SCREW SPINDLE PUMP

Abstract

A screw spindle pump, including a spindle housing, in which a drive spindle and a running spindle meshing therewith are received in spindle bores. The drive spindle has a cylindrical spindle core and at least two circumferential spindle profiles, and, on an end face, in a depression axially delimited by a planar bottom surface and in which the two profile valleys open out between the two spindle profiles offset by 180°, there is a disk-shaped coupling element, which has an insertion receptacle for a drive shaft of a drive motor and which is coupled to the drive spindle for conjoint rotation therewith via a form-fitting engagement with axially protruding projections that laterally delimit the depression and engage in lateral receptacles of the coupling element. The bottom surface is delimited by the spindle core in the region of the openings of the two profile valleys, and the coupling element has a rounded configuration, corresponding to the shape of the spindle core, in the element regions that adjoin the regions of the opening. The diameter of the coupling element, in the region of the rounded element regions, is no greater than the diameter of the spindle core.

Claims

1. A screw spindle pump, comprising a spindle housing, in which a drive spindle and at least one running spindle meshing therewith are received in spindle bores, wherein the drive spindle has a cylindrical spindle core and at least two spindle profiles around the circumference of the spindle core, and, on an end face of the drive spindle, in a depression which is axially delimited by a planar bottom surface and in which the two profile valleys open out between the two spindle profiles in a manner offset by 180°, there is arranged a disk-shaped coupling element, which has an insertion receptacle for a drive shaft of a drive motor and which is coupled to the drive spindle for conjoint rotation therewith in at least one direction of rotation of the drive spindle via a form-fitting engagement with axially protruding projections that laterally delimit the depression and engage in lateral receptacles of the coupling element, wherein the bottom surface is delimited by the spindle core in the region of the openings of the two profile valleys, and the coupling element has a rounded configuration, corresponding to the shape of the spindle core, in the element regions that adjoin the regions of the opening, wherein the diameter of the coupling element, in the region of the rounded element regions, corresponds at most to the diameter of the spindle core or is smaller than the diameter of the spindle core.

2. The screw spindle pump according to claim 1, wherein the coupling element has a cylindrical base portion from which four element projections protrude, wherein two adjacent element projections delimit a lateral receptacle.

3. The screw spindle pump according to claim 2, wherein the receptacle extends into the base portion.

4. The screw spindle pump according to claim 2, wherein the element projections are triangular and taper toward their free end.

5. The screw spindle pump according to claim 2, wherein the thickness of each element projection decreases toward its free end.

6. The screw spindle pump according to claim 2, wherein the insertion receptacle has a square shape.

7. The screw spindle pump according to claim 6, wherein the insertion receptacle has a rectangular shape, wherein said insertion receptacle extends between the two rounded element portions by way of its longer axis and between the two receptacles by way of its shorter axis.

8. The screw spindle pump according to claim 1, wherein the coupling element is made of plastic or metal.

9. The screw spindle pump according to claim 1, comprising a drive motor, wherein the diameter of the cylindrical drive shaft of the drive motor corresponds at most to the diameter of the cylindrical spindle core.

10. The screw spindle pump according to claim 1, wherein a central drive spindle and two running spindles arranged on either side of the drive spindle are provided.

11. A use of a screw spindle pump according to claim 1 in a motor vehicle for the purpose of delivering an operating liquid.

12. The use according to claim 11, wherein the screw spindle pump is used as a coolant pump, in particular for delivering a coolant serving to cool an energy store.

Description

BRIEF DESCRIPTION OF THE DRAWING

[0024] FIG. 1 shows a schematic illustration, in section, of a screw spindle pump according to the invention with one drive spindle and two running spindles,

[0025] FIG. 2 shows an exploded view of the drive spindle and of the coupling element not inserted in the depression,

[0026] FIG. 3 shows the arrangement of FIG. 2 illustrating the relevant diameter on the spindle core and on the base portion,

[0027] FIG. 4 shows a view of the end face of the drive spindle looking toward the depression receiving the coupling element,

[0028] FIG. 5 shows a plan view of the arrangement of FIG. 4 with the coupling element inserted,

[0029] FIG. 6 shows a perspective view of the arrangement of FIG. 5,

[0030] FIG. 7 shows a sectional exploded illustration of part of the screw spindle pump with a schematically illustrated drive shaft of the drive motor, and

[0031] FIG. 8 shows the arrangement of FIG. 7 in the mounted state, which is shown in section.

DETAILED DESCRIPTION OF THE INVENTION

[0032] FIG. 1 shows a screw spindle pump 1 according to the invention, comprising an outer housing 2 with an inlet port 3, which is arranged axially, and an outlet port 4, which is arranged radially. In the outer housing 2, which can also be referred to as pump housing, there is arranged a spindle housing 5, in which, in the exemplary embodiment shown, three spindles, specifically a central drive spindle 6 and two running spindles 7, arranged to either side of the drive spindle 6, are received in corresponding, intersecting spindle bores. The spindles 6, 7 each have spindle profiles which engage in one another, that is to say mesh with one another.

[0033] Furthermore, a drive motor 8, which is shown only schematically here and which may be a dry-running or wet-running drive motor, is provided. Said drive motor has a drive shaft 9, which is shown only in a stylized manner here and is connected to the drive spindle 6 for conjoint rotation therewith via a coupling element 10. This means that the drive spindle 6 is actively driven by the drive motor 8. A rotation of the drive spindle 6 imperatively also leads to a rotation of the two running spindles 7, owing to the engagement of the spindle profiles. Corresponding delivery volumes are axially moved or displaced by the mutually engaging spindle profiles and the spindle rotation, whereby the fluid delivery is effected in a known way. The fluid is axially drawn in through the inlet ports 3, is delivered along the spindle set and exits at the motor-side end of the spindle set, from where it flows to the outlet port 4 via a corresponding flow geometry.

[0034] FIG. 2 shows the drive spindle 6 and the coupling element 10 in an enlarged, perspective view in the form of an exploded view. The drive spindle 6, made of metal or plastic, has a cross-sectionally cylindrical spindle core 11, around which run two spindle profiles 12, resulting in the formation of corresponding profile valleys 13. At an axial end, the drive spindle 6 has a depression 14, which is axially delimited by a planar bottom surface 15 and which is laterally delimited by two projections 16, wherein these two projections 16 are formed, as it were, as an extension of the spindle profiles 12 that run into the base surface 15. The projections 16 are machined by material removal, which will be discussed in more detail below in connection with FIG. 4, with the result that overall a bottom surface 15 is produced which, on the one hand, in certain portions is formed by the spindle core 11 and, on the other hand, on account of the machining of the projections 16, is formed by adjacent bottom portions, which will be discussed in more detail below.

[0035] The coupling element 10, likewise made of metal or plastic, has a disk-shaped configuration, and thus has a defined, maximum thickness. It comprises a cylindrical base portion 17, which has two opposite element regions 18 with a rounded configuration. Furthermore, in the example shown, on the base portion 17 there are provided 4 element projections 19 that protrude to the side and define a respective V-shaped receptacle 20 between them, in which receptacle the projections 16 engage in the mounted position, when the coupling element 10 is inserted in the depression 14.

[0036] As FIG. 2, but also FIG. 3 shows, the bottom surface 15 is formed and bordered at least in certain portions by the cylindrical spindle core 11. This rounded border, resulting from the cylinder shape of the spindle core 11, is provided at the opening of the respective profile valley 13, since the profile valley is defined by the spindle core 11. The spindle core 11 has a core diameter DK, which is illustrated in FIG. 3.

[0037] As described, the coupling element 10 also has a disk-shaped, cylindrical base portion 17, which has a base-portion diameter DB likewise illustrated in FIG. 3. The design of the size or geometry of the coupling element 10 is then selected in such a way that the diameter of the base portion 17 is smaller than or the same as the diameter of the spindle core, and consequently DB DK. This means that, in the mounted position, the rounded element regions 18 at which the base-portion diameter DB is provided imperatively do not protrude into the flow cross section or opening cross section of the respective profile valley 13. Consequently, the coupling element 10 does not obstruct the flow, at least in the region of the rounded element portions 18.

[0038] FIG. 4 shows a plan view of the end face of the drive spindle 6 looking toward the depression 14. What is shown is the two profile valleys 13 that open out there and also the spindle core, which defines the rounded border of the bottom surface 15 in the mutually opposite edge portions 21.

[0039] The end face is machined via corresponding cross-grinding means, this on the one hand leading to an enlargement of the bottom surface 15 via the spindle core surface. On the other hand, this produces a specific form-fitting or engagement geometry of the projections 16, which have two V-shaped bearing surfaces 22 by way of which they bear against the entire surface area of corresponding bearing surfaces of the coupling element 10 or are positioned closely thereto, spaced apart by a narrow gap. The coupling element 10 is illustrated in dashed lines.

[0040] The formation of the cross-grinding means produces four lateral enlargement portions of the base surface 15, resulting in the production of an X-shape, as it were, as shown illustratively in FIG. 4.

[0041] Then, the coupling element 10 is inserted in this depression 14, and FIGS. 5 and 6 show a corresponding plan view (FIG. 5) and a perspective view (FIG. 6). Since the base-portion diameter DB corresponds at most to the core diameter DK, consequently the rounded portions 18 of the coupling element 10 do not protrude into the flow cross section defined by the spindle core 11, as shown illustratively in FIGS. 5 and 6. The element projections 19 each delimit two V-shaped, laterally open receptacles 20, which are defined by two bearing surfaces 23. The receptacles 20 extend into the base portion 17 and end just before an insertion receptacle 24, which has a square or rectangular cross section and serves to receive a correspondingly shaped engagement pin of the drive shaft 9. In the mounted position according to FIGS. 5 and 6, the receptacles 20 receive the two projections 16 in a form-fitting or shape-matched manner, as it were. Owing to the bearing of the surfaces 22, 23 and the respective V-shaped engagement, a rotationally conjoint connection is provided both in the event of clockwise and anticlockwise rotation.

[0042] The element projections 19 extend, as described, from the base portion 17, with the result that here an X-shape, as it were, corresponding to the X-like shape of the depression or the bottom surface 15 is produced. It is also the case that the element projections 19 ultimately do not protrude into the opening cross section of the respective profile valley 13 on the end face, with the result that consequently the coupling element 10 does not or virtually does not obstruct the fluid flow. Only the element projection 19 shown at the top right and at the bottom left in FIG. 5 protrudes slightly into the flow cross section, but its obstacle function is negligible.

[0043] As shown in FIGS. 5 and 6, the element projections 19 taper toward their free end, and their thickness also decreases toward their free end. Corresponding oblique surfaces or bevels are formed, indeed on both sides, with the result that reverse mounting is also possible without problems.

[0044] As shown in FIG. 5, the coupling element 10, as seen axially, lies virtually completely on the base surface 15 or axially covers it. Only the element projection 19 shown at the top right in FIG. 5 and the element projection 19 shown at the bottom left in FIG. 5 protrude somewhat radially beyond the base surface 15 into the flow cross section. This engagement or this cross-sectional covering, however, is small, and therefore the flow-obstructing effect is virtually negligible.

[0045] FIG. 7 shows an exploded view of the inner housing 5 of a screw spindle pump with only two spindles, specifically in turn one drive spindle 6 and only one running spindle 7, in comparison with the 3-spindle embodiment according to the preceding figures. This serves to illustrate that a coupling according to the invention can be provided both for a 3-spindle and for a 2-spindle screw spindle pump 1.

[0046] In the exploded illustration according to FIG. 7, at the axial end of the drive spindle 6, there is formed a depression 14 with an identical configuration as described above, and an identical coupling element 10 is inserted in this depression 14. What is furthermore schematically illustrated is the drive shaft 9 of the drive motor with the end-side insertion pin 25, which engages in a form-fitting manner in the insertion receptacle 24. In the mounted position, as shown in FIG. 8, the insertion pin 25 engages in the insertion receptacle 24, while at the same time the coupling element 10 is fitted in the depression 14. A rotation of the drive shaft 9 therefore imperatively leads to a rotation of the drive shaft 6, and via the latter also of the running spindle 7, the rotations being coupled via the coupling element 10, with the result that the pump can deliver the fluid. Owing to the geometry of the projections 16 and the receptacles 20 and the respective V-shaped configuration via the corresponding bearing surfaces, a rotation of the drive shaft 9 and thus of the drive spindle 6 both clockwise, that is to say in the delivery direction, and, where required, counterclockwise is possible, since a rotationally conjoint coupling is provided in both directions of rotation.

[0047] As is also shown in FIG. 8, the diameter of the drive shaft 9, denoted by DA in FIG. 8, is smaller than the core diameter DK of the spindle core 11. The diameter DA corresponds substantially to the diameter of the base portion DB of the coupling element 10. This is shown illustratively in FIG. 8. This results, consequently, in likewise no step constituting an obstacle to the flow being formed in the transition between the coupling element 10 and the drive shaft 9, which would be the case if the diameter DA were larger than the base-portion diameter DB. This means that the fluid axially exiting the spindle set ultimately is exposed to virtually no obstacle to the flow at all, apart from the two short element projections 19 which protrude only slightly into the flow cross section, as described above. Otherwise, the fluid can flow in a completely free-flowing manner, by contrast to coupling devices known to date, as described in the introduction.

[0048] Such a screw spindle pump 1, irrespective of whether it is a pump having two spindles or three spindles, may be used to deliver a very wide variety of fluids. With preference, it is used in the motor vehicle sector, either as a fuel pump or a delivery pump for some other operating fluid, in particular for a coolant, which is used to cool an energy store of the motor vehicle. The energy store is a large-volume traction storage unit of an electric vehicle. It is thus a coolant pump. Other intended uses are of course equally conceivable, for example as a delivery pump for a washing fluid, which is used for washing the windscreen of the vehicle or similar purposes.

[0049] While specific embodiments of the invention have been shown and described in detail to illustrate the inventive principles, it will be understood that the invention may be embodied otherwise without departing from such principles.