CROSS-REFERENCE TO RELATED APPUCATIONS

This nonprovisional application claims priority to U.S. Provisional Patent Application No. 62/258,142, entitled "Shape-Morphing Space Frame (S SF) Using Unit Ceil Bistable Elements", filed November 20 ^th , 2015 by the same inventors.

FEDERALLY SPONSORED RESEARCH OR DEVELOPMENT

This invention was made with government support under Grant Number 1053958 awarded by the National Science Foundation, The government has certain rights in the invention.

BACKGROUND OF THE INVENTION

1 . Field of the Invention

This invention relates, generally, to space frames. More specifically, it relates to space frames that have the ability to controilably and stably morph between at least two (2) shapes or sizes.

2. Brief Description of the Prior Art

A compliant mechanism is a flexible mechanism that derives some or ail its motion (mobility) from the deflection of flexible segments, thereby replacing the need for mechanical joints. It transfers an input force or displacement from one point to another through elastic body deformation. The absence or reduction of mechanical joints impacts both performance and cost. Advantages include reduced friction and wear, increased reliability and precision, and decreased maintenance and weight [Howell, L. L, 2Q01 , "Compliant Mechanisms", Wiley, New York, ISBN 978-Q471384786], Moreover, cost is also affected by reduced assembly time and, in most cases, due to its hingeless design, the fabrication of such mechanisms can be produced from a single piece. Additionally, compliant mechanisms provide the designer with an effective way to achieve mechanical stability.

A compliant bistable mechanism achieves its stability within the designed range of motion, by storing and releasing strain energy in its compliant segments [Hoetmer, Karin, Herder, Just L and Kim, Charles. "A Building Block Approach for the Design of Statically Balanced Compliant Mechanisms". International Design Engineering Technical Conference San Diego, California, USA, 2009. Vols. DETC2009 87451 ]. Such a technique enables the mechanism to stay at its two stable positions without the need of an external power/force to stay there. Energy methods, combined with pseudo-rigid-body models, can be used to analyze such compliant mechanisms [Howell, L. L., Midha A., and Norton, T. W., 1996, "Evaluation of Equivalent Spring Stiffness for Use in a Pseudo-Rigid-Body Model of Large-Deflection Compliant Mechanisms," ASME Journal of Mechanical Design, 1 18(1):128-131 ]. These mechanisms are most commonly designed in two ways. One is using pseudo-rigid- body models, and the other is using topology optimization. Both approaches have utility. The design of the compliant portion of the unit ceil components is accomplished through compliant mechanism synthesis.

There are three major approaches to the design and synthesis of compliant mechanisms: kinematic approximation methods, computationally intense methods, and linear and higher- order expansions of the governing equations. This disclosure is based primarily upon kinematic approximation methods.

The kinematic approximation or Pseudo-Rigid-Body Model (PRBM) approach works by identifying similarities between compliant mechanisms and rigid-body mechanisms, it has proved effective in identifying numerous compliant analogues to ubiquitous planar rigid-body mechanisms such as four-bar and crank-slider mechanisms. The chief criticisms of this approach are that the models are approximate and have limited, albeit known, accuracy. Moreover, the identification between flexure geometries and rigid-body mechanisms has been limited to a small but versatile set of planar configurations.

Computationally intense approaches typically combine finite element analysis with optimization to calculate optimal geometries in response to load and motion specifications. This approach has been successful, but has also been criticized for producing results identical to those produced more quickly by the PRBIVl approach, or results that are not physically realizable. As a general rule, this approach is more capable and accurate than the PRBIVl approach, but also more time consuming.

The third approach, which relies on linear and higher-order expansions of the governing equations, is well-known in precision mechanisms research, and relies heavily on flexures that are small and undergo small, nearly linear, deflections. This approach uses flexures much smaller than the overall mechanism size, so it is not generally applicable to millimeter- scale and smaller mechanisms. These techniques are important but do not have a direct bearing on the invention disclosed herein.

Systems for subdividing surfaces in the development of finite element algorithms using node definition and degrees of freedom are known. These same subdivisions schemes are applicable to the design of the novel shape-shifting surfaces disclosed hereinafter. The prior art includes techniques for node placement in a given shape. For example, in Finite Element models, the behavior between nodes is typically determined by interpolating functions. In the multi-stable shape-shifting system disclosed hereinafter, a kinematic scheme is required to fill the gaps between nodes. Thus, kinematic skeletons are developed which have the same number of nodes (typically revolute joints) and the same number of degrees of freedom. Methods for enumerating all possible kinematic linkages with a given number of degrees of freedom are known. The simplest systems satisfying degree of freedom requirements are preferred. For example, triangular elements with additional nodes along the edges and center-point nodes are known.

Tiling systems, periodic and aperiodic, are methods for subdividing surfaces and as such have been extensively studied by mathematicians and artists since antiquity. The three regular tilings are: 1) equilateral triangles only, 2) squares only, and 3) regular hexagons only. There are eight Archimedian tilings, and there are aperiodic Penrose kite-arid-dart tiling systems. The regular tilings are simple and require the fewest different types of unit cells. Some of the Archimedian tilings use polygons with several sides, yielding generous angles and areas to work with, which may be advantageous. Penrose tiles are specifically shaped quadrilaterals that can be assembled in multiple, non-periodic ways.

In 1827, Carl Fredrich Gauss published his Theorema Egregium' which is the foundational result in differential geometry. The basic result is that small triangles do not change their shape when bent and that there is a fundamental difference in the shape of triangles that are planar (the sum of the angles is equal to 180 degrees) and the shape of triangles on a sphere (the sum of the angles is always more than 180 degrees) and the shape of triangles on a hyperbolic or saddle-shaped surface (the sum of the angles is always less than 180 degrees). His result means that spheres cannot be made into planes without crumpling or tearing or stretching (distorting) the surface. This fundamental geometric limitation makes the building of certain types of curved surfaces (those with two non-zero principal curvatures) intrinsically more difficult than working with planar surfaces (both principal curvatures equal to zero) or developable surfaces (one principal curvature equal to zero).

A surface is defined as a material layer constituting such a boundary. Examples of this are walls, ceilings, doors, tables, armor, vehicle bodies, etc. However, in some cases, it may be valuable for these surfaces to change shape while still maintaining rigidity in the direction normal to the surface. In addition, having surfaces able to change between two different sizes on demand and stabilize in those sizes may be of even more value. One valuable application of size changing surfaces may be rigid containers, for example milk crates, trash barrels, dumpsters, laundry baskets, suit cases, truck beds, freight trains, trash compactors, etc. Such containers are designed for large volumes, however, when not in use, may become cumbersome. Thus, containers with large volumes when in use and small volumes when empty are of value. This includes the ability for containers to maintain large or small sizes both when in use and when empty.

This leads to a need for innovation that allows conventional surfaces to achieve new functionality, to be constructed more precisely, or at lower cost. More particularly, a low-cost modular building system with customizable DOF and stiffness with stability in multiple positions is needed, in addition to potential savings when a new barrier is erected, an innovative system would provide new methods and functionality to surfaces and objects. Objects that function as physical barriers or supporting surfaces include walls, fable tops, shelves, floors, ceilings, stairs, vehicle bodies, and pipelines. Conventional methods for constructing these barriers can be costly, but even when they are inexpensive, the numbers of these kinds of objects mean that they represent a significant economic investment. Such barriers often incur additional costs when they require modification or removal. Thus there is a need for a surface, and a method for designing such surface, having a shape that may be modified or adjusted without damaging the surface or rebuilding it, and that has stability in multiple positions or shapes.

Space frames are widely used in structures (roof structure for example) with complex geometries that involve heavy computations and optimization using genetic algorithm. However, there is no current ability to provide bistability to space frames in a predictable and controllable manner.

Accordingly, what is needed is an improved structure and methodology for providing predictable and controllable structural change using unit cell bistable elements, thus allowing the morphing of one specific shape into a different specific shape. However, in view of the art considered as a whole at the time the present invention was made, it was not obvious to those of ordinary skill in the field of this invention how the shortcomings of the prior art could be overcome.

While certain aspects of conventional technologies have been discussed to facilitate disclosure of the invention, Applicants in no way disclaim these technical aspects, and it is contemplated that the claimed invention may encompass one or more of the conventional technical aspects discussed herein.

The present invention may address one or more of the problems and deficiencies of the prior art discussed above. However, it is contemplated that the invention may prove useful in addressing other problems and deficiencies in a number of technical areas. Therefore, the claimed invention should not necessarily be construed as limited to addressing any of the particular problems or deficiencies discussed herein.

In this specification, where a document, act or item of knowledge is referred to or discussed, this reference or discussion is not an admission that the document, act or item of knowledge or any combination thereof was at the priority date, publicly available, known to the public, part of common general knowledge, or otherwise constitutes prior art under the applicable statutory provisions; or is known to be relevant to an attempt to solve any problem with which this specification is concerned.

BRIEF SUMMARY OF THE INVENTION

The long-standing but heretofore unfulfilled need for an improved bistable mechanism and method of fabrication thereof is now met by a new, useful, and nonobvious invention. In an embodiment, the current invention is a shape-morphing space frame apparatus using unit cell bistable elements. The apparatus includes a first structural framework (P i) formed of nodes and links, including at least one bistable link. The Pi framework has two stable positions, a parallelogram-shaped (e.g. , rectangular) constraint in one position and a trapezoidal (e.g. , isosceles trapezoidal) constraint in the other position. The apparatus further includes a first set of second structural frameworks (P2) and a second set of second structural frameworks (P3). The P2 and P?, frameworks are each formed of nodes and links, including at least one bistable link. The P2 and P3 frameworks each having two stable positions, a parallelogram-shaped (e.g., square-shaped) constraint in one position and a trapezoidal (e.g. , isosceles trapezoidal) constraint in the other position. The P2 frameworks are adjacent to each other, as are the P3 frameworks. They are straight or curved in one stable position, and curved in the other stable position. The P2 frameworks are coupled on an end to an end of the Pi framework, and the P3 frameworks are coupled on an end to an opposite end of the Pi framework. The P2 and P3 frameworks are also coupled to each other on their opposite ends, thus forming a straight or curved triangular prism in the first stable position and a curved triangular prism in the second stable position (e.g., without any use of curved links). Bistabiiity is achieved by the bistable links in each of the frameworks and without use of any hard stop. In certain embodiments, the links of each framework can be disposed within in a single plane within each framework, so that none of the links interfere with each other within the framework.

A single rigid links may be positioned between two nodes if a relative displacement between the nodes is zero. On the other hand, two or more rigid links can be positioned between the two nodes if the relative displacement between the two nodes is coliinear, where the node disposed between the two rigid links would be a living hinge.

One of the stable positions may be a disk configuration, and the other stable position may be a hemisphere configuration, in this case, the radial lines on the surface of the disk bend but do not stretch, and become the longitude lines on the hemisphere. Additionally, the circumferential lines on the disk compress and become latitude lines on the hemisphere, in a further embodiment, the transition between the stable positions can be accomplished by applying an inward radial force on the P? and P3 frameworks. In an embodiment, the disk configuration can be formed of ten (10) sectors connected together in a circular pattern as one layer, in this case, the links would not include any curved links.

Alternatively, one of the stable positions can be a two-layered disk configuration, and the other stable position can be a sphere configuration, where the disk has an upper layer that forms an upper hemisphere and a lower layer that forms a lower hemisphere (thus forming the overall sphere, such as a 80-sided polyhedron without any curved links). In an embodiment, the upper and lower layers can each be formed of an odd number of evenly- spaced sectors with a gap formed between each sector. The sectors would window each other to fill the gaps in the two-layered disk. Further, the upper and lower layers can be coupled together using the sectors' vertices located mid-plane, where a flange can be disposed at each vertex with an aperture disposed therein to function as a hinge between the layers.

In a separate embodiment, the current invention is a method of fabricating predictable and controllable length or shape changes in a bistable, shape-morphirig mechanism, allowing the morphing from an initial specific shape into a resulting specific shape that is different from the initial shape, without use of a hard stop. The method includes identifying the stable shapes desired and providing a plurality of links and nodes that interconnect the links in the initial shape (the links should not change length between the shapes). The nodes include fixed ground pivots and moving pivots (e.g. , torsional springs may be placed at these moving pivots), and the links include fixed links and moving links. A first attachment point of a non- interfering potential energy element (PEE; e.g. , a compliant link) is identified to be positioned on a fixed link, and a first attachment point of PEE is identified to be positioned on a moving link. These attachment points are based on a path of travel of the PEE between the stable shapes. The PEE is positioned between two moving pivots to provide a degree-of-freedom during actuation of the mechanism between its stable shapes. The potential energy of the PEE is minimized in these stable shapes, and increases during transition between these shapes. The PEE is capable of generating sufficient potential energy to overcome any restoring torques within the moving pivots when transitioning between the stable shapes. Based on the foregoing steps, the bistable, shape-morphing mechanism can be fabricated, for example by laser cutting or three-dimensional printing.

The methodology may further include over-constraining the mechanism to facilitate behavior of the mechanism as a structure in both stable shapes with sufficient flexibility in the PEE to transition or toggle between the shapes.

The methodology may also include creating a pole point at an intersection between two perpendicular bisectors. The first bisector would originate from a line disposed between a first moving pivot in the initial shape and that same pivot in the resulting shape. The second bisector would originate from a line disposed between a second moving pivot in the initial shape and that same pivot in the resulting shape. These bisecting lines would then intersect each other, and that is where the pole point is created. The pole point also bisects a path of travel of the PEE.

These and other important objects, advantages, and features of the invention will become clear as this disclosure proceeds.

The invention accordingly comprises the features of construction, combination of elements, and arrangement of parts that will be exemplified in the disclosure set forth hereinafter and the scope of the invention will be indicated in the claims.

BRIEF DESCRIPTIO OF THE D AWIMGS For a fuller understanding of the invention, reference should be made to the following detailed description, taken in connection with the accompanying drawings, in which:

Figure 1 A depicts a general disk-to-sphere geometry.

Figure 1 B depicts a more specific disk-to-sphere geometry without use of curved link mechanisms.

Figure 2 is a top view of the three ten-sided polygons (lengths are in mm).

Figure 3 depicts the constructed wireframe for the polygon's sector with notations.

Figure 4 depicts the sector's wireframe back surface shown from the side view.

Figure 5 depicts the morphed sector's wireframe.

Figure 6 depicts the quadrilateral structure in its 2D and 3D form.

Figure 7 depicts the triangular structure in its 2D and 3D form.

Figure 8 shows the 1 1 planes needed to construct the sectors structure.

Figure 9 shows the nodes and planes in (a) sector, (b) wedge.

Figure 10A depicts the initial and final state of a generalized Pi mechanism.

Figure 10B depicts the initial and final state of a generalized P2 mechanism.

Figure 1 1 A depicts rigid links and nodes in a generalized Pi mechanism.

Figure 1 1 B depicts rigid links and nodes in a generalized P2 mechanism.

Figure 12A depicts a conventional four-bar isomer for one-DOF mechanism.

Figure 12B depicts a conventional six-bar isomer for one-DOF mechanism.

Figure 12C depicts a conventional six-bar isomer for one-DOF mechanism.

Figure 13A depicts a boundary of the Pi mechanism, (a) boundary, (b) without constraints, (c) constrained.

Figure 13B depicts a Pi mechanism without constraints.

Figure 13C depicts a constrained Pi mechanism.

Figure 14A depicts a conventional isomer of an eight-bar mechanism.

Figure 14B depicts a conventional isomer of an eight-bar mechanism.

Figure 14C depicts a conventional isomer of an eight-bar mechanism.

Figure 14D depicts a conventional isomer of an eight-bar mechanism.

Figure 14E depicts a conventional isomer of an eight-bar mechanism.

Figure 14F depicts a conventional isomer of an eight-bar mechanism. Figure 14G depicts a conventional isomer of an eight-bar mechanism.

Figure 14H depicts a conventional isomer of an eight-bar mechanism.

Figure 141 depicts a conventional isomer of an eight-bar mechanism.

Figure 14J depicts a conventional isomer of an eight-bar mechanism.

Figure 14K depicts a conventional isomer of an eight-bar mechanism.

Figure 14L depicts a conventional isomer of an eight-bar mechanism.

Figure 14M depicts a conventional isomer of an eight-bar mechanism.

Figure 14N depicts a conventional isomer of an eight-bar mechanism.

Figure 140 depicts a conventional isomer of an eight-bar mechanism.

Figure 14P depicts a conventional isomer of an eight-bar mechanism.

Figure 15 depicts P schematics with eight-bar mechanism and links' notation.

Figure 16 depicts the P final mechanism in its initial and final state.

Figure 17 depicts the P mechanism's movement using five different translationai positions.

Figure 18A depicts the P mechanism as an outline.

Figure 18B depicts the P mechanism in transition from an outline to a fully compliant mechanism.

Figure 18C depicts the P mechanism as a fully compliant mechanism.

Figure 19 shows the sub-section of P2 for synthesis.

Figure 20A shows the boundary of a P2S1 mechanism.

Figure 20B shows the boundary of the P2S1 mechanism fitted Stephenson's six-bar isomer. Figure 21 depicts Stephenson's six-bar isomer in graph theory.

Figure 22A depicts a step in converting a five-bar mechanism into a zero-mobility mechanism.

Figure 22B depicts a step in converting a five-bar mechanism into a zero-mobility mechanism.

Figure 22C depicts a step in converting a five-bar mechanism into a zero-mobility mechanism.

Figure 22D depicts a step in converting a five-bar mechanism into a zero-mobility mechanism. Figure 23 depicts P2S1 schematics with seven-bar mechanism and links' notation.

Figure 24A depicts the P2S1 mechanism as an outline.

Figure 24B depicts the P2S1 mechanism in transition from an outline to a fully compliant mechanism. Figure 24C depicts the P2S1 mechanism as a fully compliant mechanism.

Figure 25A depicts the Pi mechanism in its first stable position .

Figure 25B depicts the Pi mechanism in its second stable position .

Figure 26A depicts the P2 mechanism in its first stable position .

Figure 26B depicts the P2 mechanism in its second stable position,

Figure 27A depicts the sector's mechanism in initial state.

Figure 27B depicts the sectors mechanism in final state.

Figure 28A depicts actuation of the sector's wireframe from the initial position .

Figure 28B depicts actuation of the sector's wireframe from during transition from the first position to the second position.

Figure 28C depicts actuation of the sector's wireframe in a second position.

Figure 29 depicts a one-disk SMSF apparatus actuation.

Figure 30A is an isometric view of a two-disk SMSF initial state.

Figure SOB is a top view of a two-disk SMSF initial state.

Figure 31 A is an isometric view of a two-disk SMSF final state.

Figure 31 B is a top view of a two-disk SMSF final state.

Figure 32A is a top view of a modified sector's mechanism.

Figure 32B is an isometric view of a modified sector's mechanism.

Figure 33 depicts force-displacement curves and zone identification .

Figure 34 depicts the second stable position depends on spring location and first position. Figure 35A depicts the mechanism's two stable position as design input.

Figure 35B depicts the mechanism's two stable position as design input.

Figure 36 depicts the mechanism's pole point for (/ ₂ ).

Figure 37 depicts ternary link representation of the coupler link to place the point (m _Q ).

Figure 38 shows the PEE representation as (/ _Q ) with the point (Q).

Figure 39 depicts the perpendicular bisector the point (/TSQ) connected to the pole point (P).

Figure 4QA is a links display depicting the first zero-stress path of the point (mq) following the coupler curve.

Figure 4QB is a line representation depicting the first zero-stress path of the point (m ₀ ) following the coupler curve. Figure 41 depicts the second path of the point (/?¾) as an arc.

Figure 42 depicts the PEE in a compressed deformation.

Figure 43 depicts the PEE in an elongated deformation.

Figure 44 depicts Pi 's mechanism splits into two four-bar mechanism.

Figure 45 depicts the mechanism of P i 's left and right halves at both stable positions.

Figure 46 depicts Pi 's right half at both state with the pole point (P) identified

Figure 47 depicts PEE placement with its point (Q) placed on the ground link (/ ₂ ).

Figure 48 depicts the limits of points (ma), (m'o) and (Q) on the mechanism.

Figure 49 depicts eight different coupler curves generated for (/?¾) within its limits.

Figure 50A depicts the superimposed two paths of (m _Q ) for a selected coupler curves.

Figure SOB depicts the superimposed two paths of (m _Q ) for a selected coupler curves.

Figure 50C depicts the superimposed two paths of (m ₀ ) for a selected coupler curves.

Figure 50D depicts the superimposed two paths of (m _Q ) for a selected coupler curves.

Figure 51 A depicts the Pi mechanism with mobility of one.

Figure 51 B depicts the Pi mechanism with mobility of (-1 ).

Figure 52A depicts a parallelogram linkage at a toggled position.

Figure 52B depicts a parallelogram linkage at a toggled position.

Figure 52C depicts a parallelogram linkage at a toggled position.

Figure 53A depicts the mechanism where the PEE experiences tension.

Figure 53B depicts the mechanism where the PEE experiences compression.

Figure 54 depicts a finalized mechanism, according to an embodiment of the current invention or using an embodiment of the current invention.

Figure 55A depicts an apparatus at its initial state.

Figure 55B depicts an apparatus at its intermediate state.

Figure 55C depicts an apparatus at its final state.

Figure 56 depicts FEA analysis of the mechanism at the unstable position.

Figure 57 depicts FEA analysis of the mechanism at the second stable position.

Figure 58 depicts the initial state mechanism's constraints of P-i S SF.

Figure 59 depicts the final state mechanism's constraints of Pi SMSF.

Figure 60 depicts the Pi SMSF mechanism's design dimensions (without bistability). Figure 81 depicts the initial state mechanism's constraints of P2 SMSF,

Figure 82 depicts the final state mechanism's constraints of P2 SMSF.

Figure 83 depicts the P2 SMSF mechanism's design dimensions.

Figure 64 depicts the left half PEE design dimensions of Pi SMSF.

Figure 65 depicts the Pi S SF mechanism's design dimensions (with bistability).

Figure 66 depicts the parallel four-bar bistable mechanism's initial layout dimensions.

Figure 67 depicts the parallel four-bar bistable mechanism's intermediate dimensions.

Figure 68 depicts the parallel four-bar bistable mechanism's living hinges dimensions.

DETAILED DESCRIPTIO OF THE PREFERRED EMBODIMENT

In the following detailed description of the preferred embodiments, reference is made to the accompanying drawings, which form a part thereof, and within which are shown by way of illustration specific embodiments by which the invention may be practiced. It is to be understood that other embodiments may be utilized and structural changes may be made without departing from the scope of the invention.

As used in this specification and the appended claims, the singular forms "a", "an", and "the" include plural referents unless the content clearly dictates otherwise. As used in this specification and the appended claims, the term "or" is generally employed in its sense including "and/or" unless the context clearly dictates otherwise.

In certain embodiments, the current invention includes unit cell bistable elements, and particular arrangements and uses thereof, that can transform or morph a structure from one shape to another, in an embodiment, the current invention provides a method/ability to transform any four-bar compliant mechanism into a bistable compliant mechanism. It is an object of the current invention to facilitate structures morphing from one specific shape to another specific shape using unit cell bistable elements.

Example 1 - Slhape-IV!orp ssrig Space Frame (SIVISF) Using Quadrilateral Bistable Unit Cell Elements

As a proof of concept, which is described in the following non-limiting example, a disk-like structure is morphea! into a hemisphere or spherical structure. This mechanism can be applied to alternative shapes to provide for structural change from one specific shape to another specific shape.

L Proof of Concept: Designing and Modeling

An objective of this study was to design a disk like structure with the ability to morph into a sphere. Specifically, the circumference of a disk structure is approximated by a 10-sided polygon that would then morph into a hollow sphere structure that is approximated by a 60- sided polyhedron. However, it is contemplated herein that the circumference of the disk structure can be approximated by any number of sides greater than or equal to three (3) in this 10-sided embodiment, though , the disk-to-sphere structure is tessellated into ten (10) sides for the latitude circles and twelve (12) sides for the longitude circles; the disk's thickness and radius are preset/chosen at the initial design stage. The strategy in morphing the initial shape of the structure (disk) into its final shape (sphere) is that the radial lines on the surface of the disk bend but do not stretch, whereas the circumferential lines compress. Moreover, the radial lines on the disk become longitude lines on the sphere, and the circumferential lines become latitude lines on the sphere. The disk's thickness splits in half, the upper half becoming the thickness of the upper hemisphere and the lower half becoming the thickness of the lower hemisphere. The following discuss the steps used in disk tessellation and the detailed morphing strategies.

A. Disk Tessellation

Because the disk has a given thickness, the projection of it, which is a circle, is tessellated. To better understand the topology involved in morphing the disk into a hemisphere, geometrical analysis was carried out using the known equations of circles and spheres by correlating them to each other using their parameters shown in Figure 1 A.

As it was stated before and to avoid using curved link mechanisms, polygons will be used to approximate the circles that construct the disk as shown in Figure 1 B. Using polygons to approximate circles allows the use of straight link segments to form the mechanism and provides for a manner of refining the design by increasing the number of sides, increasing the number of sides (i.e. , at least 3 sides) would refine the circle approximation and would also increase the number of unit cells and increase the complexity of the design, and vice versa. The following are the steps used to construct the disk tessellation using the computer aid ed design software SOLIDWORKS, though other CAD software may be utilized as well ; dimensions used are also noted to illustrate how those parameters affect the final design. Step 1 : A regular ten-sided polygon is used with a circumscribed circle radius (R _c ) of 150 mm was chosen, though any radius length can be used .

Step 2: in order to make the polygon's structure manageable, two smaller ten-sided polygons were constructed inside one another with a difference of 50 mm, as shown in Figure 2, though any number of polygons, any number of polygonal sides, and any preselected differences therein are contemplated herein as well. Increasing the number of intermediate polygons will refine the hemisphere's outer curvature.

Step 3: A design choice of 50 mm was given to the disk's half thickness (to be consistent with the three polygons' offset dimension) and, by connecting the nodes (the vertices of the polygons) by straight lines; a polygon sector can be constructed as shown in Figure 3. Other suitable thicknesses are within the skill of one in the art as well. The polygon can have fen (or at least 3) identical sectors and, for clarity, only one is shown along with lines notation. Step 4: A design choice at this stage can be made as in which of the lines should be variable and which should be fixed in length. The thickness of the disk-to-sphere structure is considered to be fixed in this design example; thus, the lines 82, a+, bi, b , C2, <¾, and d i , shown in Figure 3, are equal 50 mm. Figure 4 shows the side view of the sector's backside wireframe after morphing; the radius of the hemisphere (R _s ) can be determined geometrically. As mentioned before (the radial lines on the surface of the disk bend and do not stretch), the lines abs, bC3, and ccb, shown in Figure 3, would bend to approximate half arc, and lines aba, box, and ccfe would behave similarly. Because those three lines are considered equal to one another and fixed in length (50 mm), the outside radius of the circumscribing hemisphere would be 96.59 mm or other suitable length.

Step 5: After the determination of the hemisphere radius, another ten-sided polygon is drawn on the top view that is in Figure 4 with a circumscribed circle radius (R _s ) of 95.49 mm or other suitable length. The nodes are then connected together forming the morphed sector as shown in Figure 5.

Step 6: Having the wireframe's sector in its two positions (before and after morphing), Table 1 is constructed showing the different non-limiting dimensions of each link between the initial and final shape. Moreover, given this data, it can be analyzed how TA and TB (see Figure 3) can morph from a trapezoidal prism to a quadrilateral-base pyramid; similarly, it can be analyzed how TC (see Figure 3) can morph from a triangular prism to the triangular-base pyramid. The morphing strate ies involved will be discussed as this specification continues.

Table 1 . The non-limiting wireframe dimensions in the initial and finai state of the sector.

B. Morphing Strategies

Herein, analysis is carried out on how a trapezoidal prism can be morphed into a quadrilateral-base pyramid and how a triangular prism can be morphed into a triangular-base pyramid. To understand the problem with clarity, working with a regular three-dimensional wireframe, such as a cube instead of the trapezoidal prism, may provide a general insight on the degrees-of-freedom (DOF) and what parameiers are involved to control the movements of each link within the wireframe. Previously, it was explained that a quadrilateral two- dimensional frame formed of six links (four sides and two diagonal) will have (-1 ) DOF: thus, only five links are needed to fully define the frame , making it a structure with zero DOF and leading to the method of five chose n or ( ⁵ ) , which was discussed fully in [Alqasimi, A., and

Lusk, C , "Shape-Morphing Space Frame (S SF) Using Linear Bistable Elements" in Proceedings of the 2015 Design Engineering Technical Conferences & Computers and Information in Engineering Conference, Boston, MA, Aug 2-5, 2015. DETC2015-47526]. Following the similar method, the same five links are used (four sides and a diagonal) but in this case it extends to the third dimension by giving it a depth as shown in Figure 6.

The mobility equations will remain the same as the planar case because ail the pin joints and links are coilinear. The method of five chose n or ^ is also applicable in this situation, where n is the number of surfaces thai need to change length. The analysis of the cube can be extended to the trapezoidal prism because it is a special case from where two opposite surfaces are inclined inward or outward from one another.

In the case of the triangular prism, the two-dimensional aspect shows that if three links were connected in a loop with three pin joints between each link, it will result in a structure with zero DOF. Adding a third dimension by giving it a thickness will result in three surfaces connected in a loop with three hinges; it is also a structure as shown in Figure 7,

From Figure 3, the chosen sector includes three (3) segments in which TA and TB is a trapezoidal prism sharing a surface, and TC is a triangular prism sharing one surface with the TB. Figure 8 shows the 1 1 different surfaces needed to construct the sector out of ten sectors. Analyzing the sector in general, it can be considered as one large triangular prism in which only three surfaces can be used to construct it, eliminating the need for the intermediate surfaces and reducing it from 1 1 to 3, though any number of surfaces is contemplated herein as long as the surfaces can form a structure. Regardless of whether the surfaces are curved or planar, the triangular prism sector can remain a structure before and after the morph, as shown in Figure 9. The kinematics involved in constructing the surface on one hand and its compliancy on the other hand, will be analyzed based on each segment's individual morph behavior.

JL Mechanism Synthesis

The mechanism synthesis involved in morphing the planes is investigated using kinematic graphic design. Because the sector in Figure 9 is composed of three surfaces (Pi , P∑, and P3) , where P2 and P3 are similar in design and behavior, controlling the nodes (ni to ne) via a compliant mechanism allows the required relative displacement between the nodes, as in the form of length change for each link (see Table 1). it is possible to solve this problem using the linear bistable link elements (LBCCSM), which results in a more complex spatial mechanism with its associated DQF and increases the number of elements needed for assembly. Using the concept of a cell element reduces the number elements needed for the design and assembly. Figures 10A-10B illustrate the area of the unit cell in which a mechanism connecting the nodes (vertices) should fit, morphing Pi from a rectangular to a trapezoidal ceil element ΡΊ (Figure 10A), and P2 from a rectangular to an arched rectangular ceil element P'2 (Figure 10B). A minimum of four (4) extra intermediate nodes are added for P2 and P3 corresponding to the disk tessellation described previously. Four (4) extra nodes are used because two (2) smaller polygons were chosen; as such, as it can be understood that in other embodiments, if three (3) smaller polygons were chosen, for example, then six (6) extra nodes can be used.

Hi. Type and Dimension Synthesis

Identifying the unit cell's initial and final state was a key step in the mechanism type selection process. Summarizing the information from Figure 3, Figure 9, and Figure 10, along with Table 1 into Table 2, guided the mechanism type selection in terms of design choices and constraints.

Table 2. The non-limiting dimensions involved in FIGS. 1 QA-1 QB.

The mechanisms' parameters from Table 2 are written in the form of constraints as follows:

* Constraint #1 for Pi : The relative displacement between nodes (m , m) and (¾, ru) should be zero in this example. However, in other embodiments and based on different Pi designs, the nodes can have relative displacement between each other.

® Constraint #2 for Pi : The relative displacement between nodes (n i , ¾) and (m, ru) should be collinear and toward each other in this example. However, in other embodiments and based on different Pi designs, the nodes can have relative displacement between each other in any other direction.

* Constraint #3 for P2 and P3: The relative displacement between each consecutive node should be zero except between nodes (nz, 12), (12, 14), and (U, ne) which should be collinear and toward each other in this example. However, in other embodiments and based on different P2 and Ps designs, the nodes can have relative displacement between each other.

® Constraint #4 for ail the nodes: If the relative displacement between two nodes is zero (no length change), then a single rigid link can be used to connect both nodes. Two or more rigid links can be used to provide a link between nodes that have collinear relative displacement (collinear length change between nodes); therefore, a minimum of one extra node should be introduced between the original two nodes. Figures 1 1 A- 1 1 B show the rigid links and identifies the minimum number of external nodes for each mechanism within Pi (Figure 1 1 A) and P2 (Figure 1 1 B). A minimum of six external nodes for Pi and five external nodes for P2 were used in the mechanism, though the minimum number of external nodes can be different based on different Pi and P2; those nodes are translated to be living hinges connecting the compliant links in this example. However, in other embodiments, the nodes can be understood to be any type of connection.

® Constraint #5: The mechanism should be contained within the assigned surfaces (Pi , P2 and P3) and its links should not interfere with each other, i.e. , links should not cross to enable single plane fully compliant manufacture. However, in other embodiments, such as multi-plane or multi-layer mechanisms, links can cross.

Furthermore, a one-DOF mechanism can be considered because the mechanism is the unit cell, and to reduce the number of actuators required to control the overall design. An optional constraint is the ability to laser cut the mechanism from a single sheet of polymer; this requires the mechanism to be planar and single layer. Solving the kinematic equations for an unknown mechanism, where only the initial and final state of four of its nodes is given, turns the problem into a mechanism synthesis. Furthermore, solving for the links' shape, interferences, overlapping, and the containment of the mechanism within a specific footprint requires extensive formulation and coding.

A. The Synthesis of Pi

For proof of concept, the approach followed in solving this design problem for Pi was simplified by the use of existing mechanisms and the use of SOLIDWORKS CAD software. From the Design of Machinery [Norton , R. , "Design of Machinery", McGraw-Hill Education Material, 5 ed. 201 1 , ISBN 9780077421717], the number of singie-DOF mechanism and its valid isomers possible for the four-bar, six-bar, eight-bar, ten-bar, and twelve-bar linkages are, respectively, 1 , 2, 16, 230, and 6856. Analyzing each isomer as a potential solution was done both deductively and via SOLIDWORKS. Figures 12A-12C show the four-bar and six-bar isomers for one-DOF mechanism.

If four of the outside pin joints of the mechanism are considered to be the nodes of Pi , then the four-bar mechanism cannot be utilized because its fixed length sides do not allow the change from rectangle to trapezoid (Figure 12A) . in the Stephenson's six-bar isomer, Figure 12B, there are five outer nodes, which violate constraint #4, which calls for a minimum of six outer nodes for it to satisfy Pi design, as shown in Figure 1 1 . in Watt's six-bar isomer in Figure 12C, there are six outer nodes, which satisfy the minimum nodes requirement in constraint #4. There are three ways to arrange those nodes.

The first arrangement involves taking nodes (J2, Ji), shown in Figure 12C, as (ni , ), shown in Figure 10, and (J4, Js) as (nz, ru) which does not satisfy constraint #2 due to its scissor type motion between (Ji , Js) and (J2, J4) , where one moves inward forcing the other to move outward . The second arrangement involves taking nodes (J i , Je) as (ni , ) and (J3, J4) as ¾, n- , which satisfies constraint #1 , #2 and #4. The satisfaction of the 5 ^ih constraint can be verified graphically by means of the CAD software using the following steps:

Step 1 : The initial and final state of the mechanism is drawn using the dimensions provided in Table 2, as shown in Figure 13A. The solid lines represent rigid links, and the broken lines are drawn to represent the area where the mechanism should be contained.

Step 2: Drawing the rest of the links' schematic according to Figure 12C without any dimensions or constraints on both Pi and ΡΊ , as shown in Figure 13B. Step 3: Using a feature in SOLIDWORKS that ai!ows the selection of two lines and constrain them to be equal is carried out between each link in Pi and the corresponding link in ΡΊ , as shown in Figure 13C . This is an effective way to figure out the dimensions associated with each link without solving for the kinematic equation.

Step 4: The constructed mechanism is then manipulated in SOLIDWORKS to fit within the assigned area in both states.

The result of this second arrangement violates constraint #5, as shown in Figure 13C, as the length of the dotted link is not the same between Pi and the corresponding link in ΡΊ . At the current length, the mechanism is contained within the assigned area , but once the final equal link constraint is added, the mechanism is driven out of bound. The third arrangement is a mirror of the second and also violates constraint #5; thus, both isomers of the six-bar mechanism with one DOF were not used in the design of this example. However, in other embodiments and based on different Pi designs, six-bar isomers can be utilized in the design.

For the reason that neither the four-bar nor the six-bar mechanisms satisfied the required constraints, the eight-bar mechanism with its 16 isomers, shown in Figure 14A-14P, were analyzed individually using the same methodology and reduced according to the following two observations:

1 ) isomers with less than five outer nodes were eliminated in this example, shown in Figure 14E, 14G, and 14P. However, in other embodiments and based on different Pt designs, it can be understood that isomers with less than five outer nodes can be utilized in the design.

2) Isomers with quaternary link, which is the link that connects to other links at four nodes, shown in Figure 14F, 14H, 141, 14J, 14K, 14L, and 14 , were eliminated in this design example, due to the extra constraints needed in SOLIDWORKS to match the initial and final state of the mechanism , unlike the ternary link where fixing its three sides fixes the link. However, in other embodiments and based on different Pi designs, these isomers can be utilized in the design.

After studying the remaining isomers shown in Figure 14A, 14B, 14C, 14D, 14N, and 140, it was concluded that the isomer of FIG. 14A can provide the solution to the given problem , of this design example, satisfying all the constraint and dimensions required by the design. This solution will be discussed thoroughly. However, in other embodiments and based on different Pi designs, it should be understood that the remaining isomers can be utilized in the design.

Figure 1 5, with reference to Figure 14A, shows the results after following the four steps involved in the 2 ^nd arrangement of Watt's six-bar isomer, where the five constrains were verified and met in this design arrangement. To fully define the sketch in SOLIDWORKS, Table 3 illustrates the additional non-limiting constraints added to the lines in both Pi and

P'1 .

Table 3. Pi with non-limiting constraints of an eight-bar mechanism.

Figure 16 shows the fully defined mechanism's arrangement, and at this stage of the design, ail the lines are considered rigid links and all the nodes are pin joints. On that note, Figure 17 illustrate the mechanism's movement using five different translationai positions from its initial state in Pi to its final state in P'1 .

The final stage of the design involves converting the mechanism's linkages to compliant segments where the pin joints are replaced with flexurai pivots. The design of those flexural pivots was done in SOLIDWORKS to meet the laser cutter's limitations. Figures 18A-1 8C show the development of the design from the concluded outline of the mechanism in Figure 18A to the complete design in a compliant form in Figure 18C; the full dimension of this design is shown in Figures 69-71 . The bistabiiity analysis for this design will become clearer as this specification continues.

It should be noted that some of the disqualified isomers can work for small length change between nodes (ni , and (m, m), and as such are contemplated by the current invention as well.

B. The Synthesis of P ₂ and P ₃ The synthesis of the remaining two pianes P2 and P3 of the sector in Figure 9 is described herein. Because the planes are identical, the analysis of one plane can be applied to the other without any modification. In order for P2 to change its initial state from rectangular to an arched rectangular cell element P'2, it was divided into three equal parts as per the disk tessellation described previously. Referring to Table 2 and constraint #3 for P2 and P3 that state "the relative displacement, between each consecutive node should be zero except between nodes (n2, i2), 2. 14) and (14, ηβ) should be collinear and toward each other", a minimum of one extra node should be placed between the nodes with collinear displacement. The analysis of P2S1 section, shown in Figure 19, is performed as an individual unit ceil and can be applied to the rest of the two sections P2S2 and P2S3- The four-bar mechanism cannot be applied due to its four sides being rigid ; where in section P2S2 one side should have the ability to displace inward. On the other hand, Stephenson's six-bar isomer Figure 12B satisfies the minimum requirement of five outer nodes along with the constraint #3. Figures 2QA-2QB show the mechanism in SOLIDWORKS in the initial and final state with the inner links constrained to be equal , thus satisfying constraint #4.

This mechanism has one DOF through its six links and seven joints; and because the design requires the unit ceils to be bistable, the mechanism should be a structure with zero DOF in its initial and final state. Analyzing the mechanism using the graph theory where links and joints are represented by points and lines respeciively, gives an alternative way to develop mechanisms undergoing certain constraints. Figure 21 illustrates the example of Stephenson's six-bar isomer using the graph theory.

A mechanism with five links connected in loop satisfies the minimum of five outer nodes (or joints) but would have two DOF, as shown in Figure 22A . Adding two links and four joints to the mechanism will reduce the mobility to zero, which in graph theory means two points and four lines respeciively need to be added . Considering the symmetry in the design, those two points (or links) can be placed either inside the loop or outside, as shown in Figure 22B. Similarly, for the four lines (or joints), two lines should be added in either side of the symmetry line and should avoid a three-line loop when connecting. Otherwise, it will result in three links connected in a loop turning it into a single link. Figure 22C shows the two possibilities of the mechanism which in fact are identical to one another, where Figure 22D shows the final mechanism schematics in reference to its graph theory representation.

The new mechanism will have seven links and nine joints resulting in zero DOF, as shown in Figure 23. To fully define the sketch in SOLIDWORKS, Table 4 illustrates the additional non-limiting constraints added to the lines in both P2S1 and P'2S1 1 the broken lines are not those of the mechanism but for constraint purposes.

The final stage of the design involves converting the mechanism's linkages to compliant segments. Figures 24A-24C show the development of the design from the outline of the mechanism in Figure 24A to the complete design in a compliant form in Figure 24C; the full dimension of this design can be seen in Fi ures 61 -63,

Tabie 4. P2S1 with non-limiting constraints of a seven-bar mechanism.

IV. Design Apparatuses and Fabrication

Physically fabricating the shape-shifting space-frame apparatus was the next step after it was designed; the fabrication procedures involved are discussed herein. The process involves laser cutting the bistable unit ceils from a sheet of material in two-dimensions and then constructing the three-dimensional S SF. Any suitable material may be used to fabricate the apparatus, though it should be noted that in certain embodiments, m aterial selection can be important for this type of design, as the compliant mechanism is based on replacing mechanical joints with living hinges that should be able to endure material deformation and fatigue during actuation. Therefore, in this embodiment, polypropylene copolymer was chosen due to its high fiexural modulus of 145,000 psi and its ability to withstand up to 10% of elongation before break. However, in other embodiments and based on different designs, different types of material can be used to fabricate and construct the design. The unit ceils were modeled in SOLIDWORKS, saved in DXF format or other format suitable for laser cutting or 3D printing or other fabrication method, and imported to the laser machine for cutting. For illustration purposes, each of the mechanisms forming the planes P-j , P2 and P3, as shown in Figure 9, are introduced separately with the actual bistable unit ceil. Figure 10A and Figure 18C reference the mechanism required to morph the unit cell within Pi from a rectangular to a trapezoidal cell element; Figures 25A-25B shows the actual Pi component in its two states. There are two additional links added to the actual component to provide the Instability feature; the placement of those two links will be discussed as this specification continues.

For the plane P2, in reference to Figure 10B and Figure 24C, the analysis of P2S1 section is patterned into the other two sections P2S2 and P2S3 as shown in Figures 26A-26B. The apparatus demonstrates the mechanism's ability to morph the unit cell from a rectangular to an arched rectangular cell element with a substantially 90° angle or other angle dependent on the design choices previously selected. The mechanism design for P2 is duplicated for the third surface P3.

The next step is constructing the sector shown in Figure 9. it should be noted that because the disk tessellation requires ten identical sectors, the number of connections between sectors can be minimized. For this reason, each sector is flattened where the mechanism of P1 is in the middle and the other two mechanisms of P2 and P3 are on either side. Joining the two ends of the final mechanism forms the sector shown in Figures 27A-27B, which also shows the isometric view of the final mechanism in its initial state as a sector to its final morphed state as a wedge with a substantially 90° arc. The designs of the bistable elements within the mechanisms will become clearer as this specification continues.

It becomes clear that if the sectors were to be arranged in a circular pattern, they would form a disk and the wedges would form a spherical shape. Two apparatuses were fabricated with two different sectors' arrangement; each arrangement will be discussed as this specification continues.

A. One Disk to Hemisphere SMSF

The sectors' arrangement in this apparatus involves connecting all ten together in a circular pattern as one single layer to form a disk that can morph to a hemisphere. The connections between sectors are done using zip ties through three circular cuts made at the top of each sector, though this rudimentary connection was done for illustrative purposes only. The sectors can be coupled together in any suitable manner. Figure 29 shows the assembled apparatus as it morphs from its initial disk state to its final hemisphere shape, and vice versa, including the transition between the initial and final states. It should be noted that the middle transition figure in Figure 29 can also be a stable position. This can be accomplished by actuating less than all of the P2 and P3 mechanisms. Now referring to Figures 26A-26B, if there are three (3) P2/P3 mechanisms present, for example, an additional stable position can be accomplished by actuating only one or two of the mechanisms, rather than ail three (i.e., less than all). As such, it is contemplated herein that one stable position can be a curved state and another stable position can be another curved state, where one curved state can have greater or less curvature than the other curved state. For example, the bottom figure of Figure 29 has a greater curvature of the P2/P3 mechanisms than the middle figure of Figure 29. It is also contemplated herein that the current invention can have more than just two (2) stable positions. The apparatus can be stable in all three figures in Figure 29, along with other levels of curvature between those positions (i.e. , different numbers of P2/P3 mechanisms can be actuated to reach a desired level of curvature).

The actuation of this apparatus can be done manually, automatically, or machine-controllably by applying an inward radial force to the sector from nodes ni and r¾2, as shown in Figure 9, via a connected cable that runs to the center of the mechanism. Illustrations of a simplified sector frame can be seen in Figures 28A-28C, illustrating the directions of force and displacement involved. The horizontal support is provided by the surface on which the apparatus is laying, and the vertical support with groove represents the other nine sectors that are a connected circular pattern. The center point of the disk translates vertically due to the symmetry in both design and applied forces around the disk's vertical axis. The ten cables connected from the disk's bottom vertices are joined at the center and pass through an opening in the surface; applying a tension downward translates to an inward radial force at the bottom vertices which can slide along the surface. The foregoing is an example used to actuate the current apparatus during testing , it can be understood that actuation of this mechanism can take place using any known methodology.

Regardless of actuation methodology used, as noted, Figure 29 depicts the apparatus' actuation, at different time frames, showing the disk SIV1SF morph into a hemisphere.

B. Two Disks to Sphere SMSF

Another possible arrangement of the current apparatus involves constructing a set of two disks, where each disk is composed of five sectors arranged in a circular pattern with equal spacing. Both disks are placed on top of each other as two layers with one sector rotational offset. Therefore, for each disk with five sectors equally spaced, a gap forms between every two sectors and by placing another five-sector disk in such a way that should cover the gaps in the first disk, as shown in the isometric and top views of Figures 3QA-3QB. This arrangement gives the apparatus the possibility to morph the structure from a two-layer disk configuration to a sphere configuration, as shown in Figures 31 A-31 B. The actuation for this apparatus will become clearer as this specification continues.

V. Spherical SMSF: Force-Displacement Analysis

Actuating the spherical S SF is similar to the hemisphere's actuation but in this case, two hemispheres are connected together symmetrically across the plane. The two disks are connected together using the sectors' vertices located mid-plane; to do that, two alterations were done on the original sector's mechanism without affecting the mechanism's dynamics. The first alteration , shown in Figures 32A-32B, was adding small material extension at the vertices with a circular cutout inside it to act as a hinge between the two disks and a connection point for the cables. The second alteration is extending the adjacent mechanisms' bottom section as a support and protection for the hinges. The disks can be connected together utilizing the first alteration as hinges when the cables (if this actuation mechanism is used) are secured and passed through the center using an aluminum disk as a ground support. The cables from each vertex are passed in an alternating manner from above and below the support through an opening within it. As a result, five cables can be pulled upward that actuate half of the sectors, and the other five cables are pulled downward to actuate the remaining sectors. Again, the foregoing is an example used to actuate the current apparatus during testing. It can be understood that actuation can be performed using any known methodology.

Assembling the spherical SIVISF in this manner allows the use of a tensile machine to provide tension at both ends of the cables for the apparatus' actuation. The experimental setups involved securing the S SF's cables from both ends to the tensile machine and apply the vertical displacement.

In the experiment, the actuation was carried out at four different rates of applied displacement to observe the force behavior at each rate. Experimental data and results can be different depending on the experimental setup and machine used; behavior can be force-controlled or displacement controlled, in this particular case, Figure 33 shows the force- displacement results at each rate combined into one plot for compression; the actual experimental data is tabulated and can be found in Tables 5-8.

36.50 2.12

36.31 2.24

36.82 2.34

37.12 2.44

37.70 2.55

38.38 2.65

39.40 2.75

40.71 2.85

41 .54 2.95

43.03 3.06

43.30 3.16

42.24 3.26

41 .00 3,36

40.77 3,47

39.49 3.57

38.18 3.67

37.19 3.77

36.08 3.87

35.50 3.98

35.37 4.08

34.38 4.18

33.07 4.28

31 .92 4.38

31 .16 4.49

32.08 4.59

31 .92 4.69

32.05 4.79

32.82 4,89

32.80 4,99

32.57 5.10

31 .64 5.20

32.35 5.30

33.34 5.40

33.68 5.50

34.48 5.60

34.07 5.60

35.97 5.71

37.57 5.81

38.94 5.91

39.18 6.01

38.67 6.12

37.04 6,22

33.99 6,32

29.47 6.42 25.95 6.53

23.43 6.64

23.83 6.73

23.79 6.83

24.28 6.94

24.59 7.04

24.99 7.14

25.41 7.24

25.57 7.34

26.56 7.45

27.76 7.55

29.84 7.65

32.15 7,75

35.02 7,85

38.03 7.95

41 .28 8.06

44.65 8.16

48.94 8.26

52.92 8.36

56.20 8.46

60.00 8.57

63.55 8.67

66.74 8.77

69.83 8.87

73.29 8.97

76.19 9.07

78.59 9.18

79.46 9,28

78.41 9,38

73.86 9.48

70.48 9.58

64.25 9.68

61 .43 9.78

66.69 9.89

72.59 9.99

81 .15 10.09

87.49 10.19

92.65 10.29

97.06 10.38

Table 5. Test data for the displacement load rate 0.081 in/sec.

Q.188 (in/sec) FORCE DISP

LBS !N

17.1 1 0.14

17.74 0.16

18.36 0.17

18.97 0.18

19.57 0.20

20.14 0.21

20.69 0.23

21 .22 0,24

19.77 0.25

20.22 0.27

21 .01 0.28

21 .70 0.29

22.30 0.31

22.87 0.32

23.32 0.34

23.78 0.35

24.22 0.37

24.74 0.38

25.29 0.39

25.84 0.41

26.30 0.42

26.66 0,43

27.21 0,45

27.64 0.46

27.82 0.48

28.03 0.49

28.57 0.50

29.1 1 0.51

29.49 0.53

29.80 0.54

30.48 0.56

31 .02 0.57

31 .51 0.58

31 .57 0.59

32.09 0.61

32.69 0.63

33.1 1 0,64

33.25 0.66

33.72 0.67

34.23 0.68

34.54 0.70 34.85 0.71

35.51 0.72

36.09 0.74

36.49 0.75

36.59 0.77

37.27 0,78

37.94 0,79

38.46 0.80

38.44 0.82

38.70 0.83

39.01 0.84

38.91 0.86

38.99 0.87

39.06 0.88

39.29 0.90

39.61 0.91

39.87 0.93

40.18 0.94

40.39 0.95

40.41 0.97

40.62 0,98

40.73 0,99

40.82 1.00

41.09 1.02

41.30 1.03

41.74 1.04

42.09 1.06

42.45 1.07

42.93 1.09

43.07 1.10

43.46 1.11

43.64 1.13

43.57 1.14

43.82 1.15

44.19 1.17

44.30 1,18

44.22 1.19

44.57 1.21

44.76 1.23

45.09 1.24

45.51 1.27

45.97 1.28

46.52 1.30

46.78 1.32 46.86 1.34

45.01 1.36

45.06 1.38

45.07 1.40

44.94 1.42

44.79 1,44

44.91 1,47

44.16 1.49

42.74 1.52

41.32 1.55

38.94 1.57

36.74 1.59

34.27 1.62

32.95 1.64

31.15 1.67

28.64 1.70

27.16 1.72

26.91 1.73

26.97 1.76

26.86 1.79

27.17 1,82

27.66 1,85

28.19 1.88

28.70 1.90

29.35 1.93

29.94 1.96

30.09 2.00

29.93 2.02

30.36 2.05

30.82 2.09

30.53 2.12

30.66 2.15

31.08 2.18

31.11 2.22

31.04 2.25

31.03 2,29

30.70 2.32

30.61 2.35

30.49 2.39

30.82 2.42

30.91 2.46

31.09 2.49

31.53 2.52

32.52 2.56 33.07 2.60

33.32 2.63

33.98 2.67

34.65 2.70

34.81 2.74

35.07 2,77

35.62 2,81

35.91 2.84

36.28 2.88

35.59 2.91

34.47 2.94

33.99 2.98

33.96 3.02

34.16 3.05

33.86 3.09

33.07 3.12

32.76 3.16

32.76 3.19

32.37 3.23

32.51 3.27

32.45 3,30

32.47 3,33

32.53 3.37

31 .72 3.40

30.84 3.44

30.53 3.48

29.66 3.51

29.26 3.54

29.20 3.58

29.06 3.62

28.86 3.65

28.24 3.68

28.32 3.72

27.96 3.75

28.32 3.78

28.28 3,82

28.05 3.86

27.81 3.89

27.47 3.93

27.21 3.96

26.78 4.00

26.35 4.04

25.74 4.07

25.47 4.10 25.09 4.14

24.45 4.17

24.25 4.21

24.15 4.25

24.47 4.28

24.74 4,32

24.60 4,36

24.32 4.39

24.09 4.43

24.25 4.46

24.66 4.50

24.74 4.54

25.06 4.57

25.07 4.61

25.45 4.65

25.51 4.69

25.26 4.72

25.61 4.76

25.48 4.79

25.42 4.83

23.74 4,87

23.53 4,90

23.86 4.94

24.54 4.98

25.31 5.01

25.66 5.05

25.48 5.09

25.61 5.13

25.49 5.16

25.16 5.19

25.90 5.23

26.39 5.27

26.79 5.30

26.99 5.34

27.77 5.38

28.66 5,42

28.74 5.45

29.55 5.49

30.43 5.52

30.73 5.56

31 .61 5.60

31 .90 5.63

32.51 5.67

33.45 5.71 34.34 5.74

34.61 5.77

34.51 5.81

34.66 5.85

35.07 5.88

34.80 5,92

34.95 5,95

34.80 5.99

34.82 6.02

34.41 6.06

33.52 6.10

32.76 6.13

32.15 6.17

31 .45 6.20

30.26 6.24

29.08 6.28

27.1 1 6.31

24.97 6.35

21 .44 6.39

17.52 6.42

16.59 6,46

15.48 6,49

14.93 6.53

14.65 6.56

14.93 6.60

15.28 6.64

15.68 6.67

16.23 6.71

16.51 6.75

16.50 6.78

16.82 6.82

16.58 6.85

17.10 6.89

17.1 1 6.92

17.35 6.96

17.36 6,99

17.64 7.03

18.16 7.06

18.59 7.10

18.56 7.14

18.74 7.18

19.07 7.21

19.24 7.25

19.22 7.29 18.94 7.32

19.30 7.36

19.22 7.39

19.69 7.43

20.16 7.47

20.70 7,50

20.89 7,54

21 .26 7.58

21 .98 7.61

22.48 7.65

22.89 7.69

23.78 7.73

24.55 7.76

24.93 7.80

25.84 7.84

26.97 7.87

27.80 7.91

29.01 7.94

29.82 7.98

31 .01 8.01

32.26 8,03

33.18 8,06

34.74 8.10

35.90 8.14

37.32 8.17

38.91 8.21

40.39 8.25

41 .94 8.28

43.16 8.32

44.49 8.36

46.16 8.39

47.86 8.43

49.53 8.47

50.84 8.50

52.22 8.53

53.47 8,57

54.48 8.61

55.41 8.64

56.48 8.68

57.36 8.72

58.91 8.75

60.44 8.79

61 .66 8.83

62.59 8.86 63.57 8.90

64.59 8.93

65.61 8.97

67.03 9.01

67.85 9.05

68.81 9,08

69.72 9,12

70.51 9.17

71 .26 9.19

71 .49 9.24

71 .95 9.27

72.45 9.31

72.49 9.35

71 .91 9.38

71 .49 9.42

70.29 9.45

68.55 9.49

66.91 9.53

65.20 9.56

64.23 9.60

61 .47 9,63

59.1 1 9,67

57.20 9.71

56.14 9.74

55.72 9.78

55.65 9.82

56.36 9.85

57.99 9.89

60.51 9.92

63.26 9.96

65.95 10.00

68.55 10.03

70.53 10.07

73.03 10.10

74.1 1 10.14

74.99 10.16

75.98 10.18

76.97 10.20

76.18 10.22

74.90 10.23

74.06 10.23

Table 6. Test data for the dispiacement load rate 0.188 in/sec. 0.275 (in/sec)

FORCE DiSP

LBS IN

15.11 0.36

16.32 0.36

17.59 0.38

18.57 0.41

19.56 0.44

20.89 0.48

22.02 0.51

22.89 0.55

24.30 0.59

25.30 0.63

26.49 0.67

26.99 0.7Q

28.14 0,75

29.09 0,78

30.06 0,82

30.90 0.86

31.99 0.90

32.97 0.94

33.80 0.97

34.76 1.01

35.30 1.05

36.16 1.09

37.15 1.13

37.97 1.17

35.70 1.21

36.22 1.25

36.40 1.29

36.82 1.33

36.36 1,37

36.20 1,41

34.90 1.45

32.98 1.49

29.97 1.53

27.87 1.57

27.44 1.60

26.29 1.64

23.30 1.68

19.84 1.72

20.11 1.76

20.24 1.80 20.82 1 .84

22.17 1 .87

22.51 1 .91

22.91 1 .95

23.72 1 .99

23.43 2.03

23.57 2.07

24.18 2.1 1

23.72 2.15

24.17 2.19

24.52 2.23

24.37 2.27

24.66 2,31

24.37 2,34

24.59 2.39

25.16 2.42

25.69 2.46

26.25 2.50

25.40 2.54

26.1 1 2.58

26.77 2.62

26.93 2.66

27.39 2.70

26.97 2.74

27.23 2.78

27.70 2.82

27.45 2.86

27.45 2,90

27.24 2,93

26.92 2.98

27.31 3.02

27.45 3.06

27.06 3.10

27.18 3.14

27.18 3.18

26.95 3.22

26.14 3.26

26.12 3.30

25.99 3.34

25.77 3.38

25.23 3.42

24.52 3,46

23.56 3,50

23.40 3.53 23.44 3.58

22.66 3.62

22.56 3.66

22.76 3.69

22.64 3.73

22.86 3.77

22.89 3.81

22.45 3.85

22.61 3.89

22.55 3.93

22.20 3.97

21 .94 4.01

21 .98 4,05

20.97 4,09

20.32 4.13

19.57 4.17

19.81 4.21

19.57 4.25

19.66 4.29

19.78 4.33

19.91 4.37

20.44 4.41

20.48 4.45

20.32 4.49

20.80 4.53

20.86 4.57

20.94 4.61

21 .26 4,65

21 .30 4,69

21 .54 4.73

20.14 4.77

19.41 4.81

19.59 4.85

19.91 4.90

20.18 4.93

19.97 4.97

20.53 5.02

20.99 5.05

21 .30 5.09

21 .85 5.14

22.32 5.17

22.49 5,21

22.48 5,25

22.74 5.29 23.15 5.33

23.59 5.38

24.27 5.42

24.61 5.45

25.35 5.49

26.01 5.53

26.47 5.58

26.89 5.61

27.68 5.65

27.82 5.70

28.25 5.73

28.94 5.77

29.03 5,81

28.73 5,85

28.24 5.89

28.39 5.93

28.21 5.97

28.06 6.01

26.89 6.05

26.32 6.09

24.85 6.13

23.51 6.17

21 .56 6.21

18.86 6.25

14.57 6.29

10.86 6.33

9.91 6.37

9.09 6,41

8.59 6,45

8.85 6.48

9.28 6.53

9.99 6.56

10.74 6.60

1 1 .59 6.64

1 1 .97 6.68

12.45 6.72

12.59 6.76

12.62 6.80

12.68 6.84

12.97 6.88

13.07 6.92

13.45 6,96

13.74 7,00

14.28 7.04 14.74 7.08

14.91 7.12

14.99 7.17

15.31 7.20

15.44 7.24

16.20 7.29

16.78 7.33

16.85 7.37

17.12 7.41

17.57 7.45

17.98 7.49

18.27 7.53

18.43 7,57

18.91 7,61

19.42 7.65

20.09 7.69

20.80 7.73

21 .74 7.77

22.66 7.81

23.24 7.85

24.07 7.89

25.14 7.93

25.61 7.97

26.82 8.01

28.36 8.05

29.64 8. 0

31 .1 1 8.13

32.15 8,17

33.76 8,21

35.08 8.26

36.59 8.30

38.03 8.34

39.26 8.38

40.51 8.42

42.19 8.46

43.91 8.50

45.28 8.54

46.84 8.57

48.27 8.62

49.95 8.66

51 .40 8.70

52.66 8,74

53.43 8,78

54.74 8.82 55.78 8.86

57.07 8.90

58.28 8.94

58.99 8.99

59.61 9.03

60.1 1 9.07

60.99 9.1 1

60.66 9.15

58.60 9.19

56.78 9.23

54.73 9.27

51 .1 1 9.32

48.07 9,36

46.01 9,39

42.72 9.43

40.98 9.48

39.82 9.52

40.34 9.56

41 .74 9.60

43.91 9.64

46.24 9.68

49.29 9.72

52.32 9.76

55.28 9.80

58.32 9.84

61 .28 9.88

64.17 9.92

66.70 9,96

69.28 10.00

71 .61 10.04

73.93 10.08

76.18 10.12

78.29 10.17

79.48 10.20

79.47 10.24

80.28 10.28

81 .22 10.32

81 .27 10.35

79.56 10.37

78.32 10.39

Table 7. Test data for the dispiacement load rate 0.275 in/sec.

0.391 (in/sec) FORCE DiSP LBS IN

10.35 0,35

12.32 0.40

14.27 0.46

16.34 0.54

18.81 0.62

20.56 0.70

23.09 0.78

25.04 0.87

26.73 0.97

27.46 1.07

29.19 1.17

30.23 1.27

31.17 1.38

26.44 1,48

11.33 1,59

11.50 1,69

12.77 1.80

14.85 1.90

15.58 2.01

17.19 2.11

18.41 2.22

19.15 2.32

20.31 2.42

21.05 2.53

21.02 2.64

20.90 2.74

21.10 2.85

21.70 2.96

21.40 3.07

21.00 3,17

20.70 3,28

20.00 3.39

19.80 3.48

19.48 3.59

19.91 3.69

19.83 3.80

19.69 3.90

19.00 4.01

17.52 4.11

16.85 4.22

15.43 4.33 13.58 4.44

12.73 4.54

12.59 4.65

12.89 4.75

13.42 4.86

14.10 4.97

15.04 5.07

15.67 5.18

16.50 5.28

16.01 5.39

16.23 5.50

15.90 5.60

14.65 5,71

13.98 5,81

12.65 5.91

1 1 .55 6.02

9.79 6.12

8.51 6.23

8.45 6.33

7.31 6.44

8.02 6.54

8.60 6.64

9.31 6.75

9.81 6.85

10.46 6.96

1 1 .08 7.07

1 1 .30 7.17

1 1 .73 7,28

1 1 .98 7,38

12.83 7.50

12.85 7.60

13.94 7.71

13.19 7.82

14.59 7.92

16.34 8.03

17.35 8.14

20.70 8.24

23.94 8.35

26.51 8.45

28.73 8.55

33.00 8.66

38.00 8,77

42.00 8,87

44.00 8.98 29.37 9.09

28.85 9.20

32.02 9.30

36.02 9.41

39.73 9.52

45.34 9.62

50.83 9.73

56.19 9.83

62.00 9.94

67.52 10.04

72.65 10.13

77.85 10.23

82.58 10.33

87.43 10.42

91 .96 10.52

94.33 10.60

96.62 10.66

98.42 10.73

99.64 10.79

101 .33 10.84

103.17 10.89

105.35 10.94

106.35 10.99

107.62 1 1 .04

108.84 1 1 .08

108.96 1 1 .12

109.19 1 1 .14

107.23 1 1 .18

106.76 1 1 .21

Table 8. Test data for the displacement load rate 0.391 in/sec.

The plot can be divided into four main stages in terms of behavior; those behaviors correspond to the apparatus' intermediate actuation. As actuation begins, the tension applied is translated into radial forces that increase gradually, storing strain energy within the compliant mechanism. Due to the mechanism's bistabiiity feature and after it reaches the unstable equilibrium position, the energy stored can be released in the form of negative force applied within the mechanism causing the sudden drop. This corresponds to P2S3 mechanism being actuated to its second stable position in ail sectors. Next, the P2S2 mechanisms are actuated to their second stable position. The force required for those mechanisms is less due to some energy stored within them during the loading accorded previously. The P2S1 mechanisms are then actuated to their second stable position, and the Pi mechanisms are finally actuated to their second stable position. After morphing the SMSF apparatus to its second stable position as a sphere, the increasing load beyond zone 4 is converted to strain energy stored within the compliant mechanisms. Because the tests were done using displacement loading, it can be observed that the reaction forces throughout the curves are inversely proportional to the displacement rate. At iow displacement rate, the potential energy gradually builds up within the compliant links showing more identifying features on its the curve than that of higher displacement rate result curve.

Example 2 - Design of Mechanism Stability Using Over-Constraint

Generally, described herein is the kinematic analysis involved in transforming regular mechanisms into bistable mechanisms using compliant segments. To aid this transformation, SOLIDWORKS was used to graphically represent the relation between links' rotation and coupler curves at a point on the mechanism. The methods followed are more effective when the initial and final states of the mechanism are given. The methodology described herein is for the fabrication of bistable mechanisms, including that discussed in Example 1 .

An extensive analysis, identifying bistabiiity behavior in four-bar compliant mechanisms, was done in [Jensen, B. D. and Howell, L. L, "Identification of Compliant. Pseudo-Rigid-Body Four- Link Mechanism Configurations Resulting in Bistable Behavior", ASME. J. Mech. Des. 2004; 125(4):701 -708. doi:10.1 1 15/1 .1625399], which resulted in calculating the required torsional stiffness in each joint and the modification of the links' geometry to achieve the bisiability behavior. The toggle positions are also set by the configuration of the mechanism links, i.e., elbow up or down; an effective manner of having a specific intermediate stable position along the movement of the linkages is by designing a hard-stop. A different approach to achieve this behavior was done in [Jensen, B. and Howell, L. L, "Bistable Configurations of Compliant Mechanisms Modeled Using Four Link and Transiational Joints" Journal of Mechanical Design, Vol. 126, Issue 4, pp. 657-666] by utilizing transiational joints and springs in the studied models. Those approaches require extensive formulation by solving the kinematic and energy equations for each specific design. With advanced software solutions such as SOLIDWORKS, simulating the kinematics can be used to design bistable behavior in a compliant mechanism with four-bar PRBM.

The following presents the steps involved using SOLIDWORKS to synthesize a mechanism's geometry in order to achieve a design's specific bistabiiity requirement. This method will ensure a stable position without the need of a hard stop as in [Jensen, B. D. and Howell, L. L., "Identification of Compliant Pseudo-Rigid-Body Four- Link Mechanism Configurations Resulting in Bistable Behavior", ASME. J. Mech. Des. 2004; 125(4):701 -708. doi:10.1 1 15/1 .1625399]. There are two main initial design considerations that should be met before considering this analysis. First, both (first and second) states of the mechanism should be chosen and should represent the mechanism's desired stable positions. The first state is the position in which the mechanism was manufactured or assembled, and the second state is the position to which the mechanism is toggled. The second consideration is the assumption that the magnitude of the joints' torsional spring stiffness is small, i.e. , living hinges [Howell, L, L, 2001 , "Compliant Mechanisms", Wiley, New York, ISBN 978- 0471384786],

L Bistability in a Four-bar Compliant Mechanism Using SOLIDWORKS

Described herein is use of the SOLIDWORKS software following a step-by-step procedure to construct a four-bar compliant mechanism with any two desired stable positions. The bistability is found by utilizing the perpendicular bisector from Burmester's theory [Ceccarelii M, Koetsier T. Burmester and Aiiievi A., "Theory and its Application for Mechanism Design at the End of 19th Century", ASME. J. Mech. Des.2008;130(7):072301 -072301 -16. doi:10.1 1 15/1 .291891 1 ; Waldron, K. J. and Kinzel, G. L., "Kinematics, Dynamics, and Design of Machinery", Wiley, New York, 2 ed. 2003, ISBN 978-0471244172] along with the coupler curve concept in a graphical representation. Those steps can be applied to any two positions of four-bar mechanism to find a solution to its bistability; further design constraints might be implemented to ensure the ability to fabricate the mechanism. Additional, optional design constraints are discussed at the end of the procedure to fine tune the final mechanism's solution.

An objective is to attach a potential energy element (PEE), such as a spring or a compliant link or any element to the mechanism, thus generating an energy curve upon actuation. This new element has two points of attachment - one of those points is attached on the mechanism itself whereas the other point is attached to the ground link or, in other embodiments, to the mechanism itself. The design steps are shown with an illustrative example, which was chosen arbitrarily, to support the generality of this method.

A. Design Stage One: Kinematic Analysis Using SOLIDWORKS

At this stage of the design, the kinematic requirements to achieve the bistability behavior in the mechanism are established using SOLIDWORKS rather than the traditional methods by solving for the kinematic coefficient through a system of equations analysis. This use of SOLIDWORKS reduces the computational time needed and gives the designer more visual understanding of the problem as well as the ability to verify the mechanism's behavior real time. For comparison, if the four-bar linkages shown in Figure 34 were to be analyzed for bistability using the method in [Jensen, B. D. and Howell, L. L., "Identification of Compliant Pseudo-Rigid-Body Four- Link Mechanism Configurations Resulting in Bistable Behavior", ASME. J. Mech. Des. 2004; 125(4):701 -7Q8. doi:10.1 1 15/1 .1625399], the second stable position would be predefined by the mechanism itself, as shown depending on the location of the torsional spring (K).

Figure 34 is an example where the unique second stable position for the given four-bar depends on the mechanism's first position and the spring location. Below are the steps to follow to specify an intermediate stable position without the use of hard-stop:

Step 1 : identify the two desired stable states of the mechanism and sketch the links as lines connecting pin joints in both states, as shown in Figure 35B as derived from Figure 35A. The lengths of the links do not change between its initial and final positions; in SOLIDWORKS, this is implemented with equality constraints. The links are numbered clockwise with the ground being link (14). The center points (fixed ground pivots) of the mechanism are identified as (ni) and (114) where the circle points (moving pivots) are (r?2) and (Π3); this leads to (12) being the targeted link for the analysis. Step 2: Construct the perpendicular bisectors of lines (¾> and n'2) and (Π3 and n'3) segments. The intersection of these perpendicular bisectors is pole point (P), as shown in Figure 36. The second link need not necessarily be a straight link connecting between joints (Π2) and (/13); it could be in any geometrical shape as long as it is rigid and it contains points (Π2 and 113). Therefore, a point on the second link, which connects to one end of the PEE, should be selected .

Step 3: To give an extra DOF for the PEE placement point, a ternary link representation of (12) is sketched out, as shown in Figure 37. The lines (I21) and (I22) do not change length and so j l2l \ = | i'21 \ and i'22 \■ The points (mQ) and (m'Q) are on the mechanism itself and represent the one attachment point of the PEE at its initial and final state, respectively.

Step 4: As shown in Figure 38, two individual lines (/Q) and (I'Q) from the points (mq) and (m'Q) are drawn to a point (Q); those lines represent the PEE at its initial and final state, respectively. Considering those two lines as a source for potential energy requires them to be un-deformed at both states (initial and final), thus an equality constraint is added to them. Both lines are attached to a single point (Q) that represents the second attachment point for the PEE. Additional constraints on the location of this point are described at a later design stage. Knowing that the point (P) represents the finite rotation pole of the second link between initial and final states, every point on that link would have the same pole while the mechanism moves between the predefined initial and final position.

Step 5: Construct the perpendicular bisector line between the points (mQ) and (m'Q) where it must pass through point (P), and every point on that line is a possible location for point (Q) generated in step 2, as shown in Figure 39.

B. Design Stage Two: Potential Energy Analysis Using SOLIDWORKS

After establishing the mechanism's kinematics, this stage will analyze potential energy aspect to the design in order to achieve bistability through the PEE. Referencing Figure 39, extra constraint imposed on the mechanism is adding the PEE, with points (Q) and (mQ) being its center point and circle point, respectively. The effect of that is the point (mQ) has two incompatible zero-stress paths while the mechanism is in motion . The first path is defined by the coupler curve generated from the mechanism's original center points (n ?) and (r?2), while the second path is a circular arc centered at (Q). The actual path the point (mQ) follows is a stressed path, which depends on the relative flexibility (or stiffness) of the four-bar versus the PEE.

Using SOL!DWORKS, the following sequence of steps identify the two paths, providing an in-depth analysis of the PEE. For steps 6 and 7, either step can be followed first, before the other, with the steps pertaining to defining the location of the two points (Q) and (ITIQ). This is an under-specify problem and leaves room to add constraints specific to the mechanism's application, for example the force required to toggle the mechanism and the stiffness of the links required by design.

Step 8: The placement of the attachment point (Q) should be decided; different designs require different locations depending on the space limitation of the mechanism. The only condition is that point (Q) cannot, be placed on a moving link; consequently, it can be only placed on the ground link. Moreover, fixing the point (Q) first, partially restrict the location of the point (mQ) by only allowing it to move at. an equal distance apart; meaning only the angle between the lines (/Q) and (/¾) will vary but the lines have to remains equal in length. For the purpose of illustration, the center point (Q) is placed above the mechanism, as shown in Figure 39, its position can be fine-tuned in a later stage of the design to satisfy the stress limits of the PEE.

Step 7: Next, the location of the point (mQ) is selected by the second link's geometrical design and limitation. In the case of this step precedes step 6, the fixing of point (rriQ) defines the pole line between points (P) and (Q), in turn making point (Q) only valid across that line. Because what is currently being described herein is a general step-by-step design procedure, the location of this point can be selected as shown in Figure 39. The exact location can be considered as a design input for a specific application. The subsequent steps can remain the same regardless of the position chosen.

Step 8: The first zero-stress for path point (mq) is found using the coupler curve generated from the mechanism's original center points. Using the motion analysis within SOLIDWORKS, the path of point (mQ) is traced throughout the rotational cycle of the mechanism. Figures 40A-40B respectively show the traced path in links display and in line representation.

Step 9: Finding the second path that point (mQ) follows by being a circle point for the center point (Q). This path is a circular arc connecting both the points' two stable positions with a radius of (IQ) and its center being point (Q), as shown in Figure 41 .

Step 10: Superimposing both paths of the point (mQ) reveals the type of deformation that the PEE experiences. In this example, and assuming the four-bar mechanism's links {/? - 14) are rigid, the link (IQ) should be compressed to be able to toggle between both stable positions, as shown in Figure 42. Knowing that, a stable equilibrium point is a minimum potential energy and that an unstable equilibrium point is a maximum potential energy is the key idea behind the bistability of such a mechanism. The points of intersection between the two curves (first and second) are going to be a minimum potential energy, a s the link (/Q) is not being compressed or stretched when the two curves intersect. Everywhere else, the difference between these two curves results in tension or compression, and the unstable equilibrium point occurs when the difference between the two curves become the maximum. A reason this concept is effective is because the path generated by the point (Q) and the path generated by the coupler curves a e different.

The foregoing describes general step-by-step design procedures to establish bistability behavior in a four-bar mechanism with any two desired positions. The analysis of the two paths is specific to each design; from the example used, the PEE will experience a compressive load to follow the coupler curve path. The same example can be re-designed if a tensional load on the PEE is required; the position of the point (Q) can act as a knob to control the magnitude and direction of deflection on the element. Figure 43 shows the result if the center point (Q) was placed at the opposite side from what is in Figure 39; the coupler curve remains the same because the mechanism did not change but the path of the circle point (/T?Q) changes. The result is that the PEE experiences elongation along the path between the two stable positions.

The specific analysis of the PEE and the two paths will be discussed further for a specific problem in this research. The general approach to the problem can remain the same for any mechanism but differ in the actual data.

|L Bistability by Over-Constraint

The idea behind bistability by over-constraining the mechanism is introducing a compliant link that represents the PEE as discussed previously. Because this research is targeting one DOF mechanisms, adding an extra link with two joints would result in zero DOF transforming the mechanism into a structure. At each stable position the mechanism will remain a structure; however, while it is in actuation, the flexibility of the compliant link permits the mechanism to toggle between its stable positions.

Discussed herein is an analysis in converting the unit ceil element in t h e Pi SMSF, from Example 1 , into a bistable element using the foregoing step-by-step design procedure. Further described herein is how to transform parallel four-bar linkages, which is a special case of linkages, into a mechanism with two stable positions using the over-constraint by compliant link.

A. SMSF: Unit Ceil Bistability Synthesis

The unit cell element used in Example 1 for the Pi design was based on an eight-bar mechanism with one DOF; because one of the design's requirements is bistability, the unit cell should behave like a structure at each stable position. Further observation on that selected design, shown in Figure 17, reveals that the mechanism can be split into two four- bar mechanisms attached at the center, as shown in Figure 44.

For the left half of the mechanism, the angle between links (/?) and i/52) remains constant at about 60° from the design constraints in Table 3. Thus, the bistability of the left part can be achieved by following the methods proposed in [Jensen, B. D. and Howell, L. L , "Identification of Compliant Pseudo-Rigid-Body Four- Link Mechanism Configurations Resulting in Bistable Behavior", ASME. J. Mech. Des. 2004: 125(4):701 -708. doi:10. 1 15/1 .1825399], by increasing the magnitude of the torsional spring constant at the joint between the two links. This was done be connecting a rigid link between links (/ ^■ /) and (Ig), essentially eliminating the joint between them. This reduces the mechanism to three links and three joints, converting to a structure with zero DOF. As a result, the mechanism, shown in the structure on the left of the broken lines in Figure 45, will toggle between the two stable positions by bucking link (/3) due to being thinner than link (J4) (reference Figure 44 as well), thus making it sufficiently flexible to toggle.

In the right half of the mechanism, the angle between links (/g) and (i¾ increases when the mechanism is in actuation to produce the final trapezoidal shape. Consequently, the joint between both links needs to be small and act as a living hinge with very low stiffness , eliminating the possibility to use the method utilized in the left half. The alternative solution is introducing a compliant link (PEE) following the method described previously; adding a link and two joints normally turns the mechanism into a structure with zero DOF. Specifically, the compliance of the PEE permits the toggling of the mechanism ; thus the placement of the compliant link can be important.

The steps previously described were used to design a solution that satisfies the following constraints:

1 ) The mechanism should be contained within a specified area without interference, though, as discussed, certain multi-layered applications may permit some interference;

2) The ability to laser cut the design from a thin sheet of polymer (any material and thickness is contemplated herein);

3) The stresses on the compliant link or PEE should be within the material's limits; and

4) The PEE's ability to generate enough potential energy to overcome the (small but non-zero) restoring torques within the mechanism's living hinge joints while moving from first to second position and back.

For steps 1 and 2: From the analysis of Pi described previously, the initial and final state of the mechanism is known with its dimensions. Figure 46 shows both states with the perpendicular bisectors drawn for the end points of (162) to identify its pole point (P). For steps 3 to 7: Given the geometrical constraint of the mechanism, the attachment point (mQ) of the compliant link (PEE) has to be on link (162)- The lines (/Q) and (/¾) are sketched out representing the PEE at its initial and final state respectively, along with its perpendicular bisector connecting its point (Q) to the pole point (P). Point (Q) is attached to link (I 2) to satisfy the constraint of the mechanism being contained within the specified area, as shown in Figure 47.

Given the fact that both attachment points (mQ) and (Q) are on the mechanism's link {!Q2) and (12), respectively, limits their position in order to satisfy the non-interference within the mechanism. The restriction is caused by the PEE at its second stable position represented in link (/¾): both of its end points (m'Q) and (Q) can only slide over the links (I '62) and (¾, respectively. Assuming point (Q) is the control, its position is limited to the distance between the joint (n,) up to where the links ( ₂ ) and (/' ₆₂ ) are parallel and coliinear, as shown in Figure 48.

For step 8: Knowing that the positions of the point (m _Q ) along the limits within (/ ₆₂ ), shown in Figure 48, are infinite in theory, eight different coupler curves generated using SOLIDWORKS at different intervals across the link (!Q2) to visualize the change in the curves' behavior, as shown in Figure 49. Those curves and any intermediate ones represent different solutions to the bistability behavior and are considered to be the first path that point (mq) traces.

For steps 9 and 10: Four coupler curves of point (mQ) are selected and superimposed on the second arc path associated with the position of the (mQ) being the circle point to the center point (Q). Each coupler curve is considered a configuration and named (A, B, C and D) for later reference, as shown in Figure 49.

The selection process for the solution was done upon visual observation (or use of algorithms and/or selection process) of each configuration, and the satisfaction of the design constraints and the ability to produce the apparatus, in this example, is as follows:

® Configuration A: It was disqualified due to the maximum distance between the two paths measured to be 0.8 mm compared to the PEE's length of 19.5 mm, which may not provide enough potential energy to overcome the shiftiness within the mechanism. Furthermore, the trace of point (mQ) has to pass the second stable position to foliow the coupler curve which might introduce an unwanted intermediate position, as shown in Figure 5QA.

® Configuration B: it was also disqualified due to the same reason as Configuration A from the trace point of view, as shown in Figure 5QB.

® Configuration C: It qualifies to be a solution due to there being enough paths suppuration and the absence of intermediate position caused by the associated coupler curve; the PEE would experience elongation to follow the coupler curve, as shown in Figure 50C,

® Configuration D: it was disqualified due to the large angle difference that the PEE undergoes between the initial and final state (about 107 degrees), which might cause high stress at the joints. Furthermore, the close proximity between the PEE and link (162) as the final state might cause issues in designing the PEE when thickness is added, as shown in Figure 50D.

For a proof of concept in the S SF design, Configuration C was selected to be the design choice, without claiming it is the only solution to the mechanism's bistability. The structure to the right of the broken lines in Figure 45 depicts the right half of the mechanism, described previously, with the compliant link added for bistability; the detailed dimensions of the PEE can be found in Figures 64-65. Adding the PEE elements leads to adding a link and two joints to the four-bar mechanism for a total of five links and six joints converting it to a structure with zero DOF. As a result, the mechanism will toggle between two stable positions by elongating the PEE, allowing for one DOF during actuation.

Looking at the final Pi mechanism, the left half combined two links as one, thus eliminating one link and one joint, but the right half added one link and two joints as shown in Figure 51 B (Figure 51 A shows the Pi mechanism without compliant links for comparison). The total mobility is (-1) using eight links and eleven joint; this over-constrained mechanism behaves as a structure in both stable positions with enough flexibility within its compliant links to toggle between them.

B. Parallel Four-bar Compliant Mechanism Bistability

The parallelogram linkage is one of the classical four-bar mechanisms with one DOF. it is considered to be a change point mechanism, and according to the work done in [Jensen, B. D. and Howell, L. L, "Identification of Compliant Pseudo-Rigid-Body Four- Link Mechanism Configurations Resulting in Bistable Behavior", ASIV1E. J. ech. Des. 2004; 125(4):701 -708. doi:10.1 1 15/1 .1625399], it can achieve bistability by placing the torsional spring at any joint location. The second stable position is considered to be predefined according to the mechanism's initial state and dimensions; any alternative second stable position can occur by a designed hard-stop. As an example, Figures 52A-52B show the two stable positions in which the mechanism can toggle between by placing the spring (K) at the bottom left and right joints, respectively, taking the bottom link as the ground. The method discussed herein allows the mechanism to have a second stable position by design via over- constraining it using compliant link as PEE. Illustrated herein is the design example using the step-by-step procedure to convert a parallelogram linkage into a mechanism with two bistable positions as shown in Figure 52C, along with a produced working apparatus for behavior demonstration. Considering the same Pi SMSF's design constraint, Figures 53A-53B illustrate the entire step-by-step procedure. The perpendicular bisectors of the link (12) at both ends are parallel unlike other mechanisms, where the intersection of the bisectors represents the pole point (P) . For this reason, the pole of (12) is considered to be any line between both bisectors that is parallel to them . The two attachment points of the PEE (Q) and (/TJQ) are placed on the pole line and link (12), respectively. The dimension (dp) represents the distance of the pole line from the left bisector and (dQ) controls the distance of point (Q) from (14) along the pole line in either direction .

The first path of the point (mq) is along the coupler curve that is an arc in which its center is the intersection point between the link (14) and the pole line. The second path is also an arc with point (Q) as its center; depending on the location of (Q) being above or below the ground link (14) translates to what type of loading the PEE experiences (either compression or tension, respectively). Assuming the mechanism's links are rigid and with low torsional stiffness at the joints, Figure 53A shows when the PEE experiences compression by being forced to follow the first path when absent the PEE, it would follow the second path instead. Furthermore, Figure 53B shows the tension loading on the PEE when point (Q) is below (14).

For illustration and example purposes only, the mechanism shown in Figure 53A is considered where the PEE or (/Q) undergo compressive loading. The mechanism was laser cut as a single piece, shown in Figure 64, and the detailed dimensions of the mechanism can be found Figures 66-68.

This example mechanism was designed to toggle between two stable positions. The first stable position is when the angle between the two links (14) and (/?) is about 120° counterclockwise, and the second stable position is about 30° counter-clockwise for the same links.

Figures 55A-55C show the individual stable positions (Figures 55A-55B) on a polar grid to illustrate their perspective angles, as well as the intermediate unstable position (Figure 55C) showing the bucking of the PEE due to the difference in paths that point (n¾) traces, as shown in Figure 53A.

The FEA analysis preformed on the model shows high stress concentration at the joints exceeding the yield point of the material, which corresponds to the material deformation observed on the apparatus. Figure 56 shows the stresses in the PEE when buckling at the mechanism unstable position, whereas Figure 57 shows the stress concentration at the joints when the mechanism at the second stable position. Behavior as a structure: This term is used herein to refer to the way an apparatus operates, specifically as a whole formed of multiple distinct components organized and arranged in a particular manner, and having a particular shape or state.

Bistable link: This term is used herein to refer to a component that facilitates stability of the overall apparatus in two (2) different positions.

Circumferential line: This term is used herein to refer to a relative or virtual line directed along the outer boundary of a circle, cylinder, or sphere.

Coilinear relative displacement: This term is used herein to refer to a change of positioning of a structure along a straight line.

Constraint: This term is used herein to refer to a restriction on the outer boundaries (typically virtual or unstructured) within which a structure should be contained.

Curved triangular prism: This term is used herein to refer to a polyhedron formed of a triangular base, a translated copy, and three faces joining corresponding sides, where the polyhedron as a whole has an appearance of being curved in a direction. The right side of Figure 9 depicts this configuration.

Fixed ground pivot: This term is used herein to refer to a node that may not move during transition between stable positions.

Fixed link: This term is used herein to refer to an elongate component (such as a rigid rod) of a mechanism that may not move during transition between stable positions.

Latitude line: This term is used herein to refer to a relative or virtual line directed toward the left or right sides of a hemisphere or sphere.

Link: This term is used herein to refer to an elongate component (such as a rigid rod) of a mechanism for transmitting a force or motion, or by which relative motion of other components is produced and constrained.

Longitude fine: This term is used herein to refer to a relative or virtual line directed toward the top or bottom of a hemisphere or sphere.

Moving Sink: This term is used herein to refer to an elongate component (such as a rigid rod) of a mechanism that may be displaced during transition between stable positions.

Moving pivot: This term is used herein to refer to a node that may be displaced during transition between stable positions.

Mode: This term is used herein to refer to a joint, connection point between two links, or attachment point of one link.

Non-interfering potential energy element: This term is used herein to refer to a structural component, such as a spring or a compliant link, disposed on the mechanism, generating an energy curve upon actuation for transition between two stable positions. The component facilitates stability of the overall apparatus in two (2) different positions, while also remaining contained and not obstructing or otherwise altering the natural displacement or position of other links.

Over-constraining: This term is used herein to refer to application of excessive conditions on the mechanism, such as inclusion of the potential energy element, to facilitate stability of the mechanism in multiple positions.

Radial line: This term is used herein to refer to a relative or virtual line passing through or otherwise directed toward the center of a circle, cylinder, or sphere from a point along the circumference.

Sector vertex: This term is used herein to refer to the ending point of a sector or triangular prism, where this point is typically located near the center (or "mid-plane") of the circle formed of the sectors.

Sector: This term is used herein to refer to a component or part of a circle that extends toward the center of that circle.

Stabile position: This term is used herein to refer to a relative location of the apparatus as a whole, along with its individual components, where the location of the structure remains consistent or relatively unchanging until an outside force is applied to the structure in a manner to change the stable position.

Straig t triangular prism: This term is used herein to refer to a polyhedron formed of a triangular base, a translated copy, and three faces joining corresponding sides, where the polyhedron as a whole has no appearance of being curved in any direction. The left side of Figure 9 depicts this configuration.

Structural framework: This term is used herein to refer to a plurality of components that are fitted, united, or other organized/arranged together to form a cohesive whole or greater component of the cohesive whole.

Window: This term is used herein to refer to positioning a structure within a gap of another structure to cover that gap, where the structures are in different planes. This can be seen clearly in Figures 30A-30B.

Without use of a hard stop: This term is used herein to refer to the absence of a structural component that physically limits the travel of a mechanism. There is no structure that, if removed, would cause the mechanism's links/nodes to continue traveling. A hard stop can be contrasted with a bistable link or a potential energy element that facilitates stability of a mechanism in multiple positions.

The advantages set forth above, and those made apparent from the foregoing description, are efficiently attained. Since certain changes may be made in the above construction without departing from the scope of the invention, it is intended that, ail matters contained in the foregoing description or shown in the accompanying drawings shall be interpreted as illustrative and not in a limiting sense.

It is also to be understood that the foiiowing claims are intended to cover ail of the generic and specific features of the invention herein described, and ali statements of the scope of the invention that, as a matter of language, might be said to fail therebetween.