VERTICAL BEARING ASSEMBLY LUBRICATION

Abstract: A self-contained vertical bearing assembly (10), which includes a shaft (5) carrying a collar flange (13) by which it is supported on bearing thrust pads (22) (figure 2) and spaced from surrounding stator wall (36) within a lubricant bath, has in stator wall (36) recesses such as (37) which define viscosity pumps that deliver lubricant from the bath to utilisation means, such as a heat exchanger (43) or lubrication gallery for a bearing part (69), as the shaft rotates. Relatively short recesses that are as wide as the flange can operate irrespective of shaft rotation direction and nothwithstanding the gap between rotor and stator surfaces to deliver lubricant at sufficient rate and/or pressure to provide extra facilities without external pumps or major internal re-design of a bearing assembly.

Description: Vertical Bearing Assembly Lubrication This invention relates to vertical bearing assemblies employed to support vertically extending rotatable shafts and provide thrust and/or journal bearing support therefor, and in particular relates to lubricant arrangements therefor. A vertical bearing assembly of known form, employed to support a vertical shaft which is capable of being rotated about its longitudinal axis in either rotational direction, is illustrated in sectional elevation in Figure 1. A shaft 5 having longitudinal axis 6 is suspended from its upper end 7 by a vertical bearing assembly shown generally at 10. The bearing assembly comprises a collar 1 1 surrounding the end 7 of the shaft and rotatable with the shaft as a rotor part, which collar has an axially extending part 12 and a radially enlarged flange 13 to define radially extending, axially directed faces 14 and 15. The bearing assembly also comprises a stator housing 20 which surrounds the collar 1 1 and contains other stator parts of the assembly. The bearing assembly comprises several bearing parts contained within the housing and is shown comprising a main thrust bearing part 21 , in the form of a ring of bearing pads 22 carried by the stator arrayed about the shaft to support the shaft by way of the face 14 of the collar flange, a reverse thrust bearing part 23, in the form of a ring of small bearing pads 24 supported by the structure to engage with the flange face 15, and a journal bearing part 25, in the form of a plurality of bearing pads 26 carried by the stator and arrayed about the axially extending pan 12 of the collar. The bearing parts are of conventional bearing material, such as white metal on a backing metal, and operate with an intervening film of liquid lubricant, formed by filling the housing with lubricant 27 to a level 27' above the highest bearing part, that is, with the bearing parts totally immersed in a bath of the lubricant. The bearing pads are also mounted such that they have a limited degree of tilt to permit the lubricant film to adopt a wedge-like thickness due to hydrodynamic forces during rotation and to accommodate minor misalignment between the shaft and stator. The total immersion of the bearing surfaces within the lubricant ensures that a hydrodynamic film is available at all times without priming; the bearing assembly is thus fully contained within the housing and for this reason is sometimes referred to as being of the vertical self-contained type. Notwithstanding that the housing parts are totally immersed in a bath of lubricant, reliance on the lubricant and its inherently low pressure head and poor extraction of heat means that the power envelope of such bearing assembly is limited and determined to a significant extent by the thermal properties of the lubricant. In particular, although lubricant is moved through the bearing parts to some extent by the shaft rotation and viscous drag on the lubricant film, the rate of flow and/or hydrodynamic pressure is limited by shaft rotation speed and lubricant temperature in the vicinity of the bearing parts. Heat generated at the bearing parts limits the speed at which the shaft can be rotated and/or the load carried by the shaft unless the heat is removed from the bearing parts by way of the lubricant of the bath and/or stator and housing structure. The structure of the stator inhibits convection currents within the lubricant from adequately distributing it through the bath. It is known to provide heat exchange pipes within the bath of lubricant and through which a coolant is caused to flow to extract heat from the bath of the lubricant, and indicated by ghosted lines 28. It is known alternatively to provide the housing with external fins 29, or the like and to dispose the whole housing in a ducted stream of cooling fluid, such as air forced to flow over the fins by a fan 29, carried at the end of the shaft or collar, or to surround the housing with a water jacket. However, such known arrangements of influencing the power envelope of the bearing assembly by influencing the behaviour and functionality of the lubricant depend upon transfer of heat through the lubricant of the bath which, notwithstanding the limited degree of fluid movement within the bearing parts, is essentially stagnant and presents a poor conductor. Bearing parts of such an assembly may benefit in respect of their performance by forced lubrication at increased lubricant supply pressure, although in the long term extraction of heat efficiently from the lubricant bath remains a problem. Likewise forcing the lubricant from the housing by an exterior pump to extract heat is possible but in both instances, the concept of the self-contained bearing is lost by interfacing with additional external elements and the costs are significant. Similarly, provision of such facilities within the housing and bearing assembly has been perceived also to offend against the principle of self containment and involve major redesign and an increase in space required within the housing, costing more to implement than the provision of external modifications and result in a housing increased dimensionally which is unacceptable. Although Figure 1 shows a specific form of self-contained vertical bearing assembly comprising thrust, reverse thrust and journal bearing parts, it will be appreciated that such an assembly may comprise fewer such parts and/or exhibit a different relative disposition with respect to the shaft. In this specification a vertical bearing assembly is defined as a bearing assembly comprising one or more bearing parts disposed in relation to a shaft rotatable about a vertically aligned longitudinal axis, said assembly comprising a rotor part carried by the shaft and a stator part surrounding the rotor part and containing a bath of lubricant for parts of the bearing assembly. It is an object of the present invention to provide for such a defined vertical bearing assembly a lubrication arrangement of simple and compact construction that permits improvement in the total power envelope of the assembly. According to the present invention a lubrication arrangement for a vertical bearing assembly (as herein defined) comprises la) a housing containing bearing parts of the assembly and providing a bath of liquid lubricant, (b) viscosity pump means comprising at least one viscosity pump set and each set comprising at least a first viscosity pump defined by (i) a rotor surface of the assembly submerged in said lubricant and (ii) a facing submerged stator surface containing a first surface recess extending part way about the rotor axis between first and second ports located at opposite end regions of the recess thereby rotation of the rotor relative to the stator- surface entrains lubricant to flow in the direction of said rotation between a leading one of said first and second ports and a trailing one of said first and second ports, and (c) associated with each said viscosity pump set, first duct means extending between said first port of each pump and an opening submerged in the lubricant bath and second duct means extending between said second port of each pump and lubricant utilisation means. The lubricant utilisation means may comprise a heat exchanger means having lubricant port means and coolant inlet and outlet means. Such heat exchanger means is preferably disposed without the housing. Alternatively or additionally the lubricant utilisation means may comprise a force lubricated bearing part of the bearing assembly. Given that H is common for shafts suspended by such vertical bearing assemblies to rotate in either direction at least one viscosity pump set may comprise also a second viscosity pump, defined by said submerged rotor surface and part of said facing submerged stator surface containing a second surface recess therein extending between first and second ports located at opposite end regions of the recess whereas rotation of the rotor relative to the stator surface entrains lubricant to flow in the direction of said rotation between a leading one of said first and second ports and a trailing one of said first and second ports, and said first duct means extends between said first port of the second pump and an opening submerged in the lubricant and said second duct means extends between said second port and lubricant utilisation means, said recess ports of the pumps being disposed with respect to each other such that a particular rotational direction of the rotor defines as the leading ports of the pumps the first recess port of one pump and the second recess port of the other pump. Depending upon the nature of the lubricant utilisation means and its coupling with the duct means, the viscosity pumps of a set may work individually or together, in parallel or tandem irrespective of the direction of shaft rotation or each pump may be isolated by one-way valve means or the equivalent such that it is effective for a particular direction of shaft rotation only. The viscosity pump means may comprise two such pump sets each set being associated with a different form of lubricant utilisation means; one viscosity pump set being associated with heat exchanger means and the other pump set being associated with forced lubrication of a bearing part of the assembly. Embodiments of the invention will now be described by way of example with reference to the accompanying drawings, in which:- Figure 1 described hereinbefore, is a sectional elevation through a known form of self-contained vertical bearing assembly for a shaft capable of rotation in either direction about its longitudinal axis and showing, in addition to a bath of lubricant formed within an assembly housing, different forms of heat exchanger means for removing heat from the bath of lubricant. Figure 2(a) is a sectional elevation through a schematic form of vertical bearing assembly but in accordance with the present invention, including a lubrication arrangement that includes viscosity pump means and lubricant utilisation means in the form of heat exchanger means external to the housing, and also forced lubrication to a journal bearing of the assembly, Figures 2(b) and 2(c) are enlargements of the regions B and C respectively of Figure 2(a) simplified to illustrate relevant features, Figure 3 is a cross-section through part of the assembly of Figure 2 along the line X-X thereof showing the viscosity pump means and duct means coupling it to the heat exchanger means, Figures 4(a) to 4(e) are schematic representations of variants on the above with possible connections between the viscosity pump means and heat exchange means or forced lubrication means, Figures 5(a) and 5(b) are schematic sectional elevations showing alternative dispositions of viscosity pump pumping chamber recesses for pumps within the same set, and for different sets, respectively, Figure 6 is a schematic sectional elevation showing an alternative disposition of viscosity pump at a radially extending, rather than axially extending, stator and rotor face, Figure 7(a) is a schematic sectional elevation showing an alternative form of viscosity pump arrangement combined with journal bearing means, and Figure 7(b) is a schematic cross-sectional view showing a form of viscosity pump in combination with, but circumferentially segregated from, journal bearing means. Referring to Figures 2(a)-(c) and 3 which show a vertical bearing assembly and shaft supported thereby, the parts thereof and reference numbers employed correspond to those of Figure 1 described above. A lubrication arrangement 30 in accordance with the present invention is incorporated in such assembly. The lubrication arrangement comprises the housing 20 which forms a reservoir for a quantity of liquid lubricant 27, typically mineral oil, sufficient to submerge the bearing parts beneath the lubricant surface 27'. The lubricant thus forms a bath in which the bearing parts are immersed. In addition to the housing and bath of lubricant, the arrangement also comprises viscosity pump means indicated generally at 31 comprising in this embodiment a first viscosity pump set 32 and second viscosity pump set 33. The first viscosity pump set 32 comprises at least a first viscosity pump 34, defined by a rotor surface 35 submerged in the reservoir and a facing submerged stator surface 36 containing a first surface recess 37 extending part way about the rotor axis 6, between end regions 37,, 37 2 of the recess at which are located first and second ports 38, and 38 2 respectively. The rotor surface 35 comprises an axially extending periphery of the flange 13 that otherwise provides the thrust faces 14 and 15 and is the radially outermost part of the collar 1 1 which, for any particular angular speed of the shaft, has maximum linear speed relative to the stator surface 36 and recess 37 which faces it. The surfaces 35 and 36 have no bearing function and thus are separated to avoid contact between them, typically of order of 1 mm clearance. However, the surfaces and recess are submerged between the surface of the lubricant bath and are permanently primed with lubricant such that the recess 37 forms a pumping chamber and as the rotor surface rotates with respect to the stator surface it entrains lubricant to flow along the recess in the direction of the rotation between a leading one of the ports and a trailing one, that is, between ports 38, and 38 2 for the clockwise rotation shown in Figure 3. The first viscosity pump 32 has associated with it first duct means 39,, comprising a duct 40, extending between the first port 38, and an opening 41 , submerged below the surface of the lubricant bath, and second duct means 39 2 , comprising a duct 42, extending between the second port 38 2 and lubricant utilisation means included generally at 43. The lubricant utilisation means comprises heat exchanger means 44 having lubricant port means 45, 46 and coolant inlet and outlet means 47, 48. In the form illustrated, it comprises a finned multiple- tubed, or serpentine-tubed, core 49 through which lubricant circulates between port means 45 and 46, and is disposed without the housing but within an air duct 50 surrounding the housing and through which air is forced by fan 51 mounted on the collar 1 1 or shaft 5, the finned surface of the core 49 defining at each side thereof the coolant inlet and outlet means 47 and 48. The first viscosity pump set 32 also comprises a second viscosity pump 54 which comprises a second recess 57 in the stator surface 36 extending about the rotor axis in series with the recess 37 at the same vertical level facing rotor surface 35. The second recess 57 has end regions 57, and 57 2 at which open first and second ports 58, and 58 2 respectively. First duct means 39, includes a duct 40 2 extending from first port 58, to an opening 41. submerged below the surface of the lubricant bath, like opening 41 ,. The second duct means 39 2 includes a duct 42 2 extending from the second port 58, to the heat exchanger means 44. The second viscosity pump of the set is identical to the first in that a clockwise shaft rotation defines the second port 58 2 as a leading port and the first port 58, as a trailing port. It will be appreciated that if and when the shaft rotates in an opposite, counter clockwise, direction the ports 38 2 and 58, become leading ports and the ports 38, and 58 2 becomes trailing ports. Each viscosity pump, of which viscosity pump 34 is typical, is formed with a pumping chamber recess 37 of substantially uniform width and depth in a central part 37, between end regions 37, and 37 2 , that is, the recess base 37 4 extends parallel to stator surface 36 and the side walls of the recess are sutatantially perpendicular to the stator surface 36. The end regions 37, and 37 2 whose function is to direct fluid between the leading and trailing ports (as defined by shaft rotation direction) and separate it from the fluid constrained to flow with the rotor surface across the stator surface 36, conveniently each comprise an arc of a circle, but clearly more complex and efficient shapes could be implemented if the bearing assembly structure supports them, as discussed hereinafter. As mentioned above, the viscosity pumps 34 and 54 of the first set are disposed at the same vertical height and are of the same dimensions such that they pump at substantially the same rate. The recesses 37 and 57 are disposed end to end in series about the rotor axis. For reasons which will become apparent, the viscosity pump set 32 is confined to an angular extent of 180° about the rotation axis, each pump recess therefore extending for less than 90°, but preferably not significantly less than 70°. A minimum length in a circumferential direction is considered to be about 100mm. The viscosity pump set is therefore provided by making only minor modifications to the structure of a known bearing assembly and utilises surfaces thereof having no other function. Particularly, and unusually for a viscosity pump which makes use of bearing lubricant, it is not found in a bearing surface which has hydrodynamic bearing pressures and a compromise between the provision of stator recess and absence of bearing surfaces found at said stator recess, although if desired, such viscosity pump could be formed in the manner shown if the stator surface 33 were a bearing surface supporting rotor surface 35 as discussed hereinafter. In addition to the relative simplicity with which the arrangement may be incorporated into a known design of bearing assembly without major redesign of the latter, each viscosity pump means may be defined simply with low criticaiity of dimensions and surface forms in view of its submerged location and the efficiency of lubricant pick-up from the bath in the permanently primed state that then exists, notwithstanding compromised efficiency in other areas that would at first sight seem to militate against the use of the adopted form. It is well known that lubricant is caused to move along the pumping chamber recess of a viscosity pump by the turbulence associated with proximity to the rotor surface and that the delivery pressure is a function of rotor speed and recess length (if below a minimum value of about 100mm) whereas the delivery rate is a function of rotor speed and effective cross-sectional area of the recess, provided that a maximum depth is not exceeded beyond which circulation within the recess destroys a pumping action. Thus the effective cross-sectional area is determined largely by its width. Thus in the above described bearing assembly structure, when the dimensions circumferentiallγ about, and axially along, the rotor-stator interface are fixed and the shaft can rotate in both directions, cooling of the lubricant is achieved by passing it through heat exchanger means 46 at a flow rate which takes precedence over delivery pressure; that is, each viscosity pump is of maximum recess width in the axial direction at the expense of being relatively short circumferentially. The above construction also compromises efficiency in another respect. Whereas the viscosity pump inherently functions for either direction of rotor rotation, it is found with such a significant clearance between rotor and stator surfaces that if there is significant resistance to lubricant being drawn into the pumping chamber recess by way of the leading port then lubricant tends to be drawn into the recess from the clearance, from the turbulent flow associated with the rotor surface, and proper flow rate is reduced significantly. Thus in the bidirectional rotor assembly, it is appropriate to try to maximise flow rate whilst accommodating bidirectional rotation by using both pumps of the set for both rotation directions whilst if possible avoiding a large suction resistance. To this end, in the embodiment shown, the second duct means 39 2 extends between, and couples, both lubricant port means of the heat exchanger to the viscosity pump set. The duct 42, is connected to the first lubricant port means 45 and duct 42- is connected to the second lubricant port means 46 such that notwithstanding shaft rotation direction, lubricant is drawn from the bath by the leading port of one viscosity pump of the set, delivered to the core of the heat exchanger means, and then drawn from the heat exchanger means and delivered by the trailing port of the other pump of the pair to the bath. In the arrangement 30 the lubricant utilising means 43 comprises in addition to heat exchanger means 44, a forced lubrication arrangement 60 shown in relation to the journal bearing part 25 and associated with second viscosity pump set 33 of the viscosity pump means 31 . The viscosity pumps 64 and 65 which comprise the set are substantially identical to the first and second pumps 34 and 54, the stator recesses thereof being of the same length and in series at substantially the same vertical position in the stator surface 36 and facing rotor surface 35. The first port of each viscosity pump 64 and 65 is coupled by way of first duct means 66 to open into the lubricant bath. The second port of each pump is coupled by way of second duct means 67 comprising duct 68, and duct 68 2 to an annular gallery 69 which comprises a manifold providing access to the journal bearing pads 26 but is sealed from direct contact with the bath by seal 70. The bearing part 25 thus comprises a lubricant utilisation means of which the gallery 69 comprises input port means and interfaces between the bearing surface and both output port means. Thus for the aforementioned exemplary clockwise rotation of shaft 5, the viscosity pump 64 draws lubricant from the bath and delivers it at elevated pressure to the gallery 69 in which it is made available to all bearing pads 26 and forced onto the bearing surfaces thereof, from which it returns directly to the lubricant bath. Forced lubrication is therefore also provided by simple inboard viscosity pumping means with few additional modifications. If and when the shaft rotation reverses the pump 65 effects the same operation of supplying lubricant from the bath to the annular gallery 69. It will be appreciated that as the pumps 64 and 65 function irrespective of shaft rotational direction it may be undesirable for one pump to be withdrawing lubricant from the gallery that is supplied by the other pump. To this end the second duct means 67 may include one-way valve means 72 operable to prevent lubricant from being drawn from the annular gallery 69 by either pump. Conveniently, the one-way valve means comprises for each said duct 68, and 68 2 a ball 73 contained in a vertically extending section of the duct above an apertured valve seat 74 to which it is biased by gravity to close off the duct and responsive to a positive pressure differential between the pump and gallery 69 to be lifted from the seat and permit lubricant flow along the duct. Thus notwithstanding the direction of shaft rotation only one pump at a time supplies lubricant to the gallery 69. If a bearing structure is chosen which has both supply ducts coupled to the gallery at substantially the same point or by way as a common duct, the one-way valve means may be provided by a shuttle valve responsive to the highest positive pressure to shut off the other duct. The second viscosity pump set 33 thus occupies the other part of the stator surface about the shaft axis and accounts for the other 180° of stator periphery surface about axis 6 with the limited stator space available for the viscosity pump means. As an example of the benefit achieved by providing pumped cooling of lubricant by such simple viscosity pump means, it has been found that for typical vertical bearing assemblies of the form shown in Figure 1 the power envelope is such that to maintain a lubricant bath temperature of 80°C whilst supporting a thrust load of 1.7 Pa, bearing assemblies for shafts of diameters 60mm and 140mm permit maximum sustained operating speeds of 2500 rpm and 1800 rpm respectively. A vertical bearing assembly having a lubrication arrangement including heat exchanger means in accordance with the present invention and of the form shown in Figures 2 and 3 having a viscosity pump chamber recess depth of 2-3mm and axial width of about 15mm was found to permit sustainable speeds of 6500 rpm and 3000 φm for the same range of shaft diameters. This is of particularly practical importance as it permits such shafts to be rotated by rotors synchronised to the local mains frequency of 50 Hz or, for some diameters, 60 Hz. It will be appreciated that the above described embodiment may be varied in several respects without departing from the invention. The lubrication arrangement may comprise only one lubricant utilisation means, that is, either heat exchanger means or a force lubricated bearing pan but not both, thereby enabling each viscosity pump to extend further about the shaft or to operate several such pumps in parallel. The heat exchanger means insofar as it comprises lubricant utilisation means may be connected to the first viscosity pump set and the lubricant bath in a manner similar to that described for a force lubricated bearing arrangement, namely with the first lubricant pon means thereof connected to the second duct means 39 2 and the second lubricant pon means thereof connected directly to the lubricant bath. Referring to Figure 4(a) this illustrates schematically the arrangement 30 of Figures 2 and 3 in which the heat exchanger means 44 is connected in series between the first pump 34 and second pump 54. Figure 4(b) illustrates the lubricated bearing pan 25 connected by the way of second duct means 67 to both pumps 64 and 65 and by way of one-way valve means 72 and returning lubricant directly to the bath. Figure 4(c) shows such a configuration employing the heat exchanger means 44 with the second lubricant pon means 46 connected directly to the lubricant bath (terminating either above or below the surface) and the first lubricant pon means 45 connected to the second duct means 39 2 which includes one-way valve means 75 (shown as a shuttle valve) associated with each duct such that only one pump at a time circulates lubricant through the heat exchanger core dependant upon the direction of shaft rotation. Figures 4(d) and 4(e) illustrates alternative forms in which each heat exchanger means 44 has two separate cores 49 and 49, each connected to receive lubricant from a respective pump 34, 54 and return it directly to the bath. If the second duct means includes one-way valve means 73, as in Figure 4(d), and/or each second lubricant pon terminates above the surface of the lubricant bath, only one heat exchanger core and one viscosity pump is operative at any one time, whereas without such valve means and with the second lubricant pon terminating beneath the surface 27' of the lubricant bath, as in Figure 4(e), both pumps and both heat exchanger cores operate for both directions of shaft rotation, albeit that the pump drawing lubricant through the heat exchanger core may be working at low efficiency. It will be appreciated that if the shaft 5 rotates in one direction only for all or a substantial portion of its operations, it may be unnecessary for each viscosity pump set to include two viscosity pumps which respond to different rotation directions. In such an arrangement, and in accordance with the above outlined principles of flow rate efficiency, it may still be beneficial to have two circumfereπtially shon pumping chamber recesses of maximum width and for the first pon of each to be disposed as a leading port as illustrated in Figure 4(f), the pumps then working in parallel and doubling the effective chamber width and thus the flow rate. It will be appreciated that if appropriate, that is, if the pumping of lubricant to the relevant utilisation means by each set is capable of extending the power envelope beyond that required, it may be unnecessary to have lubricant pumped continuously and irrespective of shaft rotational direction. For example, if the shaft rotates in opposite directions with required frequency and duration, it may be possible for each viscosity pump set to respond effectively to one rotation direction only and idle or effectively idle during rotation in the opposite direction. As described and illustrated in all the above embodiments, the viscosity pumps are ail defined by stator surface recesses at substantially the same vertical position with respect to the lubricant bath and the recesses in series about the axis. If desired, and axial space permits, the recesses of the viscosity pump of a set may be defined vertically separated, as shown at 37, and 57, in Figure 5(a), enabling each such recess to extend circumferentially further about the axis 6. It may be possible to maintain pumping chamber means width to a required value for each pump and rely upon extra circumferential length to facilitate the inclusion of further pumps or sets of pumps, or each recess may be made longer if necessary to increase delivery pressure. For some lubrication means, such as a bearing part which may benefit from a higher supply pressure at the expense of a lower delivery rate caused by narrower recesses, such an arrangement of pumping chamber recesses may be appropriate when stator area is limited, as in the vertical bearing assembly described in detail above. Alternatively, as illustrated in Figure 5(b) the surface recesses associated with the viscosity pumps of any one set may share the same vertical position and the chambers of the viscosity pump sets, such as 32, and 33, may be separated vertically, and possibly of different widths. Although defining the viscosity pumps at the outer periphery of such a rotor flange involves maximum linear rotor speed, such grooves may be defined within the stator facing other rotor surfaces. Referring to Figure 6 the rotor surface 80 is defined by the radially extending face 15 of the collar flange and the facing stator surface 81 , in which one or more pumping chamber recesses 82 are formed, is defined instead of a reverse thrust bearing 24. Different recesses of a pump set or of different sets may be defined at different radial positions. Whereas the structure of the viscosity pump means submerged beneath the surface of the lubrication bath permits it to be disposed where rotors and stator surfaces are spaced and otherwise unused, the viscosity pumps thereof may be defined by pumping chamber recesses formed in bearing surfaces which normally are in contact with a facing rotor surface except for an intervening film of the lubricant. Such recesses may be defined, for instance as shown in Figure 7(a) at 85 within journal bearings, such as journal bearing 25 or at 86 in a journal bearing 25' formed lower in the lubricant bath about the periphery of the rotor flange 13, or possibly in the surface of a thrust bearing surface. Such viscosity pump chamber recesses may be defined extending circumferentially and bounded axially (or radially) by bearing surfaces, and/or may be defined of limited circumferential extent and separated in the circumferential direction by bearing surfaces as illustrated in plan in Figure 7(b). If such recesses 87,, 87 2 .... are separated circumferentially by bearing surfaces 88, the stator surface regions containing each recess may be spaced from the rotor and a non-bearing, or be adjacent to the rotor and comprises a bearing. As described, the surface recess of each chamber which defines a pumping chamber is substantially regular in width and depth for ready machining as are the simply curved end regions. It will be understood that each such recess may be of more complex shape to improve efficiency, as may the forms and positioning of the ports and duct means. The first and second ports to each recess may be arranged to extend substantially tangentially with respect to the rotor and blend more uniformly with respect to the base of the recess. Where two end regions of adjacent pumps are located closely, as seen in Figure 3, the ports of adjacent recesses may be oppositely inclined with respect to the plane of the drawing so as to cross each other whilst retaining a more tangential line. It will also be appreciated that the heat exchanger means may take other forms both without, and possibly within, the housing. It will be appreciated that if desired the coolant could be caused to flow through a folded or multi-tubed core by way of well defined ports forming the coolant inlet and outlet means whilst the lubricant flows over and between the faces of the core by way of such less well defined lubricant ports. Such a configuration permits use of a coolant which requires constraining within such tube work. Whereas indefinitely defined lubricant ports may be of limited practicality without the housing, such a configuration may be employed within the housing with such heat exchanger core being disposed in or above the lubricant bath and the first and second duct means arranged to extract lubricant from adjacent one face of the core and return it adjacent to the other face such that a flow of lubricant across the core is effected. Whereas the provision of cooling and/or forced lubrication is effected within a bath of lubricant provided to lubricate bearing parts which hitherto have needed submerging in the possibly provided lubricant, it may be possible by forced lubrication to operate with a reduced quantity of lubricant such that some bearing pan, such as 25 in Figure 2, is not fully immersed and relies upon lubricant being pumped thereto in operation.

Claims: CLAIMS 1. A lubrication arrangement (30), for a shaft vertical bearing assembly (10) comprising a housing (20) containing a rotor part (11 ) carried by the shaft and a stator part surrounding the rotor part, one or more bearing parts (21 , 23, 25) formed between the rotor and stator parts and a bath of lubricant (27) for the bearing parts, the arrangement being characterised by viscosity pump means (31 ) comprising at least one viscosity pump set (32, 33) and each set comprising at least a first viscosity pump (34; 64) defined by a rotor surface (35; 65; 80) of the assembly submerged in said lubricant and a facing submerged stator surface (35; 81 ) containing a first surface recess (37; 82; 85) extending part way about the rotor axis between first and second ports (38,, 38 2 ) located at opposite end regions of the recess, whereby rotation of the rotor relative to the stator surface entrains lubricant to flow in the direction of said rotation between a leading one of said first and second ports and a trailing one of said first and second ports, and, associated with each said viscosity pump set, first duct means (39,; 66) extending between said first port of each pump and an opening submerged in the lubricant bath and second duct means «39 2 ; 67) extending between said second port of each pump and lubricant utilisation means (43). 2. An arrangement as claimed in claim 1 characterised in that the lubricant utilisation means (43) comprises heat exchanger means (44) having first and second lubricant port means (45, 46) and coolant inlet and outlet means (47, 48). 3. An arrangement as claimed in claim 1 or claim 2 characterised in that the lubricant utilisation means (43) comprises a force lubricated bearing part of the bearing assembly (60). 4. An arrangement as claimed in claim 3 when dependant on claim 2 characterised in that the viscosity pump means includes at least two viscosity pump sets (32, 33), a first set (32) being associated with lubricant utilisation means comprising heat exchanger means (44) and a second set (33) being associated with lubricant utilisation means comprising a force lubricated bearing part of the bearing assembly (60). 5. An arrangement as claimed in any one of the preceding claims characterised in that at least one viscosity pump set (32) comprises also a second viscosity pump (56), defined by said submerged rotor surface (35) and part of said facing submerged stator surface (36) containing a second surface recess (57) therein extending between first and second ports (58„ 58 2 ) located at opposite end regions of the recess, whereby rotation of the rotor relative to the stator surface entrains lubricant to flow in the direction of said rotation between a leading one of said first and second ports and a trailing one of said first and second ports, and said first duct means (39,) extends between said first port of the second pump and an opening submerged in the lubricant and said second duct means (39 2 ) extends between said second port and lubricant utilisation means, said recess ports (38,, 38 2 ; 58,, 58 2 )of the pumps being disposed with respect to each other such that a particular rotational direction of the rotor defines as the leading ports of the pumps the first recess port of one pump and the second recess port of the other pump. 6. An arrangement as claimed in any one of the preceding claims characterised in that the lubricant utilisation means (43) has first lubricant port means (45) connected to the second duct means (30 2 ) of said first viscosity pump and second lubricant port means (46) connected directly to the housing bath. 7. An arrangement as claimed in claim 6 characterised in that at least one viscosity pump (54; 64, 65) of at least one set (33, 34) has associated therewith one-way valve means (72) operable to prevent flow of lubricant between the lubricant utilisation means and the viscosity pump when the direction of rotor rotation defines the second recess port as the leading port. 8. An arrangement as claimed in claim 7 characterised in that each one-way valve means is included in the second duct means (67). 9. An arrangement as claimed in claim 8 characterised in that said one-way valve means (72) comprises at least one ball (73) adapted to be contained in said duct means (67) vertically above an apertured valve seat (74) and is responsive to a positive pressure difference between the pump and lubricant utilisation means to be lifted from the seat and permit lubricant flow along the duct means. 0. An arrangement as claimed in claim 5 when dependent on claim 2 characterised in that the second duct means (39 2 ) associated with at least one viscosity pump set (32) extends between the second port (38 2 ) of the first viscosity pump (34) of the set and the first lubricant port means (45) of the heat exchanger means (44) and extends between the second port (58 2 ) of the second viscosity pump (54) of the set and the second lubricant port means (46) such that said lubricant flows to and from said heat exchanger means by way of two viscosity pumps (34; 54) of the set. 1 1. An arrangement as claimed in claim 5 or any one of claims 6 to 10 dependent on claim 5 characterised in that the surface recesses (37, 57) of each viscosity pump (34; 54) of at least one set (32) are disposed at substantially the same vertical position with respect to the lubricant, are of substantially the same length and extend in series about the rotor axis. 12. An arrangement as claimed in any one of the preceding claims characterised in that each surface recess (37, 57) extends about the rotor axis subtending an angle thereat in the range 70° to 170°. 13. An arrangement as claimed in any one of the preceding claims characterised in that each surface recess (37, 57) defining a pumping chamber is of substantially uniform width and depth between its end regions. 14. An arrangement as claimed in claim 13 characterised in that the walls of the recess extend substantially perpendicularly to the surface of the stator and the recess face. 15. An arrangement as claimed in any one of the preceding claims characterised in that for at least one viscosity pump (34) the rotor surface (35) is defined by an axially extending periphery (12) of the rotor. 16. An arrangement as claimed in any one of the preceding claims characterised in that said rotor surface (80) is defined on a radially extending thrust bearing collar (15) of the bearing assembly at or near the periphery of the collar. 17. An arrangement as claimed in any one of the preceding claims characterised in that the rotor surface (35; 80) is displaced from the stator surface including viscosity pump recess by a clearance in normal rotation, said clearance being filled with the lubricant (27) that does not provide a hydrodynamic bearing. 18. An arrangement as claimed in any one of claims 1 to 16 characterised in that the rotor surface is able to contact said stator surface including a viscosity pump recess (86) and form a bearing (25') therewith, the surfaces being separated by a hydrodynamic film of the lubricant in rotation. 19. An arrangement as claimed in any one of claims 1 to 16 characterised in that the stator surface, for each portion thereof about the axis including a viscosity pump recess (87,, 87 2 ), is displaced from the rotor surface by a clearance in normal rotation, said clearance being filled with the lubricant that does not provide a hydrodynamic bearing, and each said portion is bounded by a portion (88) able to contact the rotor surface and form a bearing therewith, the surfaces being separated by a hydrodynamic film of lubricant in rotation.

Inventors: NEW NIGEL HENRY, NEW, NIGEL, HENRY
Applicants: GLACIER METAL CO LTD, NEW NIGEL HENRY, NEW, NIGEL, HENRY, THE GLACIER METAL COMPANY LIMITED
Application year: 1995
Main classification: F16N7
IPC codes: F16N7, F16N39