Separation device and fluid machine having the separation device

Abstract

The invention relates to a separating device for a fluid machine, which has at least one housing (12) and at least one agitation unit (32). The housing has at least one bearing receiving part (24), which defines at least one bearing axis (26), and the housing has at least one impeller-side space (28). The agitation unit is particularly 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), and the flow recess extends spaced apart from the bearing axis (26) inside the impeller-side space (28). The invention provides that the agitation unit (32) includes at least one sealing gap element (40) arranged on the wall (36) of the housing (12), and the sealing gap element is arranged to deflect and / or agitate at least one fluid flow and / or particle flow (34) flowing along and / or towards the bearing axis (26) through the flow recess (38).

Description

Field of the Invention

[0001] A separating device for a fluid machine (Strömungsmaschine) has been proposed, which has at least one housing having at least one bearing receiving portion defining at least one bearing axis, and the housing having at least one impeller-side space (Radseitenraum), and the separating device having at least one, in particular arranged on the housing, swirling unit (Verwirbelungseinheit) for deflecting and / or swirling at least one fluid flow and / or particle flow, wherein the swirling unit has at least one flow recess defined by a wall of the housing, which flow recess extends spaced apart from the bearing axis inside the impeller-side space. Summary of the Invention

[0002] The present invention relates to a separating device for a fluid machine, which has at least one housing having at least one bearing receiving portion defining at least one bearing axis, and the housing having at least one impeller-side space, and the separating device having at least one, in particular arranged on the housing, swirling unit for deflecting and / or swirling at least one fluid flow and / or particle flow, wherein the swirling unit has at least one flow recess defined by a wall of the housing, which flow recess extends spaced apart from the bearing axis inside the impeller-side space.

[0003] The present invention proposes that the swirling unit includes at least one sealing gap element (Dichtspaltelement) arranged on the wall of the housing, which sealing gap element is provided for deflecting and / or swirling at least one fluid flow and / or particle flow flowing along and / or towards the bearing axis through the flow recess.

[0004] Preferably, the sealing gap element is configured as a shaped part, a sealing ring, a sealing flange or the like. Preferably, the sealing gap element is fixed to the housing, in particular integrally formed with the housing. "Integrally formed" should in particular be understood as a material-locking connection, such as, for example, by means of a welding process and / or an adhesive process, etc., and is particularly preferably molded, for example by manufacturing from a casting and / or by manufacturing using a single-component or multi-component injection molding method. Particularly preferably, when viewed along the bearing axis, the sealing gap element is configured as an annular shape. Preferably, the sealing gap element is configured as a hollow cylinder. Preferably, the sealing gap element has a cross-sectional area that is at least approximately rectangular in a plane in which the bearing axis is arranged. Preferably, the sealing gap element is arranged uniformly around the bearing axis. Preferably, the sealing gap element has a central axis, wherein the sealing gap element is in particular symmetrically configured around 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 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 perpendicular to the bearing axis and / or the central axis. "Substantially perpendicular" should in particular be understood as the orientation of a straight line or a plane, in particular an observation plane, relative to another straight line or another plane, in particular the bearing axis, wherein the straight line or the plane forms an angle of 90° with the other straight line or the other plane, in particular when 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 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 surface and at least one outer surface, and the inner surface and the outer surface are in particular at least partially and at least substantially parallel to each other. The orientation of one surface of the sealing gap element, in particular the outer surface, "substantially parallel to" an axis, a plane or another surface, in particular the inner surface of the sealing gap element, should in particular be understood as that the surface has a minimum distance from the axis, the plane or the other surface at each point of the surface, and the minimum distance at all points differs from the average value of the minimum distances at all points by less than 5%, preferably less than 3% and particularly preferably less than 1%. Preferably, the inner surface and the outer surface of the sealing gap element are in particular at least partially and at least substantially parallel to the bearing axis. In particular, the outer surface of the sealing gap element is arranged on the side of the sealing gap element facing away from the bearing axis for the most part. Preferably, the inner surface of the sealing gap element is arranged on the side of the sealing gap element facing the bearing axis for the most part. Preferably, the sealing gap element has at least one sealing gap surface, and the sealing gap surface is in particular at least substantially perpendicular to the bearing axis.Preferably, the sealing gap surface, viewed at least substantially perpendicular to the bearing axis, extends at least substantially completely over the maximum width of the sealing gap element. Particularly preferably, the sealing gap surface is configured as a ring. In particular, the sealing gap surface is delimited by the inner and / or outer surface of the sealing gap element.

[0005] Preferably, the separating device is arranged to prevent a fluid flow and / or a particle flow from flowing through from the impeller-side space in the direction of the bearing axis. In particular, the fluid flow and / or the particle flow is / are formed within the fluid to be moved by means of the fluid machine. For example, the fluid flow and / or the particle flow is configured as contaminants and / or residues in the fluid to be moved. Preferably, the agitation unit is arranged to deflect the fluid flow and / or the particle flow flowing along and / or towards the bearing axis through the flow recess in a direction which is away from the wall of the housing and / or is at least substantially parallel to the bearing axis and / or the longitudinal extent of the sealing gap element.

[0006] Preferably, the housing, in particular the wall of the housing that defines the flow recess, is configured such that the flow recess is optimally configured for flow optimization when viewed at least substantially perpendicular to the bearing axis. In particular, the wall of the housing that defines the flow recess has a rounded, in particular at least partially elliptical, configuration when viewed at least substantially perpendicular to the bearing axis. In particular, the contour of the wall of the housing that defines the flow recess is configured to be non-angular. The flow recess is preferably arranged in the edge region of the impeller-side space that is spaced apart from the bearing axis. The flow recess is in particular fluid-technically connected to the impeller-side space. Preferably, the flow recess extends at least substantially completely around the bearing axis. In particular, when viewed along the circumferential direction around the bearing axis, the flow recess has a cross-sectional area that 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 along the circumferential direction. Preferably, the bearing housing is arranged around the bearing axis. Preferably, the impeller-side space is arranged around the bearing axis and / or the bearing housing. Preferably, the housing has a spiral space that is fluid-technically connected to the impeller-side space and the flow recess. Preferably, the spiral space extends at least substantially completely around the bearing axis. Preferably, when viewed along the bearing axis, the spiral space is at least partially configured in a spiral shape. Particularly preferably, the spiral space abuts the edge region of the impeller-side space and / or the flow recess. Preferably, the spiral space includes at least one outlet opening for discharging the fluid to be moved. In particular, the spiral space and the impeller-side space are connected to each other through at least one fluid opening. Preferably, when viewed at least substantially perpendicular to the bearing axis, the fluid opening has an opening width that is at least substantially parallel to the bearing axis. "Substantially parallel" should in particular be understood as the orientation of a straight line or a plane, in particular the opening width of the fluid opening, relative to another straight line or another plane, in particular the bearing axis, where 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° relative to the other straight line or the other plane, in particular in the projection plane. Preferably, the fluid opening extends at least substantially completely around the bearing axis. In particular, the opening width of the fluid opening is less than the maximum longitudinal extent of the spiral space at least at one point in the cross-sectional plane passing through the bearing axis, in particular at least for the most part along the circumferential direction.

[0007] The advantageous design of the separation device according to the invention can advantageously prevent the undesired intrusion of fluid flows and / or particle flows into the bearing housing. A highly advantageous separation rate of the fluid flow and / or particle flow can be achieved. A highly advantageous agitation of the fluid flow and / or particle flow in the impeller-side space can be achieved.

[0008] Furthermore, it is proposed that the sealing gap element at least partially delimits the flow recess. Preferably, the sealing gap element is arranged on the wall of the housing that delimits the flow recess. In particular, when viewed at least substantially perpendicular to the bearing axis, the outer face of the sealing gap element is preferably flush with the wall of the housing that delimits the flow recess in a plane in the connection region between the sealing gap element and the wall of the housing that delimits the flow recess. Preferably, the outer face of the sealing gap element is rounded in the connection region between the sealing gap element and the wall of the housing that delimits the flow recess, in particular oriented transversely to the bearing axis. A advantageously large flow recess can be achieved, especially since the flow recess can be constructed into the impeller-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.

[0009] Furthermore, it is proposed that the agitation unit includes at least one further sealing gap element, which is arranged on the 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 fixed to the housing, in particular is integrally formed with the housing. Particularly preferably, when viewed along the bearing axis, the further sealing gap element is configured as an annular shape. 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 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 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 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 surface and at least one outer surface, and the inner surface and the outer surface are at least partially arranged at least substantially parallel to each other. Preferably, the inner surface and the outer surface 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 in particular transverse to, preferably at least partially at least substantially perpendicular to the bearing axis. The side surface of the further sealing gap element is in particular defined by the inner surface and / or the outer surface of the further sealing gap element. Preferably, the further sealing gap element is arranged on the wall of the housing that defines the flow recess. In particular, at least the vast majority of the outer surface of the further sealing gap element is arranged on the side of the further sealing gap element facing away from the bearing axis. Preferably, at least the vast majority of the inner surface of the further sealing gap element is arranged on the side of the further sealing gap element facing the bearing axis. In particular, the inner surface of the further sealing gap element, when viewed at least substantially perpendicular to the bearing axis, is preferably flush with the wall of the housing that defines the flow recess in a plane in the connection region between the further sealing gap element and the wall of the housing that defines the flow recess. Preferably, the inner surface of the sealing gap element is rounded in the connection region between the further sealing gap element and the wall of the housing that defines the flow recess, in particular oriented transversely to the bearing axis. Particularly preferably, the further sealing gap element is configured and / or arranged such 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 impeller-side space and the spiral space.Preferably, the other sealing gap element, in particular the side surface of the other sealing gap element, at least partially delimits a fluid opening. The other sealing gap element has a maximum lateral extent that is greater than that of the sealing gap element, in particular at least substantially parallel to the bearing axis. Advantageously directed flow into the flow recess can be achieved, in particular since the fluid flow and / or particle flow can be guided directly into the flow recess along the other sealing gap element. Advantageously large flow recesses can be achieved, in particular since the flow recesses can be configured up to the side surface of the other sealing gap element.

[0010] Furthermore, it is proposed that the agitation unit includes at least one, in particular the other sealing gap element mentioned above, which, when viewed at least substantially perpendicular to the bearing axis, has a minimum radial spacing relative to the bearing axis that is greater than the minimum radial spacing between the sealing gap element and the bearing axis, wherein the flow recess is arranged between the sealing gap element and the other sealing gap element when viewed from the bearing axis. Preferably, the minimum radial spacings of the sealing gap element and the other sealing gap element relative to the bearing axis extend at least substantially perpendicular to the bearing axis. Preferably, the minimum radial spacing of the sealing gap element extends from the inner face of the sealing gap element towards the bearing axis. Preferably, the minimum radial spacing of the other sealing gap element is arranged from the inner face of the other sealing gap element towards the bearing axis. Preferably, the minimum radial spacing of the sealing gap element is at least 40%, preferably at least 50% and particularly preferably at least 60% of the minimum radial spacing of the other sealing gap element. Particularly preferably, the sealing gap element and the other sealing gap element, together with the wall of the housing that delimits the flow recess, form a flow recess in the impeller-side space. Advantageous arrangement of the flow recesses can be achieved especially between the sealing gap elements. Advantageously large flow recesses can be achieved, in particular since the flow recesses can be formed by two sealing gap elements.

[0011] Furthermore, it is proposed that the agitation unit includes at least one, in particular another sealing gap element as mentioned above, wherein at least two outer faces of the another sealing gap element that are adjacent to each other and form a sealing edge, in particular the inner face, outer face and / or side face as mentioned above, form at least one angle of less than 90°, preferably less than 80° and particularly preferably less than 70° when observed at least substantially perpendicular to the bearing axis, particularly in the vicinity of the sealing edge of the another sealing gap element. Preferably, the side face of the another sealing gap element and the outer face or inner face of the another sealing gap element form at least one angle, particularly in the vicinity of the sealing edge of the another sealing gap element, which angle is particularly less than 90°, preferably less than 80° and particularly preferably less than 70°. The "vicinity" should particularly be understood as the area surrounding the component, particularly the area surrounding the sealing edge, wherein the maximum distance of each point within this area to the component is at most 5 mm, preferably at most 3 mm and particularly preferably 1 mm. In particular, the sealing edge of the another sealing gap element is at least substantially perpendicular to the bearing axis and is at least substantially completely arranged around the bearing axis. Advantageously small flow of the fluid flow and / or particle flow from the spiral space, in particular past the another sealing gap element, particularly past the sealing edge of the another sealing gap element, into the impeller-side space and the flow recess can be achieved. Unwanted intrusion of the fluid flow and / or particle flow into the bearing housing can be advantageously prevented.

[0012] Furthermore, it is proposed that the agitation unit includes at least one, in particular another sealing gap element as mentioned above, the another sealing gap element having in particular a sealing edge as mentioned above or another sealing edge, and the sealing edge being arranged such that at least one of the two outer faces of the another sealing gap element that form the sealing edge of the another sealing gap element, in particular at least one of the inner faces as mentioned above, is at least substantially oriented parallel to the bearing axis. Advantageously small flow of the fluid flow and / or particle flow from the spiral space, in particular past the another sealing gap element, particularly past the sealing edge of the another sealing gap element, into the impeller-side space and the flow recess can be achieved. Unwanted intrusion of the fluid flow and / or particle flow into the bearing housing can be advantageously prevented.

[0013] Furthermore, a fluid machine, in particular a coolant pump, is proposed, which has at least one drive unit, at least one conveying unit driven around a drive axis, in particular a wheel disc (Radscheibe), the drive unit having at least one drive axis, the conveying unit being used for conveying in particular the fluid as mentioned above, in particular coolant, the conveying unit having at least one conveying element, in particular a blade, and the fluid machine having at least one separating device according to the invention, wherein the conveying unit is arranged at least mostly around the drive axis in the impeller-side space.

[0014] 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 impeller-side space. Particularly preferably, the conveying element has a maximum lateral extent which is at least substantially perpendicular to the drive axis and which is less than the minimum radial spacing of the other sealing-gap element, in particular the inner face of the other sealing-gap element, from the drive shaft. Preferably, the maximum lateral extent of the conveying element is greater than the minimum radial spacing of the sealing-gap element, in particular the inner face of the sealing-gap element, from the drive shaft. Preferably, the conveying element delimits at least one conveying channel for conveying a fluid. Preferably, the conveying channel extends from a conveying inlet which is arranged at least substantially parallel to the drive axis of the conveying channel to a conveying outlet which is oriented at least substantially perpendicular to the drive axis of the conveying channel. Preferably, the conveying unit, in particular the conveying element, is designed to guide a fluid flow and / or a particle flow which has been deflected and / or agitated by the flow recess and the sealing-gap element along the wall of the conveying unit, in particular of the conveying element, preferably in a direction away from the drive axis by means of centrifugal force caused by the rotation of the conveying element. 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 fluid-guiding element is designed to guide a fluid flow and / or a particle flow which has been guided to the wall in a direction away from the drive axis, in particular in a direction towards the other sealing-gap element. For example, the fluid-guiding element is configured as a shaped part, a flow element, a surface structure, a fin and / or other fluid-guiding elements which are meaningful to a person skilled in the art. The conveying unit in particular has a plurality of conveying elements which are arranged, in particular, uniformly around the drive axis and delimit a plurality of conveying channels.

[0015] By virtue of the inventive design of the fluid machine, an undesired ingress of a fluid flow and / or a particle flow into the intermediate space between the drive shaft and the bearing receptacle can be advantageously prevented. A advantageously high separation rate of the fluid flow and / or the particle flow can be achieved. A advantageously high agitation of the fluid flow and / or the particle flow in the impeller-side space can be achieved.

[0016] Furthermore, it is proposed that the maximum spacing between the sealing gap element and the conveying element, which is at least substantially oriented parallel 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 sealing gap element and the conveying element, which is at least substantially oriented parallel to the drive axis, extends from the sealing gap surface of the sealing gap element towards the conveying element, in particular towards at least one surface of the conveying element that is at least substantially oriented 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 via the maximum spacing. The flow flowing out from the flow recess between the sealing gap element and the conveying element can be advantageously prevented. The fluid flow and / or particle flow can be advantageously guided past the sealing gap constructed between the sealing gap element and the conveying element inside the flow recess.

[0017] Furthermore, it is proposed that the agitation unit has at least one, in particular another sealing gap element as mentioned above, which, when viewed at least substantially perpendicular to the drive axis, is at least partially arranged within the maximum longitudinal extension of the conveying element. In particular, the maximum longitudinal extension is at least substantially oriented parallel to the drive axis. Preferably, the another sealing gap element, when viewed at least substantially perpendicular to the drive axis, is arranged outside the maximum longitudinal extension of the conveying outlet of the conveying channel, which maximum longitudinal extension is in particular at least substantially oriented parallel to the drive axis. Preferably, the maximum longitudinal extension of the conveying outlet of the conveying channel at least substantially corresponds to the opening width of the fluid opening that is at least partially defined by the another sealing gap element. In particular, the conveying element is arranged relative to the separation device such that the conveying outlet and the fluid opening, when viewed in at least one cross-sectional plane of the fluid machine passing through the drive axis and viewed from the drive axis, are arranged successively and coincide with each other. Preferably, at least part of the side surface of the another sealing gap element, in particular when viewed in at least one cross-sectional plane of the fluid machine passing through the drive axis, is arranged in a plane that has the inner surface of the conveying element that defines the conveying outlet. Preferably, the inner surface of the conveying element that defines the conveying outlet is at least substantially oriented perpendicular to the drive axis. The inner surface of the conveying element that defines the conveying outlet is arranged facing away from the flow recess. A advantageously small fluid flow and / or particle flow returning from the spiral space into the flow recess can be achieved. The fluid flow and / or particle flow can be advantageously prevented from flowing directly from the conveying channel into the flow recess.

[0018] Furthermore, it is proposed that the maximum spacing between the other sealing gap element and the conveying element, which is at least substantially perpendicular 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 other sealing gap element and the conveying element, which is at least substantially perpendicular to the drive axis, extends from the inner face of the other sealing gap element to the side face of the conveying element that surrounds (umranden) the conveying outlet, wherein in particular the side face of the conveying element is at least partially at least substantially parallel to the drive axis. Preferably, the other sealing gap element and / or the conveying element are arranged such that another sealing gap is formed between the other sealing gap element and the conveying element, in particular by means of the maximum spacing. Advantageously small fluid flows and / or particle flows can be achieved from the spiral space, in particular via the other sealing gap, back into the flow recess. Fluid flows and / or particle flows can be advantageously prevented from flowing directly from the conveying channel into the flow recess, in particular because the other sealing gap is arranged at least substantially parallel to the outflow direction in which the fluid flow and / or particle flow flows out of the conveying outlet, and the fluid flow and / or particle flow flowing out of the conveying outlet is guided past beside the sealing gap.

[0019] 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 the rounding at least partially extend along the circumferential direction around the drive axis. In particular, in a design of the conveying element with a rounding, the rounding is preferably arranged on the side face of the conveying element. In particular, in a design of the conveying element with a chamfer, the chamfer is defined by the side face of the conveying element and / or by a face of the conveying element that is at least substantially perpendicular to the drive axis, and this face in particular forms the sealing gap. Particularly preferably, the conveying element has at least one sealing edge, which is in particular defined by the side face and the inner face of the conveying element that defines the conveying outlet. In particular, the sealing edge of the conveying element at least partially at least substantially perpendicular to the drive axis and forms along the circumferential direction around the drive axis. Preferably, the side face and the inner face of the conveying element that defines the conveying outlet are at least partially, in particular in the region near the sealing edge of the conveying element, clamped at an angle of in particular at most 90°, preferably at most 80° and particularly preferably at most 70°. Advantageously high flow from the flow recess into the spiral space can be achieved, in particular because the fluid flow and / or particle flow diverted and / or agitated by the flow recess and the sealing gap element can be advantageously guided past beside the chamfer and / or the rounding.

[0020] Furthermore, it is proposed that the sealing gap element has a minimum radial spacing relative to the drive axis, which minimum radial spacing 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 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 around the drive axis. In particular, the minimum radial spacing of the sealing gap element from the drive axis extends at least substantially perpendicular to the drive axis. Preferably, the minimum radial spacing of the sealing gap element relative to the drive axis extends from the inner face of the sealing gap element towards the drive axis. Advantageously large flow recesses can be achieved, in particular since another sealing gap element defining the flow recess is arranged around the drive axis outside the maximum radial extent of the conveying element. An advantageous and effective guiding of the fluid flow and / or particle flow back into the spiral space can be achieved, in particular since the high rotational speed of the conveying element in the outer edge region of the conveying element can cause an increased centrifugal force for deflecting the fluid flow and / or particle flow.

[0021] Here, the separation device according to the invention and / or the fluid machine according to the invention should not be limited to the above applications and embodiments. In particular, the separation device according to the invention and / or the fluid machine according to the invention may have a number different from the number of the individual elements, components and units mentioned herein in order to fulfill the mode of action described herein. Furthermore, within the value ranges given in this disclosure, the values lying within the mentioned limits should also be considered as disclosed and can be used arbitrarily. Description of the Drawings

[0022] Other advantages are given by the following description of the drawings. An embodiment of the invention is shown in the drawings. The drawings, the description and the claims contain a large number of combined features. A person skilled in the art can also appropriately consider these features individually and derive other meaningful combinations therefrom. Shown therein:

[0023] Figure 1 A schematic cross-sectional view through the central plane of a fluid machine according to the invention having a separation device according to the invention is shown,

[0024] Figure 2 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 is shown,

[0025] Figure 3 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, having a fluid flow through the sealing gap of the fluid machine, and

[0026] Figure 4 A schematic sectional view of a fluid machine according to the invention with a separating device according to the invention is shown through a plane oriented perpendicular to the central plane of the fluid machine, with an exemplary fluid flow through the sealing gap of the fluid machine. DETAILED DESCRIPTION

[0027] In Figure 1 a sectional view through the fluid machine 10 is shown. The fluid machine 10 is configured as a coolant pump. However, other design options for 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 conveying unit 18 driven around the drive axis 16 for conveying a fluid, in particular a coolant, and a separating device 20. The conveying unit 18 is configured as a disk and includes a plurality of conveying elements 22 configured as blades, where in particular only one conveying element 22 is shown in the figure. However, other design options for the conveying unit 18 are also conceivable. The housing 12 is configured as part of the separating device 20. The housing 12 has a bearing receiving portion 24 that defines a bearing axis 26. Preferably, the bearing receiving portion 24 is arranged around the bearing axis 26. The bearing axis 26 is configured within the drive axis 16. The cross-section of the fluid machine 10 shown in Figure 1 in particular extends 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 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 receiving portion 24. The conveying unit 18 includes a drive shaft 30, and the conveying element 22 is arranged on the drive shaft. The drive unit 14 is configured to drive the conveying unit 18 around the drive axis 16 via the drive shaft 30, where in particular the conveying element 22 moves around 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 arranged within the bearing receiving portion 24 of the housing 12. The separating device 20 includes a stirring unit 32 for deflecting and / or stirring at least one fluid flow and / or particle flow 34. The stirring unit 32 is arranged on the housing 12. The stirring unit 32 includes a flow recess 38 defined by a wall 36 of the housing 12, which extends spaced apart from the bearing axis 26 within the impeller-side space 28. The stirring unit 32 includes a sealing gap element 40 arranged on the wall 36 of the housing 12, which is configured to deflect and / or stir 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.

[0028] The conveying element 22 delimits a conveying channel 42 for conveying a fluid, respectively. 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 configured to guide the fluid flow and / or particle flow 34 which is redirected 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 in a direction 50 away from the drive axis 16 by the centrifugal force caused by the rotation of the conveying 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 fluid guiding element 52 on the side facing the flow recess 38, which fluid guiding element is configured to guide the fluid flow and / or particle flow 34 guided onto the wall 48 of the conveying unit 18 in a direction 50 away from the drive axis 16. For example, the fluid guiding element 52 is configured as a shaped part, a flow element, a surface structure, a fin and / or other fluid guiding element 52 which is meaningful to a person skilled in the art for redirecting the fluid flow and / or particle flow 34.

[0029] The sealing clearance element 40 is configured as a formed part configured as a sealing flange. The sealing clearance element 40 is integrally configured with the housing 12. Viewed along the bearing axis 26, the sealing clearance element 40 is configured as an annular ring. The sealing clearance element 40 is configured at least mostly as a hollow cylinder. The sealing clearance element 40 has a cross-sectional area 54 that is at least approximately rectangular in a plane in which the bearing axis 26 is arranged. The sealing clearance element 40 is arranged uniformly around the bearing axis 26, wherein in particular the cross-sectional area 54 of the sealing clearance element 40 is configured to be at least substantially constant along the circumferential direction 56 around the bearing axis 26. The sealing clearance element 40 has a central axis 58, wherein in particular the sealing clearance element 40 is symmetrically configured around the central axis 58. The sealing clearance element 40 is arranged such that the central axis 58 of the sealing clearance element 40 is arranged inside the bearing axis 26. The sealing clearance element 40 has an inner face 60 and an outer face 62, and the inner face and the outer face are in particular at least partly arranged at least substantially parallel to each other. Preferably, the inner face 60 and the outer face 62 of the sealing clearance element 40 are in particular at least partly arranged at least substantially parallel to the bearing axis 26. The outer face 62 of the sealing clearance element 40 is arranged at least mostly on the side of the sealing clearance element 40 facing away from the bearing axis 26. The inner face 60 of the sealing clearance element 40 is arranged at least mostly on the side of the sealing clearance element 40 facing the bearing axis 26. The sealing clearance element 40 has a sealing clearance face 64, and the sealing clearance face is in particular at least substantially perpendicular to the bearing axis 26. Particularly preferably, the sealing clearance face 64 is configured as an annular ring. In particular, the sealing clearance face 64 is defined by the inner face 60 and the outer face 62 of the sealing clearance element 40. However, other design variants of the sealing clearance element 40 are also conceivable, for example as a sealing ring and / or having a shape different from that of a hollow cylinder, in particular having a different arrangement on the housing 12.

[0030] The housing 12, in particular the wall 36 of the housing 12 which defines the flow recess 38, is designed so that the flow recess 38 is designed to be flow-optimized when viewed at least substantially perpendicularly to the bearing axis 26. The wall 36 of the housing 12 which defines the flow recess 38, when viewed at least substantially perpendicularly to the bearing axis 26, has a contour 66 which is rounded, in particular at least partially elliptical. In particular, the contour 66 of the wall 36 of the housing 12 which defines the flow recess 38 is designed to be non-angular. The flow recess 38 is arranged in an edge region 68 of the impeller side chamber 28 which is spaced apart from the bearing axis 26. The flow recess 38 is fluidically connected to the impeller side chamber 28. The flow recess 38 extends at least substantially completely around the bearing axis 26. Viewed along the circumferential direction 56 about the bearing axis 26, the flow recess 38 has a cross-sectional area 70 which has a maximum deviation from an average value of the cross-sectional area 70 of the flow recess 38 along the circumferential direction 56 of at most 5%, preferably at most 3% and particularly preferably at most 1%. 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 completely around the bearing axis 26. Viewed along the bearing axis 26, the spiral space 72 is at least partially designed in a spiral shape. The spiral space 72 is adjacent to the edge region 68 of the impeller side space 28 and / or the flow recess 38. The spiral space 72 comprises at least one outlet opening 74 for discharging the fluid to be moved (see Figure 4 ). The spiral space 72 and the impeller 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 is smaller in at least one point in a sectional plane through the bearing axis 26, in particular at least for the most part along the circumferential direction 56, than the maximum longitudinal extension 80 of the spiral space 72 at this point.

[0031] In particular, the fluid flow and / or particle flow 34 moved by the conveying unit 18 flows at least partially along the wall 36 of the housing 12 from the spiral space 72 in the direction of the bearing axis 26 into the impeller-side space 28 and the flow recess 38. The fluid flow and / or particle flow 34 are each shown with an exemplary flow path in the drawing. Preferably, the separating device 20 is arranged to prevent the fluid flow and / or particle flow 34 from flowing away from the impeller-side space 28 in the direction of the bearing axis 26. In particular, the fluid flow and / or particle flow 34 is configured 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 residues within the fluid to be moved. Preferably, the agitation unit 32 is arranged to deflect the fluid flow and / or particle flow 34 flowing along and / or towards the bearing axis 26 through the flow recess 38 in a direction 82 that is 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 extent of the seal gap element 40.

[0032] The seal gap element 40 at least partially delimits the flow recess 38. The seal gap element 40 is arranged on the wall 36 of the housing 12 that delimits the flow recess 38. The outer face 62 of the seal gap element 40, viewed at least substantially perpendicular to the bearing axis 26, is preferably flush with the wall 36 of the housing 12 that delimits the flow recess 38 in a plane in the connection region 86 between the seal gap element 40 and the wall 36 of the housing 12 that delimits the flow recess 38. The outer face 62 of the seal gap element 40 is rounded in the connection region 86 between the seal gap element 40 and the wall 36 of the housing 12 that delimits the flow recess 38, in particular oriented transversely to the bearing axis 26.

[0033] The agitation unit 32 includes another seal gap element 88 which is arranged on the wall 36 of the housing 12 and at least partially defines the flow recess 38. The other seal gap element 88 is configured as a shaped part. However, other design options for the other seal gap element 88 can also be considered. The other seal gap element 88 is integrally constructed with the housing 12. Viewed along the bearing axis 26, the other seal gap element 88 is circularly constructed. The other seal gap element 88 is at least partially hollow cylindrical in construction. The other seal gap element 88 has a central axis 90, and in particular the other seal gap element 88 is arranged such that the central axis 90 of the other seal gap element 88 is arranged inside the bearing axis 26. The other seal gap element 88 has an inner face 92 and an outer face 94, and the inner face and the outer face are at least partially at least substantially parallel to each other. The inner face 92 and the outer face 94 of the other seal gap element 88 are at least partially at least substantially parallel to the bearing axis 26. The other seal gap element 88 has side faces 96 which are in particular arranged transversely to, preferably at least partially at least substantially perpendicular to, the bearing axis 26. The side faces 96 of the other seal gap element 88 are defined by the inner face 92 and the outer face 94 of the other seal gap element 88. The other seal gap element 88 is arranged on the wall 36 of the housing 12 which defines the flow recess 38. The outer face 94 of the other seal gap element 88 is arranged at least mostly on the side of the other seal gap element 88 facing away from the bearing axis 26. The inner face 92 of the other seal gap element 88 is arranged at least mostly on the side of the other seal gap element 88 facing the bearing axis 26. In particular, the inner face 92 of the other seal gap element 88, viewed at least substantially perpendicular to the bearing axis 26, is preferably flush with the wall 36 of the housing 12 which defines the flow recess 38 in a plane in the connection region 98 between the other seal gap element 88 and the wall 36 of the housing 12 which defines the flow recess 38. Preferably, the inner face 92 of the seal gap element 40 is rounded in the connection region 98 between the other seal gap element 88 and the wall 36 of the housing 12 which defines the flow recess 38, in particular oriented transversely to the bearing axis 26. The other seal gap element 88 is constructed and / or arranged such that the other seal gap element 88, in particular the outer face 94 of the other seal gap element 88, at least partially defines the spiral space 72. The other seal gap element 88 is arranged between the impeller-side space 28 and the spiral space 72. The other seal gap element 88, in particular the side faces 96 of the other seal gap element 88, at least partially define the fluid opening 76.

[0034] At Figure 2A sectional view of a fluid machine 10 in a region on one side of the drive axis 16 and / or the bearing axis 26 is shown. The sealing gap element 40 has a maximum width 100 of at most 5 mm, preferably at most 3 mm, and particularly preferably at most 2 mm, which maximum width is 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 at least 1 mm, preferably at least 1.5 mm, and particularly preferably at least 2 mm. The sealing gap surface 64, observed at least substantially perpendicular to the bearing axis 26, extends at least substantially completely over the maximum width 100 of the sealing gap element 40. The conveying element 22 has a maximum lateral extent 102 that is at least substantially perpendicular to the drive axis 16, and this maximum lateral extent is less than the minimum radial spacing 104 between the other sealing gap element 88, in particular the inner face 92 of the other sealing gap element 88 and the drive shaft 30. The maximum lateral extent 102 of the conveying element 22 is greater than the minimum radial spacing 106 between the sealing gap element 40, in particular the inner face 60 of the sealing gap element 40 and the drive shaft 30. The other sealing gap element 88 has a maximum width 108 of at most 5 mm, preferably at most 3 mm, and particularly preferably at most 2 mm, which maximum width is oriented at least substantially perpendicular to the bearing axis 26 and / or perpendicular to the central axis 90 of the other sealing gap element 88. In particular, the fluid opening 76 extends along the maximum width 108 of the other sealing gap element 88. The maximum width 108 of the other sealing gap element 88 is at least 1 mm, preferably at least 1.5 mm, and particularly preferably at least 2 mm. The other sealing gap element 88 has a maximum longitudinal extent that is greater than that of the sealing gap element 40 and is at least substantially parallel to the bearing axis 26.

[0035] Said another seal clearance element 88 has a minimum radial spacing 110 when observed relative to the bearing axis 26 and at least substantially perpendicular to the bearing axis 26, and said minimum radial spacing is greater than the minimum radial spacing 112 between the seal clearance element 40 and the bearing axis 26. Wherein, when observed from the bearing axis 26, the flow recess 38 is arranged between the seal clearance element 40 and said another seal clearance element 88. The minimum radial spacings 110, 112 of the seal clearance element 40 and the another seal clearance element 88 relative to the bearing axis 26 extend at least substantially perpendicular 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 towards the bearing axis 26. The minimum radial spacing 110 of the another seal clearance element 88 extends from the inner face 92 of the another seal clearance element 88 towards the bearing axis 26. The minimum radial spacing 112 of the seal clearance element 40 is at least 40%, preferably at least 50% and particularly preferably at least 60% of the minimum radial spacing 110 of the another seal clearance element 88. The seal clearance element 40 and the another seal clearance element 88 together with the wall 36 of the housing 12 that defines the flow recess 38 form the flow recess 38 in the impeller side space 28.

[0036] Two adjacent outer faces 92, 94, 96 of the another seal clearance element 88 that form the seal edge 114 of the another seal clearance element 88, especially the inner face 92, the outer face 94 and / or the side face 96, when observed at least substantially perpendicular to the bearing axis 26, especially form at least one angle 118 less than 90°, preferably less than 80° and particularly preferably less than 70° in the vicinity of the seal edge 114 of the another seal clearance element 88. The angle 118 formed by the side face 96 of the another seal clearance element 88 and the outer face 94 or the inner face 92 of the another seal clearance element 88 especially in the vicinity of the seal edge 114 of the another seal clearance element 88 is especially less than 90°, preferably less than 80° and particularly preferably less than 70°. The seal edge 114 of said another seal clearance element 88 is at least substantially perpendicular to the bearing axis 26 and is arranged at least substantially completely around the bearing axis 26. The seal edge 114 of the another seal clearance element 88 is arranged such that at least one of the two outer faces 92, 94, 96 of the another seal clearance element 88 that form the seal edge 114 of the another seal clearance element 88, especially the inner face 92, is at least substantially parallel to the bearing axis 26 in orientation.

[0037] The maximum spacing 120, which is at least substantially parallel to the drive axis 16 between the sealing gap element 40 and the conveying element 22, is in particular less than 2 mm, preferably less than 1.5 mm, and particularly preferably less than 1 mm. Preferably, the maximum spacing 120, which is at least substantially parallel to the drive axis 16 between the sealing gap element 40 and the conveying element 22, extends from the sealing gap surface 64 of the sealing gap element 40 towards the conveying element 22, in particular towards at least one surface 122 of the conveying element 22 which is 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 via the maximum spacing 120. The maximum spacing 124, which is at least substantially perpendicular to the drive axis 16 between the further sealing gap element 88 and the conveying element 22, is in particular less than 2 mm, preferably less than 1.5 mm and particularly preferably less than 1 mm. Preferably, the maximum spacing 124, which is at least substantially perpendicular to the drive axis 16 between the further sealing gap element 88 and the conveying element 22, extends from the inner surface 92 of the further sealing gap element 88 towards the side surface 126 of the conveying element 22 which surrounds the conveying outlet 46, wherein in particular the side surface 126 of the conveying element 22 is at least partly 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 via the maximum spacing 124.

[0038] Said further sealing gap element 88 is arranged at least partially inside the maximum longitudinal extent 128 of the conveying element 22, when observed at least substantially perpendicular to the drive axis 16. The maximum longitudinal extent 128 of the conveying element 22 is oriented at least substantially parallel to the drive axis 16. Said further sealing gap element 88 is arranged outside the maximum longitudinal extent 130 of the delivery outlet 46 of the conveying channel 42, when observed at least substantially perpendicular to the drive axis 16, which maximum longitudinal extent is in particular oriented at least substantially parallel to the drive axis 16. The maximum longitudinal extent 130 of the delivery outlet 46 of the conveying channel 42 at least substantially corresponds to the opening width 78 of the fluid opening 76 which is delimited at least partially by said further sealing gap element 88. In particular, the conveying element 22 is arranged relative to the separating device 20 such that the delivery outlet 46 and the fluid opening 76 are arranged successively and coinciding with each other starting from the drive axis 16, when observed in at least one cross-section plane of the fluid machine 10 passing through the drive axis 16. The side surface 96 of said further sealing gap element 88 is arranged at least partially, in particular when observed in at least one cross-section plane of the fluid machine 10 passing through the drive axis 16, in a plane which has the inner face 132 of the conveying element 22 that delimits the delivery outlet 46. The inner face 132 of the conveying element 22 that delimits the delivery outlet 46 is oriented at least substantially perpendicular to the drive axis 16. The inner face 132 of the conveying element 22 that delimits the delivery outlet 46 is arranged facing away from the flow recess 38.

[0039] 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 can be considered that the conveying element 22 has a chamfer in the edge region on the side facing the sealing gap element 40 and / or the flow recess 38. The rounding 134 extends at least partially along the circumferential direction 56 around the drive axis 16. The rounding 134 is preferably arranged on the side surface 126 of the conveying element 22. The conveying element 22 has at least one sealing edge 136 which is delimited in particular by the side surface 126 of the conveying element 22 and the inner face 132 that delimits the delivery outlet 46. The sealing edge 136 of the conveying element 22 is constructed at least partially at least substantially perpendicular to the drive axis 16 and along the circumferential direction 56 around the drive axis 16. The side surface 126 of the conveying element 22 and the inner face 132 that delimits the delivery outlet 46 have an angle 138 of in particular at most 90°, preferably at most 80° and particularly preferably at most 70°, at least partially, in particular in the region in the vicinity of the sealing edge 136 of the conveying element 22.

[0040] 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 a maximum radial extension 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 at least 30%, preferably at least 40%, and particularly preferably at least 50% of the maximum radial extension 142 of the conveying element 22 around 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 towards the drive axis 16.

[0041] exist Figure 3 and Figure 4 An exemplary fluid flow and / or particle flow 34 through the fluid machine 10 is shown in FIG. Figure 3 In the embodiment, the fluid machine 10 is similar to Figure 2 It is shown as a cross-section extending through the bearing axis 26 and the drive axis 16. Figure 4 In the figure, the turbomachine 10 is shown in a cross-sectional plane oriented at least substantially perpendicular to the bearing axis 26 and the drive axis 16. The conveying unit 18 is provided for moving a fluid flow and / or a particle flow 34 through the conveying channel 42 into the impeller side space 28 and / or the spiral space 72. The fluid flow 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 flow 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 extension 80 along the circumferential direction 56 around the bearing axis 26, wherein a maximum lateral extension 148 of the spiral space 72 oriented at least substantially perpendicular to the bearing axis 26 varies in particular along the circumferential direction 56 around the bearing axis 26. If the maximum lateral extension 148 of the spiral space 72 is greater than a limit value 150 of the maximum lateral extension 148 (see Figure 4 ), the fluid flow and / or particle flow 34 moves from the flow recess 38 into the spiral space 72 and / or the conveying channel 42. If the maximum lateral extension 148 of the spiral space 72 is less than the limit value 150 of the maximum lateral extension 148 (see Figure 4), the fluid flow and / or particle flow 34 moves from the helical space 72 and / or the conveying channel 42 into the flow recess 38. Preferably, the separating device 20 is arranged to move the fluid flow and / or particle flow 34 out of the fluid machine 10 from the helical space 72 through the output opening 74.

Claims

1. A separation device for a fluid machine, the separation device having at least one housing (12), the housing having at least one bearing receiving portion (24), the bearing receiving portion defining at least one bearing axis (26), and the housing having at least one impeller side space (28), the separation device having a conveying unit (18) for conveying a fluid, the conveying unit including a conveying element (22) having a conveying outlet (46), and the separation device having at least one agitation unit (32), the agitation unit being adapted to deflect and / or agitate at least one fluid stream and / or particle stream (34), wherein, The stirring 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), characterized in that the stirring 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 stirring 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), wherein the stirring unit (32) comprises at least one further sealing gap element (88), wherein at least two mutually adjacent outer surfaces (92, 94, 96) of the further sealing gap element (88) forming a sealing edge (114) form an angle (118) of less than 90° when viewed at least substantially perpendicularly to the bearing axis (26), The further sealing gap element (88) has a side surface (96) which is arranged at least partially in a plane having an inner surface (132) of the conveying element (22) which defines the conveying outlet (46).

2. The 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, characterized in that The sealing gap element (40) at least partially defines the flow recess (38).

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

5. The separation device according to any one of claims 1 to 3, characterized in that The further sealing gap element (88) has a minimum radial spacing (110) relative to the bearing axis (26) when viewed at least substantially perpendicularly to the bearing axis (26), the minimum radial spacing being greater than a minimum radial spacing (112) between 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) when viewed from the bearing axis (26).

6. The separation device according to any one of claims 1 to 3, characterized in that, At least one of the two outer surfaces (92, 96) of the further sealing gap element (88) which form the sealing edges (114) is oriented at least substantially parallel to the bearing axis (26).

7. A fluid machine having at least one drive unit (14), the drive unit having at least one drive axis (16), the fluid machine having at least one conveying unit (18) driven about the drive axis (16) for conveying a fluid, the conveying unit having at least one conveying element (22), and the fluid machine having at least one separating device (20) according to any one of claims 1 to 6, wherein, The delivery unit (18) is arranged at least predominantly around the drive axis (16) in the impeller side chamber (28).

8. The fluid machine according to claim 7, characterized in that, The fluid machine is a coolant pump.

9. The fluid machine according to claim 7, characterized in that, The conveying unit (18) is a wheel.

10. The fluid machine according to claim 7, characterized in that, 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), which is oriented at least substantially parallel to the drive axis (16), is less than 2 mm.

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

14. The fluid machine according to claim 13, characterized in that, The maximum spacing (124), which is at least substantially perpendicular to the drive axis (16) between the other sealing gap element (88) and the conveying element (22), is less than 2 mm.

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) relative to the drive axis (16), and the minimum radial spacing corresponds to at most 90% of the maximum radial extent (142) of the conveying element (22) around the drive axis (16).

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