TW202529669A - Wind up swing assembly and method of use - Google Patents

Abstract

The present disclosure is directed to a windup swing assembly. The windup swing assembly comprises a swing arm assembly, a drive spring, and an escapement assembly. Each of the axes of the swing arm assembly, the drive spring, and the escapement assembly can be angled relative to each other. The axis of the drive spring can be angled in a non-vertical direction relative to a vertical plane. The axis of the swing arm assembly can be angled in a non-horizontal direction relative to a horizontal plane or support surface.

Description

Spring-type pendulum assembly

The present disclosure generally relates to a child swing assembly, and more particularly, to a non-electric child swing assembly and method of using the same.

Children's swings are well known. Many known children's swings are powered by electricity or batteries. These types of swings can be considered electric swings because they have a dedicated motor unit or other drive mechanism to produce the cyclical or swinging motion and require an electrical power source. Due to environmental concerns, there is a growing commercial demand in many consumer sectors for more environmentally friendly products that do not require electrical power to operate, which typically requires the consumption of fossil fuels or batteries, which can be harmful to the environment.

Before the commercialization of electric swings, many known child swings relied on human power or were driven by a horizontally positioned drive spring. Typically, the drive spring has a horizontally extending central axis (i.e., the drive spring axis) and is positioned above the child swing.

While using a drive spring to power a swing assembly can meet the growing demand for more environmentally friendly options for children's swings, traditional drive spring-driven swings often have drawbacks that make them less than ideal. For example, traditional spring-driven swings have a relatively short operating time (e.g., 20 minutes) when fully wound. Furthermore, traditional spring-driven swings often require a large footprint or take up a large amount of space.

In addition to increasing the running time and reducing the footprint of a clockwork child's pendulum, it can be difficult to effectively transmit force between the various subcomponents of the pendulum assembly, such as the drive spring, escapement assembly, and pendulum arm assembly.

Because springs can store relatively little energy, minimizing energy losses due to friction is crucial. Therefore, a low-friction design is desirable, especially when transferring rotation between shafts. This is also beneficial for shafts that are not parallel to one another. Advantageously, energy transfer between the shafts of various components is achieved with minimal frictional losses, while maintaining a cost-effective and viable design.

It would therefore be desirable to provide a compact clockwork children's pendulum device that offers a relatively long operating time and effectively transmits force between the major components.

This disclosure relates to a clockwork children's swing that addresses the typical shortcomings of traditional clockwork swings. Unlike traditional clockwork swings, where the drive spring is oriented along a horizontal axis above the swing itself, the disclosed swing assembly features a drive spring with a central axis (i.e., the drive spring axis) oriented in a non-horizontal direction. In some examples, the drive spring axis can be angled a few degrees with respect to a vertical direction. In some examples, the drive spring axis can be at any angle from 45 to 90 degrees with respect to the ground support surface (i.e., perpendicular to the ground support surface). In other examples, the drive spring axis can extend in a vertical direction. The clockwork oscillating mechanism disclosed herein also has a longer operating time, which can exceed 45 minutes to 60 minutes based on the user winding the drive spring for about 20 seconds or about 20 to 30 turns.

This disclosure relates to a clockwork children's swing that addresses the typical shortcomings of traditional clockwork swings. Unlike traditional clockwork swings, where the drive spring is oriented along a horizontal axis above the swing itself, the disclosed swing assembly features a drive spring with a central axis (i.e., the drive spring axis) oriented in a non-horizontal direction. In some examples, the drive spring axis can be angled at several degrees relative to the vertical. In some examples, the drive spring axis can be at any angle from 45 to 90 degrees relative to the ground support surface (i.e., perpendicular to the ground support surface). In other examples, the drive spring axis can extend in a vertical direction. The clockwork oscillating mechanism disclosed herein also has a longer operating time, which can exceed 45 minutes to 60 minutes based on the user winding the drive spring for about 20 seconds or about 20 to 30 turns.

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

The tightening mechanism may further include: a first upper tightening gear arranged around the upper tightening shaft and attached to the attachment plate; and a second upper tightening gear engaged with the first upper tightening gear, and the stored energy released from the drive spring may rotationally drive the first upper tightening gear, which rotationally drives the second upper tightening gear. The escapement assembly may include an escapement shaft connected to a second upper tensioning gear that rotationally drives the escapement shaft, the escapement shaft being oriented along an escapement axis (X2), the escapement assembly including: a bracket coupled to the escapement shaft and configured to rotate about the escapement axis (X2), and a first end coupled to the bracket and coupled to the swing arm. The pusher at the second end of the assembly is connected, and when the escapement gear is driven by the stored energy released from the driving spring via the connection between the escapement shaft and the second upper tensioning gear, the pusher can drive the swing arm assembly to rotate, and the escapement gear fixed to the escapement shaft and configured to be driven via the second upper tensioning gear, the escapement gear including a plurality of teeth.

The escapement assembly may further include: a pawl pivotally attached to the frame assembly, the pawl including a pawl tooth that selectively engages with a tooth of the escapement gear to prevent the escapement gear from rotating in a driving direction when the swing arm is in a neutral state; a clamp pivotally attached to the carrier and selectively engages with a tooth of the escapement gear when the swing arm rotates and the pawl tooth disengages from the escapement gear; an amplitude control assembly; and an amplitude control lever. The amplitude control lever includes a first stop and a second stop spaced apart from each other, each stop configured to control the amplitude of the swing.

The amplitude control assembly may include a drop plate configured to selectively limit the travel of the clamp, and the amplitude control lever may be configured to selectively adjust the position of the drop plate, wherein the drop plate includes an engagement portion configured to engage with a portion of the clamp and an attachment configured to engage with a portion of the amplitude control lever. The amplitude control lever may include a closed position. The housing supporting the amplitude control assembly may include a downward stop for limiting further movement of the amplitude control lever, the downward stop corresponding to the closed position of the amplitude control lever. When the amplitude control lever is in the closed position, a gap may be provided between the attachment configured to engage with a portion of the amplitude control lever and the housing supporting the amplitude control assembly, allowing the drop plate to float.

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

The torque limiting clutch may be radially supported at its axis of rotation. An outer lower bearing circumference of the torque limiting clutch may be axially supported by the housing. A low friction spacer may be inserted between the housing and the lower bearing circumference of the torque limiting clutch. An outer upper supporting circumference of the torque limiting clutch may be axially supported by the crown. The tightening mechanism may have a first end connected to the crank assembly and a second end connected to the bobbin. The torque limiting clutch may include a torque clutch spring assembled on the bobbin, the torque clutch spring being configured to tighten when the tightening shaft rotates in a tightening direction and to slide when the drive spring is tightened beyond a predetermined torque. The tightening mechanism may include a tightening shaft positioned along the drive spring axis (X3), the tightening mechanism having a first end connected to the crank assembly and a second end connected to the spool.

The torque limiting clutch may include: a first housing operably connected to the crank assembly, the first housing including a clutch drive tooth; a clutch hub fixed to the crank assembly; and a clutch pawl pivotally connected to the clutch hub via a biasing element, the clutch pawl being biased by the biasing element to selectively engage the clutch drive tooth. The drive spring can be tightened via the crank assembly, the clutch pawl engages the clutch drive tooth until a predetermined torque limit to transfer torque from the crank assembly to the drive spring, and when the torque transferred from the crank assembly to the drive spring exceeds the predetermined torque limit, the clutch pawl disengages from the clutch drive tooth to prevent further torque from being transferred from the crank assembly to the drive spring.

The torque-limiting clutch may include an input shaft connected to the crank assembly, an output shaft connected to the drive spring, a cap secured to the input shaft, and a clutch spool secured to the output shaft and clamped to the cap. The cap and spool may be configured to slide relative to each other when a predetermined force is overcome to prevent the drive spring from being overtightened.

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

According to another embodiment, a spring-loaded swing assembly includes: a frame assembly having an upper end and a lower end; a base member located at the lower end of the frame assembly; and an upright frame member extending from the base member to the upper end of the frame assembly, the frame assembly including a housing, a drive spring axis (X3) positioned within the housing and oriented in a non-vertical direction relative to an orthogonal plane, and a swing arm assembly connected to the frame assembly to receive energy from the drive spring, the swing arm assembly including a swing arm and a swing arm pivot, the swing arm being rotatable about a swing arm axis (X1), the swing arm axis being oriented in a non-horizontal direction relative to a horizontal plane. The upright frame member is welded to the base member.

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

Additional embodiments are described below.

Certain terminology is used in the following description for convenience only and is not intended to be limiting. The words "front," "rear," "upper," and "lower" designate directions in the drawings with reference to the accompanying drawings. The words "inwardly" and "outwardly" refer to directions toward and away from the components as illustrated in the drawings. A reference to a list of items "at least one of a, b, or c" (where a, b, and c represent listed items) refers to any one or more of a, b, or c. This terminology includes the words specifically mentioned above, derivatives thereof, and words of similar import.

As shown in Figures 1A to 1C, a clockwork swing assembly 10 is generally disclosed herein. As shown in Figures 2, 4B, and 5E, clockwork swing assembly 10 includes a swing arm assembly 12, which includes a swing arm 25 and a swing arm pivot 27 having a swing arm axis (X1). As shown in Figure 4A, swing arm pivot 27 generally includes a pivot housing 27a and at least one bearing 27b. For example (but not limitation), at least one bearing 27b may include two bearings, a first bearing in an upper region of pivot housing 27a and a second bearing in a lower region of pivot housing 27a. The bottom of the pivot housing 27a may be supported by a portion of the frame assembly 35a (eg, upright frame member 35c), as will be described in greater detail herein.

As shown in Figures 5C-5D and described in greater detail herein, pivot housing 27a may include an opening 27c configured to receive a portion of pusher 90 (i.e., first end 90a of pusher 90). Pivot housing 27a is configured to support swing arm 25, and swing arm 25 pivots about swing arm pivot 27. Swing arm 25 may include a first end 25a configured to engage swing arm pivot 27 and a second end 25b configured to support seat frame 15. A housing 26 may be provided to enclose the interface between first end 25a of swing arm 25 and swing arm pivot 27.

The arm axis (X1) can be oriented in a non-horizontal direction or in an angled direction relative to the ground or a horizontal plane (P1) along the x-axis. In one aspect, the arm axis (X1) can be oriented in a non-vertical direction or in an angled direction relative to a vertical plane (P2). The angle (θ1) between the arm axis (X1) and the horizontal plane (P1) is shown in FIG4B . The arm axis (X1) can be at an angle of 30 to 70 degrees relative to the ground or the horizontal plane (P1). Preferably, the arm axis (X1) can be at an angle of 40 to 60 degrees relative to the ground or the horizontal plane (P1). More preferably, the arm axis (X1) can be at an angle of 45 to 55 degrees relative to the ground or the horizontal plane (P1). In another example, the swing arm axis (X1) can be angled 50 degrees relative to the ground or horizontal plane (P1). The relative orientation and angle of the swing arm axis (X1) are configured to maximize the potential energy of the clockwork spring assembly 10, thereby increasing its operating time. In addition, the swing arm axis (X1) is arranged to minimize the footprint of the clockwork spring assembly 10.

The clockwork pendulum assembly 10 also includes a drive spring 60 having a drive spring axis (X3). The drive spring axis (X3) can be oriented in a non-vertical orientation or at an angle relative to a vertical plane (P2) along the y-axis, and can be angled relative to the pendulum arm axis (X1). In one aspect, the drive spring axis (X3) can be oriented in a non-horizontal orientation or at an angle relative to the ground or a horizontal plane (P1) along the x-axis. Those skilled in the art will 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 FIG4B . The drive spring axis (X3) may be angled between 5 and 20 degrees relative to the vertical plane (P2). A person skilled in the art will appreciate that, depending on the arrangement of any associated bevel gears, in another configuration, the drive spring axis (X3) may be angled at greater than 20 degrees relative to the vertical plane (P2). Preferably, the drive spring axis (X3) may be angled between 5 and 15 degrees relative to the vertical plane (P2). More preferably, the drive spring axis (X3) may be angled between 5 and 10 degrees relative to the vertical plane (P2). In one example, the drive spring axis (X3) may be angled at 7 degrees relative to the vertical plane (P2). The orientation and angle of the drive spring axis (X3) may be selected to optimize the stability of clockwork pendulum assembly 10 while also ensuring that the center of gravity of clockwork pendulum assembly 10 is positioned relative to base assembly 35b to minimize the risk of any accidental tipping.

The clockwork swing assembly 10 also includes an escapement assembly 70 having an escapement axis (X2). The escapement axis (X2) can be angled relative to the swing arm axis (X1). The escapement axis (X2) can be substantially parallel to the ground or horizontal plane (P1). Alternatively, as will be understood by one of ordinary skill in the art, the escapement axis (X2) can be angled relative to the ground or horizontal plane (P1).

As shown in Figures 2, 4B, and 5E, the swing arm axis (X1), the escapement axis (X2), and the drive spring axis (X3) can be angled relative to one another. As shown in Figure 4B, the swing arm axis (X1), the escapement axis (X2), and the drive spring axis (X3) can be angled relative to one another. In one embodiment, the relative angles between any of the first, second, and/or third axes (X1, X2, X3) can be between 0 and 90 degrees. Those skilled in the art will appreciate that these angles can vary depending on the specific desired configuration of the clockwork spring assembly 10. Furthermore, in another embodiment, the first, second and/or third axes (X1, X2, X3) may be arranged at any relative angles and may be arranged in a plurality of different planes.

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

In contrast to an upper spring assembly that requires a vertical space to support the drive spring, the spring-loaded swing assembly 10 disclosed herein positions the drive spring 60 laterally adjacent to or to the side of the seat frame 15. Therefore, the drive spring 60 is not positioned above the seat frame 15.

The clockwork pendulum assembly 10 further includes a frame assembly 35a, a base assembly 35b, and an upright frame member 35c. The frame assembly 35a, including the upright frame member 35c and the base assembly 35b, may include an outer shell or housing that generally surrounds or encloses internal components (e.g., the drive spring 60).

Frame assembly 35a may include a support member 37 at a lower end and a handle 36 at an upper end. Support member 37 is configured to provide an additional stable surface for engagement with the ground. Support member 37 may be formed as a protrusion that is large enough to accommodate a user's foot at the upper side, allowing the user to step on support member 37 and stabilize clockwork pendulum assembly 10 while tightening drive spring 60 via crank assembly 40. Support member 37 may extend outward from the remainder of frame assembly 35a. For example, but not limitation, support member 37 may extend outward from frame assembly 35a by at least 3 inches. In an embodiment, but not limitation, support member 37 may be less than 1 inch in height. The support member 37 preferably extends from the frame assembly 35a in a direction opposite to the base assembly 35b.

The handle 36 can be configured as a lip, edge, or other type of recess formed on the frame assembly 35a. Those skilled in the art will appreciate that the handle 36 can also be formed on areas of the clockwork pendulum assembly 10 other than the frame assembly 35a. The handle 36 is sized or configured to accommodate a user's hand to provide additional support to the clockwork pendulum assembly 10 when tightening the drive spring 60. The handle 36 can also be used to lift or otherwise move the clockwork pendulum assembly 10. For example, but not limitation, the handle 36 can have a depth of at least 1 inch, preferably at least 2 inches. The handle 36 is configured to allow the user to more easily move the clockwork pendulum assembly 10 and to enhance the overall mobility of the clockwork pendulum assembly 10.

The base assembly 35b can be formed as two legs 39a, 39b extending from the upright frame member 35c, as shown in the top view of FIG1C . In one example, the base assembly 35b can include two curved or bowed legs 39a, 39b, each having a generally U-shaped or horseshoe-shaped profile. As shown in FIG1C , the profile of the base assembly 35b can generally at least partially overlap with or fit within the profile or outer shape of the seat frame 15 (as shown by the ends of the legs 39a, 39b). Those skilled in the art will appreciate that the profile of the base assembly 35b can vary.

The clockwork pendulum assembly 10 also includes a crank assembly 40, which provides an interface for a user to apply motion or energy to the drive spring 60. The crank assembly 40 may generally be disposed on the frame assembly 35a. The crank assembly 40 may be positioned on the upper surface of the frame assembly 35a. Those skilled in the art will appreciate that the crank assembly 40 may be disposed on other portions or areas of the frame assembly 35a, or on any other portion of the clockwork pendulum assembly 10.

As shown in Figures 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 input to drive spring 60. Crank handle 44 may be configured to fold outward from frame assembly 35a in a use configuration and to fold into pocket 47 defined on frame assembly 35a in a storage configuration. A handle 42 may be provided on crank handle 44 and configured to be engaged by a user when tightening drive spring 60.

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

As shown in Figures 3C to 3F, various configurations can be provided for crank assembly 40. As shown in Figure 3C, arm 144 of crank assembly 40 can be operated as a handle, rotating outward in the use or cranking position and can be eccentrically positioned relative to the center portion of the frame. As shown in Figure 3D, arm 244 of crank assembly 40 can be operated as a handle, which also rotates outward from the frame. Increasing the arm length can provide greater input to drive spring 60. As shown in Figure 3E, arm 344 of crank assembly 40 can be translated radially outward to operate as a handle. As shown in Figure 3F, arm 444 of crank assembly 40 can have a rotating portion 444a configured to be grasped by a user.

Figures 3G to 3I provide additional views of a crank assembly according to another example. In one configuration, a tower cap 540 is provided that is typically attached 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 (also referred to as a knob) may be configured to rotate to tighten the drive spring 60. The arm 544 may be configured to be biased by a spring or biasing element to a closed or non-use position, which may serve as a safety feature. The tower cap 540 may be snap-fitted onto the body of the frame assembly 35a. The tower cap 540 may include an inner wall 546 that corresponds to the wall of the first housing 402 of the torque-limiting clutch assembly 400 (shown in greater detail in FIGS. 12A-12G and described in greater detail herein). This creates a snug fit between the tower cap 540 and the first housing 402 with minimal rotational movement (e.g., twisting) therebetween. The inner wall 546 also helps align the tower cap 540 with the clutch assembly 400 during assembly. For safety purposes and a cleaner aesthetic, the tightening knob or arm 544 may be configured to pivot downward to align with the tower cap 540.

As shown in detail in Figures 4A and 4B, the clockwork pendulum assembly 10 further includes a winding mechanism 50 disposed between the crank assembly 40 and the drive spring 60. The winding mechanism 50 is generally configured to provide an interface between the crank assembly 40 and the drive spring 60, such that a cranking input (cranking input) from a user is converted into the winding of the drive spring 60. As shown in Figure 4B, the winding mechanism 50 may include a winding shaft 55 connected to the crank assembly 40 at a first end 55a of the winding shaft 55. 4D to 4E , the upper tensioning shaft 55 may extend inside the drive spring 60 and may be connected to a quiet wind spool 105 at a second end 55b of the upper tensioning shaft 55. Alternative arrangements for the upper tensioning shaft 55 may be provided.

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

As shown in Figures 4A to 4E, the drive spring 60 may include a first end 60a connected to the attachment plate 52 and a second end 60b connected to the silent upper tensioning shaft 105, so that the rotation of the upper tensioning shaft 55 tightens the drive spring 60 via the silent upper tensioning shaft 105.

As shown in Figures 4C and 4E, a power tube 66 is provided to center the drive spring 60 and prevent it from snaking or otherwise becoming tangled during the tightening process. A first bearing 64 may be provided to support both the tightening 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 tightening shaft 55.

The silent tensioning shaft 105 may define a connector 62 connected to the second end 60b of the drive spring 60. Turning the tensioning shaft 55 clockwise rotates the silent tensioning shaft 105, which tightens the drive spring 60 via the connector 62. A connector 108 may be provided that connects the tensioning shaft 55 to the silent tensioning shaft 105. The connector 108 may include a set screw, a knurled connection, or any other attachment structure that connects the tensioning shaft 55 to the silent tensioning shaft 105.

A sliding clutch spring 100 may also be provided, typically configured to prevent the tensioning shaft 55 from rotating in a non-tensioning direction. Rotating the tensioning shaft 55 in the tensioning direction (e.g., clockwise as shown) causes the sliding clutch spring 100 to expand and slide. Conversely, rotating the tensioning shaft 55 in the non-tensioning direction causes the sliding clutch spring 100 to contract around the silent tensioning cable 105. When the user stops tightening the tensioning shaft 55, the counterclockwise force on the silent tensioning cable 105 causes the sliding clutch spring 100 to contract. Whenever the drive spring 60 is in the tightened position, whether during tightening or when the oscillating mechanism is in operation, the sliding clutch spring 100 prevents energy from being released from the drive spring 60. Therefore, in the event of a mechanical failure of the escapement mechanism, the tightening crank (i.e., knob, spring, etc.) cannot rotate uncontrollably and release energy, providing a safety feature and preventing injury to the user. As shown in Figures 4C and 4E, a bracket 35d can be provided that is fixed to the upright frame member 35c. Thus, the rotational torque of the drive spring 60 is resisted by the attachment of the sliding clutch spring 100 to a pin 102, which is connected to the bracket 35d or upright frame member 35c. For illustration purposes only, Figure 4E shows the drive spring 60 pulled upward from the bottom of the frame. As shown in Figure 4F, one end 100' of the sliding clutch spring 100 can be fixed to a portion of the upright frame member 35c or bracket 35d.

The escapement assembly 70 is configured to control the release of energy from the drive spring 60 and to provide a discrete and controlled burst of energy to drive the seat frame 15. The escapement assembly 70 is also configured to prevent the drive spring 60 from accidentally releasing. The escapement assembly 70 may include an escapement gear 74 including a plurality of teeth 74a and configured to be driven via an escapement arbour 75 connected to the second upper tensioning gear 56. The escapement gear 74 may be fixed to the escapement arbour 75. U.S. Patent 6,283,870 discloses one such escapement assembly, which is incorporated herein by reference as if fully set forth herein.

5A-5B , the escapement assembly 70 is shown in greater detail, along with a drop plate 85 and an amplitude control lever 95. The escapement assembly 70 may also include a carriage 72, a pawl 76, an actuator 78, a dog 80, and a pusher 90, each of which will be described in greater detail herein.

Pawl 76 is pivotally supported at pawl pivot 76 c. In one aspect, pawl pivot 76 c can be pivotally attached to a portion of frame assembly 35 a (e.g., upright frame member 35 c). The force of drive spring 60 biases escapement gear 74 to rotate in the drive direction (e.g., clockwise). However, in an initial state, pawl tooth 76 a is engaged with tooth 74 a of escapement gear 74, preventing escapement gear 74 from rotating clockwise and simultaneously preventing drive spring 60 from releasing. The escape gear 74 is biased clockwise by the force of the drive spring 60, causing the escape gear 74 to exert a force on the pawl 76, which keeps the pawl gear 76a engaged with the escape gear 74. Without such engagement, the pawl counterweight 76e would cause the pawl 76 to rotate clockwise due to gravity, thereby rotating out of engagement with the escape gear 74.

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

The clamp 80 is pivotally secured to the bracket 72 at the clamp pivot 80 c so that when the bracket 72 rotates about the escapement axis ( X2 ) along with the swing arm assembly 12 , the clamp 80 moves with the bracket 72 . The shape of the clamp 80 and the configuration of the clamp teeth 80 a, 80 d are such that the clamp weight causes the clamp 80 to rotate clockwise about the clamp pivot 80 c to disengage the clamp teeth 80 a from the teeth 74 a of the escapement gear 74 .

Actuator 78 is coupled to the escapement shaft and configured to rotate about the escapement axis (X2). Actuator 78 is configured to selectively engage with the clamp 80 via a clamp engagement surface 78b that engages with a clamp control arm 80b. Actuator 78 is also configured to selectively engage with the pawl 76 via a pawl engagement surface 78a that engages with a pawl control arm 76b. This selective engagement controls the movement of the clamp 80 and pawl 76. Actuator 78 also includes an actuator counterweight 78c positioned such that actuator 78 is biased in a clockwise direction when not engaged by the pawl 76 or clamp 80.

Pusher 90 operably connects escapement assembly 70 to swing-arm assembly 12. Pusher 90 is generally configured to convert rotation of escapement assembly 70 about the escapement axis (X2) into swing or oscillation of swing arm 25 about the swing-arm axis (X1). In one example, pusher 90 can be a rigid wire. Those skilled in the art will appreciate that pusher 90 can include a pair of bevel gears or any other type of mechanical linkage. For example, in the embodiment shown in Figures 13A and 13B, swing-arm pivot 127 can include a first bevel gear 190a. A second bevel gear 190b can be configured to drivably engage with first bevel gear 190a. The second bevel gear 190b can be connected to the bracket 72 or another part of the frame assembly. In one configuration, the second bevel gear 190b can be formed integrally with the bracket 72. The drive connection between the bevel gears 190a, 190b transmits the rocking or oscillating motion to the swing arm 25 and otherwise provides the same functionality as the pusher 90 and its associated components. The configuration including the bevel gears can be configured to provide a 1:1 rotational motion ratio between the first bevel gear 190a and the second bevel gear 190b, thereby providing a more efficient oscillating configuration.

Pusher 90 includes a first end 90a coupled to bracket 72 and a second end 90b coupled to swing arm pivot 27. Pusher 90 can be configured to rotate and move with multiple degrees of freedom. First end 90a and second end 90b of pusher 90 can be retained within bracket 72 and swing arm pivot 27 with a predetermined amount of slack or tolerance, allowing for some predetermined amount of play when pusher 90 is driven back and forth for a swinging motion.

As shown in Figures 5C and 5D, the first end 90a and the second end 90b of the pusher 90 may include portions that are bent or angled relative to the 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 retained in the opening 72a of the bracket 72. The opening 72a in the bracket 72 may include a through hole and at least one tapered area adjacent to the through hole. The opening 27c in the pivot housing 27a may also include a through hole and at least one tapered area adjacent to the through hole. By not rigidly fixing the ends 90a, 90b relative to the bracket 72 and the pivot housing 27a, the pusher 90 is allowed to swing more freely, which increases the swinging time.

Figures 5E through 5H illustrate further aspects of the structure of pusher 90. Referring to Figure 5E , energy must be transferred from the escapement axis (X2) to the swing-arm pivot axis (X1). These axes can be arranged non-parallel to one another and, in one configuration, can be angled at 40 to 60 degrees relative to one another. Pusher 90 is positioned between bracket 72 and pivot housing 27a to provide improved bending strength for torque transmission. The connection of pusher 90 to both bracket 72 on the escapement axis (X2) and pivot housing 27a on the swing-arm pivot axis (X1) is configured to allow self-alignment of pusher 90 with the corresponding connection hole 72a on bracket 72 and connection hole 27c on pivot housing 27a. Those skilled in the art will appreciate that the connection of pusher 90 to pivot housing 27a is similar. The profiles of the ends 90a, 90b of pusher 90 can be circular or cylindrical. As shown in Figures 5C and 5D, the arcuate contact surface provided in the connection hole 27c of pivot housing 27a can provide an engagement surface for the first end 90a of pusher 90. Although element 90 is shown as a pusher 90, one of ordinary skill in the art will understand that any linkage or connection may be provided between bracket 72 and pivot housing 27a that is configured to apply a pushing or pulling force (ie, a tensioning force).

6A to 6D illustrate various states of the clockwork pendulum assembly 10. FIG6A generally illustrates the unpowered stage, FIG6B illustrates the transition from the unpowered stage to the powered stage, FIG6C illustrates the powered stage, and FIG6D illustrates the transition from the powered stage to the unpowered stage.

FIG6A shows the escapement assembly 70 in an intermediate position (i.e., a non-powered state) when the drive spring 60 is fully wound. As shown in FIG6A , the pawl tooth 76 a is engaged with the tooth 74 a of the escapement gear 74, preventing the escapement gear 74 from rotating clockwise (due to the energy from the wound drive spring 60) and also preventing the drive spring 60 from inadvertently releasing. In this state, the clamp engagement surface 78 b and the clamp control arm 80 b on the actuator 78 are disengaged from each other. FIG6A generally illustrates the non-powered state, in which the clamp 80 is fully disengaged, the pawl 76 is engaged, and rotation is configured to occur in a counterclockwise direction relative to the actuator 72.

FIG6B shows that as the swing arm assembly 12 is initially pushed by the user, the swing arm assembly 12 and bracket 72 rotate counterclockwise. This movement opposes the spring force from the drive spring 60, which normally drives the swing arm assembly 12 to rotate in a clockwise direction. As shown in FIG6B , the inertia from the initial push causes the swing arm assembly 12 to move counterclockwise, driving the pusher 90, which then drives the bracket 72 to begin rotating counterclockwise. This movement of the bracket 72 also drives the clamp 80 counterclockwise. The counterclockwise movement of the clamp 80 causes the clamp control arm 80b to engage the clamp engagement surface 78b of the actuator 78. This engagement causes clamp 80 to rotate about clamp pivot 80 c, and clamp gear 80 a is driven into engagement with tooth 74 a of escape gear 74. Inertia from swing arm assembly 12 is applied to clamp gear 80 a, causing the torque from drive spring 60 to now be present between the seat frame (i.e., upright frame member 35 c) on one end and clamp 80 on the other. Because clamp 80 is connected to bracket 72, any movement applied to bracket 72 from swing arm assembly 12 also drives clamp 80. The engaged clamp 80 then rotates escape gear 74 counterclockwise, releasing the force on pawl 76.

Due to the pawl counterweight 76e, the pawl 76 is biased by gravity and then rotates clockwise and disengages from the escapement gear 74. During this phase, the torque applied to the pawl 76 from the escapement gear 74 is released, and the pawl 76 temporarily disengages from the escapement gear 74. The clamp 80 (now engaged to the escapement gear 74) transmits the spring torque from the escapement gear 74 to the carriage 72, thereby providing energy to drive the pendulum assembly in a counterclockwise pendulum motion.

FIG6C illustrates the power stroke phase, in which swing-arm assembly 12 rotates clockwise. During this phase, drive spring 60 applies a force that drives escapement gear 74 in a clockwise direction. During this phase, pawl 76 disengages from escapement gear 74, and collar 80 engages with escapement gear 74. Escapement gear 74 is configured to drive collar 80 to rotate clockwise, which in turn drives carriage 72 clockwise. Bracket 72, secured to pusher 90, then applies this driving motion to swing-arm assembly 12 via pusher 90, thereby providing power for the swinging motion. During this phase, pawl 76 remains disengaged, which is necessary to allow escape gear 74 to rotate clockwise. As collar 80 rotates clockwise, it remains in contact with actuator 78. Based on this engagement, collar 80 is configured to control the timing of the clockwise rotation of actuator 78. Actuator 78 is normally biased to rotate clockwise due to gravity (i.e., due to actuator counterweight 78c), and collar 80 controls this rotation until actuator 78 engages pawl 76.

6D , when the oscillating assembly transitions from the powered stage to the unpowered stage, actuator 78 engages pawl 76 with escapement gear 74 (i.e., via engagement between pawl engagement surface 78 a and pawl control arm 76 b). During this stage, carrier 72 continues to rotate clockwise, releasing clamp 80 from engagement with actuator 78 (i.e., disengaging clamp control arm 80 b from clamp engagement surface 78 b). This allows clamp 80 to rotate clockwise about clamp pivot 80 c to disengage from escapement gear 74. After actuator 78 causes pawl 76 to drop into the next tooth 74a of escapement gear 74, torque is transferred to pawl tooth 76a as it engages escapement gear 74. During this step, due to gravity (i.e., due to the shape of the pawl and its pivoted position), the clamp 80 disengages from the escapement gear 74. Consequently, power is no longer provided to the swing-arm assembly 12 via the drive spring 60, even though the swing-arm assembly 12 is still rotating in the clockwise direction. Shortly after pawl tooth 76a engages the escapement gear 74, it is no longer held in place by actuator 78. However, the pawl 76 controls the position of the actuator 78 and prevents the actuator 78 from rotating further clockwise due to gravity. The swing arm assembly 12 continues to swing clockwise for the remaining power stroke, and then the swing arm assembly 12 begins to travel counterclockwise. This occurs after the momentum from the power stroke to the swing arm assembly 12 stops.

When the pendulum assembly transitions back to the fully unpowered stage, the carriage 72 and pendulum arm assembly 12 begin to travel counterclockwise, the clamp 80 engages the actuator 78, and the actuator 78 causes the clamp tooth 80a to rotate counterclockwise around the clamp pivot 80c and engage the next tooth of the escapement gear 74. After this step, the power stroke is repeated.

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

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

The drop plate 85 is configured to rotate with the bracket 72 through frictional engagement between the engagement portion 85a of the drop plate 85 and the clamp control arm 80b. Rotation of the drop plate 85 is limited by a first stop 95a and a second stop 95b. If the actual swing amplitude is within predetermined limits set by the amplitude control assembly 92, the clamp 80 remains engaged with the engagement portion 85a of the drop plate 85, thereby preventing the drop plate 85 from falling. The drop plate 85 includes a narrow slot 85e through which the escapement shaft 75 is configured to extend, allowing the drop plate 85 to move or fall. When the amplitude control lever 95 is rotated upward or counterclockwise, a greater swing amplitude is permitted. Allowing the attachment 85c of the drop plate 85 to rotate a greater distance between the stops 95a, 95b allows the clamp control arm 80b to maintain contact with the engagement portion 85a of the drop plate 85 for a longer period of time when the swing arm assembly 12 swings higher. As shown in Figures 7B and 7C, as long as the engagement portion 85a of the drop plate 85 is engaged with the clamp control arm 80b, the drop plate 85 will not drop.

FIG7D illustrates a situation or stage where the actual swing amplitude exceeds a predetermined or set limit. As shown in FIG7D , the drop plate 85 drops, causing the clamp control arm 80b to engage beyond the control edge 85d and be received within the recess 85b adjacent to the control edge 85d. The control edge 85d of the drop plate 85 drives the clamp gear 80a into engagement with the same tooth 74a on the escapement gear 74 with which it was previously engaged, rather than the next tooth 74a on the escapement gear 74. Thus, the control edge 85d drives the clamp gear 80a into engagement with the escapement gear 74 before the actuator 78 further drives the clamp gear 80a back into engagement with the escapement gear 74. Additionally, the control edge 85d of the drop plate 85 is angled, allowing the clamp control arm 80b to push the drop plate 85 upward when swung counterclockwise.

If the swing arm assembly 12 swings beyond a predetermined amplitude limit, the drop plate 85 drops downward, causing the clamp gear 80a to engage with the escapement gear 74 and then rise. This process repeats for each swing cycle until the amplitude drops below the predetermined limit. As the swing arm assembly 12 moves clockwise (i.e., in the direction in which the drive spring 60 releases its energy), the drop plate 85 drops downward, and the clamp control arm 80b is received in the recess 85b of the drop plate 85.

The pawl tooth 76a and the clip tooth 80a are shown in various positions relative to the escapement gear 74 (more specifically, relative to the first set of teeth 74a on the escapement gear 74). The pawl safety tooth 76d and the clip safety tooth 80d are also shown. The second set of teeth 74b on the escapement gear 74 is configured to engage with the pawl safety tooth 76d and the clip safety tooth 80d. The pawl safety tooth 76d and the clip safety tooth 80d are generally configured to engage with corresponding teeth in the second set of teeth 74b on the escapement gear 74 when the drive spring 60 is tightened, thereby preventing the drive spring 60 from being accidentally released. The clamp safety tooth 80d can be configured to prevent the clamp 80 from falling too far when the clamp 80 disengages from the escapement gear 74 during swinging.

8A-8C illustrate additional features of pawl safety tooth 76d. Those skilled in the art will appreciate that the description provided herein regarding the function of pawl safety tooth 76d also applies to clamp safety tooth 80d. For illustrative purposes, a portion of pawl 76 supporting pawl safety tooth 76d is not shown to illustrate the engagement between pawl safety tooth 76d and second set of teeth 74b on escapement gear 74. During normal operation, pawl safety tooth 76d and clamp safety tooth 80d typically follow the corresponding pawl tooth 76a and clamp tooth 80a as pawl tooth 76a and clamp tooth 80a are regularly driven inward and outward relative to escapement gear 74. In the event of a potential failure of one of the components (e.g., a breakage of the collar tooth 80a), it is desirable for the pawl 76 to reengage to prevent the high torque from the drive spring 60 from occurring in the escapement gear 74, regardless of the actuator position and the escapement mechanism. If the collar tooth 80a is inoperable, the collar 80 cannot prevent any relative movement of the escapement gear 74, and there is a risk that a high, uncontrolled torque from the drive spring 60 will be released on the escapement gear 74. In this situation, the second set of teeth 74b, which is beginning to rotate at high speed, is configured to contact the pawl safety tooth 76d at high speed (rather than the generally counterclockwise force generated by gravity). This forcibly pulls pawl tooth 76a downward into the gap between the first set of gears 74a, completely independent of any movement of actuator 78, which normally controls the movement of pawl 76. Pawl tooth 76a is then driven toward escapement gear 74 with considerable energy and momentum. In this state, escapement gear 74 rotates at a high speed in a clockwise direction. The engagement of pawl tooth 76a with the first set of gears 74a stops gear rotation. This same type of configuration would occur if pawl tooth 76a were damaged or otherwise failed, and the clamp tooth safety gear 80d had to stop the uncontrolled rotation of escapement gear 74.

Another example of an amplitude control assembly is shown in Figures 30 to 33.

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

9A to 9C , a torque-limiting clutch can be provided to prevent damage from over-tightening. The silent tightening spool 105 can be divided into an upper portion 105a and a lower portion 105b to provide a torque-limiting configuration for the drive spring 60. During tightening, torque is transferred from the lower portion 105b to the upper portion 105a via the torque clutch spring 900.

The torque clutch spring 900 is configured so that, before being assembled onto the silent upper tension shaft 105, its inner diameter is smaller than the outer diameter of the silent upper tension shaft 105. The torque clutch spring 900 is assembled onto the upper portion 105a and the lower portion 105b of the silent upper tension shaft 105 by temporarily expanding the inner diameter of the torque clutch spring 900. This is achieved by applying a torque force to the torque clutch spring 900. Once assembled onto the silent upper tension shaft 105, the torque force is removed and the torque spring 900 clamps the upper portion 105a and the lower portion 105b of the silent upper tension shaft 105. This tightening of the torque clutch spring 900 on the silent bobbin portion 105 allows torque to be transferred from the lower portion 105b to the upper portion 105a.

During tightening, torque from the tightening shaft 55 causes the lower portion 105b to rotate. This torque is then transmitted to the upper portion 105a, and the rotation of the upper portion 105a tightens the drive spring 60. The winding direction of the torque clutch spring 900 is such that when the tightening torque is transmitted, the coil of the torque clutch spring 900 is configured to slide at a given or predetermined torque. However, when the torque of the fully tightened drive spring 60 is resisted, the torque clutch spring 900 locks the upper portion 105a of the silent tightening shaft 105 to the lower portion 105b. At the connection between the lower portion 105b and the pin 102, the torque is further resisted by the sliding clutch spring 100.

Those skilled in the art will appreciate that various modifications may be made to the clockwork pendulum assembly. For example, as shown in Figures 10B, 10C, and 11, in one configuration, a gear assembly 300 may be included to facilitate easier tightening of the pendulum. Gear assembly 300 may include a plurality of gears. For example, crank gear 302 may be coupled to shaft 140, which is coupled to crank assembly 40. In one example, crank gear 302 may be directly engaged with spring gear 306. In one example, an idler or intermediate gear 304 may be disposed between crank gear 302 and spring gear 306. Spring gear 306 may be rotationally fixed to tightening shaft 55. An idler gear 304 may be provided to maintain both user input/rotation and spring-loaded rotation. Gear assembly 300 reduces the force required by the user to apply to crank assembly 40 and also allows crank assembly 40 to be centered relative to the housing. Those skilled in the art will appreciate that crank assembly 40 need not be centered and may be located in a variety of positions. Shaft 140, to which crank assembly 40 is connected, may generally have a more centrally located axis of rotation, while the axis of rotation of take-up shaft 55 may be offset from the axis of rotation of shaft 140. Although a particular gear configuration is shown, one of ordinary skill in the art will appreciate that various gear configurations may be used that make the oscillating mechanism easier to wind and also position the crank assembly 40 in a more ideal location on the housing for stability and weight distribution purposes. Another exemplary embodiment of a gear assembly is shown in Figures 28A to 29.

A torque-limiting clutch assembly 400 may also be provided, as shown in greater detail in Figures 12A through 12G. The torque-limiting clutch assembly 400 may include a first housing 402 configured to support a portion of the crank assembly 40 (e.g., the handle 42). The first housing 402 may be considered an upper housing or upper portion. The first housing 402 may include a clutch drive gear 402a. A second housing 406 may be provided, which may serve as a cover or lower portion of the torque-limiting clutch assembly 400. In some embodiments, the second housing 406 may be omitted.

A clutch hub 404 is also provided and is configured to interact or engage with the first housing 402, more specifically, with the clutch drive gear 402a. The clutch hub 404 can be rotationally locked with the crank assembly 40. The clutch hub 404 can include at least one pawl 404a. In one example, the at least one pawl 404a can include two pawls. The pawl 404a can include at least one pawl tooth 404b, which can be configured to selectively engage with the clutch drive gear 402a. The clutch hub 404 may also include a biasing element 404c configured to pivot or drive the pawls 404a outward, causing the pawl teeth 404b to engage the clutch drive teeth 402a. In one example, the biasing element 404c may include a spring. A pivoting connection 404d may be provided at one end of at least one pawl 404a to attach the pawl 404a to the body of the clutch hub 404.

Torque is applied to the first housing 402, causing the clutch drive tooth 402a to engage the pawl tooth 404b. The pawl 404a is configured to be driven clockwise by the contact between the clutch drive tooth 402a and the pawl tooth 404b. Torque is thereby transmitted from the crank assembly 40 to the drive spring 60. The pawl 404a is normally biased radially outward by the biasing element 404c. At a given or predetermined torque, the force of the biasing element 404c is overcome by the tightening torque applied to the crank assembly 40. When this happens, pawl 404a rotates clockwise, disengaging pawl tooth 404b from clutch drive tooth 402a. Consequently, no torque is transferred from crank assembly 40 to drive spring 60. This prevents over-tightening of the system, which could damage components of crank assembly 40, drive spring 60, and related components.

As shown in Figures 12D and 12E, arrows are shown representing the user-applied tightening torque. During this state, pawl tooth 404b and clutch drive tooth 402a are engaged. As shown in Figure 12F, if the user applies excessive torque to crank assembly 40, pawl tooth 404b and clutch drive tooth 402a disengage. In this case, since torque-limiting clutch assembly 400 is disengaged, torque is not transferred from crank assembly 40 to drive spring 60. Torque-limiting clutch assembly 400 is configured to ensure that the torque or input applied to the spring-type swing assembly does not exceed a predetermined torque amount. As shown in more detail in FIG12G , the first housing 402 further defines a plurality of auxiliary teeth 404e that are configured to allow the nose of the pawl 404a to pass over the auxiliary teeth 404e and produce an audible noise indicating that the clutch is disengaging due to excessive input torque to the system. The pawl teeth 404b are configured to engage the clutch drive teeth 402a when the first housing 402 and the clutch hub 404 continue to rotate a predetermined circumferential range (e.g., 180 degrees).

12H and 12I illustrate an alternative torque-limiting clutch 400′ according to one embodiment of the present disclosure. The torque-limiting clutch 400′ can be implemented with the clockwork swing assembly 10 to prevent the user from tightening the drive spring 60 beyond a predetermined torque limit. The torque-limiting clutch 400′ is positioned 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 400′ can also include a cap 406′, a bobbin 408′, and a spring 410′. Cap 406' is fixed to input shaft 402', and spool 408' is fixed to output shaft 404'. Cap 406' and spool 408' are clamped together by spring 410' and can slide relative to each other when friction is overcome. The sliding between cap 406' and spool 408' prevents drive spring 60 from being overtightened.

12J-12M illustrate an alternative torque-limiting clutch assembly 420 according to one aspect of the present disclosure. The torque-limiting clutch assembly 420 shown in FIG12K-12M operates similarly to the torque-limiting clutch assembly 400 shown in FIG12A-12G , but requires fewer components, which can reduce the size and cost of the torque-limiting clutch assembly 420 and also reduce the possibility of mechanical problems and improper assembly. The torque-limiting clutch assembly 420 can include an input hub 422 and an output hub 424. The output hub 424 can be rotationally locked to the shaft 140. The input hub 422 can be considered the upper portion and can support a portion of the crank assembly 40 (e.g., the handle 42). The input hub 422 may include at least one engagement member 426 for engaging with at least one protrusion 428 of the output hub 424. The at least one engagement member 426 may be, for example, a resilient material (e.g., a spring claw 430 having an engagement portion 432), such as an engagement hole or an engagement surface, configured to engage with the at least one protrusion 428 of the output hub 424.

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

12J to 12M illustrate an input hub 422 having three engaging members 426 and an output hub 424 having three protrusions 428; however, those skilled in the art will recognize that other variations in the number of engaging members 426 and protrusions 428 may be utilized within the scope of the present disclosure. Furthermore, those skilled in the art will recognize that the positions of at least one engaging member 426 and at least one protrusion 428 may be reversed, such that at least one protrusion 428 is located on the input hub 422 and at least one engaging member 426 is located on the output hub 424.

12N-12Q illustrate an alternative torque-limiting clutch assembly 440 according to one aspect of the present disclosure. Torque-limiting clutch assembly 440 can include an input hub 442 and an output hub 448. Output hub 424 can be rotationally locked to shaft 140. Input hub 442 can include an upper portion 444 and a lower portion 446. Upper portion 444 can support a portion of crank assembly 40 (e.g., handle 42). Output hub 448 can be positioned below upper portion 444 of input hub 442. Output hub 448 can include an upper portion 450 and a lower portion 452. In one example, upper portion 450 and lower portion 452 of output hub 448 can be positioned within upper portion 444 and lower portion 446 of input hub 442.

The input hub 442 can include at least one engaging member 454 having an engaging surface 455 for engaging with at least one protrusion 456 of the output hub 448. The at least one engaging member 454 can be pivotally attached to the input hub 442 or a resilient portion of the input hub 442, for example. A spring 458 can be attached to the at least one engaging member 454 to bias the engaging member 454 inwardly toward the output hub 448. In one example, the input hub 442 includes two engaging members 454, the output hub 444 includes two engaging protrusions 456, and the spring 458 biases the engaging surface 455 of each engaging member 454 toward engagement with the protrusion 456.

The input hub 442 can be rotationally locked with the crank assembly 40. Torque applied to the input hub 442 causes the engagement surface 455 of at least one engagement member 454 to engage with at least one protrusion 456. This causes torque to be transferred from the crank assembly 40 to the drive spring 60. At a given or predetermined torque, the biasing force of the engagement member 454 is overcome by the tightening torque applied to the crank assembly 40. When this occurs, the protrusion 456 slides or disengages from the engagement surface 455 of the engagement member 454, preventing torque from being transferred from the crank assembly 40 to the drive spring 60. This prevents over-tightening of the drive spring 60, which could damage components of the crank assembly 40, the drive spring 60, and related components.

12N-12Q illustrate an input hub 442 having two engaging members 454 and an output hub 448 having two protrusions 456; however, those skilled in the art will recognize that other variations in the number of engaging members 454 and protrusions 456 may be utilized within the scope of the present disclosure. Furthermore, those skilled in the art will recognize that the positions of at least one engaging member 454 and at least one protrusion 456 may be reversed, such that at least one protrusion 456 is located on the input hub 442 and at least one engaging member 454 is located on the output hub 448. Another exemplary embodiment of a torque clutch is illustrated in FIG28A-29.

As shown in FIG14 , a swing arm hub 22 can be provided that is connected to a swing arm 25 and a first end 25a and a second end 25b of the swing arm 25. A tilt axis (AR) is defined based on the angle of the adjustment assembly 20, and a seat rotation axis (ASR) is defined that extends generally perpendicular to the swing arm hub 22. A center of gravity (COG) scatter plot is also shown in FIG14 . The center of gravity (COG) is typically determined based on the weight distribution of the frame itself and the occupant or child in the swing arrangement. Overall, the clockwork swing assembly 10 provides an improved configuration that is easier to use, provides a longer duration of swing, and provides a smoother, more predictable swing than other known swing assemblies. The recline axis (AR) and the seat rotation axis (ASR) intersect each other and both extend generally through the center of gravity (COG). A schematic diagram of an occupant is shown in FIG14 . Those skilled in the art will appreciate that soft goods or seat components may be provided to support the occupant. The occupant's weight is typically located in an area of the seat frame 15 where the center of gravity (COG) intersects the recline axis (AR) and the seat rotation axis (ASR). Those 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 contour of the soft goods, etc., may be adjusted or modified. The configuration shown in FIG14 improves the stability of the clockwork pendulum assembly 10 based on the positioning of the tilt axis (AR) and the seat rotation axis (ASR) as well as the center of gravity.

Figures 15A-15C illustrate additional aspects or features of the swing arm 25 and its interface with the swing arm pivot 127. A swing arm connector 125 can be provided, having a first end secured to the swing arm pivot 127 and configured to attach or connect to the swing arm 25. For example, the swing arm 25 can be received within the swing arm connector 125 and further secured via a rivet 125a and a snap pin 125b. The snap pin 125b can be provided on the swing arm 25 and configured to be received within an opening in the swing arm connector 125. The rivet 125a can extend through an opening in the swing arm connector 125 and be located within a slot 125c defined in the swing arm 25. This connection arrangement reduces or limits any play or loose connection between the swing arm 25 and the swing arm pivot 127, thereby providing improved swing time. In addition, the connection allows a user to quickly and easily remove the swing arm 25 from the swing arm pivot 127 for disassembly. The detent 125b can prevent the two components from being removed from each other, and the rivet/slot connection minimizes twisting and rotational movement between the swing arm 25 and the swing arm pivot 127.

The clockwork pendulum assembly 10 disclosed herein generally provides a small footprint, i.e., lacks any overhead or vertical support, and requires very limited energy to drive the pendulum assembly. The clockwork pendulum assembly 10 disclosed herein also provides an improved and efficient configuration for transmitting force between multiple axes, i.e., the pendulum axis (X1), the escapement axis (X2), and the drive spring axis (X3). This configuration imparts a pendulum-like motion to the pendulum arm through the use of bearings, thereby overcoming wind resistance and increasing the running time of the clockwork pendulum assembly 10. The clockwork oscillating mechanism disclosed herein also has a longer operating time, which can exceed 45 minutes to 60 minutes based on the user winding the drive spring for about 20 seconds or about 20 to 30 turns.

Figures 16A through 27 illustrate an alternative embodiment of a clockwork swing assembly 600 according to the present disclosure. Portions of the alternative embodiment of clockwork swing assembly 600 disclosed in Figures 16A through 27 are similar to those of clockwork swing assembly 10 described in Figures 1A through 15C , and the functions of those portions are similar to those described above. Clockwork swing assembly 600 includes a swing arm assembly 612, which includes a seat frame 615 and a swing arm 625 connected to a swing arm pivot 627. Clockwork swing assembly 600 also includes a frame assembly 635 and a crank assembly 640.

The swing arm 625 extends between the swing arm pivot 627 and the seat frame 615. The swing arm 625 forms a substantially L-shape. The shape and position of the swing arm 625 can alleviate safety concerns by minimizing the possibility of a child's hands, fingers, legs, or head becoming trapped between the swing arm 625 and the seat frame 615. It should be understood that the swing arm 625 can include other shapes to affect the distance between the swing arm 625 and the seat frame 615 for safety reasons.

The configuration of the connection between the swing arm 625 and the frame assembly 635 allows for easy access to the seat on the seat frame 615. For example, there is no structure directly above the seat frame 615 (see FIG16B ). This configuration creates an open passageway that allows a caregiver to place a child in and out of the swing assembly 600. It should be understood that a removable toy bar or other removable or removable play toys can be included on the seat frame 615 without obstructing the open passageway to the seat on the seat frame 615.

Crank assembly 640 includes a crank arm 644, a ring 646, and a plate 648. Ring 646 extends around the periphery of plate 648 and can be secured to seat frame 615. Crank arm 644 is coupled to plate 648 such that rotation of crank arm 644 causes plate 648 to rotate. Crank arm 644 and plate 648 can rotate about the same axis of rotation. Rotation of crank arm 644 can tighten drive spring 60. During operation (as described further below), when a user tightens crank arm 644 to tighten drive spring 60, the user can grasp ring 646 to facilitate the tightening motion.

Crank arm 644 can have a curved or rounded shape and can be rotated downward toward plate 648. In one aspect, crank arm 644 can be rotated downward into a recess or opening defined by plate 648. The ability to rotate downward and the shape of crank arm 644 can minimize "snagging" (e.g., ropes, clothing, or other materials becoming caught or tangled in the area of crank arm 644).

FIG18 to FIG26 illustrate an alternative embodiment of a swing arm assembly and seat assembly 740 according to the present disclosure. Swing arm assembly 712 includes a swing arm 725 and a support hub 727. Swing arm 725 can extend between a swing arm pivot 627 and the support hub 727. Seat assembly 740 includes a seat frame 715, a seat portion 717, and a base assembly 719. Seat assembly 740 can be removably connected to support hub 727 (see FIG19 and FIG20).

21A to 21D , the support hub 727 may include a swivel hub 750 and a fixed hub 752. The fixed hub 752 may be fixedly connected to the swing arm 725. The swivel hub 750 may be rotatably connected to the fixed hub 752 such that the swivel hub 750 may rotate relative to the fixed hub 752 about a swivel axis A. The swivel hub 750 includes a swivel body 754 extending upward from a swivel base 753. The swivel body 754 is configured to accommodate the seat assembly 740 thereon. The swivel body 754 defines a circular recess 756 and at least one anti-rotation channel 758. The circular recess 756 may be located in the center of the swivel body 754. In one aspect, the center of the circular recess 756 can be located on the rotation axis A. The rotating body 754 also includes at least one latch 760. The at least one latch 760 can be located within the at least one anti-rotation channel 758. It should be understood that the at least one latch 760 can be located elsewhere on the rotating hub 750. In one aspect, the rotating body 754 includes four anti-rotation channels 758 and four latches 760 located within the corresponding anti-rotation channels 758. It should be understood that the rotating body 754 can include fewer or more anti-rotation channels 758 and latches 760.

21C and 21D , the support hub 727 may further include a plunger 762 and a biasing element 764. The biasing element may be a resilient member, such as a spring. The plunger 762 and the biasing element 764 may be at least partially positioned between the rotating hub 750 and the fixed 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 correspond to the shape and configuration of the plunger 762 such that the plunger 762 may be received by the at least one plunger recess 766. The connection between the plunger 762 and the at least one plunger recess 766 creates a temporary rotational lock between the rotating hub 750 and the fixed hub 752. The temporary rotational lock can be overcome by applying a rotational force to the rotating hub 750 to force the biasing element 764 to retract the plunger 762 from at least one plunger recess 766. The rotating hub 750 can include four plunger recesses 766 spaced circumferentially around the rotating hub 750. It should be understood that the rotating hub 750 can include fewer than or more than four plunger recesses 766. In one aspect, the plunger recesses 766 can be equally spaced from one another around the rotating hub 750.

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

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

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

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

25-27 illustrate cross-sections of at least one actuator 774 and a portion of a coupling assembly 772. Coupling assembly 772 includes an actuator biasing element 777, a pivot member 778, and a hub latch 780. Coupling assembly 772 further defines a hub protrusion 782 and at least one anti-rotation rib 784 within a coupling recess 776. The at least one anti-rotation rib 784 is sized to be received within the corresponding at least one anti-rotation channel 758 of the swivel hub 750. The coupling of the at least one rib 784 within the at least one anti-rotation channel 758 substantially prevents rotation between coupling assembly 772 and swivel hub 750. It should be understood that the rotating hub 750 can include at least one rib and the connecting assembly 772 can include at least one channel configured to receive the at least one rib. The hub protrusion 782 is sized to be received by the circular recess 756 of the rotating hub 750.

Actuator biasing element 777 can be, for example, a resilient member (e.g., a spring) and is connected between at least one actuator 774 and pivot member 778. Pivoting member 778 can be, for example, a pivot shaft or a pivot latch and is pivotally connected to body 772a of connecting assembly 772 at pivot connection 779. Pivoting member 778 is also connected between biasing element 777 and hub latch 780. A first end 778a of pivot member 778 is connected to at least one actuator 774 and is biased by biasing element 777. The 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, allowing the hub latch 780 to engage the swivel hub 750. The hub latch 780 may be pivotally coupled to the body 772a of the connection assembly 772. Actuation of the actuator 774 or movement of at least one actuator 774 to an actuated position causes the hub latch 780 to transition between an unlocked position ( FIG. 26 ) and a locked position ( FIG. 27 ). For example, referring to FIG26 , when the actuator 774 is actuated (e.g., moved upward in the view shown in FIG26 ), the actuator 774 overcomes the biasing force of the biasing element 777 and causes the pivot member 778 to pivot about the pivot connection 779. The pivoting movement of the pivot member 778 transitions the hub latch 780 from the locked position to the unlocked position. When at least one of the actuators 774 is released, the biasing element 777 pulls the at least one actuator 774 downward and causes the pivot member 778 to rotate about the pivot connection 779, which transitions the hub latch 780 to the locked position.

27 , the hub latch 780 is in the locked position, with the swivel hub 750 positioned within the coupling recess 776. The hub latch 780 is in the locked position and engages the at least one latch bracket 760 of the swivel hub 750. The engagement between the at least one latch bracket 760 and the hub latch 780 essentially locks the seat assembly 740 to the swivel hub 750. To remove the seat assembly 740, the at least one actuator 774 can be actuated to transition the hub latch 780 to the unlocked position. In the unlocked position, the seat assembly 740 can be removed from the swivel hub 750.

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

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

The spring-loaded oscillating assembly 10 disclosed herein also provides enhanced operating time or swing time compared to known non-electric or manually driven oscillating assemblies. For example, the spring-loaded oscillating assembly disclosed herein can provide a running time of approximately one hour. This running time is based on the user cranking the winder for approximately 20 seconds or approximately 20 to 30 revolutions.

Compared to known spring-loaded rocker assemblies, the disclosed spring-loaded rocker assembly 10 provides a reduced floor space while also offering improved accessibility to the seat frame for supporting a child. As shown, the drive spring 60 is positioned in a non-upper position relative to the seat frame. This offers several advantages, including unimpeded access to the seat frame and child, and also provides an ideal center of gravity by positioning the drive spring 60 relatively close to the ground, compared to spring-loaded rocker assemblies that require the drive spring 60 to be positioned above the seat frame. This positioning lowers the center of gravity to the ground, requiring a relatively smaller support assembly for the frame.

With general reference to Figures 28A through 34, additional exemplary embodiments of the present disclosure are shown. These embodiments provide various beneficial features, such as: (a) a mechanical design of the tightening gear, shaft, and tightening components that simplifies assembly and reduces cost; (b) radial support around the axis of rotation; (c) axial support at the outer circumference of the torque clutch; (d) an enhanced tightening experience/feel for the consumer—for example, reduced friction, increased stiffness, and improved support for the tightening rotator; (e) an amplitude-controlled shutoff feature; and (f) a welded steel frame design for reduced shipping size.

Referring to Figures 28A through 29 , another exemplary embodiment of a gear assembly and torque clutch, generally designated by the reference numeral 800, is illustrated in sequential assembled steps to illustrate the components. The operation of the torque-limiting clutch assembly 800 illustrated in Figures 28A through 29 is similar to the torque-limiting clutch assembly illustrated in Figures 12A through 12G and/or Figures 12K through 12M . Aspects of the assembly process are applicable to the various torque clutches disclosed herein. The gear assembly includes shafts 802 and 804 received in shaft bores 806 and 808 of a housing 810, to which gears 811 and 812 are coupled. Gear cap 814 is then mounted on housing 810 and secured thereto with fasteners, such as screws 816. A low-friction support washer 820 may be installed in gear cap 814. A torque clutch 824 is then mounted to gear cap 814 and rotationally coupled to shaft 802. Once torque clutch 824 is installed, tightening knob 828 is coupled to torque clutch 824. Crown trim piece 830 is then mounted on gear cap 814 and torque clutch 824, and tightening rotator 832 is coupled to torque clutch 824. It should be understood that the order in which the components are assembled may be different from the order described above, and some components may first be combined into subassemblies that are then assembled into a unit. In addition, the various components may be secured together in a variety of ways (e.g., by fasteners, friction fit, snap fit, adhesives, etc.).

In FIG28G , an exemplary application utilizes a pin to connect the tightening knob 828 to the torque clutch 824, although it can also be snapped onto a boss instead. In addition, the tightening knob 828 is shown flipped downward. For aesthetic and safety reasons, this design can be implemented, although other mounting methods are also contemplated. For this example design, it should be noted that the tightening knob 828 is directly connected to the torque clutch 824 and can be mounted around a straight or other axis, with or without fasteners.

In FIG28H , the crown ornament 830 is installed as a decorative piece and can have an aesthetically pleasing design. Because the ornament is rigidly attached to the gear cap 814, concentricity between the rotational tightening component and any aesthetically pleasing cover components is always ensured. This minimizes friction between the components due to flexing during tightening.

When the components are assembled as shown in Figures 28A to 28L, the resulting assembly is shown in cross-section in Figure 29. In this embodiment, gears 806 and 808 are axially retained by gear caps 814, torque clutch 824 is radially positioned by center shaft 802, the outer lower support circumference of torque clutch 824 is supported by low-friction support washers 820, and the outer upper support circumference of torque clutch 824 is supported by crown trim 830 for vertical retention. The tightening rotator 832 provides an aesthetically pleasing cover and a snap-fit connection with the torque clutch 824 provides axial retention of the tightening shaft 802. Thus, this exemplary embodiment of the assembly provides: minimal components, a torque clutch with radial support at the center and axial thrust at the periphery to resist the consumer's tightening force during tightening, and a tightening rotator that maintains the center of the tightening shaft when the tightening rotator is engaged. The improved radial and axial support of the torque clutch, combined with the low-friction support washer, greatly improves the tightening experience through component rigidity and low friction.

As described above in conjunction with Figures 7A to 7D, in an embodiment, the escapement mechanism 70 has a minimum operating swing angle, which may be approximately 9 degrees per side. If the swing amplitude is below this value, the mechanism will not operate. A swing amplitude control device 92 is provided to set the swing amplitude to a preferred height. Generally, the amplitude must be greater than 9 degrees per side to be effective. For a given design, the swing amplitude control is set to a minimum of approximately 15 degrees per side and a maximum of 25 degrees per side. The purpose of the swing amplitude control lever 95 is to reduce the swing amplitude by moving the lever downward. However, moving the swing amplitude control lever 92 too far downward will cause the lever to jam against the drop plate. When this occurs, the swing amplitude control fails and the swing mechanism will swing at its maximum amplitude.

Referring to Figures 30-33, an exemplary closing feature for amplitude control can be implemented in the escapement mechanism 70. In Figure 33, by strategically placing downward stops 910 to limit downward rotation of the amplitude control lever 95, a position can be found in which the drop plate 85 can be actuated at less than the required exemplary 9-degree side-to-side pitch angle without causing the drop plate 85 to become stuck. Furthermore, the drop plate 85 must be able to "float." Therefore, a space (e.g., gap 920) is provided as shown to provide a closed position. Furthermore, moving the amplitude control lever 95 downward would cause it to bind against the drop plate 85, rendering it inoperable. Therefore, the stop 910 is positioned as shown to prevent the amplitude control lever 95 from descending further, thereby preventing the drop plate 85 from becoming stuck. The stop 910 may be disposed in a housing that supports the amplitude control device 92 or another adjacent component.

Referring to FIG. 34 , in some embodiments, a welded steel frame can be provided, allowing for reduced shipping dimensions and offering other benefits. The various mechanical components disclosed herein provide improved performance when the frame is substantially rigid. As shown, an exemplary frame design includes a welded frame 1005 comprising a tower-shaped member 1010 rigidly welded to a horizontal member 1020 of a base 1030. A corresponding U-shaped or curved member 1040 of the base 1030 is adapted to be inserted into or otherwise coupled to the horizontal member 1020 of the welded frame.

The above-mentioned swing assembly can be implemented in various structures and operated in various methods as listed below: 1. A spring-loaded swing assembly comprising: a frame assembly including a housing; a drive spring positioned within the housing and having a drive spring axis (X3) oriented in a non-vertical direction relative to a vertical plane; and a swing arm assembly connected to the frame assembly to receive energy from the drive spring, the swing arm assembly comprising a swing arm and a swing arm pivot, the swing arm being rotatable about a swing arm axis (X1), the swing arm axis being oriented in a non-horizontal direction relative to a horizontal plane. 2. The clockwork oscillating assembly according to configuration 1, wherein the drive spring axis (X3) is angled relative to the swing arm axis (X1). 3. The clockwork oscillating assembly according to configuration 1, wherein the swing arm axis (X1) is oriented at an angle of 30 to 70 degrees relative to a horizontal plane. 4. The clockwork oscillating assembly according to configuration 1, wherein the drive spring axis (X1) is oriented at an angle of 5 to 20 degrees relative to a vertical plane. 5. The clockwork oscillating assembly according to configuration 1, further comprising an escapement assembly connected to the frame assembly, the escapement assembly having an escapement axis (X2) angled relative to the swing arm axis (X1). 6. The clockwork pendulum assembly of configuration 5, wherein the pendulum arm axis (X1), the escapement axis (X2), and the drive spring axis (X3) are each angled relative to one another. 7. The clockwork pendulum assembly of configuration 5, wherein the escapement axis (X2) is substantially parallel to a horizontal plane. 8. The clockwork pendulum assembly of configuration 1, wherein the pendulum arm assembly includes an adjustment assembly and a seat frame, and the adjustment assembly is configured to adjust the tilt angle of the seat frame. 9. The clockwork pendulum assembly of configuration 8, wherein the drive spring is arranged transversely relative to the seat frame. 10. The clockwork pendulum assembly of Configuration 1, wherein the frame assembly includes: an upper end and a lower end; a base located at the lower end of the frame assembly; and an upright frame member extending from the base to the upper end of the frame assembly. 11. The clockwork pendulum assembly of Configuration 10, wherein the frame assembly further includes: a support member located at the lower end of the frame assembly, the support member configured to rest on the ground; and a handle positioned adjacent to the upper end of the frame assembly. 12. The clockwork pendulum assembly of Configuration 11, wherein the support members extend from the base in opposite directions. 13. The clockwork pendulum assembly of Configuration 1, wherein a crank assembly is provided on the frame assembly to wind the drive spring. 14. The clockwork pendulum assembly of configuration 13, wherein the crank assembly includes a crank handle configured to extend away from the frame assembly, and rotation of the crank handle about the crank pivot causes the drive spring to wind. 15. The clockwork pendulum assembly of configuration 14, wherein the crank handle is configured to fold outward from the frame assembly in a use state and is configured to fold into a pocket defined in the frame assembly in a storage state. 16. The clockwork pendulum assembly of configuration 13, further comprising a winding mechanism disposed between the crank assembly and the drive spring to convert an activation input from the crank assembly to wind the drive spring. 17. The clockwork oscillating assembly of configuration 16, wherein: the winding mechanism includes a winding shaft connected to the crank assembly at a first end and connected to the spool at a second end; and the drive spring includes a first end connected to an attachment plate disposed around the winding shaft and a second end connected to the spool, such that rotation of the winding shaft winds the drive spring via the spool. 18. The clockwork pendulum assembly according to configuration 17 further includes a gear assembly disposed between the crank assembly and the drive spring to reduce the force required to wind the drive spring, the gear assembly comprising: a crank gear secured to a shaft connected to the crank assembly; and a spring gear engaged with the crank gear and secured to the spool. 19. The clockwork pendulum assembly according to configuration 1 further includes a winding mechanism comprising a winding shaft positioned along the drive spring axis (X3), the winding mechanism having a first end connected to the crank assembly and a second end connected to the spool. 20. The clockwork pendulum assembly of configuration 19, wherein the drive spring includes a first end connected to an attachment plate disposed about the upper tensioning shaft and a second end connected to the spool, such that rotation of the upper tensioning shaft causes the drive spring to be tightened via the spool. 21. The clockwork pendulum assembly of configuration 20, wherein the tightening mechanism further includes: a first tightening gear disposed about the upper tensioning shaft and attached to the attachment plate; and a second tightening gear meshingly engaged with the first tightening gear; wherein the stored energy released from the drive spring rotationally drives the first tightening gear, and the first tightening gear rotationally drives the second tightening gear. 22. The clockwork oscillating assembly according to configuration 21, further comprising an escapement assembly connected to the frame assembly, the escapement assembly comprising an escapement shaft connected to a second tightening gear that rotationally drives the escapement shaft, the escapement shaft being oriented along an escapement axis (X2). 23. The clockwork oscillating assembly according to configuration 22, wherein the escapement shaft is oriented substantially parallel to a horizontal plane. 24. The clockwork oscillating assembly according to configuration 22, wherein the escapement assembly further comprises an escapement gear fixed to the escapement shaft, the escapement gear being configured to be driven via the second tightening gear. 25. The clockwork swing assembly according to configuration 24, wherein the escapement assembly further comprises: a carriage coupled to the escapement shaft and configured to rotate about the escapement axis (X2); and a pusher comprising a first end coupled to the carriage and a second end coupled to the swing-arm assembly, wherein when the escapement gear is driven by stored energy released from the drive spring via the connection to the second upper tensioning gear via the escapement shaft, the pusher drives the swing-arm assembly to rotate. 26. The clockwork pendulum assembly of configuration 25, wherein: the pusher comprises a wire, the first and second ends of the pusher comprise portions angled relative to a main body of the pusher, the first end of the pusher is configured to be retained in an opening of a bracket, the bracket comprising a through-hole and at least one tapered region adjacent to the through-hole, and the second end of the pusher is configured to be retained in an opening in a pivot housing of the pendulum assembly, the opening comprising the through-hole and at least one tapered region adjacent to the through-hole. 27. The clockwork pendulum assembly of configuration 25, wherein the pusher comprises a first bevel gear and a second bevel gear drivingly engaged with the first bevel gear, the first bevel gear being attached to the pendulum pivot, and the second bevel gear being connected to the bracket. 28. The clockwork pendulum assembly of configuration 25, wherein the escapement gear includes a plurality of teeth, and the escapement assembly further includes: a pawl pivotally attached to the frame assembly, the pawl including a pawl tooth selectively engageable with a tooth of the escapement gear to prevent the escapement gear from rotating in the driving direction when the pendulum arm is in the neutral state; and a clamp pivotally attached to the carrier, the clamp selectively engaging with a tooth of the escapement gear when the pendulum arm rotates and the pawl tooth disengages from the escapement gear. 29. The clockwork oscillating assembly according to configuration 28, wherein the escapement assembly further includes an actuator coupled to the escapement shaft and configured to rotate about the escapement axis (X2), the actuator selectively engaging with the pawl and the clamp to control the selective engagement between the pawl and the clamp and the escapement gear. 30. The clockwork oscillating assembly according to configuration 28, further including: an amplitude control assembly comprising a drop plate configured to selectively limit the travel of the clamp; and an amplitude control lever configured to selectively adjust the position of the drop plate. 31. The clockwork oscillating assembly according to configuration 30, wherein the drop plate includes an engagement portion configured to engage with a portion of the clamp and an attachment configured to engage with a portion of the amplitude control lever. 32. The clockwork swing assembly of configuration 31, wherein the amplitude control lever includes a first stop and a second stop, the first stop and the second stop being spaced apart from each other and each configured to engage with an attachment of the drop plate to control the swing amplitude. 33. The clockwork swing assembly of configuration 19, further comprising a torque-limiting clutch configured to prevent over-tightening of the drive spring. 34. The clockwork swing assembly of configuration 33, wherein the torque-limiting clutch includes a torque clutch spring assembled on a bobbin, and the torque clutch spring is configured to tighten when the tightening shaft rotates in a tightening direction and to slip when the drive spring is tightened beyond a predetermined torque. 35. The clockwork swing assembly of configuration 33, wherein the torque limiting clutch comprises: a first housing operably connected to the crank assembly, the first housing including a clutch drive gear; a clutch hub fixed to the crank assembly; and a clutch pawl pivotally connected to the clutch hub via a biasing element, the clutch pawl being biased by the biasing element to select the clutch drive gear. selectively engageable; wherein, when the drive spring is tightened by the crank assembly, the clutch pawl engages with the clutch drive tooth up to a predetermined torque limit to transfer torque from the crank assembly to the drive spring, and when the torque transferred from the crank assembly to the drive spring exceeds the predetermined torque limit, the clutch pawl disengages from the clutch drive tooth to prevent further torque from being transferred from the crank assembly to the drive spring. 36. The clockwork pendulum assembly of configuration 33, wherein the torque limiting clutch comprises: an input shaft connected to the crank assembly; an output shaft connected to the drive spring; a cap secured to the input shaft; and a spool secured to the output shaft and clamped to the cap; wherein the cap and spool are configured to slide relative to each other when a predetermined force is overcome to prevent the drive spring from being over-tightened. 37. The clockwork oscillating assembly of configuration 33, wherein the torque limiting clutch comprises: a shaft connected to the crank assembly; an input hub including at least one engaging member; and an output hub connected to the shaft, the output hub including at least one protrusion engageable with the engaging member; wherein the at least one protrusion is configured to disengage from the at least one engaging member when a predetermined force from the crank assembly is overcome, thereby preventing the drive spring from being over-tightened. 38. The clockwork oscillating assembly of configuration 37, wherein the at least one engaging member is a resilient member biased toward engagement with the at least one protrusion. 39. The clockwork oscillating assembly of configuration 37, wherein the at least one engaging member is pivotally attached to the input hub. 40. The clockwork swing assembly of configuration 37, further comprising a spring coupled to the at least one engaging member and biasing the at least one engaging member toward engagement with the at least one protrusion. 41. The clockwork swing assembly of configuration 1, wherein the swing arm is coupled to the swing arm pivot via a swing arm connector, the swing arm connector comprising a rivet and a bayonet. 42. The clockwork swing assembly of configuration 1, wherein the swing arm assembly comprises a seat frame, and an occupant's center of gravity (COG) within the seat frame substantially intersects the seat frame's tilt axis (AR) and seat rotation axis (ASR). 43. The clockwork swing assembly of configuration 1, wherein the swing arm assembly includes a seat frame, and a tilt axis (AR) of the seat frame and a seat rotation axis (ASR) of the seat frame intersect each other, and both axes extend through a center of gravity (COG) defined by the seat frame and an occupant of the clockwork swing assembly. 44. A swing assembly comprising: a frame assembly; a swing arm assembly connected to the frame assembly, the swing arm assembly including a swing arm pivot pivotally attached to the frame assembly; and a swing arm having a first end connected to the swing arm pivot and a second end connected to the seat assembly; wherein the swing arm is rotatable about a swing arm axis (X1) oriented in a non-horizontal direction relative to a horizontal plane. 45. The swing assembly of configuration 44, wherein the swing arm is L-shaped. 46. The swing assembly of configuration 44, wherein the swing arm further includes a support hub located at the second end of the swing arm and configured to receive the seat assembly. 47. The swing assembly of configuration 46, wherein the seat assembly is removably connected to the support hub. 48. The swing assembly of configuration 46, wherein the support hub is rotatable relative to the swing arm. 49. The swing assembly of configuration 46, wherein the seat assembly includes a connection recess, and the support hub includes a connection stud received in the connection recess to secure the seat assembly to the support hub. 50. The swing assembly of configuration 46, wherein the support hub includes: a fixed hub fixed to the swing arm; and a swivel hub rotatably connected to the fixed hub, the swivel hub being configured to be attached to the seat assembly and swivel relative to the fixed hub. 51. The swing assembly of configuration 50, further including: a plunger; a biasing element attaching the plunger to the fixed hub; and a stopper formed on the swivel hub to selectively receive the plunger, thereby inhibiting rotation between the swivel hub and the fixed hub. 52. The swing assembly of configuration 50, wherein the seat assembly further includes: a seat frame; at least one support leg connected to the seat frame; and a connection assembly including a connection recess for receiving the swivel hub. 53. The swing assembly of configuration 51, wherein the pivot hub includes at least one rib, and the connecting recess defines at least one channel to accommodate the at least one rib. 54. The swing assembly of configuration 51, wherein the seat assembly includes an actuator to release the engagement between the seat assembly and the support hub. 55. The swing assembly of configuration 54, wherein the connecting assembly includes: a body; a pivot member having a first end and a second end and pivotally connected to the body at a pivot connection located between the first end and the second end, the first end of the pivot member being attached to the actuator; and an actuator biasing element applying a biasing force to the first end of the pivot member to release the actuator. biased to a rest position; and a hub latch coupled to the second end of the pivot member and biased to a locked position with the swivel hub to secure the seat assembly to the swivel hub; wherein movement of the actuator toward the actuated position overcomes the biasing force of the actuator biasing element and causes the pivot member to pivot about the pivot connection, thereby moving the hub latch to an unlocked position and disengaging the swivel hub. 56. The swing assembly of configuration 52, wherein the seat assembly further includes a support base for use of the seat assembly independently of the swing arm assembly when the seat assembly is removed from the swing arm assembly. 57. A spring-loaded swing assembly comprising: a frame assembly; a drive spring positioned within the frame assembly and oriented in a non-vertical orientation relative to an orthogonal plane; a crank assembly disposed on the frame assembly, the crank assembly configured to input a drive torque to the drive spring; a seat frame rotatably coupled to the frame assembly, the seat frame including a swing arm oriented in a non-horizontal orientation relative to a horizontal plane; and a gear assembly coupled to the crank assembly and the drive spring to transmit energy from the drive spring to provide a swinging motion to the seat frame. 58. A method of using a clockwork swing assembly, the method comprising: engaging a crank assembly by rotating a crank handle, wherein the crank assembly is connected to a winding mechanism; winding a drive spring connected to the winding mechanism; and selectively releasing energy from the drive spring via a catch assembly having a carriage connected to a swing arm pivot via a pusher, causing the swing arm pivot to move in a first direction during a powered stroke and in a second direction during a non-powered stroke. 59. A method for driving a seat frame having a spring-type swing assembly, the method comprising: rotating a crank assembly connected to a drive spring so that the drive spring is tightened, the drive spring being positioned along a drive spring axis (X3) oriented in a non-vertical direction relative to a vertical plane; transferring energy from the tightened drive spring to an escapement assembly having an axis (X3) relative to a vertical plane; A drive spring axis (X3) is angled relative to an escapement axis (X2); and selectively releases energy from the escapement assembly to a swing arm pivot, wherein the swing arm pivot is connected to the seat frame and has a swing arm axis (X1) that is oriented in a non-horizontal direction relative to a horizontal plane and is angled relative to the drive spring axis (X3) and the escapement axis (X2).

Having described the present embodiment in detail, those skilled in the art will understand and appreciate that many physical changes can be made without changing the inventive concepts and principles embodied therein, only some of which are exemplified in the detailed description of this disclosure.

It should also be understood that many embodiments are possible that combine only parts of the preferred embodiments without altering the inventive concepts and principles embodied therein with respect to those parts.

Therefore, the present embodiments and optional configurations are considered in all aspects to be exemplary and/or illustrative, rather than restrictive, and the scope of the disclosure is specified by the appended patent application rather than the foregoing description, and therefore all alternative embodiments and changes to the embodiments that fall within the meaning and range of equivalents of the patent application are included therein.

10: Clockwork swing assembly 12: Swing arm assembly 15: Seat frame 20: Adjustment assembly 25: Swing arm 25a: First end 25b: Second end 26: Housing 27: Swing arm pivot 27a: Pivot housing 27b: Bearing 35a: Frame assembly 35b: Base assembly 35c: Upright frame member 35d: Bracket 36: Handle 37: Support member 39a: Leg 39b: Leg 40: Crank assembly 42: Handlebar 44: Crank handle 46: Crank pivot 47: Pocket 50: Clamping mechanism 52: Attachment plate 54: First tensioning gear 55: Tensioning shaft 55a: First end 55b: Second end 56: Second tensioning gear 60: Drive spring 60a: First end 60b: Second end 62: Connector 64: First bearing 66: Power tube 70: Escapement assembly 72: Bracket 72a: Opening 74: Escapement gear 74a: Gear 74b: Second set of gears 75: Escapement shaft 76: Pawl 76a: Pawl tooth 76b: Pawl control arm 76c: Pawl pivot 76d: Pawl safety tooth 76e: Pawl counterweight 78: Actuator 78a: Pawl engagement surface 78b: Clamp engagement surface 78c: Actuator counterweight 80: Clamp 80a: Clamp teeth 80b: Clamp control arm 80c: Clamp pivot 80d: Clamp teeth 85: Drop plate 85a: Engaging portion 85b: Recess 85c: Attachment 85d: Control edge 85e: Slot 90: Pusher 90a: First end 90b: Second end 92: Amplitude control assembly 95: Amplitude control lever 95a: Stop 95b: Stop 100: Sliding clutch spring 100': End 102: Pin 105: Silent upper tensioning shaft 105a: Upper section 105b: Lower section 106: Secondary bearing 108: Connector 120: Energy level indicator 125: Swing arm connector 125a: Rivet 125b: Bayonet 125c: Slot 127: Swing arm pivot 140: Shaft 144: Arm 190a: First bevel gear 190b: Second bevel gear 200: 244: Arm 300: Gear assembly 302: Crank gear 304: Idle gear 306: Spring gear 344: Arm 400: Clutch assembly 400': Torque-limiting clutch 402: First housing 402': Input shaft 402a: Clutch drive gear 402e: 404: Clutch hub 404': Output shaft 404a: Pawl 404b: Pawl tooth 404c: Biasing element 404d: Pivot connector 404e: Auxiliary gear 406: Second housing 406': Cap 408': Spool 410': Spring 420: Torque-limiting clutch assembly 422: Input hub 424: Output hub 426: Connector 428: Protrusion 430: Spring pawl 432: Engaging portion 440: Torque-limiting clutch assembly 442: Input hub 444: Upper portion 444a: Rotating portion 446: Lower portion 448: Output hub 450: Upper portion 452: Lower portion 454: Engaging member 455: Engaging surface 456: Protrusion 458: Spring 540: Cap 542: Opening 544: Arm 546: Inner wall 600: Spring-loaded swing assembly 612: Swing arm assembly 615: Seat frame 625: Swing arm 627: Swing arm pivot 635: Frame assembly 640: Crank assembly 644: Crank arm 646: Ring 648: Plate 712: Swing arm assembly 715: Seat frame 717: Seat section 719: Base assembly 725: Swing arm 727: Support hub 740: Seat assembly 750: Swivel hub 752: Fixed hub 753: Swivel base 754: Swivel body 756: Circular recess 758: Anti-rotation channel 760: Latch bracket 762: Plunger 764: Biasing element 766: Plunger recess 768: Support leg 770: Support base 772: Connector assembly 772a: Body 774: Actuator 776: Connecting recess 777: Biasing element 778: Pivot member 778a: First end 778b: Second end 779: Pivot connector 780: Hub latch 782: Hub protrusion 784: Anti-rotation rib 800: Torque-limiting clutch assembly 802: Shaft 804: Shaft 806: Shaft hole 808: Shaft hole 810: Housing 811: Gear 812: Gear 814: Gear cap 816: Screw 820: Low-friction support washer 824: Torque clutch 827: Support base 828: Tightening knob 829: Connecting stud 830: Crown ornament 832: Tightening rotator 872: Connecting assembly 874: Connecting recess 900: Torque clutch spring 910: Stop 920: Clearance 1005: Welding frame 1010: Tower component 1020: Horizontal component 1030: Base 1040: U-shaped or curved component AR: Inclined axis ASR: Seat rotation axis COG: Center of gravity P1: Horizontal plane P2: Vertical plane X1: Swing arm axis X2: Escapement axis X3: Drive spring axis θ1: Angle θ3: Angle

The foregoing summary and the following detailed description will be better understood when read in conjunction with the accompanying drawings, which illustrate preferred embodiments of the present disclosure. In the drawings:

FIG1A is a perspective view of a clockwork children's pendulum assembly.

FIG1B is another perspective view of the clockwork child pendulum assembly.

FIG1C is a top view of the clockwork child pendulum assembly.

FIG2 is a perspective view of the clockwork children's pendulum assembly with the housing frame removed.

FIG3A is a perspective view of the top of the frame assembly with the crank assembly in a non-use or storage position.

FIG3B is a perspective view of the top of the frame assembly with the crank assembly in use.

Figure 3C is a schematic diagram of the crank assembly according to the first embodiment.

Figure 3D is a schematic diagram of a crank assembly according to the second embodiment.

Figure 3E is a schematic diagram of a crank assembly according to a third embodiment.

Figure 3F is a schematic diagram of a crank assembly according to a fourth embodiment.

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

Figure 3H is a perspective view of the top of the frame assembly according to one example, wherein the crank assembly is in use.

FIG3I is a bottom view of the tower cap on top of the frame assembly.

FIG4A is a perspective view of the upper portion of a clockwork child's pendulum assembly.

FIG4B is a side view of the upper portion of the clockwork child's pendulum assembly.

FIG4C is a perspective view of the bottom of the drive spring.

FIG4D is a perspective cross-sectional view of the bottom portion of the drive spring.

FIG4E is another perspective view of the bottom portion of the drive spring and portion of the frame.

4F is another perspective view of a portion of a frame and a bottom portion of a drive spring according to another example.

FIG5A is another perspective view of the upper portion of the clockwork child pendulum assembly.

FIG5B is an exploded perspective view of the escapement assembly.

FIG5C is a perspective view of the bracket, pivot housing, and pusher in an assembled state.

FIG5D is a perspective view of the bracket, pivot housing, and pusher in a disassembled state.

FIG5E is a side cross-sectional view showing the various axes of the clockwork child pendulum assembly.

Figure 5F is an enlarged view of the interface between the pusher and the bracket.

Figure 5G is a front view of the interface between the pusher and the bracket.

Figure 5H is an enlarged view of a portion of the bracket configured to accommodate the pusher.

FIG6A is a front view of the escapement assembly in a first state.

FIG6B is a front view of the escapement assembly in the second state.

FIG6C is a front view of the escapement assembly in the third state.

FIG6D is a front view of the escapement assembly in the fourth state.

FIG7A is a perspective view of the amplitude control assembly.

FIG7B is a front view of the amplitude control assembly in a first state.

FIG7C is a front view of the amplitude control assembly in the second state.

FIG7D is a front view of the amplitude control assembly in the third state.

8A-8C illustrate various stages of the pawl safety tooth and the second set of teeth.

FIG9A is a perspective view of a torque limiting clutch according to one embodiment.

FIG9B is a side view of the torque limiting clutch.

FIG9C is a side cross-sectional view of the torque limiting clutch.

FIG10A is a perspective view of another example of a frame assembly.

FIG10B is an enlarged view of a portion of the top area of the frame assembly of FIG10A.

FIG10C is another enlarged view of a portion of the top area of the frame assembly of FIG10A.

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

FIG12A is a side view of the torque limiting clutch assembly.

FIG12B is another side view of the torque limiting clutch assembly.

FIG12C is an exploded perspective view of the torque limiting clutch assembly.

FIG12D is a top view of the torque limiting clutch assembly in a first state.

FIG12E is a top view of the torque limiting clutch assembly in the second state.

FIG12F is a top view of the torque limiting clutch assembly in a third state.

FIG12G is a bottom view of the interior of the torque limiting clutch assembly.

FIG12H is a perspective view of a torque limiting clutch according to one embodiment.

FIG12I is an exploded perspective view of the torque limiting clutch shown in FIG12H.

Figure 12J is a cross-sectional view of a torque limiting clutch according to one embodiment.

FIG12K is an exploded perspective view of the torque limiting clutch shown in FIG12J.

FIG12L is a perspective view of the upper side of the torque limiting clutch shown in FIG12J.

FIG12M is a perspective view of the underside of the torque limiting clutch shown in FIG12J.

FIG12N is a perspective view of a torque limiting clutch according to one embodiment.

FIG12O is a plan view of the torque limiting clutch shown in FIG12N.

FIG12P is a cross-sectional view of the torque limiting clutch taken along plane I-I shown in FIG12O.

FIG12Q is a cross-sectional view of the torque limiting clutch taken along plane II-II shown in FIG12O.

FIG13A is an enlarged view of the interface between the frame assembly and the swing arm.

FIG13B is another enlarged view of the interface between the frame assembly and the swing arm.

FIG14 is a perspective view of the seat frame in one orientation.

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

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

FIG15C is an enlarged view of the swing arm removed from the swing arm pivot.

16A is a perspective view of a clockwork children's pendulum assembly according to an alternative embodiment of the present disclosure.

FIG16B is a side view of the clockwork child's pendulum assembly shown in FIG16A.

16C is a perspective view of the clockwork child swing assembly shown in FIG. 16A , illustrating the seat portion of the seat assembly and the base assembly.

16D is a perspective view of the clockwork child swing assembly shown in FIG. 16B , illustrating the seat portion of the seat assembly and the base assembly.

Figure 17 is a top perspective view of the crank assembly.

FIG18 is a perspective view of the swing arm assembly and the seat assembly located above the swing arm assembly.

19 is a first side view of the swing arm assembly and the seat assembly shown in FIG. 18 , with the seat assembly positioned on the swing arm assembly.

20 is a second side view of the swing arm assembly and the seat assembly shown in FIG. 18 , with the seat assembly positioned on the swing arm assembly.

21A and 21B are perspective views of the swing arm assembly.

FIG21C is an exploded perspective view of the support hub of the swing arm assembly shown in FIG21A and FIG21B.

FIG21D is a bottom perspective view of a portion of the support hub shown in FIG21C.

FIG22 is an exploded perspective view of the seat assembly shown in FIG18.

23A and 23B include top and bottom perspective views, respectively, of the support base of the seat assembly shown in FIG. 22 .

24A and 24B are perspective views of a connection assembly and a support hub, respectively, according to an alternative embodiment of the present disclosure.

25 is a cross-sectional view of a portion of the support base shown in FIG. 23B in a locked position.

26 is a cross-sectional view of a portion of the support base shown in FIG. 23B in an unlocked position.

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 positioned therein.

28A to 28L are perspective views illustrating a sequential assembly of a gear assembly and a torque clutch according to another example.

Figure 29 is a cross-sectional view of Figure 28L.

Figures 30 to 33 are cross-sectional views of an example amplitude control subassembly according to one example.

Figure 34 is a perspective view of a frame assembly according to an example.

10: Clockwork swing assembly

12: Swing arm assembly

15: Seat frame

20: Adjusting components

25: Arm swing

25a: First End

26: Shell

35a: Frame assembly

35b: Base assembly

37: Support parts

40: Crank assembly

Claims (24)

A clockwork swing assembly, comprising: a frame assembly including a housing; a drive spring positioned within the housing and having a drive spring axis (X3) oriented in a non-vertical direction relative to a vertical plane; a swing arm assembly connected to the frame assembly to receive energy from the drive spring, the swing arm assembly including a swing arm and a swing arm pivot, the swing arm being rotatable about a swing arm axis (X1) oriented in a non-horizontal direction relative to a horizontal plane; and A tensioning mechanism includes a tensioning shaft positioned along the drive spring axis (X3), the tensioning mechanism having a first end connected to the crank assembly and a second end connected to the spool; wherein the drive spring includes a first end connected to an attachment plate disposed about the tensioning shaft and a second end connected to the spool, such that rotation of the tensioning shaft tightens the drive spring via the spool. The clockwork oscillating assembly of claim 1, wherein the winding mechanism further comprises: a first winding gear disposed about the winding shaft and attached to the attachment plate; and a second winding gear engaged with the first winding gear; wherein the stored energy released from the drive spring rotationally drives the first winding gear, and the first winding gear rotationally drives the second winding gear; An escapement assembly connected to the frame assembly, the escapement assembly including an escapement shaft connected to the second upper tensioning gear for rotationally driving the escapement shaft, the escapement shaft being oriented along an escapement axis (X2), the escapement assembly comprising: a carriage connected to the escapement shaft and configured to rotate about the escapement axis (X2); and a pusher including a first end connected to the carriage and a second end connected to the swing arm assembly; When the escapement gear is driven by stored energy released from the drive spring via the connection between the escapement shaft and the second take-up gear, the pusher drives the swing arm assembly to rotate; and an escapement gear fixed to the escapement shaft and configured to be driven via the second take-up gear, the escapement gear including a plurality of teeth. The clockwork swing assembly of claim 2, wherein the escapement assembly further comprises: a pawl pivotally attached to the frame assembly, the pawl including a pawl tooth selectively engageable with a tooth of the escapement gear to prevent the escapement gear from rotating in a driving direction when the swing arm is in a neutral state; a clamp pivotally attached to the carrier and selectively engageable with a tooth of the escapement gear when the swing arm rotates and the pawl tooth disengages from the escapement gear; an amplitude control assembly; and an amplitude control lever; The amplitude control lever includes a first stopper and a second stopper, wherein the first stopper and the second stopper are spaced apart from each other and are each configured to control the swing amplitude. A clockwork swing assembly according to claim 3, wherein the amplitude control assembly includes a drop plate, the drop plate is configured to selectively limit the travel of the clamp, and the amplitude control rod is configured to selectively adjust the position of the drop plate, wherein the drop plate includes an engaging portion and an attachment, the engaging portion is configured to engage with a portion of the clamp, and the attachment is configured to engage with a portion of the amplitude control rod. The clockwork swing assembly of claim 4, wherein the amplitude control lever includes a closed position. The clockwork pendulum assembly according to claim 5, wherein the housing supporting the amplitude control assembly includes a downward stop for limiting further movement of the amplitude control rod, the downward stop corresponding to the closed position of the amplitude control rod. The clockwork swing assembly of claim 4 further comprising a gap between the attachment configured to engage with a portion of the amplitude control lever and the housing supporting the amplitude control assembly when the amplitude control lever is in a closed position, thereby enabling the drop plate to float. A clockwork swing assembly, comprising: a frame assembly including a housing; a drive spring positioned within the housing and having a drive spring axis (X3) oriented in a non-vertical direction relative to a vertical plane; a swing arm assembly connected to the frame assembly to receive energy from the drive spring, the swing arm assembly including a swing arm and a swing arm pivot, the swing arm being rotatable about a swing arm axis (X1) oriented in a non-horizontal direction relative to a horizontal plane; a tightening mechanism including a tightening shaft positioned along the drive spring axis (X3); and A torque-limiting clutch is configured to prevent over-tensioning of the drive spring. The clockwork pendulum assembly of claim 8, wherein the torque limiting clutch is radially supported at its rotational axis. The clockwork pendulum assembly of claim 8, wherein an outer lower support circumference of the torque limiting clutch is axially supported by the housing. The clockwork swing assembly of claim 10, further comprising a low friction spacer between the housing and the lower bearing circumference of the torque limiting clutch. The clockwork pendulum assembly of claim 8, wherein the outer upper support circumference of the torque limiting clutch is axially supported by the crown. The clockwork oscillating assembly of claim 8, wherein the winding mechanism has a first end connected to the crank assembly and a second end connected to the spool. The clockwork swing assembly according to claim 13, wherein the torque limiting clutch includes a torque clutch spring assembled on the bobbin, the torque clutch spring being configured to be tightened when the tightening shaft rotates in a tightening direction, and to slide when the drive spring is tightened beyond a predetermined torque. The clockwork oscillating assembly of claim 14, further comprising a winding mechanism, the winding mechanism comprising a winding shaft positioned along the drive spring axis (X3), the winding mechanism having a first end connected to the crank assembly and a second end connected to the spool; wherein the torque limiting clutch comprises: a first housing operably connected to the crank assembly, the first housing including a clutch drive tooth; a clutch hub fixed to the crank assembly; and a clutch pawl pivotally connected to the clutch hub via a biasing element, the clutch pawl being biased by the biasing element to selectively engage the clutch drive tooth; When the drive spring is tightened via the crank assembly, the clutch pawl engages the clutch drive tooth up to a predetermined torque limit to transmit torque from the crank assembly to the drive spring. When the torque transmitted from the crank assembly to the drive spring exceeds the predetermined torque limit, the clutch pawl disengages from the clutch drive tooth to prevent further torque from being transmitted from the crank assembly to the drive spring. The clockwork oscillating assembly of claim 8, wherein the torque-limiting clutch comprises: an input shaft connected to the crank assembly; an output shaft connected to the drive spring; a cap secured to the input shaft; and a clutch spool secured to the output shaft and clamped to the cap; wherein the cap and spool are configured to slide relative to each other when a predetermined force is overcome to prevent the drive spring from being overtightened. The clockwork oscillating assembly of claim 16, wherein the torque limiting clutch comprises: a shaft connected to the crank assembly; an input hub including at least one engaging member; and an output hub connected to the shaft, the output hub including at least one protrusion engageable with the engaging member; wherein the at least one protrusion is configured to disengage from the at least one engaging member when a predetermined force from the crank assembly is overcome, thereby preventing the drive spring from being over-tightened. The clockwork swing assembly of claim 17, wherein the at least one engagement member is a resilient member that is biased toward engagement with the at least one protrusion. The clockwork oscillating assembly of claim 17, wherein the at least one engagement member is pivotally attached to the input hub. The clockwork swing assembly according to claim 17, further comprising a spring connected to the at least one engaging member and biasing the at least one engaging member toward engagement with the at least one protrusion. The clockwork swing assembly of claim 8 further comprising a low-friction support washer located between the housing and the torque-limiting clutch, the low-friction support washer being mounted in a gear cap of the housing. A clockwork swing assembly, comprising: a frame assembly having an upper end and a lower end, a base member located at the lower end of the frame assembly, and an upright frame member extending from the base member to the upper end of the frame assembly, the frame assembly including a housing; a drive spring positioned within the housing and having a drive spring axis (X3) oriented in a non-vertical direction relative to a vertical plane; and a swing arm assembly connected to the frame assembly to receive energy from the drive spring, the swing arm assembly including a swing arm and a swing arm pivot, the swing arm being rotatable about a swing arm axis (X1) oriented in a non-horizontal direction relative to a horizontal plane; wherein the upright frame member is welded to the base member. The clockwork swing assembly of claim 22, wherein the frame assembly further comprises: a support member located at a lower end of the frame assembly, the support member being configured to rest on the ground, and a handle positioned adjacent to an upper end of the frame assembly. The clockwork pendulum assembly of claim 23, wherein the support members extend from the base member in opposite directions.