EP4198310A1 - Pompe à vis - Google Patents

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Publication number
EP4198310A1
EP4198310A1 EP22209989.7A EP22209989A EP4198310A1 EP 4198310 A1 EP4198310 A1 EP 4198310A1 EP 22209989 A EP22209989 A EP 22209989A EP 4198310 A1 EP4198310 A1 EP 4198310A1
Authority
EP
European Patent Office
Prior art keywords
spindle
drive
coupling element
core
diameter
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.)
Pending
Application number
EP22209989.7A
Other languages
German (de)
English (en)
Inventor
Herr Jürgen METZ
Florian Popp
Kristin Lissek
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.)
Leistritz Pumpen GmbH
Original Assignee
Leistritz Pumpen GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Leistritz Pumpen GmbH filed Critical Leistritz Pumpen GmbH
Publication of EP4198310A1 publication Critical patent/EP4198310A1/fr
Pending legal-status Critical Current

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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
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/12—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C2/14—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F04C2/16—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
    • 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
    • F04C15/0057—Driving elements, brakes, couplings, transmission specially adapted for machines or pumps
    • F04C15/0061—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
    • 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
    • F04C15/0057—Driving elements, brakes, couplings, transmission specially adapted for machines or pumps
    • F04C15/008—Prime movers
    • 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
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/12—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C2/123—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with radially or approximately radially from the rotor body extending tooth-like elements, co-operating with recesses in the other rotor, e.g. one tooth
    • 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
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/12—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C2/14—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F04C2/16—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
    • F04C2/165—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type having more than two rotary pistons with parallel axes
    • 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
    • F04C2240/00—Components
    • F04C2240/10—Stators
    • 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
    • F04C2240/00—Components
    • F04C2240/20—Rotors
    • 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
    • F04C2240/00—Components
    • F04C2240/30—Casings or housings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2210/00—Working fluid
    • F05B2210/10—Kind or type
    • F05B2210/11—Kind or type liquid, i.e. incompressible
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2240/00—Components
    • F05B2240/10—Stators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2240/00—Components
    • F05B2240/20—Rotors

Definitions

  • the invention relates to a screw spindle pump, comprising a spindle housing in which a drive spindle and at least one idler spindle meshing with it are accommodated in spindle bores.
  • Such a screw pump is used to deliver a fluid, for example fuel or a supply or cooling liquid or the like.
  • the conveyance takes place via at least two spindles which mesh with one another, namely a drive spindle which is coupled to a drive motor and a running spindle which is accommodated in a spindle housing.
  • the spindle housing has intersecting spindle bores corresponding to the number of spindles.
  • the spindle housing is accommodated in a pump or outer housing, via which the fluid to be pumped is supplied and removed.
  • the functional principle is based on the fact that the drive and idler spindles mesh with one another and a delivery volume is shifted axially as a result of the spindle rotation.
  • the drive spindle has a cylindrical spindle core and usually two spindle profiles running around the spindle core. Two circumferential profile valleys are formed via these spindle profiles, into which the corresponding spindle profiles of the idler spindle engage.
  • the screw spindle with three spindles, which means that two running spindles are then provided which are offset by 180° next to the central drive spindle and mesh with it.
  • the drive spindle is to be coupled to a drive motor, since the drive spindle is actively rotated, while one or the two idler spindles are only taken along.
  • a coupling element is arranged on the end face of the drive spindle and is connected to the drive spindle in a rotationally fixed manner with a corresponding form-fitting geometry.
  • about these Positive connection is given at least one non-rotatable connection in one direction of rotation.
  • Such a screw pump is, for example, from DE 43 08 755 A1 known.
  • a dog clutch is described which couples the drive shaft of the motor to the drive spindle.
  • Two intersecting grooves are ground into one axial end of the drive spindle, as a result of which two opposite, triangular cross-section claws are formed.
  • the disk-shaped coupling element has a circular cross section and is provided with two likewise triangular recesses into which the triangular claws of the drive spindle engage.
  • a slot is provided in the center of the coupling element, in which slot the end section of the drive shaft on the motor side engages.
  • a screw pump in which the end of the spindle, on which the coupling element is to be arranged, is designed to be flat.
  • the spindle profiles also end at this face. Viewed radially, contact surfaces which are at right angles to one another are formed at two opposite positions by removing material.
  • the coupling element has a corresponding, three-dimensional receiving and engagement geometry, which is designed in such a way that axial engagement sections are provided which, as it were, engage in the two opening profile valleys and rest on the contact surfaces formed in their area, so that, viewed in the circumferential direction, a flat , A non-rotatable connection effecting system of the coupling element is given to the drive spindle, while at the same time the coupling element is seated axially on the flat end face.
  • the invention is therefore based on the problem of specifying a screw pump with an improved clutch device.
  • a screw spindle pump comprising a spindle housing in which a drive spindle and at least one running spindle meshing with it are accommodated in spindle bores, the drive spindle having a cylindrical core and at least two spindle profiles running around the spindle core and on one end of the drive spindle in a depression axially delimited by a flat bottom surface, in which the two profile valleys between the two spindle profiles open offset by 180°, a disk-shaped coupling element is arranged, which has an insertion socket for a drive shaft of a drive motor and which in at least one direction of rotation of the drive spindle a form-fitting engagement with axially protruding projections, which laterally delimit the recess and which engage in lateral receptacles of the coupling element, is coupled in a rotationally fixed manner to the drive spindle, with the bottom surface in the area of the mouths of the two profile valleys being delimited by the spin
  • the screw pump according to the invention has a flow-optimized coupling or connection between the drive spindle and the coupling element.
  • the geometry of the coupling element is selected in such a way that the coupling element only slightly, if at all, reduces the conveying cross section of the respective profile valley at its mouth on the spindle end face, so that the free conveying cross section via the coupling element is almost unaffected and consequently the flow, seen in axial direction, this is not significantly affected, which leads to an improvement in the delivery rate.
  • a specifically designed coupling element which is disk-shaped and has two laterally open receptacles, in each of which a projection protruding axially on the end face of the drive spindle engages.
  • This form-fitting engagement enables a non-rotatable connection in one, preferably naturally in both, directions of rotation.
  • a recess on the front face of the spindle is defined by these axially protruding projections, which recess has a flat bottom surface, with the coupling element being inserted into precisely this recess.
  • the bottom surface of the recess is i.a. formed by the spindle core of the drive spindle because, as described, the two profile valleys open out at this end face.
  • the coupling element is designed in such a way that it is also rounded in the element areas adjacent to the mouth of the profile valleys, i.e. corresponding to the shape of the spindle core, with the diameter of the coupling element in the area of these rounded element sections also lying opposite one another corresponding at most to the diameter of the spindle core or smaller than the diameter of the spindle core.
  • This means that the diameter of the coupling element in relation to the spindle core diameter in the area of these element sections does not protrude into the free flow cross section of the respectively opening profile valley, so that the flow cross section is not necessarily reduced and the flow is not obstructed. Unlike those known from the prior art
  • the coupling element of the screw pump according to the invention no longer represents a significant flow obstacle.
  • the pumped fluid can therefore flow past the coupling element axially almost without obstacles, which is has an extremely beneficial effect on the pumping operation.
  • the coupling element has a cylindrical base section from which four element projections protrude to the side, with two adjacent element projections delimiting a lateral receptacle.
  • These element projections only serve to define or limit the form-fitting geometry, that is to say the receptacles, into which receptacles the axial projections on the spindle engage.
  • they only have a driver function, since they are used to effect the non-rotatable coupling in the circumferential direction. It is therefore possible to also design these element projections to be narrow in a flow-optimized manner, so that they also do not significantly reduce the flow cross section.
  • the end face of the drive spindle can be machined using two cross-grindings in such a way that corresponding, defined engagement geometries are provided in the correspondingly identically designed receptacles on the protruding projections that laterally delimit the recess and which, as described, continue the two spindle profiles axially.
  • the flat bottom surface of the recess is somewhat enlarged laterally, with the element projections covering these widening areas in this area, seen axially.
  • each socket can therefore extend relatively far into the cylindrical base area. which in turn means that the driver-like element projections protruding from the base area can be dimensioned correspondingly shorter.
  • the element projections themselves are expediently triangular and taper towards their free end, so they are very narrow overall and also relatively short.
  • each element projection can decrease towards its free end.
  • the material of the coupling element is consequently reduced as much as possible.
  • the insertion receptacle itself preferably has a square shape.
  • the insertion receptacle can have a rectangular, ie somewhat elongated shape, with its longer axis extending between the two rounded element sections and its shorter axis between the two receptacles.
  • This configuration enables an extremely compact, small-format configuration of the coupling element. This is because this alignment of the rectangular insertion receptacle makes it possible to pull the two quasi-V-shaped receptacles of the coupling element relatively far into the cylindrical base section. They end just before the insertion receptacle, which, as already described, ultimately means that the element projections on the coupling element side can be made short.
  • the coupling element itself can be made of plastic, i.e. a plastic component produced in an injection molding process from a plastic that has the desired mechanical and physical properties, e.g. in terms of its hardness, temperature resistance and the like.
  • the coupling element can also be made of metal, for example aluminum or steel.
  • the screw spindle pump also regularly has a drive motor or one is attached to it, which is placed axially on the outer housing and whose drive shaft is necessarily aligned axially with the longitudinal axis of the drive spindle.
  • the drive shaft engages in the insertion receptacle of the coupling element, which is also located centrally in the longitudinal axis of the drive spindle.
  • the operating principle of The screw pump is based on the fact that the fluid is conveyed axially, ie it leaves the spindle pack axially and flows past the coupling element, which, as stated, does not reduce the flow cross section or negligibly reduces it due to its geometry according to the invention.
  • the drive shaft on the motor side usually also has a cylindrical cross section, and the corresponding insertion geometry is formed at the end of the shaft, ie, for example, an engagement pin that is also quadrangular or rectangular. Since the conveyed fluid leaves the spindle pack axially, it flows past the coupling element as described, but then inevitably also on the drive shaft at least in the coupling area to the coupling element. In order to have no flow obstruction in the transition from the coupling element to the drive shaft, an expedient development of the invention provides a drive motor, the diameter of the cylindrical drive shaft of the drive motor corresponding at most to the diameter of the cylindrical spindle core.
  • the diameter is also matched here, so that it is ensured that the drive spindle cross-section, seen radially, does not engage in the flow cross-section of the drive spindle and reduces it, so to speak, retrospectively at the spindle-side outlet.
  • the diameter of the drive shaft can also be smaller than the spindle core diameter of the drive spindle, it can also correspond to the diameter of the cylindrical base section of the coupling element.
  • the screw pump can be a 2-screw pump, with a drive screw and only one idler screw positioned laterally thereto.
  • it can also be a 3-spindle pump, with a central drive spindle and two running spindles positioned to the left and right of it and meshing with it.
  • the invention also relates to the use of such a screw spindle pump in a motor vehicle for pumping an operating fluid.
  • This operating liquid can be fuel or another fluid such as a cooling fluid, for example for cooling a traction or drive battery, or another useful fluid such as a window cleaning fluid or the like.
  • Such screw pumps can also be used in other land or air vehicles such as airplanes or drones, although the possible uses are not limited to this.
  • the screw spindle pump is used as a coolant pump, in particular for pumping a coolant that serves to cool an energy store. It can be any coolant.
  • a screw pump 1 shows a screw pump 1 according to the invention, comprising an outer housing 2 with an inlet connection 3, which is arranged axially, and an outlet connection 4, which is arranged radially.
  • the outer housing 2 which can also be referred to as the pump housing, there is a spindle housing 5, in which three spindles, namely a central drive spindle 6 and two running spindles 7 arranged on both sides of the drive spindle 6, are accommodated in corresponding spindle bores that intersect one another .
  • the spindles 6, 7 each have spindle profiles that engage with one another, that is to say mesh with one another.
  • a drive motor 8 shown here only in principle, which can be a dry or wet-running drive motor.
  • This has a drive shaft 9 , shown here only in a stylized manner, which is connected in a torque-proof manner to the drive spindle 6 via a coupling element 10 .
  • a rotation of the drive spindle 6 inevitably also leads to a rotation of the two running spindles 7 due to the spindle profile engagement corresponding delivery volumes are moved or shifted axially, via which the fluid delivery takes place in a manner known per se.
  • the fluid is sucked in axially via the inlet connector 3, conveyed along the spindle assembly and emerges at the end of the spindle assembly on the engine side, from where it flows to the outlet connector 4 via a corresponding flow geometry.
  • the drive spindle 6 made of metal or plastic, has a spindle core 11 with a cylindrical cross section, around which two spindle profiles 12 run, so that corresponding profile valleys 13 are formed.
  • the drive spindle 6 has a depression 14, which is axially delimited by a flat bottom surface 15 and which is delimited laterally by two projections 16, these two projections 16 being formed as a kind of extension of the spindle profiles 12 running into the bottom surface 15 are.
  • the projections 16 are processed material-removing, which follows in connection with 4 will be discussed in more detail, so that overall a bottom surface 15 results, which on the one hand is formed in sections by the spindle core 11 and on the other hand due to the mechanical processing of the projections 16 by subsequent bottom sections, which will be discussed in more detail below.
  • the coupling element 10 also made of metal or plastic, is designed in the form of a disk, ie it has a defined, maximum thickness. It comprises a cylindrical base section 17 which has two opposing element areas 18 which are rounded. Furthermore, in the example 4 shown, element projections 19 protruding to the side are provided on the base section 17, which in each case define a V-shaped receptacle 20 between them, into which the projections 16 engage in the assembly position when the coupling element 10 is inserted into the recess 14 .
  • the bottom surface 15 is formed and bordered at least in sections by the cylindrical spindle core 11 .
  • This rounded boundary resulting from the cylindrical shape of the spindle core 11 is given at the mouth of the respective profile valley 13 since the profile valley is defined by the spindle core 11 .
  • the spindle core 11 has a core diameter D K that 3 is shown.
  • the coupling element 10 also has a disc-shaped, cylindrical base section 17, which has a base section diameter DB that is in 3 is also shown.
  • the design of the size or geometry of the coupling element 10 is now selected in such a way that the diameter of the base section 17 is smaller than or equal to the diameter of the spindle core; consequently DB ⁇ D K .
  • FIG. 4 shows a plan view of the end face of the drive spindle 6 with a view of the depression 14. Shown are the two profile valleys 13 that open out there, as well as the spindle core, which defines the rounded boundary of the bottom surface 15 in the opposite edge sections 21.
  • the end face is mechanically machined using corresponding cross-grindings, which on the one hand leads to an enlargement of the base area 15 over the spindle core area.
  • the coupling element 10 is shown in phantom.
  • the coupling element 10 is now used, the Figures 5 and 6 show a corresponding supervision ( figure 5 ) and a perspective view ( 6 ). Since the base section diameter D B corresponds at most to the core diameter D K , the rounded sections 18 of the coupling element 10 consequently do not protrude into the flow cross section defined by the spindle core 11, like the Figures 5 and 6 show clearly.
  • the element projections 19 each delimit two V-shaped, laterally open receptacles 20 which are defined by two contact surfaces 23 .
  • the receptacles 20 extend into the base section 17, they end just before an insertion receptacle 24, which is square or rectangular in cross section and is used to receive a correspondingly shaped engagement pin of the drive shaft 9.
  • the receptacles 20 accommodate the two projections 16 in a quasi-positive or form-fitting manner. Due to the abutment of the surfaces 22, 23 and the respective V-shaped engagement, a non-rotatable connection is given in both clockwise and counterclockwise rotation.
  • the element projections 19 extend from the base section 17, so that an X-shape results here as well, corresponding to the X-like shape of the depression or the bottom surface 15.
  • the element projections 19 also ultimately do not protrude into the mouth cross section of the respective profile valley 13 the end face, so that consequently the coupling element 10 is no or almost no flow obstacle for the fluid flow. Only the in figure 5
  • the element projection 19 shown at the top right and bottom left protrudes slightly into the flow cross section, but its obstacle function is negligible.
  • the element projections 19 taper towards their free end, they also decrease in thickness towards their free end. It Corresponding inclined surfaces or chamfers are formed on both sides, so that an inverted assembly is also possible without any problems.
  • FIG. 7 shows an exploded view of the inner housing 5 of a screw pump with only two spindles, namely again a drive spindle 6 and only one idler spindle 7, compared with the 3-spindle embodiment according to the preceding figures.
  • This serves to show that a clutch according to the invention can be provided both in a 3- and in a 2-spindle screw pump 1 .
  • an identical coupling element 10 is inserted into this recess 14 .
  • the drive shaft 9 of the drive motor with the insertion pin 25 at the end, which engages in the insertion receptacle 24 in a form-fitting manner.
  • the insertion pin 25 engages in the insertion receptacle 24, while the coupling element 10 is set in the recess 14 at the same time.
  • a rotation of the drive shaft 9 therefore inevitably leads, coupled via the coupling element 10, to a rotation of the drive shaft 6 and, via this, also the running spindle 7, so that the pump can deliver the fluid.
  • Such a screw pump can be used to convey a wide variety of fluids. It is preferably used in the motor vehicle sector and there either as a fuel pump or as a feed pump for another operating fluid, in particular for a coolant that is used to cool an energy store in the motor vehicle.
  • the energy store is a large-volume traction store of an electric vehicle. So it is a coolant pump.
  • a feed pump for a washing fluid that is used to wipe the windshield of the vehicle or the like.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
EP22209989.7A 2021-12-14 2022-11-28 Pompe à vis Pending EP4198310A1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102021133099.8A DE102021133099A1 (de) 2021-12-14 2021-12-14 Schraubenspindelpumpe

Publications (1)

Publication Number Publication Date
EP4198310A1 true EP4198310A1 (fr) 2023-06-21

Family

ID=84363936

Family Applications (1)

Application Number Title Priority Date Filing Date
EP22209989.7A Pending EP4198310A1 (fr) 2021-12-14 2022-11-28 Pompe à vis

Country Status (6)

Country Link
US (1) US11828287B2 (fr)
EP (1) EP4198310A1 (fr)
JP (1) JP7457093B2 (fr)
KR (1) KR20230090269A (fr)
CN (1) CN116263154A (fr)
DE (1) DE102021133099A1 (fr)

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4308755A1 (de) 1993-03-19 1994-09-22 Leistritz Ag Klauenkupplung für eine Schraubenpumpe und Verfahren zu ihrer Herstellung
WO2014138519A1 (fr) * 2013-03-07 2014-09-12 Ti Group Automotive Systems, L.L.C. Élément d'accouplement pour pompe à vis
DE102015101443B3 (de) 2015-02-02 2016-05-12 Leistritz Pumpen Gmbh Kraftstoffpumpe
DE102020108038A1 (de) * 2020-03-24 2021-09-30 Nidec Gpm Gmbh Elektrische schraubenspindelpumpe für flüssigkeiten

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2466888A (en) * 1945-10-03 1949-04-12 Porter Co Inc H K Floating spacer bearing link for parallel shafts
SE384069B (sv) * 1975-05-02 1976-04-12 Imo Industri Ab Skruvpump
US4308755A (en) * 1979-06-25 1982-01-05 Millar Robert J Liquid volumetric flowmeter
US4674338A (en) * 1984-12-31 1987-06-23 Lake Charles Instruments, Inc. Flow volume detection device
US4848164A (en) * 1988-05-27 1989-07-18 Graco Inc. Liquid flow meter
US8821140B2 (en) * 2010-04-29 2014-09-02 Dan Paval Gear pump
DE102017210770B4 (de) * 2017-06-27 2019-10-17 Continental Automotive Gmbh Schraubenspindelpumpe, Kraftstoffförderaggregat und Kraftstofffördereinheit
DE102017121882B3 (de) * 2017-09-21 2019-01-24 Leistritz Pumpen Gmbh Schraubenspindelpumpe
DE102019103470A1 (de) * 2019-02-12 2020-08-13 Nidec Gpm Gmbh Elektrische Schraubenspindel-Kühlmittelpumpe
DE102019132653A1 (de) * 2019-12-02 2021-06-02 Leistritz Pumpen Gmbh Schraubenspindelpumpe
DE102020104467A1 (de) * 2020-02-20 2021-08-26 Krauss-Maffei Wegmann Gmbh & Co. Kg Haltevorrichtung für Munitionskörper
DE102020133555A1 (de) * 2020-12-15 2022-06-15 Leistritz Pumpen Gmbh Schraubenspindelpumpe

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4308755A1 (de) 1993-03-19 1994-09-22 Leistritz Ag Klauenkupplung für eine Schraubenpumpe und Verfahren zu ihrer Herstellung
WO2014138519A1 (fr) * 2013-03-07 2014-09-12 Ti Group Automotive Systems, L.L.C. Élément d'accouplement pour pompe à vis
DE102015101443B3 (de) 2015-02-02 2016-05-12 Leistritz Pumpen Gmbh Kraftstoffpumpe
DE102020108038A1 (de) * 2020-03-24 2021-09-30 Nidec Gpm Gmbh Elektrische schraubenspindelpumpe für flüssigkeiten

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DE102021133099A1 (de) 2023-06-15
US11828287B2 (en) 2023-11-28
JP2023088303A (ja) 2023-06-26
KR20230090269A (ko) 2023-06-21
JP7457093B2 (ja) 2024-03-27
CN116263154A (zh) 2023-06-16

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