WINDOW TYPE OSCILLATOR ASSEMBLY AND METHOD OF USE THEREOF

Abstract

The present disclosure is directed to a wind-up swing assembly. The wind-up swing assembly includes a swing arm assembly, a drive spring, and an escapement assembly. The axes of the swing arm assembly, the drive spring, and the escapement assembly may be angled relative to one another. The axis of the drive spring may be angled non-perpendicularly relative to a vertical plane. The axis of the swing arm assembly may be angled non-horizontally relative to a horizontal plane or support surface.

Description

[Technical field]

[0001] CROSS-REFERENCE TO RELATED APPLICATIONS This application claims the benefit of priority to U.S. Provisional Patent Application No. 63 / 324,825, filed March 29, 2022, U.S. Provisional Patent Application No. 63 / 409,439, filed September 23, 2022, and U.S. Provisional Patent Application No. 63 / 485,756, filed February 17, 2023, the entireties of which are incorporated herein by reference.

[0002] FIELD OF THE DISCLOSURE The present disclosure relates generally to child rocking assemblies, and more particularly, to non-motorized child rocking assemblies. [Background technology]

[0003] Children's swings are widely known. Many known children's swings are powered through electricity or batteries. These types of children's swings may be considered motorized swings because they have a dedicated motor unit or other drive mechanism that provides a cyclical or rocking motion and requires a power source. Due to environmental concerns, there is a growing commercial demand among many consumers for more environmentally friendly products that do not require electricity to operate, which often requires the consumption of fossil fuels or batteries that can be harmful to the environment.

[0004] Prior to the commercial advent of powered swings, many known children's swings relied on human power or were powered by a horizontally disposed drive spring, typically with a central axis (i.e., the drive spring axis) extending along a horizontal direction and located above the children's swing.

[0005] While the use of a drive spring to power the swing assembly may accommodate a more environmentally friendly children's swing option, conventional swings powered by a drive spring typically suffer from undesirable drawbacks. For example, conventional reel swings have a relatively short operating time (e.g., 20 minutes) after being fully reeled in. Additionally, conventional reel swings typically require a large footprint and take up a large amount of space.

[0006] Additionally, in addition to increasing the operating time and reducing the footprint of a reel swing, it can also be difficult to efficiently transfer force between the various sub-components of the swing assembly, such as the drive spring, escapement assembly, and swing arm assembly.

[0007] Since the amount of energy that can be stored in a mainspring is relatively small, it is important that energy losses due to friction are minimized. Therefore, a low-friction design is required, especially for transmitting rotation between shafts. This is advantageous for shafts that are not parallel to each other. It is advantageous to achieve energy transfer between the shafts of the various components with minimal friction losses, while maintaining a cost-effective and feasible design.

[0008] It is therefore desirable to provide a retractable children's swing that is compact, can provide a relatively long operating time, and can transmit power efficiently between its major components. Summary of the Invention

[0009] The present disclosure relates to a wind-up children's swing that addresses the typical shortcomings of conventional wind-up swings. Unlike conventional wind-up swings in which the drive spring is oriented along a horizontal axis above the swing itself, the swing assembly of the present disclosure has a drive spring with a central axis (i.e., the drive spring axis) oriented along a non-horizontal direction. In some examples, the drive spring axis can be angled several degrees from a vertical axis. In some examples, the drive spring axis can be angled 45 degrees to 90 degrees from the ground plane (i.e., perpendicular to the ground plane). In other examples, the drive spring axis can extend along a vertical direction. The wind-up swing disclosed herein also has a longer operating time, which can exceed 45 to 60 minutes based on the user's winding of the drive spring, approximately 20 seconds, or approximately 20 to 30 turns.

[0010] In one example, a reel-type swing assembly is provided that includes a swing arm assembly having a swing arm and a swing arm pivot. The swing arm axis (X1) is oriented in a non-horizontal direction relative to the ground surface. The reel-type swing assembly is configured to impart a swing motion to a swing arm attached to a seat frame through the swing arm pivot. The swing motion can provide a pendulum-like motion in a side-to-side direction as opposed to a swing motion in a front-to-back direction. The motion imparted to the seat frame can have an arc profile and be imparted in a non-vertical plane. One of ordinary skill in the art will appreciate that the seat frame itself can be pivoted to move the seat frame side-to-side or forward-to-back based on its orientation.

[0011] A drive spring may be provided having a drive spring axis (X3), which may be non-vertical and may be at an angle to the swing arm axis (X1).

[0012] An escapement assembly may further be included having an escapement axis (X2) that may be angled relative to the swing arm axis (X1).

[0013] The swing arm axis (X1), the escapement axis (X2), and the drive spring axis (X3) may each be at an angle to one another.

[0014] The swing arm assembly may include an adjustment assembly and a seat frame, the adjustment assembly being configured to adjust a reclining angle of the seat frame.

[0015] The drive spring may be located to the side, away from the seat frame, as opposed to being located overhead on the seat frame.

[0016] A frame assembly and a base assembly may typically be provided to support the swing assembly relative to a ground surface. The frame assembly may include a support at a lower end configured to rest on the ground surface and a handle defined at an upper end, both of which may provide additional stability to the swing assembly during winding or cranking.

[0017] A crank assembly may be provided on the frame assembly. The crank assembly may be provided on a top surface of the frame assembly. The crank assembly may include a crank handle configured to extend from the frame assembly, where rotation of the crank handle about a crank pivot provides a rotational input to the mainspring assembly.

[0018] The crank handle may be configured to fold outwardly from the frame assembly in a use state and fold into a pocket defined by the frame assembly in a storage state. As one of ordinary skill in the art would appreciate, other arrangements for the crank assembly may be provided. For example, the crank assembly may be provided on the bottom of the frame.

[0019] The winding mechanism may be disposed between the crank assembly and the drive spring. The winding shaft may be coupled to the crank assembly at a first end and extend inwardly of the drive spring. The winding shaft may be coupled to the spool at a second end. A terminal end of the drive spring is further coupled to the spool such that rotation of the winding shaft winds the drive spring through the spool.

[0020] The drive spring can include a first end coupled to the mounting plate and a second end coupled to the spool. The mounting plate can be configured to be attached to a first winding gear disposed about the winding shaft and matingly coupled to a second winding gear. The second winding gear can be coupled to the escapement assembly. The second winding gear can be configured to rotate to drive the escapement shaft.

[0021] The escapement assembly may further include an escapement gear fixed to the escapement shaft. The escapement gear may be configured to be driven through the second winding gear. The escapement assembly may further include a pawl, a dog, a carrier, an actuator, and a pusher. The pusher may include a first end coupled to the actuator and a second end coupled to the swing arm pivot.

[0022] A swing control assembly may be provided that includes a drop plate configured to selectively limit the stroke of the dog and a swing control lever configured to selectively adjust a position of the drop plate. The drop plate may include an engagement portion configured to engage a portion of the dog through a control edge, a recess adjacent the control edge, and an appendage configured to engage a portion of the swing control lever. The swing control lever may include first and second stops spaced apart from one another and each configured to engage an appendage of the drop plate.

[0023] The winding oscillating assembly may further include a torque limiting clutch configured to prevent overwinding of the drive spring. In an embodiment, the torque limiting clutch may include a torque clutch spring assembled to the spool and configured to wind when the winding shaft rotates in the winding direction and to slip when the drive spring is wound beyond a predetermined torque.

[0024] In another embodiment, the torque limiting clutch includes a first housing secured to the frame assembly and operably coupled to the crank assembly, the first housing including a clutch drive tooth, a clutch hub coupled to the crank assembly, and a clutch pawl pivotally coupled to the clutch hub through a biasing element, the clutch pawl being biased by the biasing element to selectively engage the clutch drive tooth. As the drive spring winds through the crank assembly, it engages the clutch drive tooth to transfer torque from the crank assembly to the drive spring up to a predetermined torque limit. When the torque transferred by 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.

[0025] In another example, the torque limiting clutch includes an input shaft coupled to the crank assembly, an output shaft coupled to the drive spring, a cap coupled to the input shaft, and a spool secured to the output shaft and sealed to the cap, where the cap and spool may slip relative to one another to prevent the drive spring from overwinding when a predetermined force is exceeded.

[0026] In another example, a swing assembly is provided that includes a frame assembly oriented non-vertically relative to a vertical plane and a swing arm assembly coupled to the frame assembly, the swing arm assembly including a swing arm pivot pivotally attached to the frame assembly, the swing arm having a first end coupled to the swing arm pivot and a second end coupled to the seat assembly. The swing arm is rotatable about a swing arm axis (X1) oriented non-horizontally relative to the horizontal plane. The swing arm further includes a support hub disposed at the second end of the swing arm and configured to receive the seat assembly.

[0027] In another example, a winding type rocking assembly includes a frame assembly, a drive spring disposed within the frame assembly and oriented in a non-vertical direction relative to a vertical plane, a crank assembly provided on the frame assembly and configured to input a drive torque to the drive spring, a seat frame pivotally coupled to the frame assembly, the seat frame including a rocking 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 and configured to transfer energy from the drive spring to impart a rocking motion to the seat frame.

[0028] A method of using a wind-up oscillating assembly is provided that includes driving a crank assembly coupled to a winding mechanism by rotating a crank handle, winding a drive spring coupled to the winding mechanism, and selectively releasing energy from the drive spring through an escapement assembly having a carrier linked to the oscillating arm pivot through a pusher to move the oscillating arm pivot in a first direction during a power stroke and in a second direction during a non-power stroke.

[0029] A method of driving a seat frame of a wind-up rocker assembly is provided, the method comprising: rotating a crank assembly coupled to a drive spring such that the drive spring is wound, the drive spring being disposed along a drive spring axis (X3) oriented non-perpendicularly relative to a vertical plane; transferring energy from the wound drive spring to an escapement assembly having an escapement shaft (X2) angled relative to the drive spring axis (X3); and selectively releasing energy from the escapement assembly to a rocker arm pivot. The rocker arm pivot is coupled to the seat frame and has a rocker arm axis (X1), the rocker arm axis (X1) oriented non-horizontally relative to a horizontal plane and angled relative to the drive spring axis (X3) and the escapement shaft (X2).

[0030] Further configurations are disclosed below and in the claims.

[0031] The foregoing summary, as well as the following detailed description, will be best understood when read in conjunction with the accompanying drawings illustrating preferred embodiments of the present disclosure. [Brief description of the drawings]

[0032] [Figure 1A] FIG. 1A is a perspective view of a retractable child rocking assembly. [Figure 1B] FIG. 1B is another perspective view of the retractable child rocking assembly. [Figure 1C] FIG. 1C is a top view of a retractable child rocking assembly. [Diagram 2] FIG. 2 is a perspective view of the winding child rocking assembly with the outer housing frame removed. [Figure 3A] FIG. 3A is a top perspective view of the frame assembly with the crank assembly in an unused or stowed position. [Figure 3B] FIG. 3B is a top perspective view of the frame assembly with the crank assembly in use. [Figure 3C] FIG. 3C is a schematic diagram of the crank assembly according to the first embodiment. [Figure 3D] FIG. 3D is a schematic diagram of a crank assembly according to a second embodiment. [Figure 3E] FIG. 3E is a schematic diagram of a crank assembly according to a third embodiment. [Figure 3F] FIG. 3F is a schematic diagram of a crank assembly according to a fourth embodiment. [Figure 3G] FIG. 3G is a top perspective view of a frame assembly with a crank assembly in an unused or stowed position according to an example. [Figure 3H] FIG. 3H is a top perspective view of a frame assembly with a crank assembly in use according to one example. [Figure 3I] FIG. 3I is a bottom view of the tower cap on top of the frame assembly. [Figure 4A]FIG. 4A is a perspective view of the top of a retractable child rocking assembly. [Figure 4B] FIG. 4B is a side view of the top of the retractable child rocking assembly. [Figure 4C] FIG. 4C is a perspective view of the bottom of the drive spring. [Figure 4D] FIG. 4D is a perspective cross-sectional view of the bottom of the drive spring. [Figure 4E] FIG. 4E is another perspective view of the drive spring and the bottom of the frame portion. [Figure 4F] FIG. 4F is another perspective view of the drive spring and the bottom of the frame part according to another example. [Figure 5A] FIG. 5A is a perspective view of the top of a retractable child rocking assembly. [Figure 5B] FIG. 5B is an exploded perspective view of the escapement assembly. [Figure 5C] FIG. 5C is a perspective view of the carrier, pivot housing, and pusher in an assembled state. [Figure 5D] FIG. 5D is a perspective view of the carrier, pivot housing, and pusher in an exploded state. [Figure 5E] FIG. 5E is a cross-sectional view showing the various axes of the winding rocker assembly. [Figure 5F] FIG. 5F is a close-up view of the interface between the pusher and the carrier. [Figure 5G] FIG. 5G is a front view of the interface between the pusher and the carrier. [Figure 5H] FIG. 5H is an enlarged view of a portion of the carrier configured to receive a pusher. [Figure 6A] FIG. 6A is a front view of the escapement assembly in a first state. [Figure 6B] FIG. 6B is a front view of the escapement assembly in a second state. [Figure 6C] FIG. 6C is a front view of the escapement assembly in a third state. [Figure 6D] FIG. 6D is a front view of the escapement assembly in the fourth state. [Figure 7A] FIG. 7A is a perspective view of the swing control assembly. [Figure 7B] FIG. 7B is a front view of the swing control assembly in a first state. [Figure 7C] FIG. 7C is a front view of the swing control assembly in a second state. [Figure 7D] FIG. 7D is a front view of the swing control assembly in a third state. [Figure 8A] FIG. 8A shows the various phases of the pawl and the second set of teeth. [Figure 8B] FIG. 8B shows the various phases of the pawl and the second set of teeth. [Figure 8C] FIG. 8C shows the various phases of the pawl and the second set of teeth. [Figure 9A] FIG. 9A is a perspective view of a torque limiting clutch according to an embodiment. [Figure 9B] FIG. 9B is a side view of the torque limiting clutch. [Figure 9C] FIG. 9C is a cross-sectional view of the torque limiting clutch. [Figure 10A] FIG. 10A is a perspective view of another example of a frame assembly. [Figure 10B] FIG. 10B is an enlarged view of the vertex area of ​​the frame assembly of FIG. 10A. [Figure 10C] FIG. 10C is another enlarged view of the vertex area portion of the frame assembly of FIG. 10A. [Figure 11] FIG. 11 is a top perspective view of a gear assembly according to an example. [Figure 12A] FIG. 12A is a side view of the torque limiting clutch assembly. [Figure 12B] FIG. 12B is another side view of the torque limiting clutch assembly. [Figure 12C] FIG. 12C is an exploded perspective view of the torque limiting clutch assembly. [Figure 12D] FIG. 12D is a top view of the torque limiting clutch assembly in a first condition. [Figure 12E]FIG. 12E is a top view of the torque limiting clutch assembly in a second condition. [Figure 12F] FIG. 12F is a top view of the torque limiting clutch assembly in a third condition. [Figure 12G] FIG. 12G is a bottom view of the interior of the torque limiting clutch assembly. [Figure 12H] FIG. 12H is a perspective view of a torque limiting clutch according to an embodiment. [Figure 12I] FIG. 12I is an exploded perspective view of the torque limiting clutch shown in FIG. 12H. [Figure 12J] FIG. 12J is a cross-sectional view of a torque limiting clutch according to an embodiment. [Figure 12K] FIG. 12K is an exploded perspective view of the torque limiting clutch shown in FIG. 12J. [Figure 12L] FIG. 12L is a top perspective view of the torque limiting clutch shown in FIG. 12J. [Figure 12M] FIG. 12M is a perspective view of the underside of the torque limiting clutch shown in FIG. 12J. [Figure 12N] FIG. 12N is a perspective view of a torque limiting clutch according to an embodiment. [Figure 12O] FIG. 12O is a plan view of the torque limiting clutch shown in FIG. 12N. [Figure 12P] FIG. 12P is a cross-sectional view of the torque limiting clutch taken along plane II shown in FIG. 12O. [Figure 12Q] FIG. 12Q is a cross-sectional view of the torque limiting clutch taken along the plane II-II shown in FIG. 12O. [Figure 13A] FIG. 13A is a close-up view of the interface between the frame assembly and the swing arm. [Figure 13B] FIG. 13B is another close-up view of the interface between the frame assembly and the swing arm. [Figure 14] FIG. 14 is a perspective view of a seat frame in one direction. [Figure 15A] FIG. 15A is a first close-up view of the interface between the swing arm and the swing arm pivot. [Figure 15B] FIG. 15B is a second close-up view of the interface between the swing arm and the swing arm pivot. [Figure 15C] FIG. 15C is a close-up view of the swing arm removed from the swing arm pivot. [Figure 16A] FIG. 16A is a perspective view of a retractable child rocking assembly according to an alternative aspect of the present disclosure. [Figure 16B] FIG. 16B is a side view of the winding child rocking assembly shown in FIG. 16A. [Figure 16C] FIG. 16C is a perspective view of the roll-up child rocking assembly shown in FIG. 16A showing the seat portion of the seat assembly and the base assembly. [Figure 16D] FIG. 16D is a perspective view of the roll-up child rocking assembly shown in FIG. 16B showing the seat portion of the seat assembly and the base assembly. [Figure 17] FIG. 17 is a top perspective view of the crank assembly. [Figure 18] FIG. 18 is a perspective view of a swing arm assembly and a seat assembly disposed above the swing arm assembly. [Figure 19] 19 is a first side view of the swing arm assembly and seat assembly shown in FIG. 18 with the seat assembly disposed on the swing arm assembly. [Figure 20] 20 is a second side view of the swing arm assembly and seat assembly shown in FIG. 18 with the seat assembly disposed on the swing arm assembly. [Figure 21A] FIG. 21A is a perspective view of the swing arm assembly. [Figure 21B] FIG. 21B is a perspective view of the swing arm assembly. [Figure 21C] FIG. 21C is an exploded perspective view of the support hub of the swing arm shown in FIGS. 21A and 21B. [Figure 21D] FIG. 21D is a bottom perspective view of a portion of the support hub shown in FIG. 21C. [Figure 22]22 is an exploded perspective view of the seat assembly shown in FIG. [Figure 23A] 23A includes a top perspective view of the support base of the seat assembly shown in FIG. [Figure 23B] 23B includes a bottom perspective view of the support base of the seat assembly shown in FIG. [Figure 24A] FIG. 24A is a perspective view of a connecting assembly according to an alternative aspect of the present disclosure. [Figure 24B] FIG. 24B is a perspective view of a support hub according to an alternative aspect of the present disclosure. [Diagram 25] FIG. 25 is a cross-sectional view of a portion of the support base shown in FIG. 23B in a locked position. [Figure 26] FIG. 26 is a cross-sectional view of a portion of the support base shown in FIG. 23B in an unlocked position. [Figure 27] FIG. 27 is a cross-sectional view of a portion of the support base shown in FIG. 23B in a locked position with the support hub disposed therein. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0033] Certain terminology is used in the following description for convenience only and not as a limitation. The terms "front," "back," "upper," and "lower" refer to the orientations specified in the drawings to which reference is made. The terms "inwardly" and "outwardly" refer to directions toward and away from the part referenced in the drawings. "At least one of a, b, and c," where a, b, and c represent enumerated items, means any single item a, b, or c, or a combination of each item. This term includes the words specifically mentioned above, derivatives thereof, and similar words.

[0034] A wind-up child rocking assembly 10 is disclosed herein, as shown in Figures 1A-1C. The wind-up rocking assembly 10 includes a rocking arm assembly 12 with a rocking arm 25 and a rocking arm pivot 27 having a rocking arm axis (X1), as shown in Figures 2, 4B, and 5E. The rocking arm pivot 27 typically includes a pivot housing 27a and at least one bearing 27b, as shown in Figure 4A. For example, and without limitation, the at least one bearing 27b may 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 may be supported through a portion of the frame assembly 35a, such as the upright frame member 35c, which will be described in further detail herein.

[0035] 5C-5D and described in more detail herein, the pivot housing 27a may include an opening 27c configured to receive a portion of the pusher 90 (i.e., a first end 90a of the pusher 90). The pivot housing 27a is configured to support the swing arm 25, which pivots about a swing arm pivot 27. The swing arm 25 may include a first end 25a configured to engage the swing arm pivot 27 and a second end 25b configured to support the seat frame 15. The housing 26 is provided to enclose the first end 25a of the swing arm 25 and the swing arm pivot 27.

[0036] The swing arm axis (X1) may be oriented in a non-horizontal direction or angled with respect to the horizontal plane (P1) along the x-axis. In one aspect, the swing arm axis (X1) may be oriented in a non-vertical direction or angled with respect to the vertical plane (P2). The angle (θ1) between the swing arm axis (X1) and the horizontal plane (P1) is shown in FIG. 4B. The swing arm axis (X1) may be oriented at an angle of 30 degrees to 70 degrees with respect to the ground surface or horizontal plane (P1). Preferably, the swing arm axis (X1) may be oriented at an angle of 40 degrees to 60 degrees with respect to the ground surface or horizontal plane (P1). More preferably, the swing arm axis (X1) may be oriented at an angle of 45 degrees to 55 degrees with respect to the ground surface or horizontal plane (P1). In another example, the swing arm axis (X1) may be oriented at an angle of 50 degrees with respect to the ground surface or horizontal plane (P1). The relative direction and angle of the swing arm axis (X1) is configured to maximize the potential energy of the take-up swing assembly 10, thereby increasing the operating time. In addition, the swing arm axis (X1) is positioned to minimize the footprint of the take-up swing assembly 10.

[0037] The wind-up oscillating assembly 10 also includes a drive spring 60 having a drive spring axis (X3). The drive spring axis (X3) may be non-vertical or oriented at an angle to a vertical plane (P2) along the y-axis, and may be angled to the oscillating arm axis (X1). In one aspect, the drive spring axis (X3) may be non-horizontal or oriented at an angle to a horizontal plane (P1) along the earth's surface or the x-axis. One of ordinary skill in the art would recognize that the vertical plane (P2) is perpendicular to the horizontal plane (P1). The angle (θ3) between the drive spring axis (X3) and the vertical plane (P2) is shown in FIG. 4B. The drive spring axis (X3) may be angled from 5 degrees to 20 degrees to the vertical plane (P2). One skilled in the art will appreciate that in other examples, the drive spring axis (X3) may be at an angle of 20 degrees or more with respect to the vertical plane (P2) depending on the arrangement of any of the associated bevel gears. Preferably, the drive spring axis (X3) may be at an angle of 5 degrees to 15 degrees with respect to the vertical plane (P2). More preferably, the drive spring axis (X3) may be at an angle of 5 degrees to 10 degrees with respect to the vertical plane (P2). In one example, the drive spring axis (X3) may be at an angle of 7 degrees with respect to the vertical plane (P2). The direction and angle of the drive spring axis (X3) may be selected to optimize the stability of the wind-up oscillating assembly 10 while minimizing the risk of inadvertent tipping by locating the center of gravity of the wind-up oscillating assembly 10 with respect to the base assembly 35b.

[0038] The winding oscillating assembly 10 further comprises an escapement assembly 70 having an escapement shaft (X2). The escapement shaft (X2) may be at an angle to the oscillating arm axis (X1). The escapement shaft (X2) may be substantially parallel to the earth's surface or a horizontal plane (P1). Alternatively, one of ordinary skill in the art will appreciate that the escapement shaft (X2) may be at an angle to the earth's surface or a horizontal plane (P1).

[0039] The swing arm axis (X1), the escapement shaft (X2), and the drive spring axis (X3) may each be angled relative to one another, as shown in FIGS. 2, 4B, and 5E. As shown in FIG. 4B, the swing arm axis (X1), the escapement shaft (X2), and the drive spring axis (X3) may be angled relative to one another. The relative angles between the first, second, and / or third axes (X1, X2, X3) may be between 0 degrees and 90 degrees in embodiments. One of ordinary skill in the art will appreciate that these angles may vary depending on the particular configuration desired for the wind-up spring assembly 10. Additionally, the first, second, and / or third axes (X1, X2, X3) may be disposed at any relative angle and may be disposed in a number of different planes in other embodiments.

[0040] 1A and 1B, the swing arm assembly 12 may include, in addition to the swing arm 25, an adjustment assembly 20 and a seat frame 15. The adjustment assembly 20 is configured to adjust the reclining angle of the seat frame 15, and the adjustment assembly 20 may be disengaged or engaged through a button, lever, or other actuation / adjustment feature. The seat frame 15 may be configured to be adjusted (either forward or reverse) from 0 degrees relative to a horizontal plane (i.e., flat) to at least 20 to 30 degrees of inclination relative to a horizontal plane.

[0041] Unlike overhead wind-up spring assemblies that require vertical space to support the drive spring, the wind-up oscillating assembly 10 disclosed herein positions the drive spring 60 laterally adjacent or to the side of the seat frame 15. Thus, the drive spring 60 is not located overhead relative to the seat frame 15.

[0042] The winding oscillating assembly 10 further comprises a frame assembly 35a, a base assembly 35b, and an upright frame member 35c. The frame assembly 35a, including the base assembly 35b and the upright frame member 35c, may include an outer shell or housing that surrounds or contains internal elements, such as the drive spring 60.

[0043] The frame assembly 35a may include a support 37 at a lower end and a handle 36 at an upper end. The support 37 is configured to engage the ground surface to provide an additional stable surface. The support 37 may be formed as a protrusion large enough to accommodate a user's foot on the upper side, where the user can place their foot on the support 37 to stabilize the wind-up oscillating assembly 10 while winding the drive spring 60 through the crank assembly 40. The support 37 may extend outwardly from the remainder of the frame assembly 35a. For example, but not limited to, the support 37 may extend outwardly at least 3 inches from the frame assembly 35a. In one example, but not limited to, the support 37 may 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.

[0044] The handle 36 may be provided as a lip, edge, or other type of recess formed in the frame assembly 35a. One of ordinary skill in the art will appreciate that the handle 36 may be formed in other areas of the winding oscillating assembly 10 in addition to the frame assembly 35a. The handle 36 may be sized or configured to accommodate a user's hand to further support the winding oscillating assembly 10 while winding the drive spring 60. The handle 36 may be used to lift or move the winding oscillating assembly 10 to another location. For example, but not limited to, the handle 36 may have a depth of at least 1 inch, and preferably at least 2 inches. The handle 36 is configured to allow a user to move the winding oscillating assembly 10 more easily and to improve the overall mobility of the winding oscillating assembly 10.

[0045] The base assembly 35b, shown in a top view in FIG. 1C, may be formed as two legs 39a, 39b extending from an upright frame member 35c. In one example, the base assembly 35b may include two bent or arched legs 39a, 39b having a generally U-shaped or horseshoe profile. As shown in FIG. 1C, the base assembly 35b may have a profile that generally overlaps or fits at least partially into the profile or contour of the seat frame 15 (as shown by the termination of the legs 39a, 39b). One of ordinary skill in the art will appreciate that the profile of the base assembly 35b may vary.

[0046] The windup oscillating assembly 10 further includes a crank assembly 40 that provides an interface for a user to impart motion or energy to the drive spring 60. The crank assembly 40 may be generally located on the frame assembly 35a. The crank assembly 40 may be provided on a top surface of the frame assembly 35a. One of ordinary skill in the art will appreciate that the crank assembly 40 may be located on other portions or areas of the frame assembly 35a or other portions of the windup oscillating assembly 10.

[0047] 3A and 3B, crank assembly 40 may include a crank handle 44 configured to extend from frame assembly 35a. Rotation of crank handle 44 about crank pivot 46 provides an input to drive spring 60. Crank handle 44 may be configured to fold outwardly from frame assembly 35a in an in-use state and may be configured to fold within a pocket 47 defined on frame assembly 35b in a stored state. Crank handle 44 may include a grip 42 configured to be grasped by a user while winding drive spring 60.

[0048] An energy level indicator may be provided in the wind-up oscillating assembly 10. In one example in FIGS. 3A and 3B, an energy level indicator 120 is shown. The energy level indicator 120 may be a torque sensor in one example and may be operatively disposed between the drive spring 60 and the crank assembly 40. The energy level indicator 120 may provide indicia, such as a gauge, that indicate the amount of energy stored by the drive spring 60. A user may quickly determine how much time is left for the oscillating motion to continue and decide to further drive the crank assembly 40. The energy level indicator 120 may include a sensor or spring disposed in series with the drive spring 60. One of ordinary skill in the art will appreciate that various configurations may measure the energy in the drive spring 60. Additionally, the location and specific shape of the energy level indicator 120 may vary.

[0049] Various configurations of the crank assembly 40 can be provided, as shown in FIGS. 3C-3F. As shown in FIG. 3C, the arm 144 of the crank assembly 40 can act as a handle that pivots outward in the use or crank position and can be provided off-center from the mid-portion of the frame. As shown in FIG. 3D, the arm 244 of the crank assembly 40 can act as a handle that pivots outward from the frame. Increasing the length of the arm can provide a larger input force to the drive spring 60. As shown in FIG. 3E, the arm 344 of the crank assembly 40 can move radially outward to act as a handle. As shown in FIG. 3F, the arm 444 of the crank assembly 40 can have a pivot portion 444a configured to be gripped by a user.

[0050] 3G-3I provide further views of the crank assembly according to another example. In one configuration, a tower cap 540 is provided that generally mounts to the top of the frame assembly. The tower cap 540 may include an opening 542 configured to allow an arm 544 of the crank assembly 40 to extend therethrough. The arm 544, which may also be referred to as a knob, may be configured to rotate to wind the drive spring 60. The arm 544 may be biased to a closed or non-use position with a spring or biasing element as a safety feature, which serves as a safety feature. The tower cap 540 may be snapped 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 detail in FIGS. 12A-12G and described in detail), creating a tight fit between the tower cap 540 and the first housing 402 with minimal pivoting (e.g., wiggle) movement therebetween. The inner wall 546 also aids in aligning the tower cap 540 with the clutch assembly 400 during assembly. The take-up knob or arm 544 can be configured to pivot downwardly to be flush with the tower cap 540 for safety purposes and for a cleaner aesthetic.

[0051] As shown in Figures 4A and 4B, the wind-up oscillating assembly 10 further includes a wind-up mechanism 50 disposed between the crank assembly 40 and the drive spring 60. The wind-up mechanism 50 is generally configured to provide an interface between the crank assembly 40 and the drive spring 60 such that crank input from a user is converted into winding of the drive spring 60. The wind-up mechanism 50 may include a wind-up shaft 55 connected at a first end 55a to the crank assembly 40 as shown in Figure 4B. The wind-up shaft 55 may extend inside the drive spring 60 and be connected to the silent take-up spool 105 at a second end 55b of the wind-up shaft 55 as shown in Figures 4D-4E. Alternative arrangements of the wind-up shaft 55 may be provided.

[0052] Referring to the winding mechanism 50, as shown in FIGS. 4A and 4B, a mounting plate 52 can be attached to a first winding gear 54 that is disposed about a winding shaft 55 and configured to mate and engage with a second winding gear 56. The first and second winding gears 54, 56 can be bevel gears, in one example. The second winding gear 56 can be coupled to an escapement assembly 70. In one configuration, the second winding gear 56 is configured to rotate to drive an escapement shaft 75 (shown in FIGS. 5A-5B). Alternative arrangements can be provided for transferring motion or energy from the drive spring 60 to the escapement assembly 70.

[0053] As shown in FIGS. 4A-4E, the drive spring 60 can include a first end 60a connected to the mounting plate 52 and a second end 60b connected to the silent take-up spool 105, such that rotation of the take-up shaft 55 winds the drive spring 60 through the silent take-up spool 105.

[0054] 4C-4E, a power tube 66 may be provided that is aligned with the center of the drive spring 60 and prevents the drive spring 60 from meandering or tangling when wound. A first bearing 64 may be provided that supports both the winding shaft 55 and the power tube 66. A second bearing 106 may be provided between a portion of the upright frame member 35c and the winding shaft 55.

[0055] The silent take-up spool 105 may define a coupling 62 with the second end 60b of the drive spring 60. Clockwise rotation of the take-up shaft 55 rotates the silent take-up spool 105, thereby winding the drive spring 60 through the coupling 62. A connector 108 may be provided connecting the take-up shaft 55 to the silent take-up spool 105. The connector 108 may include a set screw, a knurled coupling, or other attachment configuration connecting the take-up shaft 55 and the silent take-up spool 105.

[0056] A slip clutch spring 100 may be provided that is configured to inhibit rotation of the winding shaft 55 in a typical non-winding direction. As shown, rotation of the winding shaft 55 in a winding direction, such as a clockwise direction, opens and causes the slip clutch spring 100 to slip. Conversely, rotation of the winding shaft 55 in a 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, a counterclockwise force on the silent winding spool 105 causes the slip clutch spring 100 to tighten. The slip clutch spring 100 resists the release of energy from the drive spring 60 whenever the drive spring 60 is in the wound position, both during winding and when the swing is in operation. Thus, in the event of a mechanical failure in the escapement, the winding crank (knob, spring, etc.) will not rotate indefinitely while releasing energy, ensuring safety and preventing injury to the user. As shown in Figures 4C-4E, a bracket 35d may be provided that is secured to the upright frame member 35c. The torque of the drive spring 60 is then resisted by the attachment of the slip clutch spring 100 to a pin 102 that is coupled to the bracket 35d or to the upright frame member 35c. Figure 4E shows the drive spring 60 pulled upward from the bottom of the frame for illustrative purposes only. As shown in Figure 4F, a terminal end 100' of the slip clutch spring 100 may be secured to a portion of the bracket 35d or to the upright frame member 35c.

[0057] The escapement assembly 70 is configured to control the release of energy from the drive spring 60 and provide separate and controlled bursts of energy to the seat frame 15. The escapement assembly 70 is configured to prevent the drive spring 60 from unwinding inadvertently. The escapement assembly 70 may include an escapement gear 74 having a plurality of teeth 74a and may be configured to be driven through engagement with the second winding gear 56 of an escapement shaft 75. The escapement gear 74 may be fixed to the escapement shaft 75. One such escapement assembly is disclosed in U.S. Patent No. 6,283,870, which is incorporated by reference as if fully set forth herein.

[0058] 5A-5B, escapement assembly 70 is shown in further detail along with drop plate 85 and swing amplitude control lever 95. Escapement assembly 70 may further include a carrier 72, a pawl 76, an actuator 78, a dog 80, and a pusher 90, each of which are described in more detail herein.

[0059] The pawl 76 is pivotally supported at a pawl pivot 76c. In one aspect, the pawl pivot 76c may be pivotally mounted to a portion of the frame assembly 35a, such as the upright frame member 35c. The force of the drive spring 60 urges the escapement gear 74 to rotate in a drive direction, such as a clockwise direction. However, initially, the pawl teeth 76a engage the teeth of the escapement gear 74 to prevent the escapement gear 74 from rotating in a clockwise direction and to prevent the drive spring 60 from unwinding all at once. The force of the drive spring 60 urges the escapement gear 74 in a clockwise direction, which causes the escapement gear 74 to exert a force on the pawl 76 to keep 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 under the force of gravity and rotate out of the way of the escapement gear 74.

[0060] The carrier 72 is coupled to the escapement shaft 75 and configured to rotate about an escapement axis (X2). The carrier 72 is further coupled to a first end 90a of a pusher 90. A second end 90a of the pusher 90 is coupled to the swing arm assembly 12. When the escapement gear 74 is driven through the coupling between the escapement shaft 75 and the second winding 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, a force from the drive spring 60 is transferred through the escapement assembly 12 to drive the swing arm assembly 12 in a first direction. After the stroke or swing is over, inertia drives the swing arm assembly 12 in a second direction opposite to the first direction. This process continues as long as there is remaining energy stored in the winding of drive spring 60.

[0061] The dog 80 is pivotally fixed to the carrier 72 at a dog pivot 80c, such that the dog 80 moves with the carrier 72 when the carrier 72 rotates with the swing arm assembly 12 about the escapement axis (X2). The shape of the dog 80 and the arrangement of the dog teeth 80a, 80b are such that the weight of the dog causes the dog 80 to rotate clockwise about the dog pivot 80c, thereby separating the dog tooth 80a from the teeth 74a of the escapement gear 74.

[0062] The actuator 78 is coupled to the escapement shaft and configured to rotate about the escapement axis (X2). The actuator 78 is configured to selectively engage the dog 80 through a dog engagement surface 78b that engages a dog control arm 80b. The actuator 78 is further configured to selectively engage the pawl 76 through a pawl engagement surface 78a that engages a pawl control arm 76b. The selective engagement controls the movement of the dog 80 and the pawl 78. The actuator 78 further includes an actuator weight 78c that is arranged to bias the actuator 78 in a clockwise direction when the actuator 78 is not acted upon by either the pawl 76 or the dog 80.

[0063] The pusher 90 operatively couples the escapement assembly 70 to the swing arm assembly 12. The pusher 90 is generally configured to convert the rotation of the escapement assembly 70 about the escapement axis (X2) into a swing or oscillation of the swing arm 25 about the swing axis (X1). The pusher 90, in one example, can be a rigid wire. One of ordinary skill in the art can 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 FIGS. 13A and 13B, the swing arm pivot 127 can include a first bevel gear 190a. The second bevel gear 190b can be coupled to the carrier 72 or other portion of the frame assembly. In one configuration, the second bevel gear 190b can be integrally formed with the carrier 72. The driving connection between the bevel gears 190a, 190b provides a swing or oscillating motion to the swing arm 25, providing the same functionality as the pusher 90 and its associated elements. The bevel gear arrangement is configured to provide a 1:1 ratio of rotational motion between the first and second bevel gears 190a, 190b, which provides a more efficient swing arrangement.

[0064] The pusher 90 includes a first end 90a coupled to the carrier 72 and a second end 90b coupled to the swing arm pivot 27. The pusher 90 may be configured to pivot and displace with multiple degrees of freedom. The first and second ends 90a, 90b of the pusher 90 may be held within the carrier 27 and swing arm pivot 27 with a predetermined amount of slack or a predetermined tolerance to allow for some predetermined play as the pusher 90 is driven back and forth for swinging motion.

[0065] As shown in Figures 5C and 5D, the first and second ends 90a, 90b of the pusher 90 may have bent or angled portions relative to the main body of the pusher 90. For example, the first end 90a may be bent upward and the second end 90b may be bent downward. The first end 90a is configured to be held within the opening 72a of the carrier 72. The opening 72a of the carrier 72 may include a through hole with at least one tapered region adjacent thereto. The opening 27c of the pivot housing 27a may include a through hole and at least one tapered region adjacent thereto. Because the ends 90a, 90b are not rigidly fixed to the carrier 72 and the pivot housing 27a, the pusher 90 may swing more freely, increasing the swing time.

[0066] 5E-5H show further aspects of the pusher 90 configuration. Referring to FIG. 5E, energy needs to be transferred from the escapement shaft (X2) to the swing arm pivot shaft (X1). These shafts can be arranged non-parallel to each other, and in one configuration, can be at an angle of 40 degrees to 60 degrees from each other. The pusher 90 is disposed between the carrier 72 and the pivot housing 27a to improve the buckling strength for transmitting torque. The coupling of the pusher 90 to both the carrier 72 on the escapement shaft (X2) and the pivot housing 27a on the swing arm pivot shaft (X1) is configured to allow the pusher 90 to cooperate with the coupling hole 72a of the carrier 72 and the coupling hole 27c of the pivot housing 27a, respectively. One skilled in the art can understand that the connection between the pusher 90 and the pivot housing 27a is similar. The ends 90a, 90b of the pusher 90 may have a rounded or cylindrical profile. As shown in Figures 5C and 5D, an arcuate contact surface provided within the coupling hole 27c of the pivot housing 27a may provide an engagement surface for the first end 90a of the pusher 90. Although the element 90 is shown as a pusher 90, one of ordinary skill in the art will appreciate that any connection or coupling configured to provide a pushing or pulling force (i.e., a tensile force) may be provided between the carrier 72 and the pivot housing 27a.

[0067] Figures 6A-6D show various states of the retractable oscillating assembly 10. Figure 6A generally shows the undriven phase, Figure 6B shows the transition phase from the undriven phase to the driven phase, Figure 6C shows the driven phase, and Figure 6D shows the transition phase from the driven phase to the undriven phase.

[0068] FIG 6A shows the escapement assembly 70 in a neutral position (i.e., non-driven phase) when the drive spring 60 is fully wound. As shown in FIG 6A, the pawl tooth 76a engages with the tooth 74a of the escapement gear 74 to prevent the escapement gear 74 from rotating clockwise (due to the wound drive spring 60) and to prevent the drive spring 60 from inadvertently fully unwinding. The dog engagement surface 78b of the actuator 78 and the dog control arm 80b are separated from each other in this state. FIG 6A shows the non-driven state, which is normally configured such that the dog 80 is fully disengaged and the pawl 76 is engaged, causing rotation to cause the actuator 72 to rotate counterclockwise.

[0069] FIG. 6B shows the swing arm assembly 12 and the carrier 72 pivoting counterclockwise due to the swing arm assembly 12 being initially pushed by the user. This motion is opposite to the spring force of the drive spring 60 that normally causes the swing arm assembly 12 to pivot in a clockwise direction. As shown in FIG. 6B, the inertia of the initial push causes the swing arm assembly 12 to move in a counterclockwise direction to drive the pusher 90, which starts to rotate in a counterclockwise direction relative to the carrier 72. This motion of the carrier 72 also causes the dog 80 to pivot counterclockwise. The counterclockwise motion of the dog 80 causes the dog control arm 80b to engage the dog engagement surface 78b of the actuator 78. This engagement causes the dog 80 to pivot about the dog pivot 80c, and the dog teeth 80a to engage the teeth 74a of the escapement gear 74. As the inertia due to the swing arm assembly 12 is applied to the dog tooth 80a, the torque from the drive spring 60 is now between the seat frame (i.e., the upright frame member 35c) at one end and the dog 80 at the other end. As the dog 80 is coupled to the carrier 72, any motion imparted to the carrier 72 by the swing arm assembly 12 drives the dog 80. The engaged dog 80 rotates the escapement gear 74 counterclockwise, relieving the force on the pawl 76.

[0070] The pawl 76, biased by gravity due to the pawl weight 76e, rotates clockwise and disengages from the escapement gear 74. During this phase, the torque force applied to the pawl 76 from the escapement gear 74 is released, causing the pawl 76 to momentarily disengage from the escapement gear 74. The dog 80, engaged with the escapement gear 74, transmits the spring torque from the escapement gear 74 to the carrier 72, thereby providing energy to cause the oscillating arm assembly to swing counterclockwise.

[0071] FIG. 6C shows the power stroke phase, which causes the swing arm assembly 12 to rotate clockwise. During this phase, the drive spring 60 applies a force that rotates the escapement gear 74 in a clockwise direction. In this phase, the pawl 76 disengages from the escapement gear 74 and the dog 80 engages with the escapement gear 74. The escapement gear 74 rotates the dog 80 clockwise, which in turn drives the carrier 72 clockwise. The carrier 72, which is fixed to the pusher 90, provides a driving motion to the swing arm assembly 12 through the pusher 90, thereby promoting a pendulum motion. In this phase, the pawl 76 remains disengaged, which is necessary to allow the escapement gear 74 to rotate in a clockwise direction. As the dog 80 rotates, the dog 80 remains in contact with the actuator 78. The dog 80 is configured to control the timing of the clockwise rotation of the actuator 78 based on this contact. The actuator 78 is normally biased towards clockwise rotation by gravity (ie, by actuator weight 78 c ) and the dog 80 controls that rotation until the actuator 78 engages the pawl 76 .

[0072] 6D, when the oscillating assembly transitions from the driving phase to the non-driving phase, the actuator 78 engages the pawl 76 with the escapement gear 74 (i.e., through the engagement between the pawl engagement surface 78a and the pawl control arm 76b). During this phase, the carrier 72 continues to rotate clockwise to disengage the dog 80 from the actuator 78 (i.e., separate the dog engagement surface 78b from the dog control arm 80b) and rotate the dog 80 clockwise about the dog pivot 80c and separate it from the escapement gear 74. After the actuator 78 drops the pawl 76 onto the next tooth 74a of the escapement gear 74, the torque is transmitted to the pawl tooth 76a since it is engaged with the escapement gear 74. During this step, the dog 80 is disengaged from the escapement gear 74 due to gravity (i.e., due to the shape of the dog and its pivot position). Thus, no force is provided to the swing arm assembly 12 through the drive spring 60, even though the swing arm assembly 12 is still rotating in a clockwise direction. Immediately after the pawl tooth 76a engages the escapement gear 74, the pawl tooth 76a is not held down by the actuator 78. However, the pawl 76 controls the position of the actuator 78 to prevent 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, after which the swing arm assembly 12 begins to travel counterclockwise. This occurs after momentum has stopped from the power stroke to the swing arm assembly 12.

[0073] When the oscillating assembly transitions completely back to the non-driven phase, the carrier 72 and oscillating arm assembly 12 start to move counterclockwise, causing the dog 80 to engage the actuator 78, which in turn rotates the dog tooth 80a counterclockwise about the dog pivot 80c to engage the next tooth of the escapement gear 74. After this step, the power stroke is repeated.

[0074] 7A-7D, an amplitude control assembly 92 may be provided that generally controls the amplitude. The amplitude control assembly 92 may include a drop plate 85 configured to selectively limit the stroke of the dog 80 and a swing control lever 95 configured to selectively adjust the position of the drop plate 85. The swing control lever 95 may be configured to set an upper limit for the amplitude. If the actual amplitude begins to exceed the upper limit set by the swing control lever 95, the swing control assembly 92 prevents the escapement assembly 70 from releasing additional energy from the drive spring 60 to the swing arm assembly 12.

[0075] The drop plate 85 may include an engagement portion 85a configured to engage a portion of the dog 80 through a control edge 85d, a recess 85b adjacent the control edge 85d, and an appendage 85c configured to engage a portion of a swing amplitude control lever 95. A user may manually engage the swing amplitude control lever 95 to adjust the swing amplitude. The swing amplitude control lever 95 may include a first stop 95a and a second stop spaced apart from each other. Each stop 95a, 95b may be configured to engage the appendage 85c of the drop plate 85. The second stop 95b may be formed in a portion of the frame or housing, in one example.

[0076] The fall plate 85 is configured to rotate together with the carrier 72 through frictional engagement between the engagement portion 85a of the fall plate 85 and the dog control arm 80b. The rotation of the fall plate 85 is limited by a first stopper 95a and a second stopper 95b. If the actual swing range is within a predetermined upper limit set by the swing range control assembly 92, the dog 80 will maintain engagement with the engagement portion 85a of the fall plate 85, thereby preventing the fall plate 85 from falling. The fall plate 80 includes a slot 85e through which the escapement shaft 75 is configured to extend, thereby allowing the fall plate 85 to slip or fall. When the swing range control lever 95 is rotated upward or counterclockwise, the swing range becomes larger. The appendage 85c of the drop plate 85 is permitted to pivot a greater distance between the stops 95a, 95b so that as the swing arm assembly 12 swings higher, the dog control arm 80b remains in contact with the engagement portion 85a of the drop plate 85 longer. As long as the engagement portion 85a of the drop plate 85 is engaged with the dog control arm 80b, the drop plate 85 will not fall, as shown in Figures 7B and 7C.

[0077] 7D shows a state or phase when the actual swing exceeds a predetermined or set upper limit. As shown in FIG. 7D, the drop plate 85 drops so that the dog control arm 80b engages beyond the control edge 85d and is received in the recess 85b adjacent to the control edge 85d. The control edge 85d of the drop plate 85 engages the dog tooth 80a with the same tooth 74a of the escapement gear 74 that it was previously engaged with, rather than the next tooth 74a of the escapement gear 74. Thus, the control edge 85d engages the dog tooth 80a with the escapement gear 74 before the actuator 78 returns to engage the dog tooth 80a with the escapement gear 74. In addition, the control edge 85d of the drop plate 85 is angled so that the dog control arm 80b can push the drop plate 85 upwards when swinging counterclockwise.

[0078] If the swing arm assembly 12 swings beyond a predetermined swing upper limit, the drop plate 85 drops, causing the dog teeth 80a to engage with the escapement gear 74 and rise. This is repeated during one swing until the swing width falls below the predetermined upper limit. The drop plate 85 drops when the swing arm assembly 12 is moving clockwise (i.e., in the direction in which the drive spring 60 is releasing its energy), and the dog control arm 80b is received within the recess 85b of the drop plate 85.

[0079] The pawl 76a and dog tooth 80a are shown in various states with respect to the escapement gear 74, and more specifically, with respect to the first set of teeth 74a of the escapement gear 74. The pawl safety tooth 76d and the dog safety tooth 80d are shown. The second set of teeth 74b of the escapement gear 74 are configured to engage with the pawl safety tooth 76d and the dog safety tooth 80d. The pawl safety tooth 76d and the dog safety tooth 80d are normally configured to engage with respective teeth between the second set of teeth 74b of the escapement gear 74 to prevent the drive spring 60 from inadvertently unwinding as the drive spring 60 is wound. The dog safety tooth 80d may be configured to prevent the dog 80 from falling too far when it separates from the escapement gear 74 during oscillation.

[0080] 8A-8C show further features of the pawl safety tooth 76d. One skilled in the art will understand that the description provided herein regarding the function of the pawl safety tooth 76d may also be applied to the dog safety tooth 80d. For illustrative purposes, the portion of the pawl 76 that supports the pawl safety tooth 76d is not shown to show the engagement between the pawl safety tooth 76d and the second set of teeth 74b of the escapement gear 74. In normal operation, the pawl safety tooth 76d and the dog safety tooth 80d generally follow the pawl teeth 76a and the dog teeth 80a, respectively, as they advance inwardly and outwardly in a regular manner relative to the escapement gear 74. In case of a possible failure of one of the elements, such as damage to the dog tooth 80a, it is desired to re-engage the pawl 76, regardless of the actuator position or the escapement mechanism, to prevent high torque on the escapement gear 74 from the drive spring 60. If the dog tooth 80a becomes inoperative, there is a high risk that the dog 80 will not be able to prevent any relative movement of the escapement gear 74 and will not be able to release the uncontrollable torque from the drive spring 60 on the escapement gear 74. In this overview, the second set of teeth 74b is configured to contact the pawl safety tooth 76d at high speed when it starts to rotate at high speed (opposite the normal counterclockwise force caused by gravity). This forces the pawl tooth 76a down into the gap between the first set of teeth 74a, but is completely independent of any movement of the actuator 78 that normally controls the movement of the pawl 78. The pawl tooth 76a is driven with significant energy and momentum towards the escapement gear 74. The escapement gear 74 in this state rotates in a clockwise direction at high speed. The engagement of the pawl tooth 76a with the first set of teeth 74a stops the rotation of the gear. This same type of configuration may also occur if dog safety tooth 80d is to stop uncontrolled rotation of escapement gear 74 in the event of damage to pawl tooth 76a or other malfunction.

[0081] As an additional feature, the windable oscillating assembly 10 may be implemented with a torque limiting clutch configured to prevent a user from winding the drive spring 60 beyond a predetermined upper torque limit. The torque limiting clutch may be configured to slip when wound in the reverse or non-winding direction.

[0082] 9A-9C, a torque limiting clutch may be provided to prevent damage from excessive winding. The silent take-up spool 105 may be split into an upper portion 105a and a lower portion 105b to provide a torque limiting arrangement 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.

[0083] Prior to assembly to the silent take-up spool 105, the torque clutch spring 900 is configured such that its inner diameter is smaller than the outer diameter of the silent take-up spool 105. The torque clutch spring 900 is assembled to the upper and lower 105a, 105b portions of the silent take-up spool 105 by temporarily widening the inner diameter of the torque clutch spring 900. This is accomplished by applying a torque force to the torque clutch spring 900. Once assembled to the silent take-up spool 105, the torque force is removed and the torque spring 900 grips the upper and lower 105a, 105b portions of the silent take-up spool 105. This tightening of the torque clutch spring 900 on the silent take-up spool portion 105 transfers torque from the lower 105b to the upper 105a.

[0084] During winding, torque from the winding shaft 55 rotates the lower portion 105b. This torque is transferred to the upper portion 105a, and the rotation of the upper portion 105a winds the drive spring 60. The winding direction of the torque clutch spring 900 is configured such that the coils of the torque clutch spring 900 slip at a given or predetermined torque when a winding torque is transferred. However, when resisting the torque of a fully wound drive spring 60, the torque clutch spring 900 locks the upper portion 105a to the lower portion 105b of the silent take-up spool 105. The torque is then resisted by the connection of the slip clutch spring 100 to the lower portion 105b and the pin 102.

[0085] One skilled in the art will appreciate that various modifications may be made to the wind-up swing assembly. For example, as shown in FIGS. 10B, 10C, and 11, in one configuration, a gear assembly 300 may be incorporated to facilitate winding of the swing. The gear assembly 300 may comprise multiple gears. For example, a crank gear 302 may be coupled to the shaft 140 coupled to the crank assembly 40. The crank gear 302 may be directly engaged to a spring gear (scissor gear) 306 in one example. In one example, an idler or intermediate gear 304 may be disposed between the crank gear 302 and the spring gear 306. The spring gear 306 may be rotatably fixed to the wind-up shaft 55. The idler gear 304 may be provided to maintain the user's input / rotation and the rotation of the spring wind-up. The gear assembly 300 reduces the force required for the user to apply to the crank assembly 40 and allows the crank assembly 40 to be centered relative to the housing. One of ordinary skill in the art will appreciate that the crank assembly 40 need not be centrally located, but may be located in a variety of locations. The shaft 140 coupled to the crank assembly 40 may typically have a more centrally located pivot axis, while the pivot axis of the winding shaft 55 is offset from the pivot axis of the shaft 140. Although one specific gear configuration is shown, one of ordinary skill in the art will appreciate that various gear configurations may be used that would make winding easier and place the crank assembly 40 in a more desirable location on the housing for purposes of stability and weight distribution.

[0086] A torque limiting clutch assembly 400 may be provided, as shown in more detail in Figures 12A-12G. The torque limiting clutch assembly 400 may include a first housing 402 configured to support a portion of the crank assembly 40, such as the grip 42. The first housing 402 may be considered an upper housing or portion. The first housing 402 may include clutch actuation teeth 402a. A second housing 406 may be provided that functions as a cover or lower portion of the torque limiting clutch assembly 400. The second housing 406 may be omitted in the second embodiment.

[0087] A clutch hub 404 is provided that interacts or engages with the first housing 402, and more specifically, the clutch drive teeth 402a. The clutch hub 404 may be pivotally locked to the crank assembly 40. The clutch hub 404 may include at least one pawl 404a. The at least one pawl 404a may include, in one example, two pawls. The pawl 404a may include at least one pawl tooth 404b, which may be configured to selectively engage the clutch drive teeth 402a. The clutch hub 404 may further include a biasing element 404c configured to pivot or drive the pawl 404a such that the pawl tooth 404b engages the clutch drive teeth 402a. In one example, the biasing element 404c may include a spring. A pivot connection 404 d may be provided at one end of at least one pawl 404 a for attaching the pawl 404 a to the body of the clutch hub 404 .

[0088] Torque is applied to the first housing 402, which causes the clutch drive tooth 402a to engage with the pawl tooth 404b. The pawl 404a is configured to be driven in a clockwise direction through the connection between the clutch drive tooth 402a and the pawl tooth 404b. Torque is thereby transferred from the crank assembly 40 to the drive spring 60. The pawl 404a is normally biased radially outward through the biasing element 404c. At a given or predetermined torque, the force of the biasing element 404c is exceeded by the winding torque applied to the crank assembly 40. When this occurs, the pawl 404a rotates clockwise, which causes the pawl tooth 404b to disengage the clutch drive tooth 402a. Thus, no further torque is transferred from the crank assembly 40 to the drive spring 60. This prevents overwinding of the system, which may damage the crank assembly 40, the drive spring 60, and associated components.

[0089] As shown in Figures 12D and 12E, the arrow indicates the winding torque applied by the user. During this condition, the pawl tooth 404b and the clutch drive tooth 402a are engaged. As shown in Figure 12F, the pawl tooth 404b and the clutch drive tooth 402a disengage if the user applies too much torque to the crank assembly 40. In this condition, the torque limiting clutch assembly 400 disengages so that no torque is transferred from the crank assembly 40 to the drive spring 60. The torque limiting clutch 400 ensures that the torque or input applied to the winding oscillating assembly does not exceed a predetermined amount of torque. As shown in more detail in Figure 12G, the first housing 402 also defines a plurality of second teeth 404e that are configured such that a protruding portion of the pawl 404a rides over the second teeth 404e to emit an audible sound indicating that the clutch is disengaged due to excessive input torque being input to the system. The pawl tooth 404b is configured to catch the clutch drive tooth 402a as the first housing 402 and clutch hub 404 continue to rotate through a predetermined circumferential range, such as 180 degrees.

[0090] 12H and 12I show an alternative view of a torque limiting clutch 400' according to an aspect of the disclosure. The torque limiting clutch 400' may be implemented in the winding oscillating assembly 10 to prevent a user from winding the drive spring 60 beyond a predetermined torque limit. The torque limiting clutch 400' is disposed between an input shaft 402' and an output shaft 404'. The input shaft 402' is operably coupled to the crank assembly 40, and the output shaft 404' is operably coupled to the drive spring 60. The torque limiting clutch 404' may further 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 sealed together through the spring 410' and slip relative to each other when a frictional force is exceeded. Slip between cap 406' and spool 408' can prevent drive spring 60 from being overwound.

[0091] 12J-12M show alternative views of a torque limiting clutch assembly 420 according to an aspect of the disclosure. The torque limiting clutch assembly 420 shown in FIGS. 12K-12M operates similarly to the torque limiting clutch assembly 420 shown in FIGS. 12A-12G, but has fewer components, reducing the size and cost of the torque limiting clutch assembly 420 and reducing the possibility 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 422 may be considered the top and may support a portion of the crank assembly 40, such as the grip 42. The input hub 422 may include at least one catch 428 for engaging at least one protrusion 428 of the output hub 424. The at least one fastener 426 may be a resilient material, such as a spring finger 430 having an engagement portion 432, such as an engagement orifice or surface, and may be configured to engage with at least one protrusion 428 of the output hub 424.

[0092] The input hub 422 may be rotatably locked to the crank assembly 40. The output hub 424 may be disposed beneath the input hub 422. At least one fastener 426 of the input hub 422 may be biased to engage at least one protrusion 428 of the output hub 424. Torque applied to the input hub 422 causes the at least one fastener 426 to engage the at least one protrusion 428. Torque is thereby transferred from the crank assembly 40 to the drive spring 60. For a given or predetermined torque, the winding torque being applied to the crank assembly 40 overcomes the force of the fastener 426. When this occurs, the protrusion 428 may slip or separate from the fastener 426, preventing torque from being transferred from the crank assembly 40 to the drive spring 60. This prevents overwinding of the drive spring 60, which could potentially damage components of the crank assembly 40, the drive spring 60, and associated components.

[0093] 12J-12M show an input hub 422 having three fasteners 426 and an output hub 424 having three protrusions 428, one of ordinary skill in the art would understand that other variations in the number of fasteners 426 and protrusions 428 are available within the scope of the present disclosure. Additionally, one of ordinary skill in the art would recognize that the location of at least one fastener 426 and at least one protrusion 428 may be interchanged such that at least one protrusion 428 is located on the input hub 422 and at least one fastener 426 is located on the output hub 424.

[0094] 12N-12Q show alternative views of a torque limiting clutch assembly 440 according to an aspect of the disclosure. The torque limiting clutch assembly 440 may include an input hub 442 and an output hub 448. The output hub 424 may be pivotally locked to the shaft 140. The input hub 442 may include an upper portion 444 and a lower portion 446. The upper portion 444 may support a portion of the crank assembly 40, such as the grip 42. The output hub 448 may be disposed below the upper portion 444 of the lower portion 442. The output hub 448 may 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 may be disposed between the upper portion 444 and the lower portion 446 of the input hub 442.

[0095] The input hub 442 may include at least one fastener 454 including an engagement surface 455 for engaging at least one protrusion 456 of the output hub 448. The at least one fastener 454 may be pivotally attached to the input hub 442 or a resilient portion of the input hub 442, for example. A spring 458 may be attached to the at least one fastener 454 to bias the fastener 454 inwardly toward the output hub 448. In one example, the input hub 442 includes two fasteners 4543 and the output hub 444 includes two engagement protrusions 456, and the spring 458 biases the engagement surface 455 of each fastener 454 toward engagement with the protrusion 456.

[0096] The input hub 442 may be rotatably locked to the crank assembly 40. Torque applied to the input hub 442 causes the engagement surface 455 of the at least one fastener 454 to engage with the at least one protrusion 456. Torque is thereby transferred from the crank assembly 40 to the drive spring 60. For a given or predetermined torque, the winding torque being applied to the crank assembly 40 exceeds the biasing force of the fastener 454. When this occurs, the protrusion 456 slips or separates from the engagement surface 455 of the fastener 454, preventing torque from being transferred from the crank assembly 40 to the drive spring 60. This prevents overwinding of the drive spring 60, which could potentially damage components of the crank assembly 40, the drive spring 60, and associated components.

[0097] 12N-12Q show input hub 442 having two fasteners 454 and output hub 448 having two protrusions 456, one of ordinary skill in the art would understand that other variations in the number of fasteners 454 and protrusions 456 are available within the scope of the present disclosure. Additionally, one of ordinary skill in the art would recognize that the location of at least one fastener 454 and at least one protrusion 456 may be interchanged such that at least one protrusion 456 is located on input hub 442 and at least one fastener 454 is located on output hub 448.

[0098] As shown in FIG. 14, a swing arm hub 22 may be provided coupled to the swing arm 25 and also to the first and second ends 25A, 25B. An axis of reclining (AR) is defined based on the angle of the adjustment assembly 20, and an axis of seat rotation (ASR) is defined that typically extends perpendicular to the swing arm hub 22. In FIG. 14, a scatter plot shows the center of gravity (COG). The center of gravity (COG) is typically determined based on the weight distribution of the occupant or child in the swing as well as the frame itself. In general, the retractable swing assembly 10 provides an improved configuration that is easier to use, swings longer, more smoothly, and with a more predictable swing range than other known swing assemblies. The axis of reclining (AR) and the axis of seat rotation (ASR) intersect each other, and both typically extend through the center of gravity (COG). A schematic diagram of an occupant is shown in FIG. 14. One skilled in the art will appreciate that a compliant or seat assembly may be provided to support the occupant. The weight of the occupant is typically located in an area such as the seat frame 15, with the center of gravity (COG) intersecting both the recline axis (AR) and the seat rotation axis (ASR). One skilled in the art will appreciate that various design considerations such as the shape of the seat frame 15, the length / angle of the swing arm 25, the compliant material, etc. may be adjusted or varied. The configuration shown in FIG. 14 improves the stability of the retractable swing assembly 10 based on the location of the recline axis (AR) and the seat rotation axis (ASR) as well as the center of gravity.

[0099] 15A-15C show additional aspects or features of the swing arm 25 and its interface with the swing arm pivot 127. A swing arm connector 125 may be provided having a first end secured to the swing arm pivot 127 and configured to be attached or coupled to the swing arm 25. For example, the swing arm 25 may be received within the swing arm connector 125 and further secured via a rivet 125a and a snap pin 125b. The snap pin 125b may be provided on the swing arm 25 and configured to be received within an opening in the swing arm connector 125. The rivet 125a may extend through the opening in the swing arm connector 125 and into a slot 125c defined in the swing arm 25. This coupling arrangement reduces or limits any play or loose coupling between the swing arm 25 and the swing arm pivot 127, thereby providing improved swing times. Additionally, the connection allows the user to quickly and easily remove the swing arm 25 from the swing arm pivot 127 for disassembly. The snap pin 125b prevents the two components from coming apart, and the rivet / slot connection minimizes twisting and pivoting motion between the swing arm 25 and the swing arm pivot 127.

[0100] The wind-up swing assembly 10 disclosed herein provides a small footprint, typically with no overhead or vertical support, and requires only a very limited energy source to drive the swing arm assembly. The wind-up swing assembly 10 disclosed herein further provides an improved and efficient configuration for transmitting power between multiple axes (i.e., swing arm axis (X1), escapement axis (X2), and drive spring axis (X3)). This configuration provides a pendulum-like motion of the swing arm 25 through the use of bearings to overcome winding resistance and increase the running time of the wind-up swing assembly 10. The wind-up swing disclosed herein further has a longer running time, which can be approximately 20 seconds, or greater than 45 to 60 seconds, based on the user winding the drive spring of approximately 20 to 30 turns.

[0101] 16-27 show an alternative side view of a retractable rocking assembly 600 according to an aspect of the present disclosure. Portions of the alternative side view of the retractable rocking assembly 600 disclosed in FIGS. 16-27 are similar to the side view of the retractable rocking assembly 10 described above in FIGS. 1-15, and these portions function similarly as described above. The retractable rocking assembly 600 includes a seat frame 615 and a rocking arm 625 coupled to a rocking arm pivot 627. The retractable rocking assembly 600 further includes a frame assembly 635 and a crank assembly 640.

[0102] The swing arm 625 extends between the swing arm pivot 627 and the seat frame 615. The swing arm 625 forms approximately an L-shape. The shape and location of the swing arm 625 can alleviate safety concerns by minimizing the possibility of a child's hand, fingers, or leg becoming caught between the swing arm 625 and the seat frame 615. It will be appreciated that the swing arm 625 can include other shapes to account for the space between the swing arm 625 and the swing frame 615 due to safety concerns.

[0103] The connection configuration of the swing arm 625 and the frame assembly 635 allows easy access to the seat frame 615. For example, there is no structure directly above the seat frame 615 (see FIG. 16B). This configuration creates open access that allows a parent to load and unload a child from the swing assembly 600. It will be appreciated that an operable toy bar or other play toy can be included in the seat frame 615 without interfering with the open access to the seat frame 615.

[0104] The crank assembly 640 includes a crank arm 644, a ring 646, and a plate 647. The ring 646 extends around a periphery of the plate 648 and may be fixed to the oscillating frame 615. The crank arm 644 is coupled to the plate 648 such that rotation of the crank arm 644 causes the plate 648 to rotate. The crank arm 644 and the plate 648 may rotate about the same pivot axis. Rotation of the crank arm 644 may wind the drive spring 60. During operation (described in further detail below), the ring 646 may be gripped by a user to facilitate the winding motion as the crank arm 644 is wound.

[0105] The crank arm 644 may have a curved or rounded shape and may pivot downwardly towards the plate 648. In one aspect, the crank arm 644 may pivot downwardly towards a recess or opening defined by the plate 648. The downward pivot feature and shape of the crank arm 644 may minimize "catching" (e.g., from laces, clothing, or other material getting caught or entangled in the crank arm 644 area).

[0106] 18-26 show alternative views of a swing arm assembly and seat assembly 740 according to aspects of the present disclosure. The swing arm assembly 712 includes a swing arm 725 and a support hub 727. The swing arm 725 can extend between the swing arm 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 removably coupled to the support hub 727 (see FIGS. 19 and 20).

[0107] 12 to 21D, the support hub 727 can include a rotating hub 750 and a stationary hub 752. The stationary hub 752 can be fixedly coupled to the swing arm 725. The rotating hub 750 can be pivotally coupled to the stationary hub 752 such that the rotating hub 750 can rotate relative to the stationary hub 752 about a pivot axis A. The rotating hub 750 includes a pivot body 754 extending upwardly from a pivot base 753. The pivot body 754 is configured to receive the seat assembly 740 thereon. The pivot body 754 defines an annular recess 756 and at least one anti-rotation groove 758. The annular recess 756 can be disposed at the center of the rotating body 754. In one aspect, the annular recess 756 can be located on the pivot axis A. The pivot body 754 further includes at least one latch ledge 760. At least one latch ledge 760 can be disposed within the at least one anti-rotation groove 758. It will be appreciated that the at least one latch ledge 760 can be disposed at other locations on the rotating hub 750. In one aspect, the pivot body 754 includes four anti-rotation grooves 758 and four latch ledges 760 disposed within each anti-rotation groove 758. It will be appreciated that the pivot body 754 can include fewer or more anti-rotation grooves 758 and latch ledges 760.

[0108] 21C and 21D, the support hub 727 may further include a plunger 762 and a biasing element 764. The biasing element may be, for example, a resilient member such as a spring. The plunger 762 and the biasing element 764 may be at least partially disposed between the rotating hub 750 and the stationary hub 752. The rotating hub 750 may define at least one plunger recess or detent 766. The shape and configuration of the at least one plunger recess 766 corresponds to the at least one plunger 762 such that the plunger 762 may be received in 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 stationary hub 752. The temporary rotational lock may be overcome by applying a rotational force to the rotating hub 750 to cause the biasing element 764 to withdraw the plunger 762 from the at least one plunger recess 766. The rotation hub 750 may include four plunger recesses 766 spaced circumferentially about the rotation hub 750. It will be understood that the rotation hub 750 may include fewer or more than four plunger recesses 766. In one aspect, the plunger recesses 766 may be spaced equidistant from one another about the rotation hub 750.

[0109] 22, the seat assembly 740 further includes at least one support leg 768, a support base 770, and a coupling 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. As shown, the at least one support leg 768 includes two legs. It will be appreciated that the at least one support leg 768 may include fewer or more legs. The support base 770 may define, for example, a rocker, a flat surface, or other shape such that the seat assembly 740 attached to the support base 770 may be used independently of the swing arm assembly 712 and positioned for use on a surface (e.g., a floor, a countertop, etc.).

[0110] The coupling assembly 772 is coupleable to the support hub 727. With reference to Figures 23A and 23B, the coupling assembly 772 defines a coupling recess 776. The coupling recess 776 is sized to receive the support hub 727 therein for coupling the seat assembly 740 to the swing arm 725. In one aspect, the coupling recess 776 defines a shape that roughly corresponds to the shape of the outer surface of the pivot 754.

[0111] The seat assembly 740 further includes at least one actuator 774. The at least one actuator 774 can control a release connection between the coupling assembly 772 and the support hub 727, as described further below. The at least one actuator 774 can be coupled to at least one of the support legs 768, the support base 770, and the coupling assembly 772.

[0112] 24A and 24B show a coupling assembly 872 and a support hub 827 according to an alternative aspect of the disclosure. The coupling assembly 872 can include at least one coupling recess 874. The support hub 827 can include at least one coupling stud 829. When the coupling assembly 872 is disposed on the support hub 827, the at least one coupling stud 829 can be received within the at least one coupling recess 872. The coupling between the at least one coupling stud 829 and the at least one coupling recess 874 provides a rotational lock (e.g., torque lock) between the coupling assembly 872 and the support hub 827. By reducing the motion between the coupling assembly 872 and the support hub 827, less energy is dissipated during operation of the oscillating assembly 600. It can be appreciated that the at least one stud 829 and the at least one recess 874 can be disposed on either the coupling assembly 872 or the support hub 827. For example, the support hub 827 may include at least one recess 874 and the coupling assembly 872 may include a counterpart of at least one stud 829 .

[0113] 25-27 show a cross section of at least one actuator 774 and a portion of a coupling assembly 772. The coupling assembly 772 includes an actuator biasing element 777, a pivot member 778, and a hub latch 780. The coupling assembly 772 further defines a hub protrusion 782 and at least one anti-rotation rib 784 within the coupling recess 776. The at least one anti-rotation rib 784 is sized to be received within a corresponding at least one anti-rotation groove 758 of the rotation hub 750. The coupling of the at least one rib 784 within the at least one anti-rotation groove 758 substantially prevents rotation between the coupling assembly 772 and the rotation hub 750. It can be appreciated that the rotation hub 750 can include the coupling assembly 772 including at least one rib and at least one groove configured to receive the at least one rib. The hub protrusion 782 is sized to be received within a tubular recess 756 of the rotation hub 750.

[0114] The actuator biasing element 777 may be a resilient member, such as a spring, coupled between the at least one actuator 774 and a pivot member 778. The pivot member 778 may be a pivot shaft or a pivot latch, pivotally coupled to a body 772a of the coupling assembly 772 at a pivot coupling 779. The pivot member 778 may further be coupled between the biasing element 777 and a hub latch 780. A first end 778a of the pivot member 778 is coupled to the at least one actuator 774 and receives a biasing force of the biasing element 777. A second end 778b of the pivot member 778 is coupled to the hub latch 780 and biases the hub latch 780 to a locked position such that the hub latch 780 can engage the rotating hub 750. The hub latch 780 may be pivotally coupled to the body 772a of the coupling assembly 772. Actuation of the actuators 774 or movement of at least one actuator 774 to an actuated position transitions the hub latch 780 between the unlocked position ( FIG. 26 ) and the locked position ( FIG. 27 ). For example, with reference to FIG. 26 , when the actuator 774 is actuated (e.g., moved upward as shown in FIG. 26 ), the actuator 774 overcomes the biasing force of the biasing element 777, causing the pivot member 778 to pivot about the pivot coupling 779. The pivoting movement of the pivot member 778 transitions the hub latch 780 from the locked position to the unlocked position. When the at least one actuator 774 is released, the biasing element 777 urges the at least one actuator 774 downward, causing the pivot member 778 to rotate about the pivot coupling 778, transitioning the hub latch 780 to the locked position.

[0115] 27 , the hub latch 780 is in the locked position and the rotating hub 750 is positioned within the coupling recess 776. The hub latch 780 is in the locked position and engages the at least one latch ledge 760 of the rotating hub 750. The engagement between the at least one latch ledge 760 and the hub latch 780 locks the seat assembly 740 to the rotating hub 750. To remove the seat assembly 740, the at least one actuator 774 may be actuated to transition the hub latch 780 to the unlocked position. In the unlocked position, the seat assembly 740 may be removed from the rotating hub 750.

[0116] A method of using the winding oscillating assembly 10 is further disclosed. It will be appreciated that the method of using the winding oscillating assembly 10 may further be used to move the winding oscillating assembly 600. The method may include driving the crank assembly 40 by rotating the crank handle 44. The crank assembly 40 is operatively coupled to the winding mechanism 50 such that a rotational input from the crank assembly 40 is provided to the winding mechanism 50. Rotating the crank handle 44 winds a drive spring 60 coupled to the winding mechanism 50. The method includes selectively releasing energy from the drive spring 60 through an escapement assembly 70, which may include a carrier 72. The carrier 72 is further linked to the rocker arm pivot 27 through a pusher 90. Based on this arrangement, the rocker arm pivot 27 moves or is driven in a first direction during a power stroke due to the discrete release of energy from the drive spring 60 through the escapement assembly 70. The swing arm pivot 27 moves in a second direction, opposite to the first direction, during a non-power stroke. This motion 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 swinging in a front to back direction based on energy from the drive spring 60.

[0117] Further disclosed herein is a method of driving the seat frame 15 of the winding rocking assembly 10. It will be appreciated that the method of driving the seat frame 15 of the winding rocking assembly 10 may further be used to operate the winding rocking assembly 600. The method may include rotating a crank assembly 40 coupled to a drive spring 60 such that the drive spring 60 is wound. The drive spring 60 may have a non-vertically oriented drive spring axis (X3). The method may include transferring energy from the wound drive spring 60 to an escapement assembly 70, which may have an escapement axis (X2) at an angle to the drive spring axis (X3). The method may include selectively releasing energy from the escapement assembly 70 to a rocker arm pivot 27. The rocker arm pivot 27 may be coupled to the seat frame 15 and may have a rocker arm axis (X1) at an angle to the drive spring axis (X3) and the escapement axis (X2).

[0118] The reelable oscillating assembly 10 disclosed herein further provides increased run or oscillating times as compared to known non-powered or manual oscillating assemblies. For example, approximately one hour of run time may be provided by the reelable oscillating assembly disclosed herein. This run time is based on a user cranking the reelable assembly for approximately 20 seconds or approximately 20 to 30 turns.

[0119] The winding rocking assembly 10 disclosed herein provides improved access to the seat frame on which a child is supported, as well as a reduced footprint compared to known winding rocking assemblies 10. As shown, the drive spring 60 is located in a non-overhead position relative to the seat frame. This provides a variety of advantages including unobstructed access to the seat frame and the child, and provides a more desirable center of gravity by locating the drive spring 60 relatively closer to ground level compared to winding rocking assemblies that require the drive spring 60 to be located overhead relative to the seat frame. Based on this, the center of gravity is lower relative to the ground, which in turn requires a smaller support assembly for the frame.

[0120] The oscillating assemblies described above can be implemented in a variety of configurations and operated in a variety of ways, as listed below.

[0121] a frame assembly including a housing; A drive spring is disposed within the housing and has a drive spring axis (X3) oriented non-perpendicularly relative to the vertical plane; a swing arm assembly coupled to the frame assembly for receiving energy from the drive spring, the swing arm assembly including a swing arm and a swing arm pivot; The swing arm is a winding swing assembly that is rotatable about a swing arm axis (X1) that is oriented in a non-horizontal direction relative to a horizontal plane.

[0122] 2. The wind-up type oscillating assembly of configuration 1, wherein the drive spring axis (X3) is angled with respect to the oscillating arm axis (X1).

[0123] 2. The winding type oscillating assembly of claim 1, wherein the oscillating arm axis (X1) is at an angle of 30 degrees to 70 degrees with respect to the horizontal plane.

[0124] The winding type oscillating assembly of configuration 1, wherein the drive spring axis (X1) forms an angle of 5 degrees to 20 degrees with respect to the vertical plane.

[0125] 1. A winding oscillating assembly of Configuration 1, further comprising an escapement assembly coupled to the frame assembly, the escapement assembly having an escapement axis (X2) that is angled with respect to the oscillating arm axis (X1).

[0126] The winding type oscillating assembly of configuration 5, wherein the oscillating arm axis (X1), the escapement shaft (X2), and the drive spring shaft (X3) are each angled with respect to each other.

[0127] A winding oscillating assembly of configuration 5, wherein the escapement axis (X2) is substantially parallel to the horizontal plane.

[0128] 2. A retractable swing assembly of claim 1, wherein the swing arm assembly includes an adjustment assembly and a seat frame, the adjustment assembly being configured to adjust the reclining angle of the seat frame.

[0129] 9. A winding type oscillating assembly of claim 8, wherein the drive spring is disposed laterally relative to the seat frame.

[0130] the frame assembly having an upper end and a lower end; A base is disposed at a lower end of the frame assembly; The take-up swing assembly of Configuration 1, wherein an upright frame member extends from said base to an upper end of said frame assembly.

[0131] The frame assembly includes: a support disposed at the lower end of the frame assembly and configured to rest on a ground surface; a handle disposed adjacent an upper end of the frame assembly; The take-up oscillating assembly of configuration 10 further comprising:

[0132] The supports extend in opposite directions from the base.

[0133] A winding type oscillating assembly of configuration 1, wherein a crank assembly is provided on the frame assembly for winding the drive spring.

[0134] The crank assembly includes a crank handle configured to extend in a direction away from the frame assembly, and the crank handle is rotated about a crank pivot to wind up the drive spring.

[0135] A winding oscillating assembly of configuration 14, wherein the crank handle is configured to fold outwardly from the frame assembly in a use state and configured to fold within a pocket defined in the frame assembly in a storage state.

[0136] 14. The winding type oscillating assembly of claim 13, further comprising a winding mechanism disposed between the crank assembly and the drive spring for converting a crank input from the crank assembly to wind the drive spring.

[0137] the take-up mechanism includes a take-up shaft coupled at a first end to the crank assembly and coupled at a second end to a spool; 17. The windable oscillating assembly of claim 16, wherein the drive spring includes a first end coupled to a mounting plate disposed about the winding shaft and a second end coupled to the spool, wherein rotation of the winding shaft winds the drive spring through the spool.

[0138] 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 includes: a crank gear fixed to a shaft coupled to the crank assembly; 18. The winding type oscillating assembly of claim 17, further comprising: a spring gear engaged with the crank gear and fixed to the winding shaft.

[0139] The drive spring further includes a winding mechanism having a winding shaft arranged along the drive spring shaft (X3), 2. The take-up oscillating assembly of claim 1, wherein the take-up mechanism has a first end coupled to a crank assembly and a second end coupled to a spool.

[0140] 20. The wind-up oscillating assembly of claim 19, wherein the drive spring includes a first end coupled to a mounting plate disposed about the wind-up shaft and a second end coupled to the spool, the wind-up shaft winding the drive spring through the spool.

[0141] The winding mechanism includes: a first winding gear disposed around the winding shaft and attached to the mounting plate; A second winding gear mated and engaged with the first winding gear, 21. The windable oscillating assembly of claim 20, wherein release of stored energy from the drive spring drives the first winding gear to rotate, and the first winding gear drives the second winding gear to rotate.

[0142] an escapement assembly coupled to the frame assembly; the escapement assembly includes an escapement shaft coupled to the second winding gear for driving the escapement shaft in rotation; 22. The winding oscillating assembly of claim 21, wherein the escapement shaft is oriented along an escapement axis (X2).

[0143] 23. The winding oscillating assembly of claim 22, wherein the escapement shaft is oriented substantially parallel to the horizontal plane.

[0144] 23. The winding oscillating assembly of claim 22, further comprising an escapement gear fixed to the escapement shaft and configured to be driven through the second winding gear.

[0145] The escapement assembly includes: a carrier coupled to the escapement shaft and configured to rotate about the escapement axis (X2); a pusher having a first end coupled to the carrier and a second end coupled to the swing arm assembly; 25. The winding type oscillating assembly according to claim 24, wherein when the escapement gear is driven by releasing the stored energy of the drive spring through the connection between the escapement shaft and the second winding gear, the pusher rotates the oscillating arm assembly.

[0146] the pusher comprises a wire; the first end and the second end of the pusher include portions that are angled relative to a main body of the pusher; the first end of the pusher is configured to be held within an opening in the carrier, the opening including a through hole and having at least one tapered region adjacent to the through hole; The take-up oscillating assembly of claim 25, wherein the second end of the pusher is configured to be retained within an opening in a pivot housing of the oscillating arm assembly, the opening including a through hole and at least one tapered region adjacent to the through hole.

[0147] 26. The winding oscillating assembly of claim 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 being attached to the oscillating arm pivot and the second bevel gear being coupled to the carrier.

[0148] the escapement gear having a plurality of teeth; The escapement assembly includes: a pawl pivotally mounted to said frame assembly and including a pawl tooth selectively engageable with teeth of said escapement gear to prevent said escapement gear from rotating in said drive direction when said rocker arm is in a neutral condition; a dog pivotally mounted to said carrier and selectively engageable with teeth of said escapement gear when said rocker arm pivots to disengage a pawl tooth from said escapement gear; 26. The winding oscillating assembly of claim 25, further comprising:

[0149] the escapement assembly further comprises an actuator coupled to the escapement shaft and configured to rotate about the escapement axis (X2); 29. The windable oscillating assembly of claim 28, wherein the actuator selectively engages the pawl and the dog to control selective engagement of the escapement gear between the pawl and the dog.

[0150] 29. The take-up swing assembly of claim 28, further comprising a swing amplitude control assembly comprising a drop plate configured to selectively limit a stroke of the dog and a swing amplitude control lever configured to selectively adjust a position of the drop plate.

[0151] 31. The take-up swing assembly of claim 30, wherein the drop plate includes an engagement portion configured to engage a portion of the dog and an appendage configured to engage a portion of the swing control lever.

[0152] 32. The take-up swing assembly of claim 31, wherein the swing control lever includes a first stopper and a second stopper each spaced apart from the other and each configured to engage the appendage of the drop plate to control the swing amplitude.

[0153] 20. The windable oscillating assembly of claim 19, further comprising a torque limiting clutch configured to prevent overwinding of the drive spring.

[0154] The torque limiting clutch is The winding type oscillating assembly according to configuration 33, further comprising a torque clutch spring that is assembled to the spool, winds when the winding shaft rotates in the winding direction, and slips when the drive spring is wound beyond a predetermined torque.

[0155] The torque limiting clutch is a first housing operatively coupled to the crank assembly and including clutch drive teeth; a clutch hub fixed to the crank assembly; a clutch pawl pivotally coupled to the clutch hub through a biasing element and biased by the biasing element to selectively engage the clutch drive teeth; The clutch pawl is engages the clutch drive teeth to transmit torque from the crank assembly to the drive spring as the drive spring is wound through the crank assembly up to a predetermined torque limit; 34. The windable oscillating assembly of claim 33, wherein the clutch drive tooth is disengaged to prevent further torque from being transmitted from the crank assembly to the drive spring when the torque transmitted by the crank assembly to the drive spring exceeds a predetermined torque limit.

[0156] The torque limiting clutch is an input shaft coupled to the crank assembly; an output shaft coupled to the drive spring; A cap fixed to the input shaft; a clutch spool coupled to the output shaft and in intimate contact with the cap, 34. The windable oscillating assembly of claim 33, wherein the cap and the spool are configured to slip relative to one another to prevent overwinding of the drive spring when a predetermined force is exceeded.

[0157] The torque limiting clutch is a shaft coupled to the crank assembly; an input hub having at least one fastener; an output hub coupled to the shaft and including at least one protrusion engageable with the fastener; 34. The windable oscillating assembly of claim 33, wherein the at least one protrusion separates from the at least one fastener to prevent overwinding of the drive spring when a predetermined force from the crank assembly is exceeded.

[0158] 38. The winding rocking assembly of claim 37, wherein the at least one fastener is a resilient member that biases the at least one protrusion in a direction to engage the at least one protrusion.

[0159] 38. The take-up oscillating assembly of claim 37, wherein the at least one fastener is pivotally attached to the input hub.

[0160] 38. The winding rocking assembly of claim 37, further comprising a spring coupled to the at least one fastener and biasing the at least one fastener in a direction to engage the at least one protrusion.

[0161] 2. The take-up swing assembly of claim 1, wherein the swing arm is coupled to the swing arm pivot through a swing arm connector comprising a rivet and a snap pin.

[0162] The swing arm assembly includes a seat frame. 2. The retractable sway assembly of claim 1, wherein an occupant's center of gravity (COG) within the seat frame intersects with an recline axis (AR) and a seat pivot axis (ASR) of the seat frame.

[0163] The swing arm assembly includes a seat frame. The seat frame has a reclining axis (AR) and a seat rotation axis (ASR), which intersect with each other; 2. The retractable rocker assembly of claim 1, wherein both axes extend through a center of gravity (COG) of the retractable rocker assembly defined by the seat frame and an occupant.

[0164] A frame assembly; a swing arm assembly coupled to the frame assembly and including a swing arm pivot pivotally attached to the frame assembly, the swing arm having a first end coupled to the swing arm pivot and a second end coupled to a seat assembly; The swing arm is a swing assembly that is rotatable about a swing arm axis (X1) that is oriented in a non-horizontal direction relative to a horizontal plane.

[0165] 45. The swing assembly of claim 44, wherein the swing arm is L-shaped.

[0166] The swing arm is 45. The swing assembly of claim 44, further comprising a support hub disposed at the second end of the swing arm and configured to receive a seat assembly.

[0167] 47. The oscillating assembly of claim 46, wherein the seat assembly is removably coupled to the support hub.

[0168] 47. The swing assembly of claim 46, wherein the support hub is pivotable relative to the swing arm.

[0169] the seat assembly includes a coupling recess; 47. The oscillating assembly of claim 46, wherein the support hub includes a coupling stud received in the coupling recess to secure the seat assembly to the support hub.

[0170] The support hub includes: a stationary hub fixed to the swing arm; 47. The oscillating assembly of claim 46, further comprising a rotating hub pivotally coupled to the stationary hub and attached to the seat assembly for pivoting relative to the stationary hub.

[0171] A plunger; a biasing element attaching the plunger to the stationary hub; 51. The oscillating assembly of claim 50, further comprising a detent formed on the rotating hub for selectively receiving the plunger and inhibiting rotational movement between the rotating hub and the stationary hub.

[0172] The seat assembly includes: Seat frame and At least one support leg coupled to the seat frame; 51. The oscillating assembly of claim 50, further comprising: a coupling assembly including a coupling recess for receiving the rotation hub.

[0173] 53. The oscillating assembly of claim 52, wherein the rotation hub includes at least one rib, and the coupling recess defines at least one groove for receiving the at least one rib.

[0174] 53. The oscillating assembly of claim 52, wherein the seat assembly includes an actuator for releasing engagement between the seat assembly and the support hub.

[0175] The coupling assembly includes: The main body and a pivot member having a first end and a second end, pivotally coupled to the main body at a pivot joint disposed between the first end and the second end, the first end of the pivot member being attached to the actuator; an actuator biasing element exerting a biasing force on a first end of the pivot member to bias the actuator to a rest position; a hub latch connected to a second end of the pivot member and biased into a locked position with the rotating hub to secure the seat assembly to the rotating hub; 55. The oscillating assembly of claim 54, wherein movement of the actuator to an actuated position overcomes the biasing force of an actuator biasing element, causing the pivot member to pivot about the pivot coupling and moving the hub latch to an unlocked position and separated from the rotating hub.

[0176] 53. The swing assembly of claim 52, further comprising a support base for independent use of the seat assembly from the swing arm assembly when the seat assembly is detached from the swing arm assembly.

[0177] A frame assembly; a drive spring disposed within the frame assembly and oriented non-perpendicular to the vertical plane; a crank assembly provided on the frame assembly and configured to input a drive torque to the drive spring; a seat frame including a swing arm pivotally coupled to the frame assembly and oriented in a non-horizontal direction relative to a horizontal plane; a gear assembly coupled to the crank assembly and the drive spring for converting energy from the drive spring to impart an oscillating motion to the seat frame; A winding rocking assembly comprising:

[0178] 1. A method of driving a seat frame of a retractable swing assembly, comprising: driving a crank assembly coupled to a winding mechanism by rotating a crank handle; winding a drive spring coupled to the winding mechanism; and selectively releasing energy from the drive spring through an escapement assembly having a carrier linked to the swing arm pivot through 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.

[0179] 1. A method of driving a seat frame of a retractable swing assembly, comprising: rotating a crank assembly coupled to a drive spring disposed along a drive spring axis (X3) oriented non-perpendicularly relative to the vertical plane such that the drive spring is wound; transferring energy from the wound drive spring to an escapement assembly having an escapement axis (X2) at an angle to the drive spring axis (X3); selectively releasing energy from the escapement assembly to a swing arm pivot; The swing arm pivot is coupled to the seat frame and has a swing arm axis (X1), The swing arm axis (X1) is non-horizontal to a horizontal plane and forms an angle with the drive spring axis (X3) and the escapement shaft (X2).

[0180] Having thus described the present embodiment, it should be understood, and will be apparent, to those skilled in the art that many physical modifications, some of which have been illustrated in the detailed description of this disclosure, may be made without altering the concepts and principles of the invention embodied therein.

[0181] It should also be understood that many embodiments are possible that incorporate only portions of the preferred embodiment and, with respect to those portions, do not change the inventive concepts and principles embodied therein.

[0182] The present embodiments and any configurations are therefore considered in all respects to be illustrative and / or explanatory and not restrictive, the scope of the disclosure being indicated by the appended claims rather than the foregoing description, and all alternative embodiments and modifications to the present embodiments that come within the meaning and range of equivalency of the claims are accordingly embraced therein.

Claims

1. a frame assembly including a housing; A drive spring disposed within the housing and having a drive spring axis (X3) oriented non-perpendicularly relative to the vertical plane; a swing arm assembly coupled to the frame assembly for receiving energy from the drive spring, the swing arm assembly including a swing arm and a swing arm pivot; A winding type swing assembly, wherein the swing arm is rotatable about a swing arm axis (X1) oriented in a non-horizontal direction relative to a horizontal plane.

2. 2. The wind-up oscillating assembly according to claim 1, wherein the drive spring axis (X3) is angled with respect to the oscillating arm axis (X1).

3. 2. The take-up type swing assembly according to claim 1, wherein the swing arm axis (X1) forms an angle of 30 degrees to 70 degrees with respect to the horizontal plane.

4. 2. The wind-up oscillating assembly according to claim 1, wherein the drive spring axis (X1) forms an angle of 5 degrees to 20 degrees with respect to the vertical plane.

5. 2. The winding oscillating assembly of claim 1, further comprising an escapement assembly coupled to said frame assembly, said escapement assembly having an escapement axis (X2) that is angled with respect to said oscillating arm axis (X1).

6. 6. The wind-up oscillating assembly according to claim 5, wherein the oscillating arm axis (X1), the escapement axis (X2), and the driving spring axis (X3) are each angled with respect to each other.

7. 6. The winding oscillating assembly according to claim 5, wherein the escapement axis (X2) is substantially parallel to the horizontal plane.

8. The wraparound swing assembly of claim 1 , wherein the swing arm assembly includes an adjustment assembly and a seat frame, the adjustment assembly configured to adjust a lean angle of the seat frame.

9. The windable oscillating assembly of claim 8 , wherein the drive spring is disposed laterally relative to the seat frame.

10. the frame assembly having an upper end and a lower end; A base is disposed at a lower end of the frame assembly; 2. The reelable swing assembly of claim 1, wherein an upright frame member extends from said base to an upper end of said frame assembly.

11. The frame assembly includes: a support disposed at the lower end of the frame assembly and configured to rest on a ground surface; a handle disposed adjacent an upper end of the frame assembly; The winding oscillating assembly of claim 10 further comprising:

12. The reelable oscillating assembly of claim 11 , wherein the supports extend in opposite directions from the base.

13. 2. The wind-up oscillating assembly of claim 1, wherein a crank assembly is provided on said frame assembly for winding said drive spring.

14. 14. The wind-up oscillating assembly of claim 13, wherein the crank assembly includes a crank handle configured to extend away from the frame assembly, and wherein rotation of the crank handle about a crank pivot winds the drive spring.

15. 15. The take-up oscillating assembly of claim 14, wherein the crank handle is configured to fold outwardly from the frame assembly in a use state and to fold into a pocket defined in the frame assembly in a storage state.

16. 14. The windable oscillating assembly of claim 13, further comprising a winding mechanism disposed between the crank assembly and the drive spring for converting a crank input from the crank assembly to wind the drive spring.

17. the take-up mechanism includes a take-up shaft coupled at a first end to the crank assembly and coupled at a second end to a spool; 17. The windable oscillating assembly of claim 16, wherein the drive spring includes a first end coupled to a mounting plate disposed about the winding shaft and a second end coupled to the spool, wherein rotation of the winding shaft winds the drive spring through the spool.

18. 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 includes: a crank gear fixed to a shaft coupled to the crank assembly; 18. The take-up oscillating assembly of claim 17, further comprising: a spring gear engaged with said crank gear and secured to said take-up shaft.

19. The drive spring further includes a winding mechanism having a winding shaft arranged along the drive spring axis (X3), 2. The take-up oscillating assembly of claim 1, wherein the take-up mechanism has a first end coupled to a crank assembly and a second end coupled to a spool.

20. 20. The windable oscillating assembly of claim 19, wherein the drive spring includes a first end coupled to a mounting plate disposed about the winding shaft and a second end coupled to the spool, the winding shaft winding the drive spring through the spool.

21. The winding mechanism includes: a first winding gear disposed around the winding shaft and attached to the mounting plate; a second winding gear mated and engaged with the first winding gear, 21. The windable oscillating assembly of claim 20, wherein release of stored energy from the drive spring drives the first winding gear to rotate, and the first winding gear drives the second winding gear to rotate.

22. an escapement assembly coupled to the frame assembly; the escapement assembly includes an escapement shaft coupled to the second winding gear for driving the escapement shaft in rotation; 22. The winding oscillating assembly of claim 21, wherein the escapement shaft is oriented along an escapement axis (X2).

23. 23. The winding oscillating assembly of claim 22, wherein the escapement shaft is oriented substantially parallel to the horizontal plane.

24. 23. The windable oscillating assembly of claim 22, wherein the escapement assembly further comprises an escapement gear fixed to the escapement shaft and configured to be driven through the second winding gear.

25. The escapement assembly includes: a carrier coupled to the escapement shaft and configured to rotate about the escapement axis (X2); a pusher having a first end coupled to the carrier and a second end coupled to the swing arm assembly; 25. The windable oscillating assembly according to claim 24, wherein the pusher rotates the oscillating arm assembly when the escapement gear is driven by releasing stored energy of the drive spring through a connection between the escapement shaft and the second winding gear.

26. the pusher comprises a wire; the first end and the second end of the pusher include portions that are angled relative to a main body of the pusher; the first end of the pusher is configured to be held within an opening in the carrier, the opening including a through hole and having at least one tapered region adjacent to the through hole; 26. The take-up swing assembly of claim 25, wherein the second end of the pusher is configured to be retained within an opening in a pivot housing of the swing arm assembly, the opening including a through hole and at least one tapered region adjacent to the through hole.

27. 26. The take-up swing assembly of claim 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 being attached to the swing arm pivot and the second bevel gear being coupled to the carrier.

28. the escapement gear having a plurality of teeth; The escapement assembly includes: a pawl pivotally mounted to said frame assembly and including a pawl tooth selectively engageable with teeth of said escapement gear to prevent said escapement gear from rotating in said drive direction when said rocker arm is in a neutral condition; a dog pivotally mounted to said carrier and selectively engageable with teeth of said escapement gear when said rocker arm pivots to disengage a pawl tooth from said escapement gear; 26. The reelable oscillating assembly of claim 25, further comprising:

29. the escapement assembly further comprises an actuator coupled to the escapement shaft and configured to rotate about the escapement axis (X2); 29. The windable oscillating assembly of claim 28, wherein the actuator selectively engages the pawl and the dog to control selective engagement of the escapement gear between the pawl and the dog.

30. 30. The take-up swing assembly of claim 28, further comprising a swing amplitude control assembly comprising a drop plate configured to selectively limit a stroke of the dog and a swing amplitude control lever configured to selectively adjust a position of the drop plate.

31. 31. The take-up swing assembly of claim 30, wherein the drop plate includes an engagement portion configured to engage a portion of the dog and an appendage configured to engage a portion of the swing control lever.

32. 32. The take-up swing assembly of claim 31, wherein the swing amplitude control lever includes a first stop and a second stop each spaced apart from the other and each configured to engage the appendage of the drop plate to control swing amplitude.

33. 20. The windable oscillating assembly of claim 19, further comprising a torque limiting clutch configured to prevent overwinding of the drive spring.

34. The torque limiting clutch is 34. The windable oscillating assembly of claim 33, further comprising a torque clutch spring assembled to the spool, winding when the winding shaft rotates in a winding direction and slipping when the drive spring is wound beyond a predetermined torque.

35. The torque limiting clutch is a first housing operatively coupled to the crank assembly and including clutch drive teeth; a clutch hub fixed to the crank assembly; a clutch pawl pivotally coupled to the clutch hub through a biasing element and biased by the biasing element to selectively engage the clutch drive teeth; The clutch pawl is engages the clutch drive teeth to transmit torque from the crank assembly to the drive spring as the drive spring is wound through the crank assembly up to a predetermined torque limit; 34. The windable oscillating assembly of claim 33, wherein the clutch drive tooth is disengaged to prevent further torque from being transmitted from the crank assembly to the drive spring when the torque transmitted by the crank assembly to the drive spring exceeds a predetermined torque limit.

36. The torque limiting clutch is an input shaft coupled to the crank assembly; an output shaft coupled to the drive spring; A cap fixed to the input shaft; a clutch spool coupled to the output shaft and in intimate contact with the cap, 34. The windable oscillating assembly of claim 33, wherein the cap and the spool are configured to slip relative to one another to prevent overwinding of the drive spring when a predetermined force is exceeded.

37. The torque limiting clutch is a shaft coupled to the crank assembly; an input hub having at least one fastener; an output hub coupled to the shaft and including at least one protrusion engageable with the fastener.

34. The windable oscillating assembly of claim 33, wherein the at least one protrusion separates from the at least one fastener to prevent overwinding of the drive spring when a predetermined force from the crank assembly is exceeded.

38. 38. The reelable oscillating assembly of claim 37, wherein the at least one catch is a resilient member biased toward engaging the at least one protrusion.

39. 38. The take-up oscillating assembly of claim 37, wherein the at least one fastener is pivotally attached to the input hub.

40. 38. The winding rocker assembly of claim 37, further comprising a spring coupled to the at least one catch and biasing the at least one catch in a direction to engage the at least one protrusion.

41. 2. The take-up swing assembly of claim 1, wherein the swing arm is coupled to the swing arm pivot through a swing arm connector comprising a rivet and a snap pin.

42. The swing arm assembly includes a seat frame.

2. The reel-type sway assembly of claim 1, wherein an occupant's center of gravity (COG) within the seat frame intersects with an occupant rest axis (AR) and a seat rotation axis (ASR) of the seat frame.

43. The swing arm assembly includes a seat frame. The reclining axis (AR) of the seat frame and the seat rotation axis (ASR) of the seat frame intersect with each other, 2. The retractable rocker assembly of claim 1, wherein both axes extend through a center of gravity (COG) of the retractable rocker assembly defined by the seat frame and an occupant.

44. A frame assembly; a swing arm assembly coupled to the frame assembly and including a swing arm pivot pivotally attached to the frame assembly, the swing arm having a first end coupled to the swing arm pivot and a second end coupled to a seat assembly; A swing assembly, wherein the swing arm is rotatable about a swing arm axis (X1) that is oriented in a non-horizontal direction relative to a horizontal plane.

45. 45. The swing assembly of claim 44, wherein the swing arm is L-shaped.

46. The swing arm is 45. The swing assembly of claim 44, further comprising a support hub disposed at the second end of the swing arm and configured to receive a seat assembly.

47. 47. The swing assembly of claim 46, wherein the seat assembly is removably coupled to the support hub.

48. 47. The swing assembly of claim 46, wherein the support hub is pivotable relative to the swing arm.

49. the seat assembly includes a coupling recess; 47. The swing assembly of claim 46, wherein the support hub includes a coupling stud received in the coupling recess to secure the seat assembly to the support hub.

50. The support hub includes: a stationary hub fixed to the swing arm; 47. The oscillating assembly of claim 46, further comprising a rotating hub pivotally coupled to the stationary hub and attached to the seat assembly for pivoting relative to the stationary hub.

51. A plunger; a biasing element attaching the plunger to the stationary hub; 51. The oscillating assembly of claim 50, further comprising a detent formed on said rotating hub for restricting rotational movement between said rotating hub and said stationary hub and for selectively receiving said plunger.

52. The seat assembly includes: Seat frame and At least one support leg coupled to the seat frame; 51. The oscillating assembly of claim 50, further comprising a coupling assembly including a coupling recess for receiving the rotation hub.

53. 53. The oscillating assembly of claim 52, wherein said rotation hub includes at least one rib, and said coupling recess defines at least one groove for receiving said at least one rib.

54. 53. The oscillating assembly of claim 52, wherein the seat assembly includes an actuator for releasing the engagement between the seat assembly and the support hub.

55. The coupling assembly includes: The main body and a pivot member having a first end and a second end, pivotally coupled to the main body at a pivot joint disposed between the first end and the second end, the first end of the pivot member being attached to the actuator; an actuator biasing element exerting a biasing force on a first end of the pivot member to bias the actuator to a rest position; a hub latch connected to a second end of the pivot member and biased into a locked position with the rotation hub to secure the seat assembly to the rotation hub; 55. The oscillating assembly of claim 54, wherein movement of the actuator to an actuated position overcomes a biasing force of an actuator biasing element, causing the pivot member to pivot about the pivot joint and move the hub latch to an unlocked position and separate from the rotating hub.

56. 53. The swing assembly of claim 52, wherein the seat assembly further comprises a support base for independent use of the seat assembly from the swing arm assembly when the seat assembly is detached from the swing arm assembly.

57. A frame assembly; a drive spring disposed within the frame assembly and oriented non-perpendicular to the vertical plane; a crank assembly provided on the frame assembly and configured to input a drive torque to the drive spring; a seat frame including a swing arm pivotally coupled to the frame assembly and oriented in a non-horizontal direction relative to a horizontal plane; a gear assembly coupled to the crank assembly and the drive spring for converting energy from the drive spring to impart an oscillating motion to the seat frame; A winding rocking assembly comprising:

58. 1. A method of driving a seat frame of a retractable swing assembly, comprising: driving a crank assembly coupled to a winding mechanism by rotating a crank handle; winding a drive spring coupled to the winding mechanism; and selectively releasing energy from the drive spring through an escapement assembly having a carrier linked to the swing arm pivot through 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.

59. 1. A method of driving a seat frame of a retractable swing assembly, comprising: rotating a crank assembly coupled to a drive spring disposed along a drive spring axis (X3) oriented non-perpendicularly relative to the vertical plane such that the drive spring is wound; transferring energy from the wound drive spring to an escapement assembly having an escapement axis (X2) at an angle to the drive spring axis (X3); selectively releasing energy from the escapement assembly to a swing arm pivot; The swing arm pivot is coupled to the seat frame and has a swing arm axis (X1), The swing arm axis (X1) is non-horizontal relative to a horizontal plane and forms an angle with the drive spring axis (X3) and the escapement axis (X2).

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