BACKGROUND OF THE INVENTION

Field Of The Invention

The present invention relates to a spring motor mechanism, and in particular, to a

spring motor mechanism for use in a child's swing having an adjustable swing height

control mechanism, an over-wind protection device, and a remaining swing run indicator

device.

Description Of The Related Art

Spring motor mechanisms are well known and subject to various applications,

however, they are especially suited for use in a child's swing and will therefore be

particularly described in that connection. Child swings are often powered by a torsion

spring, typically formed from wire, that receives and stores an input torque when wound

by an operator through use of a handle linked to a crankshaft. The handle and crankshaft

are typically located at the "winding end" of the device. The spring motor mechanism,

typically located at the "escapement end" ofthe device, controls the release of the torque

stored in the spring to sustain a decreasing, periodic oscillation that drives a swing seal

containing a child. Springs used in known spring motor mechanisms typically include a plurality of

coils. As the spring is wound, the number of these coils increases while the diameter of

each coil decreases. In this way, the length of the spring grows while its diameter shrinks.

Springs often have coils within coils in a "telescope" fashion to allow room for additional

coils within a limited space.

The energy generated during winding is stored in the spring, and this energy is

released as the spring unwinds to oscillate the swing. The stored energy will continue to

be released as the added spring coils unwind. Accordingly, for purposes of swing

duration, it is the number of additional coils created during winding that is significant

rather than the actual amount of torque that has been stored in the spring.

Spring motor mechanisms driven by wound torsion springs suitable for use in a

child's swing are previously known and have been disclosed, for example, in U.S. Patent

Nos. 4,165,872 to Saint and 5,083,773 to Saint, among others. In the known device, the

torsion spring is wound to create a torque that acts upon a ratchet wheel and a carriage

thereby causing the swing, which is attached to the carriage, to oscillate.

In the known mechanism, the winding end of the device includes a handle and

crankshaft structure as discussed above. The crankshaft is directly connected to the

spring so that the rotation of the handle and crankshaft winds the spring. As discussed

above, the rotational force applied to the spring by the rotating handle tightens the spring

coils causing the coils to shrink in diameter. Eventually, with over winding, the wire

spring will deform plastically, possibly damaging the torsion spring. Thus, a first

disadvantage with known spring motor mechanisms is that the spring may become

damaged if it is overwound by the operator.

Of course, repeated over winding of the spring can place substantial stress and

strain on the main spring. If the main spring should inadvertently become disengaged

with either the wind end or the escapement end, or if the main spring breaks, the spring

could begin to unwind rapidly, and generate an alarming sound.

Conventional spring motor mechanism unwind quickly and suffer from the

disadvantage of failing to function for extended periods of time before requiring

additional winding. Because the conventional spring motor mechanism is contained

within a housing, the user cannot determine how tightly the spring is wound.

Conventional spring motor mechanism do not provide the operator with an indication of

the number of swing oscillations that can be completed before the spring must be re¬

wound (i.e.. the amount of stored energy remaining in the spring).

Another disadvantage of conventional spring motor mechanisms relates to the

non-linear release of energy from the spring over time as the child swings. Specifically,

as the conventional spring motor mechanism first begins to unwind, the spring

mechanism generates a relatively high torque output which swings the child very high.

As the spring mechanism unwinds, the torque generated decreases, and the child swing

decreases in amplitude. Consequently, known spring motor mechanisms can over swing

the child as the spring initially unwinds and under swing the child as the springs finishes

unwinding.

Known spring motor mechanisms also do not account for variations in the child's

weight. Thus, a conventional spring motor mechanism that supplies sufficient torque to

appropriately swing a larger, heavier child tends to over-swing a smaller, lighter child.

SUMMARY OF THE INVENTION

A first object of the present invention is therefore to provide a spring motor

mechanism for use in a child's swing that prevents over-winding by the operator. A

second object ofthe present invention is to provide a spring motor mechanism wherein

the spring is prevented from unwinding rapidly and uncontrollably. A third object of the

present invention is to provide a spring motor mechanism that will generate an increased

number of swing oscillations. A fourth object ofthe present invention is to provide a

more accurate indication to the operator of the number of remaining oscillations that can

be completed before the spring must be re-wound.

A fifth object ofthe present invention is to provide a swing that does not oscillate

excessively high during initial spring unwinding. A sixth object ofthe present invention

is to provide a spring motor mechanism that can satisfactorily oscillate either a relatively

heavy child or a relatively light weight child.

A seventh object of the present invention is to provide a swing housing having

rounded edges and that is less of an obstacle when the child user is put in and removed

from the child swing. An eighth object of the present invention is to provide a swing

housing that is closed at the bottom, even when the swing is oscillating, to prevent injury

to the operator or child user. A ninth object of the present invention is to provide a swing

that has swing arms that are consistently bent at a proper angle to allow the swing to

oscillate longer and in a balanced fashion. A tenth object ofthe present invention is to

provide a handle that does not have an exposed crank wire that could pinch the user's

fingers. An eleventh object ofthe present invention is to provide an internal spring

mechanism that is simpler to assemble. A twelfth object ofthe present invention is to

provide an internal spring mechanism that does not generate a noise when it is being

wound.

To achieve these and other advantages and in accordance with the purpose o the

invention, as embodied and broadly described, the invention provides an over-wind

protection system to prevent the over- winding of a motor mechanism for a child swing,

comprising a main spring having an energy storing section and an end section, and a

spring sleeve having an opening and an inner surface with the end section of the main

spring being disposed adjacent to the inner surface, the end section being compressed and

exerting an outward force on the inner surface such that the end section and the spring

sleeve are fixedly attached when the main spring applies a torque below a predetermined

maximum torque, and such that the end section relatively rotates with respect to the

spring sleeve when the predetermined maximum torque is exceeded.

In addition, the invention provides for a wind indicator disposed within a housing

for displaying a relative torque provided by a main spring to the wind indicator

comprising a spring coupling connected to an end of the main spring, an indicator

engaged with the spring coupling for receiving a torque transferred from the main spring,

the indicator capable of rotating in response to an applied torque, and a bias spring

engaged with the indicator and the housing to provide a counter torque opposite to the

main spring torque such that the indicator's rotational position is altered in response to the

torque applied by the main spring and the counter torque applied by the bias spring.

The invention provides for an adjustable swing mechanism for controlling the

oscillation angle of a child swing that is powered by torque stored in a main spring,

comprising a ratchet gear having a plurality of teeth, the ratchet gear being connected to a

main spring, a pawl located adjacent to the ratchet gear, the pawl engaging with the

ratchet gear while the ratchet gear is rotating in a direction counter to the torque stored in

the spring and disengaging with the ratchet gear while the ratchet gear is rotating in a

direction identical to the torque stored in the spring, a dog located adjacent to the ratchet

gear, the dog engaging with the ratchet gear while the ratchet gear is rotating in a

direction identical to the torque stored in the spring and disengaging with the ratchet gear

while the ratchet gear is rotating in a direction counter to the torque stored on the spring,

an actuator located adjacent to the dog and pawl for controlling the engagement and

disengagement ofthe dog and the pawl with the ratchet gear such that the dog and pawl

engage with each sequential, counterclockwise tooth ofthe rachet gear after each

oscillation, and an adjustable actuator located adjacent to the dog to direct the dog into the

same ratchet tooth on successive oscillations when the maximum oscillation angle of a

child swing exceeds a predetermined amount.

It is to be understood that both the foregoing general description and the following

detailed description are exemplary and explanatory and are intended to provide further

explanation of the invention as claimed.

BRIEF DESCRIPTION OF THE DRAWINGS

The accompanying drawings, which are included to provide a further

understanding of the invention and are incoφorated in and constitute a part of this

specification, illustrate one embodiment of the invention and together with the written

description serve to explain the principles ofthe invention. In the drawings:

Figure 1 is a perspective view of the child swing;

Figure 2A is a cross-sectional schematic view of the child swing housing;

Figure 2B is a more detailed cross-sectional view ofthe housing;

Figure 3A is a front view ofthe main spring;

Figure 3B is an end view of the main spring:

Figure 3C is an end view ofthe other end ofthe main spring;

Figure 4 is an exploded view of he wind end of the components adjacent to the

driven hanger;

Figure 5 is an exploded view the sleeve, grip and main spring;

Figure 6A is an assembly cross-sectional view of the sleeve and the cover; Figure 6B is a front view of the axial face of the sleeve;

Figure 6C is a front view of the axial face of the cover;

Figure 7 is an axial view of the backwind stop;

Figure 8 is an axial view of the indicator mechanism;

Figure 9A is an outside axial view of the indicator;

Figure 9B is a view ofthe indicator installed into the housing;

Figure 10 is an exploded view of the escapement end of the swing;

Figure 1 1 A-B are side and front views of an assembly schematic view of the gear

and main spring;

Figure 1 IC is a side view of an assembly schematic view of the gear and main

spring just prior to final installation;

Figure 1 ID is an enlarged view of Figure 1 IB;

Figure 12A-C are side, front and top views of a mounting bracket and a pawl;

Figure 13 is a cross-sectional view of the assembled escapement;

Figure 14A-D are operational schematic views of a swing in a forward position,

bottom dead center position, rearward position, and forward position;

Figure 15 A-D are operational schematic views of an escapement assembly moving

in a forward direction, rearward direction and showing a dog engaging a gear, rearward

direction, forward direction and showing a pawl engaging a gear;

Figure 16A-F are operational schematic views of a modified escapement assembly

moving in a forward direction, moving in a rearward direction and showing a dog being

pivoted by a control member and engaging a gear, moving in a rearward direction,

moving in a forward direction and showing a pawl engaging a gear, moving in a forward

direction, and moving in a rearward direction and showing a dog being pivoted by a

rocker arm and engaging a gear;

Figure 17A is a top view of a control member;

Figure 17B is a top view of a cam control member;

Figure 18A-F are operational schematic views of a modified cam control

escapement assembly moving in a forward direction, moving in a rearward direction and

showing a dog being pivoted by a control member and engaging a gear, moving in a

rearward direction, moving in a forward direction and showing a pawl engaging a gear,

moving in a forward direction, and moving in a rearward direction and showing a dog

being pivoted by a rocker arm and engaging a gear.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

Reference will now be made in detail to the present preferred embodiment o the

invention, an example of which is illustrated in the accompanying drawings.

As shown in Figure 1 , swing 100 includes housing 102 that is preferably formed

from a sturdy, molded plastic material. The housing 102 fully encloses the interior parts

of the device to both protect the interior parts of the device from dust and debris, and also

to protect the operator from possible injury resulting from contact with those interior

parts. The bottom of housing 102 preferably includes are two narrow slots 212 (see

Figure 2A) that allow a first hanger 900 and a second hanger 1000 to connect the seat 1 16

to the interior mechanical parts of the swing mechanism.

The housing 102 also includes two slots 120 and 122. Slot 122 permits the swing

operator to view the wind indicator, discussed below, which is functionally similar to a

fuel gauge, it indicates an approximation of remaining spring energy. The second slot

120, allows the user to select a maximum swing arc. These features will be discussed

below.

The preferred housing 102 includes rounded edges to prevent injury to the user's

head in the event of an inadvertent collision with an edge of the housing. For this reason,

housing 102 has a front side 104 that is generally concave with rounded edges to allow

the operator additional room to remove the user from child seat 1 16. Another function of the housing is to support a crank 106. Crank 106 includes

Knob 1 14 and is connected to a shaft 210 (see Figure 2 A) which, in turn, is connected to a

main spring 300 (see Figure 2A) within housing 102. Rotation ofthe crank 106 causes a

rotation ofthe shaft 210 thereby supplying energy to the main spring 300 (see Figure 2A).

Another function of the housing 102 is to receive legs 108 that elevate and support

swing 100. Accordingly, the housing 102 has a first side 1 10 and a second side 1 12

(partially hidden in Figure 1) which are each roughly triangular in shape to secure legs

108 in such a manner that they can be positioned in a spread fashion during operation of

the swing 100 to increase the stability of the device. The first side 1 10 also supports

handle 106. Yet another function of the housing 102 is to support child seat 1 16. Accordingly,

two support arms 118 arc suspended from housing 102 and attached to the hangers 900

and 1000. Support arms 1 18 are preferably curved to reach under and grasp the child

seat. During operation of the swing, main spring 300 (see Figure 2A) transfers its energy

to oscillate support arms 1 18 which, in turn, oscillate child seat 116.

Figures 2A and 2B show the inner workings of the housing 102. The first side

1 10 of the housing 102 is a wind end that is adjacent to the crank 106. The crank 106 is

connected to the shaft 210 which extends across the entire length of the housing 102.

Both hangers 900 and 1000 are supported by the shaft 210.

First hanger 900, generally referred to as the driven hanger because it is

rotationally mounted to the shaft and not powered, and the second hanger 1000. generally

referred to as the driving hanger because it receives power from the spring, are

synchronized by a unison wire 214. This unison wire 214 rotationally couples the driving

hanger 1000 with the driven hanger 900 and stabilizes the housing and swing about

horizontal and vertical axes from excess or unwanted motion.

Figure 2B shows the interior parts ofthe housing 102 in greater detail. Wind end

1 10 receives input torque from crank 106 and applies it to main spring 300. Wind end

110 includes a slip clutch, which prevents main spring 300 from becoming over- wound,

and a wind indicator system which indicates the approximate number of oscillations that

remain before main spring 300 must be re-wound (i.e.. the amount of stored energy

remaining in the spring). As discussed below, the wind indicator system measures the

level of torque generated by the spring at a given point in time. This information can then

be used by the operator to estimate the number of times the swing can oscillate before the

spring must be re-wound.

Located on a second side 1 12 of housing 102 is an escapement end 204.

Escapement end 208 receives an output torque from main spring 300 and converts it to a

rotational force that can be used to swing the child seat 1 16. Escapement end 204

includes a swing height adjustor that can be used to control the height of the oscillation of

child scat 1 16 and lengthen the duration of the swing operation before the spring must be

re-wound. The features of wind end 1 10 and escapement end 204 will be discussed in

further detail below.

Figures 3 A, 3B and 3C show details of the main spring 300. The main spring 300

receives and stores rotational energy generated during the winding of crank 106.

Although some springs have coils of uniform size, the preferred coils 306 of main spring

300 have several different diameters. Figure 3A shows the coils 306 of main spring 300

where the coils are not of uniform diameter, but instead are of variable diameter so thai

they can fit "telescope style" within one another.

An exemplary embodiment ofthe main spring 300 has a larger diameter slip coil

section 312, a small diameter neck section 310, a variable diameter power section 314,

and a small diameter mounting section 316. Figure 3 A shows an end of main spring 300

that includes neck section 310 and slip coil section 312. Slip coil section 312 has a

greater diameter than neck section 310 so that the slip coil section can be wound down for

insertion into a spring sleeve 400 (see Figure 6A) to create an expansion force that secures

the main spring within the spring sleeve.

Figure 3B shows an end of main spring 300 where bent end portion 305 is

configured to engage a portion of the escapement assembly. Figure 3C shows the other

end of main spring 300 with a reduced diameter bent end portion 304 that is designed to

engage a projecting portion 618 (see Figure 6A).

Wind end 1 10 includes several mechanisms which assist the main spring 300 to

accumulate and retain an appropriate amount of torsional energy. Figure 4 shows

generally the parts that comprise this portion ofthe invention and their relationship with

one another. The parts include a grip 500, a sleeve 400, sleeve cover 600, back wind stop

700 and indicator 800. Driven hanger 900 is not rotationally coupled to any of the

members and free wheels on shaft 212. The indicator 800 inserts inside ofthe circular

portion 906 of the driven hanger 900. However, the display panel 808 of the indicator is

disposed radially outward of the circular portion 906. This allows the user to view the

display panel 808 through slot 122 (see Figure 1).

Figure 5 shows the initial stages of assembly of the main spring 300 with grip 500

and sleeve 400. First, slip coils 312 of main spring 300 are temporarily wound tightly and

slightly smaller than the inner diameter ofthe spring sleeve 400 for insertion into spring

sleeve 400. The slip coils are then allowed to unwind and expand to press against an

inner surface 402 of the spring sleeve.

The grip 500 preferably includes two identical, semi-circular portions that can be

joined together when assembled around the spring sleeve outer lip 408. The two semi-

circuiar portions 510 and 520 of grip 500 each have a tab 502 and slot 504 on opposite

ends that engage to lock the two portions together when they are in place. When the two

identical portions of spring sleeve grip 500 connect, tab 502 clips in and engages with slot

504.

Figure 6A shows the main spring 300, the grip 500 and the sleeve 400 after

assembly. After main spring 300 is inserted into spring sleeve 400, and the two portions

of spring sleeve grip 500 are snapped around spring sleeve 400 and main spring 300,

outer lip 404 will engage with groove 506 on the interior side of grip 500. Cylindrical

extension 508, which is adjacent to the tab 502 and slot 504. retains the neck 310 of the

main spring 300 to assure that main spring 300 does not inadvertently slide out ofthe

spring sleeve. In this way, sleeve 400 and grip 500 cooperate to grasp and hold main

spring 300 and prevent main spring 300 from disengaging and unwinding quickly and

uncontrollably. Flowever, as described above, spring sleeve grip 500 grips main spring

300 and spring sleeve 400 in such a way that the main spring can rotate and slide within

the spring sleeve when a predetermined torque has been exceeded.

Figure 6A also shows the assembled spring 300, sleeve 400 and grip 500 just prior

to assembly with the cover 600. For clarity, only a portion ofthe gears 610 found on the

outer surface of the cover are shown. Also, for clarity, the elements in all the Figures are

not shown to scale (note especially the cut lines on the cover 600). The grip 500 has a

circular, circumferential bayonet lock 510 which is designed to cooperate with a

corresponding shoulder 612 on the cover. Once the sleeve 400 and grip 500 are

assembled together with cover 600, two additional elements mate.

Figures 6B and 6C show the two adjacent, mating end faces of sleeve 400 and

cover 600. Radial slots 406 disposed on the end face of sleeve 400 mate with radial ribs

614 which are disposed on the bottom inner surface 616. Because of these slots 406 and

ribs 614, the cover 600 is able to transmit torque to sleeve 400. Sleeve 400 is able to then

transfer torque to the main spring 300 because of the interference fit between main spring

300 and sleeve 400.

Generally, the inner surface 402 of spring sleeve 400 has a frictional coefficient

such that the expansion force created by the expanding slip coils 312 generates a frictional

force that prevents main spring 300 from sliding or turning within spring sleeve 400

during normal use. Flowever, when over-winding occurs, the coils 12 shrink in

diameter, the expansion force decreases, and the spring torque increases. Accordingly,

the inner surface 402 has a desired diameter and friction coefficient such that the main

spring 300 will slip within the inner surface 402 when a maximum amount of winding of

main spring 300 has occurred (i.e.. a predetermined amount of energy is stored in the

spring and coil shrinkage has occurred), thereby preventing the over-winding of main

spring 300.

The slip clutch has the added advantage of being able to function with a wide

variety of main spring types regardless of their material or the amount of energy that they

can store. Thus, the slip clutch will function satisfactorily with main springs that are

manufactured at the extremes of specified production parameters.

Returning to Figure 6A, two other parts mate when the cover 600 is mounted over

the sleeve 400. The reduced diameter bent end portion 304 is designed to engage an

extension 618. This relationship is important when there is relative rotation between the

cover 600 / sleeve 400 assembly and the main spring 300. When there is relative rotation

between the main spring 300 and the cover 600, the device includes a structure that

generates a "clicking" sound to notify the operator that additional winding is no longer

necessary. Specifically, main spring 300 has a bent end portion 304 that rests against a

projecting portion 618 of cover 600. When the main spring 300 is being wound, the bent

end portion 304 and the rotating spring sleeve and its projecting portion 618 rotate

together. However, when the spring is being over-wound by the operator, the bent end

wire portion ofthe spring remains still due to the sliding of the spring 300 within spring

sleeve 400 while projecting portion 618 continues to spin. As the two parts come into

moving contact, a clicking sound is generated. This sound notifies the operator that the

spring is wound to a predetermined maximum level.

The invention also includes a one way clutch and a wind indicator mechanism for

indicating the amount of stored energy remaining in the main spring 300 and the

approximate length of time remaining before the main spring 300 must be re-wound. The

one way clutch and the wind indicator mechanism preferably include, as shown in Figure

4, spring sleeve 400, spring sleeve grip 500, spring sleeve cover 600, back wind stop 700

and wind indicator 800. The invention also contemplates locating this assembly within

the first driven hanger 900.

As shown generally in Figure 4, the back wind stop 700 is mounted within

indicator 800. Back wind stop 700 acts as an interface between the indicator 800 and the cover 600. The

back wind stop 700 can be seen in greater detail in Figure 7.

The back wind stop 700 nests within the indicator 800 as shown in Figure 8.

Returning to Figure 7, backwind stop 700 is preferably a "C" shaped structure, in other

words, it is any shape that is less than a full circle, that is flexible such that the space

between the ends 714 and 716 of the back wind stop 700 can be flexed together, thereby

reducing the overall diameter of the back wind stop 700. Backwind stop 700 has an

engaging portion 702, a straight portion 704, and a clamping portion 706. In addition,

backwind stop 700 includes a projection 708 which extends radially from the outer

surface, and an abutting face 718 located opposite teeth 710, which preferably point in the

same direction. Back wind stop 700 may also include additional projecting portions 712 which are present for manufacturing reasons.

Figure 8 shows the back wind stop 700 in its assembled position with respect to

the indicator 800 and the cover 600. First, the relationship between the back wind stop

700 and the indicator 800 will be discussed, then the relationship between the back wind

stop 700 and the cover 600 will be discussed.

- 18 - Back wind stop 700 mounts inside, or radially inward, of indicator 800. The back

wind stop 700 is positioned within the indicator 800 in an orientation that allows

projection 708 to engage a corresponding recess 812 in indicator 800. Indicator 800 also

has several spacing lands 814 to assist in properly locating the back wind stop 700 within

the indicator 800. The indicator has a shoulder 816 that works in cooperation with

abutting face 718.

Spring sleeve cover 600 fits inside back wind stop 700. The overall inner

diameter of the back wind stop 700 is slightly less than the outer diameter of the cover

600. So the cover 600 experiences a very slight interference fit with the back wind stop 700. This interference fit is so slight that it transfers only a minimal torsional load

between the two members, but merely serves to insure that the back wind stop 700 bears

snugly around the cover 600.

The teeth 710 of the back wind stop 700 each point in the same direction. These

teeth 710 cooperate with teeth 610 to provide a one way clutch. In other words, the teeth

710 and 610 are designed in a way which allows easy rotation in one direction, but will

intermesh and prevent rotation in the opposite direction.

In the preferred embodiment, when main spring 300 is being wound, the cover

600 rotates freely within back wind stop 700 because the straight portion 704 flexes and

allows teeth 710 to float radially outward, lifting the back wind stop teeth 710 clear of the

spring sieeve cover teeth 610. The respective teeth preferably do not contact (or only

slightly contact), during winding so that the device can be wound silently.

After winding has been completed, the torsional energy stored in main spring 300

will be released, and the main spring 300 will tend to bias the cover 600 and its associated

teeth 610 in the opposite rotational direction. This causes the teeth 710 of the back wind

stop 700 to immediately engage the cover teeth 610, thus causing the two members to

lock up. When this lock up occurs, the back wind stop constricts cover 600 and urges the

cover 600 in tighter engagement with the back wind stop 700. This, in turn, further forces

teeth 610 and 710 tighter together.

In the locked position, the cover 600 and back wind stop 700 rotate together in the

direction of spring bias ofthe main spring 300 (counter clockwise in Figure 8). Shoulder

816 on the indicator 800 cooperates with abutting face 718 on the back wind stop 700 to

prevent rotation of the back wind stop 700 within the indicator 800. This arrangement

also allows the indicator 800 to lock with cover 600 via the back wind stop 700. In other

words, when cover 600 experiences the torsional spring bias of main spring 300, all three

elements: the cover 600, the back wind stop 700 and the indicator 800 lock together and

rotate as one unit.

The indicator 800 also has spring holders 802. The preferred embodiment

contemplates the use of two, but any number would suffice. These spring holders 802

each hold a proportioning spring 804 and a curved valley 806 guides the spring around

the circumferential outer surface of the indicator. The preferred embodiment also

contemplates the use of complementary guides (not shown) disposed on the inner surface

of the housing 102. The other end of the proportioning spring 804 is attached to the

housing 102 by a similar type of spring holder 820.

The indicator 800 generally operates by displaying or indicating to a user an

approximate level of torsional spring energy remaining in the main spring 300. As the

main spring 300 biases cover 600 in the unwind (counter clockwise direction in Figure 8)

direction, the cover 600, back wind stop 700 and indicator 800 will tend to rotate in the

direction of unwind of the main spring 300. This torsional force is counter-balanced by

proportioning springs 804, which exert a torsional force in the opposite direction (i.e. a

torsional force which tends to wind the main spring 300, clockwise in Figure 8). Thus.

indicator is held in a state which balances the rotational forces of the main spring 300

with the proportioning springs 804. The more energy the main spring 300 has, the more

indicator 800 will tend to rotate against proportioning springs 804 and vice versa.

Another expression ofthe concept of counter-balancing spring forces is that the

proportioning springs 804 convert the level of spring energy in the main spring 300 to an

angular displacement which can be used to display the amount of energy currently

contained by the spring. The preferred embodiment of this concept displays an angular

displacement to a user using a label surface 808. The label surface 808 contains a mark or

indicia 818 which can be viewed by a user through slot 122 (see Figure 1 ). In the

preferred embodiment, label surface 808 is located on a banana shaped structure that is

mounted to the exterior surface of indicator 800. The relative position of the indicator

800, as shown by the mark or indicia 818 ofthe label surface 808, reveals to the operator

the approximate amount of energy, in relative terms, stored in the main spring 300. Thus,

when there is no energy stored in the main spring 300, indicia 818 will be at a first

position as determined by the two proportioning springs 804. As a maximum torque is

applied to main spring 300, that torque will push against the proportioning springs 804 and alter the rotational position of the indica 818 to a second position.

The spring constant of the bias springs 804 is chosen to preferably match the range

of torque that the main spring 300 can exert. Because the indicator 800 operates based

upon relative torsional forces, many types of main springs can be successfully used in the

swing, and the indicator 800 will still function properly. This is true even if the various

springs have varying numbers of coils or different material properties.

The wind indicator mechanism has the added advantage of being functional even

if the main spring deforms slightly or changes shape over time because the present system

measures relative torsional forces rather than counting the number of times the spring has

been wound by the operator.

Figure 9A shows a side view of the indicator 800. This Figure more accurately

portrays the relative locations of the preferred spring holders 802. Figure 9B shows the

indicator 800 installed into the housing 102. Figure 9B also shows the relationship

between the label surface 808 and slot 122.

Returning to Figure 2B, the escapement end 204 ofthe swing will now be discussed. The preferred embodiment of the invention contemplates the use of swing

height adjusting mechanism. This invention can best be understood when compared to an

escapement device without the height adjustment feature.

The escapement device of the present invention preferably allows the gradual and

intermittent release of spring energy into the swinging motion of a child sitting on the

seat. This gradual release of energy allows the spring motor to last longer because the

spring motor does not necessarily drive the seat on every oscillation. Rather the spring

motor is maintaining the swinging motion of the child by contributing small increments

of rotational energy to the swing at preferred, strategic times.

Because the escapement device controls the power output ofthe main spring 300

to the swing, the escapement device operates the driving arm 1000 (as opposed to the

driven arm 900). Figure 18 shows the preferred major components on the escapement

end 204 (Figure 2B) ofthe swing.

Figure 10 shows the driving arm 1000, a dog 1 100 that clips into a groove 1002 of

the circular portion 1004 of the driving arm 1000, a mounting bracket 1200, a height

adjuster 1500, a control member 1600, a rocker arm 1700 and a gear 1400. The main

spring 300 is rigidly mounted to gear 1400. The parts are shown in the order of assembly.

The main spring 300 (see Figure 3) is attached to gear 1400 at the end shown in

Figure 3B. Figures 1 1Λ - 1 I D shows the details of this assembly. Figure 1 1 A shows a

side view of gear 1400 and main spring 300. Gear 1400 has a holder 1402 that radially

extends from an extension boss 1404 and holds several coils of main spring 300. On the

opposite side of the boss 1404, a clip retainer assembly 1414 holds the curved end 305 of

main spring 300. The clip retainer 1414 (best shown in Figure 1 IC, a bottom view of

gear 1400) includes a recess 1406 and a resilient clip 1410. The bottom of recess 1406

includes a land 1408. Figure 1 ID is an enlarged view of the clip retainer 1414.

As the gear 1400 and the main spring 300 rotate with respect to one another, the

curved end 305 ofthe main spring 300 will deform clip 1410 towards gear 1400. The

curved end 305 will eventually snap over clip 1410 and nest in recess 1406. Land 1408

will insure that the curved end 305 does not escape axially, and the clip 1410, working in

conjunction with shoulder 1412, will insure that the curved end 305 will not escape

circumferentially.

Preferably, the main spring 300 is biased so that the curved end 305 will generally

press against shoulder 1412. In other words, with respect to Figure 1 I D, the spring

preferably urges clockwise rotation of gear 1400. In that way, shoulder 1412 experiences

the vast majority of rotational force exerted by the main spring 300 to gear 1400 and the

clip 1410 insures that the curved end 305 does not escape.

Returning to Figure 10, the exploded view of the escapement end 204 (see Figure

2B), the mounting bracket 1200 helps to mount the escapement assembly to the frame.

Generally, all ofthe parts shown in Figure 10 are suspended by shaft 210 (see Figure 2B).

The mounting bracket 1200 keeps the components axially fixed along shaft 210.

The mounting bracket 1200 has a tongue 1202 slides into groove 220 which is

rigidly secured to the housing 102 (not shown in Figure 18). The mounting bracket 1200

is the only element that is rigidly fixed to the housing in terms of rotation. All of the

other elements are fixed by the shaft 210 (see Figure 2B) to the housing, but can rotate

relative to the housing.

The escapement mechanism is assembled by axially stacking the components

shown in Figure 10 in the order shown in the figure. All ofthe components have a central

aperture which allows coaxial assembly either to the shaft 210 or to a cylindrical

extension of an adjacent member. After the dog 1 100 has been clipped to the driving

hanger 1000, in the manner discussed above, the preferred embodiment also includes the

driving hanger 1000 having a stepped central shaft 1006 with a lower larger diameter

portion and an upper smaller diameter portion.

The next step in the assembly process is to clip the pawl 1300 onto the mounting

bracket 1200. Figures 12A - 12C show this assembly process. The mounting bracket

1200 has a recess 1208 with a bayonet latch 1206 (see Figure 12C). Pawl 1300 has a

latch aperture 1308 that cooperates with the bayonet latch 1206. The recess 1208 is semi¬

circular (see Figure 12A) and the leading edge 1310 of the pawl 1300 snaps into the

recess. The recess is also wide enough (see Figure 12B) to accommodate the entire

leading edge 1310 of the pawl 1300. This mounting arrangement provides a stable mount

for the pawl 1300, allows the pawl 1300 to pivot within a predetermined angular range,

and allows easy installation of the pawl 1300.

Returning to Figure 10, after the pawl 1300 has been installed into the mounting

bracket 1200, the mounting bracket 1200 has an aperture 1204 which fits radially over the

larger lower portion ofthe stepped central shaft 1006. The height adjuster 1500 has a

central aperture 1502 and a central boss 1504. The central aperture 1502 slides over the

larger lower diameter portion of the central shaft 1006. The central boss 1504 on the

height adjuster 1500 is used to receive the aperture 2602 on cam control member 2600.

The height adjuster also has a finger actuator 1506 which extends out of slot 120 (see

Figure 1). This finger actuator is used by an operator to adjust the swing arc of the swing.

Although the discussion and Figure 10 show the cam control member 2600 being

assembled, the assembly process would be the same for the other control member 1600

(see Figure 17A and associated discussion) and its associated height adjuster 1500.

The rocker arm 1700 mounts on the upper smaller diameter portion of the central

aperture 1502 via a cylindrical tube 1710. The step prevents the rocker arm 1700 from

moving further towards the cam control member 2600. The cylindrical tube 1710 of the

rocker arm 1700 also allows the rocker arm 1700 to receive the narrow mounting tube

1460 of gear 1400. In essence, the cylindrical tube 1710 of the rocker arm 1700 bridges

over the narrow mounting tube 1460 of gear 1400 and the upper smaller diameter portion

of the central shaft 1002. The narrow mounting tube 1460 and the upper smaller diameter

portion of the central shaft 1002 have the same diameter and contact each other within the

cylindrical tube 1710. When the device is completely assembled, only the driving hanger

1000 and gear 1400 contact the shaft 210 (not shown in Figure 18). All of the rest of the

components are mounted radially outward of the shaft 210 (not shown in Figure 18).

Figure 13 shows the device after it has been fully assembled. This is a view of the

assembly from the main spring 300 looking out towards the escapement. The basic

geometric relationships can be gleaned from the figure. In addition to the apparent

angular relationships, the device also operates on two different axial planes. The height

adjuster 1500 and the control mechanism 1600 operate in a plane rearward of gear 1400.

The fingers 1 102 and 1302 also operate on this axially rearward plane. The gear 1400

generally operates in a plane located axially inward (towards the center ofthe swing) of

the control mechanism plane. Chisels 1 1 4 and 1304 operate in the same plane as gear

1400.

An overview of the swinging motion in accordance with the broad features o the

invention is shown in Figures 14A - 14D. Figure 14Λ shows the swing seat 1 16 near its

extreme forward position. At this position, the seat 1 16 is just beginning to stop and

move rearwards in a descent. Figure 14B shows the swing at bottom dead center. Here

the swing has the greatest velocity and no potential energy. At this point, the swing is

just beginning to move vertically upwards or ascend. Figure 14D shows the seat 1 16 near

its absolute maximum rearward position. After the swing reaches the absolute maximum

rearward position, the swing will then begin to descend towards bottom dead center.

The preferred embodiment applies to the torsion energy contained in the main

spring 300 during one of its forward swinging descents towards bottom dead center. In

other words, the invention contemplates the application of the main spring's 300 torsion

energy in the same direction as the motion of the scat 1 16. The invention also

contemplates the use of an escapement mechanism to carry out this intermittent

application of power from the main spring 300 to the scat 1 16.

In accordance with the invention. Figure 14 generally shows a preferred

conceptual diagram of the selective, time-varying interconnection between the swing and

the main spring. For example, Figure 14A shows the position ofthe seat 1 16 when the

user has pulled the swing forward. In this forward position, the swing freewheels (i.e. the

swing is not attached to the spring). As the seat 1 16 is released, the seat 1 16 begins to

travel rearwards. Eventually, the seat will reach the position shown in Figure 14B. In

this position the swing engages and connects to the main spring and begins its rearward

ascent as shown in Figure 14C. The main spring is biased in a forward direction, in other

words, the spring, when engaged to the swing, tends to move the swing in the forward

direction.

As the swing continues rearward, the momentum of the swing counterwinds (i.e.

tightens) the spring until the swing apex is reached. It is during this time, when the seat is

in a rearward position but traveling in a forward direction, that the main spring releases

torsional energy into the swing. As this swing passes the bottom the swing arc, the main

spring disengages from the swing. The swing then begins to freewheel and will repeat

this cycle. It should be appreciated that the disengagement point on the forward swing

will preferably occur after the swing passes the engagement point on the forward swing.

This, in effect, allows the spring to unwind and transfer energy to the swing.

The preferred embodiment ofthe escapement device is shown in Figures 15A -

15D. Turning to those figures, four elements provide this gradual and intermittent release

of spring energy. A pawl 1300 which includes a pawl finger 1302, a pawl chisel 1304

and a pawl safety 1306 are disposed near the circumference of a gear 1400.

A dog 1 100 which includes a dog finger 1 102, a dog chisel 1104 and a dog safety

1 106, is located at a different circumferential location from the pawl 1300. The dog 1 100

is also located near the circumference of the gear 1400 similar to the pawl 1300. The dog

1 100 is mounted to the driving hanger 1000. The driving hanger 1000 rotates about the

same axis as gear 1400 as the child swings back and forth. Dog 1 100 rotates with the

driving hanger 1000 as the driving hanger rotates. Dog 1 100 orbits about the gear 1400

and remains a fixed radial distance from the axis of rotation of the gear 1400.

The preferred embodiment includes a safety device which prevents the main

spring 300 from rapidly unwinding. In the past, motor springs of this type would

occasionally run away, or rapidly unwind. This condition generally occurred because one

of the chisels (either 1304 or 1 104) failed to properly engage gear 1400. When prior art

springs were free from any rotational support they would unwind so rapidly that the

chisels 1 104 or 1 04 would float and could not engage the rapidly unwinding spring.

The preferred embodiment, best seen in Figure 13, includes a device which

prevents this condition (floating) by forcing chisels back into engagement with the

exterior teeth 1420 of gear 1400. Both the pawl 1300 and the dog 1 100 have safety

catches 1306 and 1 106 respectively. These safety catches are disposed radially inward

and opposite chisels 1 104 and 1304. When an unintended rapid unwind condition occurs,

the safety catches 1 106 and 1306 bounce off interior gear teeth 1424. This bounce causes

the pawl 1300 and the dog 1 100 to violently jerk radially inward about their respective

pivots. This jerk forces either chisel 1 104 or chisel 1304 into engagement with the

exterior gear teeth 1420 and prevents further unintended unwinding ofthe main spring

300. Returning to Figures 15A - 15D, a rocker arm 1700 includes an upper arm 1704, a

lower arm 1702 and a counter weight 1706. The rocker arm is disposed in a manner

which allows the upper arm 1704 to touch the pawl finger 1302 of the pawl 1300 and

allows the lower arm 1702 to touch the dog finger 1 102 ofthe dog 1 100.

The operation of the escapement mechanism will now be described. Recall that

the pawl 1300, does not move and is rigidly attached to ground or housing 102. See

Figure 13. Recall that the dog 1 100 is rigidly mounted to the second hanger 1000 and

orbits about gear 1400 in an arc that roughly corresponds to the swinging of the child. In

other words, the fulcrum 1 108 (or pivot point about which the dog pivots) moves in a

circumferential arc that corresponds to the arc described by the lower arm 1002 and the

swinging motion of the child (see Figure 13). The rocker arm 1700 is biased in a

clockwise direction by counter weight 1706. Finally, gear 1400 is fixed to the main

spring 300 which biases the gear 1400 in a clockwise direction.

Given these basic physical relationships, this discussion will describe one power

stroke or increment advancement of the escapement mechanism. In other words, this

discussion will describe the workings of the escapement mechanism as the child swings

from an extreme forward position (a position near Figure 14 A) to an extreme rearward

position (a position near Figure 14C) to an extreme forward position (a position near

Figure 14A) and back to a rearward position (a position near Figure 14C).

7. Start: the child is at a forward position.

This position is shown in Figure 14A and 15A. At this forward position the dog

1 100, rigidly related to the driving hanger 1000, is not connected to the gear 1400 or the

rocker arm 1700. The counter weight 1706 of the rocker arm 1700 holds the pawl 1300

engaged to gear 1400. As seen in Figure 15 A, the upper arm 1704 of rocker arm 1700

contacts the pawl finger 1302 and pivots the pawl 1304 of the pawl 1300 into engagement

with a specific gear tooth 1410. The pawl 1300 prevents rotation of gear 1400. In

comparing Figures 14A and 15A, it should be noted that Figure 14A shows the swing

drawn much further forward than Figure 15 A for clarity. The seat will swing forward,

come to an extreme forward position, and begin to travel rearwards.

II. The dog engages the gear os the swing is

near bottom dead center.

Referring to Figures 14B and 15B, this is about the position that the dog 1 100

engages gear 1400. As the seat travels rearwards, the dog 1 100 will orbit gear 1400 in a

counter clockwise direction. Eventually, the dog finger 1 102 of the dog 1 100 will contact

the lower arm 1702 of the rocker arm 1700. This will cause the dog 1 100 to pivot

towards gear 1400 and the dog chisel 1 104 will engage gear 1400. The dog 1 100 is only

connected or engaged to the gear 1400 after the lower arm 1702 of the rocker arm 1700

pivots the dog chisel 1 104 ofthe dog 1 100 onto the gear 1400. The momentum of the

seat causes the dog finger 1 102 to pivot the dog 1 100. The point at which the dog 1 100

engages gear 1400 is called the engagement point.

///. The swing begins to travel rearwards against the

torsion force ofthe motor spring.

Figures 14C and 15C show the mechanism after the dog has been engaged to the

gear 1400 and about the time the pawl 1300 releases the gear 1400. After the dog 1 100 is

engaged to the gear 1400, the dog finger 1 102 drags the lower arm 1702 opposite of the

rocker arm 1700. At this time, when the lower dog 1 100 is engaged to gear 1400, the seat

1 16, the lower dog 1 100, the gear 1400 and the rocker arm 1700 all move together in

unity. Again, it should be noted that the Figures 14C and 15C are drawn in exaggerated

positions for clarity.

Remembering that the rocker arm 1700 is now rotating with gear 1400, the upper

arm 1704 of the rocker arm 1700 scrapes along the inside of the pawl 1300 and pivots the

pawl chisel 1304 of the pawl 1300 out of engagement with the gear 1400. At this time,

with the pawl chisel 1304 is out of engagement with the gear 1400, the dog chisel 1 104

on the dog 1100 is the member which primarily keeps the spring motor 300 from rotating.

As the momentum of the seat 116 continues to move the related components

rearward, the system starts to move against the torsion force of the motor spring 300.

Eventually, the torsion force o the motor spring 300 will overcome the momentum of the

seat 1 16, and the seat 1 16 will reach its rearward apex and begin to move forward. The

power ofthe spring, along with the release of gravitational potential energy of the seat,

drives the seat forward.

IV. The system travels forward and the pawl chisel

advances one tooth.

Figures 14D and 15D show the mechanism as the system is moving forward and

as the pawl 1300 advances one tooth as it engages the gear 1400. When the system is in

the rearward position, but traveling forward, the rocker arm 1700 is held against the dog

finger 1 102 by the gravitational biasing force ofthe counter weight 1706. During

rearward motion, in contrast, the rocker arm 1700 is fixed by the momentum ofthe seat

and the dog finger 1 100. As the seat 1 16 continues to move forward, the upper arm 1704

of the rocker arm 1700 will eventually hit the pawl finger 1302 of the pawl 1300. This

will pivot the pawl chisel 1304 of the pawl 1300 into engagement with the gear 1400.

Specifically, as the pawl chisel engages gear 1400, the pawl chisel 1304 will advance one

tooth and engage tooth 1412.

The advancement of the dog chisels 1 104 and 1304 about the circumference of the

gear 1400 is accomplished by carefully designing the rocker arm 1700 and the relative

positions of dog 1 100 and pawl 1300. The rocker arm 1700 is designed in a way that the

angle between the upper arm 1704 and the lower arm 1702, advances the dog 1 100 and

pawl 1300 one tooth when there is a "hand off from one finger to the other finger. This

"hand off concept will be explained in greater detail.

Generally, there are two important structural relationships in the mechanism.

First, the rocker arm 1700 must always rest on one of the fingers: either the pawl finger

1302 or the dog finger 1 102. Second, the gear 1400, which is torsionally spring biased in a clockwise direction, must always be supported (or prevented from rotating) by one of

the chisels 1304 or 1 104. The intermittent advancement of gear 1400 is based on these

two fundamental structural relationships: the necessity that the rocker arm 1700 is always

supported by one ofthe fingers 1302 or 1 102, and the necessity that the gear 1400 is

always supported by one of the chisels 1304 or 1 104. As the rocker arm 1700 engages

one pawl, it simultaneously disengages the other pawl. Given that one of the fingers

supports the rocker arm, a hand off is when there is a change in which finger supports the

rocker arm. From the discussion above, an important consequence of this hand off is that

the new finger which supports the rocker arm also becomes the pawl which supports the

gear. Restated again, we can conclude that the dog which is supporting the rocker arm is

also the dog which is supporting the gear at that time.

Returning to physical structure ofthe preferred embodiment, every time there is a

change in which finger supports the rocker arm (i.e, a hand off), the mechanism is

deigned so that the newly engaged pawl will engage the gear 1400 one half (Vi) of a tooth

forward, in the clockwise direction (the motor spring 300 biased direction). In the

preferred embodiment the hand offs work like this:

(1 ) As the swing is swinging forward, the pawl 1300 is supporting the gear 1400

and the dog 1 100 free wheels forward. This is shown in Figure 15A.

(2) As the swing moves rearward from a forward location, the dog 1 100 will

engage the lower arm 1702 of the rocker arm 1700 and the pawl 1300 will be released. A

hand off has just occurred, and the mechanism advances V a tooth in the spring biased

direction (clockwise in Figures 15A - 15D). This hand off is shown in Figure 15B.

(3) As the swing moves forward from a rearward location, the upper arm 1704 of

the rocker arm 1700 will contact the pawl finger 1302 of the pawl 1300, this will cause

the pawl 1300 to pivot towards gear 1400 and the pawl chisel 1 04 will engage gear

1400. At this point, the dog 1 100 will pivot away from gear 1400 and the dog chisel 1 104

will disengage from gear 1400. This is shown in Figure 15D. Another hand off has

occurred and the gear 1400 has advanced V a tooth.

If the two hand offs at step (2) and step (3) above are added together we get: Vi a

tooth + Vi a tooth = 1 tooth. In other words, two hand offs allows the gear 1400 to

advance one tooth. In each swing cycle or period of motion (maximum forward position

to maximum rearward position back to the maximum forward position) there are two

hand offs as discussed in steps (1) through (3) above. So the relationship between swing

cycles or periods and gear advancement is 1 : 1. In this embodiment, the mechanism

advances the gear one tooth every swing cycle or period.

Another feature ofthe preferred embodiment is to allow height adjustment. The

preferred embodiment includes a height adjusting feature that can regulate the maximum

height of the seat as it swings back and forth. The invention also allows the user to

change the maximum seat swing height during operation of the swing.

A control member works in conjunction with the escapement mechanism

discussed above. Basically, the control member prevents the motor spring 300 from

imparting rotational energy to the seat 1 16 of the swing unless the seat is oscillating at an

amplitude less than a pre-set desired maximum. In other words, if the swing is swinging

above a preset maximum, the control member will prevent the spring from imparting

rotational energy to the swing. The control member does this by interrupting the normal

operation of the escapement mechanism discussed above.

A preferred embodiment of he invention is shown in Figures 16A - 16F. The

height adjustment mechanism adds several additional elements to the escapement

assembly discussed above. A control member 1600 with an oval aperture 1602 is

mounted on a height adjuster 1500 (not shown in Figures 16A - 16F), as discussed above.

The control member 1600 has two arms, a first arm 1604 and a second arm 1606 The

control member also has a triangle 1608. The height adjuster also has a movable stop

1508. Referring back to Figure 10, when the user pivots the height adjuster 1500 with the

finger actuator 1506, then that will change the angular position of the adjustable stop

1508.

Returning to Figures 16A - 16F, the first arm 1604 of the control member 1600

contacts a fixed stop 1206 (see Figure 16B). Preferably, this fixed stop 1206 is a shoulder

of the mounting bracket 1200. The second arm 1606 of the control member 1600 contacts

the adjustable stop 1508. Now the operation of the device will now be described.

Generally, if the seat 1 16 of the swing is swinging higher than a preselected

maximum height, the control member 1600 forces the dog 1 100 to engage the gear 1400

at the same tooth it last left gear 1400. In other words, if during the last cycle of the

swing, the dog 1 100 left tooth 1450, the control member would force dog 1 100 back into

tooth 1450 if certain operating conditions are met.

Figure 16A shows the seat 1 16 (and therefore the dog 1 100) moving forwards. As

the dog 1 100 moves forward, it contacts triangle 1608 of the control member 1600.

When the dog 1 100 hits the triangle 1608, the control member will want rotate with the

dog 1 100 in a clockwise direction. However, because the second arm 1606 contacts the

adjustable stop 1508, the control member 1600 is prevented from rotating any further and

then the triangle 1608 and the control member 1600 hop over the dog 1 100 because the

oval hole 1602 allows this radiai motion. Because of this, the dog 1 100 is now located

forward, or to the left of the triangle 1608.

Figure 16B shows the dog 1 100 traveling rearwards. This Figure roughly

corresponds to Figure 15B. However, because ofthe control member 1600 and especially

the location of triangle 1608, the normal escapement operation discussed in above and

shown in Figures 15A - 15D is interrupted. As shown in Figure 15B, normally dog finger

1 102 would contact the lower arm 1702 of the rocker arm 1700. This contact between the

lower arm 1702 and the finger 1 102 would pivot the dog 1100 into contact with the gear

1400. However, because the triangle 1608 of the control member 1600 is disposed

forward of the lower arm 1702, the triangle 1608 instead of the lower arm 1702, pivots

the lower dog 1 100 into engagement with the gear 1400.

Because the control member 1600 has interrupted the normal operation of the

escapement, discussed above, and because the control member 1600 forces the dog 1 100

into contact with the gear 1400 before (i.e. circumferentially or torsionally forward of) the

lower arm 1702 o the rocker arm 1700 would normally engage the dog 1 100 to the gear

1400, a normal hand off has not occurred. This means that the control member 1600 has

prevented the dog 1 100 from advancing 1/2 a tooth on gear 1400.

The shape ofthe dog finger 1 102 (concave facing rearwards, concave facing the

triangle) prevents the control member 1600 from hopping over the dog finger 1 102

initially. The first arm 1604 ofthe control member 1600 is also supported by the fixed

stop 1206 which prevents the control member 1600 from rotating. These two design

features provide enough force to pivot the dog 1 100 into contact with the gear 1400 but

also does not rigidly fix the control member 1600 in position in view of the oval aperture

1602.

Figure 16C shows the dog 1 100 in a position slightly further rearwards than is

shown in Figure 16B. In Figure 16C, the dog 1 100 has moved rearwards of triangle 1608

because the dog finger 1 102 has pushed the control member 1600 upwards, l he oval

aperture 1602 accommodated this radial motion. After the dog 1 100 has moved

rearwards or to the right ofthe control member 1600, the dog 1 100 eventually engages the

lower arm 1702 of the rocker arm 1700. During this rearward travel of the dog 1 100, the

system functions the same as the normal escapement shown in Figure 15C. The pawl

1300 disengages, and the seat 1 16, the dog 1 100, the rocker arm 1700 and the gear 1400

all travel together rearwards against the torsion force of the main spring 300.

Figure 16D shows the dog 1 100 as it is traveling forward and shows the hand off

ofthe rocker arm from the dog 1 100 to the pawl 1300. Because the dog 1 100 did not

advance on the gear 1400 (by moving to the adjacent tooth) on this cycle, the pawl 1300

will not advance either. Remember that the engagement of pawl 1300 is dependent on the

engagement of dog 1 100. Because of there has not been an advance this cycle, the main

spring 300 will not unwind and will not transfer energy into the swing, and the main

spring 300 will maintain or conserve its energy level.

What has just been described and shown in Figures 16A - 16D is the situation

where the control member 1600 interrupts the normal operation of the escapement.

Figures 16E and 16F show the situation where the control member 1600 does not affect

the normal operation ofthe escapement.

Figure 16E shows the dog 1 100 in its maximum forward travel. Note that in this

Figure, unlike Figure 16A above, the dog 1 100 does not travel forward of the triangle

1608 of the control member 1600. In other words, the dog 1 100 remains rearward ofthe

triangle 1608 at all times. Because of this, the triangle 1608 docs not have the

opportunity to interrupt the normal operation of the escapement and the dog 1 100 will

pivot onto the gear by the normal escapement mechanism. The lower arm 1702 of the

rocker arm 1700 will pivot the dog 1 100 into engagement with the gear 1400, and, as

discussed above, will advance the gear 1400 one tooth. This allows the spring to unwind

and provide power to the swing as the swing travels forward.

We can summarize the operation of the control member 1600 by considering the

relative positions of the dog 1 100 and the triangle 1608. If the dog 1 100 is ever to the

left, or forward of the triangle 1608, the control member 1600 is "in play" or functions on

that cycle. The dog 1 100 has moved to the active side of the triangle 1608. If the dog

1 100 remains rearward of the triangle 1608 at all times, then the control member is "out

of play" and the control member 1600 does not function that cycle. The dog 1 100

remains in the inactive region (i.e. to the right or rearward of triangle 1608).

The user can control the height of the swing indirectly with this arrangement. By

changing the position of the height adjuster 1500 and the moving stop 1508, the user also

changes the position of the triangle 1608. The user can control when the dog 1 100

engages the gear. The further forward the triangle 1608 is moved the higher the swing

will travel. This is because the control member will only be able to interrupt the normal

operation of the escapement on high swings (far forward advancements of dog 1 100).

A most preferred embodiment of the height adjustment mechanism is shown in

Figures 18A - 18G. Figure 17 shows the preferred cam control member 2600. The cam

control member 2600 has an oval aperture, similar to the normal control member. The

cam control member 2600 has an arm 2604 and a cam surface 2606. Cam control

member 2600 also has a cam face 2608. Instead of a triangle 1608, the cam control

member uses the leading edge or face 2608 of a cam to interact and pivot the dog finger

1 102 into engagement with gear 1400.

The cam mechanism is a modified version of the control mechanism 1600

discussed above. Instead of the triangle 1608 found on the control mechanism 1600, the

cam mechanism has a cam face 2608. The cam face 2608 corresponds to the forward face

of the triangle 1608.

The cam moving stop 1510 operates on the same side of the gear 1400 as the fixed

stop 1206. The cam moving stop 1510, similar to moving stop 1508, controls the location

ofthe cam face 2608. In the present cam embodiment, the location of the cam face 2608

relative the dog 1 100 determines whether the cam member 2608 is active or inactive.

Turning to Figures 18A - 18F, the cam mechanism functions in the same way as

the control mechanism 1600 except for a few modifications. Figures 18A - 18F

correspond to Figures 16A - 16F. First, as noted above, the triangle 1608 has been

replaced with a cam face 2608. The second arm 1606 has been eliminated. The cam

member 2600 has a first arm 2604 similar to the control member's arm 1604. The cam

member 2600 also has a cam surface 2606. The height adjuster 1500 has also been

modified. In the control member 1600, the height adjuster 1500 had a movable stop 1508

disposed opposite the fixed stop 1200. However, the height adjuster 1500 adapted for use

with the cam member 2600 has the fixed stop moved to a location which is angularly

spaced from the fixed stop 1200. See Figure I 8D.

The cam member 2600 operates in a manner similar to that ofthe control member

1600 with a few variations. The cam face 2608 is designed in a way which allows it to

actuate the dog finger 1 102. This cam face 2608 replaces the triangle 1608 as the item

which pivots the dog 1 102. After engagement, the dog finger 1 102 slides over the cam

surface 2606. See Figure 18C.

As the dog finger 1 102 continues to slide over the cam surface 2606, the dog

finger 1 102 eventually engages the lower arm 1702. When the dog finger 1102 is

engaged to the lower arm 1702, the system which includes the dog 1 100, the rocker arm

1700 and the gear 1400 will all move in unison, as the normal escapement. The system

will travel rearwards against the torsion force ofthe main spring 300 and will eventually

reach a maximum rearwards position. After reaching this maximum rearward position,

the system will then start to travel forwards.

Remembering that both the control member 1600 and the cam member 2600

operate only during rearward travel of the swing and dog 1 100, forward movement

experiences normal escapement operation. This forward movement is shown in Figure

18D. The normal escapement operation dictates that, as the system travels forward, the

upper arm 1704 ofthe rocker arm 1700 will actuate the finger 1302 of the pawl 1300.

The pawl 1300 will then pivot, and the chisel 1304 of the pawl 1300 will engage the gear

1400. Since, on the rearward travel, the dog 1 100 engaged the same tooth that it left the

cycle before, the pawl 1300 will engage the same tooth that it left on the previous cycle

also. This is similar to the operation ofthe control member 1600 on its forward travel.

See Figure 16D. Because the pawl 1300 enters the same tooth that it left the previous

cycle, the gear 1400 does not rotate and therefore, the main spring 300 does not expend

any energy this cycle.

Turning now to Figures 18E and 18F, similarly to the control mechanism 1600, if,

on the forward swing, the finger 1 102 of the dog 1 100 does not move forward of the cam

face 2608, then the cam member 2600 is inactive or "out of play." In other words, the

cam face 2608 does not actuate the dog 1 100 into engagement with the gear 1400.

Rather, the device will function as the normal escapement mechanism discussed in detail

above. It is apparent that the two control mechanisms control the height of the swing by

determining when rotational power is added to the motion of the swing. While both

mechanisms function well, the cam control mechanism 2600 is preferred. Although the

cam control mechanism 2600 introduces a little more friction into the system (because the

dog finger 1 102 slides on the cam surface 2606) it is a preferred design for several

reasons. First, the cam control mechanism 2600 greatly reduces the irregular and

confusing "clicking" sound. The cam control mechanism uses smaller parts, avoids lost

motion and allows easy assembly.

It will be apparent to those skilled in the art that various modifications and

variations can be made in the motor mechanism for a child's swing o the present

invention without departing from the spirit or scope of the invention. Thus, it is intended

that the present invention cover the modifications and variations of this invention

provided they come within the scope ofthe appended claims and their equivalents.