Folding device

Abstract

The present specification relates to an articulated device, such as an articulated computing device. One example may include a first portion associated with a first axial timing surface and a second portion associated with a second axial timing surface. The example may also include a clutch lamination across the first portion and the second portion and a timing shuttle configured to engage with the first axial timing surface and the second axial timing surface to synchronize rotation of the first portion and the second portion over a range of rotation. The example may include an orientation dependent cam that controls compression of the clutch laminations as the first portion and the second portion rotate within the range of rotation.

Description

Background Art

[0001] Many computer form factors, such as smartphones, tablets, and laptop computers, can provide enhanced functionality by folding for storage and opening for use. For example, a folded device is easier to carry, while an open device provides more input / output area. Summary of the Invention

[0002] This patent relates to articulated devices, such as articulated computing devices. One example may include a first portion associated with a first axial timing surface and a second portion associated with a second axial timing surface. The example may also include a clutch stack spanning the first portion and the second portion and a timing shuttle configured to engage the first axial timing surface and the second axial timing surface to synchronize the rotation of the first portion and the second portion within a certain range of rotation. The example may include an orientation-dependent cam that controls the compression of the clutch stack as the first portion and the second portion rotate within the range of rotation.

[0003] This example is intended to provide a summary of some of the concepts described and is not meant to be inclusive or restrictive. Brief Description of the Drawings

[0004] The various drawings illustrate implementations of the concepts conveyed herein. The features of the illustrated implementations may be more readily understood by reference to the following description in conjunction with the drawings. Wherever possible, the same reference numerals are used in the various drawings to refer to the same elements. Additionally, the leftmost digit of each reference numeral conveys the drawing and associated discussion in which the reference numeral was first introduced. Where space permits, for the convenience of the reader, both the element and its associated reference numeral are shown on the drawing page. Otherwise, only the reference numeral is shown.

[0005] Figure 1A - 1C Figures 2B, 3B, 4B, and 5B show perspective views of example devices according to some implementations of the concepts of the present invention.

[0006] Figure 2C - 2E Figure 2A shows an exploded perspective view of an example device according to some implementations of the concepts of the present invention.

[0007] Figure 2A 、 3A Figures 4A and 5A show front views of example devices according to some implementations of the concepts of the present invention.

[0008] Figure 2F Figure 4B shows an exploded front view of an example device according to some implementations of the concepts of the present invention. Detailed Description

[0009] The present inventive concept relates to devices, such as computing devices that employ a timed hinge assembly that allows a first and a second device portion to rotate through a range of angles (e.g., relative angles). In addition to timing or synchronizing the rotation of the first and second portions, the hinge assembly can also provide a frictional force associated with a rotational resistance (e.g., frictional torque) based on the orientation. In a first sub-range of orientations, the frictional force can hold the first and second portions in any orientation set by the user. In another sub-range of orientations, such as near zero degrees, the hinge assembly can provide a small frictional force and assist the user in causing the device to spring open from a closed orientation when opening the device. These and other aspects will be described by way of example.

[0010] Introductory Figure 1A - 1C Two example device configurations are shown together. Device 100A includes a first portion 102 and a second portion 104 that are coupled by a hinge assembly 106A to allow rotation through a range of orientations (e.g., relative angles). The first portion 102 includes a housing or base 108, and the second portion 104 includes a housing or base 110. The first portion 102 extends from a hinge end 112 to a distal end 114, and the second portion 104 extends from a hinge end 116 to a distal end 118. The hinge assembly 106 defines a hinge axis (HA).

[0011] Figure 1A Device 100A is shown in a closed or approximately zero-degree orientation. As used herein, the approximately zero-degree orientation can be exactly zero degrees and can also include orientations within + / - about three degrees (e.g., -3 degrees to +3 degrees). Figure 1B A first variant of device 100A is shown in an open orientation of approximately 180 degrees, and Figure 1C A second device variant of device 100B is shown in an open orientation of approximately 180 degrees. As used herein, the approximately 180-degree orientation can be exactly 180 degrees and can also include approximate orientations within + / - about five degrees (e.g., 175 - 185 degrees).

[0012] Figure 1B Example device 100A is shown having a first display 120(1) positioned on the base 108 of the first portion 102 and a separate and distinct second display 120(2) positioned on the base 110 of the second portion 104. Displays 120(1) and 120(2) are adjacent to the hinge assembly 106A in a 180-degree orientation.

[0013] Figure 1CIllustrates an example device 100B having a single display 120 that spans from a first portion 102 across hinge assembly 106B to a second portion 104. The single display 120 can be a flexible display that can bend at hinge assembly 106B when the device is closed. As the device 100B closes, hinge assembly 106B can provide space for the display 120 above hinge assembly 106 with an enlarged minimum bending radius (e.g., teardrop shape) to reduce potential damage such as curling of the flexible display. In Figure 1B and Figure 1C the configuration shown, portions of hinge assemblies 106A and 106B are visible at the edges of the device. In other implementations, the hinge assemblies may not be readily visible.

[0014] Hinge assembly 106 can meet various design parameters by providing technical solutions, such as providing relatively high friction (e.g., frictional rotational resistance or frictional torque) in some orientations (e.g., a first orientation sub - range) to hold the various parts of the device in a given orientation. For example, if the user places the device in a 100 - degree orientation, the friction (e.g., rotational torque) provided by the hinge assembly can hold that orientation until the user changes it. Some implementations can employ a stop mechanism at a specific orientation within the first orientation sub - range, such as 180 degrees or near 180 degrees (e.g., fully open). The stop mechanism will help hold the device in the fully open state and give the user positive tactile feedback indicating that the device is fully open.

[0015] The hinge assembly can also produce relatively low friction in some other orientations (e.g., a second orientation sub - range), such as the closed orientation, to facilitate easy opening. For example, a high - friction sub - range provides a high - friction rotational sub - range, such as from 180 degrees to 15 degrees, and then a low - friction sub - range reduces the amount of friction, such as from 15 degrees to 0 degrees.

[0016] This low - friction sub - range can correspond to a pop - out feature. For example, the device can include a lock that automatically engages when the device is closed (e.g., in a closed state). When the user releases the lock, stored energy (such as energy stored in a bent flexible display) can automatically pop the device open a few degrees, such as from 0 degrees to 10 degrees. The low - friction sub - range avoids "canceling out" the pop - out force and allows the stored energy to easily open the device a few degrees.

[0017] The hinge assembly can also synchronize (e.g., in time) the rotation of the first and second parts such that the rotation of one part causes a simultaneous and equal rotation of the other part. Current hinge assembly concepts are capable of providing synchronization while minimizing the timing gap to prevent the motion of one half of the device from becoming unsynchronized with the motion of the other half. Unsynchronized motion is aesthetically unpleasing and can cause damage to the display. This solution can implement these technical solutions on devices that are relatively thin in the z-reference direction.

[0018] Figure 2A - 2F 3A - 3B and 4A - 4B together show details of an example hinge assembly 106C. Figure 2A - 2D A hinge assembly is shown in a 180 - degree orientation, Figure 3A and 3B a hinge assembly is shown in a 90 - degree orientation, and Figure 4A and 4B a hinge assembly is shown in a closed or 0 - degree orientation. Note that in this implementation, the orientation range of the hinge assembly is from 0 degrees to 180 degrees. Other implementations can have smaller or larger ranges. For example, the hinge assembly can be configured to rotate from 0 to 100 degrees or 0 to 360 degrees, among other configurations.

[0019] In this case, the hinge assembly 106C includes a hinge guide 202, a shaft 206, a clutch stack 208, a timing module 210, and a support bracket or spine 212. (Not all elements are designated in each figure, but the elements listed in this paragraph are designated in at least Figure 2D ). The clutch stack 208 can include a central clutch plate 214, which is arranged together with a first - side clutch plate 216 and a second - side clutch plate 218. (Only representative clutch plates are labeled to avoid clutter on the drawing page). In this case, the timing module 210 is embodied as a timing shuttle 220 and a helical slider 222. The timing shuttle 220 interacts with the helical slider 222 to provide a timing or synchronization function between the first and second parts. The timing shuttle 220 can define timing surfaces 224 and 226, the helical slider 222 can define a timing surface 228, and the hinge guide 202 can define a timing surface 230.

[0020] This hinge assembly 106C also includes a spring assembly 232 in the form of a plurality of springs 234. The hinge assembly 106C includes a follower rod 236, a cam rod 238, a spring rod 240, and a low - torque adjustment screw 242. As Figure 2E and 2FAs indicated, the follower rod 236 has a follower surface or profile that includes alternating follower protrusions and follower recesses 246 disposed radially about the axis. The cam rod 238 has a cam surface or profile that includes alternating cam protrusions 248 and cam recesses 250 disposed radially about the axis. To avoid cluttering the drawing sheet, these elements are labeled only with respect to the respective sides of the follower rod 236(1) and the cam rod 238.

[0021] Both shafts 206(1) and 206(2) non-rotationally fix the clutch plates 214, the cam rod 238, the spring rod 240, and the timing shuttle 220 within the backbone 212. Shaft 206(1) also passes through the clutch plate 216, the follower rod 236(1), the helical slider 222(1), and the hinge guide 202(1), and these components are rotatable about the shaft. Shaft 206(2) also passes through the clutch plate 218, the follower rod 236(2), the helical slider 222(2), and the hinge guide 202(2), and these components are rotatable about the shaft. Shaft 206 defines and / or is coextensive with the hinge axis (HA), and the follower rod 236, the hinge guide 202, the clutch plates 216 and 218, and the helical slider 222 are rotatable about the hinge axis (HA).

[0022] Spring 234(1) is located on shaft 206(1), spring 234(2) is located on shaft 206(2), and spring 234(3) is located on the low-torque adjustment screw 242. Spring 234 is confined between the cam rod 238 and the spring rod 240. Accordingly, the helical slider 222 contacts the other side of the spring rod 240.

[0023] The hinge guides 202(1) and 202(2) are respectively fixed to the first part 102 and the second part 104. In some cases, the hinge guides 202 are firmly fixed to the first and second parts. In other cases, the hinge guides 202 may be movably fixed to the first and second parts. As used herein, “movably fixed” means that limited linear motion (e.g., sliding or translation) and / or limited rotational motion (e.g., pivoting) may occur between the hinge guide and the first and second parts. In the latter configuration, the motion of the first and second parts is driven or determined by the rotation of the hinge guide about shaft 206.

[0024] The hinge guide 202(1) is fixed to the first part 102 (generally shown, specifically shown in Figure 1A - 1C ), and the hinge guide 202(2) is fixed to the second part 104 (generally shown, specifically shown in Figure 1A - 1C(shown specifically in). The hinge guide 202(1) is positioned in a non-rotational relationship with the helical slider 222(1) (e.g., the helical slider is slidably retained on the hinge guide), and the hinge guide 202(2) is positioned in a non-rotational relationship with the helical slider 222(2) (e.g., the helical slider is slidably retained on the hinge guide).

[0025] The timing shuttle 220 is located on the low-torque adjustment screw 242 (e.g., bisected by it). The timing surfaces 224 and 226 of the timing shuttle interact with the timing surface 228 of the helical slider 222 and the timing surface 230 of the hinge guide 202 to substantially synchronize the rotation of the first part 102 and the second part 104. Thus, for example, a 40-degree rotation of the first part results in a 40-degree simultaneous rotation of the second part (due to component tolerances of + / - at most 5 degrees). In this case, the timing surfaces 228 of the helical slider 222 and 230 of the hinge guide 202 are axial surfaces. As the timing shuttle 220 moves parallel to the hinge axis in response to the rotation of the first part and / or the second part, the timing shuttle 220 follows the axial timing surfaces 228 and 230.

[0026] The position of the timing shuttle 220 in the y reference direction is determined by the interaction of the timing shuttle with the helical slider 222 and the hinge guide 202. Recall that the orientation of the helical slider 222 is determined by the orientation of the hinge guide 202. Thus, the helical timing surfaces 228 and 230 provide a technical solution that causes the timing shuttle 220 to move along the y reference axis by an amount (e.g., linear distance) determined by the engagement of the timing surface 224 with the axial timing surface 228 and the engagement of the timing surface 226 with the axial timing surface 230, in accordance with the rotation of the first part and / or the second part.

[0027] The timing shuttle 220 provides a technical solution to synchronize the rotation of the first part 102 and the second part 104. For example, the rotation of the first part 102 causes the rotation of the helical slider 222(1). The rotation of the helical slider 222(1) causes the timing surface 228(1) to engage the timing surface 224(1) of the timing shuttle and the timing surface 230(1) to engage the timing surface 226(1) of the timing shuttle. The axial shape of these timing surfaces causes the timing shuttle to move along the y reference axis. The movement of the timing shuttle along the y reference axis causes the timing surface 224(2) of the timing shuttle to engage the timing surface 228(2) and the timing surface 226(2) of the timing shuttle to engage the timing surface 230(2). Thus, the linear movement of the timing shuttle caused by the rotation of the first part causes the timing shuttle to simultaneously rotate the helical slider 222(2) and the hinge guide 202(2), causing the second part to rotate the same angle in the opposite direction, and vice versa.

[0028] The clutch stack 208 provides a variable friction engine. The amount of rotational friction (e.g., frictional torque) generated by the clutch stack 208 is related to how much force is applied to squeeze or compress the clutch plates together (e.g., a greater squeezing force causes the clutch stack to generate a greater frictional torque). The spring force generated by the spring 234 can squeeze the clutch plates together. The present invention provides a technical solution in which the magnitude of the spring force applied to the clutch plates is determined by the position of the timing shuttle 220 and the relative relationship between the cam lever 238 and the follower lever 236. Accordingly, the position of the timing shuttle 220 and the relationship between the cam lever 238 and the follower lever 236 are determined by the orientation of the first part and the second part.

[0029] From one perspective, the spring 234 creates a bias on the cam lever 238 in the y-reference direction towards the clutch stack 208, but whether the spring force is transferred from the cam lever 238 to the follower lever 236 and ultimately to the clutch stack 208 depends on the orientation of the first part and the second part. Thus, the hinge assembly provides orientation-dependent rotational frictional force, which is determined by the orientation of the first part and the second part within their orientation ranges. In this case, the rotational frictional force can be divided into a relatively high frictional force sub-range and a relatively low frictional force sub-range. For example, the relatively high frictional force sub-range can be from about 180 degrees to about 15 degrees, while the relatively low frictional force sub-range can be from about 15 degrees to about 0 degrees, and so on.

[0030] The timing shuttle 220 also has a technical advantage because it can provide overload protection. If one half of the device (e.g., the first part or the second part) (e.g., during a device drop) is forced to rotate out of sync with the other half, the helical slider 222 can move to achieve a temporary asynchronous motion by further compressing the spring 234. When the overload is released, the spring load will return the device to the synchronous state.

[0031] As mentioned above, this implementation employs three springs 234. Spring 234(1) is located on shaft 206(1), while spring 234(2) is located on shaft 206(2). Spring 234(3) is located between springs 234(1) and 234(2) on the low torque adjustment screw 242. The spring 234 is restricted between the cam lever 238 and the spring lever 240. The spring 234 acts on the spring lever 240, and the spring lever 240 in turn acts on the helical slider 222. The helical slider 222 can move axially to remove any clearance in the timing provided by the timing shuttle 220. The helical slider 222 is in close contact with the timing shuttle 220, and the timing shuttle 220 is in turn in close contact with the hinge guide 202. This spring-loaded close contact of the timing surfaces (228 with 224 and 226 with 230) eliminates any timing clearance in the system throughout the rotation range (e.g., between the hinge assembly and the first part and / or the second part).

[0032] In the illustrated configuration, three springs 234 also act on the cam lever 238. In Figure 3A and 3B within the high-friction rotor range represented by the 90-degree orientation, the cam lever 238 can slide freely along the axis 206. The cam lever 238 acts on the follower lever 236, and the follower lever 236 applies a load to the clutch stack 208. The interleaved clutch plates 214, 216, 218 in the clutch stack 208 generate frictional forces to resist unnecessary hinge movement. The high-torque frictional force can be adjusted by changing the spring load or the number of clutch plates in the clutch stack.

[0033] The axial cam system formed between the cam lever 238 and the follower lever 236 provides at least two technical solutions. The first technical solution is to separate the spring load from the clutch stack 208 in order to provide low torque for the ejection angle sub-range (e.g., 0 - 15 degrees) in the illustrated version. This can be achieved by comparing Figure 3A and 3B the high-torque sub-range represented by the 90-degree orientation in Figure 4A and 4B with the low-torque sub-range represented by the zero-degree orientation in Figure 2A - 2F shown). The second technical solution is to provide a pawl mechanism that can latch and fix the various parts of the device when the device approaches 180 degrees (as

[0034] shown). This design has technical advantages because at the 180-degree orientation, the pawl mechanism can provide most of the holding force (e.g., rotational frictional force). At other orientations, the clutch stack can provide most of the holding force (e.g., rotational frictional force).

[0035] Different from other designs, the hinge assembly 106C provides a technical solution that does not require the timing shuttle 220 to unload the clutch stack 208. This is a technical advantage because it reduces the force on the timing shuttle 220, thereby reducing the stress on the timing shuttle 220. In addition, the use of axial cams on the timing shuttle 220, the helical slider 222, and the hinge guide 202 makes the transition from the low-torque sub-range to the high-torque sub-range more flexible.

[0036] Recall that, as Figure 2E and 2FAs shown, the follower rod 236 includes alternating follower protrusions 244 and follower depressions 246. The cam rod 238 includes alternating cam protrusions 248 and cam depressions 250. When the device approaches the 180-degree orientation of full open, the follower protrusions 244 on the follower rod 236 can snap into the cam depressions 250 on the cam rod 238 to provide a braking mechanism. This can be achieved by selecting a relatively steep cam depression profile. Additionally, play can be reduced by matching the width of the follower rod protrusion 244 with the width of the cam depression 250, so that the first and second parts are held closely together in the 180-degree orientation and do not wobble. Alternatively, the cam can be designed such that the follower rod is located in the lower half of the cam ramp at 180 degrees (thereby applying torque). Further movement beyond 180 degrees is restricted by another constraint (commonly referred to as a "stop") of the hinge guide rotation. This configuration also prevents wobbling, but this wobbling occurs between the cam in one direction and the stop in the other direction.

[0037] Figure 3A and 3B Figure 6 shows the hinge assembly 106C in the 90-degree orientation, which represents the high-friction rotor range. In the high-friction rotor range, the follower protrusions 244 on the follower rod 236 are aligned with the cam protrusions 248 on the cam rod 238. This alignment enables the cam rod to transfer the spring force fully to the follower rod 236 and, in turn, to the clutch stack 208. This structure also forces the cam rod to press slightly downward against the spring 234. This can be demonstrated by the slight downward force applied by the low-torque adjustment screw 242 from the lower end of the spine 212 (e.g., at the other end of the clutch stack 208).

[0038] Figure 4A and 4B Figure 7 shows the hinge assembly 106C in the zero-degree orientation, which represents the low-friction rotor range. In the low-friction rotor range, the follower protrusions 244 on the follower rod 236 fall into the cam depressions 250 on the cam rod 238, causing the cam rod 238 to slide further toward the follower rod 236 (moving along the positive y-axis reference direction (e.g., toward the top of the drawing page)). However, the movement of the cam rod is restricted by the low-torque adjustment screw 242, such that the spring load is transferred through the low-torque adjustment screw 242 rather than being applied to the follower rod 236. The clutch stack 208 is unloaded and thus in a low-friction torque state.

[0039] This can be seen by comparing Figure 3A and 3B wherein, due to the cam alignment transferring the spring energy along a "path" through the cam rod 238 to the follower rod 236, the bottom of the low-torque adjustment screw is forced away from the spine, thus pressing the clutch stack against the spine. In contrast, in Figure 4A and4B In this case, the alignment of the cam and the cam follower creates a clearance in the "path" between the cam rod 238 entering the follower rod 236. To complete this path, the cam rod 238 must move upward toward the follower rod 236 to transfer the spring force to the clutch stack 208. However, the upward movement of the cam rod 238 is limited by the low-torque adjustment screw 242 screwed into the cam rod 238. When the bottom of the low-torque adjustment screw 242 contacts the ridge frame 212, the upward movement amplitude of the cam rod 238 stops.

[0040] The threaded relationship between the cam rod 238 and the low-torque adjustment screw 242 provides adjustability to define a sub-range of low-friction rotation. For example, screwing the low-torque adjustment screw 242 further into the cam rod 238 shortens the length of the low-torque adjustment screw 242 between its bottom and the cam rod 238. This will increase the low-friction sub-range. For example, if the low-friction sub-range is initially set from 0 degrees to 10 degrees, screwing the low-torque adjustment screw 242 further into the cam rod 238 can increase the low-friction sub-range to, for example, 0 degrees to 15 degrees. The ability to control the low-friction range may be limited by the cam shape. If the cam slope is small, large-angle adjustments can be made. Some cam designs include a fixed opening angle. Further adjustments can consider the manufacturing differences in the lengths of many components involved in the load path in the y-reference direction. In this case, adjustments can be made to establish an appropriate clearance between the cam and the follower to ensure that the load path is interrupted within the low-friction range.

[0041] Figure 5A and 5B Another example hinge assembly 106D in the 180-degree orientation is shown. In this configuration, the follower rod 236 is integrated into the hinge guide 202. The spring rod 240 is located on the other side of the cam rod 238 of the clutch stack 208. The low-torque adjustment screw 242 passes through the ridge frame 212 and the spring 234(3) and is screwed into the cam rod 238. The low-torque adjustment screw 242 can be adjusted to adjust the position of the cam rod 238 (in the y-axis reference direction).

[0042] In the high-friction sub-range, when the follower projection 244 aligns with the cam projection 248 ( Figure 2E and 2F ), the spring force is transferred from the spring 234 to the cam rod 238, then to the follower rod 236, and then to the clutch stack 208. However, in the low-friction sub-range, the follower recess 246 aligns with the cam projection 248 ( Figure 2E and 2F), and since the bottom of the low-torque adjustment screw 242 contacts the ridge frame 212, the cam lever 238 cannot move towards the follower lever 236. As a result, the spring force applied to the clutch stack 208 is small or zero, and the rotational resistance provided by the hinge assembly 106D is relatively small.

[0043] At the 180-degree orientation, the interaction between the cam of the cam lever 238 and the cam follower of the follower lever 236 (e.g., the follower projection 244 aligned with the cam recess 250) acts as a braking mechanism, thereby providing a bias to maintain the 180-degree orientation. The user can overcome this bias by applying sufficient rotational force to move the follower projection 244 upward, out of the cam recess 250 and compress the spring 234 (e.g., move into the high-friction sub-region). In some embodiments, the cam can be designed to partially or fully reduce the friction of the clutch stack at the braking position. Alternatively, it can also be designed to almost maintain full friction. This can be achieved by designing the cam such that even when the follower is partially below the cam ramp, the cam can still maintain contact with the follower at the 180-degree orientation.

[0044] This concept provides a technical solution in which the radial arrangement of the follower projection 244, the cam recess 250, and the cam projection 248 allows the orientation of the first and second parts to determine their relative alignment. Thus, when the first and second parts are in the 180-degree orientation, the follower projection 244 and the cam recess 250 provide a braking mechanism. In the high-friction sub-range, the follower projection 244 aligns with the cam projection 248, thus completing the path for transmitting the spring force to the clutch stack. In the low-friction sub-range, the alignment of the follower projection with the cam recess limits the transmission of the spring force.

[0045] The hinge assembly 106D also employs a different timing module 210. In this case, the timing module 210 is embodied as one or more figure-eight cords 502 that are directly positioned around the shaft 206 on the spool 504. The figure-eight cord 502 can be configured to form an anti-slip relationship with the shaft to synchronize the rotation of the shaft during normal operation of the device. For example, the rotation of the first part causes the rotation of the shaft 206(1), which in turn causes the rotation of the figure-eight cord 502, and then drives the rotation of the shaft 206(2) and the second part. The figure-eight cord can provide synchronous timing in the system (e.g., between the first part, the hinge assembly, and the second part) with little to no clearance (e.g., play or looseness). The figure-eight cord can be associated with the shaft such that in the event of a traumatic stress event such as a drop, the cord can slide relative to the shaft, thereby reducing / preventing damage to the hinge assembly.

[0046] A variety of configurations may be employed. For example, a single figure-eight can be made from a single rope. Alternatively, multiple ropes can be used, with each rope forming a figure-eight wrap (e.g., they can be adjacent to each other along the y reference axis in a non-overlapping manner). Alternatively, a single rope can form multiple figure-eight wraps like a shoelace (e.g., adjacent wraps are arranged along the y reference axis in a non-overlapping manner). In some configurations, each figure-eight can be fixed to the reel with glue, welding, or soldering, which allows each wrap (e.g., the loop on the reel) to act independently.

[0047] The figure-eight rope 502 can be made of various materials, such as metal or polymer, and can be single-strand or multi-strand. Dyneema is an example of a relatively strong and low-stretch rope material that can be used. Another example is a steel wire rope, such as a 7x7 steel wire rope with a diameter of 0.27 mm. The steel cable can be welded or soldered, and the synthetic cable can be glued. Alternatively, crimping can also be performed at both ends of a fixed-length cable. Then, the cable can be tensioned while fixing the crimping parts to the hinge guide via glue, welding, etc.

[0048] Individual device components can be made of various materials, such as metal, plastic, and / or composite materials. These materials can be prepared in various ways, such as being prepared from formed metal sheets, die-cast metals, machined metals, 3D-printed materials, molded or 3D-printed plastics, and / or molded or 3D-printed composite materials, etc., and / or any combination of these materials and / or preparations can be employed.

[0049] The hinge assembly concept of the present invention can be used with any type of device, such as but not limited to laptop computers, smart phones, wearable smart devices, tablets, and / or other types of existing, developing, and / or yet-to-be-developed devices.

[0050] In addition to the above-referenced Figure 1A - 5B methods of manufacturing, assembling, and / or using the hinge assemblies and sensors shown, various methods of manufacturing, assembling, and / or using hinge assemblies and devices are also contemplated.

[0051] Although the technology, methods, devices, systems, etc. related to hinge assemblies have been described in language specific to structural features and / or method acts, it is understood that the subject matter defined in the appended claims need not be limited to the specific features or acts described. Instead, the specific features and acts are disclosed as example forms for implementing the claimed methods, devices, systems, etc.

[0052] Various examples are described below. Additional examples are described below. One example includes a device that includes: a first portion fixed to a first hinge guide and a second portion fixed to a second hinge guide, the first hinge guide being configured to rotate relative to a first axis and defining a first axial timing surface, the second hinge guide being configured to rotate relative to a second axis and defining a second axial timing surface; a clutch stack spanning the first axis and the second axis; a timing shuttle located between the first axis and the second axis, the timing shuttle being configured to engage the first axial timing surface and the second axial timing surface to synchronize the rotation of the first portion and the second portion within a certain range of rotation; and an orientation-dependent cam that limits the compression of the clutch stack within a first sub-range of the range of rotation and promotes the compression of the clutch stack within a second sub-range of the range of rotation.

[0053] Another example may include any of the examples above and / or below, wherein the device further includes a first display located on the first portion and a second display located on the second portion, or further includes a single display extending across both the first portion and the second portion.

[0054] Another example may include any of the examples above and / or below, wherein the device further includes a first helical slider associated with the first hinge guide and defining a third axial timing surface, and a second helical slider associated with the second hinge guide and defining a fourth axial timing surface.

[0055] Another example may include any of the examples above and / or below, wherein the timing shuttle is restricted between the first axial timing surface and the third axial timing surface and the second axial timing surface and the fourth axial timing surface.

[0056] Another example may include any of the examples above and / or below, wherein the device further includes a spring located between the clutch stack and the timing shuttle.

[0057] Another example may include any of the examples above and / or below, wherein the spring biases the third axial timing surface and the fourth axial timing surface toward the first axial timing surface and the second axial timing surface.

[0058] Another example may include any of the examples above and / or below, wherein the spring biases the orientation-dependent cam toward the clutch stack.

[0059] Another example may include any of the above and / or below examples, wherein the orientation-dependent cam is located on a cam rod, the cam rod is located on the first shaft and the second shaft, and the orientation-dependent cam includes a first orientation-dependent cam positioned around the first shaft and a second orientation-dependent cam positioned around the second shaft.

[0060] Another example may include any of the above and / or below examples, wherein the first orientation-dependent cam includes alternating cam lobes and cam recesses radially arranged around the first shaft, and the second orientation-dependent cam includes alternating cam lobes and cam recesses radially arranged around the second shaft.

[0061] Another example may include any of the above and / or below examples, wherein the device further includes a first follower rod positioned around the first shaft and configured to rotate with the first hinge guide, the first follower rod including alternating follower lobes and follower recesses radially arranged around the first shaft.

[0062] Another example may include any of the above and / or below examples, wherein within the first sub-range of the rotation range, the follower lobe aligns with the cam recess to transmit a small spring force to the clutch stack, thereby generating a relatively low rotational resistance.

[0063] Another example may include any of the above and / or below examples, wherein within the second sub-range of the rotation range, the cam lobe aligns with the follower lobe to transmit a large spring force to the clutch stack, thereby generating a relatively high rotational resistance.

[0064] Another example may include any of the above and / or below examples, wherein at the 180-degree orientation, the follower lobe aligns with the inclined surface of the cam recess to generate a stop bias, thereby keeping the first part and the second part in a 180-degree orientation.

[0065] Another example includes a device, the device including: a first part associated with a first axial timing surface and a second part associated with a second axial timing surface; a clutch stack spanning the first part and the second part; a timing shuttle configured to engage with the first axial timing surface and the second axial timing surface to synchronize the rotation of the first part and the second part within a certain rotation range; and an orientation-dependent cam that controls the compression of the clutch stack when the first part and the second part rotate within the rotation range.

[0066] Another example may include any of the above and / or below examples, wherein the first axial timing surface is defined by a first helical slider that is slidably held in a first hinge guide fixed to the first part, and wherein the second axial timing surface is defined by a second helical slider that is slidably held in a second hinge guide fixed to the second part.

[0067] Another example may include any of the above and / or below examples, wherein the first hinge guide defines a third axial surface, the second hinge guide defines a fourth axial surface, and further includes a spring that biases the timing shuttle between the first helical slider and the second helical slider and between the first hinge guide and the second hinge guide.

[0068] Another example may include any of the above and / or below examples, wherein the orientation-dependent cam is configured to transfer the force from the spring to the clutch stack in a high-friction rotor range and is configured not to transfer the force from the spring to the clutch stack in a low-friction rotor range.

[0069] Another example includes a device that includes: a timing module configured to synchronize the rotation of a first device part and a second device part between which a flexible display extends; a clutch stack configured to apply rotational resistance to the first part and the second part; and an orientation-dependent cam configured to apply a greater compressive force to the clutch stack in a first rotor range and a lesser compressive force to the clutch stack in a second rotor range including a closed orientation in which the flexible display bends between the first part and the second part.

[0070] Another example may include any of the above and / or below examples, wherein the timing module includes a timing shuttle, or wherein the timing module includes an 8-shaped timing cord.

[0071] Another example may include any of the above and / or below examples, wherein the clutch stack and the orientation-dependent cam are located on a shaft, and wherein the 8-shaped timing cord is positioned around the shaft.

[0072] Another example may include any of the above and / or below examples, wherein the 8-shaped cord is directly located on the shaft, or wherein a reel is located on the shaft and the 8-shaped cord is located on the reel.

[0073] Another example may include any of the above and / or below examples, wherein the 8-shaped cord includes a single 8-shaped timing cord.

[0074] Another example may include any of the above and / or following examples, where the single figure-eight timing cord forms a single loop figure-eight around the axis, or where the single figure-eight timing cord forms multiple figure-eight windings around the axis.

[0075] Another example may include any of the above and / or following examples, where the figure-eight timing cord includes multiple figure-eight timing cords, and each figure-eight timing cord forms a figure-eight winding around the axis.

Claims

1. A device, comprising: a first portion fixed to a first hinge guide and a second portion fixed to a second hinge guide, the first hinge guide being configured to rotate relative to a first axis and defining a first axial timing surface, the second hinge guide being configured to rotate relative to a second axis and defining a second axial timing surface; a clutch stack spanning the first axis and the second axis; a timing shuttle located between the first axis and the second axis, the timing shuttle being configured to engage with the first axial timing surface and the second axial timing surface to synchronize the rotation of the first portion and the second portion within a certain range of rotation; and an orientation-dependent cam that restricts the compression of the clutch stack within a first sub-range of the rotation range and promotes the compression of the clutch stack within a second sub-range of the rotation range.

2. The device according to claim 1, characterized in that, Further comprising a first display located on the first portion and a second display located on the second portion, or further comprising a single display extending across both the first portion and the second portion.

3. The device according to claim 1, characterized in that, Further comprising a first helical slider associated with the first hinge guide and defining a third axial timing surface, and a second helical slider associated with the second hinge guide and defining a fourth axial timing surface.

4. The device according to claim 3, characterized in that, The timing shuttle is restricted between the first axial timing surface and the third axial timing surface and the second axial timing surface and the fourth axial timing surface.

5. The device according to claim 4, wherein Further comprising a spring located between the clutch stack and the timing shuttle.

6. The device according to claim 5, characterized in that, The spring biases the third axial timing surface and the fourth axial timing surface toward the first axial timing surface and the second axial timing surface.

7. The device according to claim 6, characterized in that, The spring biases the orientation-dependent cam toward the clutch stack.

8. The device according to claim 7, characterized in that, The orientation-dependent cam is located on a cam rod that is located on the first axis and the second axis, and the orientation-dependent cam includes a first orientation-dependent cam positioned around the first axis and a second orientation-dependent cam positioned around the second axis.

9. The device according to claim 8, characterized in that, The first orientation-dependent cam includes alternating cam protrusions and cam depressions radially arranged around the first axis, and the second orientation-dependent cam includes alternating cam protrusions and cam depressions radially arranged around the second axis.

10. The device according to claim 9, characterized in that, Further comprising a first follower rod positioned around the first axis and configured to rotate with the first hinge guide, the first follower rod including alternating follower protrusions and follower depressions radially arranged around the first axis.

11. The device according to claim 10, characterized in that, Within the first sub-range of the rotation range, the follower protrusions are aligned with the cam depressions to transmit a small spring force to the clutch stack, thereby generating a relatively low rotational resistance.

12. The device according to claim 11, characterized in that, Within the second sub-range of the rotation range, the cam protrusions are aligned with the follower protrusions to transmit a large spring force to the clutch stack, thereby generating a relatively high rotational resistance.

13. The device according to claim 12, characterized in that, At the 180-degree orientation, the follower protrusions are aligned with the inclined surfaces of the cam depressions to generate a stop bias, thereby holding the first portion and the second portion in a 180-degree orientation.

14. A device, comprising: a first portion associated with a first axial timing surface and a second portion associated with a second axial timing surface; a clutch stack spanning the first portion and the second portion; a timing shuttle configured to engage the first axial timing surface and the second axial timing surface to synchronize rotation of the first portion and the second portion within a range of rotation; and an orientation-dependent cam that controls compression of the clutch stack as the first portion and the second portion rotate within the range of rotation.

15. The device according to claim 14, characterized in that The first axial timing surface is defined by a first helical slider slidably retained in a first hinge guide fixed to the first portion, and wherein the second axial timing surface is defined by a second helical slider slidably retained in a second hinge guide fixed to the second portion.

16. The device according to claim 15, characterized in that, The first hinge guide defines a third axial surface, the second hinge guide defines a fourth axial surface, and further includes a spring that biases the timing shuttle between the first helical slider and the second helical slider and between the first hinge guide and the second hinge guide.

17. The device according to claim 16, characterized in that, The orientation-dependent cam is configured to transfer a force from the spring to the clutch stack within a sub-range of rotation of high friction and is configured not to transfer a force from the spring to the clutch stack within a sub-range of rotation of low friction.

18. A device, comprising: a timing module configured to synchronize rotation of a first device portion and a second device portion, with a flexible display extending therebetween; a clutch stack configured to apply rotational resistance to the first portion and the second portion; and, an orientation-dependent cam configured to apply a greater compressive force to the clutch stack within a first sub-range of rotation and a lesser compressive force to the clutch stack within a second sub-range of rotation including a closed orientation in which the flexible display is bent between the first portion and the second portion.

19. The device of claim 18, wherein the timing module includes a timing shuttle, or wherein the timing module includes an 8-shaped timing cord.

20. The device according to claim 19, characterized in that, The clutch stack and the orientation-dependent cam are located on a shaft, and wherein the 8-shaped timing cord is positioned around the shaft.

21. The device according to claim 20, characterized in that, The 8-shaped timing cord is directly located on the shaft, or wherein a reel is located on the shaft and the 8-shaped timing cord is located on the reel.

22. The device according to claim 20, wherein, The 8-shaped timing cord includes a single 8-shaped timing cord.

23. The device according to claim 22, characterized in that, The single 8-shaped timing cord forms a single loop 8-shape around the shaft, or wherein the single 8-shaped timing cord forms multiple 8-shaped windings around the shaft.

24. The device according to claim 20, characterized in that The 8-shaped timing cord includes multiple 8-shaped timing cords, each 8-shaped timing cord forming an 8-shaped winding around the shaft.

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