EP4198311A1 - Screw spindle pump - Google Patents

Abstract

Screw spindle pump, with a spindle housing (2), in which a drive spindle (3) and at least one running spindle (4) meshing with this are accommodated in spindle bores (27), an outer housing (7) enclosing the spindle housing (2), and an axially The cover component (8) placed on the outer housing (7), on which both an axial fluid inlet connection (9) and a lateral fluid outlet connection (10) are provided, the fluid inlet connection (9) being connected to a fluid inlet of the spindle housing (2) and the fluid outlet connection (10 ) communicates with a fluid outlet of the spindle housing (2), wherein the cover component (8) can be fastened to the outer housing (7) in several distinct rotational positions with a first pitch, and the spindle housing (2) in several distinctive rotational positions with a second, smaller pitch can be attached to the cover component (8) and/or in the outer housing (7).

Description

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. 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. For this purpose, the spindle housing has several intersecting spindle bores corresponding to the number of spindles. In most cases, 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. For this purpose, 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. In addition to such a two-spindle configuration, it is also conceivable to design the screw spindle with three spindles, which means that two running spindles are then provided, which are arranged offset by 180° next to the central drive spindle and mesh with it.

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. This in turn presupposes that the outer housing, on which the corresponding inlet and outlet connections are provided, is configured accordingly. 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.

To solve this problem, 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.

First, 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. No 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. Ultimately, 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.

To enable different spatial orientations of the lateral fluid outlet connection (the fluid inlet connection is positioned axially in or parallel to the pump longitudinal axis, as described), 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.

In order to also create the possibility that the spindle housing and with it the spindles can be brought into the best possible spatial position for pump operation in the installed position of the pump, a second rotation possibility is also provided, i.e. a second rotational degree of freedom. According to the invention, 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. If 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.

As a result of the fact that there are two different degrees of freedom of rotation, each of which enables excellent positioning of the cover component and the spindle housing, 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. This is because the outer housing and the cover component are ultimately rotated together relative to the spindle housing, which, as mentioned, should be arranged, for example, horizontally in relation to the spindle axis plane in the final assembly end position. The final twisted position can now be such that the laterally protruding fluid outlet connection is in a twisted or circumferential position into which it cannot be brought solely by twisting the cover component relative to the outer housing and its attachment to the outer housing.

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.

As described, 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°. This means that the cover assembly can be attached to the outer case in four distinct positions, namely 0°, 90°, 180° and 270°. In contrast, 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°. This in turn means that, in effect, 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.

In addition to the fact that 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. For this purpose, 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.

In a further development of the invention, 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 means that 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.

As described, 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. In order to make this fixing possible, 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. This means that 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.

In a specific form of implementation, 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.

Alternatively, it is conceivable to arrange the first and second fastening means in the opposite way. This means that 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. In this case, 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.

As already described, the attachment of the spindle housing to the cover component is an attachment variant. Alternatively, it is also conceivable that the spindle housing can be fastened to the outer housing in the corresponding, marked rotational positions of the second division. For this purpose, it is conceivable to provide several 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.

It is conceivable here for the 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. This means that ultimately a type of tongue and groove design is provided, with corresponding grooves on the outside of the spindle housing and corresponding tongues on the inside of the outer housing. The springs can be pushed axially into the grooves, which is used to secure them against twisting. Of course, it is also conceivable that 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.

In principle, of course, there is the possibility of manufacturing the spindle housing, the outer housing and/or the cover component from metal. As an alternative to this, however, it is also conceivable to mold the spindle housing, the outer housing and/or the cover component from plastic, i.e. to design them as corresponding injection-molded or 3D-printed components. If a corresponding support component, for example the feather key, is provided, then this is preferably made of metal, as are the spindles, which, however, can in principle also be made of plastic.

In order to be able to seal the inside of the pump accordingly and to avoid leakage, 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. For this purpose, 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. On the one hand there is an axial seal between the spindle housing and the cover component and on the other hand there is a radial seal between the outer housing and the cover component, with the cover component expediently enclosing the outer housing radially in this sealing area.

An expedient development of the invention provides that 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. According to this aspect of the invention, 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. Furthermore, 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. During operation, this fluid chamber is filled with the fluid at the pump or outlet pressure. The result of this is that 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. Instead, 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.

Viewed axially, 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.

Furthermore, 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.

Irrespective of this, 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.

As an alternative to the integration of such an intermediate component, it is of course also conceivable to place the motor housing directly on the outer housing, ie to connect the two directly to one another. In this case, 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. Again, a shaft sealing ring can be provided, or an axial flow of the fluid for motor cooling can be possible. In any case, in this variant of the invention, the base plate of the motor housing has one or more deflection cavities, since, as stated, it forms the axial housing closure.

Expediently, 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.

In addition to the screw pump itself, the invention also relates to the use of such a screw pump in a motor vehicle for pumping an operating fluid. When used in this way, the screw pump can be used for different purposes. On the one hand, 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

eine erfindungsgemäße Schraubenspindelpumpe in teilaufgeschnittener Perspektivansicht ohne eingesetztem Antriebsmotor,

Fig. 2

eine Perspektivansicht des Deckelbauteils,

Fig. 3

eine Aufsicht auf die Innenseite des Deckelbauteils aus Fig. 2,

Fig. 4

eine Perspektivansicht der Schraubenspindelpumpe aus Fig. 1 von der anderen Seite mit teilaufgeschnittenem Deckelbauteil,

Fig. 5

die Schraubenspindelpumpe aus Fig. 4 mit um 90° verdrehtem komplettem Deckelbauteil,

Fig. 6

eine Perspektivansicht des Spindelgehäuses zur Darstellung der Vorsprünge,

Fig. 7-14

verschiedene Teilansichten der erfindungsgemäßen Schraubenspindelpumpe mit teilaufgeschnittenem zur Darstellung der unterschiedlichen Positionierungsmöglichkeiten des Fluidauslassanschlusses,

Fig. 15

eine Prinzipdarstellung der Befestigungsmöglichkeit des Spindelgehäuses im Außengehäuse, und

Fig. 16

eine Prinzipdarstellung einer erfindungsgemäßen Schraubenspindelpumpe mit angesetztem Antriebsmotor zur Darstellung der Fluidkammer.

Further advantages and details of the present invention result from the exemplary embodiments described below and from the drawings. show:

1

a screw pump according to the invention in a partially cutaway perspective view without a drive motor used,

2

a perspective view of the cover component,

3

a top view of the inside of the cover component 2 ,

4

Figure 12 shows a perspective view of the screw pump 1 from the other side with partially cut cover component,

figure 5

the screw pump off 4 with complete cover component rotated by 90°,

6

a perspective view of the spindle housing to show the projections,

Figures 7-14

various partial views of the screw pump according to the invention with a partially cutaway to show the different positioning options of the fluid outlet connection,

15

a schematic representation of the possibility of fastening the spindle housing in the outer housing, and

16

a schematic diagram of a screw pump according to the invention with attached drive motor to show the fluid chamber.

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. Viewed axially, the outer housing 7 is closed on this side via the drive motor or the motor housing, which is not shown in detail. On the opposite side, 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.

Just as the connection between the outer housing 7 and the drive motor or the motor housing is appropriately sealed via one or more sealing elements, the connection of the cover component 8 to the outer housing 7 and to the spindle housing 2 is also sealed. For this purpose, 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.

Between the spindle housing 2 and the outer housing 7 there is 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. This means that 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, For which purpose 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. In the opposite direction, 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 . On this web 21, 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. Accordingly, 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 means that 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.

Sometimes, however, due to the geometry of the peripheral connection in relation to the fluid outlet connection 10, it is also necessary to bring this into intermediate positions, that is to say positions other than those that can be realized solely by twisting the cover component. In order to realize this, it is possible to bring the spindle housing 2 together with a spindle 3, 4 into different twisted positions relative to the outer housing 7 and the cover component 8, with these distinguished, defined twisted positions being arranged according to a second division. This second division is a 45° division. The aim is that the spindle housing 2 and with it its two spindles 3, 4 (the same also applies to a 3-spindle design) always remain in the same basic position, i.e. are positioned horizontally, for example, so that the two spindles are horizontal in one Level are respectively the spindle longitudinal axes are in a common horizontal plane. This means that 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. This makes it possible for 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° . This makes it possible to optimally position the fluid outlet connection 10 with respect to the connection periphery (the fluid inlet connection 9 remains axially fixed in position as described), while at the same time it is ensured that the spindle housing 2 and with it the spindle assembly is always arranged in the best possible spatial alignment for pumping operation, namely horizontally in this case.

In order to make this possible, it is necessary on the one hand to ensure the axial support of the spindles 3, 4 in every twisted position, as well as the corresponding fixing of the spindle housing 2 relative to the outer housing 7 and the cover component 8.

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. For this purpose, 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.

Also provided are a plurality of 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.

The Figures 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. In order to be able to show the position of the feather key 19 in the respective arrangement, the cover component 8 is in 4 shown partially open. In fact, it is of course axially closed except for the fluid inlet 9 . In figure 5 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. Shown are the axially extending projections 26 provided on the radial flange 13 of the spindle housing 2, of which, for example, only four can be provided, or also eight, corresponding number of depressions 25. 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 .

figure 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°. This adaptability of the axial support via the adjustable feather key 19 and the possibility of enabling the spindle housing 2 to be secured against rotation in any twisted position make it possible to realize the four different positions of the cover element 8 without any problems.

6 shows the spindle housing 2 and the feather key 19 in a perspective view. 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. As described above, of course, the outer housing 7 also rotates, which is not shown here for reasons of clarity.

7 shows the initial situation as already described in figure 5 was described. Only the cover component 8 is shown here in principle, as well as the drive spindle 3 and the running spindle 4, which are supported axially on the feather key 19.

8 shows the arrangement in which the fluid outlet port 10 is directed vertically upward. In this arrangement, 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 . During the assembly of the cover component 8, the projections 26 engage at 45° to the situation according to FIG 7 offset depressions 25, so that this 45 ° position is fixed.

9 shows the situation in which the cover component 8 is rotated by a further 45°. This situation can be based on the assembly situation according to 7 be taken simply by the fact that the outer housing 7 in the starting position according to 7 remains, but the cover component 8 is rotated by 90°, at the same time the feather key 19 is also inserted by 90° into the next but one receiving groove 24. The spindles 3, 4 remain in their horizontal orientation, as already described. This means that ultimately the outer housing 7 only has to be rotated through 45° into each intermediate position between two distinct rotational positions of the first division.

10 shows the cover component 8 by a further 45° starting from the arrangement 9 twisted. Here again, 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 situation according to 11 ultimately corresponds to the off 7 , only the cover component 8 is positioned here rotated by 180°. Starting according to the situation 7 it would not be necessary to implement the key 19.

The arrangements in the Figures 12, 13 and 14 Modifications shown result in accordance with the procedure described above or the arrangement of the components involved.

Overall, it is thus possible to bring the fluid outlet connector 10 into eight defined circumferential positions, while at the same time ensuring that the spindle housing 2 or the spindles 3, 4 remain in the best possible spatial alignment. Since there is also a certain tolerance range in this regard, and, for example, the plane in which the longitudinal axes of the spindles 3, 4 lie together can also be tilted slightly relative to the horizontal plane, each of the Figures 7-14 Arrangements shown provided with a certain tolerance range in the circumferential direction, for example +/- 5 ° or +/- 10 °, so that an even more variable alignment option with respect to the fluid outlet port 10 is given.

Of course, it is also possible to reverse the two fastening variants. It would thus be conceivable to form corresponding axial projections 26 on the cover component 8 while axial depressions 25 are formed on the spindle housing 2 .

As described above, 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. As an alternative to this anti-twist device or fixation, it is also conceivable to connect the outer housing 7 to the spindle housing 2 in the corresponding 45° twisted positions. 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. On the inner circumference of the outer housing 7, which in principle is cylindrical on the inside, 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 On the outside of the spindle housing 2, 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.

Likewise, it is alternatively conceivable to provide corresponding receiving grooves 29 on the inner circumference of the outer housing 7 , while two projections 28 are formed on the outside of the spindle housing 2 .

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.

Also shown is 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. As already described, the fluid chamber 16 communicates with the fluid outlet connection 10 so that the pressurized fluid can be drawn off via this.

16 is purely a representation of the principle. Of course, 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 . Depending on the configuration of the spindle housing 2, 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.

Even if not shown in more detail, there are of course also one or more corresponding sealing elements in the area of the connection of the drive motor 30 to the outer housing 7 or, if an intermediate component 35 is provided, in the area of the connection of this intermediate component 35 to the outer housing 7.

Finally, it should also be mentioned that 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.

Claims (21)

Screw spindle pump, with a spindle housing (2), in which a drive spindle (3) and at least one running spindle (4) meshing with this are accommodated in spindle bores (27), an outer housing (7) enclosing the spindle housing (2), and an axially The cover component (8) placed on the outer housing (7), on which both an axial fluid inlet connection (9) and a lateral fluid outlet connection (10) are provided, the fluid inlet connection (9) being connected to a fluid inlet of the spindle housing (2) and the fluid outlet connection (10 ) communicates with a fluid outlet of the spindle housing (2), wherein the cover component (8) can be fastened to the outer housing (7) in several distinct rotational positions with a first pitch, and the spindle housing (2) in several distinctive rotational positions with a second, smaller pitch can be attached to the cover component (8) and/or in the outer housing (7). Screw pump according to Claim 1, characterized in that the first pitch is 90° and the second pitch is 45°. Screw spindle pump according to Claim 1 or 2, characterized in that two running spindles (4) are provided, which are arranged on both sides next to the central drive spindle (3). Screw spindle pump according to one of the preceding claims, characterized in that the drive spindle (3) and the running spindle (4) are supported axially on a support component (18) arranged on the cover component (8). Screw pump according to claim 4, characterized in that the support member (18) is a key (19) in different Excellent twisted positions can be positioned with the second division on the cover component (8). Screw spindle pump according to Claim 5, characterized in that receiving grooves (24) are provided on the cover component (8) corresponding to the various rotational positions, into which keyways (19) can be inserted. Screw spindle pump according to Claim 6, characterized in that the feather key (19) is clamped in the receiving grooves (24). Screw spindle pump according to one of the preceding claims, characterized in that a plurality of first fastening means (25) positioned according to the second division are provided on the cover component (8) and can be connected to second fastening means (26) provided on the spindle housing (2). Screw spindle pump according to Claim 8, characterized in that the first fastening means on the cover component (8) are depressions (25) formed into which axial projections (26) provided as second fastening means on the spindle housing (2) engage, or in that the first fastening means on the cover component ( 8) are provided axial projections (26) which engage in depressions (25) formed as second fastening means on the spindle housing (2). Screw spindle pump according to one of Claims 1 to 7, characterized in that a plurality of first fastening means (28) positioned according to the second division are provided on or in the outer housing (7) and can be connected to second fastening means (29) provided on the spindle housing (2). . Screw pump according to Claim 10, characterized in that the first fastening means are radially directed projections (28) which in radially open receptacles (29) provided on the spindle housing (2) and serving as second fastening means engage, or that the first fastening means are open receptacles (29) into which radially directed projections (28) provided on the spindle housing (2) engage. Screw spindle pump according to one of the preceding claims, characterized in that the spindle housing (2), the outer housing (7) and/or the cover component (8) is made of plastic and the possibly provided supporting component (18) is made of metal. Screw spindle pump according to one of the preceding claims, characterized in that the cover component (8) is sealed against the spindle housing (2) by a first sealing element and against the outer housing (7) by a second sealing element. Screw spindle pump according to Claim 13, characterized in that a first axial receiving groove (12), into which the first sealing element is inserted, is provided on the cover component (8) or on the spindle housing (2), and in that on the outer housing (7) or on the cover element (8 ) a second radial receiving groove (14) is provided, in which the second sealing element is inserted. Screw spindle pump according to one of the preceding claims, characterized in that the spindle housing (2) has an axial fluid outlet for the fluid conveyed through the spindle housing (2) via the drive spindle and the running spindle (3, 4), which fluid outlet has a pressure between the spindle housing ( 2) and the outer housing (7) communicates fluid chamber (16) extending through 360°, which in turn communicates with the radial fluid outlet connection (10) of the cover component (8). Screw spindle pump according to Claim 15, characterized in that the fluid chamber (16) extends over at least half the length of the spindle bore (27). Screw spindle pump according to one of the preceding claims, characterized in that an intermediate component (35) placed axially on the outer housing (7) is provided, which is designed for connecting a drive motor (30), wherein on the intermediate component (35) one or more, the from the fluid outlet of the spindle housing (2) coming fluid to the fluid chamber (16) deflecting deflection cavities (33) are provided. Screw spindle pump according to one of Claims 1 to 16, characterized in that on a housing (34) of a drive motor (30) placed on the outer housing (7), one or more fluid coming from the fluid outlet of the spindle housing (2) to the fluid chamber (16) deflecting deflection cavities (33) are provided Screw spindle pump according to Claim 17 or 18, characterized in that one deflection cavity (33) is an annular groove or cup-shaped depression which is rounded in the region of the groove or depression base (36). Use of a screw pump (1) according to one of the preceding claims in a motor vehicle for delivering an operating fluid. Use according to Claim 20, characterized in that the screw spindle pump (1) is used as a coolant pump, in particular for pumping a coolant which is used to cool an energy store.

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