EP4198311A1 - Pompe à vis - Google Patents

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Publication number
EP4198311A1
EP4198311A1 EP22209992.1A EP22209992A EP4198311A1 EP 4198311 A1 EP4198311 A1 EP 4198311A1 EP 22209992 A EP22209992 A EP 22209992A EP 4198311 A1 EP4198311 A1 EP 4198311A1
Authority
EP
European Patent Office
Prior art keywords
spindle
housing
cover component
fluid
screw
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
EP22209992.1A
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 EP4198311A1 publication Critical patent/EP4198311A1/fr
Pending legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/10—Outer members for co-operation with rotary pistons; Casings
    • F01C21/104—Stators; Members defining the outer boundaries of the working chamber
    • F01C21/108—Stators; Members defining the outer boundaries of the working chamber with an axial surface, e.g. side plates
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0003—Sealing arrangements in rotary-piston machines or pumps
    • F04C15/0007—Radial sealings for working fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • 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
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/06—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • 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
    • F04C2/082—Details specially related to intermeshing engagement type machines or pumps
    • F04C2/086—Carter
    • 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
    • F04C2210/00—Fluid
    • F04C2210/20—Fluid liquid, i.e. incompressible
    • 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
    • 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
    • F04C2240/40—Electric motor
    • 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
    • F04C2240/80—Other components
    • F04C2240/805—Fastening means, e.g. bolts
    • 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
    • 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
    • F05B2260/00—Function
    • F05B2260/30—Retaining components in desired mutual position

Definitions

  • the invention relates to a screw spindle pump, with a spindle housing in which a drive spindle and at least one running spindle meshing with it are accommodated in spindle bores, and an outer housing enclosing the spindle housing.
  • Such a screw pump is used to deliver a fluid, for example fuel or a supply or cooling liquid or the like, as required in a motor vehicle.
  • a fluid for example fuel or a supply or cooling liquid 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 conveying takes place via at least two intermeshing spindles, namely a drive spindle which is coupled to a drive motor and a running spindle, both of which are accommodated in a spindle housing.
  • the spindle housing has several intersecting spindle bores corresponding to the number of spindles.
  • the spindle housing is accommodated in an outer or pump housing, via which the fluid to be pumped is supplied and removed.
  • the functional principle of the screw pump is based on the fact that the drive spindle and the idler spindle mesh with each other with their spindle profiles and a delivery volume is shifted axially due to the spindle rotation.
  • the drive spindle has a cylindrical spindle core and usually two spindle profiles running around the spindle core. Circumferential profile valleys are formed via these spindle profiles, into which the corresponding spindle profiles of the idler spindle engage, and vice versa.
  • the fluid to be pumped is fed to the screw spindle pump via an inlet provided on the outer housing on the suction side, which is usually designed as a connecting piece, while the pumped, pressurized fluid is supplied on the pressure side via a corresponding outlet provided on the outer housing, also designed as a connecting piece , is carried away.
  • Corresponding lines of the fluid circuit, in which the screw pump is connected are to be connected to the inlet and the outlet, ie the respective connection piece. It often happens that the line ends to be connected to the inlet and the outlet are provided in certain positions that are not flexible, for example due to the installation space situation, which in turn means that the inlet connection piece and the outlet connection piece must of course also be positioned appropriately on the pump side in order to make the connections close.
  • the outer housing is usually a pot-like, one-piece component, usually a cast or injection-molded component or a 3D printed part, on which the corresponding sockets are formed in a fixed position.
  • a varying connection geometry of the assembly environment therefore means that different outer housings, into which the spindle housing is inserted, must be available for different assembly situations. This is expensive.
  • the invention is therefore based on the problem of specifying a screw pump that is improved in comparison thereto.
  • a screw spindle pump is provided according to the invention, with a spindle housing in which a drive spindle and at least one running spindle meshing with it are accommodated in the spindle bores, an outer housing enclosing the spindle housing, and a cover component placed axially on the outer housing, on which both an axial Fluid inlet connection, a lateral fluid outlet connection is also provided, the fluid inlet connection communicating with a fluid inlet of the spindle housing and the fluid outlet connection communicating with a fluid outlet of the spindle housing, the cover component in can be fastened to the outer housing in a number of excellent rotational positions with a first pitch, and wherein the spindle housing can be fastened to the cover component and/or in the outer housing in a number of excellent rotational positions with a second, smaller pitch.
  • the screw pump according to the invention makes it possible with particular advantage to be able to arrange the fluid inlet connection and the fluid outlet connection in different spatial positions, combined with the possibility of aligning the spindle housing in a spatial orientation that is advantageous for the conveying process, in which, for example, the longitudinal axes of the spindles lie in a horizontal plane. to be placed in the outer casing.
  • the outer housing is open on both axial sides. While the drive motor is placed on one axial side and closes it, which drive motor is coupled to a drive shaft via a clutch with the drive spindle for actively driving the same or the spindle pack, the other side of the outer housing is closed via a cover component. Both the fluid inlet connection and the fluid outlet connection are now provided on this cover component.
  • the fluid inlet connection is directed axially, while the fluid outlet connection is directed to the side and is at an angle of 90° to the inlet, for example. This means that the cover component closes the outer housing on the one hand, but has both connection points on the other hand.
  • connection modifications are provided on the outer housing itself, that is to say the component which is open on both sides and is approximately quasi-hollow-cylindrical, so that this can be designed in a relatively simple manner.
  • this also applies to the cover component, which is a relatively narrow component and, particularly if it is made of plastic, can be equipped with the appropriate connecting piece without any problems.
  • the cover component is in different, defined twisted positions with the outer housing connectable. These marked, defined twisted positions have a first pitch. This means that the cover component can be attached to the outer housing in different defined positions rotated about the longitudinal axis of the outer housing. The result of this is that the laterally protruding fluid outlet connection can inevitably be brought into different circumferential positions.
  • a second rotation possibility is also provided, i.e. a second rotational degree of freedom.
  • the spindle housing can also be fastened in different, distinct twisted positions either on the cover component or on the outer housing or on both. These excellent rotational positions with respect to the spindle housing have a second division, this division being smaller than the first division in which the cover component can be fastened.
  • the spindle housing is always to be positioned in such a way that the longitudinal axes of the spindles accommodated therein lie approximately in a horizontal plane, the spindle housing can be inserted into the outer housing in relation to the final assembly position in such a way that this horizontal alignment can be assumed.
  • the screw spindle pump offers a high degree of flexibility with regard to the positioning, in particular of the radial or laterally projecting fluid outlet connection. Because on the one hand there is the possibility of carrying out a rough alignment of the laterally protruding fluid outlet connection in relation to the assembly position by appropriately positioning the cover component in a required twisted position. Then, by appropriate positioning of the spindle housing in a preferred twisted position in the outer housing or attachment of the spindle housing, resulting from the smaller second division, quasi a Fine positioning of the laterally projecting fluid outlet connection can be made.
  • the screw pump according to the invention thus offers the possibility, on the one hand, of very flexible spatial positioning of the laterally or radially projecting fluid outlet connection in the circumferential direction, and on the other hand of the possibility of arranging the spindle housing with the spindles in a correspondingly spatially oriented manner for the best possible pump operation.
  • the first and the second pitch differ, the second pitch is smaller than the first pitch.
  • the first pitch is preferably 90°, while the second pitch is 45°.
  • the cover assembly can be attached to the outer case in four distinct positions, namely 0°, 90°, 180° and 270°.
  • the spindle housing can be arranged and fixed in eight excellent rotational positions relative to the outer housing or cover component, namely 0°, 45°, 90°, 135°, 180°, 225°, 270° and 315°.
  • the fluid outlet port can also be located in eight distinct final circumferential positions that correspond to the angular positions described with respect to the second division, assuming that the spindle housing is positioned so that the longitudinal axes of the spindle are in common horizontal plane. Since a certain slight tilting of the horizontal plane of the spindle axes is of course also possible without this having an overly negative effect on the conveying operation, for example a tilting by a maximum of 10° on both sides, it is inevitable that far more corresponding circumferential positions on the part of the Fluid outlet port can be accepted and thus this can be optimally aligned with respect to the port modification of the line to be connected.
  • the screw spindle pump is designed as a 2-spindle pump, comprising only one drive spindle and a running spindle arranged parallel and to the side, it is of course also possible to design the screw spindle pump as a 3-spindle pump, with a central drive spindle and two running spindles arranged on both sides, offset by 180° and both meshing with the drive spindle.
  • the drive spindle and the one or both running spindles are expediently supported axially on the suction side, ie adjacent to the fluid inlet connection.
  • a support component arranged on the cover is provided in a further development of the invention, on which all spindles are supported axially or against which they can run for axial support.
  • Such a support is also expediently provided on the opposite side of the spindle housing, and corresponding support means can also be provided there at least for the two running spindles, since the drive spindle is ultimately supported axially on the drive shaft of the drive motor.
  • the support component provided on the suction side, adjacent to the fluid inlet connection is a feather key which, according to the invention, can be positioned in different defined twisted positions with the second division on the cover component.
  • This feather key moves with the spindle housing and is therefore also horizontal if the spindle housing is to be aligned horizontally, for example, as described.
  • This variable arrangement of the feather key consequently always ensures optimum spindle support on the suction side.
  • Receiving grooves are preferably provided on the cover component corresponding to the various twisted positions, into which the elongated feather key can be used. These elongated grooves are arranged in a star shape, with one receiving groove always being positioned horizontally or approximately horizontally, depending on the orientation of the cover. Since these grooves, as described, are positioned according to the second division, in which the spindle housing can also be arranged, the key and spindle housing or spindles are always positioned or aligned in the same way.
  • the feather key is preferably clamped in the respective receiving groove, which means that the feather key has a slight oversize relative to the dimension of the feather key, so that a clamped fixation, which can also be a snap fixation, is ensured.
  • the spindle housing can be fixed either only or at least additionally also on the cover component in the plurality of twisted positions corresponding to the second division.
  • several first fastening means are provided on the cover component, positioned according to the second division, which can be connected to second fastening means provided on the spindle housing.
  • first and second fastening means are provided both on the cover component side and on the spindle housing side, which interact with one another only in the corresponding twisted positions and enable the spindle housing to be fastened to the cover component in a particularly torsion-proof manner.
  • the first fastening means can be depressions formed on the cover component, into which axial projections provided as second fastening means on the spindle housing engage. This means that ultimately a depression geometry corresponding to the second division is formed on the cover housing. If, for example, two axial projections arranged by 180° are provided as second fastening means on the spindle housing, then two depressions offset by 180° from one another are also provided on the cover component in the respective division, but two in each defined rotational position, i.e. with a 45° division a total of eight pairs of indentations. By the axial engagement of the projections in the recesses a torsion-proof, form-fitting connection is readily possible. On the other side, the spindle housing is of course also supported axially, for example on a corresponding stop on the outer housing or on a stop on the motor housing or an intermediate plate or the like.
  • first and second fastening means in the opposite way.
  • a plurality of axial projections are provided on the cover component as the first fastening means, which are arranged in pairs and offset from one another by 180° opposite one another in the corresponding defined twisted positions on the cover component.
  • the second fastening means are axial depressions provided on the end face of the spindle housing, which are positioned offset from one another by 180° and into which two projections on the cover component engage.
  • the attachment of the spindle housing to the cover component is an attachment variant.
  • the spindle housing can be fastened to the outer housing in the corresponding, marked rotational positions of the second division.
  • first fastening means positioned according to the second division, on or in the outer housing, which can be connected to second fastening means provided on the spindle housing. This means that corresponding first and second fastening means, which interact with one another for torsion-proof fixing, are also provided with respect to this connection plane.
  • first fastening means be radially open receptacles which engage in radially directed projections which are provided on the spindle housing and serve as second fastening means.
  • first fastening means to be radially open receptacles which engage in radially directed projections which are provided on the spindle housing and serve as second fastening means.
  • the springs can be pushed axially into the grooves, which is used to secure them against twisting.
  • Form fastening means in the reverse manner, that is, that the first fastening means are radially directed projections, which engage in the spindle housing, serving as a second fastening means radially open receptacles provided.
  • the spindle housing, the outer housing and/or the cover component from metal.
  • the cover component is expediently sealed against the spindle housing by a first sealing element and against the outer housing by a second sealing element.
  • a first axial receiving groove can be provided on the cover component or on the spindle housing, in which the first sealing element is inserted, while a second radial receiving groove is provided on the outer housing or on the cover component, in which the second sealing element is inserted.
  • the spindle housing has an axial fluid outlet for the fluid conveyed through the spindle housing via the drive spindle and the running spindle, which communicates with a fluid chamber that is formed between the spindle housing and the outer housing and extends through 360° in turn communicates with the radial fluid outlet of the cover member.
  • the pressurized fluid exits the Spindle housing axial, i.e. in the longitudinal direction of the spindle longitudinal axes. This is expedient in order to reduce or avoid disruptive flow noise.
  • this embodiment provides that the pressurized fluid is then conducted into a fluid chamber which is formed between the spindle housing and the outer housing and which extends 360° around the spindle housing.
  • this fluid chamber is filled with the fluid at the pump or outlet pressure.
  • the fluid exerts a radially inward pressure on the spindle housing.
  • This has the particular advantage that the spindle housing is radially prestressed, so that this fluid pressure can counteract any geometry changes of the spindle housing or tolerances resulting from the pump operation or the internal pressure in the spindle housing. Consequently, in no case does the spindle housing expand slightly, which would have a negative effect on the efficiency.
  • a pressure jacket is formed around the spindle housing by means of this fluid chamber, which can also be referred to as a pressure chamber.
  • this fluid chamber should extend over at least half the length of the spindle bore or the spindle housing, so that there is a correspondingly large overlap and the radial preload is given over as large an area as possible.
  • a chamber length that extends over about 2/3 of the spindle housing or over the entire length of the spindle housing is easily conceivable.
  • an intermediate component placed axially on the outer housing can be provided, which is designed for connecting a drive motor, one or more deflection cavities being provided on the intermediate component, which deflect the fluid coming from the fluid outlet to the fluid chamber.
  • This intermediate component quasi forms the assembly interface for the drive motor or the motor housing and is preferably designed in the form of a plate and is arranged between the motor housing and the outer housing. On the one hand, it has a hole through which the drive shaft of the Drive motor is guided towards the drive spindle. This hole can also serve as a shaft bearing.
  • a shaft sealing ring can be provided in the bore, via which sealing takes place there, so that no pumped fluid can penetrate into the motor.
  • the motor is therefore designed as a dry runner. If no shaft sealing ring is provided there, a certain proportion of the fluid can flow axially along the drive shaft into the motor to cool it and recirculate again, the motor then being designed as a wet-running motor.
  • one or more deflection cavities are provided on the intermediate component, which forms the axial closure of the interior of the outer housing on the pressure side, which allow the fluid flowing axially out of the spindle housing to flow radially outwards on the one hand and back into the axis on the other hand to guide the fluid chamber surrounding the spindle housing. From this fluid chamber, the fluid then reaches the area of the cover-side fluid outlet connection, ie it communicates with this, where the fluid is then discharged.
  • the motor housing directly on the outer housing, ie to connect the two directly to one another.
  • a corresponding base plate of the motor through which the drive shaft is guided, would form the axial closure of the interior of the outer housing and consequently of the interior of the pump.
  • a shaft sealing ring can be provided, or an axial flow of the fluid for motor cooling can be possible.
  • the base plate of the motor housing has one or more deflection cavities, since, as stated, it forms the axial housing closure.
  • only one deflection cavity is provided, which is designed as an annular groove or cup-shaped depression that is rounded in the area of the bottom of the groove or depression.
  • the pressurized fluid flows into the groove or indentation and is guided radially outwards via the rounded groove or indentation geometry on the one hand, but also on the other guided axially back into the fluid chamber.
  • This rounded design and the avoidance of corners or edges in turn allow for the quietest possible pump operation, since no flow noises arise in the deflection area either.
  • the invention also relates to the use of such a screw pump in a motor vehicle for pumping an operating fluid.
  • the screw pump can be used for different purposes.
  • it can be used to convey a cleaning fluid, such as a windshield wiper fluid, accordingly.
  • It is preferably used as a coolant pump, i.e. it pumps a coolant.
  • the coolant can be any fluid coolant.
  • the focus here is in particular on conveying a coolant for cooling an energy store.
  • Modern electrically operated motor vehicles have an appropriately dimensioned energy store, ie an appropriately dimensioned traction battery, which heats up during operation and must be cooled accordingly. You must therefore be supplied with an appropriate coolant, which is easily possible by using the screw pump according to the invention, since the screw pump is able to circulate a high flow rate with a correspondingly high pressure.
  • FIG. 1 shows a screw pump 1 according to the invention, with a spindle housing 2, in which two spindles, namely a drive spindle 3 with a spindle profile and a running spindle 4 with a spindle profile, are accommodated in the exemplary embodiment shown. Both spindle profiles or spindles mesh with one another in a manner known per se.
  • This spindle package is driven via the drive spindle 3, which is coupled to a drive motor or its drive shaft, which is not shown in detail here.
  • a coupling element 5 with an insertion receptacle 6 for a coupling pin of the drive shaft is used for this purpose, the coupling element 5 being coupled to the drive spindle 3 in a rotationally fixed manner.
  • the drive motor is placed on or on an outer housing 7 and screwed to it, with the quasi-hollow-cylindrical outer housing 7, such as 1 shows, the spindle housing 2 accommodates completely.
  • the outer housing 7 is closed on this side via the drive motor or the motor housing, which is not shown in detail.
  • a cover component 8 is placed axially onto the outer housing 7, which closes the outer housing 7 and thus the interior of the pump on this side.
  • the cover component 8, preferably a plastic component has an axial fluid inlet connection 9, which means that the fluid to be conveyed is sucked in or introduced axially onto this suction side. It also has a fluid outlet port 10 that protrudes to the side, that is to say rotated here by 90° to the fluid inlet port 9, and via which the pressurized fluid is discharged to the side.
  • connection between the outer housing 7 and the drive motor or the motor housing is appropriately sealed via one or more sealing elements
  • connection of the cover component 8 to the outer housing 7 and to the spindle housing 2 is also sealed.
  • an annular flange 11 with an axial receiving groove 12 is provided on the cover component 8, in which a first sealing element, which is not shown in detail here, is to be arranged.
  • This sealing element seals axially towards an annular flange 13 of the spindle housing 2 .
  • the sealing to the outer housing 7 also takes place via a sealant, not shown in detail, which is accommodated in a radially open receiving groove 14 formed on the outer housing 7, with this receiving groove 14 being overlapped radially by a flange 15 of the cover component 8. In this way, a complete seal is achieved on the one hand of the outer housing 7, but on the other hand also of the spindle space, so that the pressurized volume can no longer flow back into the suction area.
  • a fluid chamber 16 which encompasses the spindle housing 2 by 360° and into which the fluid exiting the spindle housing 2 axially, i.e. in the direction of the drive motor, is deflected and enters.
  • the fluid outlet on the spindle housing side communicates with the fluid chamber 16 .
  • the fluid chamber 16 in turn communicates with the fluid outlet port 10,
  • a corresponding opening 17 is provided on the cover component 8, as in FIG 3 shown. This opening 17 is open to the fluid chamber 16 .
  • the fluid is already under pressure in the fluid chamber 16 so that the fluid can exert a corresponding pressure on the circumference of the spindle housing 2 , which is made of plastic, for example, which counteracts any change in geometry of the spindle housing 2 .
  • the two spindles 3, 4 are axially on the suction side, i.e. on the cover part 8, via a support component 18, here a feather key 19 (see 3 ) supported axially, so that a defined abutment is formed here.
  • the drive spindle 3 is supported on the drive shaft on the one hand, and the running spindle 4 is supported axially on the other hand on a corresponding support element 20 which is formed here on a corresponding web 21 of the spindle housing 2 .
  • the bearing for the drive shaft is also provided or, if the spindle housing is made of plastic, directly molded.
  • the bearing accommodating the drive shaft is aligned exactly with the central axis of the spindle bore accommodating the drive spindle, so that there are no tolerances between the drive shaft bearing and the spindle axis and thus within the coupling of the two components. As a result, there are no imbalances, which means that the spindles run very smoothly and silently.
  • the Figures 2 and 3 show the cover component 8 in different views.
  • 2 shows a perspective view of the outside, showing on the one hand the central axial fluid inlet connection 9 and the fluid outlet connection 10 protruding to the side and here running quasi tangentially.
  • Corresponding openings 22 are provided in the four corners of the basically square cover component 18 , through which corresponding fastening screws are passed, which are screwed into corresponding internally threaded bores 23 provided on the outer housing 7 .
  • the bores 22 and the internally threaded bores 23 are positioned at a first pitch, a 90° pitch. This means that the cover component 8 can be rotated in four distinct positions on the outer housing 7, provided it stays in position, it can be fixed in a 0°, 90°, 180° and 270° position.
  • the fluid outlet port 10 projects, viewed from the outside, either obliquely to the top left, obliquely to the top right, obliquely to the bottom right or obliquely to the bottom left, while the axial fluid inlet port remains in its position in the middle.
  • this configuration resulting from the fact that both the fluid inlet connection 9 and the fluid outlet connection 10 are arranged on one cover component 8, means that there are basically four distinct rotational positions of the cover component 8 and thus also of the fluid outlet connection 10.
  • the outer housing 7 can be rotated around the spindle housing 2 in more or less 45° steps, together with the cover component 8 that is attached to it, but of course also the cover component 8 in turn in the four defined rotating positions on the outer housing described above 7 can be attached.
  • the fluid outlet connection 10 protruding to the side here to be positioned in a total of eight different defined spatial positions or circumferential positions, namely at 0°, 45°, 90°, 135°, 180°, 225°, 270° and 315° .
  • FIG. 3 shows the possibility of how the feather key 19 can be arranged on the cover component 8 according to the rotation, which yes, if the spindle assembly is to remain horizontal, must be fixed in different positions in the cover component 8 when the cover component 8 is rotated.
  • four receiving grooves 24 are provided on the cover component 8 in a quasi-star-shaped arrangement, into which the elongate feather key 19 can be inserted, the feather key 19 being expediently fixed in the receiving grooves 24 by clamping.
  • the four receiving grooves 24 are arranged in a 45° division, so their division corresponds to the second division, in which the spindle housing 2 can also be arranged. This means that the feather key can be rotated in 45° steps about the central axis or the cover component 8 can be rotated in 45° steps relative to the feather key 19 when the feather key 19 is in a fixed position.
  • indentations 25 which are formed on the inner wall surface of the cover component 8, the indentations 25 between the corresponding groove sections also being arranged according to the second division, ie in 45° steps. Accordingly, eight indentations 25 are provided equidistantly offset in the circumferential direction. These indentations 25 serve to accommodate corresponding axial projections which are formed on the spindle housing 2 and which therefore engage in the indentations 25, by means of which the anti-twist protection and position fixing takes place.
  • FIGs 4 and 5 show two corresponding examples of arrangement, with the outer housing 7 remaining in its position, but with the lid component 8 seen at 90° counterclockwise between 4 and 5 is positioned twisted.
  • the cover component 8 is in 4 shown partially open. In fact, it is of course axially closed except for the fluid inlet 9 .
  • the feather key is indicated by dashed lines.
  • In 4 shows the fluid outlet connection 10 protruding upwards to the right.
  • the feather key 19 is located in a first receiving groove 24.
  • the spindle housing 2 together with the drive spindle 3 and the idler spindle 4 is in a horizontal arrangement and remains in this position.
  • Each axial projection 26 engages in a depression 25 in the assembly position, so that there is a form fit, so to speak, or the cylindrical projections 26 are in contact with the corresponding lateral walls of the depressions 25 . This provides a non-rotating connection between the spindle housing 2 and the cover component 8 .
  • FIG 5 shows screw pump 1 4 , whereby here the cover component is turned 90° to the left.
  • the fluid outlet port 10 protrudes to the top left.
  • the feather key 19 is accommodated in a second receiving groove 24 which is offset by 90° to the receiving groove 24 in which the feather key 19 in the arrangement according to FIG 4 was recorded.
  • the axial projections 26 in turn engage in corresponding depressions 25, but in the respective, according to the arrangement 4 Indentation 25 offset by 90°.
  • the spindle housing 2 has an axially extending portion in which the spindle bores are formed, and a terminal and radially extending flange portion on which the projections 26 are provided, such as 6 clearly shows.
  • Four projections 26 are provided, which are positioned on the cover component 8 in the arrangement angle corresponding to the division of the depressions 25 . These projections 26 engage in the depressions 25 as described.
  • the Figures 7-14 also show the possibility of being able to set intermediate positions between the four excellent cover component positions. This is possible because the combination of the outer housing 7 and the cover component 8 can be rotated in 45° steps around the fixed spindle component 2 . At the same time, as described, the feather key 19 moves along in the corresponding 45° steps, just as the spindle housing 2 is of course also fixed in position in each 45° position via the corresponding engagement of the axial projections 26 in the recesses 25 .
  • Shown here is a top view of the inside of the cover component 8, showing the feather key 19 and, in broken lines, the spindles 3, 4, which are axially supported on the feather key 19.
  • These views clearly show the gradual turning of the cover component 8 relative to the spindle housing 2 and the spindles 3, 4 and the repositioning of the key 19, as well as the fact that the spindles can remain in their preferred position despite changing the connection position.
  • the outer housing 7 also rotates, which is not shown here for reasons of clarity.
  • the outer housing 7 together with the cover component 8 is positioned at 45° relative to the spindle housing 2 or the spindles 3, 4, which always remain in the horizontal orientation. This is made possible by inserting the feather key 19 through 45° into the next receiving groove 24 and rotating the cover component 8 together with the outer housing 7 through 45° around the spindle housing 2 .
  • the projections 26 engage at 45° to the situation according to FIG 7 offset depressions 25, so that this 45 ° position is fixed.
  • FIG. 10 shows the cover component 8 by a further 45° starting from the arrangement 9 twisted.
  • the outer housing 7 together with the cover component 8 is rotated by 45° relative to the spindle assembly while at the same time the feather key 19 is displaced by a further 45° into the next receiving groove 24.
  • the spindle housing 2 is fixed in the different twisted positions on the cover component 8 via the engagement of the axial projections 26 in the corresponding depressions 25.
  • a schematic representation of such a possibility is shown 15 .
  • the outer housing 7 and the spindle housing 2 with its spindle bores 27 which intersect one another are shown here purely in principle. Three intersecting spindle bores are shown here as an example, which means that a 3-spindle screw pump 1 is shown here.
  • a plurality of radially inwardly projecting projections 28 are provided corresponding to the second 45° division, i.e. a total of eight such projections 28 with a 45° division
  • two receiving grooves 29 are provided, opposite one another by 180°, each receiving a projection 28 in the respective assembly position. If the spindle housing 2 is placed in the outer housing 7, when the axial end position is reached, two projections 28 lying opposite one another by 180° are inserted into the receiving grooves 29, by means of which the fixing and anti-twist protection is realized. It is therefore a tongue and groove arrangement. There does not have to be a longer engagement when viewed axially, since the spindle housing 2 or the spindles 3, 4 are supported axially on both sides.
  • FIG. 16 finally shows a further embodiment of a screw pump 1, in which a drive motor 30 is attached to the outer housing 7 and fixed there. This is done via screw connections, not shown in detail, which pass through the corresponding bores and engage in internally threaded bores on the opposite component. Otherwise, the screw spindle pump 1 again has a cover component 8 on which the fluid inlet connection 9 and the fluid outlet connection 10 projecting to the side, radially or tangentially are provided.
  • the spindle housing 2 is also shown, in which the central drive spindle 3 and two lateral running spindles 4, which are shown here vertically one above the other for reasons of clarity, are accommodated. As described, the spindles 3, 4 mesh with each other.
  • the drive spindle 4 is connected to the drive motor 30 via a drive shaft 31 on the motor side, which engages with an insertion pin 32 in the coupling element 5 already described, which is coupled to the drive spindle 3 in a torque-proof manner.
  • About the drive spindle 3 is supported axially.
  • the spindles 4 are not shown in detail, but already closed 1 manner described axially supported.
  • the key 19 for axial support of all three spindles 3, 4 is located on the opposite suction side.
  • the fluid chamber 16 which surrounds the spindle housing 2 on all sides by 360°.
  • the fluid chamber 16 communicates with the axial fluid outlet of the spindle housing 2.
  • the fluid flowing out of the spindle housing 2 first reaches a corresponding deflection cavity 33, which is in 16 Schematic representation shown is provided on a base plate of the motor housing 34, but which can also be provided on an intermediate component 35, shown here in dashed lines because it is optional, which is plate-shaped and ultimately offers a separate assembly interface for the drive motor 30.
  • This deflection cavity which is designed here as a cup-shaped depression or annular groove, has a rounded depression or bottom surface 36.
  • the inflowing fluid is deflected radially outwards here on the one hand and flows through corresponding openings 37, which are provided on a radial flange 38 of the spindle housing 2 , Axially back into the annular fluid chamber 16, in which the pump pressure thus inevitably builds up. This weighs on the spindle housing 2 so that it is stabilized and its geometry cannot change due to pressure or operation.
  • the fluid chamber 16 communicates with the fluid outlet connection 10 so that the pressurized fluid can be drawn off via this.
  • the deflection cavity 33 can also be connected to the fluid chamber 16 in a way other than via the openings 37 in the radial flange 28 .
  • no radial flange is provided at this end if the spindle housing is radially supported elsewhere, or only a few radial projections are provided which provide support to the outer housing 7, or the like.
  • the drive motor 30 can be either a dry-running or a wet-running type. If it is a dry runner, the drive shaft 31 shown here only stylized of the drive motor 30 shown only stylized here is accommodated in a shaft sealing ring so that no fluid can flow along the drive shaft 31 and get into the drive motor 30 . The rest of the sealing on this side takes place via the motor wall or the intermediate component 35. If it is a wet rotor that is to be cooled via the fluid, there is no shaft sealing ring around the drive shaft 31 so that the fluid can flow along it.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
EP22209992.1A 2021-12-14 2022-11-28 Pompe à vis Pending EP4198311A1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102021133114.5A DE102021133114A1 (de) 2021-12-14 2021-12-14 Schraubenspindelpumpe

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EP4198311A1 true EP4198311A1 (fr) 2023-06-21

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US (1) US20230184249A1 (fr)
EP (1) EP4198311A1 (fr)
JP (1) JP7457092B2 (fr)
KR (1) KR20230091044A (fr)
CN (1) CN116263155A (fr)
DE (1) DE102021133114A1 (fr)

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KR102652394B1 (ko) * 2022-11-15 2024-03-29 주식회사 코아비스 밸브 일체형 펌프 장치

Citations (2)

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Publication number Priority date Publication date Assignee Title
DE102013102031A1 (de) * 2013-03-01 2014-09-04 Netzsch Pumpen & Systeme Gmbh Aus wenigstens zwei Teilen gebildete Schraubenspindelpumpe
DE102019128602B3 (de) * 2019-10-23 2021-02-11 Leistritz Pumpen Gmbh Schraubenspindelpumpe

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Publication number Priority date Publication date Assignee Title
US3269328A (en) * 1964-09-28 1966-08-30 Laval Turbine Screw pumps or motors
US6152719A (en) 1997-09-18 2000-11-28 Roper Pump Company Gear pump having an inlet port aligned with the drive shaft
DE102005025816B4 (de) 2005-06-02 2010-06-02 Joh. Heinr. Bornemann Gmbh Schraubenspindelpumpe
US20110103987A1 (en) * 2009-11-04 2011-05-05 General Electric Company Pump system
DE102014000846A1 (de) * 2014-01-27 2015-07-30 Klaus Union Gmbh & Co. Kg Schraubenspindelpumpe
DE102014102390B3 (de) * 2014-02-25 2015-03-26 Leistritz Pumpen Gmbh Schraubenspindelpumpe
DE102017112743B3 (de) * 2017-06-09 2018-10-25 Leistritz Pumpen Gmbh Modulares System zur Herstellung einer Schraubenspindelpumpe
DE102019118094A1 (de) 2019-07-04 2021-01-07 Nidec Gpm Gmbh Temperierungsvorrichtung für ein Batteriespeichermodul

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102013102031A1 (de) * 2013-03-01 2014-09-04 Netzsch Pumpen & Systeme Gmbh Aus wenigstens zwei Teilen gebildete Schraubenspindelpumpe
DE102019128602B3 (de) * 2019-10-23 2021-02-11 Leistritz Pumpen Gmbh Schraubenspindelpumpe

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US20230184249A1 (en) 2023-06-15
JP7457092B2 (ja) 2024-03-27
JP2023088302A (ja) 2023-06-26
DE102021133114A1 (de) 2023-06-15
KR20230091044A (ko) 2023-06-22
CN116263155A (zh) 2023-06-16

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