CN114667396A - Separating device and fluid machine with a separating device - Google Patents

Abstract

The invention relates to a separating device for a turbomachine, comprising at least one housing (12) having at least one bearing receptacle (24) which defines at least one bearing axis (26) and having at least one impeller-side chamber (28), and comprising at least one stirring unit (32), which is arranged in particular on the housing (12) for deflecting and/or stirring at least one fluid and/or particle flow (34), wherein the stirring unit (32) has at least one flow recess (38) which is defined by a wall (36) of the housing (12) and which extends inside the impeller-side chamber (28) at a distance from the bearing axis (26). The invention proposes that the stirring unit (32) comprises at least one sealing gap element (40) arranged on a wall (36) of the housing (12), which sealing gap element is provided for deflecting and/or stirring at least one fluid and/or particle flow (34) flowing through the flow recess (38) along and/or towards the bearing axis (26).

Description

Separating device and fluid machine with a separating device

Technical Field

A separating device for a turbomachine (string mini-singmaschine) has already been proposed, which has 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 (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 and/or particle stream, wherein the stirring unit has at least one flow recess which is defined by a wall of the housing and which 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 turbomachine, having 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 having at least one stirring unit which is arranged, in particular, on the housing for deflecting and/or stirring at least one fluid and/or particle stream, wherein the stirring unit has at least one flow recess which is defined by a wall of the housing and which extends inside the impeller-side space at a distance from the bearing axis.

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

Preferably, the sealing gap element is configured as a shaped part, a sealing ring, a sealing flange or the like. The sealing gap element is preferably fastened to the housing, in particular is formed in one piece with the housing. "integrally" is to be understood to mean, in particular, a material-to-material connection, such as, for example, by a welding process and/or an adhesive process, and is particularly advantageously molded, for example, by being produced from a casting and/or by being produced in a single-component or multi-component injection molding method. Particularly preferably, the sealing gap element is of annular design, viewed along the bearing axis. Preferably, the sealing gap element is designed 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 seal gap elements are arranged uniformly about the bearing axis. Preferably, the seal gap element has a central axis, wherein the seal 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 within the bearing axis. Preferably, the sealing gap element has a maximum width of, in particular, at most 5 mm, preferably at most 3 mm and particularly preferably at most 2 mm. Preferably, the maximum width of the sealing gap element is oriented at least substantially perpendicularly to the bearing axis and/or the central axis. "substantially perpendicular" is to be understood to mean, in particular, an orientation of a line or a plane, in particular a viewing plane, relative to a further line or a further plane, in particular a bearing axis, wherein the line or the plane, viewed in particular in a projection plane, encloses an angle of 90 ° and the angle has a maximum deviation, in particular of less than 8 °, advantageously of less than 5 °, and particularly advantageously of less than 2 °. Preferably, the maximum width of the sealing gap element is in particular at least 1 mm, 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 arranged, in particular, at least partially, at least substantially parallel to one another. One face, in particular the outer face, of the seal gap element is oriented "substantially parallel" to a root axis, a plane or another face, in particular the inner face of the seal gap element, in particular it being understood that the face in each point of the face has a minimum spacing relative to the root axis, the plane or the other face which differs by less than 5%, preferably less than 3% and particularly preferably less than 1% for all points and the average of the minimum spacings of all points. Preferably, the inner and outer faces of the sealing gap element are arranged, in particular, at least partially, at least substantially parallel to the bearing axis. In particular, the outer face of the seal gap element is arranged at least for the most part on the side of the seal gap element facing away from the bearing axis. Preferably, the inner face of the sealing gap element is arranged at least predominantly 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 seal gap face, at least substantially perpendicularly to the bearing axis, extends at least substantially completely over the maximum width of the seal gap element. Particularly preferably, the sealing gap face is configured as a ring. In particular, the seal clearance face is defined by an inner face and/or an outer face of the seal clearance 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 within a fluid to be moved by means of a fluid machine. For example, the fluid flow and/or the particle flow are configured as contaminants and/or residues within the fluid to be moved. Preferably, the agitation unit is provided for deflecting the fluid flow and/or the 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 seal gap element.

Preferably, the housing, in particular the wall of the housing, which delimits the flow recess, is designed in such a way that the flow recess is optimally designed, at least viewed substantially perpendicularly to the bearing axis. In particular, the wall of the housing which delimits the flow recess, viewed at least substantially perpendicularly to the bearing axis, has a rounded, in particular at least partially elliptically shaped contour. In particular, the contour of the wall of the housing which delimits the flow recess is designed to be corner-free. The flow recess is preferably arranged in an edge region of the wheel-side space which is spaced apart from the bearing axis. The flow recess is in particular fluidically connected to the impeller-side space. Preferably, the flow recess extends at least substantially completely 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 in the circumferential direction of at most 5%, preferably at most 3% and particularly preferably at most 1% of the mean value of the cross-sectional areas of the flow recess. Preferably, the bearing receptacle is arranged around the bearing axis. Preferably, the wheel-side space is arranged around the bearing axis and/or the bearing receptacle. Preferably, the housing has a spiral space (spiralarum) 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, viewed along the bearing axis. Particularly preferably, the spiral space adjoins an edge region of the wheel-side space and/or the flow recess. Preferably, the spiral space comprises at least one outlet opening for the fluid to be moved. In particular, the spiral space and the wheel-side space are connected to each other by at least one fluid opening. Preferably, the fluid opening has an opening width, viewed at least substantially perpendicularly to the bearing axis, which is oriented at least substantially parallel to the bearing axis. "substantially parallel" is to be understood in particular as meaning the orientation of a line or a plane, in particular the opening width of a fluid opening, relative to a further line or a further plane, in particular a bearing axis, wherein the line or the plane has a deviation, in particular in the projection plane, of in particular less than 8 °, advantageously less than 5 ° and particularly advantageously less than 2 ° relative to the further line or the further plane. Preferably, the fluid opening extends at least substantially completely around the bearing axis. In particular, the opening width of the fluid opening at least one point in a sectional plane through the bearing axis, in particular at least for the most part in the circumferential direction, is smaller than the maximum longitudinal extent of the helical space at this point.

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

It is furthermore proposed that the seal 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 face of the seal gap element, viewed at least substantially perpendicularly to the bearing axis, is preferably formed flush with the wall of the housing delimiting the flow recess in one plane in the connecting region of the seal gap element and the wall of the housing delimiting the flow recess. Preferably, the outer face of the seal gap element is rounded in the connecting region of the seal gap element and the wall of the housing which delimits the flow recess, in particular is 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 wheel-side space by the sealing gap element. A advantageously high degree of agitation of the fluid flow and/or 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 designed as a shaped part. Preferably, the further sealing gap element is fixed to the housing, in particular is formed in one piece with the housing. Particularly preferably, the further sealing gap element is designed as a ring, viewed along the bearing axis. Preferably, the further sealing gap element is at least partially designed 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 its center axis is arranged within the bearing axis. The further sealing gap element preferably has a maximum width of, in particular, at most 5 mm, 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 perpendicularly to the bearing axis and/or perpendicularly to the center axis of the further sealing gap element. Preferably, the maximum width of the further sealing gap element is in particular at least 1 mm, 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 in sections at least substantially parallel to one another. Preferably, the inner face and the outer face of the further sealing gap element are arranged at least partially at least substantially parallel to the bearing axis. Preferably, the further sealing gap element has at least one side face which is arranged, in particular, transversely, preferably at least partially, at least substantially perpendicularly, to the bearing axis. The side faces of the further sealing gap element are in particular defined by an inner face and/or an outer face of the further sealing gap element. Preferably, the further sealing gap element is arranged on a wall of the housing which defines 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, at least viewed substantially perpendicularly to the bearing axis, is preferably flush with the wall of the housing delimiting the flow recess in one plane in the connecting region of the further sealing gap element and the wall of the housing delimiting the flow recess. Preferably, the inner face of the seal-gap element is rounded, in particular oriented transversely to the bearing axis, in the region of the connection of the further seal-gap element and the wall of the housing which delimits the flow recess. Particularly preferably, the further sealing gap element is designed and/or arranged in such a way that the further sealing gap element, in particular the 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 wheel-side space and the spiral 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, a greater maximum transverse extent at least substantially parallel to the bearing axis than the sealing gap element. An advantageously directed flow into the flow recess can be achieved, in particular because the fluid flow and/or the particle flow can be guided directly into the flow recess along the further sealing gap element. An advantageously large flow recess can be achieved, in particular because the flow recess can be formed up to the side of the further sealing gap element.

It is furthermore proposed that the stirrer 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 spacing relative to the bearing axis which is greater than the minimum radial spacing 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 seal gap element and the further seal gap element with respect to the bearing axis extends at least substantially perpendicularly to the bearing axis. Preferably, the minimum radial spacing of the seal clearance element extends from an inner face of the seal clearance 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 seal gap element is at least 40%, preferably at least 50% and particularly preferably at least 60% of the minimum radial distance of the further seal gap element. Particularly preferably, the seal gap element and the further seal gap element form a flow recess in the wheel-side space together with a wall of the housing which delimits the flow recess. An advantageous arrangement of the flow recess 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 outer faces, in particular the aforementioned inner face, outer face and/or side faces, which adjoin one another and form a sealing edge, of the further sealing gap element, at least substantially perpendicularly with respect to the bearing axis, in particular in the vicinity of the sealing edge of the further sealing gap element, form at least one angle of less than 90 °, preferably less than 80 °, and particularly preferably less than 70 °. Preferably, the side face of the further seal-gap element and the outer face or the inner face of the further seal-gap element, in particular in the vicinity of the sealing edge of the further seal-gap element, enclose at least one angle, which is in particular less than 90 °, preferably less than 80 ° and particularly preferably less than 70 °. "vicinity" is to be understood to mean, in particular, a region around the component, in particular around the sealing edge, wherein each point in this region has a maximum distance of at most 5 mm, preferably at most 3 mm, and particularly preferably 1 mm, from the component. 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 particle flow from the spiral space, in particular from the side of the further sealing gap element, in particular from the side of the sealing edge of the further sealing gap element, into the wheel-side space and into the flow recess can be achieved. It is advantageously possible to prevent an undesired penetration of the fluid flow and/or particle flow 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, in particular, the aforementioned or a further sealing edge, which is arranged in such a way that at least one of the two outer faces, in particular the aforementioned inner face, of the further sealing gap element, which outer faces 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 particle flow from the spiral space, in particular from the side of the further sealing gap element, in particular from the side of the sealing edge of the further sealing gap element, into the wheel-side space and into the flow recess can be achieved. It is advantageously possible to prevent an undesired penetration of the fluid flow and/or particle flow into the bearing receptacle.

Furthermore, a turbomachine, in particular a coolant pump, is proposed, which has at least one drive unit having at least one drive axis, at least one conveying unit, in particular a wheel disk (Radscheibe), which is driven about the drive axis and which is used for conveying a fluid, in particular a coolant, in particular as mentioned above, the conveying unit having at least one conveying element, in particular a blade, and the turbomachine having at least one separating device according to the invention, wherein the conveying unit is arranged at least predominantly about the drive axis in the wheel-side space.

The drive axis is arranged in particular within the bearing axis of the separating device. Preferably, the conveying unit has at least one drive shaft, which is arranged on the drive axis. Preferably, the conveying element extends from the drive shaft into the wheel-side space. Particularly preferably, the conveying element has a maximum transverse extent, in particular at least substantially perpendicular to the drive axis, which is smaller than a minimum radial spacing of the further sealing gap element, in particular of an inner face of the further sealing gap element, from the drive shaft. Preferably, the maximum transverse extent of the conveying element is greater than the minimum radial spacing of the sealing gap element, in particular of the inner face of the sealing gap element, and the drive shaft. Preferably, the transport element defines at least one transport channel for transporting the fluid. Preferably, the conveying channel extends from a conveying inlet of the conveying channel, which is arranged at least substantially parallel to the drive axis, to a conveying outlet of the conveying channel, which is oriented at least substantially perpendicularly 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 redirected and/or agitated by the flow recess and the sealing gap element in a direction away from the drive axis along a wall of the conveying unit, in particular of the conveying element, preferably by centrifugal forces caused by the rotation of the conveying element. It is conceivable that the conveying unit, in particular the conveying element, comprises at least one flow guiding element on the side facing the flow recess, which flow guiding element is provided for guiding the fluid flow and/or the particle flow guided onto the wall in a direction facing away from the drive axis, in particular in a direction pointing towards the further sealing gap element. For example, the flow guiding element is configured as a shaping, flow element, surface structure, fin, and/or other flow guiding element that appears to be meaningful to a person skilled 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.

The design of the fluid machine according to the invention advantageously prevents an undesired penetration of fluid and/or particle flows into the intermediate space between the drive shaft and the bearing receptacle. A advantageously high separation rate of the fluid stream and/or the particle stream can be achieved. A advantageously high agitation of the fluid flow and/or particle flow in the impeller-side space can be achieved.

It is furthermore proposed that the maximum spacing between the sealing gap element and the conveying element, which is oriented at least substantially parallel to the drive axis, is less than 2 mm, preferably less than 1.5 mm, particularly preferably less than 1 mm. Preferably, the maximum distance between the sealing gap element and the transport 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 transport element, in particular towards at least one face of the transport element, which is oriented at least substantially perpendicularly 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 the sealing gap formed between the sealing gap element and the conveying element within 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 viewed 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, viewed at least substantially perpendicularly to the drive axis, is arranged outside a maximum longitudinal extent of the delivery outlet of the delivery channel, which maximum longitudinal extent 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 at least substantially corresponds 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 in such a way that the conveying outlet and the fluid opening, viewed in at least one section plane of the fluid machine through the drive axis, are arranged one behind the other, viewed in a manner overlapping one another, viewed from the drive axis. Preferably, the side of the further sealing gap element is arranged at least partially, in particular as viewed in at least one section plane of the turbomachine through the drive axis, in a plane having 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 perpendicularly to the drive axis. The inner face of the conveying element defining the conveying outlet is arranged facing away from the flow recess. A advantageously small fluid flow and/or particle flow from the spiral space back into the flow recess can be achieved. The flow of fluid and/or particles from the conveying channel directly into the flow recess can advantageously be prevented.

It is furthermore provided 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 spacing between the further sealing gap element and the conveying element, which is oriented at least substantially perpendicularly to the drive axis, extends from the interior of the further sealing gap element towards the side of the conveying element surrounding (umanden) 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 flow of fluid and/or particles from the spiral space, in particular back into the flow recess through the further sealing gap, can be achieved. The flow of fluid and/or particle flow from the supply 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 supply outlet, wherein the fluid and/or particle flow flowing from the supply 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 rounding in the edge region on at least one side facing the sealing gap element and/or the flow recess. Preferably, the chamfer and/or radius extends at least partially in a circumferential direction around the drive axis. In particular in the case of an embodiment of the conveying element with rounding, the rounding is preferably arranged on a side face of the conveying element. In particular in the case of an embodiment in which the conveying element has a chamfer, the chamfer is defined by a side face of the conveying element and/or by a face of the conveying element which is oriented at least substantially perpendicularly to the drive axis, which face in particular forms a sealing gap. In particular, the conveying element preferably has at least one sealing edge, which is defined in particular by a lateral surface and an inner surface of the conveying element that delimits 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 in a circumferential direction extending around the drive axis. Preferably, the side faces and the inner face of the conveying element which delimits the conveying outlet enclose an angle of, in particular, at most 90 °, preferably at most 80 °, and particularly preferably at most 70 °, at least in sections, in particular in the vicinity of the sealing edge which surrounds the conveying element. An advantageously high flow from the flow recess into the spiral space can be achieved, in particular because the fluid and/or particle flow diverted and/or agitated by the flow recess and the sealing gap element can advantageously be guided past the chamfer and/or rounding.

It is furthermore proposed that the sealing gap element has a minimum radial spacing relative to 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 about the drive axis. Preferably, the minimum radial spacing 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 about the drive axis. In particular, the minimum radial distance of the seal gap element from the drive axis extends at least substantially perpendicularly to the drive axis. Preferably, the minimum radial spacing of the seal clearance element relative to the drive axis extends from an inner face of the seal clearance 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 advantageously effective guidance of the fluid flow and/or particle flow from the flow recess back into the spiral space, in particular because a high rotational speed of the conveying element in the outer edge region of the conveying element can cause increased centrifugal forces for redirecting the fluid flow and/or particle flow.

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 can have a number which is different from the number of individual elements, components and units mentioned here in order to satisfy the mode of action described here. Furthermore, in the value ranges given in the present disclosure, values lying within the mentioned limits should also be regarded as disclosed and can be used arbitrarily.

Drawings

Other advantages are given by the following description of the figures. An embodiment of the invention is shown in the drawings. The figures, description and claims contain a large number of combined features. The person skilled in the art can also appropriately consider these features individually and conclude other combinations of significance. In which is shown:

figure 1 shows a schematic cross-sectional view of a fluid machine according to the invention with a separating device according to the invention through a central plane of the fluid machine,

figure 2 shows a schematic detail of a cross section of a turbomachine according to the invention in the region of the wheel-side space of a separating device according to the invention,

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

fig. 4 shows a schematic cross-sectional view of a turbomachine according to the invention with a separating device according to the invention through a plane oriented perpendicularly to the center plane of the turbomachine, with an exemplary fluid flow through a sealing gap of the turbomachine.

Detailed Description

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

The transport elements 22 each define a transport channel 42 for transporting a fluid. The conveying channel 42 extends within 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 perpendicularly to the drive axis 16. Preferably, the transport unit 18, in particular the transport element 22, is provided for guiding the fluid flow and/or the particle flow 34 diverted and/or agitated by the flow recess 38 and the sealing gap element 40 along a wall 48 of the transport unit 18, in particular of the transport element 22, preferably in a direction 50 away from the drive axis 16 by centrifugal forces caused by the rotation of the transport element 22 about the drive axis 16. It is conceivable that the conveying unit 18, in particular the conveying element 22, comprises at least one flow 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 flow guide elements 52 are configured as shapes, flow elements, surface structures, fins, and/or other flow guide elements 52 that appear meaningful to one skilled in the art for redirecting the fluid flow and/or the particle flow 34.

The sealing gap element 40 is designed as a molded part designed as a sealing flange. The sealing gap element 40 is formed integrally with the housing 12. The sealing gap element 40 is configured in the form of a ring, viewed along the bearing axis 26. The sealing gap element 40 is at least predominantly of hollow-cylindrical design. The seal 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 seal gap element 40 is arranged uniformly about the bearing axis 26, wherein in particular a cross-sectional area 54 of the seal gap element 40 is configured at least substantially constantly in a circumferential direction 56 about the bearing axis 26. The seal gap element 40 has a central axis 58, wherein the seal gap element 40 is in particular designed symmetrically about the central axis 58. The seal gap element 40 is arranged such that the center axis 58 of the seal gap element 40 is arranged within the bearing axis 26. The seal gap element 40 has an inner face 60 and an outer face 62, which are arranged, in particular, at least partially at least substantially parallel to one another. Preferably, the inner face 60 and the outer face 62 of the seal gap element 40 are arranged, in particular, at least partially at least substantially parallel to the bearing axis 26. The outer surface 62 of the seal gap element 40 is arranged at least for the most part on the side of the seal gap element 40 facing away from the bearing axis 26. The inner face 60 of the seal-gap element 40 is arranged at least for the most part on the side of the seal-gap element 40 facing the bearing axis 26. The seal gap element 40 has a seal gap surface 64 which is arranged, in particular, at least substantially perpendicularly to the bearing axis 26. Particularly preferably, the sealing gap face 64 is configured as a circular ring. In particular, the seal clearance face 64 is defined by the inner face 60 and the outer face 62 of the seal clearance member 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, which wall defines the flow recess 38, is designed in such a way that the flow recess 38 is optimally designed at least substantially perpendicularly to the bearing axis 26 with respect to flow. The wall 36 of the housing 12, which delimits the flow recess 38, at least substantially perpendicularly to the bearing axis 26, has a contour 66 which is of rounded, in particular at least partially oval, design. In particular, the contour 66 of the wall 36 of the housing 12 delimiting the flow recess 38 is configured without edges. The flow recess 38 is arranged in an edge region 68 of the wheel-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 completely around the bearing axis 26. Viewed 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 fluidically connects the wheel-side space 28 and the flow recess 38. The helical space 72 extends at least substantially completely around the bearing axis 26. The spiral space 72 is at least partially configured as a volute, 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 for the fluid to be moved (see fig. 4). The spiral space 72 and the wheel-side space 28 are connected to each other via a fluid opening 76. Viewed at least substantially perpendicularly to the bearing axis 26, the fluid opening 76 has an opening width 78 which is oriented at least substantially parallel to the bearing axis 26. The fluid opening 76 extends at least substantially completely around the bearing axis 26. In particular, the opening width 78 of the fluid opening 76 in at least one point, in particular at least for the most part, in a sectional plane through the bearing axis 26 in the circumferential direction 56 is smaller than the maximum longitudinal extent 80 of the helical space 72 in this point.

In particular, the fluid and/or particle flow 34 moved by means of the conveying unit 18 flows at least partially along the wall 36 of the housing 12 from the spiral space 72 into the wheel-side space 28 and the flow recess 38 in the direction of the bearing axis 26. The fluid and/or particle flow 34 is shown in the figures in an exemplary flow pattern. Preferably, the separating device 20 is provided for preventing a fluid flow and/or a particle flow 34 from flowing away from the wheel-side space 28 in the direction of the bearing axis 26. In particular, the fluid flow and/or the particle flow 34 is formed within the fluid to be moved by the fluid machine 10. For example, the fluid flow and/or particle flow 34 is configured as contaminants and/or residue within the fluid to be moved. Preferably, the agitation unit 32 is provided for deflecting the fluid flow and/or the particle flow 34 flowing through the flow recess 38 along the bearing axis 26 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 to the longitudinal extension of the seal clearance element 40.

The seal clearance member 40 at least partially defines the flow recess 38. The seal clearance member 40 is disposed on the wall 36 of the housing 12 that defines the flow recess 38. The outer face 62 of the seal play element 40, viewed at least substantially perpendicularly to the bearing axis 26, is preferably formed flush with the wall 36 of the housing 12 delimiting the flow recess 38 in one plane in a connecting region 86 of the seal play element 40 and the wall 36 of the housing 12 delimiting the flow recess 38. The outer face 62 of the seal play element 40 is rounded in the connecting region 86 of the seal play element 40 and the wall 36 of the housing 12 delimiting the flow recess 38, in particular oriented transversely to the bearing axis 26.

The agitation unit 32 includes another sealing clearance member 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 configured as a shaped part. However, other embodiments of the further sealing gap element 88 are also conceivable. The further sealing gap element 88 is formed integrally with the housing 12. Viewed along the bearing axis 26, the further sealing gap element 88 is of annular design. The further sealing gap element 88 is at least partially hollow-cylindrically formed. 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 within 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 other 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 partially at least substantially perpendicularly, to the bearing axis 26. The side 96 of the other seal clearance element 88 is defined by the inner face 92 and the outer face 94 of the other seal clearance element 88. The further sealing gap element 88 is arranged on a wall 36 of the housing 12, which wall defines the flow recess 38. The outer face 94 of the further seal-gap element 88 is arranged at least for the most part on the side of the further seal-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, viewed at least substantially perpendicularly to the bearing axis 26, is preferably flush with the wall 36 of the housing 12 delimiting the flow recess 38 in one plane in a connecting region 98 of the further sealing gap element 88 and the wall 36 of the housing 12 delimiting the flow recess 38. Preferably, the inner face 92 of the seal gap element 40 is rounded in a connecting region 98 of the further seal gap element 88 and the wall 36 of the housing 12 delimiting the flow recess 38, in particular oriented transversely to the bearing axis 26. The further sealing gap element 88 is designed and/or arranged in such a way that the further sealing gap element 88, in particular an outer surface 94 of the further sealing gap element 88, at least partially delimits the spiral space 72. Another seal gap member 88 is disposed between the wheel-side space 28 and the spiral space 72. The further sealing gap element 88, in particular a side 96 of the further sealing gap element 88, at least partially defines the fluid opening 76.

Fig. 2 shows a sectional view of the fluid machine 10 in the region on one side of the drive axis 16 and/or the bearing axis 26. The seal gap element 40 has a maximum width 100 of, in particular, at most 5 mm, preferably at most 3 mm and particularly preferably at most 2 mm, which is oriented, in particular, at least substantially perpendicularly to the bearing axis 26 and/or the central axis 58 of the seal 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 seal gap face 64, at least viewed substantially perpendicularly to the bearing axis 26, extends at least substantially completely over a maximum width 100 of the seal gap element 40. The conveying element 22, in particular, at least substantially perpendicularly to the drive axis 16, has a maximum transverse extent 102 which is smaller than a 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 transverse extent 102 of the conveying element 22 is greater than the minimum radial distance 106 of the seal gap element 40, in particular of the inner face 60 of the seal gap element 40, from the drive shaft 30. The further sealing gap element 88 has a maximum width 108 of, in particular, at most 5 mm, preferably at most 3 mm and particularly preferably at most 2 mm, which is, in particular, oriented at least substantially perpendicularly 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, in particular, a greater maximum longitudinal extent at least substantially parallel to the bearing axis 26 than the sealing gap element 40.

The further seal-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 seal-gap element 40 and the bearing axis 26, wherein the flow recess 38 is arranged between the seal-gap element 40 and the further seal-gap element 88, viewed from the bearing axis 26. The minimum radial distances 110, 112 of the seal-gap element 40 and the further seal-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 member 40 extends from the inner face 60 of the seal clearance member 40 toward the bearing axis 26. The minimum radial distance 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 seal 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 seal gap element 88. The seal clearance element 40 and the further seal clearance element 88 form the flow recess 38 in the wheel-side space 28 together with the wall 36 of the housing 12 which delimits the flow recess 38.

The two outer faces 92, 94, 96, in particular the inner face 92, the outer face 94 and/or the side face 96 of the further sealing gap element 88, which adjoin one another and form the sealing edge 114 of the further sealing gap element 88, at least substantially perpendicularly to the bearing axis 26, in particular in the vicinity of the sealing edge 114 of the further sealing gap element 88, form 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 96 of the further seal-gap element 88 and the outer face 94 or the inner face 92 of the further seal-gap element 88, in particular in the vicinity of the sealing edge 114 of the further seal-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 in such a way that at least one of the two outer faces 92, 94, 96, in particular the inner face 92, of the further sealing gap element 88, which forms 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 2 mm, preferably less than 1.5 mm, and particularly preferably less than 1 mm. Preferably, a maximum distance 120 between the seal gap element 40 and the transport element 22, which is oriented at least substantially parallel to the drive axis 16, extends from the seal gap face 64 of the seal gap element 40 to the transport element 22, in particular to at least one face 122 of the transport 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 perpendicularly to the drive axis 16, is in particular less than 2 mm, 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 face 126 of the conveying element 22 surrounding the conveying outlet 46, wherein in particular the side face 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, at least viewed substantially perpendicularly to the drive axis 16, is arranged at least partially within the maximum longitudinal extent 128 of the conveying element 22. The maximum longitudinal extent 128 of the conveying element 22 is oriented at least substantially parallel to the drive axis 16. The further sealing gap element 88, viewed 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 duct 42, which is oriented at least substantially parallel to the drive axis 16, in particular. The maximum longitudinal extent 130 of the delivery outlet 46 of the delivery channel 42 at least substantially corresponds to the opening width 78 of the fluid opening 76, in particular at least partially defined 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, viewed in at least one section plane of the fluid machine 10 through the drive axis 16, are arranged one behind the other, coinciding 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 viewed in at least one section plane of the fluid machine 10 through the drive axis 16, in a plane having an inner face 132 of the conveying element 22 which delimits the conveying outlet 46. The inner face 132 of conveying element 22 defining conveying outlet 46 is oriented at least substantially perpendicularly to drive axis 16. An inner face 132 of conveying element 22 defining conveying outlet 46 is arranged facing away from flow recess 38.

The conveying element 22 has a rounding 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 fillet 134 extends at least partially in the circumferential direction 56 about the drive axis 16. The rounded portion 134 is preferably disposed on the side 126 of the transport 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 that defines 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 in the circumferential direction 56 around the drive axis 16. The side face 126 of the conveying element 22 and the inner face 132 delimiting 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 sections, in particular in the vicinity of a sealing edge 136 around the conveying element 22.

The seal gap element 40 has a minimum spacing 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 a maximum radial extent 142 of the conveying element 22 about the drive axis 16. Preferably, the minimum spacing 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 seal gap element 40 relative to the drive axis 16 extends at least substantially perpendicularly to the drive axis 16. Preferably, the minimum spacing 112 of the seal clearance element 40 relative to the drive axis 16 extends from the interior face 60 of the seal clearance element 40 toward the drive axis 16.

An exemplary fluid flow and/or particulate flow 34 through fluid machine 10 is illustrated in fig. 3 and 4. In fig. 3, the fluid machine 10 is shown in a sectional view similar to fig. 2, extending through the bearing axis 26 and the drive axis 16. In fig. 4, the fluid machine 10 is shown in a sectional plane oriented at least substantially perpendicularly to the bearing axis 26 and the drive axis 16. The conveying unit 18 is provided for moving the fluid flow and/or the particle flow 34 through the conveying channel 42 into the wheel-side space 28 and/or the spiral space 72. The fluid and/or particle flow 34 moving from the spiral space 72 and/or the conveying channel 42 into the flow recess 38 and the fluid and/or particle flow 34 moving from the flow recess 38 into the spiral space 72 and/or the conveying 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 an at least substantially constant maximum longitudinal extent 80 in the circumferential direction 56 about the bearing axis 26, wherein a maximum transverse extent 148 of the spiral space 72, which is oriented at least substantially perpendicularly to the bearing axis 26, in particular varies in the circumferential direction 56 about the bearing axis 26. If the maximum lateral extension 148 of the helical space 72 is greater than a limit value 150 of the maximum lateral extension 148 (see fig. 4), the fluid flow and/or the particle flow 34 moves from the flow recess 38 into the helical space 72 and/or the conveying channel 42. If the maximum lateral extension 148 of the helical space 72 is less than the limit 150 of the maximum lateral extension 148 (see fig. 4), the fluid flow and/or the particle flow 34 moves from the helical space 72 and/or the conveying channel 42 into the flow recess 38. Preferably, the separation device 20 is provided for moving the fluid flow and/or the particle flow 34 out of the fluid machine 10 from the spiral space 72 through the outlet opening 74.

Claims (12)

1. A separating device for a turbomachine, having at least one housing (12) which has at least one bearing receptacle (24) which defines at least one bearing axis (26) and which has at least one impeller-side space (28) and which has at least one stirring unit (32) which is arranged in particular on the housing (12) and which serves for deflecting and/or stirring at least one fluid and/or particle stream (34), wherein the stirring unit (32) has at least one flow recess (38) which is defined by a wall (36) of the housing (12) and 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) which is arranged on the wall (36) of the housing (12), the seal gap element is provided for deflecting and/or agitating at least one fluid and/or particle flow (34) flowing through the flow recess (38) along and/or towards the bearing axis (26).

2. The separation device of claim 1, wherein the seal gap element (40) at least partially defines a flow recess (38).

3. The separating device according to claim 1 or 2, wherein the agitation unit (32) comprises at least one further sealing gap element (88) arranged on a wall (36) of the housing (12) and at least partially defining the flow recess (38).

4. The separating device according to one of the preceding claims, wherein the stirring unit (32) comprises at least one further seal gap element (88), the further seal gap element (88) having a minimum radial spacing (110) relative to the bearing axis (26), viewed at least substantially perpendicularly to the bearing axis (26), which is greater than a minimum radial spacing (112) of the seal gap element (40) from the bearing axis (26), wherein the flow recess (38), viewed from the bearing axis (26), is arranged between the seal gap element (40) and the further seal gap element (88).

5. Separating device according to one of the preceding claims, characterized in that the stirring unit (32) comprises at least one further sealing gap element (88), wherein at least two outer faces (92, 94, 96) of the further sealing gap element (88) adjoining one another, which outer faces form a sealing edge (114), form an angle (118) of less than 90 °, viewed at least substantially perpendicularly to the bearing axis (26).

6. Separating device according to one of the preceding claims, characterized in that the stirring unit (32) comprises at least one further sealing gap element (88) having a sealing edge (114) which is arranged such that at least one of the two outer faces (92, 96) of the further sealing gap element (88) forming the sealing edge (114) is oriented at least substantially parallel to the bearing axis (26).

7. Fluid machine, in particular coolant pump, having at least one drive unit (14) having at least one drive axis (16), having at least one conveying unit (18), in particular a wheel disc, driven about the drive axis (16) for conveying a fluid, in particular a coolant, having at least one conveying element (22), in particular a blade, and having at least one separating device (20) according to one of the preceding claims, wherein the conveying unit (18) is arranged at least predominantly about the drive axis (16) in the wheel-side space (28).

8. Fluid machine according to claim 7, characterised in that the maximum spacing (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 less than 2 mm.

9. Fluid machine according to claim 7 or 8, characterised in that the stirring unit (32) has at least one further sealing gap element (88) which, viewed at least substantially perpendicularly to the drive axis (16), is arranged at least partially within the maximum longitudinal extension (102) of the conveying element (22).

10. Fluid machine according to claim 9, characterised in that the maximum spacing (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) is less than 2 mm.

11. The separating device according to one of claims 7 to 10, 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).

12. The separating device according to one of claims 7 to 11, characterized in that the sealing gap element (40) has a minimum radial spacing (112) relative to the drive axis (16) which corresponds to at most 90% of a maximum radial extent (142) of the conveying element (22) about the drive axis (16).

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