Spring type swing assembly

Abstract

The present disclosure relates to a clockwork swing assembly comprising: a frame assembly comprising a housing; a drive spring positioned within the housing and having a drive spring axis oriented in a non-vertical direction relative to a vertical plane; a swing arm assembly connected to the frame assembly to receive energy from the drive spring, the swing arm assembly including a swing arm and a swing arm pivot, the swing arm rotatable about a swing arm axis oriented in a non-horizontal direction relative to a horizontal plane; the tightening mechanism comprises a tightening shaft positioned along the axis of the driving spring, and the tightening mechanism is provided with a first end connected with a crank assembly and a second end connected with a bobbin; wherein the drive spring includes a first end connected with an attachment plate disposed about the tightening shaft and a second end connected with the spool such that rotation of the tightening shaft tightens the drive spring via the spool.

Description

TECHNICAL FIELD

[0001] The present disclosure relates generally to a child swing assembly, and more particularly to a non-electric child swing assembly and methods of using the same. BACKGROUND

[0002] Child swing devices are well known. Many known child swing devices are powered by electricity or batteries. These types of child swing devices can be considered electric swing devices because there is a dedicated motor unit or other driving mechanism to create the periodic or swinging motion, and an electrical power source is required. Due to environmental concerns, there is an increasing commercial demand for more environmentally friendly products in many consumer areas that do not require electrical power to operate, which typically requires the consumption of fossil fuels or batteries that can be harmful to the environment.

[0003] Prior to the commercialization of electric swing devices, many known child swing devices relied on human power or were driven by a horizontally positioned drive spring. Typically, the drive spring has a central axis that extends in a horizontal direction (i.e., a drive spring axis) and is arranged above the child swing device.

[0004] While powering a swing assembly using a drive spring can satisfy the increasing demand for more environmentally friendly child swing device options, conventional drive spring driven swing devices typically have drawbacks that make them less than ideal. For example, conventional spring wound swing devices have a relatively short run time (e.g., 20 minutes) after being fully wound. In addition, conventional spring wound swing devices typically require a large footprint or occupy a large space.

[0005] In addition to increasing run time and reducing the footprint of a spring wound child swing device, it can also be difficult to efficiently transfer force between various subcomponents of the swing assembly, such as the drive spring, escapement assembly, and swing arm assembly.

[0006] Because the energy that can be stored by a spring is relatively low, it is important to minimize energy loss due to friction. Therefore, a low friction design is needed, especially when transferring rotation between shafts. This is also advantageous for shafts that are not parallel to each other. Advantageously, the transfer of energy between the shafts of various components is achieved with minimal loss of friction while still maintaining a cost effective and feasible design.

[0007] Therefore, it would be desirable to provide a compact spring wound child swing device that provides a relatively long run time and also efficiently transfers force between the main components. SUMMARY

[0008] The present disclosure relates to a clockwork child swing that addresses typical shortcomings of conventional clockwork swings. Unlike conventional clockwork swings, in which the drive spring is oriented along a horizontal axis on the top of the swing, the swing assembly of the present disclosure has a drive spring that has a central axis (i.e., drive spring axis) that is oriented in a non-horizontal direction. In some examples, the drive spring axis can be angled a few degrees from the vertical direction. In some examples, the drive spring axis can be angled anywhere from 45 degrees to 90 degrees from the ground support surface (i.e., perpendicular to the ground support surface). In other examples, the drive spring axis can extend in the vertical direction. The clockwork swing disclosed herein also has a longer run time that can exceed 45-60 minutes based on a user winding the drive spring for about 20 seconds or about 20-30 windings.

[0009] The present disclosure relates to a clockwork child swing that addresses typical shortcomings of conventional clockwork swings. Unlike conventional clockwork swings, in which the drive spring is oriented along a horizontal axis on the top of the swing, the swing assembly of the present disclosure has a drive spring that has a central axis (i.e., drive spring axis) that is oriented in a non-horizontal direction. In some examples, the drive spring axis can be angled a few degrees from the vertical direction. In some examples, the drive spring axis can be angled anywhere from 45 degrees to 90 degrees from the ground support surface (i.e., perpendicular to the ground support surface). In other examples, the drive spring axis can extend in the vertical direction. The clockwork swing disclosed herein also has a longer run time that can exceed 45-60 minutes based on a user winding the drive spring for about 20 seconds or about 20-30 windings.

[0010] In one example, a clockwork swing assembly includes a frame assembly including a housing, a drive spring positioned within the housing and having a drive spring axis (X3) oriented in a non-vertical direction relative to a vertical plane, a swing arm assembly connected with the frame assembly to receive energy from the drive spring, the swing arm assembly including a swing arm and a swing arm pivot, the swing arm rotatable about a swing arm axis (X1) oriented in a non-horizontal direction relative to a horizontal plane, and a winding mechanism including a winding shaft positioned along the drive spring axis (X3), the winding mechanism having a first end connected with a crank assembly and a second end connected with a spool. The drive spring includes a first end connected with an attachment plate disposed about the winding shaft and a second end connected with the spool such that rotation of the winding shaft winds the drive spring via the spool.

[0011] The winding mechanism can further include a first winding gear disposed about the winding shaft and attached to the attachment plate, and a second winding gear meshed with the first winding gear, and the stored energy released from the drive spring can rotationally drive the first winding gear, which rotationally drives the second winding gear. The escapement assembly can include an escapement shaft connected with the second winding gear that rotationally drives the escapement shaft, the escapement shaft oriented along an escapement axis (X2), the escapement assembly including a carriage coupled with the escapement shaft and configured to rotate about the escapement axis (X2), and a pusher including a first end connected with the carriage and a second end connected with the swing arm assembly, the pusher can drive the swing arm assembly to rotate when the escapement gear is driven by the stored energy released from the drive spring via the connection of the escapement shaft with the second winding gear, and an escapement gear fixed to the escapement shaft and configured to be driven via the second winding gear, the escapement gear including a plurality of teeth.

[0012] The escapement assembly can further include a pawl pivotably attached with the frame assembly, the pawl including pawl teeth that selectively engage with the teeth of the escapement gear to prevent rotation of the escapement gear in the drive direction when the swing arm is in the neutral state, a clip pivotably attached with the carriage and selectively engaged with the teeth of the escapement gear when the swing arm is rotated and the pawl teeth are disengaged from the escapement gear, an amplitude control assembly, and an amplitude control lever. The amplitude control lever includes a first stop and a second stop spaced apart from each other, and each stop is configured to control the swing amplitude.

[0013] The amplitude control assembly can include a drop plate configured to selectively limit the clip travel, and the amplitude control lever can be configured to selectively adjust the position of the drop plate, wherein the drop plate includes an engagement portion configured to engage with a portion of the clip and an attachment configured to engage with a portion of the amplitude control lever. The amplitude control lever can include a closed position. A housing supporting the amplitude control assembly can include a downward stop for limiting further movement of the amplitude control lever, the downward stop corresponding to the closed position of the amplitude control lever. A gap can be provided between the attachment configured to engage with a portion of the amplitude control lever and the housing supporting the amplitude control assembly when the amplitude control lever is in the closed position, such that the drop plate can float.

[0014] According to an alternative, the clockwork swing assembly includes a frame assembly including a housing, a drive spring positioned within the housing and having a drive spring axis (X3) oriented in a non-vertical direction relative to a vertical plane, a swing arm assembly connected with the frame assembly to receive energy from the drive spring, the swing arm assembly including a swing arm and a swing arm pivot, the swing arm being rotatable about a swing arm axis (X1) oriented in a non-horizontal direction relative to a horizontal plane, a winding mechanism including a winding shaft positioned along the drive spring axis (X3), and a torque limiting clutch configured to prevent over-winding of the drive spring.

[0015] The torque limiting clutch can be radially supported at its axis of rotation. An outer lower bearing circumference of the torque limiting clutch can be axially supported by the housing. A low friction spacer can be interposed between the housing and the lower bearing circumference of the torque limiting clutch. An outer upper bearing circumference of the torque limiting clutch can be axially supported by a crown. The winding mechanism can have a first end connected with the crank assembly and a second end connected with the spool. The torque limiting clutch can include a torque clutch spring assembled on the spool, the torque clutch spring being configured to wind when the winding shaft is rotated in a winding direction and to slip when the drive spring is wound beyond a predetermined torque. The winding mechanism can include a winding shaft positioned along the drive spring axis (X3), the winding mechanism having a first end connected with the crank assembly and a second end connected with the spool.

[0016] The torque limiting clutch can include a first housing operably connected with the crank assembly, the first housing including a clutch drive tooth, a clutch hub fixed to the crank assembly, and a clutch pawl pivotably connected with the clutch hub via a biasing element, the clutch pawl being biased by the biasing element to selectively engage the clutch drive tooth. The drive spring can be wound via the crank assembly, the clutch pawl engaged with the clutch drive tooth up to a predetermined torque limit to transfer torque from the crank assembly to the drive spring, and the clutch pawl disengaged from the clutch drive tooth when the torque transferred from the crank assembly to the drive spring exceeds the predetermined torque limit to prevent further transfer of torque from the crank assembly to the drive spring.

[0017] The torque limiting clutch can include an input shaft connected with the crank assembly, an output shaft connected with the drive spring, a cap fixed to the input shaft, and a clutch spool fixed to the output shaft and clamped to the cap. The cap and the spool can be configured to slide relative to each other when a predetermined force is overcome to prevent over-winding of the drive spring.

[0018] The torque limiting clutch can include a shaft connected with the crank assembly, an input hub including at least one catch, and an output hub connected with the shaft, the output hub including at least one protrusion engageable with the catch. The at least one protrusion can be configured to disengage from the at least one catch when a predetermined force from the crank assembly is overcome to prevent the drive spring from being over-tightened. The at least one catch can be a resilient member biased toward engagement with the at least one protrusion. The at least one catch can be pivotally attached to the input hub. A spring can be connected with the at least one catch and bias the at least one catch toward engagement with the at least one protrusion. A low-friction support washer can be located between the housing and the torque limiting clutch, the low-friction support washer mounted in a gear cap of the housing.

[0019] According to another aspect, a clockwork swing assembly includes a frame assembly having an upper end and a lower end, a base member at the lower end of the frame assembly, and an upright frame member extending from the base member to the upper end of the frame assembly, the frame assembly including a housing, a drive spring axis (X3) positioned within the housing and oriented in a non-vertical direction relative to a vertical plane, and a swing arm assembly connected with the frame assembly to receive energy from the drive spring, the swing arm assembly including a swing arm and a swing arm pivot, the swing arm rotatable about a swing arm axis (XI) oriented in a non-horizontal direction relative to a horizontal plane. The upright frame member is welded to the base member.

[0020] The frame assembly can further include a support at the lower end of the frame assembly, the support configured to rest on the ground, and a handle positioned adjacent the upper end of the frame assembly. The support can extend in opposite directions from the base member.

[0021] Additional embodiments are described below. BRIEF DESCRIPTION OF DRAWINGS

[0022] The foregoing summary, as well as the following detailed description of the preferred embodiments of the present disclosure, will be better understood when read in conjunction with the appended drawings. In the drawings:

[0023] Figure 1A is an isometric view of a clockwork child swing assembly.

[0024] Figure 1B is another isometric view of a clockwork child swing assembly.

[0025] Figure 1C is a top view of a clockwork child swing assembly.

[0026] Figure 2 is an isometric view of a clockwork child swing assembly with the housing frame removed.

[0027] Figure 3A is a top perspective view of the frame assembly with the crank assembly in a non-use or storage state.

[0028] Figure 3B is a top perspective view of the frame assembly with the crank assembly in a use state.

[0029] Figure 3C is a schematic view of a crank assembly according to a first embodiment.

[0030] Figure 3D is a schematic view of a crank assembly according to a second embodiment.

[0031] Figure 3E is a schematic view of a crank assembly according to a third embodiment.

[0032] Figure 3F is a schematic view of a crank assembly according to a fourth embodiment.

[0033] Figure 3G is a top perspective view of the frame assembly with the crank assembly in a non-use or storage state according to one example.

[0034] Figure 3H is a top perspective view of the frame assembly with the crank assembly in a use state according to one example.

[0035] Figure 3I is a bottom view of the tower cap of the top of the frame assembly.

[0036] Figure 4A is a perspective view of the upper portion of the clockwork child swing assembly.

[0037] Figure 4B is a side view of the upper portion of the clockwork child swing assembly.

[0038] Figure 4C is a perspective view of the bottom of the drive spring.

[0039] Figure 4D is a perspective cutaway view of the bottom of the drive spring.

[0040] Figure 4E is another perspective view of the bottom of the drive spring and a portion of the frame.

[0041] Figure 4F is another perspective view of the bottom of the drive spring and a portion of the frame according to another example.

[0042] Figure 5A is another perspective view of the upper portion of the clockwork child swing assembly.

[0043] Figure 5B is an exploded perspective view of the escapement assembly.

[0044] Figure 5C is an isometric view of the cradle, pivot housing, and pusher in an assembled state.

[0045] Figure 5D is an isometric view of the cradle, pivot housing, and pusher in a disassembled state.

[0046] Figure 5E is a side cross-sectional view showing various axes of the clockwork child swing assembly.

[0047] Figure 5F is a close-up view of the interface between the pusher and the cradle.

[0048] Figure 5G is a front view of the interface between the pusher and the cradle.

[0049] Figure 5H is a close-up view of a portion of the cradle configured to house the pusher.

[0050] Figure 6A is a front view of the escapement assembly in a first state.

[0051] Figure 6B is a front view of the escapement assembly in a second state.

[0052] Figure 6C is a front view of the escapement assembly in a third state.

[0053] Figure 6D is a front view of the escapement assembly in a fourth state.

[0054] Figure 7A is an isometric view of the amplitude control assembly.

[0055] Figure 7B is a front view of the amplitude control assembly in a first state.

[0056] Figure 7C is a front view of the amplitude control assembly in a second state.

[0057] Figure 7D is a front view of the amplitude control assembly in a third state.

[0058] Figures 8A-8C shows various stages of the pawl safety tooth and the second set of teeth.

[0059] Figure 9A is an isometric view of a torque limiting clutch according to one embodiment.

[0060] Figure 9B is a side view of the torque limiting clutch.

[0061] Figure 9C is a side view of a torque limiting clutch.

[0062] Figure 10A is a perspective view of another example of a frame assembly.

[0063] Figure 10B is a perspective view of a frame assembly. Figure 10A is a close-up view of a portion of the top region of the frame assembly of

[0064] Figure 10C is another close-up view of a portion of the top region of the frame assembly of Figure 10A

[0065] is a top perspective view of a gear assembly according to one example. Figure 11

[0066] is a side view of a torque limiting clutch assembly. Figure 12A

[0067] is another side view of a torque limiting clutch assembly. Figure 12B

[0068] is an exploded perspective view of a torque limiting clutch assembly. Figure 12C

[0069] is a top view of a torque limiting clutch assembly in a first state. Figure 12D

[0070] is a top view of a torque limiting clutch assembly in a second state. Figure 12E

[0071] is a top view of a torque limiting clutch assembly in a third state. Figure 12F

[0072] is a bottom view of the interior of a torque limiting clutch assembly. Figure 12G

[0073] is a perspective view of a torque limiting clutch according to one example. Figure 12H

[0074] is a perspective view of a torque limiting clutch. Figure 12I Figure 12H is an exploded perspective view of the torque limiting clutch shown in

[0075] Figure 12J is a cross-sectional view of a torque limiting clutch according to one example.

[0076] Figure 12K is an exploded perspective view of the torque limiting clutch shown in Figure 12J

[0077] ​​ Figure 12L is Figure 12J a perspective view of the upper side of the torque limiting clutch shown in

[0078] Figure 12M is Figure 12J a perspective view of the lower side of the torque limiting clutch shown in

[0079] Figure 12N is a perspective view of a torque limiting clutch according to an embodiment.

[0080] Figure 12O is Figure 12N a plan view of the torque limiting clutch shown in

[0081] Figure 12P is a sectional view of the torque limiting clutch taken along the plane I-I shown in Figure 12O

[0082] Figure 12Q is a sectional view of the torque limiting clutch taken along the plane II-II shown in Figure 12O

[0083] Figure 13A is an enlarged view of the interface between the frame assembly and the swing arm.

[0084] Figure 13B is another enlarged view of the interface between the frame assembly and the swing arm.

[0085] Figure 14 is a perspective view of the seat frame in one orientation.

[0086] Figure 15A is a first enlarged view of the interface between the swing arm and the swing arm pivot.

[0087] Figure 15B is a second enlarged view of the interface between the swing arm and the swing arm pivot.

[0088] Figure 15C is an enlarged view of the swing arm detached from the swing arm pivot.

[0089] Figure 16A is a perspective view of a clockwork child swing assembly according to an alternative of the present disclosure.

[0090] Figure 16B is Figure 16A a side view of the clockwork child swing assembly shown in

[0091] Figure 16C is Figure 16A a perspective view of the clockwork child swing assembly shown in, showing the seat portion of the seat assembly and the base assembly. ​​

[0092] Figure 16D is Figure 16B is a perspective view of a spring-wound child swing assembly showing a seat portion of a seat assembly and a base assembly.

[0093] Figure 17 is a top perspective view of a crank assembly.

[0094] Figure 18 is a perspective view of a swing arm assembly and a seat assembly positioned above the swing arm assembly.

[0095] Figure 19 is Figure 18 is a first side view of a swing arm assembly and a seat assembly with the seat assembly positioned on the swing arm assembly.

[0096] Figure 20 is Figure 18 is a second side view of a swing arm assembly and a seat assembly with the seat assembly positioned on the swing arm assembly.

[0097] Figure 21A and Figure 21B is a perspective view of a swing arm assembly.

[0098] Figure 21C is Figure 21A and Figure 21B is an exploded perspective view of a support hub of a swing arm assembly.

[0099] Figure 21D is Figure 21C is a bottom perspective view of a portion of a support hub.

[0100] Figure 22 is Figure 18 is an exploded perspective view of a seat assembly.

[0101] Figure 23A and Figure 23B respectively comprise Figure 22 are a top perspective view and a bottom perspective view of a support base of a seat assembly.

[0102] Figure 24A and Figure 24B are perspective views of a connecting assembly and a support hub, respectively, according to an alternative of the present disclosure.

[0103] Figure 25 is a cross-sectional view of a portion of a support base in a locked position. Figure 23B

[0104] is a cross-sectional view of a portion of a support base in an unlocked position. Figure 26 Figure 23B

[0105] ​​ Figure 27 is in a locked position Figure 23B is a cross-sectional view of a portion of the support base, with the support hub positioned therein.

[0106] Figures 28A-28L is a sequential perspective view of an assembly of a gear assembly and torque clutch according to another example.

[0107] Figure 29 is Figure 28L a cross-sectional view.

[0108] Figures 30-33 is a cross-sectional view of an example amplitude control subassembly according to an example.

[0109] Figure 34 is a perspective view of a frame assembly according to an example. DETAILED DESCRIPTION

[0110] Certain terms are used solely for convenience and are not intended to limit the application. The terms "front," "back," "upper," and "lower" designate directions in the drawings to which reference is made. The terms "inwardly" and "outwardly" refer to directions toward and away from, respectively, the center of the components shown in the drawings. The term "at least one of a, b, or c" (where a, b, and c represent items in a list of items) means any of items a, b, or c individually or any combination of two or more of items a, b, and c. This term encompasses the phrases "a, b, or c," "at least one of a, b, or c," and "at least one of a, b, or c," as well as similar phrases.

[0111] As shown in Figures 1A-1C , generally disclosed herein is a clockwork swing assembly 10. As shown in Figure 2 , Figure 4B and Figure 5E , the clockwork swing assembly 10 includes a swing arm assembly 12 that includes a swing arm 25 and a swing arm pivot 27 having a swing arm axis (XI). As shown in Figure 4A , the swing arm pivot 27 can generally include a pivot housing 27a and at least one bearing 27b. For example (but not limitation), the at least one bearing 27b can include two bearings, a first bearing in an upper region of the pivot housing 27a and a second bearing in a lower region of the pivot housing 27a. The bottom of the pivot housing 27a can be supported by a portion of the frame assembly 35a, such as an upright frame member 35c, which will be described in greater detail herein.

[0112] As shown in Figures 5C-5DAs shown and described in greater detail herein, the pivot housing 27a can include an opening 27c configured to receive a portion of the push member 90 (i.e., the first end 90a of the push member 90). The pivot housing 27a is configured to support the swing arm 25, and the swing arm 25 pivots about the swing arm pivot 27. The swing arm 25 can include a first end 25a configured to interface with the swing arm pivot 27 and a second end 25b configured to support the seat frame 15. The housing 26 can be provided to enclose the interface between the first end 25a of the swing arm 25 and the swing arm pivot 27.

[0113] The swing arm axis (XI) can be oriented in a non-horizontal direction or at an angle relative to the ground or a horizontal plane (PI) along the x-axis. In one aspect, the swing arm axis (XI) can be oriented in a non-vertical direction or at an angle relative to a vertical plane (P2). The angle (θ1) between the swing arm axis (XI) and the horizontal plane (PI) is shown. Figure 4B The swing arm axis (XI) can be oriented in a non-horizontal direction or at an angle relative to the ground or a horizontal plane (PI) along the x-axis. In one aspect, the swing arm axis (XI) can be oriented in a non-vertical direction or at an angle relative to a vertical plane (P2). The angle (θ1) between the swing arm axis (XI) and the horizontal plane (PI) is shown.

[0114] The clockwork swing assembly 10 also includes a drive spring 60 having a drive spring axis (X3). The drive spring axis (X3) can be oriented in a non-vertical direction or at an angle relative to a vertical plane (P2) along the y-axis, and can be oriented at an angle relative to the swing arm axis (XI). In one aspect, the drive spring axis (X3) can be oriented in a non-horizontal direction or at an angle relative to the ground or a horizontal plane (PI) along the x-axis. Those skilled in the art will recognize that the vertical plane (P2) is perpendicular to the horizontal plane (PI). The angle (θ3) between the drive spring axis (X3) and the vertical plane (P2) is shown. Figure 4BAs shown. The drive spring axis (X3) can be at an angle of 5 to 20 degrees relative to the vertical plane (P2). Those skilled in the art will understand that, depending on the arrangement of any associated bevel gears, in another configuration, the drive spring axis (X3) can be at an angle greater than 20 degrees relative to the vertical plane (P2). Preferably, the drive spring axis (X3) can be at an angle of 5 to 15 degrees relative to the vertical plane (P2). More preferably, the drive spring axis (X3) can be at an angle of 5 to 10 degrees relative to the vertical plane (P2). In one example, the drive spring axis (X3) can be at an angle of 7 degrees relative to the vertical plane (P2). The orientation and angle of the drive spring axis (X3) can be selected to optimize the stability of the spring-loaded oscillating assembly 10 while also ensuring that the center of gravity of the spring-loaded oscillating assembly 10 is positioned relative to the base assembly 35b to minimize the risk of any accidental tipping.

[0115] The wind-up oscillating assembly 10 also includes an escapement assembly 70 having an escapement axis (X2). The escapement axis (X2) may be angled relative to the swing arm axis (X1). The escapement axis (X2) may be substantially parallel to the ground or a horizontal plane (P1). Alternatively, those skilled in the art will understand that the escapement axis (X2) may be angled relative to the ground or a horizontal plane (P1).

[0116] like Figure 2 , Figure 4B and Figure 5E As shown, the swing arm axis (X1), escapement axis (X2), and drive spring axis (X3) can be at an angle relative to each other. Figure 4B As shown, the swing arm axis (X1), escapement axis (X2), and drive spring axis (X3) can be angled relative to each other. In one embodiment, the relative angle between any one of the first, second, and / or third axes (X1, X2, X3) can be from 0 degrees to 90 degrees. Those skilled in the art will understand that these angles can vary depending on the specific configuration required for the clockwork spring assembly 10. Furthermore, in another embodiment, the first, second, and / or third axes (X1, X2, X3) can be arranged at any relative angle and can be arranged in multiple different planes.

[0117] Return to reference Figure 1A and Figure 1B In addition to the swing arm 25, the swing arm assembly 12 may also include an adjustment assembly 20 and a seat frame 15. The adjustment assembly 20 may be configured to adjust the tilt angle of the seat frame 15, and the adjustment assembly 20 may be released or engaged via a button, lever, or other actuation / adjustment feature. The seat frame 15 may be configured to be adjustable from 0 degrees (i.e., a plane) relative to the horizontal plane (in either the positive or negative direction) to a tilt of at least 20 to 30 degrees relative to the horizontal plane.

[0118] In contrast to an over-the-top spring assembly that requires vertical space to support the drive spring, the spring-driven swing assembly 10 disclosed herein positions the drive spring 60 laterally adjacent to or alongside the seat frame 15. Thus, the drive spring 60 is not positioned over the seat frame 15.

[0119] The spring-driven swing assembly 10 also includes a frame assembly 35a, a base assembly 35b, and an upright frame member 35c. The frame assembly 35a, including the upright frame member 35c and the base assembly 35b, can include an outer shell or housing that generally encloses or encompasses the internal components (e.g., the drive spring 60).

[0120] The frame assembly 35a can include a support 37 at a lower end and a handle 36 at an upper end. The support 37 is configured to provide an additional stable surface for engagement with the ground. The support 37 can be formed as a protrusion that is large enough to accommodate a user’s foot on the upper side so that the user can step on the support 37 and stabilize the spring-driven swing assembly 10 while tightening the drive spring 60 via the crank assembly 40. The support 37 can extend outwardly from the rest of the frame assembly 35a. For example, but not by way of limitation, the support 37 can extend at least 3 inches outwardly from the frame assembly 35a. In an embodiment, but not by way of limitation, the support 37 can have a height of less than 1 inch. The support 37 preferably extends from the frame assembly 35a in a direction opposite the base assembly 35b.

[0121] The handle 36 can be provided as a lip, edge, or other type of recess formed on the frame assembly 35a. Those of ordinary skill in the art will appreciate that the handle 36 can also be formed on other areas of the spring-driven swing assembly 10 other than the frame assembly 35a. The handle 36 is sized or configured to accommodate a user’s hand to provide additional support for the spring-driven swing assembly 10 while tightening the drive spring 60. The handle 36 can also be used to lift or otherwise move the spring-driven swing assembly 10. For example, but not by way of limitation, the handle 36 can have a depth of at least 1 inch, and preferably at least 2 inches. The handle 36 is configured to allow a user to more easily move the spring-driven swing assembly 10 and improve the overall mobility of the spring-driven swing assembly 10.

[0122] The base assembly 35b can be formed as two legs 39a, 39b that extend from the upright frame member 35c, which is shown in a top view in FIG. 4. In one example, the base assembly 35b can include two curved or arcuate legs 39a, 39b that generally have a U-shaped profile or a horseshoe-shaped profile. As shown in FIG. 4, the base assembly 35b can include a first leg 39a and a second leg 39b that are curved or arcuate in shape. The first leg 39a and the second leg 39b can be curved or arcuate in shape so that the base assembly 35b has a U-shaped profile or a horseshoe-shaped profile. Figure 1C Figure 1C ​As shown, the profile of the base assembly 35b can generally at least partially overlap or fall within the profile or outer shape of the seat frame 15 (as shown at the ends of the legs 39a, 39b). Those of ordinary skill in the art will appreciate that the profile of the base assembly 35b can vary.

[0123] The clockwork swing assembly 10 also includes a crank assembly 40 that provides an interface for a user to impart motion or energy onto the drive spring 60. The crank assembly 40 can generally be disposed on the frame assembly 35a. The crank assembly 40 can be disposed on an upper surface of the frame assembly 35a. Those of ordinary skill in the art will appreciate that the crank assembly 40 can be disposed on other portions or areas of the frame assembly 35a, or on any other portion of the clockwork swing assembly 10.

[0124] As shown in Figure 3A and Figure 3B , the crank assembly 40 can include a crank handle 44 configured to extend from the frame assembly 35a. The crank handle 44 provides input to the drive spring 60 about a crank pivot 46. The crank handle 44 can be configured to fold outward from the frame assembly 35a in a use state, and can be configured to fold into a pocket 47 defined on the frame assembly 35a in a storage state. A handle 42 can be disposed on the crank handle 44 configured to be engaged by a user when tightening the drive spring 60.

[0125] An energy level indicator can be provided for the clockwork swing assembly 10. In one example, an energy level indicator 120 is shown. In one example, the energy level indicator 120 can be a torque sensor, and can be operably disposed between the drive spring 60 and the crank assembly 40. The energy level indicator 120 can provide a marker, such as a gauge, that shows the amount of energy stored by the drive spring 60. A user can quickly determine how much time is left to continue a swing motion, and decide to further engage the crank assembly 40. The energy level indicator 120 can include a sensor or spring disposed in series with the drive spring 60. Those of ordinary skill in the art will appreciate that various structures for measuring energy in the drive spring 60 are possible. Further, the location and specific form of the energy level indicator 120 can vary. Figure 3A Figure 3B As shown in

[0126] As shown in Figures 3C-3F , various structures can be provided for the crank assembly 40. As shown in Figure 3C ​As shown, the arm 144 of the crank assembly 40 can operate as a handle that rotates outward in a use or activation position and can be eccentrically disposed relative to the middle portion of the frame. As shown, Figure 3D As shown, the arm 244 of the crank assembly 40 can operate as a handle that also rotates outward from the frame. Increasing the arm length can provide greater input to the drive spring 60. As shown, Figure 3E As shown, the arm 344 of the crank assembly 40 can translate radially outward to operate as a handle. As shown, Figure 3F As shown, the arm 444 of the crank assembly 40 can have a rotating portion 444a that is configured to be grasped by a user.

[0127] Figure 3G-Figure 3I Additional views of a crank assembly according to another example are provided. In one configuration, a tower cap 540 is provided that is generally attached to the top of the frame assembly. The tower cap 540 can include an opening 542 that is configured to allow the arm 544 of the crank assembly 40 to extend therethrough. The arm 544 (which can also be referred to as a knob) can be configured to rotate to tighten the drive spring 60. The arm 544 can be configured to be biased to a closed position or non-use position by a spring or biasing element, which can serve as a safety feature. The tower cap 540 can be snap fit onto the body of the frame assembly 35a. The tower cap 540 can include an inner wall 546 that corresponds to the wall of the first housing 402 of the torque limiting clutch assembly 400 (shown in more detail in Figures 12A-12G and described in more detail herein), which creates a tight fit between the tower cap 540 and the first housing 402 with minimal rotational movement (e.g., wobble) therebetween. The inner wall 546 also helps to align the tower cap 540 with the clutch assembly 400 during assembly. The tightening knob or arm 544 can be configured to pivot downward to be flush with the tower cap 540 for safety purposes and a more tidy aesthetic appearance.

[0128] As shown, Figure 4A and Figure 4B As shown in detail, the clockwork swing assembly 10 also includes a tightening mechanism 50 that is disposed between the crank assembly 40 and the drive spring 60. The tightening mechanism 50 is generally configured to provide an interface between the crank assembly 40 and the drive spring 60 such that cranking input from a user is converted into tightening of the drive spring 60. As shown, Figure 4B The tightening mechanism 50 can include a tightening shaft 55 that is connected to the crank assembly 40 at a first end 55a of the tightening shaft 55. As shown, Figures 4D-4EAs shown, the winding shaft 55 can extend inside the drive spring 60 and can be connected with a quiet wind spool 105 at a second end 55b of the winding shaft 55. Alternative arrangements of the winding shaft 55 can be provided.

[0129] Referring to the winding mechanism 50 as shown in Figure 4A and Figure 4B The attachment plate 52 can be attached with a first winding gear 54 disposed about the winding shaft 55 and configured to matingly engage with a second winding gear 56. In one example, the first winding gear 54 and the second winding gear 56 can be bevel gears. The second winding gear 56 can be connected with the escapement assembly 70. In one configuration, the second winding gear 56 is configured to rotationally drive the escapement shaft 75 (as shown in Figures 5A-5B Alternative arrangements can be provided to transfer motion or energy from the drive spring 60 to the escapement assembly 70.

[0130] As shown in Figures 4A-4E The drive spring 60 can include a first end 60a connected with the attachment plate 52 and a second end 60b connected with the quiet wind spool 105 such that rotation of the winding shaft 55 winds the drive spring 60 via the quiet wind spool 105.

[0131] As shown in Figures 4C-4E A power tube 66 is provided that centers the drive spring 60 and prevents the drive spring 60 from snaking or otherwise tangling during the winding process. A first bearing 64 can be provided to support both the winding shaft 55 and the power tube 66. A second bearing 106 can be provided between a portion of the upright frame member 35c and the winding shaft 55.

[0132] The quiet wind spool 105 can define a connector 62 that is connected with the second end 60b of the drive spring 60. Clockwise rotation of the winding shaft 55 causes the quiet wind spool 105 to rotate, which winds the drive spring 60 via the connector 62. A connector 108 can be provided that connects the winding shaft 55 with the quiet wind spool 105. The connector 108 can include a set screw, knurled connector, or any other attachment structure that connects the winding shaft 55 with the quiet wind spool 105.

[0133] A slip clutch spring 100 can also be provided, which is generally configured to prevent the winding shaft 55 from rotating in a non-winding direction. Turning the winding shaft 55 in the winding direction (e.g., the clockwise direction as shown in the figures) causes the slip clutch spring 100 to open and slip. Conversely, turning the winding shaft 55 in the non-winding direction causes the slip clutch spring 100 to tighten around the silent winding spool 105. When the user stops winding the winding shaft 55, the counterclockwise force on the silent winding spool 105 causes the slip clutch spring 100 to tighten. This slip clutch spring 100 prevents energy from being released from the drive spring 60 whenever the drive spring 60 is in the wound position, whether during the winding process or when the swing apparatus is in operation. Thus, in the event of a mechanical failure of the escapement, the winding crank (i.e., knob, spring, etc.) does not spin uncontrollably releasing energy, which provides a safety feature and prevents injury to the user. As Figures 4C-4E A bracket 35d can be provided that is fixed to the upright frame member 35c, as shown. Thus, the rotational torque of the drive spring 60 is resisted by the attachment of the slip clutch spring 100 to the pin 102, which is connected to the bracket 35d or the upright frame member 35c. For illustrative purposes only, Figure 4E The drive spring 60 is shown being pulled upward from the frame bottom. As Figure 4F One end 100' of the slip clutch spring 100 can be fixed to a portion of the upright frame member 35c or bracket 35d, as shown.

[0134] The escapement assembly 70 is configured to control the release of energy from the drive spring 60 and is configured to provide discrete and controlled bursts of energy to drive the seat frame 15. The escapement assembly 70 is also configured to prevent the drive spring 60 from being accidentally released. The escapement assembly 70 can include an escapement gear 74 that includes a plurality of teeth 74a and is configured to be driven via the connection of an escapement shaft 75 to the second winding gear 56. The escapement gear 74 can be fixed to the escapement shaft 75. U.S. Patent 6,283,870, which is incorporated by reference herein as if fully set forth herein, discloses one such escapement assembly.

[0135] Figures 5A-5B The escapement assembly 70, as well as the drop plate 85 and the amplitude control lever 95, are shown in more detail in FIG. 2. The escapement assembly 70 can also include a carrier 72, a pawl 76, an actuator 78, a dog 80, and a pusher 90, each of which will be described in more detail herein.

[0136] The pawl 76 is pivotably supported at a pawl pivot 76c. In one aspect, the pawl pivot 76c can be pivotably attached with a portion of the frame assembly 35a, such as the upright frame member 35c. The force of the drive spring 60 biases the escapement gear 74 to rotate in the drive direction, such as the clockwise direction. However, in the initial state, the pawl teeth 76a are engaged with the teeth 74a of the escapement gear 74 to prevent the escapement gear 74 from rotating clockwise and also to prevent the drive spring 60 from unwinding at the same time. The clockwise bias of the escapement gear 74 due to the force of the drive spring 60 causes the escapement gear 74 to exert a force on the pawl 76 that keeps the pawl teeth 76a engaged with the escapement gear 74. Without this engagement, the pawl weight 76e would cause the pawl 76 to rotate clockwise due to gravity, thereby rotating out of engagement with the escapement gear 74.

[0137] The carrier 72 is coupled with the escapement shaft 75 and is configured to rotate about the escapement axis (X2). The carrier 72 is also coupled with a first end 90a of the pusher 90. A second end 90b of the pusher 90 is coupled with the swing arm assembly 12. When the escapement gear 74 is driven via the connection of the escapement shaft 75 with the second tensioning gear 56, the carrier 72 pushes the swing arm assembly 12 to rotate during a power stroke and is pushed by the swing arm assembly 12 during a non-power stroke. The swing arm assembly 12 is configured to swing in a pendulum-like motion. During the power stroke, energy from the drive spring 60 is transferred through the escapement assembly 70 to drive the swing arm assembly 12 in a first direction. Upon reaching the end of the stroke or swing, inertia then drives the swing arm assembly 12 in a second direction opposite the first direction. This process continues as long as there is remaining stored energy from the tensioning of the drive spring 60.

[0138] The clip 80 is pivotably secured to the carrier 72 at a clip pivot 80c such that the clip 80 moves with the carrier 72 as the carrier 72 rotates with the swing arm assembly 12 about the escapement axis (X2). The shape of the clip 80 and the configuration of the clip teeth 80a, 80d are such that the clip weight causes the clip 80 to rotate clockwise about the clip pivot 80c to disengage the clip teeth 80a from the teeth 74a of the escapement gear 74.

[0139] The actuator 78 is coupled with the escapement shaft and is configured to rotate about the escapement axis (X2). The actuator 78 is configured to selectively engage with the clip 80 through a clip engagement surface 78b that engages with the clip control arm 80b. The actuator 78 is also configured to selectively engage with the pawl 76 via a pawl engagement surface 78a that engages with the pawl control arm 76b. This selective engagement controls the movement of the clip 80 and the pawl 76. The actuator 78 also includes an actuator weight 78c that is positioned such that the actuator 78 is biased in the clockwise direction when not acted upon by the pawl 76 or the clip 80.

[0140] The pusher 90 operably connects the escapement assembly 70 with the swing arm assembly 12. The pusher 90 is generally configured to convert rotation from the escapement assembly 70 about the escapement axis (X2) into a swing or oscillation of the swing arm 25 about the swing arm axis (XI). In one example, the pusher 90 can be a rigid wire. Those of ordinary skill in the art will appreciate that the pusher 90 can include a pair of bevel gears or any type of mechanical linkage. For example, in the embodiment shown in Figure 13A and Figure 13B The swing arm pivot 127 can include a first bevel gear 190a. A second bevel gear 190b can be configured to drivably engage the first bevel gear 190a. The second bevel gear 190b can be connected with the carrier 72 or another portion of the frame assembly. In one configuration, the second bevel gear 190b can be integrally formed with the carrier 72. The drive connection between the bevel gears 190a, 190b transmits the swing or oscillation motion to the swing arm 25 and otherwise provides the same functionality as the pusher 90 and its related components. The configuration including bevel gears can be configured to provide a 1 : 1 rotational motion ratio between the first bevel gear 190a and the second bevel gear 190b, thereby providing a more efficient oscillation configuration.

[0141] The pusher 90 includes a first end 90a connected with the carrier 72 and a second end 90b connected with the swing arm pivot 27. The pusher 90 can be configured to rotate and move with multiple degrees of freedom. The first end 90a and the second end 90b of the pusher 90 can be held within the carrier 72 and the swing arm pivot 27 with a predetermined amount of slack or a predetermined tolerance such that there can be some predetermined amount of play when the pusher 90 is driven back and forth for the oscillation motion.

[0142] As shown in Figure 5C and Figure 5D The first end 90a and the second end 90b of the pusher 90 can include a bent or angled portion relative to the body of the pusher 90. For example, the first end 90a can be bent upward and the second end 90b can be bent downward. The first end 90a is configured to be held in the opening 72a of the carrier 72. The opening 72a in the carrier 72 can include a through hole and at least one tapered region adjacent to the through hole. The opening 27c in the pivot housing 27a can also include a through hole and at least one tapered region adjacent to the through hole. By not rigidly securing the ends 90a, 90b relative to the carrier 72 and the pivot housing 27a, the pusher 90 is allowed to swing more freely, which results in an increased swing time.

[0143] Figures 5E-5H Other aspects of the pusher 90 configuration are shown. Referring to Figure 5EEnergy needs to be transferred from the escapement axis (X2) to the swing arm pivot axis (X1). These axes can be arranged non-parallel to each other, and in one configuration, can be angled at 40 to 60 degrees relative to each other. A pusher 90 is arranged between the bracket 72 and the pivot piece housing 27a in order to provide improved bending strength to transfer torque. The connection of the pusher 90 to both the bracket 72 on the escapement axis (X2) and the pivot piece housing 27a on the swing arm pivot axis (X1) is configured to allow self-alignment of the pusher 90 to the connection holes 72a on the respective bracket 72 and the connection holes 27c on the pivot piece housing 27a. Those of ordinary skill in the art will appreciate that the connection of the pusher 90 to the pivot piece housing 27a is analogous. The end 90a, 90b of the pusher 90 can be rounded or cylindrical in profile. As shown in FIGS. 8 and 9, an arcuate contact surface provided within the connection hole 27c of the pivot piece housing 27a can provide an engagement surface for the first end 90a of the pusher 90. Although the element 90 is denoted as a pusher 90, those of ordinary skill in the art will appreciate that any linkage or connection can be provided between the bracket 72 and the pivot piece housing 27a that is configured to exert a pushing or pulling force (i.e., tension). Figure 5C and Figure 5D As shown in FIGS. 8 and 9, an arcuate contact surface provided within the connection hole 27c of the pivot piece housing 27a can provide an engagement surface for the first end 90a of the pusher 90. Although the element 90 is denoted as a pusher 90, those of ordinary skill in the art will appreciate that any linkage or connection can be provided between the bracket 72 and the pivot piece housing 27a that is configured to exert a pushing or pulling force (i.e., tension).

[0144] Figures 6A-6D Various states of the clockwork swing assembly 10 are shown. Figure 6A A non-powered phase is shown generally, Figure 6B A transition phase from the non-powered phase to the powered phase is shown, Figure 6C The powered phase is shown, and Figure 6D A transition phase from the powered phase to the non-powered phase is shown.

[0145] Figure 6A The escapement assembly 70 is shown in an intermediate position (i.e., non-powered phase) when the drive spring 60 is fully wound. As shown in FIG. 6, Figure 6A the pawl teeth 76a are engaged with the teeth 74a of the escapement gear 74 to prevent the escapement gear 74 from rotating clockwise (due to energy from the wound drive spring 60) and also to prevent the drive spring 60 from inadvertently unwinding suddenly. In this state, the clamp engagement surface 78b on the actuator 78 and the clamp control arm 80b are disengaged from each other. Figure 6A A non-powered state is shown generally, with the clamp 80 fully disengaged, the pawl 76 engaged, and rotation configured to occur in a counterclockwise direction for the actuator 72.

[0146] Figure 6BThe swing arm assembly 12 and the carriage 72 are shown rotating counterclockwise due to the initial push of the swing arm assembly 12 by the user. This movement is counter to the spring force from the drive spring 60, which normally drives the swing arm assembly 12 to rotate in the clockwise direction. As Figure 6B shown, the inertia from the initial push causes the swing arm assembly 12 to move in the counterclockwise direction and drive the pusher 90, which then drives the carriage 72 to begin rotating in the counterclockwise direction. This movement of the carriage 72 also drives the clevis 80 counterclockwise. The movement of the clevis 80 in the counterclockwise direction causes the clevis control arm 80b to engage the clevis engagement surface 78b of the actuator 78. This engagement causes the clevis 80 to rotate about the clevis pivot 80c and the clevis teeth 80a are driven into engagement with the teeth 74a of the escapement gear 74. The inertia from the swing arm assembly 12 is imparted to the clevis teeth 80a such that the torque from the drive spring 60 is now between the seat frame at one end (i.e., the upright frame member 35c) and the clevis 80 at the other end. Since the clevis 80 is connected to the carriage 72, any movement imparted to the carriage 72 from the swing arm assembly 12 also drives the clevis 80. The engaged clevis 80 then rotates the escapement gear 74 counterclockwise and releases the force on the pawl 76.

[0147] Due to the pawl weight 76e, the pawl 76 is biased by gravity and then rotates clockwise and disengages from the escapement gear 74. During this phase, the torque force imparted to the pawl 76 from the escapement gear 74 is released and the pawl 76 is temporarily disengaged from the escapement gear 74. The clevis 80 (which is now engaged to the escapement gear 74) transfers the spring torque from the escapement gear 74 into the carriage 72, providing energy to drive the swing arm assembly in the counterclockwise pendulum motion.

[0148] Figure 6C The power stroke phase is shown, in which the swing arm assembly 12 rotates clockwise. During this phase, the drive spring 60 exerts a force that drives the escapement gear 74 in the clockwise direction. During this phase, the pawl 76 is disengaged from the escapement gear 74 and the clevis 80 is engaged with the escapement gear 74. The escapement gear 74 is configured to drive the clevis 80 to rotate clockwise, which in turn drives the carriage 72 clockwise. The carriage 72, which is fixed to the pusher 90, then applies this driving motion to the swing arm assembly 12 through the pusher 90, thereby powering the swing motion. During this phase, the pawl 76 remains disengaged, which is necessary to allow the escapement gear 74 to rotate in the clockwise direction. As the clevis 80 rotates clockwise, the clevis 80 remains in contact with the actuator 78. Based on this engagement, the clevis 80 is configured to control the timing of the clockwise rotation of the actuator 78. The actuator 78 is normally biased to rotate clockwise due to gravity (i.e., due to the actuator weight 78c) and the clevis 80 controls this rotation until the actuator 78 engages with the pawl 76.

[0149] Referring to Figure 6D As the swing assembly transitions from the power phase to the non-power phase, the actuator 78 engages the pawl 76 with the escapement gear 74 (i.e., via engagement between the pawl engagement surface 78a and the pawl control arm 76b). During this phase, the carriage 72 continues to rotate clockwise, releasing the clip 80 from engagement with the actuator 78 (i.e., disengaging the clip control arm 80b from the clip engagement surface 78b), which allows the clip 80 to rotate clockwise about the clip pivot 80c to disengage from the escapement gear 74. After the actuator 78 drops the pawl 76 into the next tooth 74a of the escapement gear 74, torque is transferred to the pawl tooth 76a as the pawl tooth 76a engages the escapement gear 74. During this step, the clip 80 disengages from the escapement gear 74 due to gravity (i.e., due to the shape of the clip and its pivot position). Thus, power is no longer provided to the swing arm assembly 12 via the drive spring 60, even though the swing arm assembly 12 is still rotating in the clockwise direction. Shortly after the pawl tooth 76a engages the escapement gear 74, the pawl tooth 76a is no longer held in place by the actuator 78. However, the pawl 76 controls the position of the actuator 78 and prevents the actuator 78 from further rotating clockwise due to gravity. The swing arm assembly 12 continues to swing clockwise for the remainder of the power stroke, and then the swing arm assembly 12 begins to travel counterclockwise. This occurs after the momentum of the swing arm assembly 12 from the power stroke has ceased.

[0150] When the swing assembly transitions back to the fully non-powered phase, the carriage 72 and swing arm assembly 12 begin to travel counterclockwise, the clip 80 engages the actuator 78, the actuator 78 causes the clip tooth 80a to rotate counterclockwise about the clip pivot 80c, and engages the next tooth of the escapement gear 74. After this step, the power stroke is repeated.

[0151] Referring to Figures 7A-7D A swing amplitude control assembly 92 can be provided that generally controls the swing amplitude. The swing amplitude control assembly 92 can include a drop plate 85 configured to selectively limit the travel of the clip 80, and an amplitude control lever 95 configured to selectively adjust the position of the drop plate 85. The amplitude control lever 95 can be configured to set a limit to the swing amplitude. If the actual swing amplitude begins to exceed the limit set by the amplitude control lever 95, the swing amplitude control assembly 92 prevents the escapement assembly 70 from releasing additional energy from the drive spring 60 to the swing arm assembly 12.

[0152] The drop plate 85 can include an engagement portion 85a configured to engage with a portion of the clamp 80 via a control edge 85d, a recess 85b adjacent to the control edge 85d, and an appendage 85c configured to engage with a portion of the amplitude control lever 95. A user can manually engage the amplitude control lever 95 to adjust the swing amplitude. The amplitude control lever 95 can include a first stop 95a and a second stop 95b spaced apart from each other. Each stop 95a, 95b can be configured to engage with the appendage 85c of the drop plate 85. In one example, the second stop 95b can be formed on a portion of the frame or housing.

[0153] The drop plate 85 is configured to rotate with the cradle 72 by frictional engagement between the engagement portion 85a of the drop plate 85 and the clamp control arm 80b. The rotation of the drop plate 85 is limited by the first stop 95a and the second stop 95b. If the actual swing amplitude is within the predetermined limit set by the amplitude control assembly 92, the clamp 80 remains engaged with the engagement portion 85a of the drop plate 85, thereby preventing the drop plate 85 from dropping. The drop plate 85 includes a slot 85e through which the escapement shaft 75 is configured to extend, which allows the drop plate 85 to move or drop. When the amplitude control lever 95 is rotated upward or counterclockwise, a greater swing amplitude is allowed. The appendage 85c of the drop plate 85 is allowed to rotate a greater distance between the stops 95a, 95b, such that the clamp control arm 80b remains in contact with the engagement portion 85a of the drop plate 85 for a longer time when the swing arm assembly 12 swings higher. As Figure 7B and Figure 7C the drop plate 85 will not drop as long as the engagement portion 85a of the drop plate 85 is engaged with the clamp control arm 80b.

[0154] Figure 7D A situation or stage is shown in which the actual swing amplitude exceeds the predetermined or set limit. As Figure 7D shown, the drop plate 85 drops such that the clamp control arm 80b engages beyond the control edge 85d and is housed within the recess 85b adjacent to the control edge 85d. The control edge 85d of the drop plate 85 drives the clamp tooth 80a into the same tooth 74a on the escapement gear 74 that it was previously engaged with, rather than the next tooth 74a on the escapement gear 74. Thus, the control edge 85d drives the clamp tooth 80a into engagement with the escapement gear 74 before the actuator 78 additionally drives the clamp tooth 80a back into engagement with the escapement gear 74. Furthermore, the control edge 85d of the drop plate 85 is angled, thereby allowing the clamp control arm 80b to push the drop plate 85 upward when swinging counterclockwise.

[0155] If the swing arm assembly 12 swings beyond a predetermined amplitude limit, the drop plate 85 drops down, causing the collet teeth 80a to engage the escape wheel 74, and then rises. This process is repeated for each swing cycle until the amplitude drops below the predetermined limit. When the swing arm assembly 12 travels clockwise (i.e., in the direction in which the drive spring 60 releases its energy), the drop plate 85 drops down, and the collet control arm 80b is received in the recess 85b of the drop plate 85.

[0156] The pawl teeth 76a and the collet teeth 80a are shown in various states relative to the escape wheel 74 (and more specifically relative to the first set of teeth 74a on the escape wheel 74). The pawl safety teeth 76d and the collet safety teeth 80d are shown. The second set of teeth 74b on the escape wheel 74 are configured to engage the pawl safety teeth 76d and the collet safety teeth 80d. The pawl safety teeth 76d and the collet safety teeth 80d are generally configured to engage corresponding teeth in the second set of teeth 74b on the escape wheel 74 when the drive spring 60 is wound up to prevent the drive spring 60 from accidentally unwinding. The collet safety teeth 80d can be configured to prevent the collet 80 from dropping too far when the collet 80 disengages from the escape wheel 74 during a swing.

[0157] Figures 8A-8COther features of the pawl safety teeth 76d are shown. Those of ordinary skill in the art will appreciate that the description provided herein regarding the function of the pawl safety teeth 76d will also apply to the clip safety teeth 80d. For purposes of illustration, a portion of the pawl 76 that supports the pawl safety teeth 76d is not shown in order to illustrate the engagement between the pawl safety teeth 76d and the second set of teeth 74b on the escape wheel 74. During normal operation, as the pawl teeth 76a and clip teeth 80a are regularly driven in and out relative to the escape wheel 74, the pawl safety teeth 76d and clip teeth safety teeth 80d generally follow the respective pawl teeth 76a and clip teeth 80a. In the event of a potential failure in one of the components (e.g., a clip tooth 80a breaking), the pawl 76 is expected to re-engage to prevent high torque from the drive spring 60 in the escape wheel 74 regardless of actuator position and escapement. If the clip teeth 80a are inoperable, the clip 80 cannot prevent any relative motion of the escape wheel 74 and there is a risk of high uncontrolled torque from the drive spring 60 being released on the escape wheel 74. In this situation, the second set of teeth 74b, which are in the process of starting high speed rotation, are configured to contact the pawl safety teeth 76d in a high speed manner (rather than the normally counterclockwise force created by gravity). This forcibly pulls the pawl teeth 76a down into the gap between the first set of teeth 74a, which is completely independent of any motion of the actuator 78 that normally controls the motion of the pawl 76. The pawl teeth 76a are then driven toward the escape wheel 74 with considerable energy and momentum. In this state, the escape wheel 74 is rotating at high speed in the clockwise direction. The engagement of the pawl teeth 76a with the first set of teeth 74a stops the wheel rotation. If the pawl teeth 76a are damaged or otherwise inoperable, and the clip teeth safety teeth 80d must stop the uncontrolled rotation of the escape wheel 74, this same type of configuration occurs.

[0158] Another example of an amplitude control assembly is shown in Figures 30-33 .

[0159] As an additional feature, a torque limiting clutch can also be implemented with the clockwork swing assembly 10 that is configured to prevent a user from over-winding the drive spring 60 beyond a predetermined torque limit. The torque limiting clutch can also be configured to slip if wound in the opposite or non-winding direction.

[0160] With particular reference to Figures 9A-9C , a torque limiting clutch can be provided to prevent damage from over-winding. The silent winding spool 105 can be split into an upper portion 105a and a lower portion 105b in order to provide a torque limiting configuration for the drive spring 60. During winding, torque is transferred from the lower portion 105b to the upper portion 105a by a torque clutch spring 900.

[0161] The torque clutch spring 900 is configured such that its inner diameter is smaller than the outer diameter of the deadening tension spool 105 before it is assembled onto the deadening tension spool 105. The torque clutch spring 900 is assembled onto the upper portion 105a and lower portion 105b of the deadening tension spool 105 by temporarily expanding the inner diameter of the torque spring 900. This is achieved by applying a torque force to the torque clutch spring 900. Once assembled onto the deadening tension spool 105, the torque force is removed and the torque spring 900 clamps the upper portion 105a and lower portion 105b of the deadening tension spool 105. This tightening of the torque clutch spring 900 on the deadening spool portion 105 allows the torque to be transferred from the lower portion 105b to the upper portion 105a.

[0162] During tensioning, the torque from the tensioning shaft 55 rotates the lower portion 105b. This torque is then transferred to the upper portion 105a and the rotation of the upper portion 105a tensions the drive spring 60. The winding direction of the torque clutch spring 900 is such that when the tensioning torque is transferred, the coils of the torque clutch spring 900 are configured to slip at a given or predetermined torque. However, when the torque of the fully tensioned drive spring 60 is resisted, the torque clutch spring 900 locks the upper portion 105a to the lower portion 105b of the deadening tension spool 105. Under the connection of the lower portion 105b and the pin 102, the torque is further resisted by the slip clutch spring 100.

[0163] Those of ordinary skill in the art will appreciate that various modifications can be made to the clockwork swing assembly. For example, as Figure 10B , Figure 10C and Figure 11As shown, in one configuration, a gear assembly 300 can be included to facilitate easier tightening of the swing set. The gear assembly 300 can include a plurality of gears. For example, a crank gear 302 can be connected with a shaft 140 that is connected with the crank assembly 40. In one example, the crank gear 302 can be directly engaged with a spring gear 306. In one example, an idler or intermediate gear 304 can be disposed between the crank gear 302 and the spring gear 306. The spring gear 306 can be rotationally fixed with the tightening shaft 55. The idler gear 304 can be provided to maintain user input / rotation and rotation of the spring tightening. The gear assembly 300 reduces the force required by a user to apply to the crank assembly 40 and also allows the crank assembly 40 to be centrally positioned with respect to the housing. Those of ordinary skill in the art will appreciate that the crank assembly 40 need not be centrally positioned, but can be positioned in a variety of locations. The shaft 140 connected with the crank assembly 40 can generally have a rotational axis that is more centrally positioned, while the rotational axis of the tightening shaft 55 is offset from the rotational axis of the shaft 140. While a particular gear configuration is shown, those of ordinary skill in the art will appreciate that a variety of gear configurations can be used that facilitate easier tightening of the swing set and also position the crank assembly 40 in a more desirable location of the housing for stability and weight distribution purposes. Figures 28A-29 Another example embodiment of a gear assembly is shown.

[0164] A torque limiting clutch assembly 400 can also be provided, as shown in more detail below. Figures 12A-12G The torque limiting clutch assembly 400 can include a first housing 402 that is configured to support a portion of the crank assembly 40 (e.g., the handle 42). The first housing 402 can be considered an upper housing or upper portion. The first housing 402 can include a clutch drive tooth 402a. A second housing 406 can be provided that can serve as a cover or lower portion of the torque limiting clutch assembly 400. In some embodiments, the second housing 406 can be omitted.

[0165] A clutch hub 404 is also provided, which is configured to interact or engage with the first housing 402, and more particularly, the clutch drive teeth 402a. The clutch hub 404 can be rotatably locked together with the crank assembly 40. The clutch hub 404 can include at least one pawl 404a. In one example, the at least one pawl 404a can include two pawls. The pawl 404a can include at least one pawl tooth 404b, which can be configured to selectively engage with the clutch drive teeth 402a. The clutch hub 404 can also include a biasing element 404c, which is configured to pivot or drive the pawl 404a outwardly such that the pawl tooth 404b engages with the clutch drive teeth 402a. In one example, the biasing element 404c can include a spring. A pivot connection 404d can be provided at one end of the at least one pawl 404a to attach the pawl 404a to the body of the clutch hub 404.

[0166] Torque is applied to the first housing 402, thereby causing the clutch drive teeth 402a to engage with the pawl teeth 404b. The pawl 404a is configured to be driven clockwise by the contact between the clutch drive teeth 402a and the pawl teeth 404b. Torque is thereby transferred from the crank assembly 40 to the drive spring 60. The pawl 404a is normally biased radially outwardly by the biasing element 404c. At a given or predetermined torque, the force of the biasing element 404c is overcome by the tightening torque applied to the crank assembly 40. When this occurs, the pawl 404a rotates clockwise, thereby disengaging the pawl teeth 404b from the clutch drive teeth 402a. As a result, there is no longer torque transferred from the crank assembly 40 to the drive spring 60. This prevents over-tightening of the system, which can damage components of the crank assembly 40, the drive spring 60 and related components.

[0167] As shown in Figure 12D and Figure 12E , an arrow is shown representing the tightening torque applied by the user. During this state, the pawl teeth 404b and the clutch drive teeth 402a are engaged. As shown in Figure 12F , in the event that the user applies an excessive torque to the crank assembly 40, the pawl teeth 404b and the clutch drive teeth 402a disengage. In this case, since the torque limiting clutch assembly 400 disengages, torque is not transferred from the crank assembly 40 to the drive spring 60. The torque limiting clutch assembly 400 is configured to ensure that the torque or input applied to the clockwork swing assembly does not exceed a predetermined amount of torque. As shown in Figure 12GAs shown in more detail, the first housing 402 also defines a plurality of secondary teeth 404e, which are configured to allow the nose of the pawl 404a to pass over the secondary teeth 404e and produce an audible noise of clutch disengagement due to excessive input torque input to the system. The pawl teeth 404b are configured to engage the clutch drive teeth 402a as the first housing 402 and the clutch hub 404 continue to rotate within a predetermined circumferential range (e.g., 180 degrees).

[0168] Figure 12H and Figure 12I An alternative to the torque limiting clutch 400' according to one embodiment of the present disclosure is shown. The torque limiting clutch 400' can be implemented in conjunction with the spring-loaded oscillating assembly 10 to prevent the user from tightening the drive spring 60 beyond a predetermined torque limit. The torque limiting clutch 400' is located between the input shaft 402' and the output shaft 404'. The input shaft 402' is operatively connected to the crank assembly 40, and the output shaft 404' is operatively connected to the drive spring 60. The torque limiting clutch 400' may also include a cap 406', a spool 408', and a spring 410'. The cap 406' is fixed to the input shaft 402', and the spool 408' is fixed to the output shaft 404'. The cap 406' and the spool 408' are clamped together by the spring 410' and can slide relative to each other when friction is overcome. Sliding between the cap 406' and the spool 408' prevents the drive spring 60 from being over-tightened.

[0169] Figures 12J-12M An alternative to the torque limiting clutch assembly 420 according to one embodiment of the present disclosure is shown. Figures 12K-12M The operation of the torque limiting clutch assembly 420 shown is similar to... Figures 12A-12G The torque limiting clutch assembly 400 shown requires fewer parts, which reduces the size and cost of the torque limiting clutch assembly 420 and also reduces the likelihood of mechanical problems and improper assembly. The torque limiting clutch assembly 420 may include an input hub 422 and an output hub 424. The output hub 424 can be rotatably locked to the shaft 140. The input hub 422 can be considered as the upper part and may support a portion of the crank assembly 40 (e.g., handle 42). The input hub 422 may include at least one engagement member 426 to engage with at least one protrusion 428 of the output hub 424. This at least one engagement member 426 may be, for example, an elastic material (e.g., a spring claw 430 with an engagement portion 432), such as an engagement hole or engagement surface, configured to engage with at least one protrusion 428 of the output hub 424.

[0170] The input hub 422 can be rotatably locked with the crank assembly 40. The output hub 424 can be located within a lower portion of the input hub 422. At least one engagement piece 426 of the input hub 422 can be biased to engage with at least one protrusion 428 of the output hub 424. Torque applied to the input hub 422 causes the at least one engagement piece 426 to engage with the at least one protrusion 428. The torque is thereby transferred from the crank assembly 40 to the drive spring 60. At a given or predetermined torque, the force of the engagement piece 426 is overcome by the tightening torque applied to the crank assembly 40. When this occurs, the protrusion 428 slides or disengages from the engagement piece 426 to prevent torque from being transferred from the crank assembly 40 to the drive spring 60. This prevents over-tightening of the drive spring 60, which can damage components of the crank assembly 40, the drive spring 60, and related components.

[0171] Figures 12J-12M The input hub 422 is shown with three engagement pieces 426 and the output hub 424 is shown with three protrusions 428; however, those skilled in the art will recognize that other variations in the number of engagement pieces 426 and protrusions 428 can be utilized within the scope of the present disclosure. Further, those skilled in the art will recognize that the positions of the at least one engagement piece 426 and the at least one protrusion 428 can be reversed such that the at least one protrusion 428 is located on the input hub 422 and the at least one engagement piece 426 is located on the output hub 424.

[0172] Figures 12N-12Q An alternative to the torque limiting clutch assembly 440 is shown in accordance with one aspect of the present disclosure. The torque limiting clutch assembly 440 can include an input hub 442 and an output hub 448. The output hub 424 can be rotationally locked to the shaft 140. The input hub 442 can include an upper portion 444 and a lower portion 446. The upper portion 444 can support a portion of the crank assembly 40 (e.g., the handle 42). The output hub 448 can be located below the upper portion 444 of the input hub 442. The output hub 448 can include an upper portion 450 and a lower portion 452. In one example, the upper portion 450 and the lower portion 452 of the output hub 448 can be located within the upper portion 444 and the lower portion 446 of the input hub 442.

[0173] The input hub 442 can include at least one engagement piece 454 having an engagement surface 455 to engage with at least one protrusion 456 of the output hub 448. The at least one engagement piece 454 can be pivotably attached, for example, with the input hub 442 or a resilient portion of the input hub 442. A spring 458 can be attached with the at least one engagement piece 454 to bias the engagement piece 454 inwardly toward the output hub 448. In one example, the input hub 442 includes two engagement pieces 454, the output hub 444 includes two protrusions 456 engaged with each other, and the spring 458 biases the engagement surface 455 of each engagement piece 454 toward engagement with the protrusions 456.

[0174] The input hub 442 can be rotatably locked with the crank assembly 40. A torque applied to the input hub 442 causes the engagement surface 455 of the at least one engagement piece 454 to engage with the at least one protrusion 456. The torque is thereby transferred from the crank assembly 40 to the drive spring 60. At a given or predetermined torque, the biasing force of the engagement piece 454 is overcome by the tightening torque applied to the crank assembly 40. When this occurs, the protrusion 456 slides or disengages from the engagement surface 455 of the engagement piece 454 to prevent the transfer of torque from the crank assembly 40 to the drive spring 60. This prevents over-tightening of the drive spring 60, which can damage components of the crank assembly 40, the drive spring 60, and related components.

[0175] Figure 12N-Figure 12Q The input hub 442 is shown with two engagement pieces 454 and the output hub 448 is shown with two protrusions 456; however, those skilled in the art will recognize that other variations in the number of engagement pieces 454 and protrusions 456 can be utilized within the scope of the present disclosure. Further, those skilled in the art will recognize that the positions of the at least one engagement piece 454 and the at least one protrusion 456 can be reversed such that the at least one protrusion 456 is located on the input hub 442 and the at least one engagement piece 454 is located on the output hub 448. Another exemplary embodiment of a torque clutch is shown in Figures 28A-29 .

[0176] As shown in Figure 14 , an arm swing hub 22 can be provided in connection with the arm swing 25 and the first end 25a and the second end 25b of the arm swing 25. An inclination axis (AR) is defined based on the angle of the adjustment assembly 20 and a seat rotation axis (ASR) is defined extending substantially perpendicular to the arm swing hub 22. Figure 14A center of gravity (COG) scatter plot is also shown. The center of gravity (COG) is generally determined based on the weight distribution of the frame itself as well as the occupant or child in the swing device. Overall, the clockwork swing assembly 10 provides an improved configuration that is easier to use, has a longer swing duration, a smoother swing, and a more predictable amplitude than other known swing assemblies. The tilt axis (AR) and the seat rotation axis (ASR) intersect each other and both extend generally through the center of gravity (COG). Figure 14 An occupant is shown. Those of ordinary skill in the art will appreciate that a soft good or seat assembly can be provided to support the occupant. The weight of the occupant is generally located in a region of the seat frame 15 where the center of gravity (COG) intersects the tilt axis (AR) and the seat rotation axis (ASR). Those of ordinary skill in the art will appreciate that various design considerations can be adjusted or modified, such as the shape of the seat frame 15, the length / angle of the swing arm 25, the contour of the soft good, etc. Based on the positioning of the tilt axis (AR) and the seat rotation axis (ASR) as well as the center of gravity, Figure 14 The configuration shown improves the stability of the clockwork swing assembly 10.

[0177] Figures 15A-15C An additional arrangement or feature of the swing arm 25 and its interface with the swing arm pivot 127 is shown. A swing arm connector 125 can be provided that has a first end secured to the swing arm pivot 127 and is configured to attach or connect with the swing arm 25. For example, the swing arm 25 can be housed within the swing arm connector 125 and further secured by a rivet 125a and a snap pin 125b. The snap pin 125b can be provided on the swing arm 25 and can be configured to be housed within an opening on the swing arm connector 125. The rivet 125a can extend through an opening on the swing arm connector 125 and be seated within a slot 125c defined on the swing arm 25. This arrangement of the connector reduces or limits any play or loose connection between the swing arm 25 and the swing arm pivot 127, thereby providing an improved swing time. In addition, this connector allows the user to quickly and easily remove the swing arm 25 from the swing arm pivot 127 for disassembly. The snap pin 125b can prevent the two components from being removed from each other and the rivet / slot connection minimizes the twisting and rotational movement between the swing arm 25 and the swing arm pivot 127.

[0178] The spring-powered swing assembly 10 disclosed herein generally provides a small footprint, i.e., without any overhead or vertical support, and requires very limited energy to drive the swing arm assembly. The spring-powered swing assembly 10 disclosed herein also provides an improved and efficient configuration for transferring forces between multiple axes, i.e., the swing arm axis (X1), the escapement axis (X2), and the drive spring axis (X3). This configuration imparts a pendulum-like motion to the swing arm by using bearings in order to overcome wind resistance and increase the run time of the spring-powered swing assembly 10. The spring-powered swing assembly disclosed herein also has a longer run time, which can exceed 45-60 minutes based on a user winding the drive spring for about 20 seconds or about 20-30 turns.

[0179] Figures 16A-27 An alternative to the spring-powered swing assembly 600 according to the present disclosure is shown. Figures 16A-27 The alternative to the spring-powered swing assembly 600 disclosed in Figures 1A-15C The alternative to the spring-powered swing assembly 600 disclosed in

[0180] The swing arm 625 extends between the swing arm pivot 627 and the swing frame 615. The swing arm 625 forms an approximate L-shape. The shape and position of the swing arm 625 can mitigate safety concerns by minimizing the possibility of a child's hand, finger, leg, or head becoming caught between the swing arm 625 and the swing frame 615. It should be appreciated that the swing arm 625 can include other shapes to affect the spacing between the swing arm 625 and the swing frame 615 for safety considerations.

[0181] The configuration of the connection of the swing arm 625 and the frame assembly 635 allows for easy access to a seat on the swing frame 615. For example, there is no structure directly above the swing frame 615 (see Figure 16B This configuration forms an open passageway that allows a caregiver to place and remove a child from the swing assembly 600. It should be appreciated that a movable toy bar or other movable or removable play toy can be included on the swing frame 615 without impeding the open passageway to access the seat on the swing frame 615.

[0182] The crank assembly 640 includes a crank arm 644, a ring 646, and a plate 648. The ring 646 extends around the periphery of the plate 648 and can be fixed to the seat frame 615. The crank arm 644 is connected with the plate 648 such that rotation of the crank arm 644 causes rotation of the plate 648. The crank arm 644 and the plate 648 can rotate about the same rotational axis. Rotation of the crank arm 644 can cause the drive spring 60 to be tightened. During operation (as described further below), as a user tightens the crank arm 644 to tighten the drive spring 60, the user can grasp the ring 646 to facilitate the tightening motion.

[0183] The crank arm 644 can have a curved or rounded shape and can rotate downward toward the plate 648. In one arrangement, the crank arm 644 can rotate downward into a recess or opening defined by the plate 648. The ability to rotate downward and the shape of the crank arm 644 can minimize "hooking" (e.g., a rope, clothing, or other material being hooked or entangled in the area of the crank arm 644).

[0184] Figures 18-26 An alternative arrangement of an armrest assembly and a seat assembly 740 according to the present disclosure is shown. The armrest assembly 712 includes an armrest 725 and a support hub 727. The armrest 725 can extend between the armrest pivot 627 and the support hub 727. The seat assembly 740 includes a seat frame 715, a seat portion 717, and a base assembly 719. The seat assembly 740 can be detachably connected with the support hub 727 (see Figure 19 and Figure 20 ).

[0185] Referring to Figures 21A to 21D , the support hub 727 can include a rotating hub 750 and a fixed hub 752. The fixed hub 752 can be fixedly connected to the armrest 725. The rotating hub 750 can be rotatably connected to the fixed hub 752 such that the rotating hub 750 can rotate relative to the fixed hub 752 about a rotational axis A. The rotating hub 750 includes a rotating body 754 that extends upward from a rotating base 753. The rotating body 754 is configured to receive the seat assembly 740 thereon. The rotating body 754 defines a circular recess 756 and at least one anti-rotation channel 758. The circular recess 756 can be located in the center of the rotating body 754. In one arrangement, the center of the circular recess 756 can be located on the rotational axis A. The rotating body 754 also includes at least one latch shelf 760. The at least one latch shelf 760 can be located within the at least one anti-rotation channel 758. It should be appreciated that the at least one latch shelf 760 can be located at other locations on the rotating hub 750. In one arrangement, the rotating body 754 includes four anti-rotation channels 758 and four latch shelves 760 located within the respective anti-rotation channels 758. It should be appreciated that the rotating body 754 can include fewer or more anti-rotation channels 758 and latch shelves 760.

[0186] Referring to Figure 21C and Figure 21D , the support hub 727 can further include a plunger 762 and a biasing element 764. The biasing element can be a resilient member, such as a spring. The plunger 762 and the biasing element 764 can be at least partially located between the rotating hub 750 and the fixed hub 752. The rotating hub 750 can define at least one plunger recess or detent 766. The at least one plunger recess 766 is shaped and configured to correspond to the plunger 762 such that the plunger 762 can be received by the at least one plunger recess 766. The connection between the plunger 762 and the at least one plunger recess 766 creates a temporary rotational lock between the rotating hub 750 and the fixed hub 752. The temporary rotational lock can be overcome by applying a rotational force to the rotating hub 750 to force the biasing element 764 to retract the plunger 762 from the at least one plunger recess 766. The rotating hub 750 can include four plunger recesses 766 spaced circumferentially around the rotating hub 750. It should be understood that the rotating hub 750 can include fewer or more than four plunger recesses 766. In one arrangement, the plunger recesses 766 can be equally spaced from one another around the rotating hub 750.

[0187] Referring to Figure 22 , the seat assembly 740 further includes at least one support leg 768, a support base 770, and a connection assembly 772. The at least one support leg 768 extends upwardly from the support base 770 and is configured to support the seat frame 715 and the seat portion 717 above the support base 770. As shown, the at least one support leg 768 includes two legs. It should be understood that the at least one support leg 768 can include fewer or more legs. The support base 770 can define, for example, a rocker, a flat surface, or other shape such that the seat assembly 740 attached to the support base 770 can be used independently of the swing arm assembly 712 and placed on a surface (e.g., a floor, a countertop, etc.) for use.

[0188] The connection assembly 772 can be connected with the support hub 727. Referring to Figure 23A and Figure 23B , the connection assembly 772 defines a connection recess 776. The connection recess 776 is sized to receive the support hub 727 therein to connect the seat assembly 740 with the swing arm 725. In one arrangement, the connection recess 776 defines a shape that generally corresponds to a shape of an outer surface of the rotating body 754.

[0189] The seat assembly 740 further includes at least one actuator 774. The at least one actuator 774 can control a release connection between the connection assembly 772 and the support hub 727, as further described below. The at least one actuator 774 can be connected with at least one of the at least one support leg 768, the support base 770, and the connection assembly 772.

[0190] According to an alternative of the present disclosure, Figure 24A and Figure 24B A connection assembly 872 and support hub 827 are shown. The connection assembly 872 can include at least one connection recess 874. The support hub 827 can include at least one connection stud 829. When the connection assembly 872 is positioned on the support hub 827, the at least one connection stud 829 can be housed within the at least one connection recess 874. The connection between the at least one connection stud 829 and the at least one connection recess 874 provides further rotational locking (e.g., torque locking) between the connection assembly 872 and the support hub 827. By reducing movement between the connection assembly 872 and the support hub 827, less energy is wasted during operation of the swing assembly 600. It should be appreciated that the at least one stud 829 and the at least one recess 874 can be located on either the connection assembly 872 or the support hub 827. For example, the support hub 827 can include at least one recess 874, while the connection assembly 872 can include a corresponding at least one stud 829.

[0191] Figures 25-27 A cross-section of at least one actuator 774 and a portion of the connection assembly 772 is shown. The connection assembly 772 includes an actuator biasing element 777, a pivot member 778, and a hub latch 780. The connection assembly 772 also defines a hub protrusion 782 and at least one anti-rotation rib 784 within a connection recess 776. The at least one anti-rotation rib 784 is sized to be housed within a corresponding at least one anti-rotation channel 758 of the rotating hub 750. The connection of the at least one rib 784 within the at least one anti-rotation channel 758 substantially prevents rotation between the connection assembly 772 and the rotating hub 750. It should be appreciated that the rotating hub 750 can include at least one rib, and the connection assembly 772 includes at least one channel configured to house the at least one rib. The hub protrusion 782 is sized to be housed through a circular recess 756 of the rotating hub 750.

[0192] The actuator biasing element 777 may be, for example, an elastic member (e.g., a spring) and is connected between at least one actuator 774 and a pivot member 778. The pivot member 778 may be, for example, a pivot shaft or a pivot latch and is pivotally connected to the body 772a of the connecting assembly 772 at a pivot connection 779. The pivot member 778 is also connected between the biasing element 777 and a hub latch 780. A first end 778a of the pivot member 778 is connected to at least one actuator 774 and is under the biasing force of the biasing element 777. A second end 778b of the pivot member 778 is connected to the hub latch 780 and biases the hub latch 780 to a locked position, allowing the hub latch 780 to engage with the rotating hub 750. The hub latch 780 may be pivotally connected to the body 772a of the connecting assembly 772. Actuation of actuator 774 or at least one actuator 774 moving to the actuated position causes hub latch 780 to be in the unlocked position. Figure 26 ) and locking position ( Figure 27 Transition between ) . For example, refer to Figure 26 When actuator 774 is actuated (e.g., in Figure 26 (Moving upwards in the view shown), actuator 774 overcomes the biasing force of biasing element 777 and causes pivot member 778 to pivot about pivot connector 779. The pivoting movement of pivot member 778 changes hub latch 780 from the locked position to the unlocked position. When at least one actuator 774 is released, biasing element 777 pulls at least one actuator 774 downwards and causes pivot member 778 to rotate about pivot connector 779, which changes hub latch 780 to the locked position.

[0193] Reference Figure 27 The hub latch 780 is in the locked position, and the rotating hub 750 is located within the connecting recess 776. The hub latch 780 is in the locked position and engages with at least one latch bracket 760 of the rotating hub 750. The engagement between the at least one latch bracket 760 and the hub latch 780 essentially locks the seat assembly 740 to the rotating hub 750. To remove the seat assembly 740, at least one actuator 774 can be actuated to turn the hub latch 780 to the unlocked position. In the unlocked position, the seat assembly 740 can be removed from the rotating hub 750.

[0194] A method of using the clockwork swing assembly 10 is also disclosed. It should be appreciated that the method of using the clockwork swing assembly 10 can also be used to operate the clockwork swing assembly 600. The method can include engaging the crank assembly 40 by rotating the crank handle 44. The crank assembly 40 is operably connected to the tensioning mechanism 50 such that rotational input from the crank assembly 40 is applied to the tensioning mechanism 50. Rotating the crank handle 44 tensions the drive spring 60 that is connected to the tensioning mechanism 50. The method includes selectively releasing energy from the drive spring 60 via the escapement assembly 70, which can include the carriage 72. The carriage 72 can also be linked to the swing arm pivot 27 by the pusher 90. Based on this arrangement, during a power stroke, the swing arm pivot 27 moves (i.e., is driven) in a first direction due to the discrete release of energy from the drive spring 60 via the escapement assembly 70. During a non-power stroke, the swing arm pivot 27 moves in a second direction opposite the first direction. This movement in the second direction is based on momentum or gravity. The swing arm pivot 27 is configured to swing side-to-side, as opposed to fore-and-aft, based on energy from the drive spring 60.

[0195] A method of driving a seat frame 15 of the clockwork swing assembly 10 is also disclosed herein. It should be appreciated that the method of driving a seat frame 15 of the clockwork swing assembly 10 can also be used to operate the clockwork swing assembly 600. The method can include rotating the crank assembly 40 that is connected to the drive spring 60, thereby tensioning the drive spring 60. The drive spring 60 can have a drive spring axis (X3) that is oriented in a non-vertical direction. The method includes transferring energy from the tensioned drive spring 60 to the escapement assembly 70, which can have an escapement axis (X2) that is angled relative to the drive spring axis (X3). The method can include selectively releasing energy from the escapement assembly 70 to the swing arm pivot 27. The swing arm pivot 27 can be connected to the seat frame 15 and can have a swing arm axis (X1) that is angled relative to the drive spring axis (X3) and the escapement axis (X2).

[0196] The clockwork swing assembly 10 disclosed herein also provides for an enhanced run time or swing time as compared to known non-electrically powered or manually driven swing assemblies. For example, the clockwork swing assembly disclosed herein can provide for a run time of about one hour. The run time is based on a user turning the tensioning device with the crank for about 20 seconds or about 20-30 rotations.

[0197] In comparison to known clockwork swing assemblies, the clockwork swing assembly 10 disclosed herein provides a reduced footprint while also providing improved accessibility to the seat frame supporting the child. As shown, the drive spring 60 is disposed in a non-overhead position relative to the seat frame. This provides a number of advantages, including unobstructed access to the seat frame and child, and also provides an ideal center of gravity by disposing the drive spring 60 in a relatively closer-to-ground position in comparison to clockwork swing assemblies that require the drive spring 60 to be disposed overhead relative to the seat frame. Based on this positioning, the center of gravity is lowered to the ground, thus requiring a relatively smaller support assembly for the frame.

[0198] Overall Reference Figures 28A-34 Additional example embodiments of the present disclosure are shown, which provide various advantageous features, such as: (a) mechanical design of the upper tightening gears, shafts, and tightening components that simplifies assembly and reduces cost; (b) radial support around the rotational axis; (c) axial support at the outer circumference of the torque clutch; (d) enhanced consumer tightening experience / feel - e.g., reduced friction, increased rigidity, and improved support of the tightening rotator; (e) amplitude control shut-off feature; and (f) welded steel frame design for reduced shipping size.

[0199] Reference Figures 28A-29 Another example embodiment of a gear assembly and torque clutch, generally identified by reference numeral 800, is shown in assembled order steps to illustrate the constituent components. Figures 28A-29 Operation of the torque limiting clutch assembly 800 shown is similar to Figures 12A-12G and / or Figures 12K-12M the torque limiting clutch assembly shown. Various aspects of the assembly process are applicable to the various torque clutches disclosed herein. The gear assembly includes shafts 802 and 804 housed in shaft holes 806 and 808 of a housing 810, with gears 811 and 812 coupled thereto. A gear cap 814 is then installed on the housing 810 and secured thereto with fasteners, such as screws 816. A low-friction support washer 820 can be installed in the gear cap 814. A torque clutch 824 is then installed to the gear cap 814 and rotationally coupled to the shaft 802. Once the torque clutch 824 is installed, a tightening knob 828 is coupled to the torque clutch 824. A crown trim piece 830 is then installed on the gear cap 814 and torque clutch 824, and a tightening rotator 832 is coupled to the torque clutch 824. It will be appreciated that the assembly order of the components can differ from the order described above, and that some components can first be combined into a subassembly, which is then assembled into a unit. Further, the various components can be secured together in various ways, such as by fasteners, friction fit, snap fit, adhesive, etc.

[0200] In Figure 28G one example application, the exemplary application utilizes a pin shaft to connect the tightening knob 828 to the torque clutch 824, although it could alternatively snap onto the boss. Additionally, the tightening knob 828 is shown flipped down. This design can be implemented for aesthetic and safety reasons, although other mounting methods can also be considered. For this example design, it should be noted that the tightening knob 828 is directly connected to the torque clutch 824 and can be mounted about a vertical axis or other axis, with or without fasteners.

[0201] In Figure 28H one example application, the crown 830 is mounted as a trim piece and can have an aesthetic design. Since this trim piece is rigidly attached to the gear cap 814, concentricity between the rotating tightening component and any aesthetic cap component can always be ensured. This minimizes friction between components due to flexing when tightening.

[0202] When the components are assembled as shown in Figures 28A-28L , the resulting assembly is shown in cross-section in Figure 29 . In this embodiment, the gears 806 and 808 are axially held by the gear cap 814, the torque clutch 824 is radially positioned by the center shaft 802, the outer lower bearing circumference of the torque clutch 824 is supported by the low friction support washer 820, the outer upper bearing circumference of the torque clutch 824 is supported by the crown trim piece 830 for its vertical retention. The tightening rotator 832 provides an aesthetic cap and the snap connection to the torque clutch 824 provides axial retention of the tightening shaft 802. Thus, this exemplary embodiment of the assembly provides: minimal components, a torque clutch with radial support at the center and axial thrust at the perimeter to resist the tightening force of the consumer during the tightening process, and retention of the center of the tightening shaft by the tightening rotator when it is snapped on. The improved radial and axial support of the torque clutch, combined with the low friction support washer, greatly improves the tightening experience through component rigidity and low friction.

[0203] As described above in connection with Figures 7A-7D , in embodiments, the escapement 70 has a minimum operating swing that can be about 9 degrees on each side. If the swing is lower than this value, the mechanism will not work. A swing control 92 is provided to set the swing to a preferred height. Typically, the swing must be greater than 9 degrees on each side to function. For a given design, the swing control is set to a minimum of about 15 degrees and a maximum of 25 degrees on each side. The purpose of the swing control lever 95 is to move the lever down to reduce the swing. However, moving the swing control lever 92 too far down will cause the lever to catch on the drop plate. When this happens, the swing control is defeated and the swing device will swing at the maximum amplitude.

[0204] Referring Figures 30-33 An example shut-off feature for amplitude control can be implemented in the escapement 70. In Figure 33 By strategically setting the downward stop 910 to limit the downward rotation of the amplitude control lever 95, a position can be found where the drop plate 85 is activated with less than the example 9 degrees of swing per side required, while not jamming the drop plate 85. In addition, the drop plate 85 must be able to "float". Therefore, a space (e.g., gap 920) is provided as shown to provide a shut-off position. In addition, moving the amplitude control lever 95 downward will cause the amplitude control lever 95 to jam the drop plate 85, rendering it inoperative. Therefore, the stop 910 is placed as shown to prevent the amplitude control lever 95 from descending further, thereby preventing the drop plate 85 from jamming. The stop 910 can be provided in the housing that supports the amplitude control 92 or another adjacent component.

[0205] Referring to Figure 34 In some embodiments, a welded steel frame can be provided allowing for reduced shipping dimensions and other benefits. These different mechanical components disclosed herein will provide improved performance when the frame is substantially rigid. As shown, an example frame design includes a welded frame 1005 including a tower component 1010 rigidly welded to a horizontal component 1020 of a base 1030. A corresponding U-shaped or curved component 1040 of the base 1030 is adapted to be inserted or otherwise coupled into the horizontal component 1020 of the welded frame.

[0206] The swing assembly described above can be implemented in various configurations and operated in various ways as listed below:

[0207] 1. A clockwork swing assembly comprising: a frame assembly including a housing; a drive spring positioned within the housing and having a drive spring axis (X3) oriented in a non-vertical direction relative to a vertical plane; and a swing arm assembly connected with the frame assembly to receive energy from the drive spring, the swing arm assembly including a swing arm and a swing arm pivot, the swing arm being rotatable about a swing arm axis (XI) oriented in a non-horizontal direction relative to a horizontal plane.

[0208] 2. The clockwork swing assembly of configuration 1, wherein the drive spring axis (X3) is angled relative to the swing arm axis (XI).

[0209] 3. The clockwork swing assembly of configuration 1, wherein the swing arm axis (XI) is oriented at an angle of 30-70 degrees relative to the horizontal plane.

[0210] 4. The clockwork swing assembly of configuration 1, wherein the drive spring axis (XI) is oriented at an angle of 5-20 degrees relative to the vertical plane.

[0211] 5. The clockwork swing assembly of configuration 1, further comprising an escapement assembly coupled with the frame assembly, the escapement assembly having an escapement axis (X2) that is angled relative to the swing arm axis (XI).

[0212] 6. The clockwork swing assembly of configuration 5, wherein the swing arm axis (XI), the escapement axis (X2), and the drive spring axis (X3) are each angled relative to one another.

[0213] 7. The clockwork swing assembly of configuration 5, wherein the escapement axis (X2) is substantially parallel to a horizontal plane.

[0214] 8. The clockwork swing assembly of configuration 1, wherein the swing arm assembly includes an adjustment assembly and a seat frame, and the adjustment assembly is configured to adjust an angle of inclination of the seat frame.

[0215] 9. The clockwork swing assembly of configuration 8, wherein the drive spring is disposed transversely relative to the seat frame.

[0216] 10. The clockwork swing assembly of configuration 1, wherein the frame assembly includes an upper end and a lower end, a base at the lower end of the frame assembly, and an upright frame member extending from the base to the upper end of the frame assembly.

[0217] 11. The clockwork swing assembly of configuration 10, wherein the frame assembly further includes a support at the lower end of the frame assembly, the support being configured to rest on the ground, and a handle positioned adjacent the upper end of the frame assembly.

[0218] 12. The clockwork swing assembly of configuration 11, wherein the support extends in an opposite direction from the base.

[0219] 13. The clockwork swing assembly of configuration 1, wherein a crank assembly is provided on the frame assembly to tension the drive spring.

[0220] 14. The clockwork swing assembly of configuration 13, wherein the crank assembly includes a crank handle configured to extend away from the frame assembly, and rotation of the crank handle about a crank pivot causes the drive spring to be tensioned.

[0221] 15. The clockwork swing assembly of configuration 14, wherein the crank handle is configured to fold outwardly from the frame assembly in a use condition, and is configured to fold into a pocket defined on the frame assembly in a storage condition.

[0222] 16. The clockwork swing assembly of configuration 13, further comprising a tensioning mechanism disposed between the crank assembly and the drive spring to translate an activation input from the crank assembly to cause the drive spring to be tensioned.

[0223] 17. The clockwork swing assembly of configuration 16, wherein the winding mechanism comprises a winding shaft connected at a first end to the crank assembly and at a second end to the spool, and the drive spring comprises a first end connected to an attachment plate disposed about the winding shaft and a second end connected to the spool, such that rotation of the winding shaft winds the drive spring via the spool.

[0224] 18. The clockwork swing assembly of configuration 17, further comprising a gear assembly disposed between the crank assembly and the drive spring to reduce the force required to wind the drive spring, the gear assembly comprising a crank gear fixed to a shaft connected to the crank assembly and a spring gear engaged with the crank gear and fixed to the spool.

[0225] 19. The clockwork swing assembly of configuration 1, further comprising a winding mechanism comprising a winding shaft positioned along a drive spring axis (X3), the winding mechanism having a first end connected to the crank assembly and a second end connected to the spool.

[0226] 20. The clockwork swing assembly of configuration 19, wherein the drive spring comprises a first end connected to an attachment plate disposed about the winding shaft and a second end connected to the spool, such that rotation of the winding shaft winds the drive spring via the spool.

[0227] 21. The clockwork swing assembly of configuration 20, wherein the winding mechanism further comprises a first winding gear disposed about the winding shaft and attached to the attachment plate, and a second winding gear meshingly engaged with the first winding gear, wherein stored energy released from the drive spring rotationally drives the first winding gear, which rotationally drives the second winding gear.

[0228] 22. The clockwork swing assembly of configuration 21, further comprising an escapement assembly connected to the frame assembly, the escapement assembly comprising an escapement shaft connected to the second winding gear rotationally driving the escapement shaft, the escapement shaft oriented along an escapement axis (X2).

[0229] 23. The clockwork swing assembly of configuration 22, wherein the escapement axis is oriented substantially parallel to a horizontal plane.

[0230] 24. The clockwork swing assembly of configuration 22, wherein the escapement assembly further comprises an escapement gear fixed to the escapement shaft, the escapement gear configured to be driven via the second winding gear.

[0231] 25. The clockwork swing assembly of configuration 24, wherein the escapement assembly further comprises a carrier coupled to the escapement shaft and configured to rotate about the escapement axis (X2), and a pusher comprising a first end connected to the carrier and a second end connected to the swing arm assembly, wherein the pusher drives the swing arm assembly to rotate when the escapement gear is driven by stored energy released from the drive spring through the connection of the escapement shaft to the second winding gear.

[0232] 26. The clockwork swing assembly of configuration 25, wherein the pusher comprises a wire, the first and second ends of the pusher comprise portions angled relative to a body of the pusher, the first end of the pusher is configured to be retained in an opening of the carrier, the carrier comprises a through hole, at least one tapered region adjacent to the through hole, and the second end of the pusher is configured to be retained within an opening in the pivot housing of the swing arm assembly, the opening comprising a through hole and at least one tapered region adjacent to the through hole.

[0233] 27. The clockwork swing assembly of configuration 25, wherein the pusher comprises a first bevel gear and a second bevel gear in driving engagement with the first bevel gear, the first bevel gear is attached to the swing arm pivot, and the second bevel gear is connected to the carrier.

[0234] 28. The clockwork swing assembly of configuration 25, wherein the escapement gear comprises a plurality of teeth, and the escapement assembly further comprises a pawl pivotably attached to the frame assembly, the pawl comprising pawl teeth selectively engageable with the teeth of the escapement gear to prevent rotation of the escapement gear in the drive direction when the swing arm is in the neutral state, and a clip pivotably attached to the carrier, the clip selectively engages the teeth of the escapement gear when the swing arm is rotated and the pawl teeth are disengaged from the escapement gear.

[0235] 29. The clockwork swing assembly of configuration 28, wherein the escapement assembly further comprises an actuator coupled to the escapement shaft and configured to rotate about the escapement axis (X2), the actuator selectively engages the pawl and the clip to control the selective engagement between the pawl and the clip and the escapement gear.

[0236] 30. The clockwork swing assembly of configuration 28, further comprising an amplitude control assembly comprising a drop plate configured to selectively limit the travel of the clip, and an amplitude control lever configured to selectively adjust the position of the drop plate.

[0237] 31. The clockwork swing assembly of configuration 30, wherein the drop plate comprises an engagement portion configured to engage a portion of the clip and an attachment portion configured to engage a portion of the amplitude control lever.

[0238] 32. The clockwork swing assembly of configuration 31, wherein the amplitude control lever includes a first stop and a second stop, the first stop and the second stop being spaced apart from each other and each configured to engage an appendage of the drop plate to control the swing amplitude.

[0239] 33. The clockwork swing assembly of configuration 19, further comprising a torque limiting clutch configured to prevent over-tightening of the drive spring.

[0240] 34. The clockwork swing assembly of configuration 33, wherein the torque limiting clutch includes a torque clutch spring assembled on the spool, and the torque clutch spring is configured to be tightened when the tightening spool is rotated in a tightening direction, and to slip when the drive spring is tightened beyond a predetermined torque.

[0241] 35. The clockwork swing assembly of configuration 33, wherein the torque limiting clutch includes a first housing operably connected with the crank assembly, the first housing including a clutch drive tooth; a clutch hub fixed to the crank assembly; and a clutch pawl pivotably connected with the clutch hub via a biasing element, the clutch pawl being biased by the biasing element to selectively engage the clutch drive tooth; wherein, when the drive spring is tightened by the crank assembly, the clutch pawl engages the clutch drive tooth up to a predetermined torque limit to transfer torque from the crank assembly to the drive spring, and when the torque transferred from the crank assembly to the drive spring exceeds the predetermined torque limit, the clutch pawl disengages the clutch drive tooth to prevent further torque transfer from the crank assembly to the drive spring.

[0242] 36. The clockwork swing assembly of configuration 33, wherein the torque limiting clutch includes an input shaft connected with the crank assembly; an output shaft connected with the drive spring; a cap fixed to the input shaft; and a spool fixed to the output shaft and clamped to the cap; wherein the cap and the spool are configured to slide relative to each other when a predetermined force is overcome to prevent the drive spring from being over-tightened.

[0243] 37. The clockwork swing assembly of configuration 33, wherein the torque limiting clutch includes a shaft connected with the crank assembly; an input hub including at least one engagement; and an output hub connected with the shaft, the output hub including at least one protrusion engageable with the at least one engagement; wherein the at least one protrusion is configured to disengage the at least one engagement when a predetermined force from the crank assembly is overcome to prevent the drive spring from being over-tightened.

[0244] 38. The clockwork swing assembly of configuration 37, wherein the at least one engagement is a resilient member biased toward engagement with the at least one protrusion.

[0245] 39. The clockwork swing assembly of configuration 37, wherein the at least one engagement member is pivotably attached to the input hub.

[0246] 40. The clockwork swing assembly of configuration 37, further comprising a spring connected with the at least one engagement member and biasing the at least one engagement member toward engagement with the at least one protrusion.

[0247] 41. The clockwork swing assembly of configuration 1, wherein the swing arm is connected with the swing arm pivot via a swing arm connector, the swing arm connector comprising a rivet and a detent.

[0248] 42. The clockwork swing assembly of configuration 1, wherein the swing arm assembly comprises a seat frame, and a center of gravity (COG) of an occupant within the seat frame intersects approximately with an axis of recline (AR) of the seat frame and an axis of seat rotation (ASR) of the seat frame.

[0249] 43. The clockwork swing assembly of configuration 1, wherein the swing arm assembly comprises a seat frame, and an axis of recline (AR) of the seat frame and an axis of seat rotation (ASR) of the seat frame intersect with each other, and both axes extend through a center of gravity (COG) defined by the seat frame and an occupant of the clockwork swing assembly.

[0250] 44. A swing assembly comprising: a frame assembly; a swing arm assembly connected with the frame assembly, the swing arm assembly comprising a swing arm pivot pivotably attached with the frame assembly; and a swing arm having a first end connected with the swing arm pivot and a second end connected with a seat assembly; wherein the swing arm is rotatable about a swing arm axis (XI) oriented in a non-horizontal direction relative to a horizontal plane.

[0251] 45. The swing assembly of configuration 44, wherein the swing arm is L-shaped.

[0252] 46. The swing assembly of configuration 44, wherein the swing arm further comprises a support hub, the support hub located at the second end of the swing arm and configured to house the seat assembly.

[0253] 47. The swing assembly of configuration 46, wherein the seat assembly is detachably connected with the support hub.

[0254] 48. The swing assembly of configuration 46, wherein the support hub is rotatable relative to the swing arm.

[0255] 49. The swing assembly of configuration 46, wherein the seat assembly comprises a connection recess, and the support hub comprises a connection stud housed within the connection recess to secure the seat assembly to the support hub.

[0256] 50. The swing assembly of configuration 46, wherein the support hub comprises a fixed hub fixed to the swing arm and a rotating hub rotatably coupled to the fixed hub, the rotating hub configured to attach to the seat assembly and rotate relative to the fixed hub.

[0257] 51. The swing assembly of configuration 50, further comprising a plunger, a biasing element attaching the plunger to the fixed hub, and a detent formed on the rotating hub to selectively receive the plunger to inhibit rotation between the rotating hub and the fixed hub.

[0258] 52. The swing assembly of configuration 50, wherein the seat assembly further comprises a seat frame, at least one support leg coupled to the seat frame, and a coupling assembly comprising a coupling recess to receive the rotating hub.

[0259] 53. The swing assembly of configuration 51, wherein the rotating hub comprises at least one rib and the coupling recess defines at least one channel to receive the at least one rib.

[0260] 54. The swing assembly of configuration 51, wherein the seat assembly comprises an actuator to release an engagement between the seat assembly and the support hub.

[0261] 55. The swing assembly of configuration 54, wherein the coupling assembly comprises a body, a pivot member having a first end and a second end and pivotably coupled to the body at a pivot connection located between the first end and the second end, the first end of the pivot member attached to the actuator, an actuator biasing element exerting a biasing force on the first end of the pivot member to bias the actuator to a rest position, and a hub latch coupled to the second end of the pivot member and biased to a locked position with the rotating hub to secure the seat assembly to the rotating hub; wherein movement of the actuator to an actuated position overcomes the biasing force of the actuator biasing element and causes the pivot member to pivot about the pivot connection, thereby causing the hub latch to move to an unlocked position and disengage from the rotating hub.

[0262] 56. The swing assembly of configuration 52, wherein the seat assembly further comprises a support base to use the seat assembly independently of the swing arm assembly when the seat assembly is detached from the swing arm assembly.

[0263] 57. A clockwork swing assembly comprising a frame assembly, a drive spring positioned within the frame assembly and oriented in a non-vertical direction relative to a vertical plane, a crank assembly disposed on the frame assembly, the crank assembly configured to input a drive torque to the drive spring, a seat frame rotatably coupled to the frame assembly, the seat frame comprising a swing arm oriented in a non-horizontal direction relative to a horizontal plane, and a gear assembly coupled to the crank assembly and the drive spring to transfer energy from the drive spring to provide a swinging motion to the seat frame.

[0264] 58. A method of using a clockwork swing assembly, the method comprising: engaging a crank assembly by rotating a crank handle, wherein the crank assembly is connected to a winding mechanism; winding a drive spring connected to the winding mechanism; and selectively releasing energy from the drive spring via an escapement assembly having a carriage connected to a swing arm pivot via a pusher such that the swing arm pivot moves in a first direction during a power stroke and such that the swing arm pivot moves in a second direction during a non-power stroke.

[0265] 59. A method of driving a seat frame of a clockwork swing assembly, the method comprising: rotating a crank assembly connected to a drive spring such that the drive spring is wound, the drive spring being positioned along a drive spring axis (X3) that is oriented in a non-vertical direction relative to a vertical plane; transferring energy from the wound drive spring to an escapement assembly having an escapement axis (X2) that is angled relative to the drive spring axis (X3); and selectively releasing energy from the escapement assembly to a swing arm pivot, wherein the swing arm pivot is connected to the seat frame and has a swing arm axis (X1), the swing arm axis (X1) being oriented in a non-horizontal direction relative to a horizontal plane and angled relative to the drive spring axis (X3) and the escapement axis (X2).

[0266] Having described the embodiments in detail, those skilled in the art will appreciate and understand that many physical changes can be made to the embodiments without changing the inventive concept and principles embodied therein, and only some of which have been illustrated in the detailed description of the disclosure.

[0267] It should also be understood that many of the embodiments only in conjunction with a part of the preferred embodiments are possible, which do not change the inventive concept and principles embodied therein relative to those parts.

[0268] Therefore, the embodiments and optional configurations are all considered to be exemplary and / or illustrative, rather than limiting, the scope of the disclosure being specified by the appended claims rather than the preceding description, and thus, all alternative embodiments and changes to the embodiments falling within the meaning and range of equivalents of the claims are included therein.

Claims

1. A clockwork swing assembly, characterized by, Comprising: a frame assembly including a housing; a drive spring positioned within the housing and having a drive spring axis (X3) oriented in a non-vertical direction relative to a vertical plane; a swing arm assembly connected to the frame assembly to receive energy from the drive spring, the swing arm assembly including a swing arm and a swing arm pivot, the swing arm being rotatable about a swing arm axis (X1) oriented in a non-horizontal direction relative to a horizontal plane; and a winding mechanism including a winding shaft positioned along the drive spring axis (X3), the winding mechanism having a first end connected with a crank assembly and a second end connected with a spool; wherein the drive spring includes a first end connected with an attachment plate disposed about the winding shaft and a second end connected with the spool, such that rotation of the winding shaft winds the drive spring via the spool. The winding mechanism further includes:

2. The clockwork swing assembly of claim 1, wherein, a first winding gear disposed about the winding shaft and attached to the attachment plate; and a second winding gear in meshing engagement with the first winding gear; wherein stored energy released from the drive spring rotationally drives the first winding gear, the first winding gear rotationally drives the second winding gear; an escapement assembly connected to the frame assembly, the escapement assembly including an escapement shaft connected to the second winding gear for rotationally driving the escapement shaft, the escapement shaft being oriented along an escapement axis (X2), the escapement assembly including: a carrier coupled to the escapement shaft and configured to rotate about the escapement axis (X2); and a pusher including a first end connected with the carrier and a second end connected with the swing arm assembly; wherein the pusher drives the swing arm assembly to rotate when the escapement gear is driven by stored energy released from the drive spring via the connection of the escapement shaft with the second winding gear; and an escapement gear fixed to the escapement shaft and configured to be driven via the second winding gear, the escapement gear including a plurality of teeth. The escapement assembly further includes:

3. The clockwork swing assembly of claim 2, wherein, a pawl pivotably attached to the frame assembly, the pawl including a pawl tooth selectively engageable with the teeth of the escapement gear to prevent rotation of the escapement gear in a drive direction when the swing arm is in an intermediate state; a clip pivotably attached to the carrier and selectively engageable with the teeth of the escapement gear when the swing arm is rotated and the pawl tooth is disengaged from the escapement gear; an amplitude control assembly; and an amplitude control lever; wherein the amplitude control lever includes a first stop and a second stop, the first stop and the second stop being spaced apart from each other and each configured to control a swing amplitude. The amplitude control assembly includes a drop plate configured to selectively limit a travel of the clip, and the amplitude control lever is configured to selectively adjust a position of the drop plate, wherein the drop plate includes an engagement portion configured to engage with a portion of the clip and an attachment configured to engage with a portion of the amplitude control lever.

4. The clockwork swing assembly of claim 3, wherein, ​ 5. The clockwork swing assembly of claim 4, wherein, The amplitude control lever includes a closed position.

6. The clockwork swing assembly of claim 5, wherein, The housing supporting the amplitude control assembly includes a downward stop for limiting further movement of the amplitude control lever, the downward stop corresponding to the closed position of the amplitude control lever.

7. The clockwork swing assembly of claim 4, wherein, Further comprising a gap between the accessory configured to engage a portion of the amplitude control lever and the housing supporting the amplitude control assembly when the amplitude control lever is in the closed position, thereby enabling the drop plate to float.

8. A clockwork swing assembly characterized by, Comprising: a frame assembly including a housing; a drive spring positioned within the housing and having a drive spring axis (X3) oriented in a non-vertical direction relative to a vertical plane; a swing arm assembly connected to the frame assembly to receive energy from the drive spring, the swing arm assembly including a swing arm and a swing arm pivot, the swing arm being rotatable about a swing arm axis (X1) oriented in a non-horizontal direction relative to a horizontal plane; a tensioning mechanism including a tensioning shaft positioned along the drive spring axis (X3); and a torque limiting clutch configured to prevent over-tensioning of the drive spring.

9. The clockwork swing assembly of claim 8, wherein, The torque limiting clutch is radially supported at its axis of rotation.

10. The clockwork swing assembly of claim 8, wherein, An outer lower bearing circumference of the torque limiting clutch is axially supported by the housing.

11. The clockwork swing assembly of claim 10, wherein, Further comprising a low friction spacer between the housing and the lower bearing circumference of the torque limiting clutch.

12. The clockwork swing assembly of claim 8, wherein, An outer upper bearing circumference of the torque limiting clutch is axially supported by a crown.

13. The clockwork swing assembly of claim 8, wherein, The tensioning mechanism has a first end connected with a crank assembly and a second end connected with a spool.

14. The clockwork swing assembly of claim 13, wherein, The torque limiting clutch includes a torque clutch spring assembled on the spool, the torque clutch spring being configured to be tensioned when the tensioning shaft is rotated in a tensioning direction and to slip when the drive spring is tensioned beyond a predetermined torque.

15. The clockwork swing assembly of claim 14, wherein, Further comprising a tensioning mechanism including a tensioning shaft positioned along the drive spring axis (X3), the tensioning mechanism having a first end connected with a crank assembly and a second end connected with a spool; wherein the torque limiting clutch includes: a first housing operatively connected to the crank assembly, the first housing including a clutch drive tooth; a clutch hub fixed to the crank assembly; and a clutch pawl pivotably connected to the clutch hub via a biasing element, the clutch pawl being biased by the biasing element to selectively engage the clutch drive tooth; wherein when the drive spring is tensioned via the crank assembly, the clutch pawl engages the clutch drive tooth up to a predetermined torque limit to transfer torque from the crank assembly to the drive spring, and when the torque transferred from the crank assembly to the drive spring exceeds the predetermined torque limit, the clutch pawl disengages the clutch drive tooth to prevent further transfer of torque from the crank assembly to the drive spring.

16. The clockwork swing assembly of claim 13, wherein, The torque limiting clutch includes: an input shaft connected to the crank assembly; an output shaft connected to the drive spring; a cap fixed to the input shaft; and a clutch spool fixed to the output shaft and clamped to the cap; wherein the cap and the spool are configured to slide relative to one another when a predetermined force is overcome to prevent the drive spring from being over-tightened.

17. The clockwork swing assembly of claim 16, wherein, The torque limiting clutch includes: a shaft connected to the crank assembly; an input hub including at least one engagement member; and an output hub connected to the shaft, the output hub including at least one protrusion engageable with the engagement member; wherein the at least one protrusion is configured to disengage from the at least one engagement member when a predetermined force from the crank assembly is overcome to prevent the drive spring from being over-tightened.

18. The clockwork swing assembly of claim 17, wherein, The at least one engagement member is a resilient member biased toward engagement with the at least one protrusion.

19. The clockwork swing assembly of claim 17, wherein, The at least one engagement member is pivotably attached to the input hub.

20. The clockwork swing assembly of claim 17, wherein, A spring is also included, the spring connected to the at least one engagement member and biased toward engagement with the at least one protrusion.

21. The clockwork swing assembly of claim 8, wherein, A low-friction support washer is also included between the housing and the torque limiting clutch, the low-friction support washer mounted in a gear cap of the housing.

22. A clockwork swing assembly characterized by, includes: a frame assembly having an upper end and a lower end, a base member at the lower end of the frame assembly, and an upright frame member extending from the base member to the upper end of the frame assembly, the frame assembly including a housing; a drive spring positioned within the housing and having a drive spring axis (X3) oriented in a non-vertical direction relative to a vertical plane; and a swing arm assembly connected to the frame assembly to receive energy from the drive spring, the swing arm assembly including a swing arm and a swing arm pivot, the swing arm rotatable about a swing arm axis (X1) oriented in a non-horizontal direction relative to a horizontal plane; wherein the upright frame member is welded to the base member.

23. The clockwork swing assembly of claim 22, wherein, The frame assembly further includes: a support at the lower end of the frame assembly, the support configured to rest on the ground, and a handle positioned adjacent to the upper end of the frame assembly.

24. The clockwork swing assembly of claim 23, wherein, The support extends in an opposite direction from the base member.

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