that regardless of the switching position of the obturator can flow out of this, via the at least one inflow and outflow liquid in at least one of the pump housing cavities. The entire obturator, including existing interstices, can therefore be drained via the inflow and outflow channel. An additional connection is not required.
  • This embodiment of the invention has the advantage that no liquid remains in the obturator, which can freeze, for example, at low ambient temperatures and lead to frost damage to the pump assembly.
  • the at least one inflow and outflow channel can be realized by slots in the receptacle of the spherical member of the ball valve, through which the liquid can flow again into the pump housing cavity of the first or the second liquid pump unit.
  • By at least one inflow and outflow channel not only a drainage of liquid, but also a liquid flow can be produced, which can be used for example for a balance of the pressure load on the spherical member of the ball valve.
  • the ball valve proposed as a shut-off device may be a 3-way ball valve with T-bore, a 3-way ball valve with L bore or a 2-way ball valve.
  • the spherical member can be mechanically rotated by a suitable connection.
  • the rotary drive can z. B. manually, pneumatically, hydraulically or electrically.
  • the spherical member moves in a surrounding housing member. It is particularly advantageous if in this case the spherical component is fixed by means of sealing rings, wherein an inner collar is provided on receptacles of the sealing rings.
  • the sealing rings fix the ball and seal at least two of the connections on the housing component against each other.
  • the sealing rings may be formed, for example, of PTFE.
  • PTFE polytyrene
  • the provided on the receptacle for the sealing ring inner collar supports the sealing ring against deformation and / or shearing.
  • At least one of the connections on the housing component of the ball valve is designed so that it has a permanent connection to a gap between the spherical component and the housing component and thus forms the at least one inflow and outflow channel.
  • This can be realized in the present invention in that the sealing ring is surrounded at this connection at its periphery by one or more holes or openings.
  • a spring-loaded drain valve is provided in the pump assembly according to the invention between the first pump housing cavity and the second pump housing cavity.
  • a ball of the drain valve is pressed into a receptacle and thereby seals the drain channel.
  • the ball With the embodiment of the invention containing the spring-loaded drain valve no overpressure from the second pump housing cavity over the first pump housing cavity, the ball is pushed back by a compression spring and the fluid can drain from the second pump housing cavity into the first pump housing cavity.
  • the spring-loaded drain valve can be used with different bore diameters. The spring effect results in more reliable emptying compared to purely gravity based pump emptying methods.
  • Figure 1 shows schematically an embodiment of the pump assembly according to the invention in a front view with a view of a first liquid pump unit, that is, a normal or low pressure pump unit, the pump arrangement shows;
  • Figure 2 schematically shows the pump assembly of Figure 1 in a side view
  • FIG. 1 View of the first liquid pump unit, a second liquid pump unit, which is a high-pressure pump unit, and a vent pump unit; schematically shows the pump assembly of Figures 1 and 2 in a sectional view along the section A - A of Figure 1, wherein the first and the second liquid pump unit can be seen in cross section; schematically shows a sectional partial view of the pump assembly of Figures 1 to 3 along the section C - C of Figure 1, in particular a shut-off of the pump assembly is shown in detail;
  • FIG. 5 shows the region E of Figure 4 in an enlarged view; schematically shows a sectional partial view of the pump assembly of the fi gures 1 to 3 along the section D - D of Figure 4 with a view of the Ab from locking member shows; 2 schematically shows a sectional partial view of the pump arrangement of FIGS. 1 to 3 along the section B - B of FIG. 2 with a view onto a connection region of the venting pump unit and schematically shows a partial sectional view of the pump arrangement of FIGS. 1 to 3 along the section F - F of FIG overlooking an emptying valve of the pump assembly shows.
  • FIG. 1 shows an embodiment of a pump arrangement 100 according to the invention in a front view
  • FIG. 2 shows the pump arrangement 100 in a side view
  • FIG. 3 shows the pump arrangement 100 in a sectional view along the section A - A of FIG.
  • the pump assembly 100 includes a first liquid pump unit 101, which functions as a normal or low pressure pump, and a second liquid pump unit 102, which generates a high pressure.
  • the first liquid pump unit 101 and the second liquid pump unit 102 have the same rotation axis R.
  • the first fluid pump unit 101 has a first pump housing cavity 1 in which a first impeller 2 is provided for rotation in the first pump housing cavity 1.
  • the first impeller has a carrier disk 9 and a cover disk 10.
  • the second fluid pump unit 102 has a second pump housing cavity 3 in which a second impeller 4 is provided for rotation in the second pump housing cavity 3.
  • the pump housing cavities 1, 3 are fluidly connected to each other.
  • the liquid conveying direction course of a liquid flowing through the pump assembly 100 is schematically illustrated by arrows W, W s and W v in FIG.
  • outer gap 6 Between the first impeller 2 and a fixed inner wall 5 of the first pump housing hollow space 1, a gap is provided, which is referred to below as outer gap 6.
  • the outer gap 6 is in the embodiment shown by a between a support plate 9 of the first impeller 2 and the fixed inner wall
  • the outer gap 6 in the embodiment shown by way of example, has a gap dimension x of 0.8 mm ⁇ 0.3 mm.
  • the liquid flowing through the pump arrangement 100 typically water, experiences in the first liquid pump unit 101 by means of the first impeller 2 a first pressure increase, which is for example 10 bar. Thereafter, the liquid flows, as shown schematically by the arrow W s , through the outer gap 6 in the direction of the second liquid pump unit 102. Upon passage of the outer gap
  • the outer gap 6 thus acts as a filter.
  • the liquid flows radially through the outer gap 6.
  • the outer gap 6 may also be provided so that the liquid extends radially and / or diagonally and / or axially.
  • a plurality of outer gaps 6 may be provided in the pump assembly.
  • an inner gap 8 is provided between the first impeller 2 and a further fixed spacer element 51 of the first pump housing cavity 1.
  • an inner annular space 1 1 is formed.
  • holes 12 are provided in the support plate 9 of the first impeller. About these holes 12 and the adjacent inner annular space 1 1 can be done Axialschubentlastung the first fluid pump unit 101.
  • a connecting channel 7 is provided between the first pump housing cavity 1 and the second pump housing cavity 3, which extends through inner walls of the pump housing. The filtered through the outer gap 6 liquid is passed through this connecting channel 7 in the second pump housing cavity 3.
  • the second impeller 4 located in the second pump housing cavity 3 sets the liquid under high pressure.
  • a vent pump unit 16 by means of a terminal 17 is connected. This can be seen in detail in Figure 7, which shows a sectional view along the section B - B of the pump assembly 100 of Figure 2.
  • the port 17 for the vent pump unit 16 is provided at a junction 18 of a breaker 19 which separates a suction inlet 15 from a pressure outlet 20 of the second liquid pump unit 102.
  • FIGS. 4, 5 and 6 show details of a control of the pump arrangement 100 of FIGS. 1 to 3.
  • FIG. 4 shows a sectional view along the section C - C of FIG. 1
  • FIG. 5 shows an enlarged detail E of FIG. 4 and FIG Section D - D from FIG. 4.
  • a ball valve 22 provided in a bypass connection line 21 is used as a shut-off element.
  • FIGS. 4, 5 and 6 show the ball valve 22 with which the high-pressure outlet and the bypass connection line 21 are connected and disconnected.
  • the inlet and outlet channels 23 in particular for discharging into a gap 212 between the spherical member 25 and the surrounding housing 21 1 liquid flowed form.
  • the inflow and outflow channels 23 thus serve to drain the obturator.
  • the spherical member 25 is fixed in position in the receptacle 24 by means of sealing rings 26.
  • the sealing rings 26 are each provided in a sealing ring receptacle 27.
  • the sealing ring receptacle 27 has an inner collar 28 for supporting the respective sealing ring 26.
  • FIG. 8 shows a sectional view along the section F - F of FIG. 1.
  • a spring-loaded drain valve 29 is provided between the first liquid pump unit 101 and the second liquid pump unit 102.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

La présente invention concerne un arrangement de pompage comprenant une première unité de pompage de liquide, laquelle possède un premier rotor rotatif dans un premier espace creux de carter de pompe, et une deuxième unité de pompage de liquide montée en aval de la première unité de pompage de liquide dans le sens de transport du liquide de l'arrangement de pompage, produisant une deuxième pression de liquide qui est supérieure à la première pression de liquide et possédant un deuxième rotor rotatif dans un deuxième espace creux de carter de pompe. Une sortie de pression de la première unité de pompage de liquide est reliée à la deuxième unité de pompage de liquide par le biais d'au moins une liaison. En vue de réaliser un tel arrangement de pompage avec une structure compacte dans laquelle la deuxième unité de pompage de liquide est protégée de manière fiable contre la pénétration d'impuretés, l'invention est caractérisée en ce qu'entre au moins une paroi intérieure fixe du premier espace creux de carter de pompe et le premier rotor, au moins un interstice extérieur est formé entre la paroi intérieure et le premier rotor, et la liaison est formée par au moins un canal de liaison qui se trouve après l'interstice extérieur dans le sens de transport du liquide et s'étend entre le premier espace creux de carter de pompe et le deuxième espace creux de carter de pompe.
EP17832366.3A 2017-02-15 2017-12-22 Arrangement de pompage Active EP3519699B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PL17832366T PL3519699T3 (pl) 2017-02-15 2017-12-22 Układ pompowy

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102017102967.2A DE102017102967A1 (de) 2017-02-15 2017-02-15 Pumpenanordnung
PCT/IB2017/058359 WO2018150247A1 (fr) 2017-02-15 2017-12-22 Arrangement de pompage

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EP3519699A1 true EP3519699A1 (fr) 2019-08-07
EP3519699B1 EP3519699B1 (fr) 2021-09-08

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WO (1) WO2018150247A1 (fr)

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DE102018217441A1 (de) * 2018-10-11 2020-04-16 Albert Ziegler Gmbh Pumpeneinrichtung
FR3090757B1 (fr) * 2018-12-21 2021-11-19 Innovation Pool Factory Pompe pour l'entretien des piscines à configuration adaptable en fonction du besoin
DE202019101677U1 (de) * 2019-03-25 2020-06-26 PF Pumpen und Feuerlöschtechnik GmbH Pumpenaggregat

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US3542594A (en) * 1968-06-19 1970-11-24 Maytag Co Fluid control system
JPS6332195A (ja) * 1986-07-24 1988-02-10 Shibaura Eng Works Co Ltd 複合ポンプ
IT1201783B (it) * 1986-11-27 1989-02-02 Zanussi Elettrodomestici Gruppo di pompaggio in particolare per macchine lavastoviglie
FI95540C (fi) * 1990-09-25 1996-02-26 Ahlstroem Oy Menetelmä ja laite kaasun erottamiseksi kiintoainetta sisältävästä nesteestä
GB2338747B (en) 1998-06-26 2002-04-10 Godiva Ltd Pumps
FR2950941B1 (fr) 2009-10-05 2011-12-09 Arbatax Pompe electrique double pour l'entretien des piscines

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PL3519699T3 (pl) 2021-12-27
ES2897410T3 (es) 2022-03-01
EP3519699B1 (fr) 2021-09-08
WO2018150247A1 (fr) 2018-08-23
DE102017102967A1 (de) 2018-08-16

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