Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16J—PISTONS; CYLINDERS; SEALINGS
  • F16J15/00—Sealings
  • F16J15/16—Sealings between relatively-moving surfaces
  • F16J15/34—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member
  • F16J15/3404—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member and characterised by parts or details relating to lubrication, cooling or venting of the seal
  • F16J15/3408—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member and characterised by parts or details relating to lubrication, cooling or venting of the seal at least one ring having an uneven slipping surface
  • F16J15/3424—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member and characterised by parts or details relating to lubrication, cooling or venting of the seal at least one ring having an uneven slipping surface with microcavities
• • 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
  • F04D29/04—Shafts or bearings, or assemblies thereof
  • F04D29/041—Axial thrust balancing
  • F04D29/0413—Axial thrust balancing hydrostatic; hydrodynamic thrust bearings
• • 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
  • F04D29/06—Lubrication
  • F04D29/061—Lubrication especially adapted for liquid pumps
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
  • F04D29/00—Details, component parts, or accessories
  • F04D29/08—Sealings
  • F04D29/16—Sealings between pressure and suction sides
  • F04D29/165—Sealings between pressure and suction sides especially adapted for liquid pumps
  • F04D29/167—Sealings between pressure and suction sides especially adapted for liquid pumps of a centrifugal flow wheel
• • 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
  • F04D29/60—Mounting; Assembling; Disassembling
  • F04D29/62—Mounting; Assembling; Disassembling of radial or helico-centrifugal pumps
  • F04D29/622—Adjusting the clearances between rotary and stationary parts
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
  • F16C17/00—Sliding-contact bearings for exclusively rotary movement
  • F16C17/02—Sliding-contact bearings for exclusively rotary movement for radial load only
  • F16C17/026—Sliding-contact bearings for exclusively rotary movement for radial load only with helical grooves in the bearing surface to generate hydrodynamic pressure, e.g. herringbone grooves
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
  • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
  • F16C33/02—Parts of sliding-contact bearings
  • F16C33/04—Brasses; Bushes; Linings
  • F16C33/06—Sliding surface mainly made of metal
  • F16C33/10—Construction relative to lubrication
  • F16C33/1025—Construction relative to lubrication with liquid, e.g. oil, as lubricant
  • F16C33/106—Details of distribution or circulation inside the bearings, e.g. details of the bearing surfaces to affect flow or pressure of the liquid
  • F16C33/1065—Grooves on a bearing surface for distributing or collecting the liquid
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
  • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
  • F16C33/02—Parts of sliding-contact bearings
  • F16C33/04—Brasses; Bushes; Linings
  • F16C33/06—Sliding surface mainly made of metal
  • F16C33/10—Construction relative to lubrication
  • F16C33/1025—Construction relative to lubrication with liquid, e.g. oil, as lubricant
  • F16C33/106—Details of distribution or circulation inside the bearings, e.g. details of the bearing surfaces to affect flow or pressure of the liquid
  • F16C33/107—Grooves for generating pressure
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
  • F04D7/00—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts
  • F04D7/02—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts of centrifugal type
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
  • F16C2360/00—Engines or pumps
  • F16C2360/42—Pumps with cylinders or pistons

Definitions

• the present invention relates to a coolant pump with an improved gap seal between a suction side and a pressure side of the coolant pump, in particular for pumping a cooling water or a water-based coolant in the exemplary applications of a cooling circuit for an internal combustion engine or for an electric traction motor on a vehicle.
• centrifugal pumps of the radial or axial pump type which suck in a liquid conveying medium axially to the pump shaft and build up a conveying pressure by means of a radially or axially accelerating pump impeller.
• the aim is to set the gap between the pump impeller and the housing as small as possible so that a gap seal is created, i.e. a gap with a gap size effective for sealing of, for example, 20 to 80 Micrometer is achieved.
• the gap size of a gap seal between the pump impeller and the housing is significantly influenced by the result of a tolerance chain of fits that results individually after several pump components have been put together.
• Manufacturing steps that affect the tolerance chain relate, for example, to the fitting of a seat of the pump impeller on the shaft, a seat of the shaft in a shaft bearing, a seat of the shaft bearing in the housing, etc. a housing section in which the shaft is accommodated men, are not in one piece, a fit between the corresponding housing sections also has an effect on the result of the tolerance chain, which influences the gap seal between the suction side and the pressure side.
• DE 90 01 229 U1 discloses a gap seal between an impeller and a stage housing of a centrifugal pump, the sealing gap running coaxially to the shaft.
• DE 199 60 160 B4 discloses a device for optimizing the gap width in centrifugal pumps to compensate for manufacturing tolerances and positional deviations in relation to a housing bore.
• the wheel sealing collar is in contact with a split ring which is arranged in a stop surface of an inner housing bore of the pump housing.
• On the inner jacket of the split ring, a centering seat, a ring sealing collar and a free seat are arranged side by side, and on the outer jacket of the split ring webs or radial lamellas.
• seals in particular sealing lips per se, are subject to wear through abrasion, the effects of impurities or other particles and foreign bodies, embrittlement, etc.
• seals have a coefficient of friction that increases the required drive energy and worsens the energy efficiency of the pump operation.
• the object is achieved by a coolant pump with the features of claim 1.
• the coolant pump according to the invention is characterized in particular by: a rotating sliding ring which is arranged at an axial end of an inlet opening on a pump impeller; a static slip ring, which is arranged around a mouth of an inlet, opposite to the rotating slip ring on a pump housing; wherein the rotating sliding ring has a sliding surface and the static sliding ring has a sliding surface, the sliding surfaces facing each other and a Form slide bearings which absorb a force axially directed from the pump impeller to the pump housing; and a microstructure for generating a hydrodynamic lubricating film between the sliding surfaces is formed on at least one of the mutually facing sliding surfaces, the microstructure comprising cavities which are designed to store liquid coolant on the at least one sliding surface.
• the present invention provides for the first time a microstructure on a gap seal between a pump impeller and a housing of a centrifugal pump, in particular a coolant pump.
• the invention provides for the first time a microstructure on an axial bearing of a centrifugal pump, in particular an axial sliding bearing formed by two sliding rings.
• the invention is based on the generation of a hydrodynamic lubricating film in a gap seal between a pump impeller and a housing.
• a hydrodynamic lubricating film does not form on the basis of chemical requirements, such as a lubricious additive, but rather on the basis of physical requirements.
• the hydrodynamic lubricating film provided according to the invention forms independently between surfaces facing one another under the conditions of locally bound fluid accumulation, counter-rotation and hydrostatic pressure. The rotation and the hydrostatic pressure come about through the operation of the pump impeller and through a contact pressure that is dependent on the delivery pressure.
• the local binding of the fluid or the application-specific coolant is achieved according to the invention by a surface distribution of cavities, the geometry of which is suitable for droplet-like accumulation or storage of the fluid on a surface.
• the application of the invention is optimized, for example, by setting the geometry and size of the cavities with regard to wetting behavior, surface tension, adhesive force or rheological properties of a coolant, in particular a water-glycol mixture.
• the hydrodynamic lubricating film provided according to the invention, which is generated by the microstructure, has several advantages.
• the hydrostatic pressure in the hydrodynamic lubricating film largely suppresses direct surface contact between the pump impeller and the housing or between the two sliding rings. As a result, there is very little wear, which means that a long service life is achieved without deteriorating the sealing effect.
• the lack of direct surface contact with the hydrodynamic lubricating film also means that very low coefficients of friction are achieved, which contribute to the high energy efficiency of the pump.
• the hydrostatic pressure in the hydrodynamic lubricating film represents a separate pressure zone that acts as a seal between a suction pressure and a delivery pressure of the pump.
• Discrete zones of different pressures basically represent a barrier against the passage of a flow.
• This principle consists, for example, of seals with grooves or chambers for providing several different pressure zones between two sealing sides are known.
• the hydrodynamic lubricating film provided according to the invention which is generated by the microstructure, thus permanently achieves a better sealing effect between a suction side and a pressure side of the pump than a gap seal without a hydrodynamic lubricating film.
• the hydrodynamic lubricating film sets adhesion and sliding friction between the sliding surfaces 40, 50 of the sliding rings 4, 5 and at the same time provides a hydraulic seal while avoiding direct contact between the rotating pump impeller 2 and the pump housing 1, which results in low friction and good wear resistance can be achieved in favor of service life and operational reliability.
• a material of a sliding ring can differ from the material of the pump housing and from the material of the pump impeller.
• the pump housing is made from an injection-molded aluminum and the pump impeller is made from an injection-molded plastic.
• a more suitable, i.e. a functional or a harder material can be selected to provide the sliding surfaces or the microstructure.
• the microstructure can be formed on the sliding surface of the rotating sliding ring and on the sliding surface of the static sliding ring.
• the total volume of the accumulated coolant droplets can potentially be doubled with the same area-related density of the cavities.
• the rotating sliding ring and the static sliding ring or at least a respective section thereof forming the sliding surface can consist of a material or composite material based on an elastomer or a synthetic resin.
• Elastomers can be used to functionally utilize a viscoplastic property when shear forces occur on the cavities, as will be explained later.
• a synthetic resin can reduce manufacturing costs for the sliding ring or for the process for the microstructure to be introduced.
• the rotating sliding ring and the static sliding ring or at least a respective section thereof forming the sliding surface can consist of a material or an alloy based on a metal or a ceramic.
• metals or ceramics By using metals or ceramics, high surface hardness and thus high wear resistance can be achieved.
• the microstructure can only be formed on the sliding surface of the static sliding ring.
• the static sliding surface offers the advantage that the cavities of the microstructure are not exposed to any centrifugal force during operation.
• the static sliding ring or at least a section thereof which forms the sliding surface can consist of a material or composite material based on an elastomer or a synthetic resin.
• a viscoplastic property can thus be used functionally when shear forces occur on the cavities, as will be explained later.
• the rotating sliding ring or at least a section thereof which forms the sliding surface can consist of a material or an alloy based on a metal or a ceramic.
• a smooth or polished surface with low roughness, ie a low coefficient of friction, and a high surface hardness to permanently maintain the low Roughness can be created.
• the cavities of the microstructure can have a closed contour to the surface of the sliding surface. Compared to a surface roughness, the topology of which contains any shapes of cavities with undefined contours, the closed contour of the cavities ensures reliable deposition of droplets to build up a hydrodynamic lubricating film between the sliding surfaces.
• the cavities of the microstructure can have a dimension of 10 to 40 ⁇ m in a depth direction to the surrounding surface. Within the range mentioned, a capillary effectiveness of the cavities for the deposition of the application-specific liquid or the coolant in the microstructure of the sliding surface is achieved. According to one aspect of the invention, the cavities of the microstructure can have a dimension of 15 to 200 ⁇ m micrometers in a direction of the shortest extent to the surrounding surface. In this area, too, a capillary effectiveness of the cavities for the deposition of the application-specific liquid or the coolant in the microstructure of the sliding surface is achieved.
• the cavities can have the shape of a spherical cap or an ellipsoidal cap, an elongated hole or a groove.
• the other shapes listed enable an alignment or shape optimization of the microstructure in relation to the direction of rotation on the sliding surfaces.
• the sliding surfaces facing one another can run perpendicular to the pump shaft.
• there is a vertical contact pressure on the sliding surfaces which provides a secure configuration for building up a hydrostatic pressure and a hydrodynamic lubricating film.
• the pump impeller can be connected directly to the pump shaft and the pump shaft can be mounted so that it can move axially with respect to the pump housing.
• a simple connection such as, for example, a form-fitting extrusion coating of the shaft with an impeller body, can be produced.
• the pump impeller can be arranged axially movably on the pump shaft and coupled by means of a plug-in coupling.
• an axially movable mass and thus a mass inertia can be reduced, ie the response behavior of an axial movement of the sliding surfaces facing one another is improved when the hydrostatic pressure and the hydrodynamic lubricating film are built up.
• FIG. 1 shows a cross section through a coolant pump from the prior art
• FIG. 2 shows a cross section through a coolant pump according to an embodiment of the invention.
• a conventional coolant pump is shown.
• the pump impeller 2 is arranged at a small axial distance from an opposite surface of a Ge housing bore of the pump housing 1. This distance determines a leakage gap of a so-called split ring seal, which represents a barrier between a suction area with the lower pressure p1 and a pressure area with the higher pressure p2.
• the effectiveness of the split ring seal depends on the size of the leakage gap through which a leak escapes back into the suction area as part of the already pressurized delivery flow due to the pressure difference from the higher pressure p2 to the lower pressure p1.
• the pump impeller 2 is fixed in relation to an axial position in relation to the pump housing 1.
• the leakage gap is shown enlarged in FIG. 1.
• gap widths of a few tens to a few hundred micrometers are generally preferred.
• the precise setting of the leakage gap on a centrifugal pump or the coolant pump shown in FIG. 1 is, however, as described above, influenced by a tolerance chain of fits between the pump components. This makes it difficult to ensure uniform sealing effectiveness on the illustrated wear ring seal in series production.
• a leak from the pressure area to the suction area represents a hydraulic short circuit from a portion of the delivery flow and affects the volumetric efficiency of the pump.
• the coolant pump according to the invention takes this problem into account. An embodiment of the coolant pump according to the invention will be described with reference to FIG.
• a pump housing 1 of the coolant pump comprises a cavity designed as a pump chamber 10 in which a pump impeller 2 is accommodated.
• the pump impeller 2 is fixed in a rotationally fixed manner on egg nem free end of a pump shaft 3 which extends between the pump chamber 10 and a drive side, not shown.
• the pump shaft 3 is supported by a radial bearing 13 and received in the radial bearing 13 so as to be axially displaceable relative to the pump housing 1.
• On the right side, not shown, of the pump housing 1 is the drive side of the coolant pump, on which, for example, a belt pulley or an electric motor is provided.
• a pump cover is inserted into an open axial end of the pump housing 1 and closes off the pump chamber 10 at the end of the pump shaft 3 on the pump impeller 2.
• the pump cover forms a centrally arranged suction port 11 as an inlet 6 of the pump, which feeds axially to one end face of the pump impeller 2.
• the pump impeller 2 is a radial pump impeller with a central inlet opening which is arranged adjacent to an opening of the suction connector 11 in the pump chamber 10.
• the delivery flow which flows axially onto the pump impeller 2 through the intake port 11, is accelerated radially outward from the pump chamber 10 by the inner vanes.
• An outlet 7 of the pump designed as a spiral housing 12, connects to the periphery of the pump chamber 10 and ends in a pressure port (not shown), whereby the accelerated delivery flow is discharged from the pump housing 1.
• a rotating slide ring 4 is arranged, which surrounds the inlet opening of the pump impeller 2 and rotates together with the pump impeller 2.
• the rotating slide ring 4 is fitted into the pump impeller 2 through an annular groove and is fixed in a rotationally fixed manner.
• a static sliding ring 5 is arranged on the pump housing 1, which opens the suction port 11 into the pump chamber 10 in a radial area of the rotating Seal ring 4 surrounds.
• the static slide ring 5 is fitted into the pump housing 1 through an annular groove and is fixed in a rotationally fixed manner.
• the pump impeller 2 can move axially in relation to the pump housing 1. Due to the pressure difference between the lower pressure pl in a central intake area of the intake port 11 and a higher pressure p2 in a radially outer pressure area of the spiral housing 12, the pump impeller 2 is attracted to the intake port 11 during operation of thedemit telpump until the rotating seal ring 4 is attached to the pump impeller 2 runs against the static sliding ring 5 on the pump housing 1. A sliding surface 40 of the rotating sliding ring 4 pointing towards the pump housing 1 and a sliding surface 50 of the static sliding ring 5 pointing towards the pump impeller 2 thus together form an axial bearing.
• This axial bearing and the radial bearing 13 of the pump shaft 3 serve together to support the rotation of the pump impeller 2 in the pump chamber 10 of the pump housing 1.
• a microstructure (not shown) is incorporated on a sliding surface 40, 50 of the axial bearing.
• the microstructure contains cavities in which the coolant is deposited on the surface.
• a large number and a distribution of the surface area of the cavities in the microstructure result in surface wetting which, if there is sufficient pressure perpendicular to the surface, ie a hydrostatic pressure, adheres parallel to the surface even under the load of shear forces. This means that even in a rotational movement of the sliding surfaces 40, 50 relative to one another, surface wetting that is perpendicular to the axis of rotation does not tear off.
• the microstructure preferably contains cavities with dimensions whose depth is in a range from 10 to 40 ⁇ m and whose width and length are in a range from 15 to 200 ⁇ m.
• the cavities In a cross section in the depth direction, the cavities have an essentially round contour and a closed contour in relation to the surface. This results, for example, from the introduction of cavities in the form of spherical caps.
• the cavities can have the shape of ellipsoidal domes, elongated holes or grooves, a longitudinal axis or a transverse axis of the contour being oriented in relation to a radial direction or a circumferential direction of the annular sliding surface 40, 50.
• the axial bearing from a static sliding ring 5, which is made of a metal, and a rotating sliding ring 4, which is made of a
• Metal is made, formed, the microstructure being introduced into both sliding surfaces 40, 50 of the sliding rings 5.
• the axial bearing is formed from a static sliding ring 5 made of a metal and a rotating sliding ring 4 made of a metal, the microstructure only in the sliding surface 50 of the static sliding ring 5 is introduced.
• the axial bearing is formed from a static sliding ring 5 made of ceramic and a rotating sliding ring 4 made of ceramic, the microstructure being introduced into both sliding surfaces 40, 50 of the sliding rings 5 is.
• the axial bearing is formed from a static sliding ring 5 made of ceramic and a rotating sliding ring 4 made of ceramic, the microstructure only in the sliding surface 50 of the static sliding ring 5 is introduced.
• the axial bearing is formed from a static sliding ring 5 made of plastic and a rotating sliding ring 4 made of plastic, the microstructure being incorporated in both sliding surfaces 40, 50 of the sliding rings 5.
• the axial bearing is formed from a static sliding ring 5, which is made of a plastic, and a rotating sliding ring 4, which is made of a plastic, the microstructure being introduced only in the sliding surface 50 of the static sliding ring 5 is.
• the axial bearing is formed from a static sliding ring 5 made of an elastomer and a rotating sliding ring 4 made of an elastomer, the microstructure being incorporated in both sliding surfaces 40, 50 of the sliding rings 5 .
• the axial bearing is formed from a static sliding ring 5, which is made of an elastomer, and a rotating sliding ring 4, which is made of an elastomer, the microstructure only being introduced into the sliding surface 50 of the static sliding ring 5 is.
• the axial bearing is formed from a static sliding ring 5, which is made of a viscoplastic elastomer, and a rotating sliding ring 4, which is made of a metal, the microstructure only being introduced into the sliding surface 50 of the static sliding ring 5 is.
• the sliding surface 40 of the rotating sliding ring 4 made of metal has an essentially smooth surface with a low roughness.
• the viscoplastic property of the elastomer, which has the microstructure on the other hand, has the following advantageous effect on a response behavior during the build-up of the hydrodynamic lubricating film.
• the axial bearing is formed from a static sliding ring 5, which is made of a viscoplastic elastomer, and a rotating sliding ring 4, which is made of a ceramic, the microstructure only in the sliding surface 50 of the static Slip ring 5 is introduced.
• the axial bearing is formed from a combination of a static sliding ring 5 from the aforementioned embodiments and a rotating sliding ring 4 from the aforementioned embodiments.
• microstructure is only incorporated in the sliding surface 40 of the rotating sliding ring 4.
• the microstructure can have a mixture of cavities from the various shapes, such as a spherical cap, an ellipsoidal cap, an elongated hole or a groove, with a longitudinal axis or a transverse axis of the contour of the respective shapes having the same or different orientations in relation to a radial direction or a circumferential direction of the annular sliding surface 40, 50 may have.
• an axial mobility of the pump impeller 2 within the pump chamber 10 can be provided by means of a plug-in coupling.
• the pump shaft 3 can be mounted radially and axially or only radially.
• the pump impeller 2 is received by a plug connection on the pump shaft, which provides a positive connection in the direction of rotation and allows play in the axial direction.
• the invention can be implemented not only on a coolant pump of the radial pump type, but also on a coolant pump of the axial pump type or of the semi-axial pump type.

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• Engineering & Computer Science (AREA)
• General Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• Physics & Mathematics (AREA)
• Fluid Mechanics (AREA)
• Chemical & Material Sciences (AREA)
• Oil, Petroleum & Natural Gas (AREA)
• Structures Of Non-Positive Displacement Pumps (AREA)

Applications Claiming Priority (2)

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• 2019
  • 2019-10-31 DE DE102019129494.0A patent/DE102019129494A1/de active Pending
• 2020
  • 2020-09-02 CN CN202080073499.2A patent/CN114585837A/zh active Pending
  • 2020-09-02 US US17/769,086 patent/US20240102482A1/en active Pending
  • 2020-09-02 EP EP20767520.8A patent/EP4051906A1/de active Pending
  • 2020-09-02 WO PCT/EP2020/074437 patent/WO2021083568A1/de active Application Filing

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