ROTARY SEAL AND/OR BEARING

Abstract: For an impeller pump, the seal/bearing unit has two rotor-stator pairs of tapered sleeves arranged back-to-back. The sleeves have a spiral groove, and convey barrier-liquid from an entry-mouth in an entry-chamber to an exit-mouth in an exit-chamber. Having two sleeves gives the units mechanical stability, trust support capability, and resistance to vibrations and other abuses. The tapered sleeves may be arranged wide-narrow-wide, or narrow-wide-narrow. The sleeves may be mounted for sliding in the housing and on the shaft, or may be fixed to the housing or shaft.

Description: 1 Title: ROTARY SEAL AND/OR BEARING 2 3 This invention relates to a development of the technologies shown in patent publication 4. WO-96/35457 (RAMSAY) published 28 December 1995 (based on PCT/CA-95/00362). 5 6 7 BACKGROUND TO THE INVENTION β 9 In Fig 10 of RAMSAY, there is shown a bearing/seal system for a pump drive-shaft, based on the use 10 of a tapered sleeve. The sleeve is cut with grooves, which, by virtue of the rotation of the sleeve, 1 1 serve to pressurise a barrier liquid, and to drive the barrier liquid towards the process fluid being ι 2 pumped. As described, the tapered sleeve arrangement serves as a bearing, which is located ι 3 advantageously close to the pump impeller, and is a very efficient seal, u 15 In RAMSAY, however, as far as the bearing is concerned, only a journal bearing capability was 16 provided, in that the tapered sleeve was allowed to float axially, along the pump drive shaft The 17 axial or thrust location of the shaft was handled by a separate ball-bearing, 18 19 20 GENERAL FEATURES OF THE INVENTION 21 22 The present invention consists in a rotary-interaction apparatus. In one preferred option, the 23 apparatus is formatted as, and used as, a bearing -- either a journal bearing, or a combined journal- 24 and-thrust bearing In another preferred option, the apparatus is formatted as, and used as, a seal, for 25 example in a pump, for sealing the pump shaft against escape of process fluid. 26 27 The apparatus preferably includes a first pair of sleeves, comprising a first rotor sleeve and a first 28 stator sleeve, having surfaces which together define a first surface-to-surface interface between 29 them, the interface being of a first tapered configuration The interface-surface of the first rotor- 30 sleeve is provided with a first spiral groove, having an entry-mouth in liquid-f low-corn municatioπ with 31 an entry-chamber, for the supply of barrier-liquid into the groove The first-spiral-groove is so 32 disposed in the interface-surface of the first rotor-sleeve as to define plain lands of substantial width 33 between adjacent turns of the groove, the lands being of such dimensions and configuration as to 34 comprise, during rotation, a means for creating and supporting a hydro-dynamic film of barrier-liquid 35 between the interface-surfaces of the first pair of sleeves 36 37 The apparatus preferably also includes a second pair of sleeves, having characteristics similar to those 38 of the first pair. The exit-mouth of the groove of the second pair of sleeves discharges barrier-liquid 39 into an exit chamber. 40 4i Each of the pairs of sleeves may be understood as being derived, individually, from the RAMSAY 42 reference. 43 4 Preferably, the first and second pairs of sleeves are arranged in the apparatus with the first and 45 second tapered interfaces thereof in a co-axial, in-line, end-to-end, relative configuration. 46 1 As a seal, the two-pairs-of-sieeves apparatus is an excellent means for sealing a rotary shaft in a 2 machine, for example a pump housing. In a typical impeller-pump, the two sleeves can have an 3 aggregate groove length of several dm, and a correspondingly long aggregate interface, so the 4 pressure-differential-gradient along the length of the interfaces may be very small, ε 6 Basically, the interfaces are not subject to wear under steady running conditions, if the hydrodynamic 7 film remains stable operationally. Besides, as will be explained, any wear that might take place can 8 be compensated for by biassing. 9 10 As a seal, it is simple enough, as will be explained, to arrange for the sleeves apparatus to be sealed i i off from, or to be open to, the process fluid, as operational requirements may dictate. It is also simple 12 enough, as will be explained, for the pressures in the barrier-liquid to be monitored, to be compared 13 with process pressure, to be regulated, etc, in accordance with operational requirements. 14 15 As a seal, the apparatus is tolerant of vibrations or sudden loading abuse, and is secure, reliable, and 16 long lasting. 17 18 As a bearing, the apparatus makes an excellent bearing for supporting a rotary shaft in a housing or 19 fixed frame. As a bearing, the apparatus is especially suitable for shafts that experience only light 20 journal loads, such as the shafts of impeller-pumps when driven via a torque-only coupling As a 21 bearing, the apparatus is excellent at coping with vibrations, out-of-balance forces, and abusive 22 factors (such as cavitation, dead-heading, etc), which can arise occasionally, either suddenly and 23 shortlived, or gradually and progressively, and which can lead to a reduction in the length of service 24 life. 25 26 As a bearing, the interfaces are lubricated by the barrier-liquid, and the hydrodynamic film ensures 27 that direct contact sleeve-to-sleeve does not occur -- at least during normal operation. Occasional 28 abuse might cause the sleeves to touch, but the fact that two pairs of sleeves are present means that 29 the interface area is very large, and occasional touching is insignificant. 30 3i Even if prolonged touching did occur, perhaps because of a change in operating conditions, because 32 the interfaces are so large it is unlikely that failure would be immediate Rubbing interfaces could be 33 expected to last long enough for correction or repair to be planned for, with minimum disruption to the 34 operation of the machine. 35 36 As a bearing, the apparatus has a very reliable lubrication system Of course, if all the barrier-liquid 37 leaks away, the bearing will fail. But it may be noted that the barrier-liquid only needs to be present 38 at the entry chamber: there is no need for the barrier-liquid to be pressurised. Once the liquid enters 39 the first groove, it is picked up by the groove and forced, under gradually increasing pressure, through 40 the grooves and the interfaces, by the action of the groove itself 41 42 It may be noted that in other lubrication systems that involve the circulation of liquid lubricant, the 43 most common cause of failure is the circulation pump; in the present case, the "circulation pump" is 44 actually a built-in facet of the bearing interface. 45 46 The barrier liquid may be oil, or may contain a trace of oil, but an aim of the invention is to provide e system that can use water as the barrier liquid. In pumping generally, it is a common requirement that leakage of process fluid to atmosphere is a secondary failure mode that is to say, that the pnmary failure mode is that the barrier liquid leaks to atmosphere, or the barrier liquid leaks into the process fluid In other cases, contamination of the process fluid by the barrier-liquid is paramount. The invention allows water to be used as the barrier-liquid, and enables a number of different failure modes to be engineered into the design, as will be explained, which makes the apparatus of the invention very versatile as to its applicability One noteworthy area of application of the invention is in magnetic-drive (mag drive) pumps, of the kind in which the impeller shaft is placed inside an isolation chamber, and is driven magnetically through the walls of the chamber in mag-drive pumps, the difficulty has been to separate the process fluid from the lubricant for the impeller-shaft-beaπngs The invention permits this to be done in a mag-drive pump in a highly reliable manner, as will be explained As a bearing, the apparatus is axially long, which gives a good bearing spread, for stability during running When the apparatus is used as a seal and a bearing combined, as in an impeller-pump, there is no need for a seal (or at any rate, no need for an axially long seal) between the seal/bearing apparatus and the impeller on the end of the shaft In other words, the overhang of the impeller beyond the bearings can be effectively zero This lack of overhang also makes for excellent stability during running Also, the lack of overhang, even though the bearing is long, means the rotary-shaft can be thinner In rotary machines, the ma|or cost determinant usually is the base diameter of the shaft As will be described, it can be arranged that the interface clearance, i e the clearance that ts filled or bridged by the hydrodynamic film, can find its own dimensions, in that case, the slack or play in the bearing is effectively zero, and remains zero throughout the life of the bearing The apparatuses as described herein can be expected, under the correct operating conditions, to be unaffected by vibration, cavitation, dead heading, and sudden shock-loading Although nothing can be guaranteed 100%, the apparatus virtually eliminates the possibility of shaft run out over a long service life — even if the impeller should go out of balance in such a manner as by losing a blade DETAILED DESCRIPTION OF PREFERRED EMBODIMENTS By way of further explanation of the invention, exemplary embodiments of the invention will now be described with reference to the accompanying drawings, in which Fig 1 is a cross-sectioned side elevation of a pump, having an electric motor to the left and an impeller to the right; Fig 2 is a corresponding section of another pump; Fig 3 is a corresponding section of another pump; Fig 4 is a corresponding section of another pump; Fig 5 is a corresponding section of another pump; Fig 6 is a corresponding section of another pump, ι Fig 7 is a corresponding section of another pump; 2 Fig 8 is an exploded view of some of the components of the pump of Fig 7; 3 Fig 9 is a cross-section of another pump; 4 Fig 10 is a cross-section of the pump of Fig 9, shown in a different operating condition; 5 Fig 14 is a cross-sectioned side elevation of a pump having a motor to the right and an impeller to the 6 left; 7 Fig 15 is a corresponding section of another pump; 8 Fig 16 is a corresponding section of another pump; 9 Fig 17 is a corresponding section of another pump; io Fig 1 8 is a corresponding section of another pump; 11 Fig 1 9 is a corresponding section of another pump; 12 Fig 20 is a cross-section of a sealing/bearing sub-assembly; 13 Fig 20a is a cross-section showing the sub-assembly of Fig 20 built into a pump; 14 Fig 21 is a corresponding section of another pump; 15 Fig 22 is a cross-section of a machine, using sub-assemblies as in Fig 21 ; 16 Fig 23 is a side elevation of a conventional motor/ pump assembly; 17 Fig 24 is a corresponding elevation of an assembly; iβ Fig 25 is a cross-section of a sealing/bearing apparatus; 19 Fig 25a is a cross-section of a sealing/bearing assembly; 20 Fig 26 is a cross-section of a sealing/bearing assembly; 21 Fig 27 is a vertical cross-section of another pump; 22 Fig 28 is a cross-section of a cartridge for a pump; 23 Fig 29 is a cross-section of a pump, in which is fitted the cartridge of Fig 28; 24 Fig 30 is a cross-section of a pump fitted with another cartridge; 25 Fig 31 is a cross-section of a seal/bearing assembly, which is suitable for insertion in a pump, as a 26 cartridge or modular unit; 27 Fig 32 is a corresponding cross-section of a modified similar seal/bearing assembly; 2B Fig 33 is a cross-section of a seal/bearing assembly; 29 Fig 34 is a cross-section of an automotive crankshaft, with bearings; 30 Fig 35 is a cross-section of a portion of a single-cylinder reciprocating air compressor; 31 Fig 36 is a cross-section ol some of the components of a big-end bearing of the compressor of Fig 1 ; 32 Fig 37 is a cross-section of some of the components of a main-bearing of the compressor; 33 Fig 38a is a cross-section of a seal-bearing cartridge; 34 Fig 38b is a side elevation of the cartridge of Fig 38a; 35 Fig 38c is a cross-section of the cartridge of Fig 38a, shown in an intermediate configuration; 36 Figs 39a, 39b, 39c are cross-sections of components of the cartridge of Fig 38a; 37 Figs 40a, 0b, 0c are side-elevations of the components of Fig 38a; 38 Fig 41 is a side elevation of the Fig 38a cartridge installed in a pump; 39 Fig 42 is a cross-section of another seal-bearing cartridge, installed in a pump; 40 Figs 43a, 43b, 43c are side elevations showing the components of the cartridge of Fig 42; 4i Fig 43d is a cross-section of a component of the cartridge of Fig 42; 42 Fig 44 is a cross-section of an impeller-pump; 43 Fig 45 is a cross-section of another pump; 4 Fig 46 is a cross-section of another pump; 45 Fig 47 is a cross-section of another pump; 46 Fig 48 is a cross-section of another seal/bearing apparatus. ι The apparatuses shown in the accompanying drawings and described below are examples which 2 embody the invention. It should be noted that the scope of the invention is defined by the 3 accompanying claims, and not necessarily by specific features of exemplary embodiments. 4 5 Fig 1 herein shows a double taper arrangement, which has a thrust capability. 6 7 In Fig 1 , the housing 20 of the pump is fixed rigidly to a machine frame. A drive shaft 23 is coupled 8 to a rotary power source (e.g an electric motor). The pump has an impeller (which is not shown, but 9 is located at the right end of the shaft in Fig 1 ). The impeller is fixed rigidly to the shaft 23. 10 i i A sleeve 25 is attached to the shaft 23 by means of grub screws 27, by means of which the sleeve 12 stays locked to the shaft during rotation, and when undergoing such rotary and thrust loading as may 13 be encountered during operation. 14 15 The sleeve 25 is fixed also to a bushing 28, via a spacer 29 again in such a manner that the sleeve 16 and the bushing remain locked together, and to the shaft, during operation. 17 18 The sleeve and the bushing are tapered, and grooves 30 are cut in the tapers, as shown. The grooves 19 are arranged so that, when the shaft rotates, the grooves drive the barrier liquid entering the inlet 20 chamber 32 towards and into the outlet chamber 34, in the manner as described in RAMSAY. 21 Pressure in the outlet chamber 34, due to the pumping action of the grooves, rises to a level set by 22 the pressure regulator 36. The barrier liquid then recirculates back into the inlet chamber 32. 23 24 A mechanical seal 38 keeps the barrier liquid from entering the pumping chamber (to the right in 25 Fig 1 ) containing the process fluid. A bellows 40 provides bias for the mechanical seal. 26 27 The tapered sleeve 25 and the tapered bushing 28 reside inside a double-tapered cylinder 43. During 28 manufacturing assembly, the sleeve and bushing were screwed together onto the threaded spacer 29. 29 The spacer is dimensioned such that when the sleeve and the bushing are locked together, to the 30 spacer, there is |ust enough free-play or slack to permit the shaft to rotate freely, without binding 31 between the tapers Typically, about 1 thou (0.25 mm) of axial clearance would be appropriate. 32 33 The barrier liquid should be of sufficient viscosity that the 1 thou gap would still allow the grooves to 34 generate enough pressure. Any oily liquid would be acceptable, and would be selected to be 35 compatible with the process fluid Water will not generate a hydrodynamic film as thick as that, 36 however, and so water probably would not, therefore, be suitable as the barrier liquid in the Fig 1 37 case, with the double taper thrust bearing. 38 39 If the free-play were made so tight that a hydrodynamic film could build up in water, there would be a 40 danger that the sleeves might bind, and seize. Preferably, a free-play of 1 thou (measured axially) is 41 about the minimum that can be permitted, if binding is to be avoided. 42 43 It may be noted that in Fig 1 the sleeve, bushing, and cylinder can all be assembled together, lapped 44 together, adjusted, and set up for operation, during manufacturing assembly. The product as sold 45 comprises the assembly cartridge, which is then simply bolted into the pump housing by means of the 46 screws 45. The lip-type seal 47 may be assembled into the housing beforehand. It will be understood that of course the impeller is not present on the shaft at the time of assembly of the components into the housing. The shaft should be coupled to the electric motor by means of a coupling which does not transmit thrust loads from the motor: either that, or the motor itself may be of a structure that has no thrust capability itself, whereby the thrust capability of the double tapers serves to support the thrust loads inside the motor as well. Fig 2 shows a variation on the theme of providing opposed tapered surfaces, to serve as a double thrust bearing, i.e to avoid the need for any other provision for taking thrust loads on the shaft. In Fig 2, the two shaft tapers are machined on the one piece, i.e on the sleeve 50 The tapered cylinder is now in two components, 53A,53B, bolted together as shown A spacer 55 ensures the two components are separated by the correct distance to give the desired free play During manufacture, a spacer of the correct thickness is selected, to ensure the desired 1 thou or so of free play. Fig 3 shows another manner of arranging the double tapers Here, the intention is not to provide thrust bearing support in both directions, but rather to improve the security of the seal In Fig 3, the sleeve 57 is locked to the shaft, but the bushing 59 is free to float axially along the shaft The bushing is constrained to rotate with the sleeve, and with the shaft, by means of the drive-pins 60 The double-tapered cylinder 63 also is free to float axially, and is constrained against rotation by means of the pins 65 The end-plate 67 is retained by a circlip 69 For installation, the sleeve 57 is pressed to the right, as far into the housing as it can go, and then the grub screws are tightened. The tapered surface of the sleeve 57 is grooved, but the tapered surface of the bushing 59 is plain 7 When the pump ts running normally, the grooves build up a high pressure in the barrier liquid at the right end of the sleeve 57 This pressure drives the bushing to the right, opening a gap between the mating tapered surfaces of the bushing and the cylinder The barrier liquid also forms a hydrodynamic film between the tapered surfaces The pressurised barrier liquid escapes via the passage 70. in i which its pressure is regulated 2 3 If the mechanical seal 72 should fail, barrier liquid starts to leak into the process fluid Detectors can 4 be incorporated, to detect whether the quantity of barrier liquid is becoming less, to signal that the 5 mechanical seal is leaking 6 7 However, if the shaft should stop rotating, no pressure is then being generated in the barrier liquid 8 The process fluid, however, may retain some head pressure when the shaft stops If both tapers 9 were grooved, as in Figs 1 and 2, then, if the mechanical seal has failed, then, when the shaft stops, 0 there is a leakage path, up the grooves, whereby process fluid can leak into the barrier area, and i perhaps to the outside. If the process fluid is very toxic, this cannot be tolerated 2 3 The ungrooved surfaces of the bushing provide a seal even when the shaft has stopped rotating, and 4 even when the mechanical seal has failed. 5 β Fig 4 shows a version similar to Fig 3, in which the bushing is grooved partway, and plain the rest. 1 The plain portion serves as a seal when the rotation stops. 2 3 Also in Fig 4, the lip seal of Fig 3 is replaced by a packing ring. 4 ε Figs 5 to 1 3 show other variations. 6 7 Fig 14 shows a pump, in which the impeller is to the left, and the drive motor to the right. In Fig 14, 8 a rotor component 120, which is locked to, and rotates with, the shaft 1 23, is provided with 9 opposing grooved tapered sleeve portions 1 25, 1 27. 10 i i Two complementary stator tapered sleeves 1 29, 1 30 are provided, which are prevented from rotation 12 by being keyed, as at 1 32, to the pump housing 1 34. The stator sleeves 1 29, 1 30 are both free to 13 float axially along the shaft during operation. 14 15 During rotation of the shaft, barrier-liquid at low pressure is fed from a reservoir 1 36 into the low 16 pressure chamber 1 38, and is then pumped to the right and left, by the action of the grooves, 17 towards the two high pressure chambers 1 39, 1 0. 18 19 It will be noted that the grooves on the rotor sleeves are of opposite hand, whereby the barrier-liquid 20 is pumped in the two opposite directions even though both sleeve sections 1 25, 1 27 are rotating in 21 the same sense. Of course, the direction or sense of rotation of the shaft 1 23 must be arranged, in 22 relation to the hand of the grooves, so that pumping takes place in the desired direction. 23 24 From the two high-pressure chambers 1 39, 1 40, the barrier-liquid is held at the desired pressures by 25 means of pressure regulators 1 43, 145, and is then discharged and recirculated back to the low 26 pressure chamber 1 38. 27 28 The pressures in the two high-pressure chambers 1 39, 140 need not be the same, and in practice 29 usually will not be the same. The pressure in the left chamber 1 39 will be set a little higher than the 30 pressure of the process fluid in the impeller chamber to the left, so that the mechanical seal 1 47 31 "sees" only a small pressure differential; similarly, the pressure in the right chamber 140 will be set a 32 little higher than atmospheric pressure, which obtains to the right of the mechanical seal 148. 33 34 Each stator sleeve carries a respective seal 149, 1 50. The left- or outwards-facing area of each sleeve 35 exposed to the barrier-liquid pressure is considerably greater than the inwards-facing area of the same 36 sleeve exposed to that pressure, whereby the sleeves are urged towards each other by the barπer- 37 liquid pressure. 38 39 The housing 134 carries sealed plugs 1 52, 1 53 to isolate the assembly of sleeves, and to hold it in 40 position. Wavy springs 154 urge the sleeves axially, and into (light) contact with each other. 41 Pressure developed in the high-pressure chambers acts respectively on the two stator sleeves 42 29, 1 30. As mentioned, both stator sleeves can float axially, and the sleeves are therefore pressed 43 inwards, i.e towards each other, by the action of the pressure generated in the barrier-liquid chambers 44 139,140. The sleeves are thereby urged more tightly into the taper, whereby the clearance between 45 the rotor and the stator is reduced, the clearance being just sufficient for the maintenance of a 4β hydrodynamic film therebetween. 1 When the barrier-liquid has some lubricity and viscosity, the hydrodynamic film will settle at perhaps 1 2 or 2 thou thick, for example. When the barrier-liquid is water, which it often has to be in case the 3 barrier-liquid should leak into the process fluid, the thickness of the hydrodynamic film is minute, e.g 4 less than a tenth of a thou. The tapered sleeves must be carefully lapped to each other during 5 manufacture, preferably as matched pairs, in order to enable such clearances to be maintained, β 7 The engagement of the rotor sleeves with the stator sleeves serves as a journal bearing. The bearing 8 has virtually no slack clearance, in that the bearing sets itself to the correct or needed thickness of 9 hydrodynamic film. As a result, the bearing is massively able to eliminate vibration of the shaft during io operation of the pump. 1 1 12 The bearing also provides support for the shaft under axial or thrust forces. During operation, the left 13 sleeve 1 25 is held separated from the left plug 1 52 by the pressure in the left high-pressure chamber 1 1 39; similarly, the right sleeve 1 27 is held separated from the right plug 1 53 by the pressure in the 15 right high-pressure chamber 1 40. When a heavy net thrust force acts on the shaft, for example in the 16 direction towards the left in Fig 1 4, the whole assembly of shaft, rotor sleeves, and stator sleeves, 17 moves to the left until the left stator sleeve 1 29 abuts against the left plug 1 52. Similarly, a heavy I B force acting in the direction to the right would cause the whole assembly to move to the right until 19 the πght stator sleeve 1 30 abuts the right plug 1 53. 20 21 However, the pressure in left high-pressure chamber 1 39 will generally be greater than the pressure in 22 the right high-pressure chamber 140, as previously mentioned. Therefore, the whole assembly will be 23 biassed towards the right, and the assembly will normally reside with the right sleeve 1 30 in abutment 24 with the right plug 1 53. Depending on the exposed areas of the two sleeves (their exposed areas 25 need not be same) and on the different pressures in the two high-pressure chambers, the biassing 26 force can be large enough that the right sleeve remains in abutment with the right plug even though 27 the thrust forces on the shaft might be acting towards the left. 28 29 Of course, too strong a leftwards thrust on the shaft would cause the assembly of sleeves, and the 30 shaft, to move to the left, but, so long as the leftwards thrust forces are reasonably light, even in a 31 case where the thrust force might alternate in direction, the assembly of sleeves remains axially 32 completely stationary, i.e with effectively zero slack clearance in the axial direction 33 34 Thus, the arrangement of Fig 14 provides a highly effective and reliable seal between the pumped 35 process fluid to the left and the atmosphere to the right. Fig 1 4 provides also a bearing for the pump 36 shaft in which the journal bearing is stable and free of slack clearance under reversals of journal 37 loading, and in which the thrust bearing is also stable and free of slack clearance even under reversals 38 of thrust loading. 39 40 If, for some reason, a failure should occur, whereby the pressure of the barrier-liquid should fall off, 4i some slack clearance might then develop in the bearing, but that failure-clearance can be kept to a 42 minimum by allowing only a small free play (e.g 3 or 5 thou (0.8 to 1 .2 mm) measured axially) 43 between the two plugs 1 52, 1 53. 44 45 The Fig 14 arrangement is self contained, the barrier-liquid being isolated from the process fluid by 46 means of the mechanical seal 1 47, and from the atmosphere by the seal 148. If the right seal 148 ι should leak, that fact can be determined by inspection. If the left seal 147 should leak, that fact can 2 be determined by checking the level of liquid in the reservoir 136, in that the barrier-liquid will leak 3 into the process if the seel 147 should fail. 4 5 The pressure of the barrier-liquid in the left high-pressure chamber 1 39 is set by the pressure 6 regulators 143: the pressure of the process fluid may be measured, and the regulator 143 may be of 7 the kind that can be set so as to automatically keep the pressure in the chamber 1 39 always a few 8 psi higher than the process pressure. Then, the security of containment of the process fluid is very 9 high, which is advantageous in the case where the process fluid is toxic. 10 11 Alternatively, when the process fluid is a food-stuff, for example, the key factor is that the barπer- 12 liquid should not leak into the process fluid, rather than vice versa. In that case, the regulator 143 13 can be set to keep the barrier-liquid always a few psi lower than the process, whereby, if the seal 147 14 should start to leak, the volume of the barrier-liquid would then increase -- a fact which can be easily i s detected. 16 17 Thus, simply by detecting changes in pressure and volume, which can easily be done automatically, 18 the integrity of the arrangement of Fig 1 4 as a seal is virtually completely assured. Of course, that is 19 not to say that a failure could never occur, but it is suggested that the seal reliability is very high, as 20 that term is understood in the context of the current state of pump seal expertise. 21 22 It is noted that the mechanical seals 147, 148 themselves may be protected from excess pressure 23 differentials by automatically regulating the chamber pressure to be different from the process 24 pressure by only a small magnitude. Furthermore, it is noted that the mechanical seals are also 25 protected from mechanical vibration by the almost-immovable bearing capability of the Fig 14 26 arrangement. 27 28 It may be noted that in Fig 14 the bearing is situated very close to the impeller, and to the mechanical 29 seals; this may be contrasted with the layout of a conventional pump, wherein the bearings are 30 situated outside the shaft seals, i.e at a location that would be several inches to the right in the view 31 corresponding to Fig 14. In a conventional pump, the impeller lies at the end of a long, vibration- 32 prone overhang of the shaft. This inherent aspect of conventional pumps is the cause, so often, of 33 premature failures of mechanical seals in conventional pumps. 34 35 Fig 1 5 shows the impeller mounted on the left-end of the shaft. Fig 1 5 also shows a connection 36 between the high-pressure chambers, whereby both chambers are at the same pressure. As 37 mentioned, such equalisation would not necessarily be preferred. 38 39 Fig 16 shows the seal/bearing arrangement similar to that of Fig 14 incorporated into a mag-drive 40 pump, i.e a pump of the type in which the pump impeller is driven via a magnetic drive coupling. 41 Mag-drive pumps are used in cases where the process fluid being pumped is so toxic that dynamic (i.e 42 rubbing) seals - which cannot be relied upon not to leak - cannot be tolerated. In such a mag-drive 43 pump, the impeller and its associated shaft and bearings are enclosed inside a hermetically enclosed 44 housing. The housing is sealed using only static (i.e non-rubbing) seals, the drive being transmitted 45 through the walls of the housing by means of the magnetic drive coupling. 46 Although mag-drive pumps do adequately address the problem of seals that cannot be allowed to leak, and are mandatory in some applications for that reason, the abiding problem with a conventional mag-drive pump is that the bearings of the impeller shaft are immersed in the process fluid. Generally, process fluids of the kind that are so toxic that they cannot be allowed to leak even in small traces, often make poor lubricants. As a result, the applicability of mag-drive pumps has been restricted to those few applications where the (toxic) process liquid has enough lubricity to support conventional bearings. The bearing problem is especially difficult in that the impeller shaft is completely isolated mechanically from the motor drive shaft, and the impeller shaft bearings must therefore in themselves be capable of supporting all the thrust and journal loads that may be experienced by the impeller shaft As shown in Fig 1 6, these problems are much reduced when the seal/ bearing arrangement described in relation to Fig 1 4 is applied to a mag-drive pump. The impeller shaft 1 60 is keyed to the inner portion 1 63 of the magnetic coupling 165. The outer portion 1 69 of the coupling ts keyed to the drive shaft 1 70, which is intended to be driven by the usual electric motor (not shown) and which is supported in its own bearings 1 72 A shell 1 74 is unitary with the pump housing 1 76, and prevents the leakage of any liquid whatsoever through the coupling to the surroundings In Fig 1 6, the tapered sleeves are provided as previously described. The barrier-liquid is conveyed into and out of the chambers within the seal/ bearing via passageways 1 78, 1 79 The pressures and volumes of the barrier-liquid, and of the process fluid, if required, can be measured and regulated, and all adjustments made, from outside By this Fig 1 6 arrangement, the impeller of a mag-drive pump runs in bearings that are very firmly supported Also, the bearings remain uncontaminated by process fluid The Fig 1 6 arrangement still maintains the mag-drive characteristic of the cannot-possibly-leak integrity of containment In Fig 1 6, the magnets of the inner portion 1 63 of the coupling run in air, which may be contrasted with a conventional mag drive pump in which the inner magnets run in the process liquid Mechanically, this is an advantage, because the liquid inevitably must impose some drag due to liquid shear - in fact, considerably more drag than running the same components in air Also, transmitting the magnetic flux through air is more efficient than doing the same through a liquid In Fig 1 7, only the left stator sleeve 1 80 is axially floating. That sleeve abuts against a plug 183, which is sealed by an O-πng 1 85 to the housing 1 87. The plug 1 83 is axially floating also, and is forced rightwards by the pressure of the process fluid. The plug in tum urges the left sleeve 180 rightwards, thereby loading the taper, and enabling the development of the hydrodynamic film, as previously described. In Fig 1 7, the low pressure chamber 89 lies at the right end of the (fixed) right stator sleeve, and the high pressure chamber 1 90 lies at the left end of the (floating) left stator sleeve 180. The grooves in both stator sleeves are arranged to pump the barrier-liquid leftwards. In Fig 1 8, the floating left sleeve 1 92 is sealed to the housing, and the barrier-liquid pressure acts to ι press the floating left sleeve rightwards. If the barrier-liquid pressure is set greater than the process 2 pressure, the plug 194 abuts leftwards against the circlip 1 95. 3 4 Fig 19 shows an assembly 200 which is itself a pump. The pumped liquid output of the pump is at 5 high pressure, although this type of pump is only capable of delivering a small volumetric flow rate. 6 The purpose of the pump is to deliver high pressure at a low or static flow rate, the main benefit of 7 the pump being that no high pressure seals are required. 8 9 In Fig 1 9, both the left and right stator sleeves 203,205 are fixed and both the rotor sleeves 207,208 io can float axially. The rotor sleeves are driven by a drive tube 210, which is keyed to the shaft 212. 1 1 12 The liquid to be pumped is drawn in at the axial extremities. The liquid is pumped, by the grooves, 13 towards the centre, into the high-pressure chamber 21 4, and out through the discharge pipe 21 6. 14 15 The pressure in the chamber 214 serves to load both the two tapers. A spring 21 8 serves to bias the 16 floating sleeves into their tapers, and holds the floating sleeves in place even if the pressure in the 17 chamber 21 drops off. I B 19 The shaft 21 2 serves only to transmit torque to the pump rotor sleeves. The tapered sleeves provide 20 journal bearing capacity, but not thrust bearing capacity, and separate arrangements should be made 21 to locate the shaft axially. 22 23 Figs 20 and 20A show a sub-assembly 304, comprising a one-piece sleeve 320 and two separate 24 outer sleeves 306,308 The one-piece sleeve 320, having two tapered surfaces in which are 25 machined respective spiral grooves. The grooves are of opposite hand, as shown The direction of 26 the grooves, and the direction of rotation of the shaft 324 are such that barrier liquid entering the inlet 27 chamber 325, between the two tapered surfaces, is pumped axially by the action of the grooves to 28 left and right, towards and into the outlet chambers 327,328 29 30 From there, the liquid is collected and conveyed via conduits 340,342 to a barrier liquid control 31 station 345 At the station, the pressures in the two outlet chambers are monitored and regulated 32 (according to preset parameters!. Normally, it will be an aim of the designer that the pressure across 33 the two mechanical seals 346,347 in the sub-assembly be kept small; however, since the pressure 34 beyond the left seal 346 (the process pressure) is generally greater than the pressure beyond the right 35 seal 347 (atmospheric pressure) the pressures in the two outlet chambers 327,328 will need to be set 36 differently. 37 38 The sub-assembly 304, as shown in Fig 20, can be manufactured and sold as an integrated unit, 9 including the control station 345. The station includes a barrier liquid leakage detector (for detecting 0 an increase or a decrease in the volume of the barrier liquid), and various pressure sensors and 1 regulators, including a sensor for sensing the process pressure via passage 348. The station 345 may 2 be set to regulate the pressure in the outlet chamber 327 as a set value, or as a proportion of the 3 process pressure, or otherwise as may be deemed desirable. 4 5 It may be noted that the sub-assembly as shown in Fig 20 is very much self-contained, and ready to β use. To make the unit operational, a pump housing 350 (Fig 20A) is machined with a suitable bolt- face, and a shaft 324 is provided of a suitable diameter. The unit is simply slipped over the shaft, the housing bolted up, and the securing grub screws 352 tightened (access being had through a plugged hole in the housing). Very little is needed by way of careful attention or skilled craftsmanship for the mechanical set-up (which, by contrast, often is demanded with other types of seal/bearing systems). Fig 21 shows a similar unit, ready for installation, except that in Fig 21 the two tapered sections are grooved in the same sense. Now, the barrier liquid is fed into the inlet chamber 360 at the right and is pumped towards the high pressure outlet chamber 362 to the left. In Fig 21 , the shaft is cut away or relieved, at 364, in order that any slight burrs caused by the action of the grub screws will not tear the O-ring seals 365 in the sleeve. Also in Fig 21 , there is provided a means for adjusting the slack clearance of the bearing. A fine thread -s cut in the end of the housing 367, and a threaded plug 368 is engaged therein, and tightened to the desired clearance The plug is locked in place by means of a lock 369 Fig 22 shows two of the sealing/bearing units installed on the same shaft, with a nominal rotary machine 370 mounted therebetween It may be arranged that thrust forces on the shaft are shared between the two bearings, whereby both are locked to the shaft Alternatively, it will often be the case that thrust is supported only by the one bearing, in which case the sleeve of the other bearing is free to float axially along the shaft Rotary machines that will benefit from the as-described type of sealing/bearing system include the following, in addition to the impeller pumps referred to above Positive-displacement pumps Double-suction pumps Multi-stage pumps Reciprocating gas compressors Screw compressors Centrifugal compressors Alternators and Generators Blowers Rotors, both vertical and horizontal Rollers Thin film evaporators Marine stern glands Self lubricating shaft support bearings Mixers and agitators In addition to the above driven machines, the system may be used with such driver machines as: Diesel engines Gasoline engines Turbines: gas, steam, water The system may be used generally with pulleys and pulley shafts, where the high journal capacity is an advantage. On the other hand, the general sturdiness and shock resistance of the system make the system suitable for unsteady loading applications too. Applications which find especial advantage are those, like impeller pumps, where a shaft carries a considerable weight or mass on a large overhang, especially where the overhang is caused by the need to accommodate, in line, the separate seal and bearing which have been required hitherto. The system permits the overhang to be reduced. This can often be reflected as a reduction in the shaft diameter. Making the shaft smaller is usually very advantageous from the cost standpoint, because all the other components mounted on the shaft can be smaller. Fig 23 shows an impeller pump and a drive motor in an assembly of conventional layout. The motor 403 rests on a fixed frame 405, as does the impeller housing 407, and the bearing housing 409. In smaller installations, the bearings may be housed in an extension of the impeller housing 407, but the separate housing 409 to provide support for the bearings often is needed in large pump installations. Fig 24 shows the comparable installation using the invention. The motor 403 is the same length, and the impeller housing is the same length, but now there is no need to provide room for the shaft bearings. The journal and thrust bearing requirements of the shaft are taken by the seal/ bearing assembly located in the impeller housing 410, as described. Fig 24 requires a shorter shaft, and a shorter frame, and is cheaper and lighter. The following is a summary of some of the advantages that are aimed for in one or more of the exemplary embodiments of the invention. As compared with a pump which has a conventional stuffing-box seal, or mechanical seals, and conventional bearings, shaft overhang is eliminated as a problem . A pump impeller is a heavy item; in the conventional pump, the bearings have to be separated from the heavy impeller by at least the axial length of the stuffing box or mechanical seal, plus room for access thereto. Thus the bearings may be several inches away from the impeller. This overhang causes vibrations, especially under cavitation. etc, and these vibrations can damage the seal. As the bearings wear, slack develops, which exacerbates the vibration problem . In the invention, the seal/bearing unit may be closely adjacent to the heavy impeller The tendency for vibration is much reduced. So small is the vibration problem that the shaft may be of considerably reduced diameter, and shaft diameter is a critical aspect of economy in designs of rotary machinery. No other bearings, besides the seal/ bearing assembly as described, need be provided. The shaft overall length between the motor and the impeller may be reduced, which again eases the vibration problem. The unit may be self-compensating for wear of the tapered surfaces, both as to thrust and journal bearing support, whereby the vibration problem remains negligible throughout a long service life. The invention also permits a great reduction in the risk of the process fluid leaking to atmosphere. When the process liquid is toxic, it has been conventional to provide inboard and outboard seals, and to provide a pressurised barrier liquid, between the two seals; if the pressure of the barrier liquid is kept higher than the process pressure, any leakage of the inboard seal causes barrier liquid to leak into the process, not vice versa. But the problem then is the high pressure outboard seal to atmosphere. By contrast, the unit as described may produce a higher pressure than the process, and yet the outboard end of the unit need be at no more than atmospheric pressure The pressure is generated progressively along the length of the groove The conventional pressurised barrier also, of course, required an external source of pressure. In the units as described, the barrier liquid, upon being pumped by and through the groove, flows over the tapered surfaces and through the groove at a steady flow rate The flow is volumetrically large enough to allow a good circulation of the barrier liquid, to allow heat to be taken out of the liquid, and also dirt and debris etc The flow is unidirectional, and substantially without back flow, which means that all the liquid is circulated, and not just a by-pass proportion The flow is large enough that changes in the flow rate, liquid levels, temperatures, pressures, etc, can be detected quickly and easily, for monitoring and control purposes One of the common causes of failure in pump installations is corrosion following an ingress of moisture into the pump shaft bearings In the designs as described, the bearing is combined with the seal, and the bearing is constantly swept by the barrier liquid, whereby the opportunity for external moisture to enter the bearing, and cause corrosion, is largely non existent Fig 27 shows a version of the taper-sleeve seal/bearing assembly, which is particularly applicable to installations where the shaft is vertical Now, the weight of the impeller, the shaft, and the other rotating components, are all experienced as a thrust force on the shaft The double-taper design is, as mentioned, easily able to accommodate the thrust forces To make sure the shaft cannot move vertically, once it has been adjusted, a screw thread 450 is provided on the shaft 45 1 , and a lock nut 452 ensures that the double taper sleeve 453 cannot move relative to the shaft 451 Especially in the case where the shaft hangs vertically, the grub screws 456 might not be seen as adequate to hold the shaft against thrust forces Fig 25 shows a version of the taper-sleeve seal/bearing assembly, in which many of the components are provided as a sub-assembly or cartridge That is to say, the components shown in Fig 25 are finish manufactured and pre assembled, under factory conditions, and then shipped, as a cartridge, for installation as a repair in an already existing pump Alternatively, the cartπdqe type of construction is often very convenient also in the manufacture of new pumps In Fig 25, the two rotor sleeves, with spiral grooves, are machined onto the rotor component 420 The two stator sleeves 423,425 are separate, but are held together axially over the rotor by means of springs 427 The cartridge comprising the rotor component, the two stator sleeves, and the springs, can be simply pushed into the annular space between shaft and housing, as shown 0 rings 429 seal the stators to the housing Grub screw 430 locks the rotor component to the shaft 432 The stator sleeves are not locked axially to the housing - the apparatus shown in Fig 25 is for use when the shaft has other means (thrust bearings) for supporting the shaft against axial movement Fig 25A shows the corresponding apparatus where the stator-sleeves 435,436 are fixed into the housing, and the rotor-component 438 can slide axially along the shaft As mentioned, these units (Figs 25,25A) are not arranged to support thrust forces by themselves ι The shaft 432 includes a separate thrust bearing. This is not shown in Fig 25, but may be of 2 conventional design. Usually, at least in the case of impeller pumps, the thrust bearing function is 3 combined with a journal bearing structure. Fig 23 shows a typical arrangement of the bearings on the 4 shaft. The apparatus shown in Figs 25 or 25A serves as a very secure journal bearing, and it might s be considered that this journal bearing might "fight with" the journal bearing inside the housing 409, 6 unless the two bearings are absolutely co-axial (and remain absolutely co-axial throughout the service 7 life.) In fact, sometimes "fighting" cannot be ruled out, which is why the Fig 24 arrangement is 8 preferred (apart from the saving, in Fig 24, of space and expense). 9 10 But sometimes the Fig 23 arrangement is pre-existing and has to stay; but in such cases the overhang i i is generally so great that whipping of the overhanging shaft is a major problem: any tendency of the 12 bearings to " fight" is more than overcome by the fact that the impeller end of the shaft is now 13 prevented from whipping, and from run-out, due to impeller imbalance, etc - prevented, that is to say, 14 more or less perfectly and completely, in most cases. 15 16 Thus, the addition of an extra journal bearing from the sleeves apparatus is far more likely to be 17 beneficial than otherwise. 18 19 On the other hand, generally another thrust bearing on the shaft would not be acceptable, which is 20 why the assemblies of Figs 25 and 25A, despite having good journal capabilities, are deliberately 21 isolated from thrust forces. 22 23 In Fig 26, the thrust situation is a little different. Here, the stator 440 is fixed into the housing. The 24 tow rotor-sleeves 442,443 are each capable of sliding on the rotor-sleeve 445, but both are biassed 25 by springs that react against abutments on the sleeve Therefore, the assembly of Fig 26 is self- 26 centering axially. Sometimes, this is the best form of axial or thrust force-application for the 27 installation. 28 29 As depicted in other drawings, when there are no other thrust bearings on the shaft, sometimes the 30 best mode of controlling axial displacement and thrust forces is in the spring-one-way-solid-other-wβy 31 mode, as illustrated in Fig 3 for example. The designer may wish to cater for the fact that a 32 cavitation in the process fluid could cause an unpredictable force on the impeller (the force being 33 directed to the right in Fig 3), and arrange to resist that sudden, violent, force solidly. On the other 34 hand, the forces pushing the impeller shaft to the left due to normal running are much more 35 predictable, and less violent, and can be resisted by spring biassing. 36 37 Fig 26 is suitable when the thrust forces are light, and not subject to sudden violent variations. 38 39 As shown in Fig 29, the pump housing 460 which will receive the cartridge simply needs to be 0 machined with a straight-through bore 462. A wide variety of pump housings are found suitable for i the installation of the cartridge, when all that need be done to the housing is the machining of a 2 straight-through bore. Apart from the bore itself, the end 463 of the housing has to be faced end 3 provided with bolt holes 465, but that is simple enough: nothing else is required - not even O-ring 4 grooves, those being provided in the outer diameter of the cylinder 467 of the cartridge. 5 46 Often, a pump housing such as 460 is provided already with a port 468 for the connection of a hydraulic line, and this port can be utilised, if present, for conveying the barrier liquid from the high pressure chamber 469, as shown in Fig 29. The corresponding port for conveying the liquid to the low pressure chamber is built into the cylinder 467. In cases where the port is not present in the housing, the ports for conveying the barrier liquid in and out of the chambers may both be provided in the cylinder, for example in an arrangement as shown in Fig 30. In Figs 28-30, the outer sleeves are located against rotation by means of pegs 470 which are locked into a flange 472 of the cylinder 467. In addition to their function as ant-rotation means, the pegs 470 may be factory-adjusted for depth, in order to lock in the desired amount of axial slack or free- play into the sleeves. Fig 31 shows a seal/bearing cartridge 530, which is intended for fitment, as a pre-assembled contained unit, into the stator housing of a pump or other machine. The cartridge 530 includes a drive shaft 532, which is attached, via a coupling (not shown), to an electric motor at its left end, and to the rotary impeller of the pump at its right end. The shaft 532 is formed with an integral collar 534. Alternatively, the collar may be separate, and may be clipped into a groove cut in the shaft, and secured therein against axial and rotational movement relative to the shaft. 1 Two tapered sleeves 536,538 are keyed to the collar 534, so as to rotate with the shaft 532. The shaft and sleeves are assembled into a stator housing, as shown, which is bolted into the housing of 3 the pump, or other machine. The assembly as shown serves as a highly effective and secure seal; although no engineered seal can be regarded as absolutely safe against leaks, the seal is a zero-emission seal as that term is 7 understood in pump terminology. This is advantageous when the process fluid being pumped is toxic. In addition, the assembly as shown has a robust capability as both a journal and a thrust bearing. The electric motor should be connected via a coupling of the type that relieves the shaft 532 of any forces i due to the motor and its mountings, apart from the drive torque from the motor. The assembly 2 practically eliminates run-out and the effects of misalignment, and the short overhang of the impeller, 3 at the right end, means that the effects of any vibrations due to imbalance are negligible. 4 5 As shown in Fig 32, barrier liquid may be fed, during operation, into the entry chamber 540 at the left 6 end of the cartridge, via conduit 543, substantially at ambient pressure. The barrier liquid emerges, 7 under pressure, into the exit chamber 545, and is returned via conduit 547. 8 9 The pressure in conduit 547, and hence the pressure in the exit chamber 545 is regulated to a 0 pressure that is just a few psi higher than the pressure in the process fluid being pumped: if the i process pressure rises, so does the pressure in the exit-chamber 545. This ensures that the pressure- 2 differential across the mechanical seal 549 remains at a low magnitude. 3 4 The tapered surfaces 560,562 of the sleeves are formed each with a respective spiral groove. 5 6 Barrier liquid (e.g water) is drawn into the left end of the taper, and is driven by the spiral groove to 1 the right, through both tapers. Upon reaching the right end, the pressurised barrier liquid is collected, and returned for recirculation. The unit as shown in self-contained as to seals and bearings. The shaft is coupled at its left end to a torque drive, and no bearings are required on the shaft, to the left. The tapered sleeves provide all the thrust and journal bearing capacities that may be needed. The unit is very compact, especially in the axial direction, compared with conventional impeller pumps, and yet has a highly reliable shaft seal, and a high capacity shaft bearing 1 The apparatuses shown in the accompanying drawings and described below are examples which 2 embody the invention. It should be noted that the scope of the invention is defined by the 3 accompanying claims, and not necessarily by specific features of exemplary embodiments A connecting rod 620 is connected to a crankshaft 623 via a big-end bearing 625 , and to a piston 627 via a little-end bearing 629 7 8 Lubricant liquid is fed via internal passageways in the crankshaft from a reservoir (not shown) outside the crankshaft to the centres of the crank pins 630 The lubricant emerges through holes in the crank 1 Fitted around the crank pin is a double-tapered sleeve 632. The lubricant from the crank pin passes 3 out through corresponding holes 634 in the sleeve 632. The tapered surfaces of the sleeve are provided each with a spiral groove When the sleeve rotates, the groove drives the lubricant along 5 itself, creating pressure in the lubricant The grooves are arranged so that during forward rotation of 6 the engine the lubricant is pumped from the centre to the edges of the big-end bearing 7 8 The sleeve 632 is in two parts, which clamp together around the crank-pin 630 The complementary 9 female sleeves 636, (which are plain on their tapered surfaces) are also in two halves, clamped 0 around the male sleeve 632 The big end of the con-rod also is in two halves whereby the whole i bearing is held together around the crank-pin 2 3 The lubricant emerges from the ends of the tapered sleeves, and passes through thrust washers 638, 4 and then out 5 6 A passageway 40 leads up the con-rod to the little end The tapered sleeves there are not in two 7 halves, but are otherwise similar to the big end sleeves. 8 9 It will be understood that the pressure of the lubricant within the bearing is generated actually in and by the spiral grooves. Therefore, there is no need for the lubricant to be supplied under a high i pressure. Some slight pressure can be applied to ensure the bearing does not run dry, but basically, 2 the bearing runs on β hydrodynamic film between the tapered surfaces, and that film is maintained 3 under a high lubricant pressure, but no external source is required to supply a hydrostatic pressure. 5 Similarly, the lubricant in the passageway 640 is at zero, or only nominal, pressure. The lubricant is 6 drawn into the little end bearing by the action of the spiral groove drawing liquid into itself. 1 One benefit of the fact that the pressure is generated actually within the bearing is that the demands 2 are much reduced for the lubricant to be oily and to have high viscosity. In many cases, the lubricant 3 may be water. 4 5 In Fig 35, a single-cylinder air compressor 720 includes a piston 723 reciprocating in a cylinder 724. θ A connecting rod 25 has a big-end bearing connection 26 with the crank-pin 727 of a crankshaft 729. 7 The crankshaft has main bearing connections 730 with a housing 732. 8 9 It may be noted that although the rotating components of a compressor must be properly located in io place against axial movement, the axial (i.e thrust) forces on the components are usually not high. 11 The arrangement of mating tapered sleeves, with a spiral groove formed in the rotor sleeve, preferably 12 should only be required to support a limited thrust-support capability, but this is usually all that is 13 needed in the reciprocating machine situation. 14 15 The big-end bearing 726 (see also Fig 36) includes a pair of male sleeves 734, keyed to the crank-pin 16 727 at 71 35, and a pair of female sleeves 736, keyed to the connecting rod 725 at 737. Springs 17 738 urge the male sleeves 734 apart, and thereby urge the female sleeves 736 against the thrust i β washers 740. 19 20 The male sleeves 734 of the big-end bearing 726 are each tapered as to their outer surfaces, and are 21 each formed with a respective spiral groove on the said outer surfaces. The complementary inside 22 surfaces of the female sleeves are plain. The male and female sleeves are lapped to each other during 2 3 manufacture. During operation of the compressor, the male sleeves rotate with the crank-pin, and the 24 female sleeves rotate with the connecting rod. 25 26 The main bearings 730 (see also Fig 37) also have corresponding male and female sleeves, keyed to 27 the shaft and housing, as shown. Springs 743 keep the main bearing components biassed into 28 contact with each other. 29 30 In operation of the compressor, lubricant liquid enters the inlet chamber 747. From there, the 31 lubricant is pumped by the action of the spiral groove into the chamber 749. Mechanical seals 750 32 maintain the pressurised lubricant in the chamber 749. So long as the seals 750 substantially hold 33 the pressure, it does not matter if the seals leak somewhat, since the leaking lubricant simply drains 34 back to the sump 752. 35 36 The pressurised lubricant then passes inwards into the drilling 754 in the crankshaft, and thence to 37 the crank-pin 727. From there, the lubricant passes in similar fashion to the left main bearing, where 38 it is pressurised further, the pressure being set by means of pressure regulator 756, and is then 39 returned to the sump 752. 40 4i The lubricant also passes to the big-end sleeves, as shown. In passing through the big-end sleeves, 42 the pressure of the lubricant is again raised therein. From the big-end bearing, the lubricant passes 43 through the pressure regulator 758 and thence to the little-end bearing 760. The little-end bearing 44 may again be of the tapered sleeve type, or may be plain: the duty on the little end is much less than 45 on the main or the big-end bearings. 46 A conventional compressor has plain bearings, which have to be lubricated with high-viscosity oil. Also, conventionally, the oil has to be fed to the bearings under high pressure, which requires an oil pump. In a typical reciprocating machine, with conventional running clearances of 0 1 mm or so in the (plain) bearings, the oil had to be supplied to the bearing at a hydrostatic pressure of 50 psi or more At the running clearances in the compressor as described, the fit between the two sleeves is much smaller Although the magnitude of the pressure generated hydrodynamically by the spiral groove depends, to some extent, on the viscosity of the lubricant liquid, it usually turns out that the hydrodynamic pressure generated by the groove in the tapered sleeve is high enough that even low viscosity lubricants can be used In many cases, the lubricant can be water, or at least water mixed with a trace of oil The benefits of using water as the lubricant include the relatively easy disposability of dirty lubricant, and the safety enhancement due to the absence of droplets of oil in the compressed air, which can cause explosions As described, the sleeves have to be urge together, male to female, into intimate contact If a clearance gap should open up between the lapped surfaces, pressure would be lost Therefore, the designer should see to it that the surface remain pressed tightly together at all times The designer might arrange for the pressure generated by the groove to act on one of the sleeves, urging it into deeper contact with the other sleeve Or, the designer might arrange for a spring to urge the male and female sleeves into deeper contact Or, the designer might arrange for the generated pressure to hold the sleeves together during normal running, and for a light spring to press them together during start-up When the sleeves are supporting thrust bearing loads, the nature of the thrust bearing load should be borne in mind If the thrust force is acting in a direction to drive the sleeves apart, the means holding the sleeves together, whether that be the generated pressure or the spring (or both), must be greater than the thrust force tending to burst the sleeves apart Once the sleeves break apart, the spiral groove cannot generate pressure the designer should see to it, if the generated pressure is the means being used to hold the sleeves together, that the thrust force (including any momentary peak) is always below a threshold that is low enough that the sleeves stay together Preferably, the means used to bias the sleeves together is springs, the biassing force from which should be great enough to ensure the sleeves stay together under normal thrust conditions With springs, even if the sleeves should momentarily separate during peaks of thrust loading, whereby pressure generation is lost, the sleeves immediately come together again, and pressure generation recommences The heavier the spring force, the more thrust force the sleeves can support without breaking apart however, the heavy springs mean that in times when the thrust force is small, or acts the other way, the more force is experienced by the sleeves, and some rubbing wear may then take place, and especially during start-up However, the hydrodynamic film that, during running, becomes established between the male and female mating surfaces is very robust, and so quite heavy excesses of thrust force driving the sleeves together can be accommodated before the film breaks down The seal-bearing cartridge assembly 820 shown in Figs 38a, 38b includes a mounting sleeve 823. The mounting sleeve 823 (shown by itself in Figs 39a, 39b) is formed with a cylindrical tube portion 825, 1 and an end-flange 827. The mounting sleeve 823 is intended for mounting (see Fig 41 ) the cartridge 2 820 on the drive-shaft 824 of a rotary pump. The sleeve 823 is secured in place on the shaft, against 3 axial and rotary movement relative to the drive-shaft, by means of grub-screws 829. A groove 830 receives an O-ring, for sealing the sleeve 823 to the drive-shaft. 5 6 The cartridge 820 includes a male tapered-sleeve 832 (Figs 39b,40b), and a complementary female 7 tapered sleeve 834 (Figs 39c, 40c). The male sleeve 832 is provided, on its outward-facing conical 8 surface, with a helical, spiral groove (see Fig 40b). The purpose of the groove is as explained in the 9 said WO-95/35457 (RAMSAY). The mating conical surfaces of the tapered sleeves are formed as a 10 matched pair, lapped to each other, so as to be in intimate contact over substantially the whole axial i i length of the tapered surfaces. 12 13 The components are assembled together as shown in Fig 38c. The female tapered sleeve 834 is 14 placed on the mounting sleeve 823. A mechanical seal is provided in the female sleeve. This takes 15 the form of a sealing ring 836, made of carbon or other material suitable for rubbing-type mechanical 16 seals. The surface of the end-flange 827 against which the ring 836 rubs during operation is 17 manufactured to a high surface finish. The ring 836 is biassed by a spring 838, and sealed with an 0- 18 ring, as shown, with respect to the female sleeve. 19 20 The male tapered sleeve 832 is secured to the mounting sleeve 823 by means of grub screws 840. 21 The adjustment of the position of the male sleeve 832 is carried out in-factory, and in fact may be 22 done under conditions of tight inspection and quality control. The male sleeve is pressed to the right 23 until the conical surfaces of the two sleeves are making intimate contact, and the spring 838 is 24 compressed to the correct design load Then, the grub screws 840 are tightened 25 26 The assembled cartridge 820, having been manufactured, assembled, and set, all with in-factory 27 precision, is suitable to be packed, stored, transported, and sold The purchaser is required only to 28 ensure that the pump housing 843 (Fig 41 ) ts bored out to a suitable plain-cylindrical diameter 845, 29 and that a key-wav or the like 847 is provided, suitable for receiving the anti-rotation peg 848 30 provided in the female sleeve 834. After that, the purchaser needs only to slide the cartridge 820 3i along the drive-shaft 824, and lock the grub screws 829 to the shaft. There is no need for the 32 purchaser to secure the female sleeve to the housing' the female sleeve can be left to float axially in 33 the housing. 34 35 The purchaser does not need to make any adjustments or settings to the cartridge, prior to or during 36 assembly, or at least none that would be critical to the operation of the seal-bearing unit. The 37 factory-adjusted position of the male sleeve relative to the mounting sleeve, which is critical to the 38 operation, is not lost or affected by the assembly of the cartridge into the pump. Only the grub 39 screws 829 need be tightened, and that task requires only a modest degree of skill and attention. 40 41 As described in RAMSAY, the tapered-sleeves-with-spiral-groove arrangement provides a seal of 42 excellent performance and reliability. Barrier liquid is supplied to the intake chamber 849 (Fig 41 ) 43 leading to the start of the spiral groove, as described. The bearing capacity in the journal or radial 44 mode is very large, considering the envelope, and is inexpensive. 45 46 In the set-up as shown in Fig 41 , the cartridge cannot support thrust or axial forces. Other provisions must be made (for instance, by means of thrust bearings in the electric motor driving the pump) for supporting such thrust forces as may be present in the shaft It will be noted that since the cartridge is positioned very close to the impeller (not shown in Fig 41 , but affixed to the right end of the drive shaft) the impeller overhang is very small, which means that the rotating impeller has an excellent likelihood of running freely, without vibration Provision is made for barrier liquid to be collected in the outlet chamber 50 of the spiral groove From there, the barrier liquid, under pressure, is conveyed away, via conduits 852,854, to pressure regulator 856 Fig 42 shows a cartridge having a double-sleeve configuration of the tapered sleeves The cartridge has been installed in a pump, but again the cartridge is fully manufactured, assembled, and adjusted in-factory In Fig 42, the tapered sleeves are held in position relative to the mounting sleeve by means of an abutment piece 858 Figs 43a.43b, 43c are side elevations showing the components of the Fig 42 cartridge Fig 43d shows the mounting sleeve Fig 44 shows a rotary impeller-type pump 920 The shaft 923 is driven by a conventional electric motor, and the shaft is mounted in conventional bearings, which support the shaft against journal and thrust loads A rotor sleeve 925 is made fast to the shaft by means of grub screws 927 The sleeve has a tapered outer surface 929, in which is cut a spiral groove 930 A stator sleeve 932 is formed with a tapered internal surface 934 (which is plain, i e not grooved) The surfaces 929,934 are provided as a matched pair, lapped together during manufacture A mounting sleeve 936 is made fast with the pump housing 938, and the stator sleeve 932 is mounted for axial sliding in and relative to the mounting sleeve A spring 939 urges the sliding stator sleeve 932 in the direction to press the surfaces 929,934 together Barrier liquid (e g water) is supplied to an inlet chamber 940 via a port 943, and the spiral groove 930 is so arranged that when the motor turns the shaft 923, the entry mouth of the groove receives liquid from the chamber 940, and pumps or conveys the liquid along the groove to an outlet chamber 945 The chamber 945 is one with the main chamber 947 of the pump 920, i e the chamber in which the process fluid is being impelled During operation, the force pressing the two surfaces 929,934 together is derived, first, from the spring 939, and second, also from the pressure acting on the end face 949 of the sliding stator sleeve 932. This pressure is the pressure in the chamber 945 The chamber 945 contains the barrier liquid pumped through the spiral groove 930, but contains also the process fluid from the chamber 947. Thus the pressure in the chamber 945 is dictated by the pressure in the process chamber 947. Some process systems run at consistently high pressure, almost up to the pressure capability of the pump, while other systems run at pressures barely above ambient ι In addition to the system-to-system differences in nominal pressure, the system operating pressure 2 may vary, due to varying outside conditions downstream or upstream of the pump. 3 4 The spiral groove conveys or pumps barrier liquid into the chamber 945 so long as the pressure in the 5 chamber 945 is less than a threshold or breakdown pressure This breakdown pressure is a factor of β the speed of rotation, the cross-section and length of the groove, the viscosity of the barrier liquid, 7 etc, and it is a feature of the technology described in RAMSAY that this breakdown pressure can be β very high -- high, that is to say, in the context of impeller pumps, e.g considerably higher than any 9 pressure that can possibly be achieved in the pump chamber by the action of the impeller 10 11 Even so, however, when the process pressure is high, the force acting on the sliding sleeve, to urge 12 the surfaces 929,934 together, can become too high, in that the hydrodynamic film created between 13 the surfaces can start to break down, not necessarily over the whole interface, but in local spots, 14 whereby metal to-metal rubbing contact starts to occur This contact can serve to rub off the high 15 spots of the mating surfaces, and thus can be beneficial, but generally the contact is to be avoided 16 17 Also, in some systems, it can happen that operators might switch off the pump while there is still a i β high pressure in the process chamber As the shaft stops rotating, the pressure derived from the 19 spiral groove drops to zero, and if at that time the sliding stator sleeve 932 is being pushed into the 20 rotor sleeve 925 with undiminished force, the hydrodynamic film is likely to break down Then, metal 21 to metal contact will occur - as the shaft slows down, but before the shaft stops - and a great deal 22 of rubbing wear can take place during that time 23 24 The hydrodynamic film created between the surfaces 929,934 is quite robust, however, if the 25 surfaces are kept pushed together with a not-too-excessive force During normal running, the sliding 26 stator sleeve 932 is pushed back, against the process pressure and against the spring 939, by the 27 pressure generated by the action of the spiral groove, and the film thickness is established at an 28 equilibrium level A consequence of the sleeve 932 being slidable is that the interface can find its 29 own equilibrium clearance 30 31 If the sleeve is not pushed hard enough, however, the pressure generated in the spiral groove might 32 push the surfaces apart so strongly that a hydrodynamic film cannot bridge the clearance In that 33 case, the interface between the surfaces 929,934 would start to allow the process fluid to leak 34 through, even though the process pressure was quite small 35 36 Thus, it is desirable that when the process pressure is high, the force acting to press the surfaces 37 929,934 together should also be high. Causing the sliding sleeve to be exposed to the process 38 pressure, in the manner as shown, is a convenient way of achieving this aim, whereby the force on 39 the sleeve is proportional to the process pressure. 40 41 In pumping systems where the pressure varies during operation, and a high pressure in the process 42 chamber is encountered only rarely, the designer does not mind if the force on the sleeve goes quite 43 high when the process pressure goes high However, if the system is set to run with the process 44 pressure at the high level continually, that amount of force applied continually to the sleeve can be 45 too high, whereby excess wear would take place 46 Thus, the designer should ensure the force pressing the interface together is neither too high nor too low, since difficulties can be encountered in both states Thus, the designer desires to be able to adjust the ratio of force to pressure, i.e the level of force acting on the sliding sleeve as a proportion of the process pressure If the designer knows the process pressure is going to be continually high in a given system, he will wish to reduce the area of the sliding sleeve, i e the area of the end face 949 of the sliding sleeve that is exposed to the process pressure Reducing the area of the end face 949 means, in practical terms, reducing the outer diameter of the end face In many cases, it is desired to reduce the diameter of the end face to a dimension that is less than the overall diameter of the sliding sleeve 932 That is to say, in effect that it is desired that the outer form of the sliding sleeve be stepped The provision of the mounting sleeve 936 means that the sliding sleeve 932 can indeed be stepped The designer sets the diameter of the step such that the amount of force on the sleeve for a given process pressure is suited to the normal operating pressure in the process chamber If the normal process pressure is high he makes the diameter of the step such that the area of the end face 949 is low If the normal process pressure is low, he increases the diameter of the step, to make the area of the end face greater The sub-assembly comprised of the mounting sleeve 936 and the sliding sleeve 932 (and its mating rotor sleeve 925) can be tailored to a particular operating pressure at which the pump is to be operated The prospective user can specify his operating pressure and then be supplied with a sleeve sub-assembly unit in which the step diameter is tailored to that pressure Without the separate mounting sleeve for the sliding sleeve it would be difficult to tBilor the sliding sleeve so that only a suitable fraction of the area of the end face was exposed to the process pressure Fig 45 shows another pump system, in which a seal 952 is located between the chamber 945 and the process chamber 947 Now the pressure in the chamber 945 is set by the setting of the pressure relief valve connected to port 954, and the pressure in the chamber 945 can be higher (or lower) than the process pressure Thus, when the pump is switched off, even if the process pressure remains high, the setting of the relief valve can be allowed to drop at a rate that complements the rate of drop off of the pressure generated by the spiral groove, whereby the sleeves interface never experiences a heavy contact force In this case, it can still be advantageous to tailor the exposed area of the sliding sleeve to the prevailing operating pressure. In order to ensure a long service life for the mechanical seal 952, the pressure relief valve may be set to automatically follow the pressure in the process chamber, whereby the differential pressure felt by the seal 952 remains low or even zero Fig 46 shows a double-opposed taper-sleeve arrangement, in which each one of the two sliding taper- sleeves is provided with its own respective mounting sleeve Again, the step diameter can be tailored to give a desired pressure-force relationship The relationship need not be the same for each sleeve. 1 The structure shown in Fig 46 can serve as a self-contained replacement component or sub-assembly 2 for a pump. The pump impeller is attached to one end of the included shaft, and the other end being 3 attached to the usual drive coupling and motor No further bearings are needed for the shaft, because 4 the double-opposed taper-sleeves arrangement provides self-contained journal and thrust bearing 5 capability for the shaft 6 7 Fig 47 shows the structure of Fig 46 built into a magnetic-drive pump Mag-drive pumps are for use 8 with process fluids which are so dangerous that no leakage can be tolerated One of the problems of 9 conventional mag-drive pumps is that the impeller shaft bearings are exposed to the process fluid In io Fig 47, the impeller shaft bearings are isolated from the process fluid If the process fluid does leak i i into the bearing area, in Fig 47, perhaps the bearings will deteriorate, but the presence of the leak can 12 be detected (by monitoring the barrier liquid) and at least the process fluid remains sealed against 13 leakage into the environment 14 15 It may be noted that in a mag drive pump, the journal forces on the impeller shaft are very small, 16 assuming the impeller to be properly balanced and the thrust forces can be expected to be 17 predominantly uni directional Thus, the demands on the impeller shaft bearings of a mag drive pump 18 are minimal 19 20 Fig 48 is a cross-section of another seal/bearing apparatus that embodies the invention 21 22 When a radial or journal force is applied to the double-sleeve bearing seal apparatus, the radial force 23 gives rise, because of the taper angle, to an induced axial force It can be envisaged that this induced 24 axial force on the sleeves might cause them to tend to burst apart 25 26 Therefore, the designer must see to it that the means provided for holding the sleeves in contact (that 27 is to say, in hydrodynamic film separated contact) is strong enough to resist such separation This 28 can be rather awkward sometimes, particularly if the apparatus is subiected to sudden violent journal 29 loads If the sleeves are held in contact by springs, for example, the springs have to be very heavy, 30 which can promote excess wear, during start up or shut down for example If the sleeves are held in 31 contact by pressure in the exit chamber such pressure is not present of course during start up and 32 shut down 33 34 The sleeves may be held together by solid links that is to say the two rotor sleeves may be solidly 35 linked together as a rotor sub assembly, and the two stator-sleeves may be solidly linked together as 36 a stator sub-assembly Now, the sleeves cannot burst apart, but the problem here is with the axial 37 clearance built into the pairs of sleeves If the thrust on the apparatus is loading to the right, the first 38 pair of sleeves go in contact, and if the thrust reverses and pushes to the left, the contact must now 39 be between the second pair of sleeves So, if the clearance is too large, there will be a gap between 40 the two conditions, whereby, in a neutral-thrust situation, neither film would be established, and the 41 barrier-liquid would leak out, if the clearance is too small, both films may be compromised by being 42 constrained to be too thin 43 44 Fig 48 indicates a solution to this potential difficulty A third pair of sleeves, i.e a third rotor-sleeve 45 959 and a third stator-sleeve 960, are included, in addition to the first pair 962,963 and the second 48 pair 964,965 The two stator-sleeves 962,964 of the first and second pairs are solidly linked ι together, as are the first and second rotor-sleeves 963,965. The clearance between the rotors of the 2 first and second pairs can be set by means of the screw adjustment ring 967. In Fig 48, this 3 clearance may be large, whereby, under thrust-neutral conditions, neither the first pair nor the second 4 pair would be in proper hydrodynamic contact: the clearance condition as illustrated in Fig 48. Now, 5 the apparatus is still securely sealed, because the third pair 959,960 are still loaded together by the 6 spring 969. The third pair is isolated from thrust induced separation, and so the third pair remain 7 under spring-induced contact at all times. 8 9 In this specification, reference has been made to rotary shaft's having, and not hβving, bearings. 10 These conditions are defined as follows. 11 12 The rotary shaft is in with-thrust-bearing configuration, when: 13 the apparatus includes a fixed frame; 14 the apparatus includes a thrust-bearing, having a thrust-bearing-interface; 15 the thrust-bearing-interface is for transmitting axial forces acting on the rotary shaft to the fixed ie frame, and for mechanically constraining axial movement of the rotary shaft relative to the 17 frame in response to such forces; 18 the thrust-bearing-interface is defined by a shaft-surface which is operatively unitary with the rotary 19 shaft, in combination with a corresponding frame-surface which is operatively unitary with 20 the fixed frame; 21 at the thrust-bearing-interface, the said surfaces face each other in an axial sense, and are held apart 22 from direct contact by anti-friction means; 23 the said surfaces that define the thrust-bearing interface are co-axial with, but are physically and 24 structurally separate from, the inter-acting tapered surfaces of the sleeves 25 26 The rotary shaft is in a without-thrust-bearing configuration, when- 27 the apparatus includes a fixed frame; 28 the rotary-shaft is, in substance, free from any thrust-bearing that is physically and structurally 29 separate from, the inter-acting tapered surfaces of the sleeves, being a thrust-bearing for 30 transmitting axial forces acting on the rotary shaft to the fixed frame, and for mechanically 3i constraining axial movement of the rotary shaft relative to the frame in response to such axial 32 forces. 3

Claims: Claims CLAIM 1. Rotary-interaction apparatus, wherein: the apparatus includes a first pair of sleeves, comprising a first rotor sleeve and a first stator sleeve, having surfaces which together define a first surface-to-surface interface between them, the interface being of a first tapered configuration; the apparatus includes an entry-chamber, and a source of barrier-liquid, the entry-chamber being in liquid-flow-communication with the source of barrier-liquid; the interface-surface of the first rotor-sleeve is provided with a first spiral groove, having an entry- mouth in liquid-flow-communication with the entry-chamber, and having an exit-mouth; the first-spiral-groove is so disposed in the interface-surface of the first rotor-sleeve as to define plain lands of substantial width between adjacent turns of the groove, the lands being of such dimensions and configuration as to comprise, during rotation, a means for creating and supporting a hydro-dynamic film of barrier-liquid between the interface-surfaces of the first pair of sleeves; the apparatus includes a second pair of sleeves, comprising a second rotor-sleeve and a second stator- sleeve, having surfaces which together define a second surface-to-surface interface between them, the second interface being of a second tapered configuration; the apparatus includes an exit-chamber, and includes a means for conveying barrier-liquid present in the exit-chamber out of the exit-chamber; one of the surfaces defining the second interface is provided with a second spiral groove, having an entry-mouth, and having an exit-mouth in liquid-flow-communication with the exit-chamber; the second-spiral-groove is so disposed in the interface-surface of the second rotor-sleeve as to define plain lands of substantial width between adjacent turns of the groove, the lands being of such dimensions and configuration as to comprise, during rotation, a means for creating and supporting a hydro-dynamic film of barrier-liquid between the interface-surfaces of the second pair of sleeves; the first and second pairs of sleeves are arranged in the apparatus with the first and second tapered interfaces thereof in a co axial, in-line, end-to-end, relative configuration. CLAIM 2. Apparatus of claim 1 . wherein the two tapered interfaces each have a respective narrow- end and wide-end; and the first and second pairs of sleeves are arranged in the apparatus with the said ends of the interfaces in a wide-narrow-narrow-wide configuration. CLAIM 3. Apparatus of claim 1 , wherein the two tapered interfaces each have a respective narrow- end and wide-end; and the first and second pairs of sleeves are arranged in the apparatus with the said ends of the interfaces in a narrow-wide-wide-narrow configuration. CLAIM 4. Apparatus of claim , wherein, by their rotational-sense, the two spiral grooves comprise a means for conveying barrier-liquid in the entry-chamber in the direction towards the exit- chamber. CLAIM 5. Apparatus of claim 1 , wherein the said entry-chamber is a first-entrγ-chamber in respect of the first groove, and the apparatus includes a first-exit-chamber, the exit-mouth of the first groove being in liquid-flow- communication with the first-exit-chamber; the said exit-chamber is a second-exit-chamber in respect of the second groove, and the apparatus includes a second-entry-chamber, the entry-mouth of the second groove being in liquid-flow- communication with the second-entry-chamber. CLAIM 6. Apparatus of claim 5, wherein, by their rotational-sense, the two spiral grooves comprise e means for conveying barrier-liquid in the first-entry-chamber towards and into the first-exit- chamber, and for conveying barrier-liquid in the second-entry-chamber towards and into the second-exit-chamber. CLAIM 7. Apparatus of claim 5, wherein: the first-exit-chamber is in liquid-flow-communication with the second-entry-chamber, to form a combined intermediate-chamber; by their rotational sense, the two spiral grooves comprise a means for conveying barrier-liquid in the first-entry-chamber towards and into the intermediate-chamber, and from there towards and into the second-exit-chamber. CLAIM 8. Apparatus of claim 5, wherein: the first-entry-chamber is in liquid-flow-communication with the second-entry-chamber, to form a combined-entry-chamber; by their rotational sense, the two spiral grooves comprise a means for conveying barrier-liquid in the combined-entry-chamber towards and into the first- and second-exit-chambers. CLAIM 9. Apparatus of claim 5, wherein the first-exit-chamber is in liquid-flow-communication with the second-exit-chamber, to form a combined-exit-chamber; by their rotational sense, the two spiral grooves comprise a means for conveying barrier-liquid in the first- and second-entry-chambers towards and into the combined-exit-chamber. CLAIM 10. Apparatus of claim 1 , wherein: the apparatus includes a rotary machine; the rotary machine includes a rotary-shaft, on which the rotor-sleeves are carried; the rotary machine includes a non-rotary housing, in which the stator-sleeves are carried; and the two pairs of sleeves comprise a means for sealing the rotary-shaft with respect to the housing. CLAIM 1 1. Apparatus of claim 1 , wherein the apparatus includes a rotary machine; the rotary machine includes a rotary-shaft, on which the rotor-sleeves are carried; the rotary machine includes a non-rotary housing, in which the stator-sleeves are carried; and the two pairs of sleeves comprise a bearing means, for guiding and constraining the rotary-shaft for rotation in the housing. CLAIM 12. Apparatus of claim 1 1 , wherein the source of barrier-liquid for the entry-chamber is included on the machine, and the means for conveying barrier-liquid away from the exit chamber is included on the machine. CLAIM 13. Apparatus of claim 1 1 , wherein the machine is a pump for pumping process fluids, and the apparatus includes a fluid seal between the exit chamber and the process chamber of the pump, being the chamber in which the process fluid is contained. CLAIM 14. Apparatus of claim 1 3, wherein the combination includes a means for measuring the process pressure, being the pressure of the process fluid, and a means for regulating the pressure of the barrier-liquid in the exit chamber to a small difference above the process pressure. CLAIM 15. Apparatus of claims 10 and 1 1 , wherein the machine is a pump for pumping process fluids, and the exit-chamber is open to the process chamber of the pump, whereby the barrier-liquid conveyed from the exit chamber is conveyed into the process fluid. CLAIM 16. Apparatus of claim 1 1 , wherein 1 the rotor-sleeves are in sliding-sub-assembly configuration, in that: the apparatus includes a means for attaching the first rotor-sleeve fixedly to the second rotor- sleeve, and for constraining the two rotor-sleeves against movement relative to each other in the axial sense during operation, to form a unitary rotor-sleeve sub- assembly; the apparatus includes a means for guiding the rotor-sleeve sub-assembly for axial sliding along the rotary-shaft; the stator-sleeves are in both-fixed-to-housing configuration, in that- the apparatus includes a means for attaching both stator-sleeves fixedly to the housing, and for constraining both stator-sleeves against axial sliding relative to the housing; and the rotary machine is in the with-thrust-beaπng configuration, as defined herein CLAIM 17. Apparatus of claim 1 1 , wherein the rotor-sleeves are in both-fixed-to-shaft configuration, in which the apparatus includes a means for attaching both rotor-sleeves fixedly to the shaft, and for constraining both rotor-sleeves against axial sliding along the shaft, the stator-sleeves are in sliding-sub-assembly configuration, in which. the apparatus includes a means for attaching the first stator-sleeve fixedly to the second stator-sleeve, and for constraining the two stator-sleeves against movement relative to each other in the axial sense during operation, to form a unitary stator-sleeve sub- assembly; the apparatus includes means for guiding the stator-sleeve sub-assembly for axial sliding movement along and relative to the housing; and the rotary machine is in the with-thrust-beaπng configuration, as defined herein. CLAIM 18. Apparatus of claim 1 1 , wherein the rotor-sleeves are in both-fixed-to-shaft configuration, in that: the apparatus includes a means for attaching both rotor-sleeves fixedly to the shaft, and for constraining both rotor-sleeves against axial sliding along the shaft; the stator-sleeves are in a both-fixed-to-housing configuration, in that: the apparatus includes a means for attaching both stator-sleeves fixedly to the housing, and for constraining both stator-sleeves against axial sliding relative to the housing; and the rotary machine is in the without-thrυst-bearing configuration, as defined herein. CLAIM 19. Apparatus of claim 1 1 , wherein: the rotor-sleeves are in both-fixed-to-shaft configuration, in that: the apparatus includes a means for attaching both rotor-sleeves fixedly to the shaft, and for constraining both rotor-sleeves against axial sliding along the shaft; the stator-sleeves are in a one-fixed-one-sliding configuration, in that: the apparatus includes a means for attaching a fixed one of the stator-sleeves fixedly to the housing, and for constraining that stator-sleeve against sliding relative to the housing; the apparatus includes a means for guiding the other, slidable, stator-sleeve for axial sliding relative to the housing. CLAIM 20. Apparatus of claim 1 1 , wherein the rotor-sleeves are in one-fixed-one-sliding configuration, in that 1 the apparatus includes a means for attaching a fixed one of the rotor-sleeves fixedly to the shaft, and for constraining that rotor-sleeve against sliding along the shaft, the apparatus includes a means for guiding the other, slidable, rotor-sleeve for axial sliding along the shaft, the stator-sleeves are in a both-fixed-to-housing configuration, in that the apparatus includes a means for attaching both stator-sleeves fixedly to the housing, and for constraining both stator-sleeves against axial sliding relative to the housing. CLAIM 21. Apparatus of claim 19 or 20, wherein: one of the pairs of sleeves includes a slidable sleeve; the apparatus includes a sleeve biassing spring, which is so arranged in the apparatus as to urge the slidable sleeve towards the other sleeve of the pair CLAIM 22. Apparatus of claim 21 , wherein: the second pair of sleeves includes a slidable sleeve; the apparatus is so disposed that the slidable sleeve is exposed to pressure in the second exit- chamber; whereby the slidable sleeve is urged to slide towards the other sleeve of the second pair by pressure in the second exit-chamber. CLAIM 23. Apparatus of claim 1 1 , wherein the rotor-sleeves are in both-fixed-to-shaft configuration, in that: the apparatus includes a means for attaching both rotor-sleeves fixedly to the shaft, and for constraining both rotor-sleeves against axial sliding along the rotary-shaft; the stator-sleeves are in a both-slidable configuration, in that: the apparatus includes means for guiding the stator-sleeves each for axial sliding relative to the housing; each of the sliding stator-sleeves is in a spring-biassed configuration, in that, in respect of each sleeve: the apparatus includes a spring-abutment in the housing; the apparatus includes a stator-sleeve spπng-biassing means, being a means for applying force to the slidable stator-sleeve in a direction to increase the interface contact between that said sleeve and its complementary rotor-sleeve, and for reacting the said force against the spring-abutment in the housing. CLAIM 24. Apparatus of claim 1 1 , wherein the rotor-sleeves are in both-sliding configuration, in that: the apparatus includes a means for guiding the rotor-sleeves each for axial sliding along the shaft; each of the sliding rotor-sleeve is in spring-biassed configuration, in that, in respect of each sleeve: the apparatus includes a spring-abutment on the shaft; the apparatus includes a rotor-sleeve sprmg-biassing means, being a means for applying force to the slidable rotor-sleeve in a direction to increase the interface contact between that said sleeve and its complementary stator-sleeve, and for reacting the said force against the spring-abutment on the shaft, the stator-sleeves are in a both-fixed-to-housing configuration, in that 1 the apparatus includes a means for attaching both stator-sleeves fixedly to the housing, and for constraining both stator-sleeves against axial sliding relative to the housing. CLAIM 25. Apparatus of claim 23 or 24, wherein the sliding sleeve is in a pressure-biassed configuration, in that the slidable sleeve includes an axially-facing annular end-face-area, which is open to the exit chamber, and which is exposed to the hydraulic pressure of liquid contained in the exit chamber; whereby the end-face-area, exposed to the pressure, comprises a means for applying a force to the slidable sleeve in a direction to increase the interface contact between that said sleeve and its complementary sleeve CLAIM 26. Apparatus of claim 1 , wherein: the two tapered interfaces each have a respective narrow-end and wide-end, the first and second pairs of sleeves are arranged in the apparatus with the said ends of the interfaces in a narrow-wide-wide-narrow configuration, the two rotor-sleeves comprise a unitary rotor-sub-assembly, the two stator-sleeves are mechanically separate, and are assemblable axially around the rotor- sleeves, one from the left and one from the right, the apparatus includes a stator-holding-means, for preventing separation axially to left and right of the stator-sleeves after assembly thereof around the rotor-sleeves; whereby the two pairs of sleeves are arranged as a pre-assembled cartridge, which does not need to be separated for assembly into a housing of a rotary machine. CLAIM 27. Apparatus of claim 26, wherein the stator-holding-means comprises a mechanical stator- link connecting the two stator-sleeves, for constraining separation thereof. CLAIM 28. Apparatus of claim 27, wherein the stator-link includes a stator-sleeves-biassing-spring, which is arranged for urging the two stator-sleeves together axially around the rotor-sleeves. CLAIM 29. Apparatus of claim 26, wherein: the apparatus includes a first mechanical seal, comprising a first rotor-block, and a first stator-block which is carried by the first stator-sleeve, the first blocks being arranged in the apparatus for rubbing contact; the apparatus includes a second mechanical seal, comprising a second rotor-block, end a second stator-block which is carried by the second stator-sleeve, the second blocks being arranged in the apparatus for rubbing contact; the stator-holding-means includes first and second abutments that are unitary with the rotor-sub- assembly; the stator-holding-means includes a first spring-means, which acts between the first abutment and the first stator sleeve, and is for loading the first blocks together and for loading the first sleeves together; the stator-holding-means includes a second spring-means, which acts between the second abutment and the second stator sleeve, and is for loading the second blocks together and for loading the second sleeves together. CLAIM 30. Apparatus of claim 1 , wherein the two tapered interfaces each have a respective narrow- the first and second pairs of sleeves are arranged in the apparatus with the said ends of the interfaces in a wide-narrow-narrow-wide configuration, the two stator-sleeves comprise a unitary stator-sub-assembly; the two rotor-sleeves are mechanically separate, and are assemblable axially around the stator- sleeves, one from the left and one from the right, the apparatus includes a rotor-holding-means, for preventing separation axially to left and right of the rotor-sleeves after assembly thereof around the stator-sleeves; whereby the two pairs of sleeves are arranged as a pre-assembled cartridge, which does not need to be separated for assembly into a pump housing CLAIM 31. Apparatus of claim 30, wherein the rotor-holding-means comprises a mechanical rotor-link connecting the two rotor-sleeves, for constraining separation thereof CLAIM 32. Apparatus of claim 31 , wherein the rotor-link includes a rotor-sleeves-biassing-spπng, which is arranged for urging the two rotor-sleeves together axially around the stator-sleeves. CLAIM 33. Apparatus of claim 30, wherein 1 the apparatus includes a first mechanical seal, comprising a first rotor-block which is carried by the first rotor-sleeve, and a first stator-block, the first blocks being arranged in the apparatus for rubbing contact; the apparatus includes a second mechanical seal, comprising a second rotor-block which is carried by the second rotor-sleeve, and a second rotor-block, the second blocks being arranged in the apparatus for rubbing contact; the rotor-holding-means includes first and second abutments that are unitary with the stator-sub- βssembly; the rotor-holding-meens includes a first spring-means, which acts between the first abutment and the first rotor-sleeve, and is for loading the first blocks together and for loading the first sleeves together; the rotor-holding-means includes a second spring-means, which acts between the second abutment and the second rotor-sleeve, and is for loading the second blocks together and for loading the second sleeves together. CLAIM 34. Appβrβtus of claim 26 or 30, for use in combination with a rotary machine having a housing and a rotary shaft, the rotary-shaft being in the without-thrust-bearing configuration, as defined herein, wherein one of the stator-sleeves includes a flange, for locking the stator- sleeve fixedly to the housing, and one of the rotor-sleeves includes means for locking the rotor-sleeve fixedly to the shaft. CLAIM 35. Apparatus of claim 26, for use in combination with a rotary-machine, the machine having a housing and a rotary-shaft, the shaft being in the with-thrust-bearing configuration, as defined herein, wherein the stator sleeves, after assembly of the pre-assembled cartridge into the machine, are axially slidable in the housing. CLAIM 36. Apparatus of claim 30, for use in combination with a rotary machine, the machine having a housing and a rotary-shaft, the shaft being in the with-thrust-bearing configuration, as defined herein, wherein the rotor sleeves, after assembly of the pre-assembled cartridge into the machine, are axially slidable on the shaft CLAIM 37. Rotary-interaction apparatus, wherein: the apparatus includes a pair of sleeves, comprising a rotor-sleeve and a stator-sleeve, having surfaces which together define a surface-to-surface interface between them, the interface being of a tapered configuration; the apparatus includes an entry-chamber, and a source of barrier-liquid, the entry-chamber being in liquid-flow-communication with the source of barrier-liquid; the apparatus includes an exit-chamber, and includes a means for conveying barrier-liquid present in the exit-chamber out of the exit-chamber; the interface-surface of the rotor-sleeve is provided with a spiral groove, having an entry-mouth in liquid-flow-communication with the entry-chamber, and having an exit-mouth in liquid-flow- communication with the exit-chamber; the spiral-groove is so disposed in the interface-surface of the rotor as to define plain lands of substantial width between adjacent turns of the groove, the lands being of such dimensions and configuration as to comprise, during rotation, a means for creating and supporting a hydro-dynamic film of barrier-liquid between the interface-surfaces of the pair of sleeves; the apparatus includes a mechanical seal, comprising a rotor-block and a stator-block, the blocks being arranged in the apparatus for rubbing contact; the apparatus include a holding means, for preventing separation axially, after assembly, of the rotor - sleeve from the stator-sleeve, and of the rotor-block from the stator-block; the holding means includes an abutment that is unitary with the one of the sleeves; the rotor-holding-means includes a spring-means, which acts between the abutment and the other of the sleeves, and is for loading the blocks together and for loading the sleeves together; whereby the pair of sleeves and the rubbing blocks ere arranged as a pre-assembled cartridge, which does not need to be separated for assembly into a pump housing. CLAIM 38. Apparatus of claim 1 8, wherein: the apparatus includes a third pair of sleeves, comprising a third rotor-sleeve and a third stator-sleeve, having surfaces which together define a third surface-to-surface interface between them, the interface being of a tapered configuration; the apparatus includes a third entry-chamber, and a third exit-chamber; the interface-surface of the third rotor-sleeve is provided with a third spiral groove, having an entry- mouth in liquid-flow-communication with the entry-chamber, and having an exit-mouth in liquid-flow-communication with the exit-chamber; the third spiral-groove is so disposed in the interface-surface of the third rotor as to define plain lands of substantial width between adjacent turns of the groove, the lands being of such dimensions and configuration as to comprise, during rotation, a means for creating and supporting a hydro-dynamic film of barrier-liquid between the interface-surfaces of the third pair of sleeves; the apparatus includes a means for guiding the third rotor-sleeve and the third stator-sleeve for relative sliding, in the axial sense. CLAIM 39. Apparatus of claim 38, wherein: one of the third pair of sleeves is a slidable sleeve; the apparatus is so disposed that the slidable sleeve is exposed to pressure in the third exit-chamber; whereby the slidable sleeve is urged to slide towards the other sleeve of the third pair by pressure in the third exit-chamber. CLAIM 40. Apparatus of claim 1 , wherein the surfaces defining the interface between the first pair of sleeves is a first right cone, having a first cone-angle, and the surfaces defining the interface between the second pair of sleeves is a second right cone, having a second cone-angle, and the first and second cone-angles are not the same. CLAIM 41. Apparatus of claim 5, wherein: the first spiral-groove comprises a means for conveying barrier-liquid at a first flow-rate; the second spiral-groove comprises a means for conveying barrier-liquid at a second flow-rate; the first and second spiral-grooves are so dimensioned and arranged that the first flow-rate exceeds the second flow-rate; whereby the second entry-chamber is not starved of barrier-liquid. CLAIM 42. Apparatus of claim 5, wherein: the second pair of sleeves includes a slidable sleeve; the apparatus is so disposed that the slidable sleeve is exposed to pressure in the second exit- chamber; whereby the slidable sleeve is urged to slide towards the other sleeve of the second pair by pressure in the second exit-chamber. CLAIM 43. Apparatus of claim 42, wherein: the slidable sleeve of the second pair is so oriented that its wide end is exposed to the pressure in the exit-chamber. CLAIM 44. Apparatus of claim 32 or 33, wherein: the apparatus includes β fixed mounting-sleeve, for carrying the slidable sleeve; the slidable-sleeve is in a annular stepped-diameter relationship with the mounting sleeve; whereby the area of the slidable sleeve exposed to the pressure in the exit chamber is reduced by the annular area of the stepped diameter. CLAIM 45. Apparatus of claim 1 , wherein: the interface defined by the surfaces of the rotor- and stator-sleeves includes a relatively small plain area of the interface, being an area into which the spiral grooves do not extend, and in which both surfaces are plain, and complementary; whereby, if the surfaces should come into solid touching contact, the plain surfaces come into solid touching contact over the complete circumference of the interface, thereby forming a leak- proof seal. CLAIM 46. Apparatus of claim 1 , wherein: the apparatus includes an elastomeric flap-seal; the rotor-sleeve and the stator-sleeve that make up the second pair have respective planar end-faces facing into, and exposed to pressure in, the exit-chamber; whereby the second spiral-groove exit-mouth lies between the two end-faces; the sleeves are so dimensioned that the two end-faces lie, during operation, in substantially a common plane; the elastomeric seal includes a movable flap that overlies the two end-faces; the flap is so mounted that excess pressure in the exit-chamber urges the flap into sealing contact with both the two end-faces, over the said common plane; the flap is so mounted that excess pressure in the second spiral-groove urges the flap to move out of contact with the end-faces. CLAIM 47. Apparatus of claim 5, wherein: the apparatus includes a second source of barrier-liquid, and the apparatus includes an automatic means for communicating barrier-liquid therefrom into the second entry-chamber, responsive to the second-entry chamber being not otherwise supplied with barrier-liquid; whereby the second spiral-groove is protected from a failure of the first spiral-groove to provide barrier-liquid to the second entry chamber; the apparatus includes a pressure-relief means in the first exit-chamber; whereby the first spiral-groove can still convey barrier-liquid even if the second groove is blocked. CLAIM 48. Apparatus of claim 1 , wherein: the apparatus includes a rotary-machine, being a pump for pumping process fluid, the pump being of the remote- or indirect-drive type; the pump has an impeller for pumping the process fluid, mounted on a rotary shaft and a housing; the impeller and the rotary shaft are contained in an isolation-chamber; the isolation chamber is a chamber in the housing of the pump, whose walls are totally enclosing, having no rotary shafts passing through the walls, and having no rotary or rubbing seals in the walls; the apparatus includes a means for transmitting drive torque to the rotary shaft through the walls of the chamber indirectly, by remote-acting force; the two rotor-sleeves are carried by the rotary-shaft; and the two stator-sleeves are carried by the walls of the isolation chamber. CLAIM 49. Apparatus of claim 48, wherein the rotary-shaft on which the impeller is mounted is in the without -thrust-bearing configuration, as defined herein. CLAIM SO. Apparatus of claim 48, wherein the source of barrier-liquid is outside the isolation chamber, and the barrier-liquid is conveyed from the source into the entry-chamber, and is conveyed out from the exit-chamber through sealed ports in the walls of the isolation chamber. CLAIM 51. Apparatus of claim 48, wherein the drive is transmitted magnetically. CLAIM 52. Apparatus of claim 1 , wherein: the apparatus includes rotary machine having a crankshaft and a connecting-rod; the rotor-sleeves are carried by a crank-pin of the crankshaft, and the stator-sleeves are carried by a big-end of the connecting-rod; the crank-pin is in the with-thrust-bearing configuration, as defined herein CLAIM 53. Apparatus of claim 52, wherein the crankshaft is provided with internal passageways, which comprise means for conveying the barrier-liquid to the sleeves CLAIM 54. Apparatus of claim 1 , wherein the apparatus includes mean for collecting barrier-liquid conveyed out of the exit-chamber, and for conveying the liquid back to the entry chamber; whereby the barrier liquid is recirculated through the grooves and through the entry and exit- chambers. CLAIM 55. Apparatus of claim 1 , wherein the barrier-liquid includes water CLAIM 56. Apparatus of claim 1 , wherein the barrier-liquid includes lubricating oil CLAIM 57. Apparatus of claim 1 1 , wherein the bearing means is a journal bearing means CLAIM 58. Apparatus of claim 1 1 , wherein the bearing means is a combined journal and thrust bearing means.

Inventors: RAMSAY THOMAS W, RAMSAY, THOMAS, W.
Applicants: RAMSAY THOMAS W, RAMSAY, THOMAS, W.
Application year: 1996
Main classification: F16J15
IPC codes: F16J15