EP3717775A1 - Pompe volumétrique rotative pour transporter des substances apte à l'écoulement, rotor pour une telle pompe et procédé de transport ayant une telle pompe volumétrique - Google Patents

Pompe volumétrique rotative pour transporter des substances apte à l'écoulement, rotor pour une telle pompe et procédé de transport ayant une telle pompe volumétrique

Info

Publication number
EP3717775A1
EP3717775A1 EP18822262.4A EP18822262A EP3717775A1 EP 3717775 A1 EP3717775 A1 EP 3717775A1 EP 18822262 A EP18822262 A EP 18822262A EP 3717775 A1 EP3717775 A1 EP 3717775A1
Authority
EP
European Patent Office
Prior art keywords
impeller
channel
positive displacement
displacement pump
rotation
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Withdrawn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
EP18822262.4A
Other languages
German (de)
English (en)
Inventor
Gottfried Kowalik
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.)
Individual
Original Assignee
Individual
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 Individual filed Critical Individual
Publication of EP3717775A1 publication Critical patent/EP3717775A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C11/00—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations
    • F04C11/001—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations of similar working principle
    • C—CHEMISTRY; METALLURGY
    • C25—ELECTROLYTIC OR ELECTROPHORETIC PROCESSES; APPARATUS THEREFOR
    • C25B—ELECTROLYTIC OR ELECTROPHORETIC PROCESSES FOR THE PRODUCTION OF COMPOUNDS OR NON-METALS; APPARATUS THEREFOR
    • C25B1/00—Electrolytic production of inorganic compounds or non-metals
    • C25B1/01—Products
    • C25B1/02—Hydrogen or oxygen
    • C25B1/04—Hydrogen or oxygen by electrolysis of water
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/08—Rotary pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/08—Rotary pistons
    • F01C21/0809—Construction of vanes or vane holders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C13/00—Adaptations of machines or pumps for special use, e.g. for extremely high pressures
    • F04C13/001—Pumps for particular liquids
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0003—Sealing arrangements in rotary-piston machines or pumps
    • F04C15/0007—Radial sealings for working fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/22—Rotary-piston machines or pumps of internal-axis type with equidirectional movement of co-operating members at the points of engagement, or with one of the co-operating members being stationary, the inner member having more teeth or tooth-equivalents than the outer member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C2/34—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
    • F04C2/356—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01M—PROCESSES OR MEANS, e.g. BATTERIES, FOR THE DIRECT CONVERSION OF CHEMICAL ENERGY INTO ELECTRICAL ENERGY
    • H01M10/00—Secondary cells; Manufacture thereof
    • H01M10/42—Methods or arrangements for servicing or maintenance of secondary cells or secondary half-cells
    • H01M10/46—Accumulators structurally combined with charging apparatus
    • H01M10/465—Accumulators structurally combined with charging apparatus with solar battery as charging system
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01M—PROCESSES OR MEANS, e.g. BATTERIES, FOR THE DIRECT CONVERSION OF CHEMICAL ENERGY INTO ELECTRICAL ENERGY
    • H01M16/00—Structural combinations of different types of electrochemical generators
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01M—PROCESSES OR MEANS, e.g. BATTERIES, FOR THE DIRECT CONVERSION OF CHEMICAL ENERGY INTO ELECTRICAL ENERGY
    • H01M16/00—Structural combinations of different types of electrochemical generators
    • H01M16/003—Structural combinations of different types of electrochemical generators of fuel cells with other electrochemical devices, e.g. capacitors, electrolysers
    • H01M16/006—Structural combinations of different types of electrochemical generators of fuel cells with other electrochemical devices, e.g. capacitors, electrolysers of fuel cells with rechargeable batteries
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01M—PROCESSES OR MEANS, e.g. BATTERIES, FOR THE DIRECT CONVERSION OF CHEMICAL ENERGY INTO ELECTRICAL ENERGY
    • H01M8/00—Fuel cells; Manufacture thereof
    • H01M8/04—Auxiliary arrangements, e.g. for control of pressure or for circulation of fluids
    • H01M8/04007—Auxiliary arrangements, e.g. for control of pressure or for circulation of fluids related to heat exchange
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01M—PROCESSES OR MEANS, e.g. BATTERIES, FOR THE DIRECT CONVERSION OF CHEMICAL ENERGY INTO ELECTRICAL ENERGY
    • H01M8/00—Fuel cells; Manufacture thereof
    • H01M8/04—Auxiliary arrangements, e.g. for control of pressure or for circulation of fluids
    • H01M8/04082—Arrangements for control of reactant parameters, e.g. pressure or concentration
    • H01M8/04089—Arrangements for control of reactant parameters, e.g. pressure or concentration of gaseous reactants
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01M—PROCESSES OR MEANS, e.g. BATTERIES, FOR THE DIRECT CONVERSION OF CHEMICAL ENERGY INTO ELECTRICAL ENERGY
    • H01M8/00—Fuel cells; Manufacture thereof
    • H01M8/06—Combination of fuel cells with means for production of reactants or for treatment of residues
    • H01M8/0606—Combination of fuel cells with means for production of reactants or for treatment of residues with means for production of gaseous reactants
    • H01M8/0656—Combination of fuel cells with means for production of reactants or for treatment of residues with means for production of gaseous reactants by electrochemical means
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02J—CIRCUIT ARRANGEMENTS OR SYSTEMS FOR SUPPLYING OR DISTRIBUTING ELECTRIC POWER; SYSTEMS FOR STORING ELECTRIC ENERGY
    • H02J1/00—Circuit arrangements for dc mains or dc distribution networks
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02J—CIRCUIT ARRANGEMENTS OR SYSTEMS FOR SUPPLYING OR DISTRIBUTING ELECTRIC POWER; SYSTEMS FOR STORING ELECTRIC ENERGY
    • H02J3/00—Circuit arrangements for ac mains or ac distribution networks
    • H02J3/38—Arrangements for parallely feeding a single network by two or more generators, converters or transformers
    • H02J3/381—Dispersed generators
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02J—CIRCUIT ARRANGEMENTS OR SYSTEMS FOR SUPPLYING OR DISTRIBUTING ELECTRIC POWER; SYSTEMS FOR STORING ELECTRIC ENERGY
    • H02J7/00—Circuit arrangements for charging or depolarising batteries or for supplying loads from batteries
    • H02J7/34—Parallel operation in networks using both storage and other dc sources, e.g. providing buffering
    • H02J7/35—Parallel operation in networks using both storage and other dc sources, e.g. providing buffering with light sensitive cells
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02S—GENERATION OF ELECTRIC POWER BY CONVERSION OF INFRARED RADIATION, VISIBLE LIGHT OR ULTRAVIOLET LIGHT, e.g. USING PHOTOVOLTAIC [PV] MODULES
    • H02S10/00—PV power plants; Combinations of PV energy systems with other systems for the generation of electric power
    • H02S10/10—PV power plants; Combinations of PV energy systems with other systems for the generation of electric power including a supplementary source of electric power, e.g. hybrid diesel-PV energy systems
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02S—GENERATION OF ELECTRIC POWER BY CONVERSION OF INFRARED RADIATION, VISIBLE LIGHT OR ULTRAVIOLET LIGHT, e.g. USING PHOTOVOLTAIC [PV] MODULES
    • H02S10/00—PV power plants; Combinations of PV energy systems with other systems for the generation of electric power
    • H02S10/20—Systems characterised by their energy storage means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C2/40—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C2/08 or F04C2/22 and having a hinged member
    • F04C2/44—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C2/08 or F04C2/22 and having a hinged member with vanes hinged to the inner member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C2/40—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C2/08 or F04C2/22 and having a hinged member
    • F04C2/46—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C2/08 or F04C2/22 and having a hinged member with vanes hinged to the outer member
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01M—PROCESSES OR MEANS, e.g. BATTERIES, FOR THE DIRECT CONVERSION OF CHEMICAL ENERGY INTO ELECTRICAL ENERGY
    • H01M2220/00—Batteries for particular applications
    • H01M2220/10—Batteries in stationary systems, e.g. emergency power source in plant
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01M—PROCESSES OR MEANS, e.g. BATTERIES, FOR THE DIRECT CONVERSION OF CHEMICAL ENERGY INTO ELECTRICAL ENERGY
    • H01M2250/00—Fuel cells for particular applications; Specific features of fuel cell system
    • H01M2250/10—Fuel cells in stationary systems, e.g. emergency power source in plant
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01M—PROCESSES OR MEANS, e.g. BATTERIES, FOR THE DIRECT CONVERSION OF CHEMICAL ENERGY INTO ELECTRICAL ENERGY
    • H01M2250/00—Fuel cells for particular applications; Specific features of fuel cell system
    • H01M2250/40—Combination of fuel cells with other energy production systems
    • H01M2250/402—Combination of fuel cell with other electric generators
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02J—CIRCUIT ARRANGEMENTS OR SYSTEMS FOR SUPPLYING OR DISTRIBUTING ELECTRIC POWER; SYSTEMS FOR STORING ELECTRIC ENERGY
    • H02J2300/00—Systems for supplying or distributing electric power characterised by decentralized, dispersed, or local generation
    • H02J2300/20—The dispersed energy generation being of renewable origin
    • H02J2300/22—The renewable source being solar energy
    • H02J2300/24—The renewable source being solar energy of photovoltaic origin
    • 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
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B90/00—Enabling technologies or technologies with a potential or indirect contribution to GHG emissions mitigation
    • Y02B90/10—Applications of fuel cells in buildings
    • 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
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E10/00—Energy generation through renewable energy sources
    • Y02E10/50—Photovoltaic [PV] energy
    • Y02E10/56—Power conversion systems, e.g. maximum power point trackers
    • 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
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E60/00—Enabling technologies; Technologies with a potential or indirect contribution to GHG emissions mitigation
    • Y02E60/10—Energy storage using batteries
    • 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
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E60/00—Enabling technologies; Technologies with a potential or indirect contribution to GHG emissions mitigation
    • Y02E60/30—Hydrogen technology
    • Y02E60/36—Hydrogen production from non-carbon containing sources, e.g. by water electrolysis
    • 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
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E60/00—Enabling technologies; Technologies with a potential or indirect contribution to GHG emissions mitigation
    • Y02E60/30—Hydrogen technology
    • Y02E60/50—Fuel cells
    • 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
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E70/00—Other energy conversion or management systems reducing GHG emissions
    • Y02E70/30—Systems combining energy storage with energy generation of non-fossil origin

Definitions

  • Rotary positive displacement pump for conveying flowable materials, impeller for such and method of conveying with such
  • the invention relates to a rotary positive displacement pump for conveying flowable materials, an impeller for such and a method for conveying with such a positive displacement pump.
  • the flowable substances may also be those with low to high viscosity and in each case lumpy proportions.
  • the fields of application of such displacement pumps are the chemical, pharmaceutical and food-producing and. -processing industry.
  • To classify and delineate the rotating positive displacement pump according to the invention which has no model in terms of its basic principle of conveying, it can serve to indicate that in a housing a single rotary impeller and a single, separating the suction side from the pressure side, movable separating element having.
  • Positive displacement pumps for conveying flowable substances without lumpy portions or with such admixtures can be divided into those in which a conveying member carries out a reciprocating or a rotating movement.
  • Well-known membrane pumps or piston pumps belong to the first group; They require, among other check valves in the suction and pressure side and they have a pulsating promotion.
  • the second group, the rotating positive displacement pumps also includes well-known eccentric shaft pumps, rotary lobe pumps, screw pumps, gear pumps and peristaltic pumps.
  • Eccentric shaft pumps are susceptible to wear at high temperatures and complex in construction.
  • Rotary pumps are characterized by a slight pulsation of the flow; they require two mechanical seal assemblies. Screw pumps are complex in construction and also require two mechanical seal assemblies.
  • Gear pumps are only suitable for homogeneous substances without lumpy and / or abrasive admixtures; they require two mechanical seal assemblies.
  • Peristaltic pumps are structurally rather complex, they produce a slightly pulsating flow and are characterized by a more or less large hose wear.
  • MasoSine pump a rotary displacement pump which is known in the prior art as the so-called MasoSine pump (see the following link: http://www.watson-marlow.com/Documents/knowledqe-hub / Brochures / DE% 20-% 20German / MasoSine% 20EN / b- masosine-certa-DE-03.pdf). It is characterized inter alia by the fact that it has a single rotatable impeller in a housing and a single, the suction from the pressure side separating, movable separating element.
  • a circumferentially closed, wave-shaped cam he stretches.
  • the wave-shaped deflections of the cam plate are oriented axially to the Ro torachse, wherein the wave crests of one side of the cam slide on one end side of the cylindrical housing and those on the other side of the cam on the other end sealingly.
  • the schie berartige, plate-shaped separating element which is axially displaceably mounted in the lateral surface of the housing and engages on both sides in the respective end face of the housing, the cam comprises on both sides except for the lateral surface of the rotor.
  • the separating element Due to the rotational movement of the rotor and thus of the cam disc, the separating element experiences an axial reciprocating movement, which ensures a separation of the suction from the pressure side of the positive displacement pump.
  • This positive displacement pump works almost without pulsation.
  • the separator is subject to high wear due to its continuing relative movements relative to the housing, the lateral surface of the rotor and all edge surfaces of the curves encompassed by it.
  • a rotary positive displacement pump of the aforementioned type is also disclosed in DE 10 2015 116 769 A1.
  • the displacement pump described therein has a rotor rotatable about an axis of rotation, which rotor comprises a rotor hub and a shaft-shaped rotor collar extending from the rotor hub in the radial direction.
  • a pump housing forms with the rotor a pump channel, which depends on an optionally adjustable operating direction of the Pump connects a first inlet / outlet space with a second inlet / outlet space.
  • a blocking device which is arranged between the first inlet / outlet space and the second inlet / outlet space, has a blocking element which blocks the pump channel in the axial direction on both sides of the rotor collar and ensures a return flow of fluid to be pumped from the respective outlet channel. prevented to the respective inlet space.
  • the locking device has a first seat for the blocking element on the side of the first inlet / outlet space, on which the blocking element in a first operating direction for pumping from the first inlet / outlet space to the second inlet / Auslraumraum with a first contact surface ,
  • the locking device further has a second seat for the locking element on the side of the second inlet / outlet space at which the locking element abuts in a second operating direction for pumping from the second inlet / outlet space to the first inlet / outlet space with a second contact surface.
  • the distance between the first and the second seat is greater than the distance between the first and the second contact surface, each measured in the circumferential direction.
  • the publication WO 2005/066 498 A1 is based on a rotary positive displacement pump, as above in its basic structure with a view of a pump housing, a rotor, a rotor hub with a wavy umlau fenden rotor collar and the rotor collar embracing locking element with reference to the DE 10 2015 116 769 A1 was sketched.
  • the rotor collar sits at least in the circumferential direction sections planar outer surfaces on at least one of its two opposite outer sides.
  • the invention is based on a consisting of a housing and a lid body cylindrical pump housing in which rotatably and motor driven drivable an impeller with a cylindrical outer contour sealing on measure takes place.
  • the inventive idea and its concrete implementation consist in that a circumferential, groove-shaped impeller passage is provided, which engages axially at least in one of the end faces of the impeller and concentric with the axis of rotation.
  • the impeller channel may, based on ge by the axis of rotation rising levels, have a variety of cross-sectional shapes. All that is necessary is that the groove flanks of the impeller channel in the form of a uniformly wave-shaped, continuously curved radially outer channel boundary and just such uniformly wave-shaped, continuously curved radially inner channel boundary formed and, seen in the radial direction and in each plane perpendicular to the axis of rotation, are equidistant to each other and each end in a channel base.
  • annular guide ring which is fixedly connected to the lid or the housing body, engages in the impeller and extends to the channel base.
  • the so by the Guide ring divided in its radial extent range impeller channel forms in the two-sided interaction with the guide ring between adjacent outer wave crests an outer chamber volume and between adjacent held ren wave crests an inner chamber volume.
  • outer and inner chamber volumes are in the direction of rotation or circumferential Rich tion of the impeller migrating suction and pressure chambers and a total Ar beitsraum the impeller.
  • the working space is provided with a suction and a pressure opening, the channel base surface opposite housing in the pump are arranged. Their distance from one another is determined in an angle division defined by adjacent outer or inner wave crests, which is related to the axis of rotation.
  • the annular guide ring is not completely self-contained, but it is formed on the one hand in the area between the suction and the pressure opening and up to the channel base out.
  • Another essential feature of the invention is a separating element which is arranged between the suction and the pressure opening in the recessed there guide ring and in the impeller and the lid or on the housing body on all sides sealingly guided and in the direction of rotation of the impeller supported the guide ring.
  • This separator causes the necessary blockage between the suction and pressure side of the positive displacement pump by being adapted to the passage cross section of the impeller channel in cooperation with the front side of the cover or housing body and there throttle-sealed the wavy movements of the outer and inner channel boundary during rotation of the impeller responding to excursions.
  • An advantageous embodiment of the positive displacement pump provides that at least three inner and three outer or maximum so much inner and corresponding outer outer crests, the number of which is defined by a minimum angular pitch between suction and pressure opening, are provided.
  • a wave crest which forms a geometrically shaped line, is formed at the summit of the outer and the inner wavy channel boundary, the convex bulge.
  • the minimum angular pitch results from a foundedab stood between suction and pressure opening in the working space, ie in the peripheral region of the impeller, wherein the suction and pressure port and thus from this ausmündenden suction and discharge nozzles are not allowed to effetdrin gene each other, but a practicable Minimum distance from each other must have. It has proved to be useful and advantageous when five to seven outer and corresponding to five to seven inner wave crests, preferably, six outer and six inner, are provided.
  • the construction of the positive displacement pump is simplified significantly when the outer and inner channel boundaries are parallel to each other and parallel to the axis of rotation of the impeller.
  • a related rectangular impeller channel which engages perpendicularly in the end face of the cylindrical impeller, can be conceivably simple, e.g. machining, manufacture.
  • this embodiment with a cylindrical milling tool which follows the defini th wavy course of the impeller channel, are herge in the simplest way.
  • the complementary to the impeller passage guide ring with its inevitably rectangular cross-section is an equally simple ago deliverable rotary member; It is also extremely easy to insert into the impeller channel and position it there.
  • Another embodiment of the impeller channel provides that the outer and the inner channel boundary to the channel base surface taper towards each other, the former being inclined at a first angle and the other at a second angle in each case with respect to the axis of rotation of the impeller.
  • the guide ring is formed in its respective engagement region with the impeller passage complementary to the outer and the inner channel boundary.
  • the storage and sealing of the pump shaft designed according to another embodiment is very simple, because the impeller requires only a flying storage. It is provided that a pump shaft connected to the impeller on the side of the housing body led out of this and sealed with respect to the housing body or a terminal housing formed thereon with a first mechanical seal arrangement.
  • the positive displacement pump can be mounted on any commercially available geared motor with hollow shaft or with a separate bearing block.
  • the impeller in the region between the pump shaft and the working chamber with at least two of the impeller the one to the other end face penetrating, over the circumference of the impeller uniformly arranged flushing holes is provided.
  • These flushing bores are fluidly connected to a flushing chamber which radially surrounds the first mechanical seal arrangement on the outside and which is formed in the housing body or the connection housing formed thereon.
  • the access to the rinsing chamber is improved when the flushing holes in a recess in the impeller, which is concentric in the first Gleitringdingungsanowski angle facing end face of the impeller, open, wherein an annular recess or a radially inwardly continuous recess is executed.
  • the respective recess is fluidly connected to the washing chamber.
  • the invention proposes two different embodiments of the separating element. Thereafter, a first separating element, which is designed as a pivotable about its one end lever-shaped body, on the one hand at this end in one of Mouth opening adjacent supporting Leitringende the guide ring mounted radially and stationary in the direction of rotation. On the other hand, the separating element, with its radially movable end portion following the moving in the direction of rotation of the impeller wave-shaped impeller passage, guided by a pressure opening adjacent the guide ring end of the guide ring radially movable.
  • a second embodiment provides in this regard, a second separating element, which is in the form of the impeller channel and its boundary by the housing or the lid body circumferentially sealing pig, on the one hand experiences its support at one of the infant opening adjacent supporting Leitringende the guide ring and on the other hand, a degree of freedom of movement has to one of the pressure opening adjacent Leitringende the guide ring, whereby the second separating element is thus loosely or quasi free-floating positioned.
  • a third embodiment provides for a third separating element, which is likewise designed in the form of a scraper which circumferentially seals the impeller channel and the casing body or cover body.
  • This third separating element undergoes its support, in contrast to the second separating element, on the one hand at one end of a supporting joint part, which in turn is supported at its other end adjacent to one of the infant opening supporting Leitringende the guide ring, and on the other hand, it has a BEWE freedom of movement to one of the pressure port adjacent guide ring end of the guide ring.
  • the positive displacement pump according to the invention can be performed doubly in a very simple manner, in addition to an end face in the other end of the impeller, which thus becomes a second impeller, another working space is formed, all the necessary features of the already formed on one end face Working space has. It is manufacturing technically and hydraulically useful if the two working spaces are dimensioned to each other and identical in position. The degree of uniformity of the promotion and in particular the concentricity of the positive displacement pump are improved when the outer and the inner Kanalbegren tion ge in both end faces of the second impeller by half the angular pitch ge offset from each other.
  • the double-flow design of the positive displacement pump allows by a simple variation of the outside piping of the suction and discharge nozzles both a doubling of the delivery volume (parallel connection) and an increase of the final pressure by a two-stage flow control (series connection). This is achieved in that the two working spaces of the second impeller via its associated suction and pressure port connected to the one end face with egg nem associated suction nozzle and an associated discharge nozzle and on the other end face with an associated second suction nozzle and an associated second discharge nozzle are connected in parallel or in series with each other.
  • the invention further relates to an impeller for a rotary positive displacement pump for conveying flowable materials, the rotatably and motor driven drivable in a pump housing received in the region of at least ei nen working space against the pump housing sealingly receiving and the positive displacement pump, as described above, formed is.
  • the inventive basic idea and its concrete implementation consist in that the impeller has a cylindrical basic shape and that a circumferential, groove-shaped impeller passage is provided, which engages axially at least in one of the end faces of the impeller and concentric with the axis of rotation.
  • the impeller passage can, based on passing through the rotation axis levels, un ferent different cross-sectional shapes. All that is necessary is that the groove flanks of the impeller channel are shaped in the form of a uniform wave-shaped, continuously curved, radially outer channel boundary and a uniform, uniform, wave-shaped, continuously curved radially inner channel boundary and perpendicular to the axis of rotation in the radial direction and in each plane.
  • Such typical lateral surfaces may be the lateral surface of a cylinder, a conical shell or a rotationally symmetrical body whose peripheral contour is generated by rotation of a concave or convex curved line to the axis of rotation, wherein the respective peripheral contour terminates in the channel base.
  • the invention also proposes that the outer and the inner channel boundary each to the open NEN side of the impeller out point in the form of a streamlined, preferably convex rounding or an inlet / Ausströmfase expand.
  • a stall of the material to be conveyed between the guide ring and the impeller passage in the region of the respective outer and inner wave comb is favored and it is also avoided pinching small lumpy portions of the substance to be conveyed at these locations when, as the invention provides, Oriented in the direction of rotation of the impeller, immediately before the respective outer wave crest an outer stall groove and immediacy bar in front of the respective inner wave crest, an inner stall groove are provided.
  • the invention proposes that, as an alternative to penetrating openings and depending on the material to be conveyed, more than one freewheel recess in a lateral surface of the impeller are provided. These are trough-shaped, distributed over the order catch the lateral surface and arranged spaced from one another and each of the impeller channel receiving end face of the impeller. By this configuration, the leadership of each com menden for separating element is not affected.
  • the invention proposes that the at least one impeller, based on the Rotati onsachse, so positioned radially is that the outer channel boundary with their respective radially outermost extent the lateral surface of the first or the second impeller to form a respective penetration opening penetrates and thereby opens the respective impeller passage at these locations to the outside of the outer surface of the impeller in a narrow range.
  • flushing grooves of different designs and / or undercuts can be provided on the impeller.
  • the invention further proposes a method for conveying flowable substances with a positive displacement pump and with an impeller for this positive displacement pump of the type described above.
  • This method is inventively characterized in that the substance in space-fixed radially outer and radially inner chamber volumes within an impeller, i. formed in the impeller, spatially invariable cavities, in the direction of rotation of the impeller and in each case regular sequence, is separated paragraph by paragraph.
  • the outer chamber volumes are radially inwardly of one, based on the Rotationsach se of the impeller, rotationally symmetrical outer surface of a fixed guide ring and the inner chamber volumes are radially outside of a be attracted to the axis of rotation, rotationally symmetrical inner surface of the guide ring bounded.
  • the supply of the substance into the outer and inner chamber volumes takes place from a stationary, common mammalian opening and the removal from the corresponding chamber volumes takes place via a stationary, common pressure opening.
  • the demarcated in the outer and inner chamber volumes substance is moved by the impeller in the direction of rotation opposite and on the outer and the inner ren surface area of the suction to the pressure opening.
  • the outer and inner chamber volumes thus represent traveling in the direction of rotation cavities, which act as suction and pressure chambers.
  • the outer chamber volumes are offset from the inner chamber volumes offset by half an angular pitch, wherein the angular separation results from the uniform distribution over the circumference of the impeller arrangement of the outer or inner chamber volumes.
  • the staggered arrangement results in a pulsation-free flow.
  • Figure 1 is an inside view of a single-flow rotary positive displacement oh ne her cover part in the direction of its axis of rotation of the Deckelkör perseite seen from;
  • FIG. 1 a shows a meridian section through the positive displacement pump according to FIG. 1
  • FIG. 1b shows a meridian section through the positive displacement pump according to FIG. 1 in FIG.
  • FIG. 1c shows a meridian section according to FIG. 1a in the region of an impeller channel which has a geometry which is opposite to the embodiment according to FIG. 1a;
  • FIG. 2a-2c show an interior view of the positive displacement pump according to FIG. 1 in the region of a quadrant of the pump housing having a mammalian opening in three different positions of the rotor wheel;
  • FIG. 3a-3c an interior view of the positive displacement pump according to Figure 1 in the region of a pressure port having a quadrant of the Pumpenge housing in three the positions of the impeller according to the
  • Figure 4 is a view of the rotary positive displacement pump according to Figure 1 on ih ren lid body in the direction of its axis of rotation with the representation of significant hidden inner contours;
  • FIG. 4 a shows a meridian section through the positive displacement pump according to FIG. 1
  • FIG. 5 is a perspective view of an interior of the Verdrängerpum PE according to Figure 1 seen from the removed lid body, wherein the respective flange of the lid body arranged suction and discharge nozzle has remained in the illustration;
  • Figure 6a in view of a section of the positive displacement pump according to
  • FIG. 1 in the region of a first separating element
  • Figure 6b in view of a section of the positive displacement pump according to
  • FIG. 1 in the region of a second separating element
  • FIG. 7 shows the impeller corresponding to one marked "Z" in FIG. 7b
  • FIG. 7a shows a meridian section through the impeller corresponding to a in FIG
  • FIG. 7b in perspective view of the impeller according to Figure 7;
  • Figure 8 is a view of a double-flow rotary positive displacement pump on her
  • Figure 8a shows a meridian section through the double-flow positive displacement pump according to a marked in Figure 8 with "D-D" cutting path;
  • Figure 9 in cross-section an inside view of a single-flow rotary Ver pump without their cover part in the direction of its axis of rotation seen from the lid body side, with three modifications to the embodiment of Figure 1 are provided;
  • FIG. 9b shows an enlarged view of a marked "G" in FIG.
  • Figure 9c in an enlarged view a section of a meridian section through the positive displacement pump according to Figure 9 according to egg nem in Figure 9 with "E-E" marked cutting path;
  • FIG. 10 is a perspective view of the positive displacement pump according to FIG. 9; Figure 10a in an enlarged view one in Figure 10 marked "H"
  • FIG. 10b shows an enlarged illustration of an "I" marked in FIG
  • a rotary positive displacement pump 100 for conveying flowable substances P (FIG. 5) has a cylindrical pump housing 2 consisting of a housing body 4 and a cover body 6, in which it can be driven to rotate and motor driven an impeller 30 with a cylindrical outer contour sealingly receiving.
  • the groove flanks of the impeller channel 32 are in the form of a uniform wave-shaped, continuously curved radially outer channel boundary 34 and a sanctionl Chen uniformly wavy, continuously curved radially inner Kanalbegren tion 36 formed and they are perpendicular to the axis of rotation in the radial direction and in each plane R, equidistant to each other and each end in a channel base 38 ( Figures 1b, 4a).
  • An annular guide ring 50 which is fixedly connected to the lid body 6 or the housing body 4, engages the impeller passage 32 and extends to the channel base 38, wherein, seen in the radial direction, all outer wave crests WKa the outer channel boundary 34 and all inner waves combs WKi the inner channel boundary 36 ( Figures 1, 5) are each brought on their ge entire extension length to the guide ring 50.
  • the impeller channel 32 forms in mutual cooperation with the guide ring 50 between adjacent outer wave crests WKa an outer chamber volume KVa and between adjacent inner wave crests WKi an inner chamber volume KVi from, wherein the provided outer and inner chamber volumes KVa, KVi in the direction of rotation n of Impeller 30 migratory suction and pressure chambers and in total a working space AR of the impeller 30 represent.
  • FIG. 1 one of these chamber volumes KVa, KVi is shown hatched.
  • Under the outer wave crest WKa is the respective radially highest elevation of the wave-shaped, radially outer channel boundary 34, formed on a respective radially inwardly to the outside of the guide ring 50 extending outer displacer 34a to understand.
  • Under the inner wave crest WKi is the respective radial highest elevation of the wave-shaped, radially inner channel boundary 36, formed on a respective radially outwardly to the inside of the guide ring 50 extending inner displacer 36a to understand (outer displacer 34a is hatched in Figure 2a and shown in perspective in FIG. 5).
  • the outer and inner wave crests WKa, WKi are in each case over their entire axial extension length in the form of a line contact on the guide ring 50.
  • the working space AR has a suction 20 and a pressure port 22, which are arranged opposite the channel base 38 in the pump housing 2 and in an angle defined by adjacent outer or inner wave crests WKa, WKi angle division w3, which is based on the axis of rotation R, from each other beab - are standing (Fig. 1).
  • the mammal opening 20 opens into a suction port 20a and the pressure port 22 opens into a discharge port 22a.
  • the guide ring 50 is formed on the one hand in the region between the suction and the pressure opening 20, 22 and to the channel base 38 and the other in the crossing region with the outlet region of the suction 20 and with the inlet region of the pressure port 22 interrupted ( Figures 1, 4 , 5).
  • a first or a second separating element 60, 70 (FIGS. 6a, 6b, 1a and 1, 4, 4a, 5) is provided which is arranged between the suction and the pressure openings 20, 22 and in the impeller channel 32 and on the cover 6 or on the housing body 4 is guided sealingly on all sides (Figure 8a) and is supported in the direction of rotation n of the impeller 30 on the guide ring 50.
  • a second preferred embodiment of the impeller channel 32 which in addition to the advantages of the first embodiment described above allows a SET ment of the sliding and throttle gaps, characterized by ( Figure 1c in conjunction with Figure 1), that the outer and the inner channel boundary 34, 36 taper towards the channel base 38 towards each other, the former being inclined by a first angle w1 and the others by a second angle w2 each with respect to the axis of rotation R of the impeller 30, and that the guide ring 50 in its respective engagement region with the impeller passage 32 complementary to the outer and inner channel boundary 34, 36 is formed.
  • the relevant construction is simplified when the first and second angles w1, w2 are the same.
  • the impeller 30 is in the area between the pump shaft 16 and the working space AR with at least two impeller 30 from the one to the other end face penetrating, preferably evenly distributed over the circumference of the impeller 30 arranged flushing holes 42 provided ( Figures 7, 7a, 7b, 1, 5).
  • the Spellerboh stanchions 42 are fluidly connected to a first outer seal ring 12 radially outward annular sealing rinse chamber 46 which is formed in the housing body 4 or formed on this terminal housing 4a, fluidly connected (Figure 4a).
  • the flushing holes 42 open into a recess 44, 44 * in the impeller 30, which is concentric in the first Gleitringdingungsan angel 12 facing end face of the impeller 30.
  • the recess 44, 44 * is either an annular recess 44 ( Figure 4a) or a radially inwardly continuous recess 44 * ( Figure 8a).
  • the respective recess 44, 44 * is fluidly connected to the washing chamber 46.
  • the drive side is followed by a lantern 8 with a lantern housing 8c.
  • the lamp housing 8c can on the one hand be connected to a drive-side connection flange 8a with a commercially available geared motor with a hollow shaft or a bearing block, and on the other hand via a pump-housing-side connection flange 8b to the housing body 4 or the connection housing 4a connected ver ( Figure 4a).
  • At least two lantern housing bores 8d distributed over the circumference of the lantern housing 8c provide for the removal of leaking or rinsing liquid and access to the flushing connections to the flushing housing 10.
  • the housing body 4 or its connection housing 4a is followed by a flushing housing 10 within the lantern housing 8c on, which receives a second mechanical seal assembly 14 and which is equipped to flush the latter with rinsing connections, not shown.
  • a first separator 60 is provided ( Figures 6a, 1, 1a, 4, 4a, 5), on the one hand in one of the infant opening 20 adjacent supporting guide end 50a of the guide ring 50 radially and in Directed direction of rotation n and on the other hand by a pressure opening 22 adjacent the guide ring end 50b of the guide ring 50 is guided radially movable.
  • a second separating element 70 is provided in the working space AR of the positive displacement pump 100 (FIG.
  • the single-flow positive displacement pump 100 according to the invention can be expanded in a very simple way to the double-flow positive displacement pump 200 (FIGS. 8, 8a) by forming, in addition to one end face in the other end face of a then second impeller 30 *, a further working space AR which contains all the features required for this purpose of the already formed on one end side working space AR and the impeller channel 32 has.
  • the design of the double-flow displacement pump 200 is simplified significantly if the two working spaces AR are designed to be identical in terms of dimension and position.
  • the uniformity of the rotational movement and the flow rate are optimized when the outer and inner channel boundary 34, 36 in both end sides of the second impeller 30 * are arranged offset by half the angular pitch w3 against each other.
  • a double flow 2P (not blackened arrows in FIG. 8) or an approaching doubling of the final pressure of the delivery flow P (blackened arrows in FIG. 8) are easily achieved with the double-flow positive displacement pump 200 by virtue of the two working spaces AR of the second impeller 30 * via their associated suction and pressure port 20, 22, which are connected on the one end face with the associated suction port 20a and the associated discharge port 22a and on the other end side with an associated second suction port 20a * and an associated second discharge port 22a *, in parallel or are connected in series with each other ( Figures 8, 8a).
  • An impeller 30 for the above-described rotary single-flow positive displacement pump 100 (FIGS. 7, 7a, 7b) or also after modification in the form of the second impeller 30 * for the double-flow positive displacement pump 200 (FIGS. 8, 8a), in each case for conveying flowable materials, has one cylindrical basic shape.
  • the impeller 30 of the circumferential, groove-shaped impeller passage 32 is provided which engages in one of the end faces of the impeller 30 and concentric with the axis of rotation R axially.
  • the groove flanks of the impeller channel 32 are in the form of uniformly wel lenförmigen, continuously curved, radially outer channel boundary 34 and the same uniformly wave-shaped, continuously curved radially inner channel boundary 36 is formed.
  • Under the outer wave crest WKa is the respective radial highest elevation of the wave-shaped, radially outer channel boundary 34 formed on the respective respective radially inwardly to the outer surface Ma extending outer displacer 34a to understand.
  • Under the inner wave crest WKi is the respective radially highest elevation of the wave-shaped, radially inner channel boundary 36, formed on the respective radially outwardly to the inner envelope surface Mi extending inner displacer 36a to understand.
  • the outer and inner wave crests WKa, WKi each form a line contact with the outer and inner circumferential surfaces Ma, Mi over their entire axial extension length.
  • the at least one impeller channel 32 is, with respect to the axis of rotation R, the radially positioned manner that the outer channel boundary 34 with their respective radial outermost extent the lateral surface of the impeller 30, 30 * penetrates to form a respective penetration opening 34b and thereby the running wheel channel 32) at these points to the outside of the lateral surface of the impeller 30, 30 * in a narrow range opens (Figure 7b).
  • This embodiment serves to avoid deposits between the impeller 30, 30 * and the cover or the housing body 6, 4th
  • FIGS 9 and 9a show a third separator 80, which is formed in the form of a wheel channel 32 and its boundary by the housing 4 or the lid body 6 circumferentially sealing pig.
  • the third Trennele element 80 learns on the one hand on the side of the unillustrated infant opening 20 (see, eg, Figure 1) its support at one end of a supporting joint part 90, the ten at its other end to one of the infant opening 20 supporting end of the guide 50a of the guide ring 50th supported.
  • the third separating member 80 has a degree of freedom of movement to one of the pressure port 22, not shown, (see, for example, Fig. 1) adjacent the nozzle 50b of the nozzle 50.
  • Figures 9, 9a, 10, 10a, 10b show outer and inner stall grooves 30a, 30b.
  • the outer stall groove 30a is oriented in the direction of rotation n of the Laufra 30, immediately before the respective outer wave crest WKa before seen.
  • the inner stall groove 30 b is provided immediately before the respective inner Wel comb WKi.
  • the outer and inner channel boundary 34, 36 each extend to the fenen side of the impeller channel 32 out in the form of a streamlined, before preferably convex rounding or an inlet / Ausströmfase 30d, 30e (Figure 9c according to the sectional shape "EE" in Figure 9th Figures 10, 10a, 10b).
  • a lateral surface 31 of the impeller 30 ( Figure 10) more than one freewheel recess 30 c are provided. These are trough-shaped or trough-shaped and preferably formed with self-contained boundary contour, distributed over the circumference of the lateral surface 31 and in each case from each other and each of the the impeller passage 32 receiving end face of the impeller 30 is arranged at a distance, whereby a closed over the circumference of the lateral surface 31, tra ing sliding surface structure is present.
  • a method for conveying flowable substances with the positive displacement pump 100, 200 and with the impeller 30, 30 * for this positive displacement pump of the type described above is characterized by the following steps (a) to (c), which are also described below with reference to FIGS to 2c and 3a to 3c, which show a cut from the positive displacement pump 100 with six outer and six inner Wel renhimmmen (60 degree division), will be further clarified:
  • outer chamber volumes KVa radially inwardly of, be attracted to the axis of rotation R of the impeller 30, 30 *, rotationally symmetric metric outer surface Ma of the stationary guide ring 50 and the inner chamber volumes KVi radially outside of the, relative to the axis of rotation R, rotationally symmetrical inner lateral surface Mi of the guide ring 50 are bounded.
  • the respective outer chamber volume KVa is formed between the adjacent externa ßeren displacer 34a of the outer channel boundary 34 on the one hand and the externa ßeren lateral surface Ma of the guide ring 50 on the other.
  • the respective inner chamber volume KVi is formed between the adjacent inner displacers 36a of the inner channel boundary 36 on the one hand and the inner circumferential surface Mi of the guide ring 50 on the other hand (FIGS. 2a to 3c).
  • FIGS. 3a, 3b and 3c angular positions -45, -30 and -15 degrees. It is obvious that the respective passage cross-section of the pressure opening 22 in relation to the chamber volumes VKa, VKi located in their catchment area is identical to the assigned passageway. cross section of the mammal opening 22 also in relation to the chamber volumes located in their catchment area VKa, VKi.
  • the flowable substance P is in the outer and inner chamber volumes KVa, KVi by the impeller 30, 30 * in the direction of rotation n opposite and on the outer and inner circumferential surface Ma, Mi voltage from the suction to Drucköff 20, 22 moved .

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Abstract

L'invention concerne une pompe volumétrique rotative (100, 200) destinée au transport de substances (P) aptes à l'écoulement, qui comprend un conduit de rotor circonférentiel (32) en forme de gorge qui s'engage axialement au moins dans l'une des faces d'extrémité du rotor cylindrique (30) et concentriquement à son axe de rotation (R); le conduit de rotor (32) comportant des flancs de gorge qui ont la forme d'une limite de conduit radialement extérieure (34) uniformément ondulé et incurvée de manière continue et d'une limite de conduit (36) radialement intérieure et qui sont équidistantes l'une de l'autre, lorsque l'on regarde dans la direction radiale et dans chaque plan perpendiculaire à l'axe de rotation (R), et qui se terminent dans une surface de base de conduit (38), et une bague de guidage annulaire (50) qui est reliée de manière fixe au corps de couvercle (6) ou au corps de boîtier (4), qui s'engage dans le conduit de rotor (32) et qui s'étend jusqu'à la surface de base de conduit (38). Dans la direction radiale, toutes les crêtes d'onde extérieures (WKa) de la limite de conduit extérieure (34) et toutes les crêtes d'ondes intérieures (WKi) de la limite de conduit intérieure (36) sont guidées sur la totalité de la longueur d'extension jusqu'à la bague de guidage (50). L'invention concerne également un rotor (30, 30*) pour une telle pompe volumétrique et un procédé de refoulement utilisant une telle pompe volumétrique.
EP18822262.4A 2017-12-02 2018-11-19 Pompe volumétrique rotative pour transporter des substances apte à l'écoulement, rotor pour une telle pompe et procédé de transport ayant une telle pompe volumétrique Withdrawn EP3717775A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102017011154.5A DE102017011154B3 (de) 2017-12-02 2017-12-02 Rotierende Verdrängerpumpe zum Fördern von fließfähigen Stoffen, Laufrad für eine solche und Verfahren zum Fördern mit einer solchen Verdrängerpumpe
PCT/EP2018/000516 WO2019105578A1 (fr) 2017-12-02 2018-11-19 Pompe volumétrique rotative pour transporter des substances apte à l'écoulement, rotor pour une telle pompe et procédé de transport ayant une telle pompe volumétrique

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Publication Number Publication Date
EP3717775A1 true EP3717775A1 (fr) 2020-10-07

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EP18822262.4A Withdrawn EP3717775A1 (fr) 2017-12-02 2018-11-19 Pompe volumétrique rotative pour transporter des substances apte à l'écoulement, rotor pour une telle pompe et procédé de transport ayant une telle pompe volumétrique

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Country Link
EP (1) EP3717775A1 (fr)
DE (2) DE102017011154B3 (fr)
WO (1) WO2019105578A1 (fr)

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DK165462C (da) * 1982-04-07 1993-04-19 Sumitomo Heavy Industries Hydraulisk motor
DE3406543A1 (de) * 1984-02-23 1985-09-05 Rudolf 8000 München Braren Verdraengermaschine, insbes. zykloiden-planetengetriebe mit integriertem, hydraulischem motor
DE112004002786A5 (de) * 2004-01-09 2007-05-24 Manfred Sommer Drehkolbenpumpe mit axial beweglichem Flügel
DE102015116769A1 (de) 2015-10-02 2017-04-06 Watson-Marlow Gmbh Pumpe und Sperrelement

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DE202017006441U1 (de) 2018-01-15

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