CN114667396B

CN114667396B - Separation device and fluid machinery having the same

Info

Publication number: CN114667396B
Application number: CN202080081448.4A
Authority: CN
Inventors: M·克鲁斯; A·哈尼施马赫; J·沃尔特; H·布彻
Original assignee: Robert Bosch GmbH
Current assignee: Robert Bosch GmbH
Priority date: 2019-11-25
Filing date: 2020-11-23
Publication date: 2025-07-01
Anticipated expiration: 2040-11-23
Also published as: CN114667396A; DE102019218137A1; US20230009371A1; WO2021105043A1

Abstract

The invention relates to a separation device for a fluid machine, comprising at least one housing (12) and at least one agitation unit (32), wherein the housing has at least one bearing receptacle (24), the bearing receptacle defining at least one bearing axis (26), and the housing has at least one impeller side space (28), wherein the agitation unit is arranged on the housing (12) for deflecting and/or agitating at least one fluid flow and/or particle flow (34), wherein the agitation unit (32) has at least one flow recess (38) defined by a wall (36) of the housing (12), the flow recess extending inside the impeller side space (28) at a distance from the bearing axis (26). The invention proposes that the agitation unit (32) comprises at least one sealing gap element (40) arranged on the wall (36) of the housing (12), the sealing gap element being provided for deflecting and/or agitating at least one fluid flow and/or particle flow (34) flowing through the flow recess (38) along the bearing axis (26) and/or towards the bearing axis (26).

Description

Separation device and fluid machine having the same

Technical Field

A separating device for a fluid machine (Str mungsmaschine) has been proposed, which has at least one housing with at least one bearing receptacle, which defines at least one bearing axis, and which has at least one impeller side space (Radseitenraum), and which has at least one stirring unit (Verwirbelungseinheit), in particular arranged on the housing, for deflecting and/or stirring at least one fluid flow and/or particle flow, wherein the stirring unit has at least one flow recess, which is delimited by a wall of the housing and extends inside the impeller side space at a distance from the bearing axis.

Disclosure of Invention

The invention relates to a separating device for a fluid machine, comprising at least one housing, which has at least one bearing receptacle, which defines at least one bearing axis, and which has at least one impeller-side space, and at least one stirring unit, in particular arranged on the housing, for deflecting and/or stirring at least one fluid flow and/or particle flow, wherein the stirring unit has at least one flow recess, which is delimited by a wall of the housing, and which extends in the impeller-side space at a distance from the bearing axis.

The invention proposes that the stirring unit comprises at least one sealing gap element (DICHTSPALTELEMENT) arranged on a wall of the housing, said sealing gap element being provided for deflecting and/or stirring at least one fluid flow and/or particle flow flowing along and/or towards the bearing axis through the flow recess.

Preferably, the sealing gap element is configured as a molding, a sealing ring, a sealing flange or the like. Preferably, the sealing gap element is fastened to the housing, in particular integrally formed with the housing. By "integrally" is understood in particular a material-locking connection, such as, for example, by a welding process and/or an adhesive process, etc., and is particularly advantageously molded, for example, by being produced from a cast part and/or by being produced in a single-component or multicomponent injection molding process. Particularly preferably, the sealing gap element is configured in the shape of a ring, viewed along the bearing axis. Preferably, the sealing gap element is configured as a hollow cylinder. Preferably, the sealing gap element has an at least approximately rectangular cross-sectional area in a plane in which the bearing axis is arranged. Preferably, the sealing gap elements are arranged uniformly around the bearing axis. Preferably, the sealing gap element has a central axis, wherein the sealing gap element is configured in particular symmetrically about the central axis. In particular, the sealing gap element is arranged such that the central axis of the sealing gap element is arranged inside the bearing axis. Preferably, the sealing gap element has a maximum width of, in particular, at most 5mm, preferably at most 3mm and particularly preferably at most 2 mm. Preferably, the maximum width of the sealing gap element is oriented at least substantially perpendicular to the bearing axis and/or the central axis. By "substantially perpendicular" is understood in particular the orientation of a straight line or a plane, in particular a viewing plane, with respect to a further straight line or a further plane, in particular a bearing axis, wherein the straight line or the plane forms an angle of 90 ° with the further straight line or the further plane, in particular as viewed in a projection plane, and the angle has a maximum deviation of in particular less than 8 °, advantageously less than 5 ° and particularly advantageously less than 2 °. Preferably, the maximum width of the sealing gap element is in particular at least 1mm, preferably at least 1.5 mm and particularly preferably at least 2 mm. Preferably, the sealing gap element has at least one inner face and at least one outer face, which are in particular arranged at least partially, at least substantially parallel to one another. One face, in particular the outer face, of the sealing gap element is oriented "substantially parallel to" an axis, a plane or another face, in particular the inner face of the sealing gap element, it being understood in particular that the face has a minimum distance in each point of the face relative to the one axis, the one plane or the other face, which differs by less than 5%, preferably by less than 3% and particularly preferably by less than 1% from the average value of the minimum distances of all points to all points. Preferably, the inner and outer faces of the sealing gap element are in particular arranged at least partially, at least substantially parallel to the bearing axis. In particular, the outer surface of the sealing gap element is at least largely arranged on the side of the sealing gap element facing away from the bearing axis. Preferably, the inner surface of the sealing gap element is arranged at least for the most part on the side of the sealing gap element facing the bearing axis. Preferably, the sealing gap element has at least one sealing gap surface, which is arranged in particular at least substantially perpendicular to the bearing axis. Preferably, the sealing gap surface extends at least substantially completely over the maximum width of the sealing gap element, at least substantially perpendicularly to the bearing axis. Particularly preferably, the sealing gap surface is configured as a ring. In particular, the sealing gap surface is defined by an inner and/or an outer surface of the sealing gap element.

Preferably, the separating device is provided for preventing a fluid flow and/or a particle flow from flowing through the wheel-side space in the direction of the bearing axis. In particular, the fluid flow and/or the particle flow is formed inside the fluid to be moved by means of the fluid machine. For example, the fluid stream and/or the particle stream are configured as contaminants and/or residues within the fluid to be moved. Preferably, the stirring unit is provided for deflecting a fluid flow and/or a particle flow flowing through the flow recess along and/or towards the bearing axis in a direction directed away from the wall of the housing and/or at least substantially parallel to the bearing axis and/or the longitudinal extension of the sealing gap element.

Preferably, the housing, in particular the wall of the housing that delimits the flow recess, is configured such that the flow recess is optimally configured, at least substantially perpendicularly to the bearing axis, when viewed. In particular, the wall of the housing, which defines the flow recess, has a rounded, in particular at least partially oval, contour, viewed at least substantially perpendicularly to the bearing axis. In particular, the contour of the wall of the housing, which defines the flow recess, is embodied as non-angular. The flow recess is preferably arranged in an edge region of the impeller-side space which is spaced apart from the bearing axis. The flow recess is in particular fluidically connected to the wheel-side space. Preferably, the flow recess extends at least substantially entirely around the bearing axis. In particular, the flow recess has a cross-sectional area, viewed in the circumferential direction about the bearing axis, which has a maximum deviation of at most 5%, preferably at most 3% and particularly preferably at most 1% of the average value of the cross-sectional area of the flow recess in the circumferential direction. Preferably, the bearing receptacle is arranged around the bearing axis. Preferably, the impeller-side space is arranged around the bearing axis and/or the bearing receptacle. Preferably, the housing has a spiral space (Spiralraum) which is fluidically connected to the impeller-side space and the flow recess. Preferably, the helical space extends at least substantially completely around the bearing axis. Preferably, the spiral space is at least partially configured as a volute, seen along the bearing axis. Particularly preferably, the spiral space adjoins the edge region of the impeller-side space and/or the flow recess. Preferably, the spiral space comprises at least one outlet opening for outputting the fluid to be moved. In particular, the spiral space and the impeller-side space are connected to each other by at least one fluid opening. Preferably, the fluid opening has an opening width oriented at least substantially parallel to the bearing axis, viewed at least substantially perpendicular to the bearing axis. By "substantially parallel" is understood in particular the orientation of a straight line or a plane, in particular the opening width of the fluid opening, with respect to a further straight line or a further plane, in particular the bearing axis, wherein the straight line or the plane has a deviation of in particular less than 8 °, advantageously less than 5 ° and particularly advantageously less than 2 °, with respect to the further straight line or the further plane, in particular in the projection plane. Preferably, the fluid opening extends at least substantially entirely around the bearing axis. In particular, the opening width of the fluid opening is smaller at least one point in a section plane through the bearing axis, in particular at least largely in the circumferential direction, than the maximum longitudinal extent of the spiral space at this point.

The embodiment of the separating device according to the invention advantageously prevents an undesired penetration of the fluid flow and/or of the particle flow into the bearing receptacle. An advantageously high separation rate of the fluid stream and/or the particle stream may be achieved. An advantageously high agitation of the fluid flow and/or the particle flow in the wheel side space can be achieved.

It is furthermore proposed that the sealing gap element at least partially defines a flow recess. Preferably, the sealing gap element is arranged on a wall of the housing defining the flow recess. In particular, the outer surface of the sealing gap element, viewed at least substantially perpendicularly to the bearing axis, is preferably formed flush with the wall of the housing defining the flow recess in one plane in the region of the connection of the sealing gap element and the wall of the housing defining the flow recess. Preferably, the outer surface of the sealing gap element is rounded in the region of the connection of the sealing gap element and the wall of the housing that delimits the flow recess, in particular oriented transversely to the bearing axis. An advantageously large flow recess can be achieved, in particular because the flow recess can be formed into the impeller side space by the sealing gap element. An advantageously high degree of agitation of the fluid flow and/or the particle flow in the flow recess can be achieved.

It is furthermore proposed that the stirring unit comprises at least one further sealing gap element which is arranged on a wall of the housing and at least partially defines the flow recess. Preferably, the further sealing gap element is configured as a shaped part. Preferably, the further sealing gap element is fastened to the housing, in particular is formed integrally with the housing. Particularly preferably, the further sealing gap element is configured as a ring shape, viewed along the bearing axis. Preferably, the further sealing gap element is at least partially configured as a hollow cylinder. Preferably, the further sealing gap element has a central axis. In particular, the further sealing gap element is arranged such that the central axis of the further sealing gap element is arranged inside the bearing axis. the further sealing gap element preferably has a maximum width of in particular at most 5mm, preferably at most 3 mm and particularly preferably at most 2 mm. In particular, the maximum width of the further sealing gap element is oriented at least substantially perpendicular to the bearing axis and/or perpendicular to the central axis of the further sealing gap element. Preferably, the maximum width of the further sealing gap element is in particular at least 1mm, preferably at least 1.5 mm and particularly preferably at least 2 mm. Preferably, the further sealing gap element has at least one inner face and at least one outer face, which are arranged at least partially at least substantially parallel to each other. Preferably, the inner and outer faces of the further sealing gap element are at least partially arranged at least substantially parallel to the bearing axis. Preferably, the further sealing gap element has at least one side surface, which is arranged in particular transversely, preferably at least partially at least substantially perpendicularly, to the bearing axis. The lateral surface of the further sealing gap element is defined in particular by the inner and/or outer surface of the further sealing gap element. Preferably, the further sealing gap element is arranged on a wall of the housing defining the flow recess. In particular, the outer surface of the further sealing gap element is arranged at least for the most part on the side of the further sealing gap element facing away from the bearing axis. Preferably, the inner face of the further sealing gap element is arranged at least for the most part on the side of the further sealing gap element facing the bearing axis. In particular, the inner face of the further sealing gap element, viewed at least substantially perpendicularly to the bearing axis, is preferably configured flush with the wall of the housing defining the flow recess in one plane in the connection region of the further sealing gap element and the wall of the housing defining the flow recess. Preferably, the inner surface of the sealing gap element is rounded in the region of the connection of the further sealing gap element to the wall of the housing that delimits the flow recess, in particular oriented transversely to the bearing axis. Particularly preferably, the further sealing gap element is constructed and/or arranged in such a way that the further sealing gap element, in particular an outer surface of the further sealing gap element, at least partially defines a spiral space. In particular, the further sealing gap element is arranged between the impeller side space and the screw space. Preferably, the further sealing gap element, in particular a side face of the further sealing gap element, at least partially defines the fluid opening. The further sealing gap element has, in particular, at least substantially parallel to the bearing axis, a greater maximum lateral extent than the sealing gap element. Advantageously directed flow into the flow recess can be achieved, in particular because the fluid flow and/or the particle flow can be guided along the further sealing gap element directly into the flow recess. an advantageously large flow recess can be achieved, in particular because the flow recess can be embodied up to the side of the further sealing gap element.

It is furthermore proposed that the stirring unit comprises at least one, in particular the aforementioned further sealing gap element, which, viewed at least substantially perpendicularly to the bearing axis, has a minimum radial distance from the bearing axis, which is greater than the minimum radial distance of the sealing gap element and the bearing axis, wherein the flow recess is arranged between the sealing gap element and the further sealing gap element, viewed from the bearing axis. Preferably, the minimum radial distance of the sealing gap element and the further sealing gap element relative to the bearing axis extends at least substantially perpendicularly to the bearing axis. Preferably, the minimum radial distance of the sealing gap element extends from the inner face of the sealing gap element towards the bearing axis. Preferably, a minimum radial distance of the further sealing gap element is arranged from the inner face of the further sealing gap element towards the bearing axis. Preferably, the minimum radial distance of the sealing gap element is at least 40%, preferably at least 50% and particularly preferably at least 60% of the minimum radial distance of the further sealing gap element. It is particularly preferred that the sealing gap element and the further sealing gap element form a flow recess in the impeller-side space together with a wall of the housing defining the flow recess. An advantageous arrangement of the flow recesses can be achieved, in particular, between the sealing gap elements. An advantageously large flow recess can be achieved, in particular because the flow recess can be formed by two sealing gap elements.

It is furthermore proposed that the stirring unit comprises at least one, in particular the aforementioned further sealing gap element, wherein at least two mutually adjoining outer faces, in particular the aforementioned inner faces, outer faces and/or side faces, which form the sealing edge, form at least one angle of less than 90 °, preferably less than 80 ° and particularly preferably less than 70 °, viewed at least substantially perpendicularly to the bearing axis, in particular in the vicinity of the sealing edge of the further sealing gap element. Preferably, the side face of the further sealing gap element and the outer or inner face of the further sealing gap element, in particular in the vicinity of the sealing edge of the further sealing gap element, form at least one angle, which is in particular less than 90 °, preferably less than 80 ° and particularly preferably less than 70 °. By "adjacent region" is understood in particular a region surrounding the component, in particular the sealing edge, wherein each point in this region has a maximum distance from the component of at most 5mm, preferably at most 3 mm and particularly preferably 1 mm. In particular, the sealing edge of the further sealing gap element is arranged at least substantially perpendicularly to the bearing axis and at least substantially completely around the bearing axis. An advantageously small flow of the fluid flow and/or the particle flow from the spiral space, in particular from beside the further sealing gap element, in particular from beside the sealing edge of the further sealing gap element, into the impeller-side space and into the flow recess can be achieved. The fluid flow and/or the particle flow can advantageously be prevented from undesirably penetrating into the bearing receptacle.

It is furthermore proposed that the stirring unit comprises at least one, in particular the aforementioned further sealing gap element having the in particular the aforementioned or further sealing edge, which is arranged such that at least one of the outer faces, in particular the aforementioned inner faces, of the further sealing gap element, which form the sealing edge of the further sealing gap element, is oriented at least substantially parallel to the bearing axis. An advantageously small flow of the fluid flow and/or the particle flow from the spiral space, in particular from beside the further sealing gap element, in particular from beside the sealing edge of the further sealing gap element, into the impeller-side space and into the flow recess can be achieved. The fluid flow and/or the particle flow can advantageously be prevented from undesirably penetrating into the bearing receptacle.

Furthermore, a fluid machine, in particular a coolant pump, is proposed, comprising at least one drive unit, which has at least one drive axis, at least one delivery unit, in particular a wheel disk (Radscheibe), which is driven about the drive axis and serves for delivering a fluid, in particular a coolant, in particular as mentioned above, which has at least one delivery element, in particular a blade, and which has at least one separating device according to the invention, wherein the delivery unit is arranged at least largely around the drive axis in the impeller-side space.

The drive axis is arranged in particular within the bearing axis of the separating device. Preferably, the transport unit has at least one drive shaft, which is arranged on a drive shaft line. Preferably, the conveying element extends from the drive shaft into the impeller-side space. In particular, the conveying element preferably has a maximum lateral extent, at least substantially perpendicular to the drive axis, which is smaller than the minimum radial distance of the further sealing gap element, in particular of the inner face of the further sealing gap element, from the drive shaft. Preferably, the maximum lateral extent of the conveying element is greater than the minimum radial distance of the sealing gap element, in particular the inner face of the sealing gap element, from the drive shaft. Preferably, the conveying element defines at least one conveying channel for conveying the fluid. Preferably, the transport channel extends from a transport inlet of the transport channel, which is arranged at least substantially parallel to the drive axis, to a transport outlet of the transport channel, which is oriented at least substantially perpendicular to the drive axis. Preferably, the conveying unit, in particular the conveying element, is provided for guiding the fluid flow and/or the particle flow diverted and/or agitated by the flow recess and the sealing gap element along the wall of the conveying unit, in particular the conveying element, preferably by centrifugal forces caused by the rotation of the conveying element, in a direction away from the drive axis. It is conceivable that the conveying unit, in particular the conveying element, comprises at least one fluid guiding element on the side facing the flow recess, which is provided for guiding the fluid flow and/or the particle flow guided onto the wall in a direction away from the drive axis, in particular in a direction towards the further sealing gap element. For example, the fluid-directing elements are configured as shapes, flow elements, surface structures, fins, and/or other fluid-directing elements that would appear to be of interest to one of ordinary skill in the art. The conveying unit has in particular a plurality of conveying elements which are arranged in particular uniformly about the drive axis and define a plurality of conveying channels.

By means of the embodiment of the fluid machine according to the invention, an undesired penetration of the fluid flow and/or particle flow into the intermediate space of the drive shaft and the bearing receptacle can advantageously be prevented. An advantageously high separation rate of the fluid stream and/or the particle stream may be achieved. An advantageously high agitation of the fluid flow and/or the particle flow in the wheel side space can be achieved.

It is furthermore proposed that the maximum distance between the sealing gap element and the conveying element, which is oriented at least substantially parallel to the drive axis, is less than 2mm, preferably less than 1.5 mm, particularly preferably less than 1 mm. Preferably, the maximum distance between the sealing gap element and the conveying element, which is oriented at least substantially parallel to the drive axis, extends from the sealing gap face of the sealing gap element towards the conveying element, in particular towards at least one face of the conveying element, which is oriented at least substantially perpendicular to the drive axis. Preferably, the sealing gap element and/or the conveying element are arranged such that a sealing gap is formed between the sealing gap element and the conveying element, in particular by a maximum distance. The flow between the sealing gap element and the conveying element out of the flow recess can advantageously be prevented. The fluid flow and/or the particle flow can advantageously be guided past a sealing gap formed between the sealing gap element and the conveying element inside the flow recess.

It is furthermore proposed that the stirring unit has at least one, in particular the aforementioned further sealing gap element, which is arranged at least partially within the maximum longitudinal extension of the conveying element, at least substantially perpendicularly to the drive axis. In particular, the maximum longitudinal extension is oriented at least substantially parallel to the drive axis. Preferably, the further sealing gap element, at least substantially seen perpendicularly to the drive axis, is arranged outside a maximum longitudinal extension of the delivery outlet of the delivery channel, which is in particular oriented at least substantially parallel to the drive axis. Preferably, the maximum longitudinal extension of the delivery outlet of the delivery channel corresponds at least substantially to the opening width of the fluid opening, in particular at least partially defined by the further sealing gap element. In particular, the conveying element is arranged relative to the separating device such that the conveying outlet and the fluid opening are arranged one after the other, as seen in at least one section plane of the fluid machine through the drive axis, in a manner that they coincide with one another as seen from the drive axis. Preferably, the side of the further sealing gap element is arranged at least partially, in particular as seen in at least one section plane of the fluid machine passing through the drive axis, in a plane with an inner face of the conveying element defining the conveying outlet. Preferably, the inner face of the conveying element defining the conveying outlet is oriented at least substantially perpendicular to the drive axis. The inner face of the conveying element defining the conveying outlet is arranged facing away from the flow recess. An advantageously small fluid flow and/or particle flow from the spiral space back into the flow recess can be achieved. The fluid flow and/or the particle flow can advantageously be prevented from flowing from the conveying channel directly into the flow recess.

It is furthermore proposed that the maximum distance between the further sealing gap element and the conveying element, which is oriented at least substantially perpendicularly to the drive axis, is less than 2 mm, preferably less than 1.5 mm and particularly preferably less than 1 mm. Preferably, the maximum distance between the further sealing gap element and the conveying element, which is oriented at least substantially perpendicularly to the drive axis, extends from the inner side of the further sealing gap element towards the side of the conveying element surrounding (umranden) the conveying outlet, wherein in particular the side of the conveying element is oriented at least partially at least substantially parallel to the drive axis. Preferably, the further sealing gap element and/or the conveying element are arranged such that a further sealing gap is formed between the further sealing gap element and the conveying element, in particular by a maximum distance. An advantageously small fluid flow and/or particle flow from the spiral space, in particular through the further sealing gap, back into the flow recess can be achieved. The flow of fluid and/or particle flow from the conveying channel directly into the flow recess can advantageously be prevented, in particular because the further sealing gap is arranged at least substantially parallel to the outflow direction of the fluid and/or particle flow from the conveying outlet, wherein the fluid and/or particle flow from the conveying outlet is guided past the sealing gap.

Furthermore, it is proposed that the conveying element has at least one chamfer and/or at least one rounded portion in the edge region on at least one side facing the sealing gap element and/or the flow recess. Preferably, the chamfer and/or the rounding extends at least partially in a circumferential direction around the drive axis. In particular in the case of embodiments of the conveying element having a rounding, the rounding is preferably arranged on the side of the conveying element. In particular, in the case of a design of the conveying element with a chamfer, the chamfer is defined by a side face of the conveying element and/or by a face of the conveying element oriented at least substantially perpendicularly to the drive axis, which face in particular forms the sealing gap. Particularly preferably, the conveying element has at least one sealing edge, which is defined in particular by a side surface and an inner surface of the conveying element which defines the conveying outlet. In particular, the sealing edge of the conveying element is at least partially formed at least substantially perpendicularly to the drive axis and along a circumferential direction extending around the drive axis. Preferably, the side surfaces and the inner surface of the conveying element defining the conveying outlet are at least partially, in particular in the vicinity of the sealing edge around the conveying element, at an angle of in particular at most 90 °, preferably at most 80 °, and particularly preferably at most 70 °. An advantageously high flow from the flow recess into the spiral space can be achieved, in particular because the fluid flow and/or the particle flow diverted and/or agitated by the flow recess and the sealing gap element can advantageously be guided past by the chamfer and/or the rounding.

It is furthermore proposed that the sealing gap element has a minimum radial distance from the drive axis, which corresponds to at most 90%, in particular at most 80%, preferably at most 70% and particularly preferably at most 60% of the maximum radial extent of the conveying element around the drive axis. Preferably, the minimum radial distance of the sealing gap element relative to the drive axis is in particular at least 30%, preferably at least 40% and particularly preferably at least 50% of the maximum radial extent of the conveying element around the drive axis. In particular, the minimum radial distance of the sealing gap element from the drive axis extends at least substantially perpendicularly to the drive axis. Preferably, the minimum radial distance of the sealing gap element relative to the drive axis extends from the inner face of the sealing gap element towards the drive axis. An advantageously large flow recess can be achieved, in particular because the further sealing gap element defining the flow recess is arranged around the drive axis outside the maximum radial extension of the conveying element. It is possible to achieve an advantageous and efficient guiding of the fluid flow and/or the particle flow from the flow recess back into the spiral space, in particular because the high rotational speed of the conveying element in the peripheral region of the outside of the conveying element can cause an increased centrifugal force for redirecting the fluid flow and/or the particle flow.

Here, the separating device according to the invention and/or the fluid machine according to the invention should not be limited to the above-described applications and embodiments. In particular, the separating device according to the invention and/or the fluid machine according to the invention may have a number different from the number of individual elements, components and units mentioned here in order to satisfy the mode of operation described here. Furthermore, in the value ranges given in this disclosure, values lying within the mentioned limits are also to be regarded as disclosed and can be used arbitrarily.

Drawings

Other advantages are given by the following description of the drawings. An embodiment of the invention is shown in the drawings. The figures, description and claims contain a number of combined features. Those skilled in the art can also suitably consider these features alone and sum up other combinations of interest. Wherein is shown:

figure 1 shows a schematic cross-section through a centre plane of a fluid machine according to the invention with a separation device according to the invention,

Figure 2 shows a schematic detail view of a cross section of a fluid machine according to the invention in the region of the impeller-side space of a separation device according to the invention,

Fig. 3 shows a schematic detail of a cross section of a fluid machine according to the invention in the region of the impeller-side space of a separating device according to the invention, with fluid flow through the sealing gap of the fluid machine, and

Fig. 4 shows a schematic cross-section of a fluid machine according to the invention with a separating device according to the invention through a plane oriented perpendicular to the centre plane of the fluid machine, with an exemplary fluid flow through the sealing gap of the fluid machine.

Detailed Description

A cross-sectional view through a fluid machine 10 is shown in fig. 1. The fluid machine 10 is configured as a coolant pump. Other designs of fluid machine 10 are contemplated. The fluid machine 10 has a housing 12, a drive unit 14 with a drive axis 16, a delivery unit 18 for delivering a fluid, in particular a coolant, which is driven about the drive axis 16, and a separating device 20. The conveying unit 18 is configured as a wheel disk and comprises a plurality of conveying elements 22 configured as blades, wherein in particular only one conveying element 22 is shown in the figures. However, other designs of the conveying unit 18 are also conceivable. The housing 12 is configured as part of the separating apparatus 20. The housing 12 has a bearing receptacle 24 defining a bearing axis 26. Preferably, the bearing housing 24 is arranged about a bearing axis 26. Bearing axis 26 is configured within drive axis 16. The cross section of fluid machine 10 shown in fig. 1 extends in particular through bearing axis 26 and drive axis 16. The housing 12 has an impeller side space 28, which is arranged in particular between the conveying unit 18, in particular the conveying element 22, and the housing 12, in particular the inner wall of the housing 12. Preferably, the impeller-side space 28 is arranged around the bearing axis 26 and/or the bearing receptacle 24. The conveying unit 18 comprises a drive shaft 30 on which the conveying element 22 is arranged. The drive unit 14 is provided to drive the conveying unit 18 about the drive axis 16 by means of a drive shaft 30, wherein in particular the conveying element 22 moves about the drive axis 16. The conveying element 22 extends from the drive shaft 30 into the impeller-side space 28. The drive shaft 30 and the drive unit 14 are at least partially disposed within the bearing housing 24 of the housing 12. The separation device 20 comprises an agitation unit 32 for deflecting and/or agitating at least one fluid stream and/or particle stream 34. The agitation unit 32 is disposed on the housing 12. The agitating unit 32 includes a flow recess 38 defined by the wall 36 of the housing 12 that extends within the wheel side space 28 spaced from the bearing axis 26. The stirring unit 32 comprises a sealing gap element 40 arranged on the wall 36 of the housing 12, which sealing gap element is provided for deflecting and/or stirring at least one fluid flow and/or particle flow 34 flowing along the bearing axis 26 and/or towards the bearing axis 26 through the flow recess 38.

The conveying elements 22 each define a conveying channel 42 for conveying a fluid. The conveying channel 42 extends inside the conveying element 22 from a conveying inlet 44 of the conveying channel 42, which is arranged at least substantially parallel to the drive axis 16, to a conveying outlet 46 of the conveying channel 42, which is oriented at least substantially perpendicular to the drive axis 16. Preferably, the conveying unit 18, in particular the conveying element 22, is provided for guiding the fluid flow and/or the particle flow 34, which is diverted and/or agitated by the flow recess 38 and the sealing gap element 40, along the wall 48 of the conveying unit 18, in particular the conveying element 22, preferably by centrifugal forces caused by the rotation of the conveying element 22 about the drive axis 16, in a direction 50 away from the drive axis 16. It is conceivable that the conveying unit 18, in particular the conveying element 22, comprises at least one fluid guiding element 52 on the side facing the flow recess 38, which is provided for guiding the fluid flow and/or the particle flow 34 guided onto the wall 48 of the conveying unit 18 in a direction 50 facing away from the drive axis 16. For example, the fluid directing elements 52 are configured as shapes, flow elements, surface structures, fins, and/or other fluid directing elements 52 that would appear to one of ordinary skill in the art to redirect the fluid flow and/or the particle flow 34.

The sealing gap element 40 is constructed as a molded part configured as a sealing flange. The sealing gap element 40 is constructed integrally with the housing 12. The sealing gap element 40 is configured in the shape of a ring, as viewed along the bearing axis 26. The sealing gap element 40 is at least largely hollow-cylindrical in shape. The sealing gap element 40 has an at least approximately rectangular cross-sectional area 54 in a plane in which the bearing axis 26 is arranged. The sealing gap elements 40 are arranged uniformly around the bearing axis 26, wherein in particular the cross-sectional area 54 of the sealing gap elements 40 is at least substantially constantly embodied along a circumferential direction 56 around the bearing axis 26. The sealing gap element 40 has a central axis 58, wherein the sealing gap element 40 is in particular symmetrically configured about the central axis 58. The sealing gap element 40 is arranged such that the central axis 58 of the sealing gap element 40 is arranged inside the bearing axis 26. The sealing gap element 40 has an inner face 60 and an outer face 62, which are in particular at least partially arranged at least substantially parallel to one another. Preferably, the inner face 60 and the outer face 62 of the sealing gap element 40 are in particular arranged at least partially at least substantially parallel to the bearing axis 26. The outer surface 62 of the sealing gap element 40 is at least largely arranged on the side of the sealing gap element 40 facing away from the bearing axis 26. The inner face 60 of the sealing gap element 40 is arranged at least for the most part on the side of the sealing gap element 40 facing the bearing axis 26. The sealing gap element 40 has a sealing gap surface 64, which is arranged in particular at least substantially perpendicular to the bearing axis 26. Particularly preferably, the sealing gap surface 64 is configured as a ring. In particular, the seal clearance surface 64 is defined by the inner face 60 and the outer face 62 of the seal clearance element 40. However, other embodiments of the sealing gap element 40 are also conceivable, for example as a sealing ring and/or having a different shape than a hollow cylinder, in particular having other arrangements on the housing 12.

The housing 12, in particular the wall 36 of the housing 12 defining the flow recess 38, is configured such that the flow recess 38 is optimally configured, at least substantially perpendicularly to the bearing axis 26, when viewed. The wall 36 of the housing 12, which delimits the flow recess 38, has a contour 66, viewed at least substantially perpendicularly to the bearing axis 26, which is of rounded, in particular at least partially oval, design. In particular, the contour 66 of the wall 36 of the housing 12, which defines the flow recess 38, is embodied without an angle. The flow recess 38 is arranged in an edge region 68 of the impeller-side space 28, which is spaced apart from the bearing axis 26. The flow recess 38 is fluidically connected to the wheel-side space 28. The flow recess 38 extends at least substantially entirely around the bearing axis 26. Seen in the circumferential direction 56 about the bearing axis 26, the flow recess 38 has a cross-sectional area 70 which has a maximum deviation in the circumferential direction 56 of at most 5%, preferably at most 3% and particularly preferably at most 1% from the average value of the cross-sectional area 70 of the flow recess 38. The housing 12 has a spiral space 72 which is fluidically connected to the impeller-side space 28 and the flow recess 38. The spiral space 72 extends at least substantially entirely around the bearing axis 26. The spiral space 72 is at least partially configured as a volute, as viewed along the bearing axis 26. The spiral space 72 adjoins the edge region 68 of the wheel-side space 28 and/or the flow recess 38. The spiral space 72 comprises at least one outlet opening 74 (see fig. 4) for outputting the fluid to be moved. The spiral space 72 and the wheel side space 28 are connected to each other via a fluid opening 76. The fluid opening 76 has an opening width 78, viewed at least substantially perpendicular to the bearing axis 26, which is oriented at least substantially parallel to the bearing axis 26. The fluid opening 76 extends at least substantially entirely around the bearing axis 26. In particular, the opening width 78 of the fluid opening 76 in at least one point in the section plane through the bearing axis 26, in particular at least for the most part in the circumferential direction 56, is smaller than the maximum longitudinal extent 80 of the spiral space 72 in this point.

In particular, the fluid flow and/or the particle flow 34, which is moved by the conveying unit 18, flows at least partially along the wall 36 of the housing 12 from the spiral space 72 into the impeller-side space 28 and the flow recess 38 in the direction of the bearing axis 26. The fluid flow and/or the particle flow 34 are each shown in the drawing in an exemplary flow path. Preferably, the separating apparatus 20 is arranged to prevent fluid flow and/or particle flow 34 from flowing away from the wheel-side space 28 in the direction of the bearing axis 26. In particular, fluid flow and/or particle flow 34 is configured within a fluid to be moved by fluid machine 10. For example, the fluid stream and/or the particle stream 34 is configured as contaminants and/or residues within the fluid to be moved. Preferably, the stirring unit 32 is provided for deflecting the fluid flow and/or the particle flow 34 flowing through the flow recess 38 along and/or towards the bearing axis 26 in a direction 82 directed away from the wall 36 of the housing 12 and/or at least substantially parallel to the bearing axis 26 and/or parallel to the longitudinal extension of the sealing gap element 40.

The seal clearance element 40 at least partially defines the flow recess 38. The sealing gap element 40 is arranged on a wall 36 of the housing 12, which wall defines the flow recess 38. The outer surface 62 of the sealing gap element 40, at least substantially perpendicularly to the bearing axis 26, is preferably formed flush with the wall 36 of the housing 12 defining the flow recess 38 in one plane in the connection region 86 of the sealing gap element 40 and the wall 36 of the housing 12 defining the flow recess 38. The outer surface 62 of the sealing gap element 40 is rounded in the connection region 86 of the sealing gap element 40 and the wall 36 of the housing 12 defining the flow recess 38, in particular oriented transversely to the bearing axis 26.

The agitation unit 32 includes another sealing gap element 88 disposed on the wall 36 of the housing 12 and at least partially defining the flow recess 38. The further sealing gap element 88 is formed as a molded part. However, other designs of the further sealing gap element 88 are also conceivable. The further sealing gap element 88 is formed integrally with the housing 12. The further sealing gap element 88 is of annular design, viewed along the bearing axis 26. The further sealing gap element 88 is at least partially hollow-cylindrically configured. The further sealing gap element 88 has a central axis 90, wherein in particular the further sealing gap element 88 is arranged such that the central axis 90 of the further sealing gap element 88 is arranged inside the bearing axis 26. The further sealing gap element 88 has an inner face 92 and an outer face 94, which are arranged at least partially at least substantially parallel to one another. The inner face 92 and the outer face 94 of the further sealing gap element 88 are arranged at least partially at least substantially parallel to the bearing axis 26. The further sealing gap element 88 has a side face 96 which is arranged in particular transversely, preferably at least in part at least substantially perpendicularly, to the bearing axis 26. The side 96 of the other seal clearance member 88 is defined by the inner 92 and outer 94 faces of the other seal clearance member 88. The further sealing gap element 88 is arranged on a wall 36 of the housing 12, which defines the flow recess 38. The outer surface 94 of the further sealing gap element 88 is arranged at least for the most part on the side of the further sealing gap element 88 facing away from the bearing axis 26. The inner face 92 of the further sealing gap element 88 is arranged at least for the most part on the side of the further sealing gap element 88 facing the bearing axis 26. In particular, the inner face 92 of the further sealing gap element 88, at least as seen substantially perpendicularly to the bearing axis 26, is preferably configured flush with the wall 36 of the housing 12 defining the flow recess 38 in one plane in the connecting region 98 of the further sealing gap element 88 and the wall 36 of the housing 12 defining the flow recess 38. Preferably, the inner face 92 of the sealing gap element 40 is rounded in a connection region 98 of the further sealing gap element 88 and the wall 36 of the housing 12 defining the flow recess 38, in particular oriented transversely to the bearing axis 26. The further sealing gap element 88 is constructed and/or arranged in such a way that the further sealing gap element 88, in particular the outer surface 94 of the further sealing gap element 88, at least partially delimits the spiral space 72. Another sealing gap element 88 is arranged between the impeller side space 28 and the screw space 72. The other sealing gap element 88, and in particular the side 96 of the other sealing gap element 88, at least partially defines the fluid opening 76.

In fig. 2, a cross-sectional view of the fluid machine 10 is shown in the region on one side of the drive axis 16 and/or the bearing axis 26. The sealing gap element 40 has a maximum width 100, in particular of at most 5 mm, preferably at most 3 mm and particularly preferably at most 2 mm, which is in particular oriented at least substantially perpendicular to the bearing axis 26 and/or the central axis 58 of the sealing gap element 40. The maximum width 100 of the sealing gap element 40 is in particular at least 1 mm, preferably at least 1.5 mm and particularly preferably at least 2 mm. The sealing gap surface 64 extends at least substantially completely over the maximum width 100 of the sealing gap element 40, at least substantially perpendicularly to the bearing axis 26. The conveying element 22 has, in particular, at least substantially perpendicularly to the drive axis 16, a maximum lateral extent 102 which is smaller than the minimum radial distance 104 of the further sealing gap element 88, in particular of the inner face 92 of the further sealing gap element 88, from the drive shaft 30. The maximum lateral extent 102 of the conveying element 22 is greater than the minimum radial distance 106 of the sealing gap element 40, in particular the inner face 60 of the sealing gap element 40, from the drive shaft 30. The further sealing gap element 88 has a maximum width 108, in particular of at most 5 mm, preferably of at most 3 mm and particularly preferably of at most 2 mm, which is in particular oriented at least substantially perpendicular to the bearing axis 26 and/or to the central axis 90 of the further sealing gap element 88. In particular, the fluid opening 76 extends along a maximum width 108 of the other seal gap element 88. The maximum width 108 of the further sealing gap element 88 is in particular at least 1 mm, preferably at least 1.5 mm and particularly preferably at least 2 mm. The further sealing gap element 88 has a larger maximum longitudinal extent than the sealing gap element 40, in particular at least substantially parallel to the bearing axis 26.

The further sealing gap element 88 has a minimum radial distance 110, viewed at least substantially perpendicularly to the bearing axis 26, relative to the bearing axis 26, which is greater than a minimum radial distance 112 of the sealing gap element 40 and the bearing axis 26, wherein the flow recess 38 is arranged between the sealing gap element 40 and the further sealing gap element 88, viewed from the bearing axis 26. The minimum radial distances 110, 112 of the sealing gap element 40 and the further sealing gap element 88 relative to the bearing axis 26 extend at least substantially perpendicularly to the bearing axis 26. The minimum radial spacing 112 of the seal clearance element 40 extends from the inner face 60 of the seal clearance element 40 toward the bearing axis 26. The minimum radial spacing 110 of the other seal clearance element 88 extends from the inner face 92 of the other seal clearance element 88 toward the bearing axis 26. The minimum radial distance 112 of the sealing gap element 40 is at least 40%, preferably at least 50% and particularly preferably at least 60% of the minimum radial distance 110 of the further sealing gap element 88. The seal clearance element 40 and the further seal clearance element 88 form a flow recess 38 in the wheel-side space 28 together with the wall 36 of the housing 12 defining the flow recess 38.

Two outer faces 92, 94, 96, in particular inner face 92, outer face 94 and/or side face 96, of the further sealing gap element 88 adjoining one another, which form a sealing edge 114 of the further sealing gap element 88, form, at least as viewed essentially perpendicularly to the bearing axis 26, in particular in the vicinity of the sealing edge 114 of the further sealing gap element 88, at least one angle 118 of less than 90 °, preferably less than 80 ° and particularly preferably less than 70 °. The angle 118 formed by the side face 96 of the further sealing gap element 88 and the outer face 94 or the inner face 92 of the further sealing gap element 88, in particular in the vicinity of the sealing edge 114 of the further sealing gap element 88, is in particular less than 90 °, preferably less than 80 ° and particularly preferably less than 70 °. The sealing edge 114 of the further sealing gap element 88 is arranged at least substantially perpendicularly to the bearing axis 26 and at least substantially completely around the bearing axis 26. The sealing edge 114 of the further sealing gap element 88 is arranged such that at least one of the two outer faces 92, 94, 96 of the further sealing gap element 88, in particular the inner face 92, which form the sealing edge 114 of the further sealing gap element 88, is oriented at least substantially parallel to the bearing axis 26.

The maximum distance 120 between the sealing gap element 40 and the conveying element 22, which is oriented at least substantially parallel to the drive axis 16, is in particular less than 2mm, preferably less than 1.5, mm, and particularly preferably less than 1, mm. Preferably, the maximum distance 120 between the sealing gap element 40 and the conveying element 22, which is oriented at least substantially parallel to the drive axis 16, extends from the sealing gap face 64 of the sealing gap element 40 toward the conveying element 22, in particular toward at least one face 122 of the conveying element 22, which is oriented at least substantially perpendicular to the drive axis 16. The sealing gap element 40 and the conveying element 22 are arranged such that a sealing gap is formed between the sealing gap element 40 and the conveying element 22, in particular by the maximum distance 120. The maximum distance 124 between the further sealing gap element 88 and the conveying element 22, which is oriented at least substantially perpendicular to the drive axis 16, is in particular less than 2mm, preferably less than 1.5 mm and particularly preferably less than 1 mm. Preferably, a maximum distance 124 between the further sealing gap element 88 and the conveying element 22, which is oriented at least substantially perpendicularly to the drive axis 16, extends from the inner face 92 of the further sealing gap element 88 toward a side 126 of the conveying element 22 surrounding the conveying outlet 46, wherein in particular the side 126 of the conveying element 22 is oriented at least partially at least substantially parallel to the drive axis 16. The further sealing gap element 88 and the conveying element 22 are arranged such that a further sealing gap is formed between the further sealing gap element 88 and the conveying element 22, in particular by the maximum distance 124.

The further sealing gap element 88 is arranged at least partially within the maximum longitudinal extension 128 of the conveying element 22, at least as seen substantially perpendicularly to the drive axis 16. The maximum longitudinal extension 128 of the conveying element 22 is oriented at least substantially parallel to the drive axis 16. The further sealing gap element 88, at least substantially perpendicularly to the drive axis 16, is arranged outside a maximum longitudinal extent 130 of the delivery outlet 46 of the delivery channel 42, which is in particular oriented at least substantially parallel to the drive axis 16. The maximum longitudinal extension 130 of the delivery outlet 46 of the delivery channel 42 corresponds at least substantially to the opening width 78 of the fluid opening 76, which is defined, in particular at least in part, by the further sealing gap element 88. In particular, the conveying element 22 is arranged relative to the separating device 20 in such a way that the conveying outlet 46 and the fluid opening 76 are arranged one after the other, as seen in at least one section plane of the fluid machine 10 through the drive axis 16, coincident with one another, starting from the drive axis 16. The side 96 of the further sealing gap element 88 is arranged at least partially, in particular as seen in at least one section plane of the fluid machine 10 through the drive axis 16, in a plane with an inner face 132 of the conveying element 22 defining the conveying outlet 46. The inner face 132 of the conveying element 22 defining the conveying outlet 46 is oriented at least substantially perpendicular to the drive axis 16. The inner face 132 of the conveying element 22 defining the conveying outlet 46 is arranged facing away from the flow recess 38.

The conveying element 22 has a rounded portion 134 in the edge region on the side facing the sealing gap element 40 and/or the flow recess 38. Alternatively or additionally, it is conceivable for the conveying element 22 to have a chamfer in the edge region on the side facing the sealing gap element 40 and/or the flow recess 38. The radius 134 extends at least partially along a circumferential direction 56 about the drive axis 16. The rounded portion 134 is preferably disposed on the side 126 of the conveying element 22. The conveying element 22 has at least one sealing edge 136, which is defined in particular by the side face 126 of the conveying element 22 and the inner face 132 defining the conveying outlet 46. The sealing edge 136 of the conveying element 22 is at least partially at least substantially perpendicular to the drive axis 16 and is formed along the circumferential direction 56 around the drive axis 16. The side face 126 of the conveying element 22 and the inner face 132 defining the conveying outlet 46 have an angle 138 of in particular at most 90 °, preferably at most 80 °, and particularly preferably at most 70 °, at least in part, in particular in the vicinity of a sealing edge 136 surrounding the conveying element 22.

The sealing gap element 40 has a minimum distance 112 relative to the drive axis 16, which corresponds to at most 90%, in particular at most 80%, preferably at most 70%, and particularly preferably at most 60% of the maximum radial extent 142 of the conveying element 22 around the drive axis 16. Preferably, the minimum distance 112 of the sealing gap element 40 relative to the drive axis 16 corresponds to in particular at least 30%, preferably at least 40%, and particularly preferably at least 50% of the maximum radial extent 142 of the conveying element 22 about the drive axis 16. In particular, the minimum distance 112 of the sealing gap element 40 relative to the drive axis 16 extends at least substantially perpendicular to the drive axis 16. Preferably, the minimum distance 112 of the sealing gap element 40 relative to the drive axis 16 extends from the inner face 60 of the sealing gap element 40 toward the drive axis 16.

An exemplary fluid flow and/or particulate flow 34 through fluid machine 10 is shown in fig. 3 and 4. In fig. 3, fluid machine 10 is similar to fig. 2 as a cross-sectional view extending through bearing axis 26 and drive axis 16. In fig. 4, fluid machine 10 is shown in a cross-sectional plane oriented at least substantially perpendicular to bearing axis 26 and drive axis 16. The delivery unit 18 is provided for moving the fluid flow and/or the particle flow 34 through the delivery channel 42 into the wheel-side space 28 and/or the screw space 72. The fluid flow and/or particle flow 34 moving from the spiral space 72 and/or the transport channel 42 into the flow recess 38 and the fluid flow and/or particle flow 34 moving from the flow recess 38 into the spiral space 72 and/or the transport channel 42 are related to the volume, in particular the cross-sectional area, of the spiral space 72 at a position around the bearing axis 26. Preferably, the spiral space 72 has a maximum longitudinal extent 80 that remains at least substantially unchanged along the circumferential direction 56 about the bearing axis 26, wherein a maximum lateral extent 148 of the spiral space 72 that is oriented at least substantially perpendicular to the bearing axis 26 changes, in particular along the circumferential direction 56 about the bearing axis 26. If the maximum lateral extent 148 of the spiral space 72 is greater than the limit 150 (see fig. 4) of the maximum lateral extent 148, the fluid flow and/or the particle flow 34 moves from the flow recess 38 into the spiral space 72 and/or the conveying channel 42. If the maximum lateral extent 148 of the spiral space 72 is less than the limit 150 (see fig. 4) of the maximum lateral extent 148, the fluid flow and/or the particle flow 34 moves from the spiral space 72 and/or the conveying channel 42 into the flow recess 38. Preferably, the separating apparatus 20 is arranged to move the fluid and/or particulate flow 34 from the spiral space 72 out of the fluid machine 10 through the output opening 74.

Claims

1. A separating device for a fluid machine, having at least one housing (12) with at least one bearing receptacle (24) which defines at least one bearing axis (26) and which has at least one impeller-side space (28), having a conveying unit (18) for conveying a fluid, which conveying unit comprises a conveying element (22) with a conveying outlet (46), and having at least one stirring unit (32) for deflecting and/or stirring at least one fluid flow and/or particle flow (34), wherein the stirring unit (32) has at least one flow recess (38) defined by a wall (36) of the housing (12) which extends inside the impeller-side space (28) at a distance from the bearing axis (26), characterized in that the stirring unit (32) comprises at least one sealing gap element (40) arranged on the wall (36) of the housing (12) for deflecting and/or stirring at least one fluid flow and/or particle flow (34) along the bearing axis (26) through the flow recess (38),

Wherein the stirring unit (32) comprises at least one further sealing gap element (88), wherein at least two mutually adjoining outer faces (92, 94, 96) of the further sealing gap element (88) forming a sealing edge (114) form an angle (118) of less than 90 DEG, viewed at least substantially perpendicularly to the bearing axis (26),

Wherein the further sealing gap element (88) has a side surface (96) which is arranged at least partially in a plane with an inner surface (132) of the conveying element (22) which defines the conveying outlet (46).

2. A separation device according to claim 1, wherein the stirring unit (32) is arranged on the housing (12).

3. The separation device according to claim 1, wherein the sealing gap element (40) at least partially defines a flow recess (38).

4. A separating device as claimed in any one of claims 1 to 3, characterized in that the further sealing gap element (88) is arranged on a wall (36) of the housing (12) and at least partially defines the flow recess (38).

5. A separating device as claimed in any one of claims 1 to 3, characterized in that the further sealing gap element (88) has a minimum radial distance (110) from the bearing axis (26) as seen at least substantially perpendicularly to the bearing axis (26), which is greater than a minimum radial distance (112) of the sealing gap element (40) from the bearing axis (26), wherein the flow recess (38) is arranged between the sealing gap element (40) and the further sealing gap element (88) as seen from the bearing axis (26).

6. A separating device as claimed in any one of claims 1 to 3, characterized in that at least one of the outer faces (92, 96) of the other sealing gap element (88) forming the sealing edge (114) is oriented at least substantially parallel to the bearing axis (26).

7. A fluid machine having at least one drive unit (14) with at least one drive axis (16), having at least one transport unit (18) driven about the drive axis (16) for transporting a fluid, having at least one transport element (22), and having at least one separating device (20) according to any one of claims 1 to 6, wherein the transport unit (18) is arranged at least largely about the drive axis (16) within the impeller-side space (28).

8. The fluid machine of claim 7, wherein the fluid machine is a coolant pump.

9. Fluid machine according to claim 7, characterized in that the transport unit (18) is a wheel disc.

10. The fluid machine of claim 7, wherein the transport fluid is a coolant.

11. The fluid machine according to claim 7, characterized in that the conveying element (22) is a blade.

12. The fluid machine according to any one of claims 7 to 11, characterized in that a maximum distance (120) between the sealing gap element (40) and the conveying element (22) oriented at least substantially parallel to the drive axis (16) is less than 2mm.

13. Fluid machine according to any one of claims 7 to 11, characterized in that the further sealing gap element (88), at least substantially perpendicularly to the drive axis (16), is at least partially arranged within the maximum longitudinal extension (102) of the conveying element (22).

14. Fluid machine according to claim 13, characterized in that the maximum distance (124) between the further sealing gap element (88) and the conveying element (22) oriented at least substantially perpendicularly to the drive axis (16) is less than 2mm.

15. The fluid machine according to any one of claims 7 to 11, characterized in that the conveying element (22) has at least one chamfer and/or at least one rounding (134) in the edge region on at least one side facing the sealing gap element (40) and/or the flow recess (38).

16. The fluid machine according to any one of claims 7 to 11, characterized in that the sealing gap element (40) has a minimum radial spacing (112) with respect to the drive axis (16), which corresponds to at most 90% of the maximum radial extension (142) of the conveying element (22) around the drive axis (16).