Bearing arrangement for guiding a motor shaft of a vertical turbine pump

Description

Technical field

[0001] The invention relates to a bearing arrangement for guiding a motor shaft to support axial and / or radial forces of a vertical turbine pump, comprising a bearing with an inner ring and an outer ring that are rotationally fixed to the motor shaft, and an oil sump filled with oil in which the bearing is at least partially immersed in the oil. The invention further relates to the vertical turbine pump with a riser pipe extending along an axis, a motor shaft arranged in the riser pipe, a motor arranged at an upper end of the riser pipe and driving the motor shaft, an impeller arranged at an opposite, lower end of the riser pipe and driven by the motor shaft for conveying a fluid into the riser pipe, and the bearing arrangement guiding the motor shaft. Background of the invention

[0002] Vertical turbine pumps, also known as vertical turbines, semi-axial pumps, or borehole pumps, are vertical pumps used, for example, to draw water from rivers, wells, and boreholes, and are particularly common in water supply and industrial applications. Delivery heads of, for example, 40 to 250 meters can be achieved by connecting several impellers in series.

[0003] Vertical turbine pumps typically include a motor mounted on some kind of base or motor support. A motor shaft, which may be directly attached to or coupled with the motor, extends downwards through a column support or a vertical pipe assembly, also called a riser, towards an impeller. The impeller contains several impeller blades that rotate with the motor and motor shaft, thus forcing the fluid down into the riser.

[0004] In conventional vertical turbine pumps, the motor shaft is typically supported on the riser pipe below the motor by a rolling bearing. To prevent overheating of the rolling bearing, which would drastically reduce its service life, most bearings are cooled by an external auxiliary system. This system cools the bearing oil using cooling coils immersed in the oil and through which a cooling fluid flows. The cooled oil, in turn, cools the rolling bearing.

[0005] However, such external cooling systems are expensive to purchase and require regular maintenance, resulting in high operating costs. While pilot applications without external cooling have been conducted, the results so far do not allow for stable, maintenance-free operation of vertical turbine pumps. This is due, for example, to oil flow interruptions over time or excessive air ingress into the oil, which negatively impacts cooling.

[0006] EP 0233593 A2 describes a self-pumping bearing for machines with a vertical shaft, in which the bearing elements are surrounded by an oil reservoir rotating with the shaft.

[0007] WO 2007 / 040427 A1 describes a bearing device for supporting a shaft of a cyclone separator, wherein the shaft is rotatable about an axis of rotation in a frame. DE 3214030 A1 describes a shaft coupling between an electric drive motor and the pump shaft of a vertically mounted centrifugal pump equipped with a support lantern.

[0008] US 2014093201 A1 describes a self-pumping bearing for vertical pump shafts in which oil cooling is ensured by an oil deflector located in an oil pan. Description of the invention

[0009] Starting from this situation, it is an object of the present invention to provide a bearing arrangement for guiding a motor shaft to support axial and / or radial forces of a vertical turbine pump, which ensures reliable cooling of a bearing of the bearing arrangement without an external cooling system.

[0010] The object of the invention is achieved by the features of the independent claims. Advantageous embodiments are specified in the dependent claims.

[0011] Accordingly, the task is solved by a bearing arrangement for guiding a motor shaft of a vertical turbine pump with a bearing comprising an inner ring and an outer ring which are non-rotatably connected to the motor shaft, an oil pan filled with oil in which the bearing is at least partially immersed in the oil, and an inner oil deflector which is non-rotatably connected to the inner ring and which deflects oil conveyed between the inner ring and the outer ring back into the oil pan due to rotation of the bearing.

[0012] A key aspect of the proposed solution lies in the passive cooling of the bearing, eliminating the need for an external and typically costly auxiliary cooling system. This reduces the operating costs of the vertical turbine pump. Furthermore, the proposed internal oil deflector ensures a homogeneous temperature within the bearing, optimizing the service life of both the bearing and the cooling oil. Consequently, the proposed solution reduces the risk of failures, thus increasing the operational stability of the vertical turbine pump. Moreover, experiments have demonstrated that, unlike other prior art passive cooling designs, the proposed solution does not experience oil flow interruption, resulting in improved heat transfer and thus better bearing cooling. In other words, prior art passive cooling designs simply do not function reliably.

[0013] Vertical turbine pumps are generally defined as pumps designed for use in wells or boreholes. These pumps often feature a riser pipe that houses the motor shaft and may also support the bearing. The riser pipe can be several meters long, meaning the vertical turbine pump is often significantly longer axially (along the axis of the riser pipe or motor shaft) than it is radially wide. The riser pipe typically extends largely beneath a base plate to which the pump can be mounted. The riser pipe is preferably made of metal and / or has a circular or near-circular cross-section.

[0014] The inner ring can be connected to the motor shaft either directly or indirectly, for example by means of spacers, in particular by positive and / or non-positive connection. Likewise, the outer ring can be connected either directly or indirectly, for example by means of spacers, to an outer wall of the bearing assembly described later, to the riser pipe, and / or to a manifold housing described later, in particular by means of positive and / or non-positive connection. The oil pan preferably extends around the motor shaft in an axial top view and / or is arranged below the inner ring and / or the outer ring at a vertical distance in an axial side view or at a distance from it. Where the application refers to axial and / or radial, these terms refer in particular to the motor shaft or an axial extension thereof along an axis.

[0015] The oil pan is preferably closed axially downwards and partially open axially upwards, allowing oil to flow between the inner and outer rings and, deflected by the inner oil deflector, back into the oil pan. Preferably, the bearing is completely immersed in the oil. Any oil known from the prior art can be used to cool the bearing. Oil as a coolant has the advantage of being electrically insulating, providing good lubrication, and inhibiting corrosion of metals. Rotation of the bearing, as if the inner ring were rotating relative to the outer ring due to rotation of the motor shaft, exerts a centrifugal force on the oil located between the inner and outer rings, which is thus pumped out of the oil pan by the bearing.

[0016] The inner oil deflector is preferably positioned axially above the inner ring and / or the outer ring, particularly in axial extension of a bearing axis defined by a rolling element located between the inner and outer rings. The bearing axis thus defined can extend parallel to the axis of the motor shaft. Preferably, the bearing is designed as a tapered roller bearing with inclined rolling elements, as described below, such that the bearing axis thus defined is inclined relative to the axis of the motor shaft, and in particular extends radially away from it axially upwards. The oil conveyed by the bearing is preferably deflected by an inner surface of the inner oil deflector that is oriented downwards with respect to the vertical turbine pump, and thus does not flow over an outer surface of the inner oil deflector that is oriented upwards. This prevents air from mixing with the deflected oil, which would negatively affect the cooling effect.

[0017] There are various possibilities for the design of the inner oil deflector. According to a preferred embodiment, the inner oil deflector extends radially outwards from the inner ring and / or, in an axial plan view, in a ring-like fashion around the inner ring. In particular, the inner oil deflector extends radially away from the motor shaft. The inner oil deflector is preferably designed in a disc-like form, especially similar to a washer appropriately dimensioned for the vertical turbine pump. Preferably, the inner oil deflector is made of metal, particularly a precious metal.

[0018] According to a further preferred embodiment, the inner oil deflector, viewed axially from the side, is arranged above the oil pan, particularly above the bearing, and extends downwards and radially away from the inner ring in a shield-like, arc-like, and / or axially oblique manner towards the oil pan. In this respect, the inner oil deflector, viewed axially from the side, can initially extend radially away from the motor shaft and subsequently be bent downwards, particularly in a circular arc, towards the oil pan. A particularly preferred feature is that the inner oil deflector is tangential to the axial extension of the bearing axis defined by the rolling elements provided between the inner and outer rings, so that the oil conveyed by the bearing appears approximately perpendicular to the tangential axis and is deflected accordingly by the inner oil deflector.

[0019] In another preferred embodiment, an outer wall radially delimiting the oil pan is provided, on which a plurality of cooling fins are formed on the outer surface. The outer wall preferably also forms the outer wall of the bearing assembly. The cooling fins preferably extend in the axial direction and are arranged at a distance from one another. Preferably, the cooling fins are arranged radially around the outer wall. The cooling fins effectively cool the oil deflected by the inner oil deflector and subsequently flowing back into the oil pan, particularly along the outer wall, without the need for an external cooling device as known from the prior art.

[0020] As previously described, the inner oil deflector is fixed to the inner ring so that it rotates with the motor shaft. According to a further preferred embodiment, an additional outer oil deflector, also fixed to the outer ring, is provided and is arranged axially above the inner oil deflector with respect to the oil pan. In a further preferred embodiment, the outer oil deflector extends radially inwards from the outer wall and / or, in axial plan view, extends ring-like around the inner ring. This additional outer oil deflector is preferably spaced apart from, but adjacent to, the inner oil deflector located below it. The outer oil deflector can be directly connected to the outer ring or indirectly, for example, via the outer wall, to which the outer ring is preferably fixedly connected.Therefore, the outer oil deflector preferably extends from the outer wall and around the motor shaft in the direction of the motor shaft, but does not touch it. The outer oil deflector, like the inner oil deflector, can be made of a metal disc. The outer oil deflector allows any oil not deflected by the inner oil deflector to be diverted back into the oil pan. Preferably, the inner oil deflector does not touch the outer wall, so that the oil deflected by the outer oil deflector can flow through a channel between the inner oil deflector and the outer wall.

[0021] According to a further preferred embodiment, the bearing assembly has an outer wall radially delimiting the oil pan, on which the outer ring is provided. Between the outer wall and the outer ring, a drip tray extending around the outer ring in axial plan view is provided to collect the oil deflected by the inner oil deflector. The outer wall can be made of aluminum, while the rest of the bearing assembly can be made of a different metal. The outer wall can be designed as a two-part structure with respect to the rest of the bearing assembly, although a one-piece design is also conceivable. The drip tray is preferably open at the top and / or extends in an annular shape around the motor shaft. The drip tray is preferably arranged below a radial end of the inner oil deflector, so that any oil that runs off the inner oil deflector can drip into the drip tray.

[0022] In another preferred embodiment, a plurality of spaced-apart, axially extending connecting openings are provided between the collection tray and the oil pan for the flow of the oil collected in the collection tray into the oil pan. The connecting openings can be designed as channels that have a radial inward slope towards the oil pan.

[0023] According to a further preferred embodiment, the bearing is designed as a radial bearing, a thrust bearing, and / or an angular contact ball bearing. A further preferred embodiment is the bearing being designed as a rolling bearing. The rolling elements can be balls, cones, or cylinders. Other bearing configurations are also possible. Preferably, the surfaces of the inner ring and the outer ring facing each other are arranged at an angle to the axis of the motor shaft, particularly at an angle of 45°.

[0024] The object of the invention is further solved by the vertical turbine pump with a riser pipe extending along an axis, a motor shaft arranged in the riser pipe, a motor arranged at an upper end of the riser pipe and driving the motor shaft, an impeller arranged at an opposite, lower end of the riser pipe and driven by the motor shaft for conveying a fluid into the riser pipe, and a bearing arrangement guiding the motor shaft according to one of the preceding claims.

[0025] According to a preferred embodiment, the vertical turbine pump has a pressure-side elbow connected to the riser pipe at a first elbow end facing the impeller, which has a curvature continuously away from the axis and an outlet at an opposite second elbow end for the pumped fluid, wherein a radial diameter as the height of the elbow initially decreases and then increases from the first elbow end to the second elbow end.

[0026] The bend is preferably designed as a pipe bend or similar to a pipe bend and / or has a circular arc or elliptical shape in side view. The bend preferably extends over a circular arc or in a circular arc-like manner over 90°, although other values ​​such as 80° or 100° are also possible. Therefore, the feature that the bend has a continuous curvature away from the axis does not mean that the bend initially extends in a direction opposite the second bend end, for example, having an S-shaped form, but rather that it extends linearly and / or continuously, particularly in a circular arc or elliptical shape in side view, further away from the axis or the riser pipe with respect to its radial centerline.Furthermore, the characteristic that the bend exhibits a curvature continuously away from the axis is to be understood as synonymous with the characteristic that the bend extends continuously away from the axis with respect to its radial, and in particular arc-like, centerline. In the case of an elliptical shape, particularly one extending over 90°, the minor axis of the ellipse preferably runs parallel to the axis and / or the major axis runs horizontally.

[0027] The characteristic that the radial diameter, as the height of the bend, initially decreases and then increases from the first bend end to the second bend end, means, in particular, that at at least one position between the first and second bend ends, the height of the bend is less than the height at the first and / or second bend ends. In side view, the bend has a particularly flattened shape. In particular, the bend may also have a dented shape on its outer surface in side view, with the height being maximally reduced at the dent. The radial diameter is understood to be, in particular, the radial inner diameter of the bend, which defines a clear height within the bend through which the fluid can flow. Therefore, when referring to a decrease or increase in diameter, the outer diameter may also be meant, in addition to the inner diameter.

[0028] The motor and manifold are preferably arranged above the base plate, such that the riser pipe is connected to the first end of the manifold, particularly in a fluid-tight manner, just above or at the base plate, and the motor is arranged vertically above the manifold. The motor shaft preferably extends axially along the centerline of the riser pipe and, in axial extension of the riser pipe, passes through the tubular manifold on one outer side. An opening may be provided in the manifold on this outer side through which the motor shaft passes. Preferably, a seal, particularly a radial seal, is provided, which is arranged in the opening and seals the motor shaft radially around the manifold in a fluid-tight manner.

[0029] A key aspect of the design, which will be described in more detail below, is that the manifold can be shaped like a "cobra head," meaning the height of the manifold between its two ends is reduced. This reduces the distance between the motor and a base plate, which has a positive effect on stiffness and natural frequency, and of course, on the manufacturing costs of the vertical turbine pump. In other words, the proposed vertical turbine pump is less susceptible to vibration, which improves its operational stability. The reduced vertical height also makes the vertical turbine pump easier to service or repair, as it is simpler to remove the motor and / or manifold, especially if they are exposed above ground.Furthermore, the bend, with its reduced height between the two ends, minimizes potential turbulence at the outlet, which positively impacts the measurement accuracy of pressure and flow by a sensor located at the outlet. Finally, the proposed bend also improves the hydraulic properties of the vertical turbine pump.

[0030] In a preferred embodiment, the radial diameter initially decreases and then steadily increases. The radial diameter can decrease and / or increase continuously, and it is also possible for the radial diameter to remain constant for a certain distance before subsequently decreasing and / or increasing. Particularly preferably, the radial diameter does not decrease and / or increase abruptly, but rather linearly.

[0031] In a particularly preferred embodiment, the axial diameter, as the width of the bend, initially increases from the first bend end to the second bend end and then decreases. This means, in particular, that at at least one position between the first and second bend ends, the width of the bend is greater than the width at the first and / or second bend ends. In plan view, especially along a radius of the bend, the bend has a shape that is broadened, particularly in the middle of its extent. In particular, the bend can also have a bulge in plan view, with the width being maximally increased at the axial bulge. The axial diameter is understood to be, in particular, an axial inner diameter of the bend, which defines a clear width within the bend through which the fluid can flow.

[0032] In a further preferred embodiment, the cross-section of the bend is provided to be constant between the first and second bend ends. This means that if the height of the bend decreases between the first and second bend ends, the width of the bend increases accordingly.

[0033] In another preferred embodiment, a drive lantern with a coupling provided between the motor and the motor shaft is arranged between the motor and the manifold. The drive lantern and the manifold, including a manifold housing preferably comprising the manifold, are designed in one or more parts, particularly in two parts. Preferably, the drive lantern and / or the manifold housing have a rectangular cross-section in plan view and / or are cuboid in shape. The manifold housing is preferably fixedly mounted on the base plate or the like, in particular by bolting. The riser pipe preferably extends vertically and / or axially below the base plate and is also preferably fixedly mounted to the base plate and / or the manifold housing, in particular by bolting.Preferably in axial extension of the riser pipe, the drive lantern is fixed in place between the manifold housing and the engine, in particular screwed to the manifold housing and the engine.

[0034] According to a further preferred embodiment, the bend has a continuously changing elliptical cross-section between the first bend end, which has a particularly circular cross-section, and the second bend end, which also has a particularly circular cross-section. Preferably, the minor axis of the elliptical cross-section extends radially with respect to the bend as the height of the bend, while the major axis of the elliptical cross-section extends orthogonally to it as the width of the bend. According to another preferred embodiment, the first bend end and the second bend end have the same size, particularly circular, cross-section.

[0035] According to a further preferred embodiment, the radius of a radial inner manifold edge increases continuously from the first manifold edge to the second. In other words, the curvature of the radial inner manifold edge, and thus also of the manifold itself, flattens or decreases continuously from the first manifold edge to the second. This allows the manifold to be designed with a low height relative to the axis of the riser pipe, thereby positioning the engine closer to the base plate, thus reducing vibrations and resulting in more stable operation of the vertical turbine pump. Brief description of the drawings

[0036] The invention is explained in more detail below with reference to the accompanying drawings and by way of preferred embodiments.

[0037] The drawings show Fig. 1 a schematic sectional view of a vertical turbine pump according to a preferred embodiment of the invention, Fig. 2 a schematic sectional view of a bearing arrangement for guiding a motor shaft of the vertical turbine pump according to Fig. 1 according to the preferred embodiment of the invention, and Fig. 3 a schematic perspective partial sectional view of the bearing arrangement for guiding the motor shaft of the vertical turbine pump according to Fig. 2 according to the preferred embodiment of the invention. Detailed description of the implementation examples

[0038] Fig. 1 Figure 1 shows a schematic sectional view of a vertical turbine pump 1 with a manifold housing 2 having a manifold 3 according to a preferred embodiment of the invention.

[0039] The vertical turbine pump 1 has a riser pipe 5 extending along an axis 4 with a circular outer cross-section, comprising several interconnected segments. A motor shaft 6 extends centrally within the metal riser pipe 5 along the axis 4 and along the entire length of the riser pipe 5, such that a free space is formed radially around the motor shaft 6 between it and the riser pipe 5, through which the fluid pumped by the vertical turbine pump 1 rises axially upwards. For this purpose, several axially stacked impellers 8 are provided at a lower end 7 of the riser pipe. These impellers are driven by the motor shaft 6, draw in the fluid, and pump it into the free space.

[0040] The riser pipe 5 is attached to a base plate 10 at its upper riser end 9, so that the riser pipe 5 extends vertically downwards from the base plate 10. Above the base plate 5, the manifold housing 2 is attached vertically upwards in the direction of the axis 4, to which a drive lantern 11 is attached axially, followed by a motor 12 that drives the motor shaft 6. A coupling 13 is arranged in the drive lantern 11, which is connected between the motor 12 and the motor shaft 6. The manifold housing 2 and the drive lantern 11 are designed in two parts and are bolted together. The upper riser pipe end 9 is fluid-tightly connected to a first manifold end 14 of the manifold 3, which faces the impeller 8.

[0041] The bend 3 has an outlet 16 for the conveyed fluid at a second bend end 15, which is arranged opposite the first bend end 14. The tubular bend 3 directs the conveyed fluid from the vertical to the horizontal, so that the cross-sectional areas at the first bend end 14 and the second bend end 15 are arranged offset from each other by 90°. For this purpose, the inner cross-sectional areas of the two bend ends 14, 15 are of the same size and circular.

[0042] Inside the manifold housing 2, the motor shaft 6 is connected by a Figures 2 and 3The bearing arrangement 17, shown in more detail, is fixedly connected to the manifold housing 2. The bearing arrangement 17 includes a bearing 18, which is designed as a rolling bearing with rollers, or alternatively as an angular contact ball bearing, in particular a tapered roller bearing. An inner ring 19 of the bearing 18 is non-rotatably connected to the motor shaft 6 and rotates accordingly with the motor shaft 6, which is located in Figures 2 and 3 The bearing 18 extends radially around the motor shaft 6. An outer ring 20 is non-rotatably connected to the manifold housing 2.

[0043] The bearing arrangement 17 further comprises an oil pan 21 arranged vertically or axially below the bearing 18 with respect to the axis 4, which also extends radially around the motor shaft 6. The oil pan 21 is filled with oil (not shown) such that the bearing 18, including the inner ring 19 and the outer ring 20, is completely covered with oil.

[0044] Finally, the bearing arrangement 17 has an inner oil deflector 22, which is rotationally fixed to the inner ring 19 and extends radially away from the motor shaft 6. The inner oil deflector 22 is arranged vertically, or axially with respect to the axis 4, above and spaced apart from the bearing 18 and, in axial plan view, is disc-shaped, centrally enclosing the motor shaft 6. In axial side view, the inner oil deflector 22 has the following appearance as shown in Fig. 2 The inner oil deflector 22 has an umbrella-like shape, as it extends radially away from the motor shaft 6, axially covering the bearing 18, and is then bent downwards in a quarter-circle shape towards the oil pan 21.

[0045] The tapered rollers of the bearing 18 rotate as the motor shaft 6 rotates. Due to centrifugal force, the oil in the bearing 18 is pumped obliquely upwards away from the motor shaft 6 by the tapered rollers on the oil pan 21 between the inner ring 19 and the outer ring 20, as indicated in Fig. 3 by arrows 23. Since the umbrella-like or soup-plate-like curved inner oil deflector 22 is arranged axially above the bearing 18, the oil conveyed in this way hits the inner oil deflector 22, which deflects the oil axially downwards, so that the deflected oil drips downwards at the quarter-circle-like end of the inner oil deflector 22.

[0046] A ring-shaped collection tray 24, extending around the motor shaft 6 in axial plan view, is provided axially below the curved area of ​​the inner oil deflector 22 to collect the oil deflected by the inner oil deflector 18. The collection tray 24 extends axially between the outer ring 20 and an outer wall 25 of the bearing assembly 17, which radially delimits the oil pan 21.

[0047] Between the collection tray 24 and the oil pan 21, a plurality of spaced-apart connecting openings 26, extending axially inwards towards the motor shaft 23 and sloping slightly towards the axis 4, are provided in the form of channels through which the oil collected in the collection tray 26 can flow back into the oil pan 21, as indicated by arrows 23. From there, the oil can be conveyed again through the bearing 18 as described above.

[0048] In addition to the inner oil deflector 22, a further oil deflector in the form of an outer oil deflector 27 is provided, which is rotationally fixed to the outer ring 20 or to the outer wall 25 and extends radially away from it in the direction of the axis 4. With respect to the oil pan 21, the outer oil deflector 27 is arranged axially above the inner oil deflector 22. Like the inner oil deflector 22, the outer oil deflector 27 is disc-shaped and extends circumferentially around the motor shaft 6, but has no curvature. The outer oil deflector 27 serves to deflect oil that is not deflected by the inner oil deflector 22 into the oil pan 21.

[0049] Finally, a plurality of axially extending cooling fins 27 are formed around the bearing assembly 17 on its outer wall 25, through which the oil, in particular the oil flowing back into the oil pan 21, is cooled. The outer wall 26 or the bearing assembly 17 is made of metal, and the cooling fins 27 can be made of aluminum.

[0050] The described embodiments are merely examples that can be modified and / or supplemented in various ways within the scope of the claims. Reference symbol list

[0051] Vertical turbine pump 1 manifold housing 2 manifold 3 axis 4 riser pipe 5 Motor shaft 6 Lower riser pipe end 7 balance bike 8 Upper riser pipe end 9 base plate 10 drive lantern 11 Motor 12 coupling 13 First bend end 14 Second end of manifold 15 Outlet 16 Storage arrangement 17 Storage 18 inner ring 19 outer ring 20 sump 21 Inner oil deflector 22 Arrows 23 drip tray 24 Exterior wall 25 Connection opening 26 Outer oil deflector 27 Cooling fins 28

Claims

1. A bearing arrangement (17) for guiding a motor shaft (6) and / or for supporting axial and / or radial forces of a vertical turbine pump (1), comprising a bearing (18) comprising an inner ring (19) which can be connected to the motor shaft (6) for conjoint rotation, and an outer ring (20), an oil sump (21), which is filled with an oil and in which the bearing (18) is arranged so as to be at least partially immersed in the oil, and an inner oil deflector (22), which is connected to the inner ring (19) for conjoint rotation and deflects oil conveyed between the inner ring (19) and the outer ring (20) as a result of a rotation of the bearing (18) back into the oil sump (21).

2. The bearing arrangement (17) according to the preceding claim, wherein the inner oil deflector (22) extends radially outward from the inner ring (19) and / or, in an axial plan view, extends annularly around the inner ring (19).

3. The bearing arrangement (17) according to any one of the preceding claims, wherein the inner oil deflector (22), in an axial side view, is arranged above the oil sump (21) and extends from the inner ring (19) in the manner of an umbrella and / or axially obliquely downward and radially away in the direction of the oil sump (21).

4. The bearing arrangement (17) according to any one of the preceding claims, comprising an outer wall (25), which radially delimits the oil sump (21) and on the outside of which a plurality of cooling fins (28) are formed.

5. The bearing arrangement (17) according to any one of the preceding claims, comprising an outer oil deflector (27), which is connected to the outer ring (20) for conjoint rotation and is arranged axially above the inner oil deflector (22) with respect to the oil sump (21).

6. The bearing arrangement (17) according to the preceding claim, wherein the outer oil deflector (27) extends, in particular from the outer wall (25) according to the preceding claim 4, radially inward and / or, in an axial plan view, extends annularly around the inner ring (19).

7. The bearing arrangement (17) according to any one of the preceding claims, comprising an outer wall (25), which radially delimits the oil sump (21) and at which the outer ring (20) is provided, wherein a collecting pan (24) for collecting the oil deflected by the inner oil deflector (22) extends, in an axial plan view, around the outer ring (20) and is provided between the outer wall (25) and the outer ring (20).

8. The bearing arrangement (17) according to the preceding claim, wherein a plurality of spaced- apart, axially extending connecting openings (26) for draining the oil collected in the collecting pan (24) into the oil sump (21) are provided between the collecting pan (24) and the oil sump (21).

9. The bearing arrangement (17) according to any one of the preceding claims, wherein the bearing (18) is designed as a radial bearing, an axial bearing, and / or an angular-contact ball bearing.

10. A vertical turbine pump (1), comprising a riser pipe (5) extending along an axis (4), a motor shaft (6) arranged in the riser pipe (5), a motor (12) which is arranged at an upper riser pipe end (9) and drives the motor shaft (6), an impeller (8) which is arranged at an opposite lower riser pipe end (7) and is driven by the motor shaft (6) for conveying a fluid into the riser pipe (5), and a bearing arrangement (17) guiding the motor shaft (6) according to any one of the preceding claims.

11. The vertical turbine pump (1) according to the preceding claim, comprising a pressure-side manifold (3), which is connected to the riser pipe (5) at a first manifold end (14) facing the impeller (8) and has a curvature continuously away from the axis (4) and an outlet (16) at an opposite second manifold end (15) for the fluid conveyed, wherein a radial diameter as the height of the manifold (3) initially decreases from the first manifold end (14) toward the second manifold end (15) and subsequently increases.

12. The vertical turbine pump (1) according to the preceding claim, wherein the radial diameter initially continuously decreases and subsequently continuously increases.

13. The vertical turbine pump (1) according to any one of the two preceding claims, wherein an axial diameter as the width of the manifold (3) initially increases from the first manifold end (14) toward the second manifold end (15) and subsequently decreases.

14. The vertical turbine pump (1) according to any one of the three preceding claims, wherein a cross section of the manifold (3) in the course between the first manifold end (14) and the second manifold end (15) is always the same.

15. The vertical turbine pump (1) according to any one of the four preceding claims, comprising a drive lantern (11), which is provided between the motor (12) and the manifold (3) and comprises a coupling (13) provided between the motor (12) and the motor shaft (6), wherein the drive lantern (11) and the manifold (3), including a manifold housing (2) preferably comprising the manifold (3), are designed in one part or multiple parts, in particular in two parts.