PUMP BEARING RETAINER

Abstract

A wet-running pump bearing retainer (29) includes a radial bearing configured for a lubrication film between an inner sliding surface (41) and a rotor shaft (13) of a pump (1). The radial bearing is fitted into a radially inner section (49) that defines an axial fluid channel (45), located at a first radial distance (D1) to a rotor axis (R) and providing a fluid flow path (F1) in a first axial flow direction. The first radial distance is larger than a radius (D0) of the inner sliding surface. A radially outer section (51) extends from the inner section and defines a second axial fluid channel (47) for a flow path (F2) in a second axial flow direction, opposite to the first flow direction. The second axial fluid channel is located at a second radial distance (D2) to the rotor axis, which is larger than the first radial distance.

Claims

1. A pump bearing retainer for a wet-running pump with a rotor shaft, the pump bearing retainer comprising: a radially inner section; a radial bearing with an inner sliding surface configured to allow a lubrication film between the inner sliding surface and the rotor shaft of the pump, the radial bearing being fitted into the radially inner section; and a radially outer section extending radially outward from the inner section, wherein: the radially inner section defines at least one first axial fluid channel providing a first fluid flow path in a first axial flow direction; the at least one first axial fluid channel is located at a first radial distance to a rotor axis; the first radial distance is larger than the radius of the inner sliding surface; the radially outer section defines at least one second axial fluid channel providing a fluid flow path in a second axial flow direction through the at least one second axial fluid channel; the at least one second axial fluid channel is located at a second radial distance to the rotor axis; the second radial distance is larger than the first radial distance; and the second axial flow direction is opposite to the first axial flow direction.

2. The pump bearing retainer according to claim 1, wherein: the radially inner section comprises an inner section surface for a press-fit contact with an essentially cylinder-shaped radial outer surface of the radial bearing; and a shape of the inner section surface defines the at least one first axial fluid channel that is located between the inner section and the radial bearing.

3. The pump bearing retainer according to claim 1, wherein the radially outer section defines n≥2 second axial fluid channels distributed in an n-fold rotational symmetry.

4. The pump bearing retainer according to claim 1, wherein the at least one first axial fluid channel is axially offset with respect to the at least one second axial fluid channel.

5. The pump bearing retainer according to claim 1, wherein: the at least one first axial fluid channel has a total cross-sectional area that is ten times or more larger than a cross-sectional area of the lubrication film; or the at least one second axial fluid channel has a total cross-sectional area that is ten times or more larger than a cross-sectional area of the lubrication film; or the at least one first axial fluid channel has a total cross-sectional area that is ten times or more larger than a cross-sectional area of the lubrication film and the at least one second axial fluid channel has a total cross-sectional area that is ten times or more larger than a cross-sectional area of the lubrication film.

6. The pump bearing retainer according to claim 1, wherein the at least one first axial fluid channel has a total cross-sectional area that is larger than 0.5 square millimetres.

7. The pump bearing retainer according to claim 1, wherein the at least one second axial fluid channel has a total cross-sectional area that is larger than 0.5 square millimetres.

8. The pump bearing retainer according to claim 1, wherein a maximal radial extension of the at least one second axial fluid channel is below 300 microns.

9. The pump bearing retainer according to claim 1, wherein the at least one first axial fluid channel comprises m number of fluid channels; the at least one second axial fluid channel comprises n number of fluid channels; and m>n.

10. The pump bearing retainer according to claim 1, wherein each of the at least one second axial fluid channels is formed as an arc-shaped slot having an arc radius essentially equal to the second radial distance.

11. The pump bearing retainer according to claim 10, wherein each arc-shaped slot extends over 0.05 to 0.5 radians.

12. The pump bearing retainer according to claim 1, wherein: the inner section surface comprises at least one first portion and at least one second portion in a circumferential direction; the at least one first portion has a first radius; the at least one second portion has a second radius that is larger than the first radius, such that the at least first portion defines at least one contact portion for a press-fit with an essentially cylinder-shaped radial outer surface of a radial bearing and such that the at least one second portion defines the at least one first axial fluid channel located between the inner section and the radial bearing.

13. The pump bearing retainer according to claim 1, wherein the radial bearing or the inner sliding surface comprise a ceramic.

14. A wet-running centrifugal pump comprising: a permanent-magnet synchronous motor; a rotor shaft; an impeller mounted to the rotor shaft; and a pump bearing retainer comprising: a radially inner section; a radial bearing fitted into the radially inner section, the rotor shaft being arranged in the radial bearing with a clearance to an inner sliding surface of the radial bearing for establishing a lubrication film; and a radially outer section extending radially outward from the inner section, wherein: the radially inner section defines at least one first axial fluid channel providing a first fluid flow path in a first axial flow direction; the at least one first axial fluid channel is located at a first radial distance to a rotor axis; the first radial distance is larger than the radius of the inner sliding surface; the radially outer section defines at least one second axial fluid channel providing a fluid flow path in a second axial flow direction through the at least one second axial fluid channel; the at least one second axial fluid channel is located at a second radial distance to the rotor axis; the second radial distance is larger than the first radial distance; and the second axial flow direction is opposite to the first axial flow direction.

15. The pump according to claim 14, wherein an axial distance of the impeller to the radially outer section of the pump bearing retainer, measured at an outer radius of the impeller is below 2.0 millimetres.

16. The pump according to claim 14, wherein an outer radius of the impeller is smaller than the second radial distance of the at least one second axial fluid channel to the rotor axis.

17. The pump according to claim 14, wherein: the at least one first axial fluid channel has a total cross-sectional area that is ten times or more larger than a cross-sectional area of the lubrication film; or the at least one second axial fluid channel has a total cross-sectional area that is ten times or more larger than a cross-sectional area of the lubrication film; or the at least one first axial fluid channel has a total cross-sectional area that is ten times or more larger than a cross-sectional area of the lubrication film and the at least one second axial fluid channel has a total cross-sectional area that is ten times or more larger than a cross-sectional area of the lubrication film.

18. The pump according to claim 14, further comprising a rotor can, wherein: the pump bearing retainer is located axially between the rotor can and the impeller; the rotor can and the pump bearing retainer define the outer boundaries of a rotor chamber; an axial distance of the rotor can to the at least one second axial fluid channel in the radially outer section of the pump bearing retainer is larger than the axial distance of the impeller to the radially outer section of the pump bearing retainer, measured at an outer radius of the impeller.

19. A method of operating a wet-running centrifugal pump comprising a permanent-magnet synchronous motor, the method comprising: providing, when the motor is running, a first flow path from a rotor chamber into an impeller chamber through at least one first axial fluid channel defined by a radially inner section of a pump bearing retainer of the pump; and providing, when the motor is running, a second flow path from the impeller chamber into the rotor chamber through at least one second axial fluid channel defined by a radially outer section of the pump bearing retainer.

20. The method according to claim 19, wherein a circular flow from the rotor chamber into the impeller chamber along the first flow path and from the impeller chamber back into the rotor chamber along the second flow path is driven by a Tesla pump effect between the impeller and the pump bearing retainer when the motor is running.

21. The method according to claim 19, further comprising: providing, when the motor is stopped, a third flow path from the rotor chamber into the impeller chamber through an inner rotor shaft channel extending between a second axial shaft end and a first axial shaft end, wherein the second axial shaft end is located within the rotor chamber and the first axial shaft end is located in the impeller chamber; and providing, when the motor is stopped, a fourth flow path from the impeller chamber into the rotor chamber through the at least one first axial fluid channel.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

[0037] In the drawings:

[0038] FIG. 1 is a longitudinal cut view of an embodiment of a pump according to the present disclosure;

[0039] FIG. 2 is a longitudinal cut view of the pump as shown in FIG. 1 without the pump housing;

[0040] FIG. 3a is a top view of an embodiment of a pump bearing retainer according to the present disclosure with detail views of a first axial channel and second axial channel;

[0041] FIG. 3b is a cut view of the pump bearing retainer along the plane C-C as shown in FIG. 3a;

[0042] FIG. 4a is a longitudinal cut view of the pump as shown in FIG. 1 with arrows indicating flow paths during operation of the pump; and

[0043] FIG. 4b is a longitudinal cut view of the pump as shown in FIG. 1 with arrows indicating flow paths during when the pump is not running.

DESCRIPTION OF PREFERRED EMBODIMENTS

[0044] Referring to the drawings, FIG. 1 shows a wet-running centrifugal pump 1 that is typically used to circulate water in household heating systems. The pump 1 comprises a pump housing 3 having a suction inlet 5 and a pressure outlet 7. The section inlet 5 and the pressure outlet 7 are essentially coaxially aligned along an axis x. The pump 1 further comprises a motor housing 9 and an electronics housing 11. The motor housing 9 and the electronics housing 11 are essentially coaxially aligned along an axis z, which extends perpendicular to the x-axis. The motor housing 9 is fixed to the pump housing 3 and the electronics housing 11 is fixed to the motor housing 9. The pump 1 further comprises a rotor shaft 13 extending along the x-axis and defining a rotor axis R extending along the z-axis. The motor housing 9 encloses a permanent magnet synchronous motor (PMSM) 15 comprising a stator 17 and a rotor 19. The rotor 19 is fixed to the rotor shaft 13 and rotatable about the rotor axis R. The electronics housing 11 comprises electronics for controlling the motor 15.

[0045] The rotor shaft 13 comprises a first axial shaft end 21 protruding outside of the motor housing 9 and a second axial shaft end 23 located within the motor housing 9. An impeller 25 is mounted to the first axial shaft end 21 and arranged within an impeller chamber 27 formed by the pump housing 3. A boundary of the impeller chamber 27 towards the motor housing 9 is defined by a pump bearing retainer 29.

[0046] The motor housing 9 comprises a dry region 31 and a wet region in form of a rotor chamber 33. The stator 17 of the motor 15 is located within the dry region 31, whereas the rotor 19 and the rotor shaft 13 are located within the wet region, i.e. the rotor chamber 33. The rotor chamber 33 is separated from the dry region 31 by a rotor can 35.

[0047] The rotor shaft 13 is axially aligned by two radial bearings, i.e. a first radial bearing 37 and a second radial bearing 39. The first radial bearing 37 is retained by the pump bearing retainer 29 and located close to the impeller 25. The second radial bearing 39 is located close to the second axial shaft end 23. The rotor 19 is arranged between the first radial bearing 37 and the second radial bearing 39. The first radial bearing 37 comprises an inner sliding surface 41 with a clearance to the rotor shaft 13 to establish a low-friction lubrication film between the inner sliding surface 41 and the rotor shaft 13. Analogously, the second radial bearing comprises an inner sliding surface. The first radial bearing further comprises an annular sliding surface 43 facing away from the pump housing 3. Thereby, the first radial bearing 37 also serves as an axial bearing for the rotating parts of the pump 1.

[0048] It should be noted that there is a clearance of less than 20 microns between the outer diameter of the rotor shaft 13 and the inner sliding surface 41 of the radial bearing 37. Such a clearance provides for a lubrication film established by the fluid to be pumped to reduce the frictional losses in the pump 1. The total cross-sectional area of the lubrication film may be below 0.5 mm.sup.2. A fluid flow along the lubrication film is not desirable, in particular when the pump is not running, because such a flow causes precipitation and sedimentation of lime-scale between the rotor shaft 13 and the first radial bearing 37, which increases the risk of blocking the rotor shaft 13 for next pump start.

[0049] In order to reduce the risk of fluid flow along the lubrication film, the pump bearing retainer 29 defines specific alternative axial fluid channels 45, 47 that serve as a bypass or shunt. The pump bearing retainer 29 comprises a radially inner section 49 into which the first radial bearing 37 is press-fitted. Furthermore, the pump bearing retainer 29 comprises a radially outer section 51 extending radially outward from the inner section 49. The radially inner section 49 defines first axial fluid channels 45 where it contacts the first radial bearing 37. As shown in FIG. 2, this means that the first axial fluid channels 45 are located at a first radial distance D1 to the rotor axis R, wherein the first radial distance D1 essentially corresponds to the outer radius of the first radial bearing 37. It is important to note that the first radial distance D1 is larger than the radius D0 of the inner sliding surface 41 of the first radial bearing 37. The radially outer section 51 of the pump bearing retainer 29 defines second axial fluid channels 47 in form of slots. The second axial fluid channels 47 are located at a second radial distance D2 to the rotor axis R, wherein the second radial distance D2 is larger than the first radial distance D1. It should be noted that the outer radius D3 of the impeller 25 is larger than the first radial distance D1, but smaller than the second radial distance D2, i.e. D0<D1<D3<D2.

[0050] As shown in FIG. 2, there is an axial distance H of less than 2.0 mm, preferably 1.5 mm, between the impeller 25 and the radially outer section 51 of the pump bearing retainer 29, measured at the outer radius D3 of the impeller 25. Such a small axial distance H is particularly useful to provide a Tesla pump effect between the impeller 25 and the pump bearing retainer 29, so that there is a lower pressure at the first axial fluid channels 45 than at the second axial fluid channels 47. This pressure differential drives a circular flow as shown in FIG. 4a when the pump is running. The flow direction through the second axial fluid channel 47 from the impeller chamber 27 into the rotor chamber 33 is opposite to the flow direction through the first axial fluid channel 45 from the rotor chamber 33 into the impeller chamber 27. This circular flow is particularly beneficial to reduce the risk of magnetite accumulation at the rotor 19, because the magnetite leaves the rotor chamber 33 through the first axial fluid channels 45 before it reaches the rotor 19.

[0051] FIG. 3a shows the pump bearing retainer 29 in more detail. It can be seen that the radially inner section 49 of the pump bearing retainer 29 is “crenelated” in radial direction forming six “crenels” in the contact area with the first radial bearing 37. The crenels each form a first axial fluid channel 45 between the radially inner section 49 and the first radial bearing 37. In other words, the radially inner section 49 comprises an inner section surface 53 for a press-fit contact with an essentially cylinder-shaped radial outer surface 55 of the first radial bearing 37. The shape of the inner section surface 53 defines the first axial fluid channels 45 being located between the inner section 49 and the first radial bearing 37. The inner section surface 53 comprises six first portions 57 and six second portions 59 in circumferential direction. The first portions 57 have a first radius r1 and the second portions 59 have a second radius r2 being larger that than the first radius r1, i.e. r1<r2, such that the first portions 57 define contact portions for a press-fit with the essentially cylinder-shaped radial outer surface 55 of the first radial bearing 37, and such that the second portions 59 define the first axial fluid channels 45. The first portions 57 and the second portions 59 are evenly distributed in circumferential direction in a six-fold rotational symmetry. The first axial fluid channels 45 are formed as arc-shaped slots with a width, i.e. r2−r1, of less than 300 microns and an arc length L1 of more than 0.1 radians.

[0052] The total cross-sectional area A of the m=6 first axial fluid channels 45 can be approximated by A≈m.Math.L1.Math.E1, whereas the total cross-sectional area B of the n=4 second axial fluid channels 47 can be approximated by B≈n.Math.L2.Math.E2. The total cross-sectional areas A and B are each a factor of 10 or more larger than the total cross-sectional area of the lubrication film between the radial bearing 37 and the rotor shaft 13. Thereby, an axial flow along the lubrication film is significantly minimized.

[0053] The four second axial fluid channels 47 are formed as arc-shaped slots cut into the radially outer section 51 of the pump bearing retainer 29, wherein the slots have an arc radius essentially equal to the second radial distance D2 between the second axial fluid channels 47 and the rotor axis R. Analogous to the first axial fluid channels 45, the width of the second axial fluid channels 47, i.e. their maximal radial extension E2, is below 3000 microns. This is particularly beneficial to prevent larger particles from entering the rotor chamber 33 through the second axial fluid channels 47. The arc length L2 of the second axial fluid channels 47 may extend over 0.05 to 0.5 radians. Analogous to the first axial fluid channels 45, the four second axial fluid channels 47 are evenly distributed in a four-fold rotational symmetry with respect to the rotor axis R.

[0054] The method according to the present disclosure is described in FIGS. 4a,b, wherein FIG. 4a shows the predominant circular flow when the pump 1 is running. This circular flow is driven by a Tesla pump effect between the impeller 25 and the pump bearing retainer 29 having a small axial distance H of less than 2.0 mm to each other. The circular flow comprises a first flow path F1 in a first axial flow direction from the rotor chamber 33 into the impeller 29 through the first axial fluid channels 45. Furthermore, the circular flow comprises a second flow path F2 in a second axial flow direction opposite to the first axial flow direction from the impeller chamber 27 through the second axial fluid channels 47 into the rotor chamber 33.

[0055] It should be noted that the rotor shaft 13 is in this example hollow to define a third flow path F3 from the second axial shaft end 23 to the first axial shaft end 21, i.e. from the rotor chamber 33 into the impeller chamber 27. The third flow path F3 is not part of the circular flow shown in FIG. 4a, when the pump is running, but used to degas the rotor chamber 33 when the pump is stopped as shown in FIG. 4b. In fact, a flow along the third flow path F3 during pump operation should be minimized as much as possible, because such a flow reduces the pump efficiency. Therefore, the third flow path F3 has a very narrow bottle neck 61 at the first axial shaft end 21 with a very small opening of less than 0.05 mm2 into the impeller chamber 27. This is sufficient to degas the rotor chamber 33. However, due to the low pressure at the centre of the impeller 25, a significant flow along the third flow path F3 is a problem of the prior art, where it transports magnetite into the rotor chamber 33, so that it accumulates at the rotor 19 and increases frictional losses and wear of the rotor can 35. The circular flow with the first flow path F1 and the second flow path F2 through the first axial flow channels 45 and the second axial flow channels 47, respectively, significantly reduces the flow along the third flow path F3 when the pump is operating. In fact, the third flow path F3 is not needed anymore at all for the pump according the present disclosure, because the rotor chamber 33 may degas via the first fluid channels 45 and the second fluid channels 47.

[0056] When the pump is stopped, as shown in FIG. 4b, there may be a “breathing” flow due to thermal expansion of the fluid via the first flow path F1 and/or the second flow path F2 through the first fluid channels 45 and/or the second fluid channels 47, respectively. Such a “breathing” flow may, for instance, be driven by fluid temperature differences between the two axial shaft ends 21, 23. The fluid in the impeller chamber 27 may have a different temperature compared to the fluid at the second axial shaft end 23, so that fluid flows from the rotor chamber 33 into the impeller chamber 27 and back. The first axial fluid channels 45 provide the first flow path F1 and/or a fourth flow path F4 from the impeller chamber 27 into the rotor chamber 33, i.e. in an opposite direction compared to the first flow path F1 when the pump is running Thereby, both the flow along the lubrication film between the first radial bearing 37 and the rotor shaft 13 as well as the flow along the third flow path F3 is minimised, because the alternative flow paths F1, F4 and/or F2 provide a flow path of less resistance. Thus, the risk of rotor shaft blockage due to precipitation and sedimentation of lime-scale in the lubrication film during a long period of non-operating the pump, e.g. in summer periods when no heating is needed, is significantly reduced. Furthermore, the rotor chamber 33 can be degassed via the flow paths F1, F2 and/or F2.

[0057] Where, in the foregoing description, integers or elements are mentioned which have known, obvious or foreseeable equivalents, then such equivalents are herein incorporated as if individually set forth. Reference should be made to the claims for determining the true scope of the present disclosure, which should be construed so as to encompass any such equivalents. It will also be appreciated by the reader that integers or features of the disclosure that are described as optional, preferable, advantageous, convenient or the like are optional and do not limit the scope of the independent claims.

[0058] The above embodiments are to be understood as illustrative examples of the disclosure. It is to be understood that any feature described in relation to any one embodiment may be used alone, or in combination with other features described, and may also be used in combination with one or more features of any other of the embodiments, or any combination of any other of the embodiments. While at least one exemplary embodiment has been shown and described, it should be understood that other modifications, substitutions and alternatives are apparent to one of ordinary skill in the art and may be changed without departing from the scope of the subject matter described herein, and this application is intended to cover any adaptations or variations of the specific embodiments discussed herein.

[0059] In addition, “comprising” does not exclude other elements or steps, and “a” or “one” does not exclude a plural number. Furthermore, characteristics or steps which have been described with reference to one of the above exemplary embodiments may also be used in combination with other characteristics or steps of other exemplary embodiments described above. Method steps may be applied in any order or in parallel or may constitute a part or a more detailed version of another method step. It should be understood that there should be embodied within the scope of the patent warranted hereon all such modifications as reasonably and properly come within the scope of the contribution to the art. Such modifications, substitutions and alternatives can be made without departing from the spirit and scope of the disclosure, which should be determined from the appended claims and their legal equivalents.

[0060] While specific embodiments of the invention have been shown and described in detail to illustrate the application of the principles of the invention, it will be understood that the invention may be embodied otherwise without departing from such principles.

LIST OF REFERENCE CHARACTERS

[0061] 1 pump [0062] 3 pump housing [0063] 5 suction inlet [0064] 7 pressure outlet [0065] 9 motor housing [0066] 11 electronics housing [0067] 13 rotor shaft [0068] 15 motor [0069] 17 stator [0070] 19 rotor [0071] 21 first axial shaft end [0072] 23 second axial shaft end [0073] 25 impeller [0074] 27 impeller chamber [0075] 29 pump bearing retainer [0076] 31 dry region of motor housing [0077] 33 rotor chamber [0078] 35 rotor can [0079] 37 first radial bearing [0080] 39 second radial bearing [0081] 41 inner sliding surface of first radial bearing [0082] 43 annular sliding surface of first radial bearing [0083] 45 first axial fluid channel(s) [0084] 47 second axial fluid channel(s) [0085] 49 radially inner section of pump bearing retainer [0086] 51 radially outer section of pump bearing retainer [0087] 53 inner section surface [0088] 55 radial outer surface of first radial bearing [0089] 57 first portions [0090] 59 second portions [0091] 61 bottle neck [0092] R rotor axis [0093] H axial distance [0094] E1 maximal radial extension of the first axial fluid channels [0095] E2 maximal radial extension of the second axial fluid channels [0096] D0 inner radius of first radial bearing [0097] D1 first radial distance [0098] D2 second radial distance [0099] D3 outer radius of impeller [0100] F1 first flow path [0101] F2 second flow path [0102] F3 third flow path [0103] F4 fourth flow path [0104] r1 first radius [0105] r2 second radius [0106] L1 arc length of first axial fluid channels [0107] L2 arc length of second axial fluid channels [0108] A total cross-sectional area of the first axial fluid channels [0109] B total cross-sectional area of the second axial fluid channels [0110] m number of first axial fluid channels [0111] n number of second axial fluid channels