US20150192035A1 - Device with rotor, stationary part or stator, and different types of liquid pocket sliders with respective specific functions - Google Patents

Device with rotor, stationary part or stator, and different types of liquid pocket sliders with respective specific functions Download PDF

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Publication number
US20150192035A1
US20150192035A1 US14/417,182 US201314417182A US2015192035A1 US 20150192035 A1 US20150192035 A1 US 20150192035A1 US 201314417182 A US201314417182 A US 201314417182A US 2015192035 A1 US2015192035 A1 US 2015192035A1
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Prior art keywords
rotor
sliders
liquid
liquid pocket
pocket
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Pasquale Dell'aversana
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ASTRO IND Srl
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ASTRO IND Srl
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/02—Sliding-contact bearings for exclusively rotary movement for radial load only
    • F16C17/03—Sliding-contact bearings for exclusively rotary movement for radial load only with tiltably-supported segments, e.g. Michell bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
    • F01D25/16—Arrangement of bearings; Supporting or mounting bearings in casings
    • F01D25/166—Sliding contact bearing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/12—Sliding-contact bearings for exclusively rotary movement characterised by features not related to the direction of the load
    • F16C17/24—Sliding-contact bearings for exclusively rotary movement characterised by features not related to the direction of the load with devices affected by abnormal or undesired positions, e.g. for preventing overheating, for safety
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C27/00—Elastic or yielding bearings or bearing supports, for exclusively rotary movement
    • F16C27/02—Sliding-contact bearings

Definitions

  • the present invention generally regards the technical field relative to the devices comprising a rotor, a stationary part arranged around the rotor, and bearings that serve for supporting and allowing the rotation of the rotor with respect to the stationary part.
  • the present invention relates to a device of this type, in which the particular arrangement of the bearings, and their nature and conformation, allow solving a series of problems that cannot be remedied with the common ball bearings or with rollers or other bearings of the state of the art such as foil bearings.
  • the solved problems will all be discussed in the following description.
  • stator in general, it is intended a part that is fixed with respect to a machine (e.g. a turbomachine)—said stator directly surrounding the peripheral part of the rotor—while the term “rotor” indicates a rotating part integral with the rotating shaft, and whose peripheral surface directly faces the stationary part.
  • the rotating shaft constitutes the innermost rotating part of the device; of course, it is coaxial with the periphery/circumference of the rotor.
  • the device of the invention constitutes a device mounted in a turbomachine (turbine, compressor, pump, fan, etc.)
  • the stationary part corresponds with the casing
  • the rotor of the device is formed by the actual turbine and by all the rotating members integral therewith;
  • the rotor comprises the flywheel while the stationary part comprises the stator of the motor (usually electric) and the box for containing the flywheel.
  • turbomachines turbines, compressors, pumps, fans, etc.
  • a functioning that lacks vibrations is very much desired in any case in order to reduce the noise, improve the efficiency of the machine and lengthen the operative life thereof.
  • the lubrication system of the CMG spatial devices must be able to feed the correct quantity (usually very little) of lubricant in order to reliably ensure a very long functioning lifetime, to compensate for the degradation and wear of the lubricant, and to prevent the wear both of the bearings and of the shaft, or even the final seizure.
  • the bearings belonging to the prior art, used in the spatial devices for controlling the attitude are usually roller bearings or ball bearings, their rotating elements must be mechanically processed with extreme precision and hardened by special anti-wear coatings. They must not introduce any vibration that could be harmful or extremely dangerous for the correct functioning of the satellite.
  • such bearings must be capable of resisting the mechanical stresses that occur during launch, without sustaining any damage.
  • the apparatuses of the prior art often provide for the use of very hard and precise bearings, a structure characterized by rather heavy shafts as well as fairly complex lubrication systems.
  • the shafts and the bearings of the conventional apparatuses have the function of exchanging the torque with the rotor as well as the function of maintaining the amplitude of the vibrations of the rotor at the lowest possible level.
  • this involves the use of very heavy machines, with a high inertia of the shaft, with a rather poor ratio between the power developed and the mass, and consequently with a high consumption of fuel and lubricant, without mentioning the high manufacturing costs.
  • the shafts are designed and manufactured as heavy, bulky parts
  • the ball bearings are higher performing if arranged around small shafts; this signifies that the smaller the radius of the shaft, the greater its maximum functioning angular velocity (in rpm).
  • the greater the linear velocity of the bearing the greater the heat generated locally with consequent loss of viscosity of the lubricant and loss of its load capacity.
  • the requirements of the bearings may be antithetical to the requirements of the machine's overall performances, and most of the time acceptable compromises must be reached.
  • the automatic functioning (without direct human intervention) of the CMG device for controlling the attitude of the satellite implies that automatic means must be attained for detecting the start of performance deterioration, possibly due to the wear of the bearings system.
  • These means are often rather complex and are capable of detecting the start of the performance deterioration when the system has already been damaged to a certain extent. Indeed, they detect the consequences in a mechanism that has already been damaged, such as the vibrations (noise) or increased friction (by means of an increased power required to maintain the rotation velocity at a constant value).
  • the vibrations noise
  • increased friction by means of an increased power required to maintain the rotation velocity at a constant value
  • piezoelectric accelerometers are often used as detectors.
  • Such sensors/detectors are often fixed on the bearings or on the stator, but the problem then becomes that of being able to distinguish between the frequencies to be associated with different conditions. Sometimes these means are not implemented and the failure of the CMG device occurs suddenly, with dramatic consequences on the functioning of the satellite; other times, even if these automatic means are employed for detecting the incipient malfunctioning, it could be too late to enact suitable countermeasures.
  • object of the present invention is to provide a new type of structure of a generic rotating machine, and particularly of a device with flywheel for controlling the attitude of a satellite, which allows solving the above-illustrated problems of the prior art.
  • a particular type of bearing is used in an original manner, non-obvious even for a man skilled in the art; such bearing, already known in the general shape thereof, is formed by pocket sliders called liquid pocket bumpers described in the patent application WO 2004/053346 A1 by the same author.
  • the prior art also comprises other examples of bearings or pocket sliders based on a similar functioning principle, but it no case known to the author have devices similar to LPS sliders been used in the modes and for the functions described in the present invention.
  • the patent U.S. Pat. No. 4,170,389, by A. Eshel regards (see FIG.
  • a thrust bearing constituted by pockets filled with a fluid or particles of various morphology, built for tolerating, without damage, the passage of an impurity that has inserted itself between the shaft and the block of the bearing.
  • the liquid pocket bearing 87 or 89 has a toroidal shape and acts once again as an axial thrust bearing for a discoid plate 83 integral with the shaft 82 .
  • Such structures are also intended for tolerating small misalignments of the shaft, nevertheless they are not adapted to carrying out the function of stabilizing the shaft, nor for carrying out any diagnostic function or failure prevention function.
  • the prior art also comprises other hydrodynamic bearings with self-adaptive surface.
  • hydrodynamic bearings with self-adaptive surface.
  • foil bearings whose structure is indeed different from that of the pocket sliders described in WO 2004/053346. Said foil bearings have several characteristics in common with said pocket sliders (e.g.
  • a bearing constituted by a membrane containing a pressurized liquid supports a flexible foil, whose face opposite that rested on the bearing is the active surface that supports a shaft in rotation.
  • the liquid pocket carries out a function analogous to that of the so-called bump foil of the foil bearings, but the system described herein is not designed for tolerating the breakage of the foil, nor for exerting a stabilizing and self-centering action, or for predicting incipient failures.
  • liquid pocket sliders Liquid Pocket Sliders, abbreviated with LPS
  • LPS Liquid Pocket Sliders
  • LPB Liquid Pocket Bumper
  • the essential part of the invention consist of placing these special liquid pocket sliders—with a rest shape, a preload, and a rigidity that are specially designed (and possibly with special constraints for the membrane of the liquid pocket)—around the outermost periphery of the rotor, rather than placing conventional bearings (ball bearings, roller bearings, foil bearings, etc.) around the shaft of the rotor, and conferring particular characteristics to one or more liquid pocket sliders that allow them to work as “sentinel elements”, whose possible breakage does not involve any deterioration (or only a negligible deterioration) of the performances of the entire device (e.g. of a CMG, Control Moment Gyro satellite device).
  • these special liquid pocket sliders with a rest shape, a preload, and a rigidity that are specially designed (and possibly with special constraints for the membrane of the liquid pocket)—around the outermost periphery of the rotor, rather than placing conventional bearings (ball bearings, roller bearings, foil bearings, etc.) around the
  • a structure of the device like that according to the present invention would not be possible by employing conventional bearings, for the reasons indicated above. Indeed, rolling bearings would not function correctly at the extremely high linear velocities normally present on the periphery of the rotors rotating at high angular velocity; above all, even only one damaged rotating/rolling element—such as a ball or roller—would inevitably cause damage to the remaining part of the CMG device.
  • any deflection of the axis of the rotor from its nominal direction is directly opposed by the LPS sliders/bearings, which tend to be more loaded at the points towards which the rotor is moved, so as to exert a self-centering action on the rotor.
  • the deflection of the rotor axis—and hence the load overload of several elements of the LPS bearing— can never increase excessively since the reaction force that each LPS is capable of rapidly exerting increases with the compression of such LPS element.
  • the LPS element that has sustained one such small overload continues to work in hydrodynamic condition and is capable of reacting to the small deflections of the rotor without undergoing or causing an excessive increase of the friction and the heat generated on the affected surfaces.
  • FIG. 2 shows a graph of the dependence of the ratio between the misalignment “d” and the unbalance “e” for a rotating system, on the ratio between the rotation frequency (angular velocity) ⁇ 1 of the rotor and the critical frequency (of resonance) ⁇ 0 of the system; also in this case, the treatment is simplified by considering only one degree of freedom of the system;
  • FIG. 4 very schematically illustrates the liquid pocket slider ( 8 ), or LPS slider, at rest and under load, respectively (with a squeezing ⁇ against a relative slide surface 2 );
  • FIG. 5 shows various configurations, arrangements and constraints for the LPS sliders; specifically:
  • FIG. 5 b shows (always imagining the relative plan view on an area l 2 ) four spherical caps LPS lacking constraints;
  • FIG. 5 c shows (always imagining the relative plan view on an area l 2 ) a single spherical cap LPS lacking constraints and having greater size;
  • FIG. 6 shows a qualitative graph of the load (W) vs. squeezing ( ⁇ ); it is noted that the smaller the radius of curvature, the greater the reaction to the squeezing; the letters a), b) and c) refer to the respective cases of the preceding FIG. 5 ;
  • FIG. 7 shows the total force f T on the rotor (given by the sum of the centripetal reaction of the LPS bearing, shown above the abscissa, and the centrifugal force, below the abscissa, due to the unbalance “e” and to the movement or misalignment “d” of the rotor with respect to the position of the symmetry axis of the rotor in the rest state) for a system of sliders, i.e.
  • FIG. 8 is a schematic section view (orthogonal to the axis of the shaft of the rotor) of a particular structural shape of the device of the present invention, in a possible embodiment, with 4 LPS liquid pocket sliders of “sentinel cell” type (4), arranged in “strategic” positions (here at intervals of 90°) in order to obtain information regarding the distribution of the load during the rotation of the rotor ( 5 );
  • FIG. 9 is a view of an enlarged detail of FIG. 8 , which in particular shows the constraints (or containment or cage walls) ( 6 ) that must be imagined to completely surround each element LPS ( 3 ; 4 ; 10 ), and a sensor ( 7 ) associated with a LPS pocket or sentinel cell ( 4 ).
  • FIG. 10 is a view of a detail that represents the preloading cells ( 10 ) installed on the rotor ( 5 ) and provided with a generic device for adjusting the preload ( 11 ) and with a sensor ( 7 ) that can for example be a pressure sensor or a load cell.
  • d 0 is the movement of a mass M fixed to a body with elastic constant k, when a constant force F 0 is applied thereto. If a force is applied to this system, but with an amplitude F(t) that varies with a frequency ⁇ 1 between 0 and F 0 , then the movement d of the mass M will be given by the formula:
  • M mass of the rotor
  • ⁇ right arrow over ( ⁇ 1 ) ⁇ and ⁇ right arrow over ( ⁇ 0 ) ⁇ are generally different from each other since ⁇ right arrow over ( ⁇ 0 ) ⁇ depends on the characteristics of the system while ⁇ right arrow over ( ⁇ 1 ) ⁇ is set by an external actuator. Nevertheless, the entire system will oscillate with the same frequency as the centrifugal force, i.e. ⁇ 1 .
  • F c grows linearly with the movement d of the axis of the rotor and as such constitutes a destabilizing force.
  • any stabilizing force capable of opposing such centrifugal force in the machines of the prior art must be applied to the rotor by means of the bearings and the shaft, which therefore require being as rigid and balanced as possible.
  • the rotors supported by magnetic supports are an exception, which nevertheless imply an active control and much more complex embodiments.
  • the present invention instead allows designing rather light rotor systems, with simple structure and without requiring active control, at the same time relaxing certain requirements of the bearings.
  • the shaft does not have the task of generating an elastic reaction to the centrifugal force acting on the rotor; rather, most of this function is completed by the liquid pocket sliders (LPS) mounted on the periphery of the rotor and which will be described hereinbelow.
  • LPS liquid pocket sliders
  • the solution consists of a suitable preloading of the LPS sliders or bearings.
  • preloading must always be in phase with the centrifugal force, which rotates with frequency ⁇ 1 .
  • the simplest thing to do will be to obtain several special cells, with the function of preloading cells ( 10 ), directly on the rotor, with the relative slide surface obtained on the internal surface of the stator.
  • the preloading cells ( 10 ) must be fixed on the rotor ( 5 ) in a different axial or radial position in order to not interfere with the other LPS elements ( 3 ; 4 ) during rotation.
  • Each of such preloading cells will be provided with a pressure sensor like the sentinel cells 4 , as well as with preloading means, as in claim 7 , adapted to adjust the internal pressure thereof in a manner independent from all the other cells. In this manner, the preloading cells, fixed in a sufficient number on the external surface of the rotor, will rotate integrally therewith, necessarily in phase with the centrifugal force to be balanced.
  • the preload necessary for eliminating the vibrations at a given design speed ⁇ M can be obtained by employing the following procedure:
  • the preloading condition for the LPS bearings becomes:
  • ⁇ 2 M 2 ⁇ 1 4 ⁇ 4 ⁇ k ⁇ M ⁇ ( Me ) M ⁇ 1 2 +4 kMe ⁇ 1 2 , from which
  • the preload d* must be greater the greater the unbalance and the further away the work frequency from the maximum design frequency.
  • condition (4) is valid in our simplified approximation that the resultant of the forces that are opposed to the centrifugal force is of the type F LPS ⁇ k LPS d 2 . Nevertheless, it is clear that the idea underlying the invention remains valid even if the precise form of said resultant of the forces that is opposed to the centrifugal force is slightly different.
  • the distance d* ( FIG. 3 ), for which the centripetal reaction of the LPS sliders or bearings balances or compensates for the centrifugal force on the rotor, can be canceled out by suitably preloading these LPS sliders, as was shown above.
  • the minimum energy U of the system is reached when the axis of the rotor coincides with the central line of the system, also in the presence of a small unbalance or misalignment of the same rotor (see FIG. 7 , total force f T ).
  • F( ⁇ ) is the total force as a function of the movement.
  • the tilt or slope of the centripetal reaction curve of the LPS liquid pocket thrust bearing must be greater than the slope of the centrifugal force due to the unbalance/misalignment, at the point where the two absolute values compensate each other.
  • a suitable preload can only be established by taking under consideration the shape of the LPS liquid pocket sliders or bearings and their internal pressure.
  • ⁇ ⁇ ⁇ P ⁇ ⁇ ( 1 R 1 + 1 R 2 )
  • R 1 and R 2 are radii of curvature of the surface of the membrane and the tension of the membrane depends on the surface area of the membrane (this does not hold true for liquids, where the surface tension does not depend on the surface area of the liquid).
  • the load that the air film (or air channel formed between the LPS bearing and the relative slide surface) must sustain is approximately given by the product between the area of the flattened part of the membrane (contact area) and the pressure drop across the membrane.
  • the preload is determined by the tension ⁇ of the membrane, by the initial shape of the non-deformed membrane (without the load) and by the squeezing ⁇ of the LPS slider against the relative slide surface (for example the surface of the flywheel); see FIG. 4 .
  • the tension also depends on the elastic modulus E, which constitutes a property of the material.
  • E which constitutes a property of the material.
  • the graph of the load (W) can be designed as a function of the squeezing ( ⁇ ).
  • the present invention indeed, regards a self-centering rotor in which the geometric configuration of the LPS systems mounted on the periphery (edge) of said rotor is selected in a manner so as to optimize the rigidity of the LPS slider or bearing, in order to obtain a stable system at the maximum possible value of ⁇ and for a maximum of the estimated value of the unbalance “e” (such unbalance “e” must in any case be reduced to the minimum possible during the manufacturing of the rotor).
  • such geometric configuration tends to be that which maximizes the variation of the curvature of the surface of the membrane 8 of the LPS bearing, for a specific squeezing ( ⁇ ), with respect to the system not subjected to the load.
  • the present invention also includes those cases in which the condition of optimization (maximization) of the curvature of the surface for a given squeezing ( ⁇ ) with respect to the non-loaded system, is also obtained by taking under consideration possible design requirements/parameters, which could lead to a shape of the LPS membrane different from the ideal theoretical form.
  • a specific square surface with area l 2 can be filled with different LPS configurations, as the abovementioned figure shows.
  • the LPS pocket sliders of case a) are constrained by a wall ( 6 ) that prevents any movement of the membrane ( 8 ) (of the LPS slider) towards the outside, so as to oblige the membrane ( 8 ) itself to bend, with a lower radius of curvature than an analogous non-constrained membrane ( 8 ).
  • a), b) and c) refer to the cases of FIG. 5 .
  • the containment walls 6 of case a) oblige the membrane ( 8 ) to be bent more than a membrane that is not constrained.
  • said containment walls must be tangent to the surface of the membrane ( 8 ) along its fixing line, i.e. along the peripheral line where the membrane ( 8 ) “comes out” from the rigid structure to which it is fixed.
  • such rigid structure is movable so to be able to move the slider from the rest condition ( FIG. 4 , left side) towards the preloading condition against the relative slide surface ( FIG. 4 , right side), or the preloading could be obtained by increasing the internal pressure of the liquid (“swelling” or injecting liquid) inside the pocket of the slider.
  • LPS liquid pocket sliders
  • FIGS. 8 and 9 an embodiment is shown in which the liquid pocket sliders (LPS sliders) ( 3 ) are mounted on the stator ( 2 ), while the external (cylindrical) surface of the rotor ( 5 ) constitutes the relative slide surface, i.e. the surface which faces directly on the internal (cylindrical) surface for mounting the LPS bearings on the stator ( 2 ).
  • LPS sliders liquid pocket sliders
  • the numbers ( 4 ) and ( 10 ) indicate liquid pocket sliders (LPS sliders or bearings), but that these (even if they substantially have many characteristics in common with the LPS sliders indicated with the reference number ( 3 ) in this specific embodiment of the invention) constitute the so-called “sentinel cells” ( 4 ) or the so-called preloading cells ( 10 ), whose function will be clarified hereinbelow in a thorough manner.
  • the preloading means of the liquid pocket sliders ( 3 ; 4 ) advantageously comprise a movable structure (for the sake of simplicity not shown in FIG. 8 and FIG. 9 ), on which the LPS slider is directly mounted, as well as mechanical actuators (e.g. a small piston, also not represented in FIGS. 8 and 9 ) in order to press the relative LPS slider ( 3 ; 4 ; 10 ), causing the squeezing ( 6 ) thereof against the relative slide surface (or according to the modes stated above, and as specified in claim 7 ).
  • a movable structure for the sake of simplicity not shown in FIG. 8 and FIG. 9
  • mechanical actuators e.g. a small piston, also not represented in FIGS. 8 and 9
  • a certain number of liquid pocket sliders, pressurized independently from each other, arranged around a rotor in the above-described manner, are capable of obtaining a failure-tolerant system of LPS sliders. Damage caused to the single balls of a conventional ball bearing, due to a failure of the check means or to the wear or degradation of the lubricant, could cause a rapid deterioration of the performances and in the end even a series of functioning irregularities of the entire mechanism. Damage or even breakage of a single, independently-pressurized liquid pocket of a LPS bearing, would however lead to the immediate depressurization of the membrane ( 8 ) or ( 9 ) that is broken, which therefore would no longer sustain the load, but would no longer produce damage to the rotor ( 5 ).
  • LPS sliders can be specially obtained in a manner so as to be weaker than the other LPS sliders, which we will call “ordinary LPS sliders”; the weaker LPS sliders will be called “sentinel cells”.
  • Such sentinel cells can be obtained in a manner so as to have limited size, in order to support a total load percentage that is as low as possible, reinforcing the concept according to which the failure of a single sentinel cell does not affect the overall performance.
  • a sentinel cell functions as a fuse of an electrical apparatus, in the sense that the breakage of the sentinel cell indicates that an operating limit has been exceeded, given that the sentinel cell is specially made to be the weakest component of the system.
  • LPS sentinel cells do not serve to protect the remaining part of the system from damage: they represent diagnostic means rather than protection means.
  • the sentinel cells 4 work in parallel with the other ordinary sliders ( 3 ), while an electrical fuse works in series.
  • the LPS sentinel cells ( 4 ) can also sustain a breakage due to a process of progressive degradation due to the prolonged functioning, rather than following an unsupportable/unsustainable variation of their operative conditions.
  • An opportune signaling of the incipient deterioration of a LPS bearing provided with sentinel cells is easily obtainable by monitoring the LPS sentinel cells, so as to readily detect their possible irregularities.
  • Such monitoring can be implemented by means of sensors ( 7 ), as indicated in FIG. 9 .
  • the radial load on the LPS elements does not have to be distributed in a uniform manner all around the flywheel. Therefore, several LPS elements could be more stressed than others.
  • the sentinel cells will be positioned in key, i.e. strategic positions, in order to monitor the operating conditions at several points of the system.
  • the system would have the further characteristic of being capable of detecting irregularities or non-nominal functioning conditions.
  • a pressure sensor in each sentinel cell could monitor the relative internal pressure, which in turn is correlated with the local conditions of the load. This would constitute an element/important piece of information, since a non-uniform load distribution around the flywheel could cause a premature breakage of several liquid pocket sliders (LPS sliders) of ordinary type (i.e. in addition to the breakage of a sentinel cell).
  • LPS sliders liquid pocket sliders
  • the function of the sentinel cells would not be limited to supplying information only of “yes/no” type: they could also supply a more complete view of the general functioning conditions of the device, making possible the integration of their information with other data/information elements coming from other sources.
  • the present invention has various aspects and advantages that distinguish it from the prior art. While a flywheel of the prior art was supported by ball bearings or roller bearings of conventional type around the rotation shaft thereof, according to the present invention the same flywheel is automatically supported and centered by a plurality of independent LPS bearings, in the sense that the breakage of one of these causes at most the outflow of a small quantity of liquid which is dispersed in the surrounding environment without interfering with the functioning of the other LPS liquid pockets. The heat generated in the sliders/bearings, in addition to being lower, is transferred and quickly dispersed through the liquid contained in the pockets.
  • the breakage of a sentinel cell (which also carries out the function of bearing) signals the possibility of a failure to the system in a specific subsequent period, and hence the sentinel cells act as diagnostic means (in order to then take possible countermeasures) which do not interfere with the functionality of the system.
  • the monitoring of suitable sensors associated with the sentinel cells also in the absence of the breakage thereof, can supply useful information on the overall functioning, indicating for example irregular distributions of load between the various LPS elements.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Magnetic Bearings And Hydrostatic Bearings (AREA)
  • Sliding-Contact Bearings (AREA)
US14/417,182 2012-07-24 2013-07-18 Device with rotor, stationary part or stator, and different types of liquid pocket sliders with respective specific functions Abandoned US20150192035A1 (en)

Applications Claiming Priority (3)

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IT000355A ITRM20120355A1 (it) 2012-07-24 2012-07-24 Dispositivo con rotore, parte stazionaria o statore, e diversi tipi di pattini di spinta a sacca liquida con rispettive funzioni specifiche.
ITRM2012A000355 2012-07-24
PCT/IB2013/055905 WO2014016739A1 (en) 2012-07-24 2013-07-18 Device with rotor, stationary part or stator, and different types of liquid pocket sliders with respective specific functions

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EP (1) EP2877752A1 (ru)
CN (1) CN104541076A (ru)
EA (1) EA201590253A1 (ru)
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CN111781943A (zh) * 2020-07-20 2020-10-16 北京控制工程研究所 一种航天器分布式载荷位姿三超控制方法

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CN114412917B (zh) * 2022-01-19 2024-04-02 山东朝阳轴承有限公司 一种轮毂轴承
CN117231702B (zh) * 2023-11-15 2024-03-12 河南兰兴电力机械有限公司 一种液压式牵引传动装置

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