Creating Linkage Permutations to Prevent Self-Intersection and Enable Deployable Networks of Thick-Origami

Origami concepts show promise for creating complex deployable systems. However, translating origami to thick (non-paper) materials introduces challenges, including that thick panels do not flex to facilitate folding and the chances for self-intersection of components increase. This work introduces methods for creating permutations of linkage-based, origami-inspired mechanisms that retain desired kinematics but avoid self-intersection and enable their connection into deployable networks. Methods for reconfiguring overconstrained linkages and implementing them as modified origami-inspired mechanisms are proved and demonstrated for multiple linkage examples. Equations are derived describing the folding behavior of these implementations. An approach for designing networks of linkage-based origami vertices is demonstrated and applications for tessellations are described. The results offer the opportunity to exploit origami principles to create deployable systems not previously feasible.


Results
The unique kinematics of overconstrained linkages allow them to be implemented as origami-inspired mechanisms because their hinge axes are not parallel. This is illustrated through the Bennett linkage with the joints and thicknesses labeled in Fig. 1a and the sector angles noted in Fig. 1b. Here, it can be seen that joint axes 1, 2, 3 and 4 are neither parallel nor co-planar. The similarity between this linkage and an origami vertex can be seen as a i = d i = 0 for a zero-thickness vertex in Fig. 1c. Multiple variations of this and other linkages can be obtained through three different methods presented in this section. Proving that these methods do not prevent the mechanism from moving is possible if we represent the linkage using the Denavit-Hartenburg (DH) convention.
The DH convention 36 uses four parameters (θ, a, d and α) in a homogeneous transformation matrix T i (θ i , a i , d i , α i ) to describe each link. T i is defined in the Supplementary Information (SI) and represents a set of consecutive, specific rotations and translations that relate frames attached to two adjacent links. Because it must be true that the product of all T i in a linkage loop must be the identity matrix, a formal definition of a linkage can be made for this work. where each T i relates two frames rigidly fixed to adjacent links. Only θ i in each T i is allowed to vary. This definition has been used to derive formulas governing the behavior of multiple hoop linkages such as the Bennett linkage, as listed in the SI.
In thick origami, the fold angle, θ, the panel sector angle, α, and the panel thickness, a i , as shown in Fig. 1 are key variables describing the vertex geometry. They are naturally described by the twist parameter α i and linear offset a i in the DH representation. The parameter d is usually zero in these models. Using this transform and the frames shown in Fig. 1d, we define an origami panel that depends on the transform and has a simple shape.

Definition 2 Let two hinge axes z m and z n be related by a DH transformation T defined by the parameters θ, a, d, α.
Also, let z m , x m and ẑ n represent unit vectors aligned with the z-and x-axes of frame m and the z-axis of frame n, respectively. The panel P is defined by the set of all points satisfying with respect to frame m where 0 < p < R, 0 < q < R, 0 < v < a, and R is a scalar that defines the curved boundary of the panel shown in Fig. 1d. Hinge Transpose. Here, we introduce the concept of a hinge transpose. It will be valuable in preventing self-intersection of links as shown in Fig. 2a, enabling new configurations of mechanisms. This transpose takes place when the twist angles α of the two links adjacent to the hinge are replaced by their negative supplements (e.g. α − π) as shown in Fig. 2b. This transpose is shown in Fig. 2c. While hinges 1, 2, and 3 remain in the same position, the fourth hinge changes direction. A hinge transpose can also be more formally defined below.  This definition leads to the following theorem and corollary that such a transformation will not prevent the resulting mechanism from moving. The fact that multiple hinge transposes also do not prevent movement of the mechanism can be proved through variable substitutions, as shown in the SI.

Theorem 1 If we define a specific hinge transpose which exchanges
Corollary 1.1 Let B be a hooplinkage as described in Definition 1. If a hinge is transposed as defined in Theorem 1, the new mechanism B′ will also be a hoop linkage. Also, it will continue to be capable of motion.
Theorem 1 and Corollary 1.1 have important consequences. Together, they describe a simple process for modifying the geometry of an origami-inspired linkage without affecting its motion. One application of this modification would be to reduce self-intersection.
Thickness Shift. Here, we introduce another modification method called thickness shift which requires that a i = 0 for a certain subset of the transforms T 1 T 2 … T n . This operation is illustrated in Fig. 3. If the thickness shift is performed on all the links, then we obtain the spherical mechanism shown in Fig. 3b. However, if it is only applied to the middle link, then Fig. 3c shows the resulting mechanism. While the middle link may be drawn with no thickness, it may also include the material thickness above or below the panel as illustrated in Fig. 3d,e. Unlike the hinge transpose, this type of transformation does not necessarily result in an equivalent linkage. For a hoop linkage, changing the thickness parameter a to zero must respect any additional constraints enforced by the loop. For the Bennett linkage, these requirements are shown in SI Equations 2, 3 and 7. For this particular linkage, these equations can only be satisfied if all thicknesses are zero. Consequently, a thickness shift transformation can only be applied to either all or none of the links. Similar rules will apply to other linkage types.

Split Vertex.
A final modification that we consider is the split vertex technique 14,37 . In this technique, two links representing a linear offset are included at two arbitrary, non-consecutive points in a hoop linkage consisting of n links. This transformation is shown in Fig. 4. This modification is possible as long as a vector from 3 to 3′ and 1 to 1′ are identical and hinge 3 is parallel to 3′ and hinge 1 is parallel to 1′. The fact that this modification also preserves the ability of the hoop linkage to move can also be proven (see the corresponding proof in the SI). For the homogeneous transformations describing B,

and the new set of links is also a hoop linkage as described by Definition 1.
This result is significant because it shows that a split vertex transformation can be applied to any non-consecutive hinges in a hoop linkage provided the offset links T i and T j have certain properties: they must both be linear translations described by vector d and the hinges that they connect to must be parallel because T i and T j include the identity rotation I. Linkage Permutations. The hinge transpose, thickness shift and split-vertex methods can be used to generate variations of a particular hoop linkage. If we designate a hinge transpose by T[u t ], a thickness shift by Z[u z ] and a vertex split by V[u 1 , u 2 ], then recording alterations can be simplified. In this notation, u t is the hinge that is transposed, u z is the smallest hinge number adjacent to the thickness shift and u 1 and u 2 are the lowest-numbered hinges adjacent to the offset links in the split mechanism. If we list the left-most operation occurring first, a table can be created that connects every variation to a fundamental set of hoop linkages. This information is listed in Table 1. For n = 4, the Bennett linkage described in Fig. 2a is used as a starting point. For n = 6, a vertex in Fig. 5c that was described by Chen et al. 18 is the starting point. Different linkage variations created by the hinge transpose and thickness shift methods can also be combined to form more complex mechanisms. An example of a model using Linkages I and III is shown in Fig. S1 and Video S2. The hinges for this model are shown in Fig. S2. In this combined form, the new mechanism acts like an extendable tube.
Tessellation of Linkage-Based Origami. The ability of linkage-based origami to tessellate in two dimensions is an important characteristic that will influence its suitability for engineering applications such as large deployables. Such a tessellation is possible using developable vertices 27,38,39 , but complicated geometry is required to prevent self-intersection in the folded state for thick models. Tessellation is also possible using the thick, Eggbox tessellation shown in Fig. 6. The combination of Linkage II and III allows the entire pattern to fold without self-intersection. While this pattern is useful in its current state, understanding how the geometric constraints in the mechanism influence its tailorability enable its deployment to be tailored to specific applications.
Connecting hoop linkages in a network and ensuring that the network is rigid-foldable is similar to ensuring rigid-foldability in zero-thickness origami networks because a similar set of constraints apply. One of these is that fold angles must be consistent when traced in loops containing multiple vertices and creases 40 . Another constraint results from the need for panel thicknesses to be compatible throughout the pattern. While it is possible to allow  discontinuities in the panel thickness, this will not be considered here. With this information, a set of equations describing this specific tessellation can be found.
While criteria for designing networks of rigid-foldable linkages have not been mathematically proved, it will be assumed that satisfying three different constraint types throughout the pattern will be sufficient. These constraints are: Thickness Compatibility, Fold-Angle Compatibility and Sector-Angle Compatibility.
Thickness Compatibility. One constraint affecting Linkage III is that opposite panels must have the same thickness, as shown in Fig. 7a. In this figure, opposite panels around the vertices marked with dots have the same thickness a or b. Extending this constraint across the pattern requires that panels along diagonals be of the same thickness a i or b j as shown in Fig. 7b.
A relationship based on specific thickness ratios determined by the twist angles provides an additional loop thickness constraint. Specifically, this relation requires that can be reduced if we recognize that knowing that loop (k 00 , k 0n , k sn , k s0 ) and (k 00 , k 0n , k tn , k t0 ) are satisfied guarantees that loop (k s0 , k sn , k tn , k t0 ) is also satisfied. This situation is depicted in Fig. 7d. Here, we assume that 0 < i < m. This can be shown by expressing thickness consistency using Equation 11 for both loops. This yields  Substituting Equations 12 into 13 and eliminating k 00 gives k tn k s0 = k t0 k sn which matches the condition for the third loop (k s0 , k sn , k tn , k t0 ). Generally, consistency of all interior loops can be shown by guaranteeing that all loops (k 00 , k 0i , k ji , k j0 ) are compatible for all j ∈ {1, 2, 3 … m} and i ∈ {1, 2, 3 … n}.
Equation 13 is significant because it suggests that specifying k 00 , k m0 and k 0n will determine all k mn in the interior of the pattern. In the context of pattern design, this indicates that setting the vertex panel angles α 1 and α 2 for all the Bennett linkages along two edges of a rectangular pattern should specify all k i elsewhere in the pattern. While the panel angles for these interior vertices will not be completely determined, thickness consistency loops will provide additional constraints on the pattern geometry.
Fold-Angle Compatibility. A second set of constraints derives from maintaining compatible fold angles between all vertices in the tessellation because they share hinges. Making the substitutions required by Table 1 in SI Equations 8 through 10 shows that 2π = −θ 1 + θ 3 , 2π = θ 2 − θ 4 . These relations are equivalent to θ 1 = θ 3 and θ 2 = θ 4 if we assume that θ i = θ i + 2π. If opposite fold angles in a vertex are equal, then the opposite-angle chains shown in Fig. 7e should all be of equal angles. These chains are indicated by uniform line types and angles θ i , θ i+1 and θ i+2 . The relationship between the angles in Linkages II and III can be found by making the appropriate substitutions in SI Equation 10, giving Like Evans, et al. 40 we define the constant μ to simplify calculations. Here, μ ji is calculated for a vertex with coordinates i and j similar to those shown in Fig. 7c. Like constraints on thickness, perpendicular lines of constant fold angle can be related in loops between four vertices (0, 0),(0, n),(m, n) and (m, 0). This relationship can be expressed as  Because this equation has the same form as Equation 11, it can be generalized in the same way. When combined, these two equations fill a similar roll as those in 27 and manage constraint in this linkage tessellation.
Sector-Angle Compatibility. The final set of constraints guarantee that the panels of the linkage tessellation are quadrilaterals and is written as However, in its current form this equation cannot be easily integrated with the other equations. An assumption that will facilitate integration is that panel thickness is uniform throughout the pattern. This assumption will be desirable for manufacturing considerations but will also simplify the resulting equations. If a/b = 1, then sin α 1 = sin α 2 . Satisfying this equality requires that either α 1 = α 2 or α 2 = π − α 1 . The latter is impossible for non-developable vertices since for the angle sum Σα = 2α 1 + 2(π − α 2 ) ≠ 2π. If α 1 = α 2 , then Equation 15 evaluated for a single panel reduces to sec α j+1,i+1 sec α ji = sec α j+1,i sec α j,i+1 . Equation 16 can only be satisfied if either α ji + α j,i+1 = 0, π or α ji + α j+1,i = 0, π. Because α ji > 0, the angle sums must equal π. These relations effectively eliminate control over either all the vertices (0, n) or (m, 0). Once the geometry of either the horizontal or vertical row of vertices are set, the perpendicular direction is also defined.

Discussion
Linkage-based origami-inspired mechanisms have the potential to solve difficult engineering problems because of their unique ability to realize rigid-foldable mechanisms as well as incorporate materials with finite thickness. These two traits can be valuable in applications such as deployable equipment for spacecraft. However, important challenges have complicated the design of these mechanisms.
This work demonstrates a method for generating mechanism variations that can result in new thick-origami designs. A mathematical basis for generating different variations of an overconstrained, hoop linkage was proved and shown to produce legitimate variations of a hoop linkage. This was demonstrated by creating six variations of linkage-based origami vertices based on the Bennett and Bricard linkages. Equations describing the kinematics of these mechanisms were also derived to characterize the deployment of the linkage tessellation.
Another challenge facing linkage-based origami design is ensuring that they are rigid-foldable. While relations for designing thin, quadrilateral-mesh origami have been developed 27 , designing thick versions has proven challenging. This paper demonstrated that in some cases it is acceptable to require only these three classes of constraints to design rigid-foldable networks of linkage-based vertices. For patterns of quadrilateral panels and fourth-order vertices like the linkage tessellation, a method for ensuring that these constraints were met throughout the pattern was derived and demonstrated to allow design of the deployed mechanism shape. This method was used to design the mechanisms shown in Fig. 8a. Details on its construction and a video of its motion (Video S1) are provided as supporting information.
A potential application for this method is the design of deployable, curved structures such as rover wheels 41 . Deployable wheels for rovers are desirable because space is limited in a lander and reducing wheel size can save significant amounts of volume 42 . Another advantage of wheel deployment is the increased cross-country ability that larger wheels can provide 43 . A wheel approximated by a linkage tessellation of constant curvature is shown in Figs 8c through 8e. Details on its construction are provided as supporting information. This particular model is capable of folding a 15 centimeter diameter wheel into approximately one sixth the original volume. Because of the method used, the design also has significant design flexibility. If wider wheels are desired, additional rows can be added. If the wheel profile needs to be more or less jagged, the vertex geometry can be adjusted and vertices can be added or removed. Addressing the challenges of accommodating thickness and ensuring rigid-foldability will enable novel deployable mechanisms because of the solution simplicity. It is hoped that the increased accessibility of methods for developing variations of overconstrained linkages will enable knowledge in origami to be exploited to create systems not previously possible.

Methods
Model Construction. The model in Fig. 8a was constructed using vertices with angles shown in the upper rows of Table 2. The model in Fig. 8c was fabricated using vertices with the vertex angles shown in the lower rows of Table 2. No datasets were generated or analyzed during the current study.