EP3519699B1 - Pumpenanordnung - Google Patents

Pumpenanordnung Download PDF

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Publication number
EP3519699B1
EP3519699B1 EP17832366.3A EP17832366A EP3519699B1 EP 3519699 B1 EP3519699 B1 EP 3519699B1 EP 17832366 A EP17832366 A EP 17832366A EP 3519699 B1 EP3519699 B1 EP 3519699B1
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EP
European Patent Office
Prior art keywords
pump
liquid
impeller
pump housing
housing cavity
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.)
Active
Application number
EP17832366.3A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP3519699A1 (de
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/de
Application granted granted Critical
Publication of EP3519699B1 publication Critical patent/EP3519699B1/de
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • 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 combined fire extinguishing pump with at least one first liquid pump unit generating a first liquid pressure, which has at least one first impeller rotatable in a first pump housing cavity connected to a liquid supply, and one of the first liquid pump unit downstream of the pump arrangement in the direction of liquid delivery, a second liquid pressure which is higher than the first liquid pressure, generating second liquid pump unit which has at least one second impeller rotatable in a second pump housing cavity, a pressure outlet of the first liquid pump unit being connected to a suction inlet of the second liquid pump unit via at least one connection.
  • Such pump arrangements with a first liquid pump unit functioning as a normal or low pressure stage and a second liquid pump unit functioning as a high pressure stage are for example from the publication GB 2,338,747 A known.
  • a large volume of liquid per time such as. B. 750 to 6000 l / min
  • a lower flow rate of liquid such. B. 250 to 400 l / min
  • Both applications can occur separately from one another and also at the same time.
  • the normal or low pressure stage and / or the high pressure stage can, for example, be coupled to a foam generator that uses water and foaming agent or a compressed air foam generator.
  • a single or multi-stage centrifugal pump is usually used in practice, while either multi-stage centrifugal pumps or single or multi-stage peripheral pumps are used to implement the high pressure stage.
  • the well-known fire pumps are suitable for both mobile and stationary applications.
  • the pump arrangement can be driven by a power take-off a vehicle engine or with a separate drive motor.
  • the first liquid pump unit, with which normal or low pressure is generated, and the second liquid pump unit, i.e. the high pressure stage, can lie on a common drive shaft, be connected to one another via an optionally connectable gear, or be installed as separate pumps.
  • One or more impellers can be used in the normal or low pressure stage as well as in the high pressure stage.
  • the liquid placed under a first liquid pressure by the normal or low pressure stage or a partial flow of this liquid can be fed to a high pressure stage inlet, i.e. the suction inlet of the high pressure stage, via a connecting line, the high pressure stage outlet likewise via a second connecting line in which an interrupt valve is provided is connected to the normal or low pressure stage.
  • a filter is provided between the normal or low pressure stage outlet and the high pressure stage inlet.
  • the printed matter beats GB 2,338,747 A proposed, instead of a conventional, cylindrical filter having through holes, which can easily become clogged, to use an elongated slot-shaped filter with a support structure which is wound in the form of a helix and which can be easily cleaned by flushing with water.
  • the filter used collects solids or dirt and gradually clogs it.
  • the filter must therefore be used regularly cleaned or rinsed or even replaced in order to ensure permanent readiness for use of the high pressure stage.
  • the use may have to be interrupted in order to clean the filter.
  • the overall structure of the known pump arrangement is also relatively large and bulky.
  • a combined fire extinguishing pump according to claim 1.
  • at least one first cross-sectional constriction is formed with the formation of at least one outer gap for a fluid passage between the inner wall and the first impeller, the connection by at least one in the direction of fluid delivery after the outer gap provided, between the first pump housing cavity and the second pump housing cavity extending connecting channel is formed.
  • the outer gap can be designed with such a small cross-section that particles are reliably retained on it and are no longer conveyed to the second liquid pump unit, that is to say the high-pressure pump unit or high-pressure stage, and cannot damage it.
  • One or more outer gaps can be provided.
  • the outer gap can be ring-shaped, elliptical, corrugated, jagged, having angles or windings, or it can be designed in another suitable shape. It is preferably provided in such a way that the entire cross section through which the liquid can flow is covered, that is to say all excessively large particles can be caught in the at least one outer gap.
  • the outer gap has the advantage that it is integrated directly into the interior of the pump and does not have to be implemented by an external component. There is no need for a sieve or filter and the associated maintenance effort. There is also no need to interrupt a use of the pump arrangement according to the invention, such as a fire brigade operation, in order to carry out a sieve or filter cleaning.
  • the outer gap is formed between the stationary inner wall, that is to say a pump housing part, and the rotating first impeller.
  • the inner wall can be composed of several wall parts that are connected to one another straight or at an angle.
  • outer gaps in the sense of the present invention can also be formed between several of these impellers and inner walls located opposite them or between several of the impellers.
  • the inner wall opposite the impeller can be opposite not only the impeller surface, but also the radially outer edge of the impeller or a tangential projection on the radially outer impeller edge, for example.
  • an outer annular space delimited to the outside by the outer gap is formed radially inward.
  • This outer annular space can extend radially inward to the impeller hub or a drive shaft of the first impeller.
  • the outer annular space is connected to a suction inlet of the second liquid pump unit via the connecting channel.
  • a portion of the delivery flow of the first liquid pump unit ie the normal or low pressure stage, flows radially inward from the impeller outlet on a rear wall of the first impeller and passes through the outer gap. Solids or dirt that are larger than the size of the gap in the outer gap are prevented from passing through the outer gap. They remain in the first pump housing cavity of the first liquid pump unit and are conveyed to the outside via the pressure outlet of the first liquid pump unit or after the end of use of the pump arrangement via its drainage connection.
  • the distance between the outer gap and the axis of rotation of the first pump unit is less than or equal to the outer radius of the first impeller.
  • the outer gap is located between a side surface of the first impeller and the stationary inner wall of the first pump housing cavity. According to the invention, the outer gap is thus formed on a relatively large diameter, as a result of which a high delivery pressure remains in the annular space formed by the outer gap and a good delivery to the second liquid pump unit is realized.
  • the pump arrangement according to the invention can, depending on the application, have first and second liquid pump units with different drive speeds. These liquid pump units have different impeller blades depending on the drive speed, with the remaining pump components usually being able to be used identically. With a smaller impeller diameter, the respective liquid pump unit provides the same delivery capacity at a higher drive speed as a liquid pump unit with a larger impeller diameter and lower drive speed. Although it is fundamentally beneficial in the present invention to choose the largest possible diameter of the split ring, i.e.
  • the split ring diameter is selected to be so small that Even with the smallest usable diameter of the first impeller there is still a gap, that is to say the outer gap, between the first impeller and the stationary inner wall of the first pump housing cavity.
  • the present invention can thus 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 neck ring diameter of the outer gap can also be selected to be so small that turned off first impellers, that is to say impellers of the normal or low pressure stage, can still be used.
  • the outer gap can 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 outer hub diameter of the first impeller and the outer impeller diameter of the first impeller.
  • the outer gap is preferably formed between the rotating first impeller and a stationary pump housing part.
  • the outer gap can be formed by additional parts that are connected to the first impeller or the pump housing part.
  • a closed annular space is located within the mostly annular outer gap.
  • the outer gap can also run around the outer radius of the first impeller. It is also possible for the support and / or cover disk of the first impeller to have a C-shaped cross section, for example, and the outer gap then extends around the areas of the first impeller that protrude from the outer radius of the first impeller.
  • the connecting channel runs at the level of the first and second pump housing cavities.
  • the connecting channel leads inside 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 can be arranged and aligned such that a direction of flow of the liquid through the at least one outer gap runs 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 design and intended use of the particular embodiment of the pump arrangement according to the invention selected. A particularly good filter effect can be achieved through appropriate gap combinations. If the liquid flows through the outer gap radially or diagonally, this has the advantage that solids penetrating into the outer gap are conveyed radially outwards again by the centrifugal force and thus do not clog the outer gap. Is the outer gap arranged so that it is axially flowed through by the liquid, possibly existing assembly tolerances have less of an effect on the gap function or they can be compensated more easily by simple mechanical measures.
  • connection channel between the first and the second liquid pump unit is realized via external connection lines, such as hoses or the like, according to one embodiment of the pump arrangement according to the invention, the connection channel can also be formed by at least one pump housing inner wall and / or between Pump housing inner walls run.
  • the connecting channel can, for example, also merge into an inner wall of the pump housing and then merge radially outward in this into a connecting line.
  • the latter variant is a simple constructive solution in order to be able to connect a ventilation pump unit to the connecting line.
  • the at least one pump housing inner wall, through which the connecting channel runs, or the pump housing inner walls, between which the connecting channel runs lies between the outer gap and an inner gap located radially further inward than the outer gap forming second cross-sectional constriction.
  • the outer gap is provided between a support disk and / or a cover disk of the first impeller and an inner wall of the first pump housing cavity.
  • the outer gap preferably has a gap dimension between 0.2 mm and 3.0 mm.
  • the gap dimension of the outer gap is particularly preferably between 0.5 mm and 2.5 mm. In a preferred embodiment of the present invention, the gap dimension of the outer gap is 0.8 mm ⁇ 0.3 mm.
  • the size of the gap in the outer gap is selected so that only solids of such a size can pass through the outer gap that they cannot damage the second liquid pump unit, that is to say the high-pressure pump unit.
  • the size of the gap in the outer gap is, in turn, selected to be so large that the lowest possible throttling losses occur and sufficient Supply of liquid to the second liquid pump unit is guaranteed.
  • the closed annular space defined by the outer gap can extend radially inward to the impeller hub or the drive shaft of the first impeller.
  • the closed annular space can, however, 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 inward than the outer gap and forms an inner gap, in which bores are provided in a support disk of the adjacent first impeller, in an outer annular space formed between the inner gap and the outer gap, no bores are provided in the support disk of the adjacent first impeller.
  • the second, inner gap in connection with the bores in the support plate creates the pressure relief required for centrifugal pumps to relieve axial thrust. Since the support disk of the first impeller is closed in the area of the outer annular space and the outer annular space is sealed radially inward by the inner gap defining the inner annular space, no solids can reach the second liquid pump unit in any other way 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 the axial thrust relief through the inner gap.
  • the outer gap is formed by at least one spacer element provided on the inner wall of the first pump housing cavity and / or on the first impeller.
  • the at least one spacer element can be provided on a surface and / or on a circumference of the first impeller.
  • the centrifugal pumps and peripheral pumps that can be used to form 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 out before the inflowing liquid is swirled by the respective pump impeller.
  • the connection point where the priming pump assembly Sucks off air for example, at the highest point of the pump suction inlet, in the pump chamber of the first liquid pump unit or within an annular space behind the last impeller of the first liquid pump unit, i.e. the normal or low pressure stage.
  • the pump arrangement according to the invention has a ventilation pump unit connected to the suction inlet of the second liquid pump unit and / or to the connecting channel.
  • the ventilation pump unit for example, at the beginning of a use of the pump arrangement according to the invention, such as an extinguishing insert, the suction line and pump chamber of the first and the second liquid pump unit can be vented.
  • the ventilation pump unit By arranging the ventilation pump unit at the suction inlet of the second liquid pump unit and / or on the connecting channel, in particular the air from the pump chamber of the peripheral pump used as the second liquid pump unit, for example, can be sucked almost completely.
  • An additional piston pump for example, can be used as the venting pump unit.
  • a connection of the ventilation pump unit is preferably arranged on a side of the second impeller facing away from the direction of liquid delivery in the connecting channel.
  • connection of the ventilation 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 cavity. There is a reduced pressure at this transition and there is thus a lower pressure load on the vent pump unit when liquid is conveyed.
  • the liquid first flows into the first liquid pump unit and is whirled up by the rotating first impeller.
  • a lot of liquid only reaches the second liquid pump unit relatively late through the outer gap, which is located radially further inward, and the connecting channel.
  • the penetrating liquid is deflected by the rotating second impeller.
  • Hardly any liquid reaches the connection point of the ventilation pump unit. In this way, the entire pump arrangement can be almost completely vented. Very little air remains in the second liquid pump unit.
  • the delivery pressure can drop for a short time.
  • the desired high pressure is then generated continuously within a few seconds.
  • the ventilation pump unit is also protected from contamination by the outer gap.
  • connection point of the ventilation pump unit even when the second liquid pump unit is in operation, only the feed pressure from the first to the second liquid pump unit is applied, so that the connection line of the ventilation pump unit can be shut off with common low-pressure fittings.
  • first and second liquid pump unit used in the pump arrangement according to the invention for which a combination of centrifugal pump and peripheral pump on a common drive shaft is preferably used, usually works in such a way that the second impeller, i.e. the peripheral wheel, runs permanently. If no liquid is to be drawn off at the high pressure outlet, the second liquid pump unit conveys via a bypass connection 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 connection line is closed by a shut-off device and a shut-off device that may be present at the high-pressure outlet of the second liquid pump unit is opened.
  • a shut-off element in the form of a ball valve with at least one with the first pump housing cavity and / or the second is therefore in a bypass connection line between the first pump housing cavity and the second pump housing cavity Pump housing cavity connected inflow and outflow channel having receptacle provided for a spherical component.
  • This embodiment of the invention thus uses a ball valve as a shut-off device for the outlet of the second liquid pump unit, so that when high-pressure liquid is not used, it can flow back into the first liquid pump unit.
  • the ball valve is adjusted so that high-pressure liquid is present at the high-pressure outlet of the pump arrangement.
  • the at least one inflow and outflow channel can be implemented by slots in the receptacle of the spherical component of the ball valve, through which the liquid can flow back into the pump housing cavity of the first or the second liquid pump unit.
  • the at least one inflow and outflow channel not only an outflow of liquid but also an inflow of liquid can be established, which can be used, for example, to compensate for the pressure load on the spherical component of the ball valve.
  • the ball valve proposed according to the invention as a shut-off device can, depending on the desired mounting position and switching function, be a 3-way ball valve with a T-hole, a 3-way ball valve with an L-hole or a 2-way ball valve.
  • the spherical component can be rotated mechanically by means of a suitable connection.
  • the rotary drive can, for. B. manually, pneumatically, hydraulically or electrically.
  • the spherical component moves in a housing component surrounding it. It is particularly favorable if the spherical component is fixed by means of sealing rings, with an inner collar being provided on the 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 can be made of PTFE, for example.
  • the inner collar in the seat of the sealing rings also provides protection when switching slowly. If, for example, the spherical component in the ball valve is adjusted, there is a risk that the sealing ring will be deformed and / or sheared off without the inner collar.
  • the inner collar provided on the receptacle for the sealing ring 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 an intermediate space between the spherical component and the housing component and thus forms the at least one inflow and outflow channel.
  • this can be achieved in that the sealing ring at this connection is surrounded on its circumference by one or more bores or openings. These openings can also be formed by the interaction of several components. Further inflow and outflow channels can also start from the space between the spherical component and the housing component.
  • a spring-loaded drain valve is provided 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 off the drain channel.
  • the ball is pushed back by a compression spring and the liquid can flow off 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 action results in more reliable emptying compared to pump emptying methods based purely on gravity.
  • FIG. 1 shows an embodiment of a pump arrangement 100 according to the invention in a front view
  • Figure 2 shows the pump assembly 100 in a side view
  • FIG Figure 3 shows the pump arrangement 100 in a sectional illustration along the section A - A of FIG Figure 1 to see.
  • the pump arrangement 100 has 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 axis of rotation R.
  • the first liquid 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 support disk 9 and a cover disk 10.
  • the second liquid 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 fluidically connected to one another. The course of the liquid delivery direction of a liquid flowing through the pump arrangement 100 is shown schematically with the aid of arrows W, W S and W V in Figure 3 shown.
  • a gap is provided between the first impeller 2 and a stationary inner wall 5 of the first pump housing cavity 1, which gap is referred to below as the outer gap 6.
  • the outer gap 6 is formed by a spacer element 14 provided between a support disk 9 of the first impeller 2 and the stationary inner wall 5.
  • the outer gap 6 has a gap dimension x of 0.8 mm ⁇ 0.3 mm.
  • the liquid flowing through the pump arrangement 100 typically water, experiences a first pressure increase in the first liquid pump unit 101 by means of the first impeller 2, which is for example 10 bar.
  • the liquid then flows, as shown schematically with the aid of the arrow W S , through the outer gap 6 in the direction of the second liquid pump unit 102.
  • solid or dirt components are in the liquid, which form the gap dimension x exceeding the size of the outer gap, held back at the outer gap 6 and conveyed radially outward again by the centrifugal force. Some of these solid or dirt components can also be comminuted by the rotation of the first impeller 2 in the outer gap 6.
  • the outer gap 6 thus acts as a filter.
  • the liquid flows radially through the outer gap 6.
  • the outer gap 6 can also be provided such that the liquid runs radially and / or diagonally and / or axially.
  • several outer gaps 6 can also be provided in the pump arrangement.
  • an inner gap 8 is provided between the first impeller 2 and a further stationary spacer element 51 of the first pump housing cavity 1.
  • An inner annular space 11 is formed radially within the inner gap 8.
  • 2 bores 12 are provided in the support disk 9 of the first impeller. Axial thrust relief of the first liquid pump unit 101 can take place via these bores 12 and the adjoining inner annular space 11.
  • a connecting channel 7 is provided between the first pump housing cavity 1 and the second pump housing cavity 3, which channel extends through the inner walls of the pump housing. The liquid filtered through the outer gap 6 is passed through this connecting channel 7 into the second pump housing cavity 3.
  • the second impeller 4 located in the second pump housing cavity 3 puts the liquid under high pressure.
  • a ventilation pump unit 16 is connected to a suction inlet 15 of the second liquid pump unit 102 with the aid of a connection 17.
  • FIG 7 14 is a sectional view along section BB of the pump assembly 100 of FIG Figure 2 shows to see.
  • connection 17 for the deaeration pump unit 16 is provided at a transition 18 from an interrupter 19, which separates a suction inlet 15 from a pressure outlet 20 of the second liquid pump unit 102.
  • Figures 4, 5 and 6 show details of a control of the pump arrangement 100 of FIG Figures 1 to 3 . It shows Figure 4 a section along the section C - C from Figure 1 , Figure 5 an enlarged detail E of Figure 4 and Figure 6 the section D - D from Figure 4 .
  • a ball valve 22 provided in a bypass connecting line 21 is used as a shut-off element.
  • the Figures 4, 5 and 6 show the ball valve 22 with which the high-pressure outlet and the bypass connection line 21 are switched on and off.
  • a spherical component 25 of the ball valve 22 is located in a receptacle 24.
  • slots or pockets are provided that form inflow and outflow channels 23, in particular for draining liquid that has flowed into a space 212 between the spherical component 25 and the surrounding housing 211 .
  • the inflow and outflow channels 23 thus serve to drain the shut-off device.
  • the spherical component 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 to support the respective sealing ring 26.
  • FIG. 13 shows a sectional view along section F-F of FIG Figure 1 .
  • a spring-loaded emptying 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)
EP17832366.3A 2017-02-15 2017-12-22 Pumpenanordnung Active EP3519699B1 (de)

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 (de) 2017-02-15 2017-12-22 Pumpenanordnung

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Publication Number Publication Date
EP3519699A1 EP3519699A1 (de) 2019-08-07
EP3519699B1 true EP3519699B1 (de) 2021-09-08

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EP (1) EP3519699B1 (pl)
DE (1) DE102017102967A1 (pl)
ES (1) ES2897410T3 (pl)
PL (1) PL3519699T3 (pl)
WO (1) WO2018150247A1 (pl)

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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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Publication number Priority date Publication date Assignee Title
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
EP3519699A1 (de) 2019-08-07
WO2018150247A1 (de) 2018-08-23
ES2897410T3 (es) 2022-03-01
DE102017102967A1 (de) 2018-08-16

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