| JPH10184678A | 1998-07-14 | |||
| CN2052840U | 1990-02-14 | |||
| DE102005027503A1 | 2006-12-28 | |||
| US1570056A | 1926-01-19 | |||
| US1699233A | 1929-01-15 | |||
| RU100156U1 | 2010-12-10 | |||
| US3655251A | 1972-04-11 | |||
| US1443115A | 1923-01-23 |
| A Multi-tiered Lattice Packing of individual Rolling Load Bearing Elements, spatially constrained within a bearing, wherein any load, exerted upon a single Roiling Load Bearing Element (or plurality thereof) within said Lattice Packing, is simultaneously redistributed to all remaining Roiling Load Bearing Elements within the Lattice Packing; said redistribution of load by said multi- tiered packing mitigating the damaging effects of shock overloading on any single bearing component. The Multi-tiered Lattice Packing of Claim 1 wherein a partial intrusion of Rolling Load Bearing Elements from a given tier into the interstitial spacings of an adjacent tier, maintains a structured periodic separation of Roiling Load Bearing Elements of said adjacent tier; and reciprocally, the partial intrusion of Roiling Load Bearing Elements of an adjacent tier into the interstitial spacings of said given tier maintains a structured separation of Rolling Load Bearing Elements of said given tier A Means of Resilient Constraint that, when positioned in static or dynamic contact with Rolling Load Bearing Elements of the Multi- tiered Lattice Packing of Claim 1 , provides for the absorption of static and dynamic loads transferred to said Means of Resilient Constraint by individual and multiple Rolling Load Bearing Elements within the Multi-tiered Lattice Packing; said Means of Resilient Constraint reciprocally returning said static or dynamic loads to the Multi-tiered Lattice Packing of Claim 1 upon cessation of said static or dynamic loads . A Mechanical Bearing Device wherein a supportive bearing member bears the weight, inertia! mass and relative movement of a loaded bearing member through multiple intermediate tiers of Rol!ing Load Bearing Elements, thus enab!ing anti-frictionai rol!ing movement of a loaded bearing member relative to a supportive bearing member. |
Technical Field
Despite its evident departures from the prior art, the current disclosure may be said to find its primary subject matter within the technical field of Antifriction Bearings, wherein a supportive bearing member bears the weight of a loaded bearing member through a single intermediate tier of one or more complements of Rolling Load Bearing Elements, thus allowing the loaded bearing member to move in roiling, anti-frictional (non-sliding) contact with relation to the supportive bearing member.
Background Art
Drawing upon a mu!tidisciplinary base, including such diverse fields as fluid mechanics, crystallography, spherical packing, rheology and mechanical engineering, the current disclosure seeks to address, in a new light, many of the same obstacles addressed by earlier generations. As such, the current disclosure would be incomplete without grateful recognition of previous work and observations by such luminaries as Leonardo da Vinci (c.1500 A.D.), Angostino Ramelli (c.1588 A.D.), Johannes Kepler (c.181 1 A.D.), Blaise Pascal (c, 1640 A.D.), John Harrison (c.1760 A.D.), Phillip Vaughan (c. 1794 A.D.), Jules Suriray (c.1869 A.D.), Fredrich Fischer (c.1883 A.D.), Sven Wingquist (c.1907 A.D.), Henry Timken (c.1898 A.D.), Erich Franke (c.1934 A.D.), Richard Stribeck (c. 1900 AD ), Bud Wisecarver (c. 1972 A.D.), Robert Gould (c. 1972) and the unknown inventor (c. 40 AD) of a 2000 year old wooden bearing recovered from a sunken Roman ship by underwater archaeologists at Lake Nemi, Italy in 1929.
Despite whatever attributes the current disclosure may share with a 2000 year old background of Antifriction Bearing development, two years of intensive review of publicly available sources by the inventor
l has yet to identify any prior art directly relevant to the claims of the present invention.
Although an ultimate determination of utility, uniqueness, and non- obvious nature is rightfully delegated to the realm of professional patent examiners, the general tendency of the claims of this disclosure to fall within "not-otherwise-classified" categories within current IPC, USPC, or CPC patent classification schemes, may indicate the uncharted nature of the technical field into which the current disclosure has ventured.
Disclosure of Invention
Technical Problems
A primary challenge to which the current invention is drawn regards the task of augmenting the native shock absorptive capacity of Antifriction Bearings, apart from any reliance on external mechanisms. When one or more complements of Rolling Load Bearing Elements are dynamically constrained, as a single intermediate tier, between the collective non- resilient raceways of a loaded bearing member and supportive bearing member, said Rolling Load Bearing Elements and the surfaces with which they come into rolling contact, invariably experience predictable rates of deformation and/or eventual failure when subjected to momentary and/or dynamic loads in excess of their elastic limits. in an attempt to counteract such deformation, and generally extend the service life of frictionless bearing systems, prior art has generally, though not exclusively, focused on one or more of the following work-arounds:
1. the enlargement of Roiling Load Bearing Elements to distribute loads over a larger volume of material, however with a corresponding increase in weight, volumetric displacement and operational energy requirements;
2. the hardening of raceway or Rolling Load Bearing Element surfaces to make them more resistant to deformation and failure -thus mitigating the frequency of said deformation and failure, but bringing into play the associated complexity and increased costs of their manufacture;
3. the reliance upon some external means of shock absorption that is non integral to the Antifriction Bearing itself, (i.e. external suspensions, resilient bushings or linear flexure technologies, etc., or;
4. the outright abandonment of antifriction roiling element bearings in favor of sliding contact or non-contact bearing technologies.
A secondary challenge to which this invention is drawn relates to the task of maintaining separation of Rolling Load Bearing Elements, in an anti- frictional manner, when they collectively share the same curvilinear path around an axis of rotation on a common raceway. As a complement of roiling elements collectively moves around the circumference of an antifriction rotary bearing raceway, the leading face of any given Roiling Load Bearing Element moves counter-directional to the trailing face of the Rolling Load Bearing Element which immediately proceeds it. In an attempt to overcome the inherent heat and friction which would inevitably result from the contact of said leading and trailing faces, prior art has generally, though not exclusively, focused on one of the two following Roiling Load Bearing Element separation schemes:
1 . the use of a separator cage or retainer assembly to provide a relatively secure means of separation between individual rolling elements, but which, non-the-less, relies on friction producing sliding contact between said separator cage and Rolling Load Bearing Elements to accomplish said separation;
2. the insertion of discrete non-load-bearing elements which -while sometimes capable of rotating in synchronous roiling contact with both leading and trailing faces of adjacent Roiling Load Bearing Elements are, none-the-iess, obliged to operate counter-rotationaiiy and in sliding contact with respect to a bearing raceway, when operating under said conditions.
Technical Solution
To meet or exceed the aforementioned challenges, the current disclosure introduces new and useful improvements to the utility of Antifriction Bearings that, until the present have remained unobvious to the technical field.
Advantageous Effects
When incorporated into the design of an Antifriction Bearing and fabricated of materials appropriate to the service environment for which a given bearing is intended, the innovations herein claimed will, among other outcomes, dynamically mitigate, if not eliminate, the need for an external / auxiliary means of shock absorption or vibration dampening while furthermore eliminating the need for separator cages or discreet separator elements.
Said improvements will significantly increase the operational efficiency of rolling bearing technologies, provide lower life cycle cost alternatives to what is currently available in the field, and ultimately reduce the adverse environmental impact of numerous applications wherein such improvements are implemented.
Brief Description of Drawings
Drawing Component Identification Conventions
Figures 01 -14 are intended to convey the forms, function, and utility of new art primarily (though not exclusively) applicable to antifriction ball and roller bearings.
Given the design requirements unique to each subclass, it is highly predictable that the specific form of a given innovative element may vary, whereas its function and utility remain identical across classes. To mitigate potential confusion, a single, unique numeric identifier shall apply, throughout the current disclosure, to any mechanical component maintaining functional equivalence, despite changes in form.
in figures where they find incorporation, double wailed outline arrows, marked at their base with an F x or K* (wherein the superscript " x " is equal to an integer between 0 to 16), represent generalized schematic mechanical Force Vectors as they are applied to, transmitted within and/or largely redirected within or beyond the mechanical elements over which they are graphically superimposed.
In figures where said outline arrows are marked with an initial "F", said Force Vectors are largely divergent from one another.
• In figures where said outline arrows are marked with an initial "K", said Force Vectors are largely convergent with one another. in two cases, (Figures 08 and 09) respective Force Vectors K° and F° are drawn without benefit of arrows; their individual trajectories projecting toward or away from the viewer, parallel to the line of sight. it is to be noted that ail Figures of the current disclosure (and their respective descriptions) make use of a three-dimensional cylindrical coordinate system wherein the X and Y axes follow rectilinear paths; the Z- axis generally following a curvilinear path largely consistent with that of rotary bearing rotation and geometry. in figures where they find incorporation, dashed lines or dashed arcs terminating with an arrow point on one or more ends (either superimposed over or immediately proximal to an identified mechanical component) indicate the possible range and direction(s) of mechanical movement for said mechanical component. Where two rectilinear dashed-line arrows are interconnected by a dashed line arc, movement of the mechanical element may occur along any radial path intermediate to said dashed line arrows.
In figures where they find incorporation, stitch line arcs (without arrows), superimposed over a circle are intended to indicate the curvature of outer surfaces of a spheroidal Rolling Load Bearing Element.
In Table 1 , below, are listed the Symbolic Notations, Nomenclature and Definitions for symbols, terms and abbreviations employed throughout the present disclosure.
[20] Table 01 : Definition of Symbols, Terms & Abbreviations
Designated
Symbolic
Nomenclature or Definition Notation
Textual Reference
In Figure 05: a numerically designated phantom line (in two parts), vertically
Cross Sectional superimposed over mechanical
005
Reference Line(s) components, indicating the intersection of a cross-sectional view displayed within Figure 06.
In Figure 06: a numerically designated
Detail Area broken line polygon, indicating areas
008
Reference detailed with greater precision in Figure
07.
In Figure 07: a numerically designated
Detail Area
007 broken line polygon, indicating areas
Reference
detailed in alternate embodiments.
in Figures 05, 06, 07, 10, 1 1 and 12: the outermost annulus of a rotary bearing system, therein providing direct structural support for a non-resilient Raceway (1010) and Means of Resilient Constraint (1013,
Outer Bearing 1014, 1024).
1000
Member in Figures 13 and 14: the outermost annulus of a rotary bearing system, therein providing direct structural support for a radially mounted Means of Resilient Constraint (1014) and a Resilient Raceway (1016). Designated
Symbolic
Nomenclature or Definition Notation
Textual Reference
A non-resilient curvilinear surface traversing the inner perimeter of the Outer Bearing Member (1000); providing an outer boundary and support for the rolling action
1010 Outer Raceway of a multi-tiered polymorphic Lattice
Packing of Rolling Load Bearing Elements; said outer Raceway (1010) being optionally equipped with one or more Means of Resilient Constraint (1013, 1014).
In Figures 05, 08, 07, 12: a continuous groove running along a lateral
Retentive circumference of outer Raceway (1010)
101 1
Anchorage providing pivotal anchorage and support for an axiaily oriented Means of Resilient Constraint (1013).
in Figures 05, 06, 07, 10, 11 and 12: a continuous groove running along a lateral circumference of outer Raceway (1010) providing pivotal anchorage and support for an axiaily oriented Means of Resilient
Retentive Constraint (1014).
1012
Anchorage in Figures 13 and 14: a continuous concaveiy shaped channel comprising the innermost load bearing surface of Outer Bearing Member (1000); therein providing support and anchorage for Means of Resilient Constraint (1014). Designated
Symbolic
Nomenclature or Definition Notation
Textual Reference
In Figures 05, 06, 07 and 12: A component providing resilient axial support and running surfaces for a multi-tiered polymorphic Lattice Packing of Rolling Load Bearing Elements moving within an
Means of Resilient outer Raceway (1010).
1013
Constraint in Figures 13 and 14, a component providing resilient radial support for a Resilient Raceway (1018 or 2016), preferably fabricated of materials which leverage the full potential of an interpenetrating diiatant polymer composite. in Figures 05, 06, 07, 10, 1 1 and 12: A component providing resilient axial support and running surfaces for a multi-tiered polymorphic Lattice Packing of Rolling Load Bearing Elements moving within an outer
Means of Resilient Raceway (1010).
1014
Constraint in Figures 13 and 14, a component providing resilient radial support for a Resilient Raceway (1016), preferably fabricated of materials that leverage the full potential of an inter-penetrating diiatant polymer composite. Designated
Symbolic
Nomenclature or Definition Notation
Textual Reference
A dynamically responsive surface providing flexible, yet firm support and load absorption for Rolling Load Bearing
Resilient
1018 Elements... preferably fabricated of
Raceway
materials that leverage the full potential of an inter-penetrating dilatant polymer composite.
In Figure 10: a component providing resilient axial support and running surfaces
Means of Resilient
1024 for a multi-tiered polymorphic Lattice
Constraint
Packing of Rolling Load Bearing Elements moving within an outer Raceway (1010).
The outermost radial (Z-axis) surface of a bearing's outer member, providing a
Externa!
contact interface for the transmission of
1032 Bearing
loads to or from mechanical elements of a Surface
given mechanical application external to the bearing assembly, per se..
Designated
Symbolic
Nomenclature or Definition Notation
Textual Reference
In Figures 05, 08, 07 and 12: a spheroidal shaped Rolling Load Bearing Element normally in simultaneous rolling contact with non-resilient outer Raceway (1010), Rolling Load Bearing Element 3050 and a Means of Resilient Constraint (1014).
Outer Tier
in Figures 13 and 14: a Rolling Load
050 Rolling Load
Bearing Element shaped in the form of a Bearing Element
concavely shaped roller, normally in simultaneous rolling contact with an outer Resilient Raceway (1016) and a Middle Tier Rolling Load Bearing Element (3050 - shaped in the form of a convexly shaped roller).
In Figures 06 and 07: a spheroidal shaped Rolling Load Bearing Element
Outer Tier
normally in simultaneous rolling contact
1051 Rolling Load
with non-resilient outer Raceway (1010), Bearing Element
Rolling Load Bearing Element 3050 and a Means of Resilient Constraint (1013).
Designated
Symbolic
Nomenclature or Definition Notation
Textual Reference
In Figures 01 , 02, 03, and 04: a spheroidal shaped Rolling Load Bearing Element normally in simultaneous rolling contact with non-resilient outer Raceway 1010 and Rolling Load Bearing Element 3070.
Outer Tier
089 Rolling Load
In Figure 06 and 12, a spheroidal shaped Bearing Element
Rolling Load Bearing Element normally in simultaneous rolling contact with non- resilient outer Raceway (1010), Rolling Load Bearing Element 3050 and a Means of Resilient Constraint (1013),
Designated
Symbolic
Nomenclature or Definition Notation
Textual Reference
In Figures 01 , 02, 03, and 04: a spheroidal shaped Rolling Load Bearing Element normally in simultaneous rolling contact with non-resilient outer Raceway 1010, Rolling Load Bearing Element 3070, and Means of Resilient Constraint (1014). in Figures 08 and 12: a spheroidal shaped Rolling Load Bearing Element normally in
Outer Tier
simultaneous roiling contact with non-
1070 Rolling Load
resilient outer Raceway (1010), Roiling Load Bearing Element
Bearing Element 3050 and a Means of Resilient Constraint (1014). in Figures 13 and 14: a Rolling Load Bearing Element shaped in the form of a concavely shaped roller, normally in simultaneous rolling contact with an Outer Resilient Raceway (1016) and Middle Tier Rolling Load Bearing Element (3050).
Designated
Symbolic
Nomenclature or Definition Notation
Textual Reference
In Figures 05 08, 07, and 12: the innermost annuius of a rotary bearing system, therein providing direct structural support for a non-resilient Raceway (2010) and Means of Resilient Constraint (2013 and 2014).
Inner Bearing
2000
Member in Figures 13 and 14: the innermost annuius of a rotary bearing system, therein providing direct structural support for a radially mounted Means of Resilient Constraint (2014) and a Resilient Raceway (2016),
A non-resilient curvilinear surface traversing the outer perimeter of the Inner Bearing Member (2000); providing an inner boundary and support for the rolling action
2010 inner Raceway of a multi-tiered polymorphic Lattice
Packing of Rolling Load Bearing Elements; said inner Raceway (2010) being optionally equipped with one or more Means of Resilient Constraint (2013, 2014).
In Figures 06, 07 and 12: a continuous groove running along a lateral
Retentive circumference of inner Raceway (2010)
2011
Anchorage providing pivotal anchorage and support for an axiaily oriented Means of Resilient Constraint (2013). Designated
Symbolic
Nomenclature or Definition Notation
Textual Reference
In Figures 05, 06, 07 and 12: a continuous groove running along a lateral circumference of inner Raceway (2010), providing pivotal anchorage and support for an axiaiiy oriented Means of Resilient Constraint (2014).
Retentive
2012
Anchorage in Figures 13 and 14: a continuous concave!y shaped channel comprising the outermost load bearing surface of inner Bearing Member (2000); therein providing pivotal anchorage and support for Means of Resilient Constraint (2014) and Resilient Raceway (2018),
In Figures 08, 07, 08, 09, and 12: A component providing resilient axial support
Means of Resilient and running surfaces for a multi-tiered
2013
Constraint polymorphic Lattice Packing of Roiling Load
Bearing Elements moving within an inner Raceway (2010),
Designated
Symbolic
Nomenclature or Definition Notation
Textual Reference
In Figures 05, 06, 07, 08, 09, and 12: A component providing resilient axial support and running surfaces for a multi-tiered polymorphic Lattice Packing of Roiling Load Bearing Elements moving within an inner Raceway (2010).
Means of Resilient
2014
Constraint
in Figures 13 and 14, a component providing resilient radial support for a Resilient Raceway (2016), preferably fabricated of materials which leverage the full potential of an inter-penetrating dilatanf polymer composite.
In Figures 13 and 14: a dynamically responsive surface providing flexible, yet firm support and load absorption for Rolling Load Bearing Elements...
2016 Resilient Raceway
preferably fabricated of materials which leverage the full potential of an interpenetrating dilatant polymer composite.
The innermost radial surface of a bearing's inner annulus, providing a contact interface for the transmission of loads to or
2032 Inner Bore
from mechanical elements of a given mechanical application external to the bearing assembly, per se. Designated
EH ί I
Nomenclature or Definition
Textual Reference
In Figures 05, 08 and 12: a spheroidal shaped Rolling Load Bearing Element normally in simultaneous rolling contact with non-resilient inner Raceway (2010),
Rolling Load Bearing Element 3050 and a
Means of Resilient Constraint (2014). in Figures 08 and 09, as viewed from topside: a spheroidal shaped Rolling Load
Inner Tier Rolling Bearing Element in simultaneous roiling
2050 Load Bearing contact with non-resilient inner Raceway
Element (2010), Middle Tier Roiling Load Bearing
Elements (3050, 3051 ) and eans of
Resilient Constraint (2014), in Figures 13 and 14: a Rolling Load
Bearing Element shaped in the form of a concavely shaped roller, normally in simultaneous rolling contact with an Inner
Resilient Raceway (2016) and a Middle Tier
Rolling Load Bearing Element (3050).
Designated
Symbolic
Nomenclature or Definition Notation
Textual Reference
in Figures 08, 07, and 12: a Roiling Load Bearing Element in simultaneous rolling contact with inner Raceway (2010), Middle Tier Rolling Load Bearing Element 3050 and Means of Resilient Constraint (2013).
Inner Tier Rolling
2051 Load Bearing
in Figures 08 and 09: a Rolling Load Element
Bearing Element in simultaneous rolling contact with inner Raceway (2010), Middle Tier Rolling Load Bearing Elements (3050, 3051 ) and Means of Resilient Constraint (2013).
In Figures 08 and 09, as viewed from topside: a spheroidal shaped Rolling Load
Inner Tier Rolling Bearing Element in simultaneous roiling
2052 Load Bearing contact with non-resiiient inner Raceway
Element (2010), Middle Tier Rolling Load Bearing
Elements (3050, 3049) and Means of Resilient Constraint (2014).
In Figures 08 and 09, as viewed from topside: a spheroidal shaped Rolling Load inner Tier Rolling Bearing Element in simultaneous roiling
2053 Load Bearing contact with non-resiiient inner Raceway
Element (2010), Middle Tier Rolling Load Bearing
Elements (3050, 3049) and Means of Resilient Constraint (2013). Designated
Symbolic
Nomenclature or Definition Notation
Textual Reference
As viewed in Figure 06; a Roiling Load Bearing Element in simultaneous roiling
Inner Tier Rolling
contact with non-resilient inner Raceway
2069 Load Bearing
(2010), Middle Tier Rolling Load Bearing Element
Element 3070 and Means of Resilient Constraint (2013).
in Figures 06 and 12: a spheroidal shaped Rolling Load Bearing Element normally in simultaneous roiling contact with non- resilient inner Raceway (2010), Middle Tier Rolling Load Bearing Element 3070 and
Inner Tier Rolling Means of Resilient Constraint (2014).
2070 Load Bearing
Element in Figures 13 and 14: a Rolling Load
Bearing Element shaped in the form of a concavely shaped roller, normally in simultaneous rolling contact with an Inner Resilient Raceway (2016) and a Middle Tier Rolling Load Bearing Element (3070).
In Figures 08 and 09: a spheroidal shaped Rolling Load Bearing Element normally in roiling contact only with Inner Tier Roiling Load Bearing Elements 2053 and 2052
Middle Tier
and Outer Tier Rolling Load Bearing
3049 Roiling Load
Elements not shown. As true with all Bearing Element
Middle Tier Roiling Load Bearing Elements, 3049 has no contact with a non-resilient Raceway (1010, 2010) or Resilient Raceway (1016, 2016). Designated
Symbolic
Nomenclature or Definition Notation
Textual Reference
In Figures 05, 06, 07, 08, 09, 10, 1 1 , and 12:a spheroidal shaped Rolling Load Bearing Element normally in roiling contact only with Inner and Outer Tier Rolling Load Bearing Elements. As true with all Middle Tier Roiling Load Bearing Elements, 3050 has no contact with a non-resilient Raceway
Middle Tier
(1010, 2010) or Resilient Raceway (1016, Rolling Load
3050 2016).
Bearing
Element
in Figures 13 and 14: a Rolling Load Bearing Element taking form as a convexly shaped roller, normally in contact with Rolling Load Bearing Elements of an inner and Outer Tier therein represented by concavely shaped Roiling Load Bearing Elements1050 and 2050.
In Figures 08 and 09: a spheroidal shaped Rolling Load Bearing Element normally in roiling contact only with Inner and Outer
Middle Tier
Tier Rolling Load Bearing Elements. As
3051 Rolling Load
true with all Middle Tier Roiling Load Bearing Element
Bearing Elements, 3051 has no contact with a non-resilient Raceway (1010, 2010) or Resilient Raceway (1016, 2016) Designated
EH ί I
Nomenclature or Definition
Textual Reference
in Figures 01 , 02, 03 and 04: a spheroidal shaped Rolling Load Bearing Element in the topmost tier of a multi-tiered Lattice, normally in contact only with subordinate
(Outer Tier) Roiling Load Bearing
Elements 1069 and 1070. in Figures 08 and 12: a spheroidal shaped
Rolling Load Bearing Element normaliy in
Middle Tier rolling contact only with Inner and Outer
3070 Roiling Load Tier Roiling Load Bearing Elements. As
Bearing Element true with all Middle Tier Rolling Load
Bearing Elements, 3070 has no contact with a non-resilient Raceways (1010,
2010) or Resilient Raceways (1018, 2018). in Figures 13 and 14: a Rolling Load
Bearing Element taking form as a convexly shaped roller, normally in rolling contact only with Rolling Load Bearing Elements of inner and Outer Tiers.
Designated
EH ί I
Nomenclature or Definition
Textual Reference
in Figures 01 and 04: an actual Y-axis dimensional measurement between the
Spherical Center point of Rolling Load
Bearing Elements 3070 (on Elevationai
Reference Y4) and a line (Elevationai
Reference Y2) connecting the Spherical
Centerpoints of Rolling Load Bearing
Elements 1089 and 1070.
Y-axis in Figure 02: a former Y-axis dimensional dY i Dimensional measurement between the former position
Measurement of the Spherical Center point of Rolling
Load Bearing Element 3070 (earlier positioned on Elevationai Reference Y3) and a yet unchanged Elevationai
Reference Y2, connecting the Spherical
Centerpoints of Roiling Load Bearing
Elements 1069 and 1070; said former Y- axis dimensional measurement placed therein for sake of comparison with new values.
Designated
EH ί I
Nomenclature or Definition
Textual Reference
in Figure 02, 03: an actual Y-axis dimensional measurement between the
Spherical Center point of Roiling Load
Bearing Elements 3070 (on Elevationai
Reference Y3) and a line (Elevationai
Reference Y2) connecting the Spherical
Centerpoints of Rolling Load Bearing
Elements 1089 and 1070.
Y-axis In Figure 04: a former Y-axis dimensional
Dimensional measurement between the former position
Measurement of the Spherical Center point of Rolling
Load Bearing Element 3070 (earlier positioned on Elevationai Reference Y3) and a yet unchanged Elevationai
Reference Y2, connecting the Spherical
Centerpoints of Roiling Load Bearing
Elements 1069 and 1070; said former Y- axis dimensional measurement placed therein for sake of comparison with new values.
Designated
Symbolic
Nomenclature or Definition Notation
Textual Reference
in Figures 01 and 04: an actual X-axis dimensional measurement between the Spherical Centerpoints of Rolling Load Bearing Elements 1069 and 1070,
X-axis
in Figure 02: a former X-axis dimensional d i Dimensional
measurement between the Spherical
Measurement
Centerpoints of Roiling Load Bearing Elements 1089 and 1070; said former X- axis dimensional measurement placed therein for sake of comparison with new values.
in Figures 02 and 03: an actual X-axis dimensional measurement between the Spherical Centerpoints of Roiling Load Bearing Elements 1069 and 1070,
X-axis
in Figure 04: a former X-axis dimensional dX 2 Dimensional
measurement between the Spherical
Measurement
Centerpoints of Roiling Load Bearing Elements 1069 and 1070; said former X- axis dimensional measurement placed therein for sake of comparison with new values. Designated
EH ί I
Nomenclature or Definition
Textual Reference
In Figures 01 and 02: an initial input Force
Vector produced upon an instance of Y-axis loading from above; said Force Vector traversing the upper hemisphere of Load
Bering Roiling Element 3070 and thereafter being redirected as Force Vectors F and F 2 .
The genera! direction of said Force Vector is designated by an outlined arrow; the magnitude of said Force Vector, relative to other Force Vectors, being so indicated by the relative span between arrow shaft sides, and the approximate reach of said Force
Vector designated by outline arrow length.o Force Vector
In Figure 08: an initial input Force Vector produced upon an instance of Y-axis loading that originates within the line of sight, directionaliy away from the observer; said Force Vector traversing the upper hemisphere of Rolling Load Bearing
Element 3050 and thereafter being redirected into the Lattice Packing as Force
Vectors F , F 2 , F 3 and F 4 ; said Force
Vector F° therein drawn without a visible arrow due to its shared orientation with the
Y-axis line of sight. Designated
Symbolic
Nomenclature or Definition Notation
Textual Reference
In Figures 01 and 02: a Force Vector traversing portions of Rolling Load Bearing Elements 3070 and 1069; divergent from Force Vector F°.
In Figure 08: a Force Vector traversing portions of Rolling Load Bearing Elements 3050 and 2051 ; divergent from Force Vector F°.
F i Force Vector
The general direction of said Force Vector is designated by an outlined arrow; the magnitude of said Force Vector, relative to other Force Vectors, being so indicated by the relative span between arrow shaft sides, and the approximate reach of said Force Vector being designated by outline arrow length.
Designated
Symbolic
Nomenclature or Definition Notation
Textual Reference
In Figures 01 and 02: a Force Vector traversing portions of Rolling Load Bearing Elements 3070 and 1070, divergent from Force Vector F°.
In Figure 08: a Force Vector traversing portions of Roiling Load Bearing Elements 3050 and 2050; divergent from Force Vector F°.
F2 Force Vector
The general direction of said Force Vector is designated by an outlined arrow; the magnitude of said Force Vector, relative to other Force Vectors, being so indicated by the relative span between arrow shaft sides, and the approximate reach of said Force Vector being designated by outline arrow length.
Designated
Symbolic
Nomenclature or Definition Notation
Textual Reference
In Figure 08: a Force Vector traversing portions of Roiling Load Bearing Elements 3050 and 2053; divergent from Force Vector F°,
The general direction of said Force Vector
F3 Force Vector is designated by an outlined arrow; the magnitude of said Force Vector, relative to other Force Vectors, being so indicated by the relative span between arrow shaft sides, and the approximate reach of said Force Vector being designated by outline arrow length.
In Figure 08: a Force Vector traversing portions of Roiling Load Bearing Elements 3050 and 2052; divergent from Force Vector F° and therein represented in the form of an outline arrow.
The general direction of said Force Vector
Force Vector
is designated by an outlined arrow; the magnitude of said Force Vector, relative to other Force Vectors, being so indicated by the relative span between arrow shaft sides, and the approximate reach of said Force Vector being designated by outline arrow length. Designated
Symbolic
Nomenclature or Definition Notation
Textual Reference
In Figures 01 and 02: a Force Vector traversing portions of Rolling Load Bearing Element 1069. in Figure 08: a Force Vector traversing portions of Rolling Load Bearing Element 2051 and Means of Resilient Constraint (2013), divergent from Force Vector F 1 .
Fs Force Vector
The general direction of said Force Vector is designated by an outlined arrow; the magnitude of said Force Vector, relative to other Force Vectors, being so indicated by the relative span between arrow shaft sides, and the approximate reach of said Force Vector being designated by outline arrow length.
Designated
Symbolic
Nomenclature or Definition Notation
Textual Reference
In Figures 01 and 02: a Force Vector traversing portions of Rolling Load Bearing Element 1070. in Figure 08: a Force Vector traversing portions of Rolling Load Bearing Element 2050 and Means of Resilient Constraint (2014), said Vector herein divergent from Force Vector F 2 .
Force Vector
The general direction of said Force Vector is designated by an outlined arrow; the magnitude of said Force Vector, relative to other Force Vectors, being so indicated by the relative span between arrow shaft sides, and the approximate reach of said Force Vector being designated by outline arrow length.
Designated
Symbolic
Nomenclature or Definition Notation
Textual Reference
In Figure 08: a Force Vector traversing portions of Rolling Load Bearing Element 2053 and Means of Resilient Constraint (2013), said Vector herein divergent from Force Vector F 3 .
The general direction of said Force Vector
F ~ Force Vector
is designated by an outlined arrow; the magnitude of said Force Vector, relative to other Force Vectors, being so indicated by the relative span between arrow shaft sides, and the approximate reach of said Force Vector being designated by outline arrow length.
In Figure 08: a Force Vector traversing portions of Rolling Load Bearing Element 2052 and Means of Resilient Constraint (2014), said Vector herein divergent from Force Vector F 4 .
The general direction of said Force Vector
Force Vector
is designated by an outlined arrow; the magnitude of said Force Vector, relative to other Force Vectors, being so indicated by the relative span between arrow shaft sides, and the approximate reach of said Force Vector being designated by outline arrow length. Designated
Symbolic
Nomenclature or Definition Notation
Textual Reference
In Figure 08: a Force Vector traversing portions of Rolling Load Bearing Element 2051 and 3051 , said Vector herein divergent from Force Vector F 1 .
The genera! direction of said Force Vector pi Force Vector is designated by an outlined arrow; the magnitude of said Force Vector, relative to other Force Vectors, being so indicated by the relative span between arrow shaft sides, and the approximate reach of said Force Vector being designated by outline arrow length.
In Figure 08: a Force Vector traversing portions of Roiling Load Bearing Element 2050 and 3051 , said Vector herein divergent from Force Vector F 2 .
The general direction of said Force Vector p 2 Force Vector is designated by an outlined arrow; the magnitude of said Force Vector, relative to other Force Vectors, being so indicated by the relative span between arrow shaft sides, and the approximate reach of said Force Vector being designated by outline arrow length. Designated
Symbolic
Nomenclature or Definition Notation
Textual Reference
In Figure 08: a Force Vector traversing portions of Rolling Load Bearing Element 2053 and 3049, said Vector herein divergent from Force Vector F 3 .
The general direction of said Force Vector
F13 Force Vector is designated by an outlined arrow; the magnitude of said Force Vector, relative to other Force Vectors, being so indicated by the relative span between arrow shaft sides, and the approximate reach of said Force Vector being designated by outline arrow length.
In Figure 08: a Force Vector traversing portions of Rolling Load Bearing Element 2052 and 3049, said Vector therein divergent from Force Vector F 4 .
The general direction of said Force Vector l4 Force Vector is designated by an outlined arrow; the magnitude of said Force Vector, relative to other Force Vectors, being so indicated by the relative span between arrow shaft sides, and the approximate reach of said Force Vector being designated by outline arrow length. Designated
Symbolic
Nomenclature or Definition Notation
Textual Reference
In Figure 08: a Force Vector traversing portions of Rolling Load Bearing Element 3049; said Vector therein originating from the angular convergence of Force Vectors F^ and F«.
The general direction of said Force Vector pis Force Vector
is designated by an outlined arrow; the magnitude of said Force Vector , relative to other Force Vectors, being so indicated by the relative span between arrow shaft sides, and the approximate reach of said Force Vector being designated by outline arrow length.
In Figure 08: a Force Vector traversing portions of Rolling Load Bearing Element 3051 ; said Vector therein originating from the angular convergence of Force Vectors
The general direction of said Force Vector
Force Vector
is designated by an outlined arrow; the magnitude of said Force Vector , relative to other Force Vectors, being so indicated by the relative span between arrow shaft sides, and the approximate reach of said Force Vector being designated by outline arrow length. Designated
Nomenclature or
extuaf Reference
In Figures 03 and 04: an output Force Vector traversing the upper hemisphere of Rolling Load Bearing Element 3070; said vector originating from the angular convergence of two reciprocal Force Vectors Κ· and K 2 near the Spherical Center of Rolling Load Bearing Element 3070 whereupon they are upwardly redirected along the Y-axis as K°, subsequently emerging from the top center surface of 3070 .
The general direction of said Force Vector is designated by an outlined arrow; the
Force Vector
magnitude of said Force Vector, relative to other Force Vectors, being so indicated by the relative span between arrow shaft sides, and the approximate reach of said Force Vector being designated by outline arrow length. in Figure 09 : a Force Vector traversing portions of Roiling Load Bearing Element 3050; said Force Vector (in Figure 09) directed towards the viewer, along the Y- axis; said Force Vector K° therein drawn without a visible arrow due to its shared orientation with the Y-axis line of sight. . Designated
Symbolic
Nomenclature or Definition Notation
Textual Reference
In Figures 03 and 04: a Force Vector angularly traversing portions of Rolling Load
Bearing Elements 1069 and 3070; originating from Force Vector K 5 , in Figure 09: a Force Vector traversing portions of Rolling Load Bearing
Elements 2051 and 3050; originating from the convergence of Force Vectors
Ki Force Vector K* and K".
The general direction of said Force Vector is designated by an outlined arrow; the magnitude of said Force Vector, relative to other Force Vectors, being so indicated by the relative span between arrow shaft sides, and the approximate reach of said Force
Vector being designated by outline arrow length.
Designated
Symbolic
Nomenclature or Definition Notation
Textual Reference
In Figures 03 and 04: a Force Vector angularly traversing portions of Rolling Load
Bearing Elements 1070 and 3070; originating from Force Vector K 5 , in Figure 09: a Force Vector traversing portions of Rolling Load Bearing
Elements 2050 and 3050; originating from the convergence of Force Vectors
K2 Force Vector Ks and K12.
The general direction of said Force Vector is designated by an outlined arrow; the magnitude of said Force Vector, relative to other Force Vectors, being so indicated by the relative span between arrow shaft sides, and the approximate reach of said Force
Vector being designated by outline arrow length.
Designated
Symbolic
Nomenclature or Definition Notation
Textual Reference
In Figure 09: a Force Vector traversing portions of Rolling Load Bearing Elements 2053 and 3050; originating from the angular convergence of Force Vectors K 7 and K 13 .
The general direction of said Force Vector
K3 Force Vector
is designated by an outlined arrow; the magnitude of said Force Vector, relative to other Force Vectors, being so indicated by the relative span between arrow shaft sides, and the approximate reach of said Force Vector being designated by outline arrow length.
In Figure 09: a Force Vector traversing portions of Roiling Load Bearing Elements 2052 and 3050; originating from the angular convergence of Force Vectors K 8 and K
The general direction of said Force Vector
K Force Vector
is designated by an outlined arrow; the magnitude of said Force Vector, relative to other Force Vectors, being so indicated by the relative span between arrow shaft sides, and the approximate reach of said Force Vector being designated by outline arrow length. Designated
Symbolic
Nomenclature or Definition Notation
Textual Reference
in Figures 03 and 04: a Force Vector traversing portions of Rolling Load
Bearing Element 1089; originating from the application of an external, X-axis load. in Figure 09: a Force Vector traversing portions of Roiling Load Bearing
Element 2051 ; originating from the release of previously stored energy in
Force Vector Means of Resilient Constraint (2013) along the X-axis.
The general direction of said Force Vector is designated by an outlined arrow; the magnitude of said Force Vector, relative to other Force Vectors, being so indicated by the relative span between arrow shaft sides, and the approximate reach of said
Force Vector being designated by outline arrow length.
Designated
EH _Γ4 ί I -T"
Nomenclature or Definition
Textual Reference
In Figures 03 and 04: a Force Vector traversing portions of Roiling Load
Bearing Element 1070; originating from the application of an external, X-axis load.
In Figure 09: a Force Vector traversing portions of Rolling Load Bearing
Element 2050 ; originating from the release of previously stored energy in
KB Force Vector Means of Resilient Constraint (2014) along the X-axis.
The general direction of said Force Vector is designated by an outlined arrow; the magnitude of said Force Vector, relative to other Force Vectors, being so indicated by the relative span between arrow shaft sides, and the approximate reach of said Force
Vector being designated by outline arrow length.
Designated
Symbolic
Nomenclature or Definition Notation
Textual Reference
In Figure 09: a Force Vector traversing portions of Rolling Load Bearing Element 2053 ; originating from the release of previously stored energy in Means of Resilient Constraint (2013) along the X- axis.
KJ Force Vector
The general direction of said Force Vector is designated by an outlined arrow; the magnitude of said Force Vector, relative to other Force Vectors, being so indicated by the relative span between arrow shaft sides, and the approximate reach of said vector being designated by outline arrow length.
In Figure 09: a Force Vector traversing portions of Rolling Load Bearing Element 2052; originating from the release of previously stored energy in Means of Resilient Constraint (2014) along the X- axis.
KB Force Vector The genera! direction of said Force Vector is designated by an outlined arrow; the magnitude of said Force Vector, relative to other Force Vectors, being so indicated by the relative span between arrow shaft sides, and the approximate reach of said vector being designated by outline arrow length. Designated
Symbolic
Nomenclature or Definition Notation
Textual Reference
In Figure 09: a Force Vector traversing portions of Roiling Load Bearing Elements 3051 and 2051 , originating from Force Vector K
The general direction of said Force Vector
K11 Force Vector is designated by an outlined arrow; the magnitude of said Force Vector , relative to other Force Vectors, being so indicated by the relative span between arrow shaft sides, and the approximate reach of said Force Vector being designated by outline arrow length.
In Figure 09: a Force Vector traversing portions of Rolling Load Bearing Elements 3051 and 2050, originating from Force Vector K 6 .
The general direction of said Force Vector
K12 Force Vector is designated by an outlined arrow; the magnitude of said Force Vector , relative to other Force Vectors, being so indicated by the relative span between arrow shaft sides, and the approximate reach of said Force Vector being designated by outline arrow length. Designated
Symbolic
Nomenclature or Definition Notation
Textual Reference
In Figure 09: a Force Vector traversing portions of Roiling Load Bearing Elements 3049 and 2053, originating from Force Vector K
The general direction of said Force Vector
K13 Force Vector is designated by an outlined arrow; the magnitude of said Force Vector , relative to other Force Vectors, being so indicated by the relative span between arrow shaft sides, and the approximate reach of said Force Vector being designated by outline arrow length.
In Figure 09: a Force Vector traversing portions of Rolling Load Bearing Elements 3049 and 2052, originating from Force Vector K 5 .
The general direction of said Force Vector is designated by an outlined
K14 Force Vector
arrow; the magnitude of said Force Vector , relative to other Force Vectors, being so indicated by the relative span between arrow shaft sides, and the approximate reach of said Force Vector being designated by outline arrow length. Designated
Symbolic
Nomenclature or Definition Notation
Textual Reference
In Figure 09: a Force Vector traversing portions of Rolling Load Bearing Element 3049, originating from Z-axis loads transmitted to Rolling Load Bearing Element 3049 from Lattice Packing components outside the scope of Figure 09.
K15 Force Vector
The general direction of said Force Vector is designated by an outlined arrow point; the magnitude of said Force Vector , relative to other Force Vectors, being so indicated by the relative span between arrow shaft sides, and the approximate reach of said Force Vector being designated by outline arrow length.
Designated
Symbolic
Nomenclature or Definition Notation
Textual Reference
In Figure 09: a Force Vector traversing portions of Rolling Load Bearing Element 3051 , originating irorn Z-axis loads transmitted to Rolling Load Bearing Element 3051 from Lattice Packing components outside the scope of Figure 09.
Force Vector
The general direction of said Force Vector is designated by an outlined arrow point; the magnitude of said Force Vector , relative to other Force Vectors, being so indicated by the relative span between arrow shaft sides, and the approximate reach of said Force Vector being designated by outline arrow length.
One of three axes in a three dimensional Cylindrical Coordinate System, running perpendicular to the Y-axis; typically drawn as a solid line arrow with an "X" proximal to the arrow point: otherwise depicted as a period mark when coincident with the
X X-axis
observer's line of sight. Said axis being drawn, in combination with Y and Z axes, as an aid to spatial orientation within the multiple Figures of the current disclosure, but not a part of the mechanical elements of movements therein disclosed. Designated
Symbolic
Nomenclature or Definition Notation
Textual Reference
One of three axes in a three dimensional Cylindrical Coordinate System, running perpendicular to the X-axis; typically drawn as a solid line arrow with a Y proximal to the arrow point; otherwise
Y Y-axis depicted as a period mark when coincident with the observer's line of sight. Drawn, in combination with X and Z axes, as an aid to spatial orientation within the Figure, but not a part of the mechanical elements therein disclosed.
One of three axes in a three dimensional Cylindrical Coordinate System, depicted in perspective drawings as an arc; depicted in plan drawings as either a straight arrow or period mark, dependent on the observers
Z Z-axis line of sight respective to the drawing; said axis being marked with a generic Z, or, in the case of Figures 01 , 02, 03 and 04 (where it proceeds in two opposing directions along the same arc) with a +Z and -Z.
In figures 01 , 02, 03 and 04 : a relative measurement of vertical alignment as
Y-axis Elevationai
Y2 measured along the Y-axis in a three
Reference
dimensional (X, Y, Z) Cylindrical Coordinate System. Designated
Symbolic
Nomenclature or Definition Notation
Textual Reference
In Figures 02, 03and 04: a relative measurement of vertical alignment as
Y-axis E!evational
Y3 measured along the Y-axis in a three
Reference
dimensional (X, Y, Z) Cylindrical Coordinate System.
In Figures 01 , 02 and 04: a relative measurement of vertical alignment as
Y-axis Eievational
Y4 measured along the Y-axis in a three
Reference
dimensional (X, Y, Z) Cylindrical Coordinate System.
As generally derived from current patent classification schemes: a mechanical device wherein a supportive bearing member bears the weight and inertial mass of a loaded bearing member through a anti- anti- single intermediate tier of one or more frictional frictional
complements of Rolling Load Bearing bearing bearing
Elements, thus allowing a loaded bearing member to move in anti-frictional (non- sliding) contact with relation to a supportive bearing member.
In a three tiered polymorphic lattice packing of Rolling Load Bearing Elements, that layer of said elements in direct roiling contact with an inner non-resilient
Inner Tier Inner Tier
Raceway (2010), an inner resilient Raceway (2016) or Means of Resilient Constraint attached thereto. (2013 or 2014) Designated
Symbolic
Nomenclature or Definition Notation
Textual Reference
In a three tiered polymorphic lattice packing of Rolling Load Bearing Elements, that layer of said elements in direct rolling contact only
Middle Tier Middle Tier
with Roiling Load Bearing Elements belonging to an Inner or Outer Tier of said lattice packing.
In a three tiered polymorphic lattice packing of Rolling Load Bearing Elements, that layer of said elements in direct rolling contact with an outer non-resilient
Outer Tier Outer Tier
Raceway (1010), an outer resilient Raceway (1016) or Means of Resilient Constraint attached thereto. (1013 or 1014)
Any tier of Roiling Load Bearing Elements within a multi-tiered periodic Lattice Packing wherein rolling contact is intermediate
intermediate tier maintained only with Roiling Load Bearing tier
Elements of adjacent tiers; not however maintaining any direct contact with a raceway or Means of Resilient Constraint.
As defined by the International Union of Pure and Applied Chemistry: A polymer
Intercomposite comprising two or more
Interpenetrating ... networks which are at least partially penetrating
polymer interlaced on a molecular scale but not polymer
composite covaientiy bonded to each other and composite
cannot be separated unless chemical bonds are broken. Designated
Symbolic
Nomenclature or Definition Notation
Textual Reference
Any arrangement of Rolling Load Bearing Elements within a multi-tiered polymorphic Lattice, wherein individual load bearing elements of one tier partially intrude into the interstitial spaces between Roiling Load
Interstitial Interstitial
Bearing Elements of an adjacent tier, Packing Packing
therein making contact with said adjacent tier elements and thereby forming a continuous multi-tiered, largely periodic and largely anti-frictional packing of Rolling Load Bearing Elements throughout the raceway.
In the context of this disclosure: voids maintained between adjacent Rolling Load Bearing Elements of a same tier to prevent counter-rotational friction between leading interstitial
interstitial Spacings and trailing surfaces of said Elements.
Spacings
In prior art, said voids are traditionally maintained with a cage device, discreet non-ioad-bearing component or other non- load-bearing mechanisms.
Conceptual terminology adapted from the field of crystallography; herein utilized to describe the non-static, dynamic arrangement of Roiling Load Bearing
Lattice
Lattice Packing Elements within a multi-tiered, periodic Packing
and polymorphic assembly of Rolling Load Bearing Elements. Lattice Packing is otherwise referred to, within the current disclosure, as interstitial Packing. Designated
Symbolic
Nomenclature or Definition Notation
Textual Reference
Herein used to functionally describe any singular element within a larger lattice packing of similar or complementary Roiling Load Bearing Elements; said element being alternately embodied within this disclosure as a spheroidal shaped solid, a convexly
Rolling
shaped cylindrical solid or concaveiy shaped Load Rolling Load
cylindrical solid; said component (along with Bearing Bearing Element
other components within the lattice packing) Element
initially supporting the weight and inertia! mass of a loaded bearing member and thereafter transferring said loads to other Rolling Load Bearing Elements, to a Means of Resilient Constraint or to a non-resilient or Resilient Raceway.
In Figures 01 , 02, 03 and 04: that tier of
Lower
Rolling Load Bearing Elements in closest Lattice Lower Lattice Tier
proximity and rolling contact with a non- Tier
resilient outer Raceway (1010)
A packing of Roiling Load Bearing
Multi-tiered Elements, wherein multiple layers of said
Multi-tiered Lattice
Lattice elements are interstitiaily stacked, one
Packing
Packing upon another, around a common z-axis of rotation.
That pattern of Roiling Load Bearing periodic Elements, within a multi-tiered polymorphic
Periodic Lattice
Lattice Lattice, being repetitiously manifested as a grouping
grouping pattern or schema around a common
Z-axis in a Cylindrical Coordinate System. Designated
Symbolic
Nomenclature or Definition Notation
Textual Reference
Having a capability to adjust the angular orientation of contact between Roiling Load Bearing Elements of adjacent tiers within a Lattice Packing, in direct response to imposed loads, thus permitting the polymorphic polymorphic simultaneous compression of the Lattice along one axis with a corresponding expansion along a complimentary axis; said adjustment changing the inner configuration and outward shape of the Lattice Packing.
Cooperative
A harmonization of existing ECLA and
CPC Patent
USPC patent classification systems.
Classification
European The European Classification System, now
EC LA Classification replaced by the Cooperative Patent
System Classification in Espacenet.
Established by the Strasbourg Agreement 1971 , the IPC provides for a hierarchical
International
system of language independent symbols
IPC Patent
for the classification of patents and utility
Classification
models according to the different areas of technology to which they pertain.
A system for organizing all U. S. patent
United States documents and many other technical
USPC Patent documents into relatively small
Classification collections based on common subject matter. Summary Usting of Figures
] Figure 01 presents, in perspective view, three Rolling Load Bearing Elements arranged as a Multi-tiered Lattice Packing; said Lattice Packing supported at its base by a static, non-resilient raceway; said Lattice depicted in an instance of initial loading at its apex by a single Force Vector F°. ] Figure 02 presents the same elements and view of Figure 01 , now however in an instance following that of initial loading by Force Vector F°, wherein Rolling Load Bearing Elements of the lower tier have been moved farther apart along the x-axis, upper tier Rolling Load Bearing Element 3050 is now lower in elevation, and the energy of Force Vector F° divergently redistributed to lower tier spherical elements within the Lattice Packing and beyond. ] Figure 03 presents the same elements and view of Figure 02, now however in an instance of initial loading by two convergent Force Vectors K 5 and K 6 along the x-axis. ] Figure 04 presents the same elements and view of Figure 03, now however in an instance following that of initial loading by two convergent Force Vectors K 5 and K 6 ; the periodic Lattice Packing of said elements (2051 , 2050) now compressed at its base, and the energy of Force Vectors K s and K 6 convergently redistributed to a spherical element (3050) positioned above. ] Figure 05 presents a perspective partial cut-away view of an anti-frictional radial bearing incorporating three concentrically tiered layers of Rolling Load Bearing Elements arranged as a rolling Lattice confined within two non-resilient raceways and two (visible) Means of Resilient Constraint.
Figure 08 presents a cross-sectional detail view of Figure 05, depicting the dynamic Lattice Packing of ten interstitially packed Rolling Load Bearing Elements; the grouping of Roiling Load Bearing Elements enclosed within Detail Area Reference 006 being periodically repeated at 10 degree intervals throughout the raceways (1010, 2010) of the bearing as earlier depicted in Figure 05.
Figure 07 presents expanded detail of area 006 in Figure 06, upon an instance of loading along one or more of its X and/or Y axes, showing possible ranges and directions of mechanical movement for individual Rolling Load Bearing Elements.
Figure 08 presents a topside (parallel to Y-axis) view of Figure 07 wherein selected Outer Tier Rolling Load Bearing Elements have been masked to reveal the underlying packing of Middle and Inner Tier Rolling Load Bearing Elements, a non-resilient inner Raceway (2010) and two Means of Resilient Constraint (2013, 2014); said elements depicted upon an instance of radial loading by divergent Input Force Vector F°as it proceeds away from the viewer along the Y-axis.
Figure 09 presents the same elements and view of Figure 08, now upon an instance of reciprocal loading by two Means of Resilient Constraint (2013, 2014) and Middle Tier Load Bearing Elements (3049, 3051 ), as stored energy is returned along X and Z axes to converge as Force Vector K° in a direction toward the viewer, parallel to the line of sight.
Figure 10 presents an alternate embodiment of Detail Area Reference 007 in Figure 07 wherein the Means of Resilient Constraint (1014) is now duplicated by a secondary Means of Resilient Constraint (1024) of similar design and capacity.
Figure 1 1 presents an alternate embodiment of Detail Area Reference 007 in Figure 07 wherein the Means of Resilient Constraint (1014) now takes form as a pre-tensioned U spring.
Figure 12 presents a partial cutaway section of a rotary bearing, similar to thai of Figure 08, herein extended along its X-axis to accommodate additional Rolling Load Bearing Elements within the Lattice Packing.
Figure 13 presents, from a viewpoint similar to that of Figure 06, the cross sectional view of a three-tiered Lattice Packing of Roiling Load Bearing Elements, two Means of Resilient Constraint and two Resilient Raceways wherein the form of all components has been modified from the earlier embodiment of Figure 06 to meet the requirements of a rotary roller bearing. Figure 13 depicts all components in an instance immediately prior to loading by Force Vector F Q .
Figure 14 presents the same elements of Figure 13, herein modified to reflect changes wrought to Resilient Raceways (1016, 2016), Means of Resilient Constraint (1014, 2014) and the Lattice Packing of Roiling Load Bearing Elements (1050, 3050, 2050, 2070, 3070 and 1070) following the application of Force Vector F0 over time.
Detailed Description Of Drawings
gyre 01
Figure 01 presents a primitive Lattice Packing of three Roiling Load Bearing Elements (3070, 1069, 1070) vertically arranged in two tiers along a shared Y-axis, said arrangement supported at its base by non-resilient outer Raceway (1010), in an instance of dynamic or static loading by Force Vector F0.
Said arrangement, and those arrangements of Roiling Load Bearing Elements depicted in following Figures are hereinafter referred to as a "Lattice", "Lattice Packing", "Multi-tiered Lattice Packing" or "multi-tiered polymorphic Lattice Packing". Said arrangements, throughout this disclosure, poiymorphical!y adapt their outer shape and inner configuration to forces imposed upon them. In Figure 01 an upper tier of the Lattice is represented by Rolling Load Bearing Element 3070, whereas a lower tier of the Lattice is represented by Rolling Load Bearing Elements 1069 and 1070, (In Figures 05, 06, 07, 12, 13 and 14) said upper tier becomes a Middle Tier and -where included- said lower tier becomes an Inner Tier as a new tier of Rolling Load Bearing Elements is added to the present design.)
Two Y-axis Elevationai References (Y2 and Y4) indicate the relative elevation of Roiling Load Bearing Elements in said two tiers; said Y-axis Elevationai References intersecting with the Spherical Centerpoints of Rolling Load Bearing Elements through which they pass or connect.
Within the Lattice Packing of figure 01 , Rolling Load Bearing Element 3070 partially intrudes into the interstitial space between Elements 1070 and 1069 whilst maintaining contact with said Elements; said Rolling Load Bearing Element 3070 furthermore preventing static, roiling, or sliding contact between Rolling Load Bearing Elements 1070 and 1069 . Collectively, the entire Lattice Packing is supported for roiling contact by non-resilient Raceway (2010). in an instance of dynamic or static loading, external divergent Input Force Vector F° is applied top center of Rolling Load Bearing Element 3070, from which it proceeds in a generally downward direction along the Y-axis towards the Spherical Center point of Roiling Load Bearing Element 3070, herein represented by a single dot at the center of a circle.
Upon reaching proximity with said Spherical Center point, external divergent Input Force Vector F° is then largely redirected as two divergent Force Vectors F 1 and F 2 ; each of said vectors moving toward one of two Spherical Centerpoints within Roiling Load Bearing Element 1069 or 1070.
Upon reaching proximity with said Spherical Centerpoints, divergent Force Vectors F and F 2 are largely redirected as divergent Force Vectors F 5 and F s , each running, in an opposing direction, parallel to the X-axis of non- resilient Raceway (2010).
[44] In figure 01 , dY is a baseline measurement of difference in vertical elevation between the Spherical Center point of Rolling Load Bearing Element 3070 (centered on Y-axis Elevational Reference Y4) and the Spherical Centerpoints of Rolling Load Bearing Elements 1069 and 1070 (centered on Y-axis Elevational Reference Y2), immediately prior to loading by divergent input Force Vector F°.
[45] Of specific note in figure 01 is that a singular Force Vector (F°) originates from a direction, generally perpendicular to the X-axis, and is ultimately transformed by the Lattice Packing into two oppositional divergent Force Vectors (F s and F 6 ) running generally parallel to the X-axis. The direction and intensity of an input force have been altered by the Multi-tiered Lattice Packing of Roiling Load Bearing Elements.
[46] Figure 02
[47] Figure 02 presents the same elements of Figure 01 , their positions now moved by the continued application of divergent input Force Vector F° over a passage of time.
[48] In Figure 02, an Input Force Vector F° has been applied to the top (surface) center point of Roiling Load Bearing Element 3070 along its Y-axis; said Input Force Vector F° being subsequently split, in an area proximal to the Spherical Center point of said Rolling Load Bearing Element 3070, into two divergent Force Vectors: F 1 and F 2 .
[49] Each of said divergent Force Vectors F 1 and F 2 subsequently proceeds toward a respective Spherical Center point of Roiling Load Bearing
Element 1069 or 1070, whereupon said Vectors F and F 2 are largely redirected into respective divergent Force Vectors F s or F 6 . Most notably, Rolling Load Bearing Element 3070 has dropped from its former elevation, centered on Elevational Reference Y4, to its current position, now centered on Elevational Reference Y3, and Rolling Load Bearing Elements 1089 and 1070 have moved farther apart from one another along the X-axis as measured by dX 2 ,
For sake of comparison with new measurements, dY 1 and dX 1 of Figure 01 are herein included at their original positions.
Net loss in elevation for Roiling Load Bearing Element 3070 may be calculated as dY 1■ dY 2 .
Net increase in horizontal distance between Roiling Load Bearing Elements 1069 and 1070 may be calculated as dX 2 - dX 1 .
Of specific note in Figure 02 is that a single (vertical) Y-axis Force Vector (load) applied to an upper tier Rolling Load Bearing Element (3070) in the Lattice Packing results in a multiplicity of divergent X-axis Force Vectors. From a single source (F°) energy is absorbed and redirected in new directions throughout the Lattice Packing as it po!ymorphica!ly adapts its outer form and inner configuration to Force Vectors (loads) acting upon it.
As demonstrated in the balance of this disclosure, the divergence and convergence of Force Vectors may be more intricately harnessed and further manipulated in more evolved versions of the current embodiment.
Figure 03
Figure 03 presents the same elements of Figure 02 upon an initial instance of loading reciprocal to that depicted in Figure 02.
Within the Lattice Packing of figure 03, Rolling Load Bearing Element 3070 remains in nested roiling contact with Rolling Load Bearing Elements 1070 and 1069 wherein said Rolling Load Bearing Element 3070 serves to prevent rolling or sliding contact between said Rolling Load Bearing Elements 1070 and 1069 while simultaneously transmitting loads between said Elements. Collectively, the entire Lattice structure is supported by non- resilient Raceway (2010). in Figure 03, dX 2 symbolically represents a baseline X-axis (horizontal) distance between the Spherical Centerpoints of Rolling Load Bearing Elements 1069 and 1070, upon an initial instance of loading by convergent input Force Vectors K 5 and K 6 .
in Figure 03, dY 2 symbolically represents a baseline Y-axis (vertical) distance between the elevation of Rolling Load Bearing Element 3070 and the elevation of Roiling Load Bearing Elements 1070 and 1069, immediately prior to an instance of loading by convergent input Force Vectors K 5 and K 6 . in figure 03, convergent input Force Vectors K s and K 6 are initially directed toward respective Spherical Centerpoints of Roiling Load Bearing Elements 1069 or 1070 along Elevation Reference Y2.
At or near their respective targets, convergent input Force Vectors K 5 and K 6 are largely redirected as convergent input Force Vectors K 1 and K 2 toward the Spherical Center point of Roiling Load Bearing Element 3070, whereupon said convergent input Force Vectors K 1 and K 2 are largely redirected (upward) as convergent output Force Vector K° to, and beyond the upper extremities of Rolling Load Bearing Element 3070.
Of specific note in Figure 03 is that convergent input Force Vectors K 5 and K 6 originate from two diametrically opposed directions, running horizontally (generally parallel to the X-axis ), and are subsequently redirected by the Lattice Packing into a single converged Force Vector K°, running vertically (generally parallel to the Y-axis). Figure 04
Figure 04 presents the same elements of Figure 03, with the positions of some elements now modified by the continued application of energy from convergent input Force Vectors K 5 and K s over time.
As may be observed, convergent Force Vectors K 5 and K 6 have been applied to Roiling Load Bearing Elements 1069 and 1070 along their X- axis, resulting in the movement of said Roiling Load Bearing Elements into closer mutual proximity as now measured by X-axis Distance Measurement dX i .
For sake of comparison, X-axis Distance Measurement dX 2 and Y-axis Distance Measurement dY 2 are herein included, consistent with their original (Figure 03) presentation.
As may be observed from a comparison of prior X-axis Distance Measurement dX 2 and current X-axis Distance Measurement dX 1 , the relative X-axis distance between the Spherical Centerpoints of Rolling Load Bearing Elements 1069 and 1070 has been significantly decreased. This decrease may be calculated as dX 2 - dX 1 . in Figure 04, convergent input Force Vectors K 5 and K 6 are largely redirected as convergent Force Vectors K 1 and K 2 toward the Spherical Center point of Rolling Load Bearing Element 3070 and thereupon largely combined into a singular converged output Force Vector K°, whereby the elevation of Roiling Load Bearing Element 3070 is raised to Y-axis Elevational Reference Y4. This increase in elevation may be calculated as dY i -dY 2 .
Of specific note in Figure 04 is that two diametrically opposed X-axis (horizontal) input Force Vectors, applied to a plurality of Rolling Load Bearing Elements in a Lower Lattice Tier, are converged by the Lattice Packing into a singular Y-axis output Force Vector, emanating from a singular Roiling Load Bearing Element in an upper tier of the Lattice. The energy from two opposing Force Vectors has been combined into a single Force Vector and the trajectories of said opposing Force Vectors now convergent in a new direction.
As will be demonstrated in the balance of this disclosure, said convergence and redirection of Force Vectors may be harnessed and further manipulated in more evolved embodiments of the current Lattice.
Figure 05 in one of multiple possible embodiments of the current disclosure, Figure 05 presents, in partial cutaway view, a rotary Antifriction Bearing equipped with a multitiered Lattice Packing of Roiling Load Bearing Elements; said bearing being additionally equipped with a non-resilient inner Raceway (2010) and non-resilient outer Raceway (1010); each of said Raceways being integral to an Outer Bearing Member (1000) or inner Bearing Member (2000); each of said Bearing Members being fitted with a plurality of Retentive Anchorages (2012, 1012) into each of which is respectively fitted a Means of Resilient Constraint (2014, 1014). in the upper and lower sectors of Figure 05, portions of said Means of Resilient Constraint (2014, 1014) have been cut away to partially reveal the structure of an interstitially packed, multi-tiered Lattice of Rolling Load Bearing Elements; ail of said Rolling Load Bearing Elements in roiling contact with both resilient (2014, 1014) and non-resilient (2010, 1010) surfaces.
A radially oriented inner Tier of said Lattice Packing is herein represented by Rolling Load Bearing Element 2050 and runs along the curvilinear Z-axis, in a path largely concentric with the rotational axis of the bearing; said Rolling Load Bearing Element herein shown in direct roiling contact with the inner Raceway (2010).
A radially oriented Outer Tier of said Lattice Packing is herein represented by Rolling Load Bearing Element 1050 and runs along the curvilinear Z- axis, in a path largely concentric with the rotational axis of the bearing; said Rolling Load Bearing Element herein shown in direct roiling contact with the outer Raceway (1010). interposed between the two previously described tiers is a third radially oriented Middle Tier of said Lattice, herein represented by Rolling Load Bearing Element 3050; said Middle Tier of the Lattice again running along the curvilinear Z-axis, largely concentric with the rotational axis of the bearing, but in direct rolling contact only with Roiling Load Bearing Elements of said inner and Outer Tiers.
Small arced solid-lined arrows, superimposed over selected Roiling Load Bearing Elements (1050, 3050 and 2050 and other Rolling Load Bearing Elements) near the top and bottom of Figure 05 indicate the counter- rotational, anti-frictional rolling contact between individual Load Bearing Rolling Members of alternate tiers within the Lattice Packing.
Larger arced arrows, superimposed on face of the Outer Bearing Member (1000) at the 10 o'clock and 4 o'clock positions indicate general clockwise rotation of said member relative to Inner Bearing Member (2000).
Vertical Gross Sectional Reference lines, marked with the number 005 near their top or bottom, denote the approximate intersection of Figure 08 within the scope of Figure 05.
Figure 06 Figure 06 presents cross-sectional schematic detail from Figure 05 of ten interstitialiy packed Rolling Load Bearing Elements (1051 , 1050, 2051 , 2050, 2069, 2070, 1069, 1070) comprising an Outer Tier (1051 , 1050, 1069, 1070), inner Tier (2051 , 2050, 2069, 2070); and Middle Tier (3050, 3070) of Rolling Load Bearing Elements. Collectively, said inner, outer and Middle Tiers are bounded in their movement by non-resilient Raceways (1010, 2010) and a respective Means of Resilient Constraint (1013, 1014, 2013 or 2014). The Middle Tier (3050, 3070) of Rolling Load Bearing Elements is bound in its movement exclusively by Rolling Load Bearing Elements in the inner or Outer Tiers.
Collectively, the arrangement of Roiling Load Bearing Elements 1051 , 1050, 3050, 2051 , and 2050 form a multi-tiered, load bearing, and periodic Lattice grouping that, in the embodiment of Figure 05, is repeated every 10 degrees along the bearing's rotational axis; said repeated periodic Lattice grouping forming a coherent but polymorphic Lattice Packing of anti- frictional Roiling Load Bearing Elements throughout the bearing. Two of these periodic Lattice groupings (upper and lower) are visible in Figure 06.
Of specific note in Figure 06 is the partial intrusion (Interstitial Packing) of Middle Tier elements, (herein represented by 3050 and 3070) into the interstitial spacings between Roiling Load Bearing Elements of the Inner and Outer Tiers; said intrusion complemented by the partial intrusion (Interstitial Packing) of inner (2051 , 2050, 2069, 2070) and outer (1051 , 1050, 1069, 1070) tier elements into the interstitial spacings between Rolling Load Bearing Elements of the Middle Tier. Said Interstitial Packing (as herein depicted) maintains not only the roiling contact between elements of proximal tiers, but the cageless separation of Roiling Load Bearing Elements sharing a same tier.
Detail Area Reference 006 in the upper sector of Figure 06 generally demarcates the area of Figure 05 enlarged within Figure 07. Figure 07
Figure 07 presents the area encompassed by Detail Area Reference 006, in Figure 06, and is intended to convey, with greater detail, the predicted range of X-axis / Y-axis movement for individual elements of a 5-member periodic Lattice grouping as it moves in a Z-axis rotational path within two Raceways (2010, 1010) and four Means of Resilient Constraint (1013, 1014, 2013 and 2014).
In Figure 07, dashed line arrows interconnected by a dashed line arc, indicate a range of possible movement for the bearing component over which they are superimposed. As may be noted in Figure 07, there is ample range of movement within the Lattice Packing as it dynamically adapts to loads imposed on upon its Rolling Load Bearing Elements.
It is further evident that Means of Resilient Constraint (1013, 1014, 2013 and 2014) are free to resiliently flex within their Pivotal Anchors (101 1 , 1012, 201 1 and 2012) to accommodate the ebb and flow of dynamic loading. Said Means of Resilient Constraint take form in Figure 07 as a preloaded conical disk springs with approximately 3 degrees of lateral flexure in either direction. Their purpose is to absorb the impact of loads that would otherwise be borne by Rolling Load Bearing Elements, non-resilient Raceways or shock absorptive equipment mounted external to and apart from the bearing.
Other forms of said Means of Resilient Constraint follow in Figures 10, 1 1 , and 13 with the same purpose and utility, if not form, of the current embodiment.
Within elastic limits of the materials from which the Means of Resilient Constraint (1013, 1014, 2013 and 2014) are constructed, any loads imposed on a single Roiling Load Bearing Element are immediately transferred to and absorbed by other Rolling Load Bearing Elements within the Lattice Packing; said Elements partially displacing one another as energy is transferred throughout the Lattice to all other surfaces with which said Lattice is in contact. The energy of said loads are stored within multiple Means of Resilient Constraint (1013, 1014, 2013 & 2014) until cessation of said loads, upon which instance said stored energy is released back into the Lattice Packing.
Broken line polygon D, in Figure 07, demarcates areas presented as alternate embodiments in Figures 10, 1 1 and 13.
Figure 08
Figure 08 presents a topside (parallel to Y-axis) schematic of elements earlier depicted in Figure 07 wherein selected Outer Tier Rolling Load Bearing Elements (1050, 1051 ) have been removed to reveal the underlying packing of Middle Tier (3049, 3050, 3051 ) and Inner Tier (2053, 2052, 2051 and 2050) Roiling Load Bearing Elements , a non-resilient Raceway (2010) and Means of Resilient Constraint (2013, 2014); said components depicted upon an instance of radial loading by divergent Input Force Vector F°as it proceeds downward, away from the viewer, along the Y-axis of the anti-frictional bearing. The main purpose of Figure 08 is to schematically depict the redirection of Force Vectors as they transit throughout the Lattice Packing of Roiling Load Bearing Elements. (For sake of clarity, hatch markings and shading have been kept to a minimum.)
Within the Lattice Packing as presented in Figure 08 Middle Tier Rolling Load Bearing Elements 3049, 3050 and 3051 remain above, but in proximal rolling contact with four Inner Tier Rolling Load Bearing Elements (2053, 2052, 2051 and 2050) where said Middle Tier Elements serve to absorb and transfer working loads from said Inner Tier Rolling Load Bearing Elements while simultaneously maintaining their separation one from another. [96] Laterally placed, on both sides of the Lattice Packing, running parallel to the Zaxis, two Means of Resilient Constraint (2013, 2014) store energy absorbed from Force Vectors F 5 , F s , F 7 and F s ,
[97] Within said packing of Figure 08, Force Vector F Q is radially applied along the Y-axis (away from the viewer) to the top (surface) center point of Middle Tier Roiling Load Bearing Element 3050 from which point said Force Vector proceeds toward the Spherical Center point of said Rolling Load Bearing Element 3050,
[98] Upon reaching proximity with the Spherical Center point of Rolling Load Bearing Element 3050, Force Vector F° is largely redirected into four distinct vectors as Force Vector F 1 , Force Vector F 2 , Force Vector F 3 and Force Vector F 4 ; each of said Force Vectors proceeding in a divergent, but synchronous manner toward a respective Spherical Center point of an inner Tier Roiling Load Bearing Element (2053, 2052 2051 or 2050).
[99] Within Rolling Load Bearing Element 2051 , Force Vector F is angularly diverged into Force Vector F 5 and Force Vector F .
[100] Within Rolling Load Bearing Element 2050, Force Vector F 2 is angularly diverged into Force Vector F 6 and Force Vector F 12 ,
[101] Within Rolling Load Bearing Element 2053, Force Vector F 3 is angularly diverged into Force Vector F 7 and Force Vector F 13 ,
[102] And within Roiling Load Bearing Element 2052, Force Vector F 4 is angularly diverged into Force Vector F s and Force Vector F 1
[103] Of specific note in regards to Figure 08: Force Vector F° originates from a single direction (moving away from the observers point of view) and is ultimately redirected by the Lattice Packing into six angularly divergent Force Vectors. A load exerted on a single Rolling Load Bearing Element is absorbed and redirected by the interstitial Lattice Packing, to surrounding Raceways, Means of Resilient Constraint and other Roiling Load Bearing Elements.
[104] Figure 09
[105] Figure 09 generally presents the same elements of Figure 08 with the notable difference that ail Force Vectors formerly acting upon or within the Lattice Packing have been replaced by reciprocal Force Vectors, now moving in opposite directions to those of Figure 08, and are now designated with a prefix of "K". The main purpose of Figure 09 is to schematically depict the movement of reciprocal Force Vectors as energy stored in a Means of Resilient Constraint (or multiplicity thereof) is returned to the interstitial Lattice Packing of Rolling Load Bearing Elements. (For sake of clarity, hatch markings and shading have been kept to a minimum.)
[106] Within the Lattice Packing presented in Figure 09, Middle Tier Rolling Load Bearing Elements 3049, 3050 and 3051 remain above, but in proximal roiling contact with four Inner Tier Rolling Load Bearing Elements (2053, 2052, 2051 and 2050) where said Middle Tier Elements serve to absorb and transfer working loads from said Inner Tier Rolling Load Bearing Elements while simultaneously maintaining their separation one from another.
[107] Laterally placed, on both sides of the Lattice Packing, running parallel to the Zaxis, two Means of Resilient Constraint (2013, 2014) return previously stored energy to the Lattice Packing, said energy herein represented by reciprocal Force Vectors K 5 , K 6 , K 7 and K 8 .
[108] in the same instance, Roiling Load Bearing Elements 3049 and 3051 return previously stored energy (herein represented by Force Vectors K 15 and K 6 ) from other Roiling Load Bearing Elements in the Lattice Packing (said other Elements herein beyond the scope of Figure 09).
Of significant note in Figure 09:
In Rolling Load Bearing Element 3049, Force Vector K 15 is redirected as Force Vectors K 3 and K 14 .
In Rolling Load Bearing Element 2053, Force Vector K 13 and Force
Vector K 7 converge to become Force Vector K 3 ,
In Rolling Load Bearing Element 2051 , Force Vector K s and Force
Vector K 11 converge to become Force Vector K .
In Roiling Load Bearing Element 3051 , Force Vector K 16 is redirected as Force Vectors K and K 12 .
In Rolling Load Bearing Element 2050, Force Vector K 12 and Force
Vector K 6 converge to become Force Vector K 2 ,
In Roiling Load Bearing Element 2052, Force Vector K 14 and Force
Vector K 8 converge to become Force Vector K 4 .
And in Rolling Load Bearing Element 3050, Force Vectors K 1 , K 2 ,
K 3 and K 4 converge to become Force Vector K° ; said Vector emerging from the top surface of said Element in a direction toward the viewer, directly in the line of sight (with no visible arrow).
Of specific note in Figure 09: reciprocal Force Vectors originating from a six different directions (moving progressively closer to the observers point of view) converge info a single Force Vector, from which point the divergence of Vectors, earlier described in Figure 08 may begin anew.
Taken together, Figures 08 and 09 present a polymorphic Lattice Packing of Rolling Load Bearing Elements highly capable of managing the ebb and flow of dynamic Force Vectors originating or reciprocating from any single Rolling Load Bearing Element within the Lattice [1 12] Description of Embedments [1 13] Figure 10
[1 14] Figure 10 presents elements originally depicted within Detail Reference Area D of Figure 07 (therein demarcated with a broken line polygon), herein equipped with an additional Means of Resilient Constraint (1024) in the form of a conical disk spring, said supplementary Means of Resilient Constraint stacked in line with the original Means of Resilient Constraint (1014). Other elements of Figure 07 (1000, 1010, 1012, 1050 and 3050) retain the same functionality and movement as described in earlier Figures.
[1 15] Figure 11
[1 16] Figure 1 1 presents an alternate embodiment of mechanical elements originally presented within the dashed-iine polygonal area D of Figure 07. In Figure 1 1 , the Means of Resilient Constraint (1014), now takes form as a cantilevered U spring in place of the conical disk spring earlier depicted in Figures 06 through 10. Although changed in form from its former embodiment in Figures 06 through 10, the current Means of Resilient Constraint (1014) retains the same purpose and functionality as the earlier embodiment.
[1 17] Figure 12
[1 18] Figure 12 presents the cross section of a bearing equipped with multi-tiered polymorphic Lattice Packing, similar in overall structure to the bearing of Figure 06, but herein modified to accept the addition of six new complements of Rolling Load Bearing Elements within in each of three z- axis tiers comprising the polymorphic Lattice Packing. [1 19] Non-resilient raceways (1010 and 2010), largely aligned with the (cylindrical coordinate system) Zaxis of bearing rotation, are laterally extended to accommodate said additions. In terms of functionality the bearing of Figure 12 is equal to that of Figure 06, now however with a potentially much greater capacity for the absorption and transmission of loads.
[120] Figure 13
[121 ] Figure 13 presents a sectional view of a multi-tiered polymorphic Lattice Packing of Roiling Load Bearing Elements (herein represented by 1050, 3050, 2050, 1068,
3068, & 2068), two Means of Resilient Constraint (1014, 2014) and two Resilient Raceways (1016, 2016) wherein the form and positioning of certain components has been modified from their earlier embodiments of Figure 06 to now meet the requirements of a rotary roller bearing. All components are depicted in an instance immediately prior to the application of a load, herein represented by Force Vector F°.
[122] in Figure 13, non-resilient raceways (1010, 2010), of earlier embodiments, are now replaced with Resilient Raceways (1015, 2015); said Resilient Raceways and their respective Means of Resilient Constraint preferably fabricated of materials leveraging the full potential of inter-penetrating dilatant polymer composites.
[123] As evident in Figure 13, individual elements of the multi-tiered Lattice of Rolling Load Bearing Elements (represented by 1050, 3050, 2050, 2070, 3070, and 1070) now assume the shape of concave or convex rollers, said rollers collectively serving to facilitate the anti-frictional counter-rotation of an Inner Bearing Member (2000) relative to an Outer Bearing Member (1000).
[124] Figure 14 Figure 14 presents, in an instance immediately following that of radial loading by Force Vector F°, the anti-frictionai roller bearing of Figure 13. in the upper half of Figure 14, it is evident that portions of two Means of Resilient Constraint (1014, 2014), have been compressed within their Retentive Anchorages (1012 or 2012), and that certain outer extremities of Middle Tier Rolling Load Bearing Element (3050) are now occluded from view by Inner and Outer Tier Rolling Load Bearing Elements (2050 and 1050) as the result of Y-axis compression of the Lattice Packing in the lower half of Figure 14 it is evident that portions of two Means of Resilient Constraint (1014, 2014), have expanded within their Retentive Anchorages (1012 or 2012). in the upper half of Figure 14 it is evident that portions of Resilient Raceways (1016 and 2018) have been compressed into a flatter form, whereas, in the lower half of Figure 14 that remaining portions of the same Resilient Raceways have assumed a more arced form.
Of significant note in Figures 13 and 14 is the preservation of a multi-tiered interstitial lattice packing of Rolling Load Bearing Elements, despite an obvious transformation of said elements from spheroidal shape to roller shape. Despite said transformation, the lattice packing in Figures 13 and 14 maintains full capability of adjusting its inner configuration and outer shape in response to loads imposed upon it; the major difference being that, as a roller based embodiment, it now does so mostly along a single Y-axis.
Of equally significant note in Figures 13 and 14 is the radial alignment of multiple Means of Resilient Constraint, directly in line with Roiling Load Bearing Elements; said radial alignment lending significant accommodation to the use of inter-penetrating dilatant polymer composites, amorphous metals or other shock absorbent materials in the fabrication of said Means. Industrial Applicability It is anticipated that the current innovation will find broad application throughout the fields of automotive transport, rail, aerospace, energy production, medical technology, robotics, milling and sporting equipment. In many of such applications, the current disclosure will provide notable improvements in life cycle costs, operational reliability and environmental benefit over prior offerings in the field.