EP3741997B1 - Pumpenvorrichtung mit wärmetauscher zur kühlung des antriebs - Google Patents

Pumpenvorrichtung mit wärmetauscher zur kühlung des antriebs Download PDF

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Publication number
EP3741997B1
EP3741997B1 EP20175470.2A EP20175470A EP3741997B1 EP 3741997 B1 EP3741997 B1 EP 3741997B1 EP 20175470 A EP20175470 A EP 20175470A EP 3741997 B1 EP3741997 B1 EP 3741997B1
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EP
European Patent Office
Prior art keywords
cooling duct
cooling
pump device
heat exchanger
course
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP20175470.2A
Other languages
German (de)
English (en)
French (fr)
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EP3741997A1 (de
Inventor
Steve MEHLHORN
Lorenz Schneider
Max Werthmüller
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.)
Frideco AG
Original Assignee
Frideco AG
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Publication date
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Publication of EP3741997A1 publication Critical patent/EP3741997A1/de
Application granted granted Critical
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/58—Cooling; Heating; Diminishing heat transfer
    • F04D29/586—Cooling; Heating; Diminishing heat transfer specially adapted for liquid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D13/00—Pumping installations or systems
    • F04D13/02—Units comprising pumps and their driving means
    • F04D13/06—Units comprising pumps and their driving means the pump being electrically driven
    • F04D13/0653—Units comprising pumps and their driving means the pump being electrically driven the motor being flooded
    • 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
    • F04D13/02—Units comprising pumps and their driving means
    • F04D13/06—Units comprising pumps and their driving means the pump being electrically driven
    • F04D13/08—Units comprising pumps and their driving means the pump being electrically driven for submerged use
    • F04D13/086—Units comprising pumps and their driving means the pump being electrically driven for submerged use the pump and drive motor are both submerged
    • 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
    • F04D29/58—Cooling; Heating; Diminishing heat transfer
    • F04D29/5806—Cooling the drive system
    • 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
    • F04D29/58—Cooling; Heating; Diminishing heat transfer
    • F04D29/586—Cooling; Heating; Diminishing heat transfer specially adapted for liquid pumps
    • F04D29/5866—Cooling at last part of the working fluid in a heat exchanger
    • 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
    • F04D29/58—Cooling; Heating; Diminishing heat transfer
    • F04D29/586—Cooling; Heating; Diminishing heat transfer specially adapted for liquid pumps
    • F04D29/588—Cooling; Heating; Diminishing heat transfer specially adapted for liquid pumps cooling or heating the machine
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D3/00—Axial-flow pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P3/00—Liquid cooling
    • F01P2003/001—Cooling liquid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P3/00—Liquid cooling
    • F01P3/20—Cooling circuits not specific to a single part of engine or machine
    • 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

Definitions

  • the invention relates to a pump device according to the preamble of patent claim 1.
  • the object of the invention consists in particular in providing a generic device with improved properties with regard to heat exchange.
  • the object is achieved according to the invention by the features of patent claim 1, while advantageous configurations and developments of the invention can be found in the dependent claims.
  • the invention is based on a pump device, in particular a submersible pump device, with at least one heat exchanger unit, which is provided in at least one operating state for heat exchange between a cooling fluid and a liquid to be pumped and has at least one cooling channel and at least one shaft mount with an axial direction, wherein a cross-sectional area content of the cooling channel changes by at most 200% over at least a large part of a course of the cooling channel.
  • the heat exchanger unit can have a large number of cooling channels.
  • a heat exchange can be improved as a result.
  • a homogeneous heat transfer from the cooling fluid to the liquid to be pumped can be achieved.
  • an optimal cross-sectional area which allows a high flow rate of the cooling fluid and a high contact area for heat transfer, can be at least substantially maintained over the majority of the course.
  • a simple production of the heat exchanger unit can be achieved particularly advantageously.
  • a “pump device” is to be understood in particular as at least a part, in particular a subassembly, of a pump. In particular, the pump device can also have the entire pump.
  • a pump in particular a submersible pump, is to be understood in particular as a device which, in at least one operating state, provides a movement of a preferably incompressible liquid to be pumped.
  • the pump device preferably has a jacket unit which limits the pump to the outside, a pump device operated drive shaft and/or a screw unit set in rotation by the drive shaft in at least one operating state, the rotation of the screw unit providing the movement of the liquid to be pumped.
  • the pump device can have a piston unit operated by a motor unit of the pump device, which is Displacement process puts the liquid to be pumped in motion.
  • the motor unit is arranged within a motor compartment of the pump that is delimited from the outside.
  • the motor unit can have an internal combustion engine.
  • the motor unit particularly advantageously has an electric motor.
  • the pump in at least one operating state, can be arranged outside and/or at least partially or also completely inside the liquid to be pumped.
  • a "heat exchanger unit” is to be understood in particular as a unit which is intended to absorb heat from at least one fluid and/or element and to transfer it in particular to at least one other fluid and/or element.
  • the heat exchanger unit at least one portion which forms at least one surface-enlarging structure.
  • the heat exchanger unit advantageously also has at least one plate-shaped element.
  • a "plate-shaped element” is to be understood in particular as an element in which the smallest imaginary cuboid, which just accommodates the element, has a height which is at most 50%, in particular at most 20%, advantageously at most 10% and preferably at most 5%. corresponds to a length and width of the cuboid.
  • the plate-shaped element advantageously contributes to a definition of the cooling channel.
  • the heat exchanger unit particularly advantageously helps to delimit the engine compartment from the outside. It would be conceivable that the heat exchanger unit is part of the shell unit.
  • the heat exchanger unit is preferably arranged at one end of the engine compartment facing the screw unit. In an assembled state, the heat exchanger unit particularly preferably forms a sealing connection together with the jacket unit. It would be conceivable for the heat exchanger unit to be pressed and/or welded onto the jacket unit.
  • the heat exchanger unit is preferably screwed onto the shell unit.
  • the heat exchanger unit preferably has a material which is identical to a material of the shell unit. In this way, in particular, good sealing of the engine compartment can be ensured at different temperatures.
  • the heat exchanger unit can have at least one, preferably rubber-like, sealing ring, which contributes to the sealing connection with the contact surface of the jacket unit.
  • the heat exchanger unit is particularly preferably designed as a floor panel of the engine compartment.
  • a "cooling fluid” is to be understood in particular as a liquid which is intended to absorb heat from at least one element and to transfer it in particular to at least one other element, for example the heat exchanger unit.
  • the cooling fluid preferably has a high thermal conductivity and/or heat capacity. Most preferably, the cooling fluid has a viscosity that allows the cooling fluid to be pumped. It is conceivable that the cooling fluid is identical to the pumped medium, preferably however, the cooling fluid is different from the fluid being pumped and is dedicated to cooling the pump. Cooling fluids can include water and/or oils, for example.
  • a “cooling duct” is to be understood in particular as a coherent volume through which cooling fluid flows in at least one operating state.
  • a continuous depression, in particular a groove, of the heat exchanger unit advantageously contributes to a definition of the cooling channel.
  • the depression defines a channel wall which delimits the cooling channel towards the heat exchanger unit.
  • the channel wall preferably has a largely oval or round cross-section over the majority of its extent.
  • "largely oval or round cross-section” is to be understood in particular as meaning that at least 60%, advantageously at least 70%, preferably at least 80% and particularly preferably at least 90% of the cross-section of the channel wall are covered by an oval or a circle without the oval or circle intersecting the canal wall.
  • the cooling channel is in the form of a cavity open to the outside in the interior of the heat exchanger unit.
  • the cooling channel has at least one inlet opening and at least one outlet opening, which preferably define a flow direction of cooling fluid flowing through the cooling channel.
  • the inlet opening and the outlet opening are preferably at different radial distances from the shaft receptacle.
  • a radial distance between the input opening and the shaft receptacle is particularly preferably greater than a radial distance between the output opening and the shaft receptacle.
  • the cooling fluid advantageously flows within a cooling circuit in which the cooling fluid flows from the jacket unit into the inlet opening, through the cooling channel and from the outlet opening back into the jacket unit.
  • the jacket unit preferably has cooling ducts, with a further outlet opening of at least one cooling duct of the jacket unit being fluidically connected to the inlet opening and a further inlet opening of at least one cooling duct of the jacket unit being fluidically connected to the outlet opening.
  • a “shaft receptacle” is to be understood in particular as a partial area of the heat exchanger unit which surrounds at least one opening in the heat exchanger unit through which the drive shaft can penetrate the heat exchanger unit.
  • the shaft mount is preferably at least essentially in the form of a circular disk.
  • “at least essentially” should be understood to mean, in particular, taking into account common manufacturing tolerances.
  • the shaft mount is spaced at least substantially homogeneously from an outer contour of the heat exchanger unit when viewed perpendicularly to the axial direction.
  • An "axial direction" of the shaft mount is to be understood in particular as a direction which is defined by the shaft mount and in which the drive shaft is aligned in an assembled state.
  • the axial direction is the only possible direction in which the drive shaft can be oriented in the assembled state.
  • the axial direction is preferably aligned perpendicular to a main extension plane of the shaft mount.
  • a "main extension plane" of an object is to be understood in particular as a plane which is parallel to a largest side surface of an imaginary cuboid which just about completely encloses the object and in particular runs through the center point of the cuboid.
  • the drive shaft penetrates the shaft mount in the assembled state.
  • a “cross-sectional area” is to be understood in particular as meaning an area of a cross section of the cooling channel.
  • a “cross section” should be understood to mean, in particular, a surface that lies completely within the cooling channel and is oriented perpendicularly to the channel wall of the cooling channel. When viewed perpendicularly to the direction in which the surface extends, the surface preferably completely fills an intermediate space spanned by the channel wall.
  • a "major part of a course of the cooling channel” is to be understood in particular as at least 60%, advantageously at least 70%, preferably at least 80% and particularly preferably at least 90% of the course of the cooling channel. It would be conceivable that the majority of the course of the cooling channel covers the entire Includes cooling channel. The majority of the course of the cooling channel is preferably free of inlet openings and/or outlet openings of the cooling channel.
  • a “course of the cooling channel” is to be understood in particular as meaning a spatial extension of the cooling channel perpendicular to the cross-sectional area of the cooling channel.
  • “Provided” is to be understood in particular as being specially designed and/or equipped. In particular, “intended” should not be understood to mean mere suitability.
  • a unit which is intended to perform a task performs this task to an extent that is satisfactory for an operator of a device to which the unit belongs.
  • the fact that an object is provided for a specific function is to be understood in particular to mean that the object fulfills and/or executes this specific function in at least one application and/or operating state.
  • the cross-sectional area content of the cooling channel alternately decreases and increases over the majority of the course of the cooling channel.
  • the cross-sectional area of the cooling channel changes at most inversely over most of the course.
  • the fact that the cross-sectional area changes “reverse-free” is to be understood in particular to mean that the cross-sectional area changes in a monotonically increasing or monotonically decreasing direction when viewed along the course of the cooling channel.
  • the cross-sectional area content changes monotonously when viewed from the inlet opening to the outlet opening of the cooling channel.
  • a continuous increase in the flow rate of the cooling fluid while it is flowing through the cooling channel can advantageously be achieved.
  • a damming up of the cooling fluid due to a sudden drop in the flow rate can be avoided in a particularly advantageous manner.
  • the cross-sectional area content of the cooling channel is at least essentially constant over the majority of the course of the cooling channel.
  • the cooling channel over most of the course of the cooling channel an at least substantially constant cross-sectional shape.
  • a "cross-sectional shape" is to be understood in particular as an outer contour of the cross-sectional area.
  • the cross-sectional shape could be a truncated circle or a truncated oval. In this way, in particular, heat transfer from the cooling fluid to the liquid to be pumped can be even better homogenized. Production of the heat exchanger unit can advantageously be further simplified.
  • the heat exchanger unit has at least one additional cooling duct, with a circular arc distance running concentrically to a center point of the shaft mount from the cooling duct to the additional cooling duct over the majority of the course of the cooling duct being at least 50%, in particular at least 100%, advantageously at least 150% and preferably at least 200% corresponds to a width of the cooling channel.
  • a "circular arc distance running concentrically to a point" is to be understood in particular as a length of a cutting line which, when viewed in the axial direction and in a section through the heat exchanger unit, whose course corresponds to a circle around the point, separates both cooling channels.
  • a "width of the cooling duct” is to be understood in particular as a length of the cutting line which connects two opposite points of the duct wall to one another.
  • heat transfer via the heat exchanger unit can be improved.
  • the heat exchanger unit can absorb a sufficient quantity of heat from the cooling fluid and transfer it to the liquid to be pumped.
  • the heat exchanger unit preferably has at least one additional cooling duct, with a circular arc distance running concentrically to a center point of the shaft mount from the cooling duct to the additional cooling duct over the majority of the course of the cooling duct being at most 400%, in particular at most 350%, advantageously at most 300%, preferably at most 250% and particularly preferably at most 200% of the width of the cooling channel is equivalent to.
  • heat dissipation of the cooling fluid can be improved.
  • An equilibrium can advantageously be achieved between the heat that can be introduced by the cooling fluid and the heat that can be absorbed by the heat exchanger unit.
  • the cooling channel could be designed as an open cooling channel, which is completely defined by a groove of the heat exchanger unit.
  • the heat exchanger unit have at least one sealing part and at least one cover element, which together define the cooling channel over most of the course.
  • a “sealing part” is to be understood in particular as an element of the heat exchanger unit which delimits the engine compartment on the outside.
  • the sealing part preferably has the shaft receptacle.
  • the sealing part preferably has the indentation.
  • a "cover element” is to be understood in particular as a plate-shaped element of the heat exchanger unit, which together with the depression defines the cooling channel.
  • the cover element rests on the depression in a mounted state. At least two partial areas of the recess preferably extend beyond the cover element and define the inlet opening and the outlet opening.
  • the cover element could be connected to the sealing part by a press fit and/or a welding process.
  • the cover element is preferably screwed onto the sealing part.
  • a pressure in the cooling channel, with which the cooling fluid is conveyed, and accordingly the flow rate of the cooling fluid in the cooling channel can be increased.
  • the cooling channel prefferably, is curved along most of its course.
  • the fact that the cooling channel is “curved” within a sub-area is to be understood in particular to mean that the cooling channel is free of straight-line sections within the sub-area.
  • the cooling channel has a consistent change in direction within the entire sub-area. In this way, in particular, the cooling fluid can contact the heat exchanger unit be improved.
  • a contact area at which the cooling fluid and the heat exchanger unit come into contact can advantageously be increased independently of the cross-sectional area content.
  • the cooling channel is continuously curved along most of its course.
  • the fact that the cooling channel is “continuously” curved within a sub-area is to be understood in particular as meaning that the cooling channel is free of turning points within the sub-area.
  • a course direction of the cooling channel preferably undergoes a constant rotation in one direction during an imaginary movement along the majority of the course of the cooling channel.
  • a "direction of the course of the cooling channel” is to be understood in particular as a direction which runs perpendicularly to the cross-sectional area of the cooling channel.
  • the cooling duct has at least one end region which, when viewed along the axial direction, has a tangential orientation which runs at least essentially towards a center point of the shaft mount.
  • An “end area” of the cooling channel is to be understood in particular as a partial area which has at most 10%, advantageously at most 5% and preferably at most 2% of a spatial extent of the cooling channel and does not adjoin any other partial areas of the cooling channel along one direction.
  • “Tangential alignments” of a sub-area are to be understood in particular as two directions which are antiparallel to one another and parallel to a tangent which lies against an outer contour of the sub-area. In particular, the end area borders on the outlet opening of the cooling channel.
  • the cooling duct preferably has at least one further end area which, at least for the most part, meets tangentially with an imaginary circle which just barely encompasses the cooling duct and whose center is identical to the center of the shaft mount.
  • the fact that the end area hits the imaginary circle “at least to a large extent tangentially” is to be understood in particular to mean that when the end area hits the circle, there is a deviation of a maximum of 20°, advantageously a maximum of 15° and preferably a maximum of 10° from a tangent to a point of impact of the circle.
  • a flow rate of the cooling fluid in the cooling channel can be increased. Reductions in the flow rate due to friction losses can advantageously be reduced.
  • the cooling channel viewed along the axial direction, lie within a sector of a circle whose center is identical to the center of the shaft mount, with the sector of the circle having a center angle of at least 20° , in particular at least 40%, advantageously at least 60% and preferably at least 80%.
  • a contact area at which the cooling fluid and the heat exchanger unit come into contact can advantageously be increased even further, independently of the cross-sectional area content.
  • the cooling channel it would be conceivable for the cooling channel to wind around the shaft mount in a spiral.
  • the heat exchanger unit have a multiplicity of cooling channels which together have at least 10, in particular at least 15, advantageously at least 20 and preferably at least 25 rotational symmetry with respect to the axial direction.
  • the cooling fluid can be quickly conducted away from the heat exchanger unit.
  • the cooling channels are arranged at least essentially in the form of a vortex wheel. This can in particular Heat transfer from the cooling fluid to the liquid to be pumped can be further improved. A large contact area for heat transfer, a high flow rate of the cooling fluid, a high efficiency of the heat transfer and a high installation space efficiency of the cooling channels can be advantageously achieved.
  • the pump device advantageously has at least one rotatably mounted cooling wheel, which is provided for transporting the cooling fluid from an inlet opening of the cooling channel through the cooling channel to an outlet opening of the cooling channel.
  • a “cooling wheel” is to be understood in particular as an element which is intended to rotate in the operating state and to transport the cooling fluid by means of the rotation.
  • the cooling wheel transports the cooling fluid from one half of the drive shaft facing the screw unit to one half of the drive shaft facing away from the screw unit.
  • the cooling wheel is preferably attached to the drive shaft and rotates together with the drive shaft in at least one operating state.
  • the cooling wheel is fastened to a half of the drive shaft that faces the screw unit. In this way, a flow behavior of the cooling fluid can be improved in particular.
  • a direction of curvature of the cooling channel is identical to a direction of rotation of the cooling wheel.
  • the fact that the direction of curvature is “identical to the direction of rotation” should be understood in particular to mean that with an imaginary movement from the inlet opening to the outlet opening, the direction of the cooling channel runs through a rotation whose direction of rotation is identical to the direction of rotation of the cooling wheel.
  • An angular momentum of the cooling fluid flowing through the cooling channel can advantageously be at least partially transferred to the cooling wheel.
  • the figure 1 shows a pump 48 in a greatly simplified cross-sectional view.
  • the pump 48 has a motor unit 11 .
  • the motor unit 11 is designed as an electric motor.
  • the engine unit 11 could be designed as an internal combustion engine.
  • the pump 48 has a drive shaft 25 .
  • the motor unit 11 generates rotation of a drive shaft 25 in an operating state.
  • the drive shaft 25 is connected to a screw unit 15 at one end.
  • the screw unit 15 is intended to be pumped To set liquid (not shown) in motion.
  • the screw unit 15 rotates together with the drive shaft 25 in the operating state.
  • the engine unit 11 is arranged entirely within the engine room 13 .
  • the pump 48 has a shell unit 17 .
  • the jacket unit 17 is bell-shaped.
  • the shell unit 17 partially delimits the engine compartment 13 to the outside.
  • the jacket unit 17 has cooling channels (not shown) for receiving a cooling fluid (not shown).
  • the shell unit 17 is made of cast iron. Alternatively, the shell unit 17 could be made of stainless steel and/or ceramic.
  • the pump 48 has a bearing cap 19 .
  • the bearing cap 19 forms a cover of the engine compartment 13 facing away from the screw unit 15 .
  • the bearing cap 19 consists of a material which is identical to the material of the shell unit 17 .
  • the pump 48 has a pump device 10 .
  • the pump device 10 has a heat exchanger unit 12 .
  • the heat exchanger unit 12 is provided for heat exchange between the cooling fluid and the liquid to be pumped.
  • the heat exchanger unit 12 has a sealing part 26, which in the Figures 2 and 3 is shown in more detail.
  • the sealing part 26 seals an opening of the jacket unit 17 facing the screw unit 15 .
  • the sealing part 26 forms a bottom of the engine compartment 13 facing the screw unit 15 .
  • the sealing part 26 is shell-shaped.
  • the sealing part 26 consists of a material which is identical to the material of the jacket unit 17 .
  • the heat exchanger unit 12 has a cover element 28, which in figure 4 is shown in more detail.
  • the cover element 28 is plate-shaped.
  • the cover element 28 is designed in the shape of a circular disk.
  • the cover element 28 rests directly on the sealing part 26 .
  • the cover element 28 is screwed onto the sealing part 26 .
  • the heat exchanger unit 12 has 25 cooling channels.
  • the cooling channels together have a 25-fold rotational symmetry with respect to the axial direction 18 .
  • the cooling channels are designed in the form of a vortex wheel.
  • the cooling ducts are designed identically to one another, which is why only one cooling duct 14 and another cooling duct 20 are given reference symbols for reasons of clarity and are described below.
  • the sealing part 26 and the cover element 28 jointly define the cooling channel 14 .
  • the sealing part 26 has a depression which defines a channel wall 27 of the cooling channel 14 .
  • the channel wall 27 has a largely oval cross-section over most of its course.
  • the cover element 28 rests on the recess and defines a channel cover 29.
  • a portion of the recess, which is in an inner Edge region extending beyond the cover element 28 also defines an outlet opening 23 of the cooling channel 14.
  • the cooling fluid flows in a cooling circuit. The cooling fluid flows from the jacket unit 17 into the inlet port 21. The cooling fluid flows through the cooling channel 14 and through the outlet port 23 back into the jacket unit 17.
  • the heat exchanger unit 12 has a shaft mount 16 .
  • the shaft receptacle 16 is designed as a partial area of the sealing part 26 in the shape of a circular disk.
  • the shaft seat 16 defines an inner edge of the heat exchanger unit 12.
  • the shaft seat 16 has an axial direction 18 on.
  • the drive shaft 25 is aligned along the axial direction 18 .
  • the drive shaft 25 penetrates the shaft mount 16.
  • a cross-sectional area content of the cooling channel 14 changes by approximately 20% over a large part of a course of the cooling channel 14 .
  • the cross-sectional area could also change by about 50% or about 100%.
  • the cross-sectional area of the cooling passage 14 varies inversely over most of the length of the cooling passage 14 .
  • the cross-sectional area of the cooling channel 14 decreases monotonously radially toward the shaft mount 16 .
  • the cross-sectional area of the cooling passages 14 could be consistent throughout most of the run.
  • figure 5 shows the further cooling channel 20 in a sectional representation together with the cooling channel 14.
  • the sectional representation corresponds to a circular one Section along section line A, with the section surface bent into a plane.
  • the line of intersection A corresponds to a circle whose center point is identical to a center point 34 of the shaft mount 16 .
  • the further cooling channel 20 is arranged adjacent to the cooling channel 14 .
  • the additional cooling channel 20 is identical to the cooling channel 14 with regard to all other features.
  • a circular arc distance 24 running concentrically to a center point 34 of the shaft mount 16 from the cooling channel 14 to the further cooling channel 20 over the majority of the course of the cooling channel 14 corresponds to approximately 150% of a width 22 of the cooling channel 14.
  • the circular arc distance 24 could also be 50% or 400 % of width 22.
  • the cooling channel 14 is continuously curved along most of its course. Alternatively, the cooling channel 14 could run in a straight line in sections and/or have different directions of curvature.
  • the cooling channel 14 has an end area 30 .
  • the end area 30 borders on the outlet opening 23 of the cooling channel 14 .
  • the end region 30 has a tangential orientation 32 when viewed along the axial direction 18 .
  • the tangential alignment 32 essentially runs towards a center point 34 of the shaft mount 16 .
  • the cooling channel 14 has a further end area 31 .
  • the other end area 31 borders on the inlet opening 21 of the cooling channel 14 .
  • the further end region 31 largely meets tangentially on a circle (not shown) whose center point is identical to the center point 34 and which just accommodates the cooling channel 14 .
  • the cooling channel 14 When viewed along the axial direction 18, the cooling channel 14 lies within a sector 36 of the circle.
  • the circle sector 36 has a central angle (not shown) of approximately 45°.
  • the circular sector 36 could have a central angle of 90%.
  • the pump device 10 has a cooling wheel 38 .
  • the cooling wheel 38 is movably mounted.
  • the cooling wheel 38 is fastened to a half of the drive shaft 25 which faces the screw unit 15 .
  • the pump device 10 could also have one or more cooling wheels, which also on one of the Screw unit 15 facing away from half of the drive shaft 25 could be attached.
  • the cooling wheel 38 is provided to transport the cooling fluid from the inlet opening 21 of the cooling channel 14 through the cooling channel 14 to the outlet opening 23 of the cooling channel 14 .
  • a direction of curvature 44 of the cooling channel 14 is identical to a direction of rotation 46 of the cooling wheel 38.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Cooling Or The Like Of Electrical Apparatus (AREA)
EP20175470.2A 2019-05-24 2020-05-19 Pumpenvorrichtung mit wärmetauscher zur kühlung des antriebs Active EP3741997B1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102019113948.1A DE102019113948B3 (de) 2019-05-24 2019-05-24 Pumpenvorrichtung

Publications (2)

Publication Number Publication Date
EP3741997A1 EP3741997A1 (de) 2020-11-25
EP3741997B1 true EP3741997B1 (de) 2023-06-21

Family

ID=70779522

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20175470.2A Active EP3741997B1 (de) 2019-05-24 2020-05-19 Pumpenvorrichtung mit wärmetauscher zur kühlung des antriebs

Country Status (10)

Country Link
US (1) US11255344B2 (https=)
EP (1) EP3741997B1 (https=)
JP (1) JP7560963B2 (https=)
CN (1) CN111980971B (https=)
AU (1) AU2020203292B2 (https=)
CA (1) CA3081192C (https=)
DE (1) DE102019113948B3 (https=)
DK (1) DK3741997T3 (https=)
FI (1) FI3741997T3 (https=)
HU (1) HUE062967T2 (https=)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP4229301A4 (en) 2020-10-19 2025-02-19 Milwaukee Electric Tool Corporation PIN PUMP ARRANGEMENT
CN119388679B (zh) * 2024-10-28 2025-08-05 湖北双鸥汽车饰件有限公司 一种汽车方向盘成型装置及其工艺

Family Cites Families (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB998313A (en) * 1962-02-14 1965-07-14 Sigmund Pumps Ltd Improvements in and relating to pumps
US3450056A (en) * 1967-07-18 1969-06-17 Westinghouse Electric Corp Canned motor pump
DE1703433A1 (de) * 1968-05-18 1971-12-30 Emu Unterwasserpumpen Gmbh Tauchpumpenaggregat mit ueberflutbarer Antriebseinrichtung
DE19845375A1 (de) * 1998-10-02 2000-04-06 Asea Brown Boveri Verfahren und Vorrichtung zur indirekten Kühlung der Strömung in zwischen Rotoren und Statoren von Turbomaschinen ausgebildeten Radialspalten
CA2283603A1 (en) * 1998-10-01 2000-04-01 Paul W. Behnke Forced closed-loop cooling for a submersible pump motor
DE10208688B4 (de) * 2002-02-28 2005-11-10 Abs Pump Center Gmbh Tauchmotorpumpe
DE10222947A1 (de) * 2002-05-24 2003-12-04 Behr Gmbh & Co Heizvorrichtung für Kraftfahrzeuge
US20060275151A1 (en) * 2005-06-01 2006-12-07 Caterpillar Inc. Pump and heat exchanger
US7543457B2 (en) * 2005-06-29 2009-06-09 Intel Corporation Systems for integrated pump and reservoir
US8152458B2 (en) * 2009-04-28 2012-04-10 Mp Pumps, Inc. Centrifugal pump with improved drive shaft and heat exchanger
GB201307257D0 (en) * 2013-04-22 2013-05-29 Flowork Systems Ii Llc Conrollable variable flow coolant pump and flow management mechanism
US11480188B2 (en) * 2014-01-05 2022-10-25 Dajustco Ip Holdings Inc. Integrated pressurized pump shaft seal assembly and method of use thereof
DE102015114783B3 (de) * 2015-09-03 2016-09-22 Nidec Gpm Gmbh Elektrische Kühlmittelpumpe mit strömungsgekühlter Steuerschaltung
DE102017215835A1 (de) * 2017-09-07 2019-03-07 Brose Fahrzeugteile GmbH & Co. Kommanditgesellschaft, Würzburg Fluidgekühlte elektrische Maschine
DE102017131227A1 (de) * 2017-12-22 2019-06-27 Frideco Ag Pumpenvorrichtung, insbesondere überflutbare Pumpenvorrichtung

Also Published As

Publication number Publication date
CA3081192C (en) 2026-03-24
CN111980971B (zh) 2025-06-27
AU2020203292A1 (en) 2020-12-10
CA3081192A1 (en) 2020-11-24
BR102020010196A8 (pt) 2023-10-03
BR102020010196A2 (pt) 2020-12-08
DE102019113948B3 (de) 2020-10-29
CN111980971A (zh) 2020-11-24
DK3741997T3 (da) 2023-09-18
JP2020193620A (ja) 2020-12-03
US20200370564A1 (en) 2020-11-26
US11255344B2 (en) 2022-02-22
AU2020203292B2 (en) 2026-02-12
EP3741997A1 (de) 2020-11-25
HUE062967T2 (hu) 2023-12-28
JP7560963B2 (ja) 2024-10-03
FI3741997T3 (fi) 2023-09-13

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