LUBRICATION RING FOR TRANSPORTING LUBRICANT

Abstract

A lubrication ring for the transport of a lubricant from a lubricant container in a bearing, the lubrication ring to be driven by a rotating shaft, which is borne by the bearing. The lubrication ring includes a running surface configured to interoperate with the shaft, and a transport surface configured to transport lubricant, the transport surface having a plurality of pockets to transport of the lubricant, the plurality of pockets arranged adjacent to each other in a circumferential direction of the lubrication ring.

Claims

1. A lubrication ring for the transport of a lubricant from a lubricant container in a bearing, the lubrication ring to be driven by a rotating shaft, which is borne by the bearing, the lubrication ring comprising: a running surface configured to interoperate with the shaft; and a transport surface configured to transport lubricant, the transport surface having a plurality of pockets to transport of the lubricant, the plurality of pockets arranged adjacent to each other in a circumferential direction of the lubrication ring.

2. The lubrication ring according to claim 1 wherein the lubrication ring has a thickness in a radial direction, and each pocket of the plurality of pockets has a depth which is at least 10 percent of the thickness of the lubrication ring.

3. The lubrication ring according to claim 1, wherein the plurality of pockets includes at least 30 pockets and at most 60 pockets.

4. The lubrication ring according to claim 1, wherein two adjacent pockets of the plurality of pockets are separated from each other by a web.

5. The lubrication ring according to claim 4, wherein the web forms an angle, different from 90?, with the circumferential direction of the lubrication ring.

6. The lubrication ring according to claim 5, wherein the angle is at most 60?.

7. The lubrication ring according to claim 1, wherein, relative to a radial direction of the lubrication ring, each pocket of the plurality of pockets is limited by a concave surface.

8. The lubrication ring according to claim 1, wherein the running surface has a plurality of radial grooves which, when viewed in the circumferential direction, stretch across an entirety of the running surface.

9. The lubrication ring according to claim 1, wherein the running surface is made from a synthetic material.

10. The lubrication ring according to claim 1, wherein the transport surface is made from a synthetic material.

11. The lubrication ring according to claim 1, wherein the lubrication ring includes an inner part, a middle part, and an outer part, each of the inner part, the middle part, and the outer part having a ring shape, when viewed in a radial direction, the middle part is arranged in between the inner part and the outer part, the inner part includes the running surface and the outer part includes the transport surface.

12. The lubrication ring according to claim 11 wherein the middle part is made from a metallic material.

13. The lubrication ring according to claim 11, wherein the inner part and the outer part encase the middle part.

14. A bearing for a pump with a shaft for rotating around an axial direction, the bearing comprising: a bearing housing; a bearing cover attached to the bearing housing; a bearing structure configured to bear the shaft; a lubricant container for a lubricant; the lubrication ring according to claim 1, the lubrication ring configured to transport the lubricant and to supply the bearing structure with the lubricant, the lubrication ring configured to be driven by the rotating shaft.

15. A pump, comprising: a bearing comprising a bearing housing, a bearing cover attached to the bearing housing, a bearing structure configured to bear the shaft, a lubricant container for a lubricant, the lubrication ring according to claim 1, the lubrication ring configured to transport the lubricant and to supply the bearing structure with the lubricant, the lubrication ring configured to be driven by the rotating shaft.

16. The lubrication ring according to claim 5, wherein the angle is about 40?.

17. The lubrication ring according to claim 1, wherein the running surface has a plurality of radial grooves which, when viewed in the circumferential direction, stretch across an entirety of the running surface, and are arranged parallel to each other.

18. The lubrication ring according to claim 11 wherein the middle part is made from stainless steel.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

[0037] In the following, embodiments of the invention will be more closely explained using the drawings. In the drawing, it is shown:

[0038] FIG. 1 illustrates a schematic depiction of an embodiment of a pump according to the disclosure,

[0039] FIG. 2 illustrates a sectional view of an embodiment of a bearing according to the disclosure,

[0040] FIG. 3 illustrates a schematic sectional view of a first embodiment of a lubrication ring according to the disclosure,

[0041] FIG. 4 illustrates a schematic sectional view of a second embodiment of a lubrication ring according to the disclosure,

[0042] FIG. 5 illustrates a perspective depiction of a part of the second embodiment, and

[0043] FIG. 6 illustrates a detailed depiction of the outer part.

DETAILED DESCRIPTION

[0044] The disclosure concerns a lubrication ring for a bearing for a pump with a rotating shaft, as well as a bearing for a pump, which is supplied with lubricant by such a lubrication ring. FIG. 1 shows a schematic depiction of an embodiment of such a pump, which is designated with the reference sign 100 in its entirety. The pump 100 is a horizontal, between bearing centrifugal pump, as is used, for example, as process pump in the oil and gas industry. The pump 100 comprises an impeller unit 102 with a centrifugal rotor 103 for conveying a liquid from an inlet to an outlet (not depicted). The rotor 103 is mounted on a shaft 20, which is rotatable around an axis A and drives the rotor for rotation around the axis A. On each side of the impeller unit 102 a bearing 10 for bearing of the shaft 20 is provided. The details of the bearing 10 are described more closely in the following. Since the impeller unit 102 is arranged in between the two bearings 10, the pump 100 is also described as between bearing pump. Additionally, there is a drive 101, for example an electric motor, which rotates the shaft 20 of the pump 100.

[0045] It is self-evident, that the disclosure is not limited to between bearing pumps, but can be applied to all types of pumps, which use lubrication rings for lubrication (e.g., overhung pumps). The disclosure is especially suited for all types of pumps, which have bearings with annular oil lubrication, in which the lubricant needs to be transported to a bearing structure. However, the disclosure is also suited for bearings with oil splash lubrication, in which the bearing structure is arranged directly in the lubricant. In oil splash lubrication, a stronger or better splashing of the lubricant can be achieved by the disclosure, which improves the cooling effect.

[0046] FIG. 2 depicts a sectional view of an embodiment of a bearing 10 according to the disclosure with lubrication rings 1 included within it. The bearing 10 comprises a bearing housing 2 and a bearing cover 3, which is attached to the bearing housing 2 by means of screws or bolts for example. Additionally, there are two bearing structures 4 for the reception and bearing of the shaft 20 of the pump 100 present in a manner known per se. The left bearing structure 4 according to the depiction, serves as axial bearing and here includes two ball bearing elements 41, each of which comprises an inner bearing ring 411, an outer bearing ring 412 and a multitude of balls 413 as rolling bodies, respectively, which are arranged in between the outer bearing ring 412 and the inner bearing ring 411. The inner bearing ring is connected to the shaft 20 in a torque-proof way, and the outer bearing ring 412 is location-proof in relation to the bearing housing 2. For the lubrication and the cooling of the bearing structure 4 the lubrication ring 1 is provided. The lubrication ring 1 is arranged in a groove in a sleeve-like oil slinger 6, which is connected to the shaft 20 in a torque-proof way, and which rotates with the shaft 20. At a floor 21 of the bearing housing 2 of the bearing 10 a lubricant container 22 for a lubricant, for example an oil, is provided. During operation of the pump 100 the lubricant container 22 is filled with the lubricant up to a filling level indicated by the line L in FIG. 2. The lubrication ring 1 loosely hangs at the shaft 20 and is partially submerged in the lubricant within the lubricant container 22. When the shaft 20 rotates, the lubrication ring 1 also rotates and thus transports the lubricant from the lubricant container 22 to the oil slinger 6, which releases the lubricant to the bearing structure 4. The right bearing structure 4, according to the depiction, serves as radial bearing and is designed as a friction bearing here. For this bearing structure 4, designed as a friction bearing, a lubrication ring 4 is also provided, which hangs directly on the shaft 20 and transports the lubricant from the lubricant container 22 to the bearing structure 4.

[0047] The lubrication ring 1 hangs loosely on the shaft 20 or the oil slinger 6 and is driven for rotation around the shaft 20 by the friction between the oil slinger 6 and the lubrication ring 1. The lubrication ring 1 is arranged eccentrically on the oil slinger 6 or the shaft 20, so that the lubrication ring 1 rotates around a different axis of rotation than the shaft 20 in the operating state. The friction between the lubrication ring 1 and the oil slinger 20 is caused by the gravitational force acting on the lubrication ring. As already mentioned, the lubrication ring 1 rotates relative to the shaft 20 in the operating state. The rotational speed of the lubrication ring 1 is lower than the rotational speed of the shaft.

[0048] Preferably, the lubrication ring 1 is designed as a ring-shaped body, in particular as a circular ring-shaped body. In the preferred embodiment of the lubrication ring 1 for ring oil lubrication, the lubricant container 22 is arranged below (with respect to the vertical direction determined by gravity) the shaft 20. The bearing structures 4 are arranged above the line L, i.e. the bearing structures 4 are not immersed in the lubricant in the lubricant container 22, but a part of the lubricating ring 1 hanging down from the shaft 20 is immersed in the lubricant in the lubricant container 22 and transports the lubricant from the lubricant container 22 into the area of the bearing structures 4 when the lubricating ring 1 rotates.

[0049] FIG. 3 depicts a schematic sectional view of a first embodiment of a lubrication ring 1 according to the disclosure. The lubrication ring 1 here comprises an outer part 11 with a transport surface 111, a middle part 12 and an inner part 13 with a running surface 131. The running surface 131 is that surface of the lubrication ring 1, which cooperates with the shaft 20 or the oil slinger 6 to drive the lubrication ring 1. The transport surface 111 is that surface of the lubrication ring 1 which primarily serves the transporting of the lubricant. The running surface 131 is the radially internally located surface, and the transport surface 111 is the radially externally located surface of the lubrication ring 1.

[0050] All three parts 11, 12, 13 are designed in each case in a ring shape. The three individual parts 11, 12, 13 are arranged in such a way, that they have the same geometrical center MP. The outer part 11 has a radius r1 and a thickness d1, the middle part 12 a radius r2 and a thickness d2 and the inner part 13 has a radius r3 and a thickness d3. r0 refers to the outer radius of the entire lubrication ring 1. The three ring shaped parts 11, 12, 13 are designed in such a way that r3<r2<r1<r0, wherein r2=r3+d3, r1=r2+d2 and r0=r1+d1 is given.

[0051] The thickness d1, d2, d3 respectively refers to the extension of the respective part 11, 12, 13 in radial direction. The thickness D of the lubrication ring 1 is then a sum of d1, d2 and d3. This means that the three ring shaped parts are arranged adjacent to each other, so that, viewed in radial direction, a multi-layer lubrication ring is formed.

[0052] In the outer part 11 several pockets 112 are disposed in the transport surface 111. These are respectively designed as indentations in the transport surface 111 of the outer part 11. Several of these pockets 112 are arranged adjacent to each other in circumferential direction across the entire lubrication ring 1. The separation between two adjacent pockets in circumferential direction occurs by a web 113 in each case.

[0053] Each pocket 112 is preferably designed as a concave recess. As such, each pocket 112 is limited by a concave surface in regard to the radial direction. Each pocket 112 preferably has a depth T, which is at least 10% of the thickness D of the lubrication ring 1. This measure is advantageous to achieve an especially good transport rate for the lubricant.

[0054] In the inner part 13 in the running surface 131 several, here three, grooves 132 are provided. These grooves 132 run parallel to each other and stretch across the entire running surface 131 of the lubrication ring 1 in circumferential direction. The outer part 11 and/or the inner part 13 are preferably made from a synthetic material, for example from a polyactic acid (PLA) or from polytetrafluorethene (PTFE). The middle part 12 is preferable made from a metallic material, preferably a stainless steel. This has the advantage that the lubrication ring has a higher mass (in comparison with a fully non-metallic embodiment, for example an embodiment made entirely from a synthetic material), without a change to its outer dimensions. In this way, the contact pressure on the shaft or on the oil slinger 6 which is connected to the shaft 20 in a torque-proof way, is increased. This has the effect, that the drive of the lubrication ring 1 and thus the transporting of lubricant is improved.

[0055] To guarantee a good drive of the lubrication ring, it has shown to be advantageous if each of the grooves 132 has a depth of at least one millimeter. It is further preferred, that each of the grooves has a width of at least one millimeter. Here the depth of the groove 132 is its maximum extension in the radial direction and the width of the groove 132 is its extension in that direction, which stands vertically on the radial direction and vertically on the circumferential direction.

[0056] According to a version of the first embodiment the running surface 131 is designed to be smooth, meaning there are no grooves 132 in the running surface 131.

[0057] FIG. 4 depicts a schematic sectional view of a second embodiment of a lubrication ring 1 according to the disclosure. Here the lubrication ring 1 again has the composition with the three parts 11, 12, 13. In the following, only differences between the second embodiment and the previously described first embodiment will be discussed more closely. Equal components or functionally equal components of the second embodiment are designated with the same reference signs as in the first embodiment. It is understood that all previous explanations of the first embodiment are also valid in the same manner or in analogously the same manner to the second embodiment.

[0058] In the second embodiment the outer part 11 and the inner part 13 are designed in such a way that they envelop, or surround, the middle part 12. The envelopment can, depending on the version, be complete so that the middle part 12 is fully enveloped by the outer part 11 and the inner part 13, or alternatively as shown in FIG. 4, only be partial, so that the middle part 12 is not fully enveloped. The profiles of the outer part 11 and the inner part 13, respectively, are each designed in an L-shape in the second embodiment. Other profiles are also possible, however. Further possible embodiments can be designed with a U-shaped outer part 11 and a rectangular inner part 13 or a rectangular outer part 11 and a U-shaped inner part 13. Similarly, it is possible, that both the outer part 11 as well as the outer part 13 have a U-shape.

[0059] The three parts 11, 12, 13 are connected to each other in a torque-proof way. For this purpose, an adhesive connection or a welded connection can be provided. It is also possible to connect the three parts 11, 12, 13 to each other via a press fit so that an interference fit is formed.

[0060] Naturally, additional embodiments of a lubrication ring 1 are possible. The lubrication ring 1 can be designed in one piece, or be made from two parts or from more than three parts 11, 12, 13. In every case the lubrication ring 1 has a transport surface 111 designed according to the disclosure as well as a running surface 131 which is designed with or without grooves 132.

[0061] FIG. 5 depicts a perspective depiction of a part of the second embodiment. Here the outer part 11 with the transport surface 111 and the several pockets 112, arranged adjacent, which are respectively separated from each other by webs 113, and the inner part 13 with the running surface 131 and the grooves 132 present therein, arranged parallel to each other, are depicted.

[0062] FIG. 6 depicts a detailed depiction of the outer part 11. This embodiment of the outer part 11 is suitable in an analogous way both for the first embodiment (FIG. 3) as well as for the second embodiment (FIG. 4). Here several adjacent pockets 112 are present in the outer part 11, wherein two adjacent pockets are respectively separated by a web 113. The webs 113 enclose an angle ? different from 90? with the circumferential direction U. The angle ? is preferably 60? at most. Especially preferred, the angle ? is around 40?. An angle ? different from 90? is advantageous with regard to the transport properties of the lubrication ring 1. Basically, embodiments are also possible, in which the webs 113 are designed with an angle ? of 90? to the circumferential direction U, however for many applications an angle ? of significantly less than 90?, for example 40?, is preferred so that the pockets have a more hydrodynamically convenient shape. An embodiment with the angle ? equal to 90? can lead to increased friction between the lubrication ring 1 and the lubricant in the lubricant container 22. Additionally, the embodiment with the angle ? of less than 90? leads to a better containment of the lubricant for the transport in the pockets 112. This is because, for example, webs with an angle ? of 90? are less capable of avoiding draining of the lubricant due to the forces occurring because of the rotation of the lubrication ring 1, particularly at lower rotational speeds. Thus, with regard to optimal transport properties such embodiments are preferred, in which the webs 113 enclose an acute angle ? with the circumferential direction U, meaning an angle ? of less than 90?.

[0063] Of course, embodiments in which the angle ? is 90? are also possible and preferred, i.e. the webs 113 extend in a radial direction. This embodiment has the advantage that the function of the lubrication ring 1 is independent of the direction of rotation of the lubrication ring 1, i.e. the lubrication ring 1 has at least substantially the same properties, in particular with regard to the delivery rate, when it rotates clockwise as when it rotates counterclockwise. This independence of the functionality of the lubrication ring 1 represents a considerable advantage, particularly for assembly.

[0064] Both in the first as well as in the second embodiment the lubrication ring 1 preferably has at least 30 pockets 112 and at most 60 pockets 112. Especially the embodiment of the lubrication ring 1 with 45-50 pockets has been shown to be especially effective in usage of the lubrication ring in pumps 100.