EP3438555A1 - Groupe motopompe de circulation - Google Patents

Groupe motopompe de circulation Download PDF

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Publication number
EP3438555A1
EP3438555A1 EP17184776.7A EP17184776A EP3438555A1 EP 3438555 A1 EP3438555 A1 EP 3438555A1 EP 17184776 A EP17184776 A EP 17184776A EP 3438555 A1 EP3438555 A1 EP 3438555A1
Authority
EP
European Patent Office
Prior art keywords
pump unit
impeller
circulating pump
flow
flow path
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.)
Withdrawn
Application number
EP17184776.7A
Other languages
German (de)
English (en)
Inventor
Thomas Blad
Christian BLAD
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.)
Grundfos Holdings AS
Original Assignee
Grundfos Holdings AS
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 Grundfos Holdings AS filed Critical Grundfos Holdings AS
Priority to EP17184776.7A priority Critical patent/EP3438555A1/fr
Priority to PCT/EP2018/070968 priority patent/WO2019025525A1/fr
Priority to EP18745974.8A priority patent/EP3662204A1/fr
Priority to US16/635,787 priority patent/US11359822B2/en
Priority to CN201880050279.0A priority patent/CN110998191B/zh
Publication of EP3438555A1 publication Critical patent/EP3438555A1/fr
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
    • F24D3/00—Hot-water central heating systems
    • F24D3/02—Hot-water central heating systems with forced circulation, e.g. by 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
    • F04D1/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D1/006—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps double suction 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
    • F04D13/14—Combinations of two or more pumps the pumps being all of centrifugal 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
    • F04D15/00—Control, e.g. regulation, of pumps, pumping installations or systems
    • F04D15/0005—Control, e.g. regulation, of pumps, pumping installations or systems by using valves
    • F04D15/0016—Control, e.g. regulation, of pumps, pumping installations or systems by using valves mixing-reversing- or deviation valves
    • 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
    • F04D15/0005—Control, e.g. regulation, of pumps, pumping installations or systems by using valves
    • F04D15/0022—Control, e.g. regulation, of pumps, pumping installations or systems by using valves throttling valves or valves varying the pump inlet opening or the outlet opening
    • 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
    • F04D15/0066—Control, e.g. regulation, of pumps, pumping installations or systems by changing the speed, e.g. of the driving engine
    • 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
    • F04D29/4293—Details of fluid inlet or outlet
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
    • F24D3/00—Hot-water central heating systems
    • F24D3/10—Feed-line arrangements, e.g. providing for heat-accumulator tanks, expansion tanks ; Hydraulic components of a central heating system
    • F24D3/105—Feed-line arrangements, e.g. providing for heat-accumulator tanks, expansion tanks ; Hydraulic components of a central heating system pumps combined with multiple way valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
    • F24D2220/00—Components of central heating installations excluding heat sources
    • F24D2220/02—Fluid distribution means
    • F24D2220/0207—Pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
    • F24D2220/00—Components of central heating installations excluding heat sources
    • F24D2220/02—Fluid distribution means
    • F24D2220/0271—Valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
    • F24D2220/00—Components of central heating installations excluding heat sources
    • F24D2220/04—Sensors
    • F24D2220/042—Temperature sensors
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/85954—Closed circulating system
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/85978—With pump
    • Y10T137/86131—Plural
    • Y10T137/86163—Parallel

Definitions

  • This embodiment of the invention makes it possible to use the circulation pump unit in a heating circuit with a mixer and the second input of Ummélzpumpenaggregates liquid with a pre-pressure i. to supply a residual conveying height.
  • This form can be provided for example by a circulation pump in a boiler or a compact heating system.
  • the mixing point of the mixer is then located in the described Umisselzpumpenaggregat in this arrangement and it is no longer necessary to reduce the form or the residual head on the input side of the mixer to the same suction pressure on the suction side of Umisselzpumpenaggregates in the over the mixer to be supplied to the heating circuit to reach.
  • the circulatory pump unit according to the invention can be supplied with fluids at two different pressure levels.
  • the at least one first flow path and the at least one second flow path are arranged in a common impeller. Ie. upon rotation of the impeller with the two flow paths, a pressure increase of the liquid flowing through these flow paths takes place via both flow paths.
  • two non-rotatably arranged wheels which rotate together. These may be integrally formed with each other or rotatably connected to each other in any other suitable manner.
  • an impeller with two blade rings Use find, wherein a first blade ring, the first flow paths and a second blade ring defines the second flow paths.
  • Such an impeller may be formed so that the inlets or inlets for the two flow paths are located on the same axial side, viewed in the direction of the axis of rotation, or else against each other in the axial direction opposite sides. Even when using two wheels, these could be arranged so that the inlet sides or suction openings are directed opposite. Such an arrangement has the advantage that the axial forces occurring at least partially cancel.
  • the at least one second flow path is formed by a section of the at least one first flow path.
  • the first flow path then has a first section, in which only the liquid flowing through the first flow path experiences an increase in pressure.
  • the second inlet opens into a second section of the first flow path, in which then both the liquid which is supplied from the second input and the liquid emerging from the first section of the first flow path experience an increase in pressure. Ie. In the second flow path, both the fluid flow from the first inlet and the fluid flow from the second inlet experience an increase in pressure.
  • a liquid flow with a higher pressure level can be introduced into the impeller via the second inlet opening at a position at which the liquid in the impeller, which is supplied through the suction mouth, has already experienced a certain pressure increase.
  • this Umisselzpumpenaggregates in a mixer or as a mixer thus the mixing point of the two flows is in the impeller.
  • two liquid flows with different pre-pressure can be mixed at a mixing point with essentially the same pressure level, without the higher pressure in one of the two supplied liquid flows having to be reduced first. As a result, the energy loss can be minimized.
  • a plurality of first flow paths are formed between impeller blades of the at least one impeller and it opens into each of the first flow paths between the impeller blades at least a second inlet opening.
  • the sections of the first flow paths between the suction mouth and the second inlet openings then form the described first flow paths, through which only the liquid supplied through the first inlet is conveyed.
  • the second sections of the first flow paths downstream of the second inlet openings form with these a second flow path through which the liquid which is supplied through the second inlet is also conveyed.
  • a valve for adjusting the flow through this flow connection may be arranged at least in the flow connection between the second input and the at least one impeller, a valve for adjusting the flow through this flow connection.
  • This valve can form a mixing valve, via which the amount of liquid supplied from the second input can be regulated, for example, to be able to regulate the temperature of the mixed flow at the outlet of Ummélzpumpenaggregates.
  • the valve may preferably have an electric drive for changing the valve position, wherein the electric drive is preferably a stepping motor.
  • the valve can then be controlled by a control device, which controls the valve position, for example, as a function of temperature as a function of the temperature at the outlet side of the circulating pump unit, d. H. as a function of the temperature of the mixed flow.
  • it can also be arranged in one or both flow connections manually operated flow control valves to z. B. to be able to make a default of the flow rates.
  • the temperature sensor is preferably arranged on the output side of the first circulating pump unit, so that it detects the temperature of the mixed liquid flow flowing through the outlet of the first circulating pump unit. If the control device varies the rotational speed of the second circulating pump assembly, then the amount of liquid supplied to the second input can be changed. The same can be accomplished by adjusting a valve upstream of the second inlet of the first recirculation pump assembly. By changing the speed of the first circulating pump unit, it is also possible to change the mixing ratio when the flow and / or pressure ratio of the flows through the first and the second flow path changes depending on the speed.
  • first flow path and the second flow path can be achieved by appropriate geometrical configuration of the first flow path and the second flow path, in particular if the first and the second flow path end, for example, on different outer diameters of the impeller.
  • changes in the pressure ratio can be achieved in that the liquid is supplied to the second input with a, preferably constant, admission pressure.
  • Fig. 1 schematically shows a conventional heating circuit for a floor heating 2, ie a heating circuit according to the prior art.
  • the heat source is a boiler 4, for example, a gas boiler with an integrated circulation pump 6.
  • a further circulating pump unit 8 with an impeller 10 and an electric drive motor 12 is provided for the underfloor heating circuit 2.
  • a mixing device is provided here, which has a mixing point 14 which is located on the suction side of the impeller 10.
  • a feed line 18, via which the water or heating medium heated by the heating boiler 4 flows and at the mixing point 14 by the circulating pump unit 6, opens Pressure is injected.
  • two flow regulating valves R hot and R cold are provided in this embodiment.
  • the regulating valve R hot is arranged in the supply line 18 and the regulating valve R cold in the return line 16.
  • the valves can for example be controlled by a control device via an electric drive.
  • the regulating valves R hot and R cold can be coupled so that always opens one of the valves to change the flow and at the same time the other valve is closed by the same degree.
  • a 3-way valve may be used, which has a valve element which simultaneously closes the return line 16 by its movement and opens the supply line 18 or vice versa.
  • the circulating pump unit 6 can also supply a further heating circuit, not shown here, which is operated directly with the flow temperature generated by the boiler.
  • Both the circulating pump unit 6 and the circulating pump unit 8 may have a conventional pressure or flow control.
  • the flow regulating valves R are required for adjusting the mixing ratio and must be provided with a corresponding drive, for example a motor-driven or thermostatically actuated drive.
  • the flow regulating valves R are controlled so that a desired flow temperature for the underfloor heating 2 is achieved downstream of the mixing point 14.
  • Another disadvantage in this system is that the pressure generated by the circulating pump unit 6 must be reduced via the flow regulating valve R hot to the suction side Pressure of the impeller 10 at the mixing point 14 to achieve.
  • an energy loss occurs in the system, which can be avoided with the solution according to the invention described below.
  • Fig. 2 shows a first embodiment of the invention.
  • a boiler 4 for heating a liquid heating medium that is provided a liquid heat carrier such as water.
  • a circulating pump unit 6 is further arranged, which could also be integrated into the boiler 4, as it is based on Fig. 1 was explained.
  • a floor heating 2 or a supplementêt mecanic mobilis 2 is provided, which has a return, which is connected to one side to the input side of the boiler 4 and the other via a return line 16 to a mixing point 20th leads, at which also the flow line 18 opens.
  • the mixing or orifice point 20 is part of a mixing device 22 and further of a circulation pump assembly 24.
  • the mixing device 22 and the circulation pump unit 24 may form an integrated unit, so that the mixing device 22 is part of the circulating pump unit 24 or the circulation pump unit 24 is part of the mixing device 22 ,
  • the mixing point 20 may be as follows will be described, lie directly in the pump housing or in an impeller of Umisselzpumpenaggregates 24.
  • the circulation pump unit 24 is formed as a double pump with two impellers 26 and 28.
  • the wheels 26 and 28 are driven by a common drive motor 30.
  • the wheels 26 and 28 may be formed as separate wheels or as an integrated impeller with two blade assemblies or flow paths.
  • the first impeller 26 forms a first flow path and is in a first flow connection in the mixing device from the return line 16 to the mixing point 20.
  • the second impeller 28 forms a second flow path and is in a second flow connection between the flow line 18 and the mixing point 20.
  • Der Mixing point 20 is thus at the pressure side of the two wheels 26 and 28, that is, according to the invention, the two heating medium streams are mixed together after the pressure increase.
  • the drive motor 30 is controlled by a control device 34, which is used for speed control or speed control of the drive motor 30 and is designed so that it can change the rotational speed of the drive motor 30.
  • the control device 34 has a speed controller, in particular using a frequency converter.
  • the control device 34 may be integrated directly into the drive motor 30 or be arranged in an electronics housing directly on the drive motor and in particular on the motor housing.
  • the control device 34 is further connected to a temperature sensor 36 and communicates with a temperature sensor 36.
  • the temperature sensor 36 is located downstream of the mixing point 20 on or in the flow line 38, which connects the mixing point 20 with the floor heating 2. In this case, the temperature sensor 36 in the mixing device 22 and the circulating pump unit 24 be integrated.
  • the connection of the temperature sensor 36 to the controller 34 may be provided in any suitable manner, for example, wired or wireless.
  • a wireless connection can be realized, for example, via a radio link such as Bluetooth or W-LAN.
  • the controller 34 varies the rotational speed of the drive motor 30, whereby as described below, the mixing ratio of the heating medium streams mixed at the mixing point 20 changes, so that the temperature changes downstream of the mixing point 20.
  • This temperature is detected by the temperature sensor 36, so that the control device 34 can perform a temperature control by speed variation of the drive motor 30 to approximate the temperature value downstream of the mixing point 20 to the temperature setpoint value.
  • Fig. 13 is the delivery height H, ie the pressure applied over the rotational speed n of the drive motor 30.
  • Fig. 2 There are three examples Differential pressure values ⁇ P pre , ⁇ P hot and ⁇ P cold .
  • the differential pressure ⁇ P pre is generated by the circulating pump unit 6 and can not be influenced by the mixing device 22 in this case, so that it is in Fig. 13 is shown as a constant, ie independent of the rotational speed of the drive motor 30 form.
  • the impeller 26 of Umisselzpumpenaggregates 24 generates for the return of the underfloor heating 2 a differential pressure .DELTA.P cold and the impeller 28 generates for the flow from the supply line 18, a differential pressure .DELTA.P hot .
  • the wheels 26 and 28 are formed differently, so they have different pressure gradients, ie different speed-dependent pressure gradients.
  • the pressure curve for the impeller 28 is less steep than the pressure curve of the impeller 26. This can be achieved, for example, that the impeller 26 has a larger outer diameter.
  • the differential pressures ⁇ P pre and ⁇ P hot are added , so that the pressure waveform ⁇ P hot is shifted upward by a constant value in the graph. This ensures that the pressure curve curves .DELTA.P hot and .DELTA.P cold intersect at a point 39. Above and below the point of intersection of these curves are mixing areas 40 for the mixed liquid.
  • the output pressure of the impeller 28 is higher than that of the impeller 26, so that the output pressure of the impeller 28 acts in the flow path through the impeller 26 at the mixing point 20 as a back pressure and hydraulic resistance and in this Operating state, the flow through the first flow path through the impeller 26 is reduced and more heated heating medium is mixed in order to achieve a higher temperature in the flow 38 to the underfloor 2.
  • this pressure difference between the pressure curve curves ⁇ P cold and ⁇ P hot (the mixing region 42) is speed-dependent. D. H.
  • the hydraulic resistance, which acts in the flow path through the impeller 28 can be varied by changing the speed, so that the flow through the impeller 28 and thus the flow of heated heating medium can be changed. Even so, a change in the temperature on the output side of the mixing point 20 and thus a temperature control by changing the speed of the rotational speed n of the drive motor 30 is possible.
  • Fig. 5 shows an embodiment which is a variant of in Fig. 2 illustrated embodiment represents.
  • the two wheels 26 and 28 are formed in the form of a double impeller.
  • the impeller 26 is formed by a first blade ring and the impeller 28 by a second blade ring of the same impeller.
  • the variation of the mixing ratio at the mixing point 20 by changing the rotational speed n of the drive motor 30 takes place in the same way as with reference to FIG Fig. 3 and 13 described.
  • a flow regulating valve R hot and in the return line 16 are additionally provided upstream of the wheels 26 and 28 in the flow line 18.
  • the default setting is preferably carried out in such a way that initially the rotational speed of the drive motor 30 is set so that a sufficient flow is achieved by the bottom floor 2. Ie. it is the rotational speed of the wheels 26 and 28 initially adjusted so that a matched to the system, ie the hydraulic resistance of the system differential pressure is generated. Subsequently, the manual flow control valves R hot and R cold are adjusted so that at the given speed at the temperature sensor 36, a desired temperature setpoint value is reached.
  • This temperature setpoint value can be, for example, a temperature setpoint value which is preset by a heating curve at the current outside temperature.
  • the heating medium flow from the return line 16 experiences a first pressure increase ⁇ P1 upstream of the mixing point 52.
  • the heating medium flow from the supply line 18 experiences a pressure increase ⁇ P pre through the circulation pump unit 6. which leaves the impeller part 48, injected.
  • the orifice point 52 and the second impeller part 50 form a second flow path, through which the heating medium flow from the feed line 18 and further downstream of the mouth point 52 and the heating medium flow from the return line 16, which previously experienced in a first flow path in the impeller part 48, a pressure increase has, flow.
  • the mixed heating medium flow experiences a further pressure increase ⁇ P2.
  • Fig. 15 the pressure curves in the form of the delivery height H are plotted against the rotational speed n of the drive motor 30.
  • ⁇ P pre the constant form pressure
  • ⁇ P1 and ⁇ P2 are shown.
  • This arrangement has the advantage that the pressure ⁇ P pre , which is generated by the circulating pump unit 6, does not have to be reduced since the mixture of the two heating medium flows at a higher pressure level, namely at the level of the pressure .DELTA.P1 takes place. As a result, energy losses in the mixing device 44 are reduced.
  • the embodiment according to Fig. 6 to 9 shows an integrated circulation pump mixing device, ie a circulating pump unit with integrated mixing device or a mixing device with integrated circulation pump unit.
  • the circulating pump unit has, in a known manner, an electric drive motor 30 to which an electronics housing or terminal box 56 is attached.
  • the control device 34 is arranged in this embodiment.
  • the electric drive motor has a stator or motor housing 58, inside which the stator 60 of the drive motor 30 is arranged.
  • the stator 60 surrounds a gap pot or a can 62, which separates the stator space from a centrally located rotor space.
  • In the rotor space of the rotor 64 is arranged, which may be formed for example as a permanent magnet rotor.
  • the rotor 64 is connected via a rotor shaft 66 to the impeller 68, so that the rotor 64 rotatably drives the impeller 68 as it rotates about the rotation axis X.
  • the impeller 68 is formed in this embodiment as a double impeller and combines the wheels 26 and 28, as they are based on Fig. 2 and 5 has been described.
  • the impeller 68 has a central suction mouth 70, which opens into a first blade arrangement or a first blade ring, which forms the impeller 26. So is defined by the suction port 70 and the impeller 26, a first flow path through the impeller 68.
  • the impeller 26 is formed closed and has a front cover plate 72, which merges into a suction mouth 70 limiting collar. On the front cover plate 72, a second blade ring is arranged or formed, which forms the second impeller 28.
  • the second impeller 28 has an annular suction port 74 on the inlet side, which annularly surrounds the suction port 70.
  • the second suction port 74 forms a second inlet opening of the impeller 68.
  • Both the impeller 26 and the impeller 28 have circumferentially outlet openings, which in a pressure chamber 76 of a Pump housing 78 open.
  • a first flow connection through the pump housing 78 is defined via the suction line 82, the suction port 70, the first impeller 26, the pressure chamber 76 and the discharge port 80.
  • the pump housing 78 also has a second suction port 86, which forms a second input.
  • the second suction nozzle is connected in the interior of the pump housing 78 via a connecting channel 88 with an annular space 90 on the suction side of the impeller 68.
  • the annular space 90 surrounds a ring element 92 on the outside.
  • the ring element 92 is inserted into the suction chamber of the pump housing 78 and engages with its annular collar with the collar surrounding the suction mouth 70, so that a sealed flow connection is created from the suction channel 82 into the suction mouth 70. Externally, the ring element 92 is surrounded by the annular space 90, so that the ring element 92 separates the flow path to the suction mouth 70 from the flow path to the second suction mouth 74. Inserted into the pump housing is also an annular sealing element 94, which abuts against the inner circumference of the pump housing 78 and sealingly comes into contact with the outer periphery of the impeller 68.
  • the sealing element 94 in the outer peripheral region of the second suction mouth 74 with the impeller 68 in sealing contact so that it separates the suction region on the inlet side of the suction mouth 74 of the pressure chamber 76 in the pump housing.
  • the flow regulating valves R cold and R hot are formed as rotatable valve elements 98, which are each inserted into a cylindrical receiving space. By rotation, the valve elements 98 reach different degrees into the suction line 82 or cover the connecting channel 88, so that the free flow cross section in the first or second flow path can be changed by rotation of the corresponding valve element 98.
  • the 10 to 12 show an embodiment of the Umisselzpumpenaggregates 46 with the mixing device 44, as shown by Fig. 4 and 15 has been described.
  • the mixing device 44 and the circulation pump unit 46 also represent an integrated unit.
  • the drive motor 30 with the attached electronics housing 56 corresponds in a structure to the drive motor 30, as it is based on the Fig. 7 to 9 has been described.
  • the pump housing 78 'in its construction substantially corresponds to the above-described pump housing 78.
  • a first difference is that the pump housing 78' has no flow control valves R hot and R cold , it being understood that in this second embodiment, such flow control valves R could be provided, as described above.
  • a second difference is that the second suction port 86 'in this embodiment has an external thread.
  • the suction port 86 according to the preceding embodiment could be designed according to or the Saugstutzten 86 'could also have an internal thread.
  • the impeller part 78 is formed by the radially inner impeller part, ie in the flow direction between the suction mouth 102 and the openings 106.
  • the openings 106 face the annular space 90, so that heating medium can enter via the connecting channel 88 into these openings 106.
  • the outlet side of the openings 106 is thus in the Flow channels 108 in this embodiment, the mixing point 52 according to Fig. 4 ,
  • valves R hot or R cold may optionally be coupled to each other or be formed together as a three-way valve.
  • An electric drive of these valves could be controlled by a common control device 34, which also controls the speed of the drive motor 30.
  • the mixing ratio and thus the temperature in the flow line for underfloor heating can be regulated or controlled.
  • a larger control range can be achieved.
  • the losses can be reduced by larger valve opening degrees.
  • the speed can be increased only for a short time to mix in an increased amount of heated heating medium.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP17184776.7A 2017-08-03 2017-08-03 Groupe motopompe de circulation Withdrawn EP3438555A1 (fr)

Priority Applications (5)

Application Number Priority Date Filing Date Title
EP17184776.7A EP3438555A1 (fr) 2017-08-03 2017-08-03 Groupe motopompe de circulation
PCT/EP2018/070968 WO2019025525A1 (fr) 2017-08-03 2018-08-02 Unité de pompe de circulation
EP18745974.8A EP3662204A1 (fr) 2017-08-03 2018-08-02 Unité de pompe de circulation
US16/635,787 US11359822B2 (en) 2017-08-03 2018-08-02 Circulation pump assembly
CN201880050279.0A CN110998191B (zh) 2017-08-03 2018-08-02 循环泵机组

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP17184776.7A EP3438555A1 (fr) 2017-08-03 2017-08-03 Groupe motopompe de circulation

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EP17184776.7A Withdrawn EP3438555A1 (fr) 2017-08-03 2017-08-03 Groupe motopompe de circulation
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WO2021123155A3 (fr) * 2019-12-19 2021-08-05 Rift Ip Limited Pompe améliorée

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US12085081B1 (en) * 2023-09-23 2024-09-10 Cooper-Standard Automotive Inc. Fluid pump and valve switch

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EP2871420A1 (fr) * 2013-11-07 2015-05-13 Grundfos Holding A/S Module de pompe de circulation pour un système de chauffage et/ou de refroidissement

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EP3037669B1 (fr) * 2014-12-22 2019-07-24 Grundfos Holding A/S Système hydraulique

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DE1119485B (de) * 1959-06-06 1961-12-14 Thermo Appbau G M B H Wasserumwaelzpumpe, vorzugsweise fuer Sammelheizungsanlagen
DE2107000A1 (de) * 1971-02-13 1972-08-24 Loewe Pumpenfabrik Gmbh Kreiselpumpe, insbes. Heizungsumwälzpumpe
DE69004616T2 (de) * 1989-04-21 1994-05-26 I C F Fluidumlauf- und -verteilergerät.
DE102004059567A1 (de) * 2004-12-09 2006-06-29 Ari-Armaturen Albert Richter Gmbh & Co. Kg Steuer- oder Regeleinrichtung zum Fördern und Mischen fluider Medien in Heizungs-, Brauch- oder Trinkwasseranlagen
EP2871420A1 (fr) * 2013-11-07 2015-05-13 Grundfos Holding A/S Module de pompe de circulation pour un système de chauffage et/ou de refroidissement

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WO2021123155A3 (fr) * 2019-12-19 2021-08-05 Rift Ip Limited Pompe améliorée
GB2604554A (en) * 2019-12-19 2022-09-07 Motion Control Products Ltd Twin pump
GB2604554B (en) * 2019-12-19 2023-12-27 Motion Control Products Ltd An improved pump

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EP3662204A1 (fr) 2020-06-10
US20200340684A1 (en) 2020-10-29
CN110998191A (zh) 2020-04-10
WO2019025525A1 (fr) 2019-02-07
US11359822B2 (en) 2022-06-14
CN110998191B (zh) 2021-12-21

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