TW201946601A - Elevating walker chair and convertible seat - Google Patents

Abstract

A convertible seat and an elevating walker chair having a convertible seat. The chair elevates by a parallelogram mechanism that can be functionally connected to a seat deployment mechanism to allow the seat to transform between a saddle and seat upon changes in saddle/seat elevation.

Description

Lifting walking chairs and convertible seats

The present invention relates to a device for assisting an individual, and more particularly to lifting a walking chair and a convertible seat.

The conventional devices used to assist individuals with mobility difficulties are divided into two categories—walkers and wheelchairs—and several intermediate combinations that can additionally help passengers to stand up and walk.

The conventional walking device increases support and stability, but will involve the user's hands and arms to a certain extent, making it impossible to carry or manipulate anything while moving. Four-wheeled walkers can also include seats, but they cannot be used unless the user stops or turns around.

Walkers are slow and isolated, and are set aside for inherent danger when sitting down.

Most users of unpowered and powered wheelchairs are still sitting for long periods of time, which is detrimental to muscle, circulation and heart health.

"Lifting" wheelchairs use large motors to lift seated occupants to a standing position, and some lifting wheelchairs can provide occupants with the power to move around in an upright position, but will not enhance movement Ability or need any muscle contribution.

Another intermediate category of assistive devices includes "standing" walkers, which partially lift passengers and encourage them to walk.

Unfortunately, existing standing walkers inhibit user interaction with the outside world-either entering large structures at front and rear entrances, or having awkward uncomfortable folding seats, procedures, and restraints. And users must still use their legs and arms to raise a significant percentage of their weight in order to stand up from a sitting position to a standing position.

Lack of a means for individuals with restricted mobility to sit and stand at will, walk in a natural gait, and interact with their environment safely (easily cooking, cleaning, washing, dressing, and traveling), all of which are expected Highly advanced, and using at least a small part of the individual's own energy and previous athletic ability.

A lift chair is disclosed that can be beneficial to people with limited mobility due to impaired muscle tissue, coordination, or balance, or to strong individuals who must perform tasks that require help. The disclosed elevated walking chair provides a novel hybrid of riding and walking, which promotes normal gait, but will generally prevent falls. An illustrative embodiment allows a user to walk, step, and glide, and sit and stand relatively easily—all of these actions are performed in a functionally balanced and weightless or near-weightless condition—without leaving Device and free hands as needed for other purposes.

The disclosed embodiment includes a seat deployment mechanism and a lifting mechanism functionally connected to the seat deployment mechanism. The seat deployment mechanism converts a convertible seat between a seat configuration and a seat configuration. The lifting mechanism raises and lowers the walking chair. When functionally connected, the lifting mechanism causes the seat deployment mechanism to change between a seat and a vehicle seat in accordance with the height to which the lifting walking chair is raised or lowered.

This application claims priority to the following application: the title on March 29, 2018 filed it as "walking chair lift, lifting mechanism and seat (Elevating Walker Chair, Lifting Mechanism And Seat) ," US Provisional Application No. 62 / No. 649,746; title on March 29, 2018 made the application to "lift chair (lifting chair)," US provisional application No. 62 / 649,809; and the title on March 22, 2019 filed it to "upgrade institutions and chair (Lifting mechanism and chairs) US provisional application / No "62nd 822,496, all of such application to the Department hereby incorporated by reference.

FIG. 1 illustrates an isometric view of a lifting walk chair 1 according to an illustrative embodiment, visible in its lifted “walking” position. The lifting walk chair 1 includes a wheeled frame 2 attached to a lifting chassis 3 The components of the lifting chassis 3 pivot the lifting extension frame 4a downwards and the attached lifting pillars 4 with a force and elasticity. When the frame rises towards the upper limit of its parallelogram support process, the force is Calibration to allow the folding seat / seat 6 to balance the occupant by counteracting the occupant's weight to provide a substantially "weightless" condition.

An armrest / seat back frame 8 is attached to the seat mounting block 7 (shown in FIG. 10) and supports the armrest assemblies 9a, 9b. The left and right folding seat wings 6a, 6b are shown as folded down in the "seat" position, which is suitable for elevated seating. The armrests 6a, 6b are shown in a retracted position, but can be deployed forward as appropriate, which can assist in supporting the torso in one of the positions for walking. The sufficient clearance of the seat relative to the floor frame 2 (including the side and underside of the seat) is provided to allow a walker's legs and feet to step backwards or, if necessary, contact the ground on the side.

Since the embodiment of the elevated walking chair allows walking without the frontal obstacles found in traditional walkers, a user will maintain forward access to sinks, stoves, kitchen cabinets, etc. at various heights (including a standing height), And will be able to manipulate between the two.

FIG. 2A to FIG. 2B are side elevation views of the lift walking chair 1. FIG. 2A shows a seat / seat 6 that is deployed to form a chair when the lift walking chair 1 is in its lowest seat height position ("sit-down mode"). The height of the chair is modified by a parallelogram device formed by the seat mounting block 7, the lower parallelogram lifting pillar 4, the upper parallelogram pillars 5a, 5b, and the lifting chassis 3. In the sitting mode position, the lift walking chair 1 serves as a conventional chair, which may include a padded seat back and cushions for the armrests 9a, 9b as appropriate. The seat frame 2 may be formed of any suitable tough material (including carbon fiber, curved aluminum box beams, etc.). Note that the lifting pillar 4 and the parallelogram pillars 5a, 5b are curved in the illustrative embodiment shown in the drawings. These bends allow the seat to occupy space that would otherwise not be available, thereby increasing the travel distance of seat 6 compared to one embodiment where the pillars are straight.

Fig. 11A illustrates the position of the seat 6 within the curved parallelogram pillars 5a, 5b. These bends allow the back edge of seat 6 to remove obstacles to the pillars when lowering the seat. The curved lifting pillars 4 can also enlarge the available space of the seats 6. Although the lifting pillar 4 and the parallelogram pillars 5a, 5b are curved, they are configured to perform similarly to one of the configurations having straight parallelogram edges.

FIG. 2B shows the seat 6 being lifted to a selected position where a user can walk using the user's legs. The seat wings 6a, 6b are folded down to form a cone seat configuration of the seat 6. The seat frame 8 is attached to a seat mounting block and support armrest assemblies 9a, 9b. The rear wheels 17a, 17b preferably have a fixed orientation (i.e., non-rotatable) and can be attached to motor mounting plates 18a, 18b, which can be adapted to receive customary small self-sustaining motors and battery packs (not (Show) to supplement the power of feet and legs as needed, and to assist steering by applying forward and reverse torque to the rear wheels 17a, 17b. A preferred wireless joystick (not shown) can be attached to the top surface of the armrests 9a or 9b to add a small amount of forward, backward or steering motive power as needed to the extent necessary to replenish the capacity of only one body.

FIG. 3A is an isometric view of one of the lifting chassis 3 including a lifting box 14, and the lifting box 14 accommodates the elastic power units 15 a, 15 b, and 15 c (shown in FIG. 3B). The extendable shaft members 56a, 56b, 56c of the elastic power units 15a, 15b, 15c are shown as engaging the receiving rod 13. The receiving lever 13 pivots on a wheel shaft 13a in the end of the lifting extension frame 4a. The lifting extension frame 4a is connected to the lower parallelogram lifting pillar 4 and pivots the lower parallelogram lifting pillar 4 upward to lift the seat / seat 6 and Its human payload.

FIG. 3B includes a perspective view of the elastic lifting box 14 showing the elastic power units 15a, 15b, 15c mounted inside the elastic lifting box 14, such as, for example, small and powerful gas springs. The elastic power units 15a, 15b, and 15c may be selected from a combination of completely or nearly completely balancing or offsetting the weight of the seat occupant. The cassette 14 is pivoted inside the chassis 3 around the axle 14 a so that the elastic power units 15 a, 15 b, 15 c (such as gas springs) can remain extended to the receiving lever 13. Since the elastic power unit 15a, 15b, 15c can provide a strong compression force, the elastic power unit 15a, 15b, 15c is strongly biased downward to lift the extension in the manner of a heavier occupant on the short end of a seesaw. Frame 4a. A heavier rider on the short end of the seesaw can offset a lighter rider on the longer end. In fact, for example, since the effective pivot length of the lifting pillar 4 in this embodiment is about 6.9 times the pivot length of the lifting extension frame 4a, a predetermined set of elastic power units 15a, 15b, 15c The sum of the applied forces can be divided by their ratio to indicate the approximate weight of one person that it will support. In order to get closer, the weight of seat 6 must be included, minus about half of the individual weight of the human legs-but in practice it has been found that the weight of one person plus about 10 lbs will provide a good boost for the net elastic unit. Instruction, this will successfully make people "float" in an equilibrium condition that makes people stand and sit as if they were near a "zero gravity" state.

The following chart illustrates the net lift values of some available gas spring-type elastic power units that can be illustratively used in an embodiment of a lifting mechanism. It can be seen that when each box is pressed to provide an expansion force of up to 691 lbs., The strongest gas spring on this list will actually lift one of the net payloads of almost 100 lbs. (Effective in lifting the parallelogram forward) At the load end).

Although the external air springs (15a and 15c) should be selected to be equivalent (to avoid the load on the receiving rod 13 and the extension frame 4a from being greatly off-center), it is obvious that the combination of obtainable net lift values can be easily specified as Roughly anyone "floats" with a weight between 80 lbs. And 300 lbs.

For example, the combination of the elastic power units 15a, 15b, and 15c may include a single central spring, two equivalent outer springs, or a combination of an inner spring and one of two equivalent outer springs. Other numbers of individual elastic power units may be used; however, off-center forces should preferably be avoided. In one illustrative embodiment of the lifting mechanism, the combination is selected to equal the weight of the rider plus approximately 10 lbs.

The following chart shows the parameters of an illustrative gas spring. The total lift is the inherent lift of the spring. The net lift is the total lift divided by 6.9, which is an illustrative ratio between the length of the lifting pillar 4 and the length of the extension frame 4a. In this illustration, all springs have a shaft history of 3.15 inches.

Net lift (lbs.) Total lift (lbs.)
6 40
12 81
16 94
18 121
23 157
25 173
32 220
42 292
50 346
75 519
100 690

Different power springs or other elastic power units usually have different outer diameters or other sizes. In order to easily switch the elastic power unit, a standard connection or other adjustment can be present in the lifting box, and an adapter (such as a standard diameter sleeve) can be provided to make all the elastic power units appear in phase with the elastic lifting box 14 One form of content.

FIGS. 4A to 4B are side elevational views of the chair lift 1, which illustrate two alternate positions of the box wheel axle 14 a along the slot 14 b, and the two alternate positions generate a difference in payload enhancement efficiency. The term "iso-elasticity" refers to an exemplary lifting force profile from the lowest to the highest course obtained by a parallelogram arm designed to float similar to the offset force profile of a Steadicam® camera stabilizer. For the promotion of humans, isoelasticity may be desirable, so that humans do not need muscle strength to stand up from a sitting position to a standing position, but unlike the camera payload, a seated person stands up and is supported by the seat. Weight changes occur during this transition. In practice, although most of a person's weight is initially pressed on the seat, the remaining weight (about half of the weight of the legs and feet) is actually pressed on the bottom surface, and this proportion will change as people prepare to stand up . When a person leans forward to get up, significantly more leg weight is transferred from the seat to the bottom. The result is that in this transition, one person is actually "equilibrium" or effectively makes one person "zero gravity". The lifting force provided must also be changed in the same way, and it is found that a consistent "equival elasticity" lifting force can initially rise. Speed, and rise too slowly when the occupant supported by the seat approaches a standing position. Therefore, the lifting force profile can be changed to provide a larger lifting force in an initial part of the journey from the sitting mode to the standing mode compared to the lifting force applied by the lifting mechanism when the occupant approaches the standing. The lifting force of this change may gradually increase from the sitting mode to the standing mode of a chair lift, instead of changing in insignificant increments.

FIG. 4A illustrates an angle 20 between the centerline 19 of the lifting extension and the force applied along the centerline 21 of the cassette, which angle may be optimal. In this illustrative embodiment, this angle is reached when the cassette wheel axle 14a slides to the "rear" of the adjustable cassette of the positioning slot 14b. In this embodiment, the obtained 29 ° lifting angle will produce a "super-elastic" lifting force curve, which will cause an inactive payload to drop excessively at the bottom of the stroke and rise greatly at the maximum height. Humans with lifting legs in contact with the bottom surface are preferred. An illustrative angle range is from about 27 ° to about 31 °. The resulting "super-elasticity" can generate a suitable lifting force for two reasons: first, to provide a limited course with a high "seesaw" ratio of force to payload weight. Secondly, the instantaneous expansion force of the selected gas spring along the center line 21 of the cassette is applied in a direction that is optimal for lifting the center line 19 of the extension throughout the stroke. The initial 29 ° force angle is inefficient for lifting and allows the occupant to remain seated before leaning forward, thereby transferring sufficient leg / foot weight to the ground so that the parallelograms begin to point upwards. When the seat 6 reaches its maximum upward position (and realizes a seat configuration), the angle of the force applied to the short lever arm designated to lift the extension frame 4a reaches 119 °. At this extension, the gas springs 15a, 15b, 15c exert only about 0.6 of their original force, but at a relatively efficient angle with the extension centerline 19, which will make it difficult for an inactive payload to hit the upper stop. However, once the occupant's legs are close to vertical and a large percentage of their weight is placed on the seat, improving efficiency can more effectively balance the human payload.

In contrast, FIG. 4B illustrates an optimal "equival elasticity" lifting angle of 48 °. In this illustrative embodiment, this angle will uniformly lift an inactive non-human payload. However, as explained above, a dynamically changing human payload will have difficulty lowering itself to the seat height. In particular, part of the descent inertia was actually changed to start seat deployment (as shown in FIGS. 11A to 11B). And the occupant will have difficulty reaching the maximum height, because the decreasing proportion of the weight of the leg reaching the ground will effectively make it heavier. It is therefore not obvious that, although iso-elastic lift can be achieved, this may not be optimal for the very specific human equilibrium needs of a chair lift.

One of the more beneficial changes, such as one of the elastic history, is illustratively ranging from about 46 ° to about 50 °. Generally, when the lifting angle is increased above 48 °, the payload will need to add an upward or downward force externally to reach the top or bottom of the stroke, respectively, while a lifting angle less than 48 ° may cause the payload to require upward force In order to ascend from the lowest position and add downward force to descend from the maximum height.

5A to 5B are side elevation views illustrating the angle between the center line 21 of the flexible box and the center line 19 of the lifting frame when the seat 6 is at its lowest course, and the configuration is configured in each case. At 29 °, various other selected installation angles of the lifting extension frame 4a can produce similar or equivalent lifting performance. FIG. 5A illustrates a structural change according to one of the illustrative embodiments of a lift walk chair in which the lift extension frame 4a is attached to the upper parallelogram pillars 5a, 5b instead of being attached to it as in the previous drawings. Lower parallelogram lifting pillar 4. Note that the lifting efficiency may be similar or equivalent, and therefore similarly suitable for human occupants, because the angle between the centerline 19 of the lifting frame and the centerline 21 of the cassette has been constructed again to be 29 ° or approximately 29 °. This configuration can be advantageous for several reasons, including keeping the lifting assembly higher behind the back, and therefore less hindering backward foot and leg movements when striding and sliding.

FIG. 5B illustrates another illustrative change in the angular position of the lifting device. In this view, the center line 19 of the lifting extension is almost at a right angle to the longitudinal center line 58 of the portion to which the lifting pillar 4 is attached, and the elastic lifting box 14 projects straight back. Note, however, that the box centerline 21 and the hoisting frame centerline 19 again form a 29 ° angle, and therefore this version (although it is only illustrative and not particularly practical) will achieve similar or equivalent appropriate boost performance for its human payload .

As shown in Figs. 5A to 5B, the extension frame 4a can be rotated around the pivot center to any desired angle at its attachment to the lifting post 4, which is illustrated in the configuration of Fig. 5A as being at an angle of 191 ° And illustrated in the configuration of FIG. 5B as being at an angle of 115 °. The rotation of the extension frame 4a may position the lifting box 14 on the inside or outside of the parallelogram defined by the pivots 50a, 50b, 50c, and 50d as required.

The lifting mechanism including the lifting box 14, the extension frame 4a, and the associated parallelogram structure can be used in other applications in which the parallelogram lifting structure can be used, that is, not only in the chair lift described herein. In other words, the lifting mechanism described in this article is essentially an independent mechanism that can be incorporated into other devices that require the lifting function provided by the equipment. The sides of the parallelograms of such lifting mechanisms may be curved, such as the lifting pillar 4 and the parallelogram pillars 11a, 11b, or may be straight, such as in a conventional parallelogram link. The bends of the parallelogram sides can be designed to allow the best course required for a particular application. The lifting mechanism can be mounted on a shelf, a fixed or movable structure, or even a vest that a user will wear.

6A to 6C show the deployment positions of the left / right armrest assemblies 9a and 9b. When the user changes from the seat mode to the seat mode and walks, the left / right armrest assemblies 9a and 9b can be adjusted to appropriately Control the seat height and lock and unlock the rear wheels 17a, 17b. FIG. 6A illustrates a chair mode in which the armrests 9a, 9b are fully retracted to serve as a conventional armrest. Figure 6B shows the handrails 9a, 9b partially deployed. The front / rear parallelogram deployment pillars 11a, 11b have uneven lengths, and therefore will begin to change the angle of the cover plates 12a, 12b relative to the armrest support plates 18a, 18b when they swing to the side. This armrest position is suitable for "boarding" a lift chair. FIG. 6C illustrates the final forward deployment of the armrests 9a, 9b, where the non-uniform parallelogram link group swings the cover panels 12a, 12b inwardly to form appropriate restraints and armrest surfaces suitable for walking. As can be seen in FIGS. 9A to 9C, in one illustrative embodiment of an elevated walking chair, these three armrest positions will be used to actuate separate locking / unlocking of the seat height and rear wheel brakes.

7A to 7D illustrate a stepwise engagement made by a user using a novel actuated armrest control function of a lifted walking chair when a user is seated and a downward transition to one of the seat heights is achieved. In FIG. 7A, the user grasps the armrest in the extended position (this preferably has locked the rear wheel brakes) and approaches the seat. In Figure 7B, the user transfers his weight to the seat and preferably buckles his seat belt (not shown). The extended armrest position also preferably unlocks the seat height. In FIG. 7C, the user may appear to lean back slightly so that the seat is lowered while supporting the entire user weight except a few pounds. In FIG. 7D, the user has descended to the seat height, the seat wings have been automatically deployed outwards and the user pulls the armrest toward his conventional sitting position, thereby better activating the seat height lock and releasing the brake (borrow By the means illustrated in Figures 9A to 9C).

FIG. 8 illustrates the armrests 9a, 9b, which are swung forward to a position suitable for walking forward, thereby enclosing the user, providing a surface of the armrest that will facilitate walking, and (if available in the embodiment) Move the seat height lock and release the brakes. The user is presented with one of the appropriate postures for walking. Depending on the user's level of health and ability, the user can choose to lean forward further, transfer more body weight to the armrest, and step at a slightly larger step to glide between the two and further extend backwards and feet And the ground where your legs touch.

For example, one illustrative variation in height between the seated position of FIG. 7D and the step position of FIG. 8 is about 18 inches to about 34 inches.

9A to 9C show the right-hand-actuated armrest assembly 9a illustrated from the angle of the transparent top cover 12a to illustrate the position of the armrest and its various positions generated by the process of the parallelogram pillars 11a, 11b with uneven front / back length Don't activate the function. The upper left image shows the position of the above components with the arm assembly in its retracted position. The upper right image shows the armrest assembly 9a slightly shifted to the side (preferably starting to actuate the right rear wheel brake). The lower left illustration shows the armrest 9a extending completely to the side (preferably to unlock the lifting function and implement full braking). The lower right image shows the armrest 9a in its most forward position, so the top cover extends at least partially in front of a user, thereby closing, stabilizing and supporting walking activities, and better locking and lifting and actuating the right-hand wheel brake Its release. These functions are further illustrated in Figures 9A to 9C.

9A to 9C show an armrest 9a, which shows one illustrative mechanism for actuating the braking and lift-locking functions throughout the sequential armrest deployment positions shown. The crank shaft axles 37a, 37b are fixed to the front / rear armrest deployment pillars 11a, 11b, so the crank shaft axles 37a, 37b rotate in unison with the front / rear armrest deployment pillars 11a, 11b. The arrows extending from the crankshaft axles 37a, 37b shown in Figs. 9A to 9C indicate the direction of the attached arms associated with the crankshaft axles. The crankshaft arm is adapted to pull the actuation wire 36 indicated by the dotted lines on the two armrests. The dashed line shows the path of the center wire end, which can, for example, come from four conventionally terminated bicycle type brake cables (not shown). Actuated by the crankshaft axle 37a, one end of the wire 36 on each armrest is preferably adapted to actuate and release its respective side rear wheel brakes conventionally. The other end of the wire 36 on each side is driven 180 ° in the opposite direction by the crankshaft axle 37b. This can also be used via a bicycle cable (not shown) to activate two redundant seat height locks (not shown) One of them. The seat height lock may include a conventional disc brake or a hydraulic lock cylinder assembly, as well as other conventional brakes and restriction options, and is therefore preferably used to limit the upward and downward journeys of the lifting parallelogram of a pedestrian chair.

Fig. 9A shows the armrest assembly 9a, 9b in its rear seated position. The crankshaft arms associated with the crankshaft axle 37a on both armrests are oriented outwards (indicated by arrows), with their dashed brake cables 36 adjusted so that the respective left / right wheel brakes are released. The forward crankshaft arm associated with the crankshaft axle 37b on each side is oriented inward, and its brake type cable is adjusted so that the seat height is locked. FIG. 9B shows the crankshaft arms 12a, 12b swinging outward and the crankshaft arms (indicated by arrows) fixedly associated with the crankshaft axles 37a, 37b on the two armrests rotated 90 °, respectively, as shown. Both the left crank shaft arm and the right crank shaft arm have been swung forward, and as a result, the ends of the brake wire 36 have been extended and the respective left / right wheel brakes are firmly engaged. Also note that the respective left / right wheel brakes can therefore be independently controlled by their position on the same side armrest. This permits the use of instantaneous light wheel brakes independently to slow down the respective left or right wheels and help to steer during walking. Also on the left and right armrests 9a, 9b, the crankshaft axle 37b is now shown swinging back, thereby releasing its respective redundant double seat height brakes (not shown). Note that the seat height unlock can also be independently activated for a different reason, so that any armrest in the sitting or walking position (as shown in Figures 9A and 9C, respectively) can effectively prevent the seat from rising or falling; and two The armrest must be positioned to extend to the side position shown here to release the seat height lock, such that when boarding the seat or rising from a sitting position or selecting only a new middle seat position (such as the "bar stool" height), The seat / seat 6 is easily free to raise and lower the balanced occupant. Fig. 9C shows the position of the crankshaft arms associated with the crankshaft axles 37a, 37b when the two armrests are swung forward into the walking position. Note that the crankshaft arms associated with the crankshaft axle 37a are now releasing their respective wheel brake cables inward. The crankshaft arms associated with the crankshaft axle 37b respectively engage their respective seat height locks outwards, so that if two feet leave the bottom surface at any time during (for example) gliding, or if the two feet are on the optional foot pedal In the case of (not shown), when relaxed in a high fixed position, the walking is completed without dropping the seat. Note that the non-uniform parallelogram deployment of the handrails is initiated by appropriate arched arm movements that simulate the arched course of the parallelogram pillars 11a, 11b.

FIG. 10 shows the folding seat / seat 6 assembly, whose wings 6a and seat mounting block 7 are transparent to show that the seat mounting post 7a rotating in the seat mounting block 7 can promote limited dynamics of the seat / seat 6 A way of turning to clear obstacles for one of the legs of the occupant stepping backwards. The novel seat turning structure effectively narrows the width of the back of seat 6 during vigorous walking, when the other leg swings straight backwards in an unobstructed path formed by swinging away the triangular rear end of seat 6 , Alternating thigh forward unhindered. 18A to 18B show continuous bottom side views of the folded seat / seat 6 when the folded seat / seat 6 is rotated around the axis of the seat post 7a to form an alternate unobstructed backward path relative to either side. The seat 6 is preferably adapted to rotate up to at least 15 ° with respect to either side during walking, so that the wider rear portion of the seat moves away from the leg path, and the side edge of the seat that the pushing leg is in contact with becomes parallel to the lift Front and rear axis of walking chair. A baffle (not shown) or a stopper or only the sides of the seat wings 6a, 6b folded down can limit the degree of seat rotation.

FIGS. 11A to 11B respectively show the seat / seat 6 in the unfolded position and the folded position, and show the manner in which the seat wing 6b is swung upwards by retracting the wing deployment pillar 38 into a seat mode when the seat is lowered. Two such equivalent struts may be used to raise both seat wings 6a, 6b at the same time, but for clarity, only the right-hand strut 38 is shown here. FIG. 11A shows an attachment mechanism including the ball joint 39 including the upper (inner) telescopic section of the pillar 38 to the bottom side of the seat side wing 6b. FIG. 11B shows how the lower outer section of the pillar 38 is attached to a lower part of the parallelogram lifting pillar 4 by means of a ball joint 39 and a short support tube, so that the parallelogram lifting pillar 4 has upward-facing wings during seat deployment. One of the sections 6b has an accessible path. Note that when the seat 6 is raised and the wings 6b are folded down, the telescopic tube 38 is fully extended. The strut 38 only begins to lift the wings 6b when its telescopic stroke is fully retracted, because the seat 6 is close to the bottom of the deployment in which it becomes a seat mode, as illustrated by the comparison in FIGS. 11A-11B.

FIGS. 12A to 12B and FIG. 32 illustrate alternate implementations of one of the lifting walking chairs that raises and lowers the seat bracket assembly 28 between walking and seat height by means of left / right elastic components 29a, 29b and linear bearing assemblies 27a, 27b. example. FIG. 12A shows the seat 6 in a seat-up mode in which the elastic member 29b (for example, a gas spring) is fully extended so that the seat bracket assembly 28 is raised by the left / right linear bearing assemblies 27a, 27b, and the rollers are caused The backrest fabric or cover 30 is retracted upward and over the backrest roller assembly 31, and is tensioned by the left / right backrest tension pulley assemblies 32a, 32b. The forces of the elastic components 29a, 29b, such as springs and gas springs, decay linearly as the elastic components 29a, 29b extend and retract. As used herein, in order to apply force straight along the left / right linear bearing track pair 26a, 26b, the left / right linear bearing track pair 26a, 26b is not completely "equal elastic" and is fully compressed (or stretched elastically) In the case of a component, the maximum strength is increased when extended. Therefore, the linear power embodiment of FIG. 12A to FIG. 12B is suitable for a user who maintains some leg power and can supply a lack of lifting power when the seat 6 is near the top of the stroke. Figure 12B shows the gas springs 29a, 29b fully compressed when the seat support 28 reaches the bottom of the linear bearing travel and the roller back fabric 30 is extended and ready for use. The left / right foot-operated caster steering pedals 33a, 33b are fixedly associated with the rotating axles of the front swivel casters 16a, 16b and serve as dynamic pedals, which also help promote socialization through one of the lift chairs "Push" form where the rider is at eye level upwards or the participant is the same, the participant can easily push (for example) the armrest (instead of having to turn the handle backwards), and the pedals enable the rider to A caster is selectively rotated to cause the chair to "steer" following a desired path. An unaccompanied rider can also continue to "step" (skateboard style) with one leg and turn with the other leg to advance in a precise direction (such as through a narrow doorway), and when there is only one caster When steering in this way, steering link sets between casters or elaborate steering geometry are not required.

Figure 32 is an isometric view of one of the two linear bearing assemblies 27a, 27b that continues between the left / right linear bearing track pair 26a, 26b to raise and lower the seat bracket assembly 28, seat 6, The actuating armrest assembly 9a, 9b and roller back fabric 30 may also be attached to the seat bracket assembly 28. The linear bearing assemblies 27a, 27b function by means of tapered rollers mounted in contact with the opposing linear bearing track pairs 26a, 26b.

FIGS. 13A to 13B respectively show a low (seat) deployment and a lifted (seat) deployment of an illustrative embodiment of a lifted walking chair. The lifted walking chair is a user (not shown) and an elastic power payload. A support arm 35 (such as the Zero-G ™ support arm sold by Equipois LLC) or other combined weights of a balanced or balanced arm and a preferred ring frame industrial payload (such as shown in Figure 16) provides support. FIG. 16 illustrates an illustrative joint arm 52 and a ring-shaped tool holder 54. Other tool holders and arms can be used for specific applications, whether in industry or to assist individuals in their daily work. 13A to 13B illustrate lifting joint arms each having two lifting links. Each link is a parallelogram configuration having an elastic member for providing a lifting force. The aforementioned arm may have one or more lifting links. A handle or armrest can be attached to the distal end of the lifting arm, which will allow a user's hand to perform a task freely while being supported by a bracket attached to the lifting arm. This embodiment of a walking chair lift can assist in the deployment of heavy tools in an industrial environment, otherwise it can cause, for example, repeated straining of the shoulders by holding the heavy tools for extended hours of work. An industrial worker can raise himself plus the payload of arms and tools to the "seat" height to relatively easily walk between workplace opportunities, and iteratively lowers to the seat height and back again depending on the altitude of any particular task Back up.

A particular embodiment or application of lifting a walking chair may require a more perfect balance between the user and the payload, and may therefore utilize the "iso-elastic" parallelogram power embodiment illustrated in Figure 1 with the help of the "iso-elastic" The parallelogram-powered embodiment allows a occupant to easily perform a "pick and place" (also referred to as "material handling") operation. This lifting walking chair will be better configured to allow for heavy items to be picked up and transported easily and with little risk of injury by lowering a worker to the height of the chair, engaging the arms with the payload, and minimizing the legs The force stands up, moves the payload to its rest position, and hangs down to remove the arm (it can be conveniently limited to any selected maximum height). This procedure will transfer the weight of the payload being transported from hand to more powerful thighs and calves, and will "float" the worker's own weight throughout the "pick and place" operation.

FIG. 14 shows the maximum height adjustment screw 24 and the impact plate 25. The maximum height adjustment screw 24 and the impact plate 25 are used to limit one of the upper parallelogram pillars 5a, 5b so as to be appropriate for the user's inseam measurement Set the maximum seat height, and ensure that the height of the seat / seat 6 is appropriately limited to ease the user's transition from an adjacent unsupported standing position "on the seat" and to set the optimal seat height for walking.

FIGS. 15A to 15C show one illustrative embodiment of one of the folding seats / seats 6 which are bent to be ergonomically interposed between the unfolded “seat” mode and the folded “seat” mode. A form that is academically suitable for humans, and provides a narrowness suitable for male riders forward and a slightly wider width that is generally more comfortable for women. FIG. 15A is a bottom side view showing one of the seat folding and retracting cutouts 41a and 41b. The seat folding and retracting cutouts 41a and 41b allow a slightly curved plane of the seat 6. The seat 6 includes wings 6a and 6b and a central triangular portion. When the seat is folded The central triangles will be tightly connected, but still maintain the optimal narrowness as a seat in the forward area. The front / rear hinge groups 40a, 40b are shown. The front / rear hinge groups 40a, 40b are formed into a v-shape to fold into a pointed seat shape approximately 1 inch wide in the front and 6 inches wide in the rear. The front and rear components of the hinge groups 40a, 40b are positioned in line with each other, but the middle is interrupted by the left and right folding seat withdrawal cutouts 41a, 41b. FIG. 15B shows the extremely shallow curvature imposed on the entire unfolded top surface of the seat 6 as if it were cut from a cylindrical section of a very large radius. The result of the combination of this large radius, the "main" curvature and the cutouts 41a, 41b and the hinge groups 40a, 40b is a cushion shape, which can be folded into a seat shape with an exemplary narrowness as seen in Fig. 15C. Upholstery materials such as gel sections and elastic covering materials are preferably used, so the seat 6 remains narrow but is comfortably filled when folded into a seat and when unfolded into a seat. Non-upholstered saddles are also an option.

The topology of this main curve will coincide when folded and help prevent the cushion from bulging when unfolded because the radius of the fold does not increase as much as it does around a full straight hinge line. Excess material can "take shortcuts" and is pulled inwardly into the incision gap when folded and elastically released when unfolded. The strong flexible outer covering material will also help to ensure that a rider's clothing will not be caught by the sides of the cutouts 41a, 41b when they are close together. Note that as the radius of the main curvature decreases and the width of the folding back cutouts 41a, 41b increases, the folding seat becomes narrower and narrower.

19A-19B illustrate another illustrative embodiment of a convertible seat 300 that is changed from a seat configuration or mode to a seat configuration or mode. FIG. 19A illustrates the convertible seat 300 in a chair configuration. The thigh sections 308, 310 are movably attached to the seat section 302, such as by one or more hinges. In the chair mode, the thigh sections 308, 310 extend from the seat section 302 to form a sitting surface. The sitting surface may be substantially flat or contoured. Generally, the sitting surface supports a user in a sitting position in a manner similar to a chair. The saddle segment 302 has a rear portion 304 and a narrower front portion 306 extending from the rear portion 304. Thus, as shown in FIG. 19B, when the thigh sections 308, 310 are folded back relative to the seat section 302, the device forms a seat configuration. Optionally, a handrail seat frame 301 is included to attach a handrail such as 9a, 9b shown in FIG. 1 or a conventional handrail such as a handrail commonly found on a wheelchair. The configuration and positioning of the armrest mount 301 will depend on the particular type of armrest used.

Although the right thigh section 308 and the left thigh section 310 are shown as separate components, the right thigh section 308 and the left thigh section 310 may be connected as a single thigh section spanning one of the left and right sides of the front section 306, The condition is that it can be folded away from the side of the front portion 306 to form a seat.

The convertible seat 300 may be used in an elevated walking chair or other device in which a conversion from a seat configuration to a seat is desired. The convertible seat 300 may be used in any of the lift walking chairs disclosed herein.

20A to 20B illustrate the bottom sides of the convertible seat 300 in a seat mode and a seat mode, respectively. The right thigh section 308 and the left thigh section 310 are directly or indirectly hinged to the seat section 302 at the right thigh section hinge 312 and the left thigh section hinge 314, respectively. The two-arm cranks 328, 330 are disposed between the seat support walls 320, 322, and are functionally connected to the shaft members 336, 338 of the thigh section hinges 312, 314, so that the movement of the two-arm cranks 328, 330 causes the thigh section 308, 310 rotate around the shaft members 336, 338.

The cam 316 is fixed between the two-arm cranks 328 and 330. The springs 332 and 334 extend from the two-arm cranks 328 and 330 to the spring wheel shaft 392, respectively. As will be explained in more detail below, the cam 316, the dual-arm cranks 328, 330, and the seat deployment springs 332, 334 bias the thigh sections 308, 310 to one of the folded positions as shown in FIG. 20B or as shown in FIG. 20A. A portion of a seat deployment mechanism in an extended (expanded) position is shown. Although portions 332, 334 are shown as springs, other types of elastic components may be used, provided that they are compatible with the purpose and function of the seat deployment mechanism 346.

Fig. 21A is a cross-sectional view taken through A-A of Fig. 21B. 21A-21B show thigh sections 308, 310 deployed to form a seat structure. FIG. 21A shows a cam 316 extending toward the front of the convertible seat 300 to allow the thigh sections 308, 310 to be deployed in a seat configuration. Returning to FIG. 21A, it can be seen that when the end of the cam 316 is directly or indirectly attached to the two-arm cranks 328, 330 and therefore the seat deployment springs 332, 334 rotate toward the front of the convertible seat 300, the seat deployment springs 332, 334 is extended as the thigh sections 308, 310 rotate upwards to form a seat.

Fig. 22A is a cross-sectional view taken through B-B of Fig. 22B. 22A, 22B show thigh sections 308, 310 rotated to a seat position. FIG. 22A shows a cam 316 that rotates toward the rear of the convertible seat 300, causing the thigh sections 308, 310 to rotate downward from the seat front portion 306 to form a seat structure. Compared to when the convertible seat 300 is in a seating position, the seat deployment springs 332, 334 are compressed. To provide sufficient clearance for a user's legs during a walking exercise, the thigh sections 308, 310 can be rotated toward the rear of the convertible seat 300.

Fig. 23A is a sectional side view taken through C-C of Fig. 23B. 23A to 23B illustrate a side view of one of the lift walking chairs 350. The lift walking chair 350 is in a lowered position, with the thigh sections 308, 310 deployed forward to a seating position. The seat deployment mechanism 346 switches the convertible seat 300 between a seat mode when in a lowered position and a seat mode when in a raised position, such as shown in FIG. 26A. The seat deployment mechanism 346 is functionally connected to a lifting mechanism 348, which is one of the lifting and lowering walking chairs 350. For example, the lifting mechanism 348 may be used instead of the lifting mechanism shown in FIGS. 5A to 5B. The disclosed embodiment of a raised walk chair may use a seat / seat that can raise and lower the lift chair and also functionally coordinate with a seat deployment mechanism to convert a convertible seat from a seat to a seat (and vice versa) Ran) any lifting mechanism. Next to the seat deployment mechanism 346, the lift mechanism 348 and the relationship between the two mechanisms will be explained.

The lifting mechanism 348 of the lifting walking chair 350 includes a parallelogram structure defined by pivots 352, 354, 356, and 358. The lower parallelogram link 360 extends between the main pivot 352 and the pivot 354. In the illustrative embodiment of FIG. 23A, the lower parallelogram link 360 has an extension frame 370 in a fixed relationship therewith. The main pivot 352 allows the lower parallelogram link 360, along with the extension frame 370, to rotate relative to the frame of the lift walking chair 350 to which it is attached.

As used herein, "parallel quadrilateral" and "parallel quadrilateral structure" refer to a structure containing one of four pivot points, in which components that pivot around their points are traditionally made up of components of a traditional parallelogram in a certain way. Fixed angle relationships move uniformly. These terms do not limit the pivoting components to be linear, and therefore are not necessarily parallel or necessarily equal in length.

The extension frame 370 provides components for adjusting the lifting mechanism 348. The effective force of the lifting mechanism can be adjusted to suit users of different weights and abilities. A lift spring 362 extends from the upper spring pivot 364 to a lift spring termination pivot 366. The lift spring termination pivot 366 is adjustable along the slot 368. When the lift spring 362 expands, it causes the lower parallelogram link 360 to rotate about the main pivot 352, which in turn raises the seat 300. The lifting mechanism 348 may be adjustable, such as by an adjustable spring termination mechanism shown in FIG. 23A or by other mechanisms, or the lifting mechanism 348 may be non-adjustable. Although part 362 is shown as a spring, other types of elastic components may be used, provided that it is compatible with the purpose and function of the lifting mechanism 348.

FIG. 24 shows an enlargement of one of the extension frames 370, in which the lift spring termination pivot 366 and the slot 368 are engaged in a relatively "unstable" position because the extension frame 370 is at the termination pivot 366 and the main pivot 352 The shortest lever arm is formed between them. For the relative position of the termination pivot 366 and the main pivot 352, please refer to FIG. 23A. The position of the lift spring termination pivot 366 in the slot 368 can be adjusted by the drive screw 372.

FIG. 25 illustrates a cabin 374, which is one of the lifting mechanisms 348. In this illustrative embodiment, the cabin 374 is an internal component of the extension frame 370. The cabin 374 moves between the cabin walls 376, 378 to allow the lift spring termination pivot 366 to move along the slot 368. The idler roller 380 stabilizes the nacelle 374 to prevent or prohibit tilting around the lift spring termination pivot 366.

The spring receiving seat 381 receives the lift spring 362. In the embodiment shown in FIG. 25, the spring receptacle 381 is shown as an opening, and a component of the lift spring 362 is inserted into the opening. Other lifting spring connection mechanisms may be used, provided that they allow operation of the lifting mechanism 348 and are sufficiently durable to withstand the resulting force.

Fig. 26A is a sectional side view taken through D-D of Fig. 26B. FIG. 26B is a front view of one of the chair lifts 350. 26A and 26C illustrate a side view of one of the lifting walking chairs 350. One of the parallelograms 382 of the lifting mechanism 348 is defined by the pivots 352, 354, 356, 358, and is shown with a dashed line in FIG. 26C. The convertible seat 300 or a component to which it is attached is in a fixed relationship with the parallelogram 382. When the seat 300 is raised or lowered, the parallelogram links between the pivots 352, 356 remain in a fixed angular relationship with the horizontal plane. The seat segment 302 of the seat 300 is in a fixed angular relationship with the parallelogram link connecting the pivots 352, 356. Therefore, when the seat saddle section 302 is raised or lowered, the seat saddle section 302 remains in its fixed position relative to the horizontal line. Generally, the seat 300 will be substantially horizontal or at a selected angle relative to the horizontal. Note that the convertible seat 300 is not necessarily horizontal, but can be fixed at other angular positions relative to the horizontal, and the other angle can be adjusted.

The longitudinal line of the slot 368 does not necessarily coincide with the instantaneous lever arm between the main pivot 352 and the spring termination pivot 366.

FIGS. 27A to 27B illustrate a convertible seat 300 having a seat deployment mechanism 346 connected to a parallelogram 382 (partially shown) in a lowered position and a raised position, respectively. FIG. 27A illustrates a seat deployment mechanism 346 connected to a portion of the lifting mechanism 348 when the lifting walking chair 350 is in a lowered position, in which the thigh sections 308 and 310 have a seat configuration. The portion of the lifting mechanism 348 shown includes a lower parallelogram link 360 and pivots 354, 358. A slide arm 384 attached to the lower parallelogram link 360 and extending beyond the lower parallelogram link 360 is also shown. The seat deployment mechanism 346 is functionally connected to the lift mechanism 348 by means of a slide arm 384, and therefore, when the angle of the parallelogram 382 is modified (such as by the action of the lift mechanism 348, or more specifically, in this embodiment With the lifting spring 362), the seat deployment mechanism 346 is acted upon.

Although the seat deployment mechanism 346 is shown as engaging the lift mechanism 348, the seat deployment mechanism may be functionally connected to other cam actuation mechanisms that act on the cam 316 to change the convertible seat 300 between a seat or a seat configuration.

The cam 316 is connected to the thigh paddle axles 336, 338 of the convertible seat 300 via a double-arm crank 328, 330. Alternatively, a single axle may span the right thigh section 308 and the left thigh section 310 with the cam 316 attached to that single axle. Therefore, for the purpose of simplicity, the right thigh pad axle 336 and the left thigh pad axle 338 should also mean the right thigh pad axle section 336 and the left thigh pad axle section 338.

The first end of each of the seat deployment springs 332, 334 is fixed to a spring wheel axle 392. A spring wheel shaft 392 is fixed to the convertible seat 300. The second ends of the seat deployment springs 332 and 334 are fixed to the two-arm cranks 328 and 330 (shown in FIGS. 20A and 20B). The two-arm cranks 328 and 330 are attached to the thigh pad wheels 336 and 338 of the thigh section pivot 388. Connected in a line. The seat deployment springs 332, 334 are shown as tension springs. Various types of spring parts can be used. A cam belt 390 has a first end attached to one of the slide arms 384 and a second end fixed to one of the cams 316. The cam belt 390 may include a material such as steel core polyester. For example, the cam belt 390 may be an elastic but stretch-resistant material. The cam belt 390 is typically an elongated flexible component, and may be, for example, a wire, rope, wire, belt, or cable.

FIG. 27B illustrates the seat deployment mechanism 346 connected to a part of the lifting mechanism 348 when the lifting walking chair 350 is in the lifted position, in which the thigh sections 308 and 310 have a seat configuration. When the convertible seat 300 is lifted, the slide arm 384 rotates toward the cam 316, so that the attachment point of the cam belt 390 and the slide arm 384 moves closer to the attachment point of the cam belt 390 and the cam 316, thereby causing the cam belt 390 to relax. The pressure from the thighs of a occupant on the thigh sections 308, 310 provides a force to push the thigh sections 308, 310 downward. The force of the seat deployment springs 332, 334 on the two-arm cranks 328, 330 (shown in Figs. 20A, 20B) and therefore on the cam 316 causes the cam 316 to rotate (for example) 180 ° or approximately 180 °, causing the thigh The sections 308, 310 are turned over to the rear of the convertible seat 300, thereby forming a seat configuration.

Similarly, when an occupant starts to sit on the convertible seat 300 in a seat position, the force from the occupant's weight causes the convertible seat 300 to be lowered. As the convertible seat 300 descends, the cam belt 390 tightens, thereby tightening the cam 316 to rotate forward, or counterclockwise in this illustration, and in turn expands the seat deployment springs 332, 334. This allows the thigh sections 308, 310 to rotate forward to form a seat. In an exemplary embodiment, the belt 390 is taut and the thigh sections 308, 310 are deployed at 8 inches from the lowest seating position. One illustrative range for the deployment height of the thigh section is 6 inches to 10 inches above the final seat height. One illustrative seat height is a standard 18-inch height. However, the sitting position can be lower or higher than the standard chair seat height. An illustrative range is about 16 inches to 20 inches. This illustrative range and height can be applied to any of the embodiments of the chair lift.

The lifting mechanism 348 is coordinated with the seat deployment mechanism 346 to preferably provide a comfortable and safe transition between the seat configuration of the convertible seat 300 and the seat configuration when lowering or raising the lifting walk chair 350.

Many lifting systems are equally elastic, in other words, they counteract the constant gravity on the payload to balance the payload and provide uniform lifting power throughout the vertical course. In one illustrative embodiment of the lifting walk chair 350 and the lifting mechanism 348, the elasticity is not uniform throughout the entire course of lifting or lowering the seat. Instead, the force is varied to provide the desired deployment force at a selected time or altitude. The power of the lifting mechanism 348 is slightly reduced at the extreme bottom of the stroke, so the lowering momentum can be used to help power seat deployment. The most suitable geometry to provide the most beneficial user experience will depend on various aspects of the geometry of the lifting mechanism 348, user weight, and other chair characteristics. As used herein, the term "payload" includes components that provide a rider and a lifting chair 350 that counteract the force of the lifting spring 362. In some places, the term "occupant" may also be used interchangeably with "payload" or "user."

28A-28B, 29A-29B illustrate illustrative specifications affecting the force and user experience of the lifting spring termination pivot 366 at different vertical levels and positions in the slot 368. For clarity, the following two different types of spring components are explained: seat deployment springs 332, 334 and lift springs 362. The seat deployment springs 332, 334 are used to change between a seat and a seat mode or to help change the convertible seat 300. The lift spring 362 is used to raise and lower the seat 300.

The following is an explanation of how to obtain and enhance such elasticity or balance to provide the lifting chair 350 with compensation for the weight of the user or a part of the weight of a user temporarily supported by the ground, such as an elastic profile or lifting curve. Explain the structure that allows the iso-elastic profile to be adjusted as required or as needed. Although the term "iso-elasticity" is used, as explained herein, it will be understood that there may be changes in lifting force over the course of a lowered position to a raised position.

The measured values are obtained when the upper and lower links of the parallelogram 382 are horizontal (ie, perpendicular to the direction of gravity). Note that as shown here, "horizontal" is higher than the actual seat height. General angles are illustrated when the parallelograms are horizontal so that various versions can be compared.

These measurements include lifting angle 394, slot angle 396, distance between parallelogram pivots 354 and 358 or between parallelogram pivots 352 and 356 (therefore equal distances are equal to each other), parallelogram pivots The distance between 356 and 358 or the parallelogram pivots 352 and 354 (which is therefore equal to each other), and the distance between the lift spring termination pivot 366 and the main pivot 352. The distance between the parallelogram pivots 354 and 358 or the parallelogram pivots 352 and 356 will be referred to as the parallelogram short link length 398, and between the parallelogram pivots 356 and 358 or the parallelogram pivots 352 and 354 The distance between them will be referred to as a parallelogram long link length 400. The distance between the lift spring termination pivot 366 and the main pivot 352 will be referred to as the termination pivot distance 402.

The lifting angle 394 is an angle between a line connecting the upper lifting spring pivot 364 and the lifting spring termination pivot 366 and a line connecting the lifting spring termination pivot 366 and the main pivot 352. The line between the lift spring termination pivot 366 and the main pivot 352 acts as one of the "virtual lever arms" or "lever arms" on the parallelogram 382. The slot angle 396 is the angle between the line connecting the upper lift spring pivot 364 and the lift spring termination pivot 366 and the line along which the lift spring termination pivot 366 can be adjusted in the slot 368. The slot angle 396 only illustrates a potential path for the lift spring termination pivot 366 as the length of the lever arm changes.

Note that when the parallelogram arm is horizontal, as in these illustrations, the spring 362 is almost completely compressed (for this embodiment, a 50% progression rate is specified so that the force when extended is half of the force when compressed). So with regard to isoelasticity, when approaching the maximum course height, the compressive force should be reduced and the elongation force should be enhanced, because otherwise in a non-equival elastic configuration, the payload will float in the middle and additional downward force is required To reach the bottom and additional lift to reach the top.

FIG. 28A illustrates the lifted walking chair 350 in a lowered position (toward the lowest height level but not at the lowest height level), with the lift spring termination pivot 366 in the rearmost position of the slot 368, that is, as a relatively long Lever arm. FIG. 28B is an enlarged view of a part of FIG. 28A. There are two different lifting conditions. When the lever arm is long (for strong lift), it is necessary to form a geometric structure of equal elasticity or close to equal elasticity throughout the course. This is because the entire spring course is used, from the largest to the smallest. In this illustrative embodiment, the lifting angle 394 is significantly tilted-an inefficient pushing angle-so that the payload is balanced without additional force to the lifting spring 362. In fact, in this embodiment, it can be very inefficient such that the force is actually slightly reduced when approaching the seat height in order to facilitate seat deployment. Since the lifting angle 394 is significantly inclined, that is, an inefficient pushing angle, the payload is balanced with or without additional force.

FIG. 29A illustrates the lifted walking chair 350 in a vertical position (toward the lowest height level but not at the lowest height level), which has a smaller ending pivot distance 402, thereby forming a distance from the graphs shown in FIGS. 28A to 28B Compared to a shorter one lever arm. The end pivot distance 402 can be adjusted, for example, by rotating the drive screw 372 (shown in FIG. 29B). Therefore, the configuration shown in Figs. 29A to 29B will provide a "light" improvement over the structure shown in Figs. 28A to 28B.

FIG. 29B is an enlarged view of a part of FIG. 29A. When the lever arm is short (for the lowest lift), the isoelastic profile may need to be modified by reducing the resulting change in equivalent elasticity so that it provides equivalent performance. In this illustrative embodiment, the slot angle 396 does not coincide with the lift angle 394, so that the force efficiency is increased relative to the shorter lever arm (ie, the termination pivot distance 402). This divergent slot angle offsets the inherent change in elastic contour that occurs with decreasing spring travel (ie, when the spring does not have a full course from full compression to full expansion). This shorter lever arm only uses the middle part of the spring journey, but the high-efficiency angle compensates for the difference and allows the spring to provide lift, which is the same as for a longer lever arm and larger payload for a small payload throughout the course It is iso-elastic or has an iso-elastic profile similar to that of a longer lever arm.

As can be seen by comparing FIGS. 28A to 28B with FIGS. 29A to 29B, when the slot angle 396 increases, the lift angle 394 decreases. Therefore, the desired change in isoelasticity throughout the lifting process is established by selecting the parameters described, which can be interdependent, for example. For example, the optimal lifting angle 394 will vary depending on the selected length of the "lever arm" to which the lifting force is applied.

FIG. 30 and FIG. 31 show the lift walking chair 350 at a higher level of history than that shown in FIGS. 28A and 29A. In the illustrative embodiments of FIGS. 30 and 31, the upper portion of the parallelogram 382 is not parallel to the lower link.

FIG. 30 illustrates the spring termination pivot 366 in the rearmost position along the slot 368. FIG. 31 illustrates a spring termination pivot 366 positioned in the slot 368 further toward the front of the lift chair 350. In FIG. 30, the lifting angle 394 and the slot angle 396 are smaller than when the device is in the lowered position. FIG. 30 shows a parallelogram 382 that raises the convertible seat 300 to its maximum height. In this embodiment, the lifting angle 394 crosses the center (passes below 90 °). In this configuration, the force is exerted on the lever arm at an angle that provides equal or nearly equal elastic lift, and continues to the top of the course or substantially to the top of the course.

In FIG. 31, the lifting angle is below 90 °, and it is crossed and is decreasing so as to offset the progress of the small spring at the center of the stroke.

Therefore, the selection of the slot angle 396, the position of the spring main pivot 352, and the adjustment of the lift spring termination pivot 366 along the slot 368 determine at least in part the lift spring 362 at Lifting efficiency for instant lifting angle. One illustrative range for the distance between the lift spring termination pivot 366 and the main pivot 352 is 0.7 inches to 2.8 inches. An illustrative usable slot length is in the range of 2.0 inches to 2.5 inches.

Generally, if the aspect ratio of the long side and the short side of the parallelogram 382 remains the same, the optimal lifting angle will remain the same. One illustrative range of parallelogram short link lengths 398 is 4 inches to 7 inches. One illustrative range of the parallelogram long link length 400 is 14 inches to 16 inches.

For example, an effective upper lift arm angle is measured from horizontal to a line passing through pivots 356, 358. One illustrative range of effective lift arm angles through the lifted position is 40 ° to 45 °. One illustrative range of the effective lift arm angle of the lowered position is 11 ° to 13 °.

Table 1 lists illustrative parameter ranges for a parallelogram for lifting a walking chair in one of a lowered position and a raised position.
table 1
Table 2 provides overall illustrative parameters for a parallelogram with a 4-inch short link and a 15-inch long link in a lowered position and a raised position.
table 3

The parameters provided can be applied to various embodiments of chair lifts and lifting mechanisms. The parameters are dependent on each other. For example, the length of the parallelogram lifting arms will require different degrees of rotation to achieve the desired force and equal elastic range. Generally speaking, the specific combination of the slot angle, lifting angle, the length from the spring end point to the main pivot, the length of the parallelogram short link and the length of the parallelogram long link will achieve the desired lifting force and iso-elastic profile.

The concept of "equival elasticity" related to lifting members is explained by various patents of Garrett W. Brown, which include US patents 8,066,251, 5,360,196, 7,618,016, 5435515, Re. 32,213, 6,030,130, 4,394,075 and 4,208,028 (the equivalent elastic interpretations contained therein are incorporated herein by reference).

In one illustrative embodiment of the lifting mechanism, the aspect ratio of the sides of the lifting parallelogram is relatively low. Even when adjusting the maximum lifting power, a relatively short "lever arm" (which may be connected to a parallelogram link group or side or fixedly attached to an extension of one of the parallelogram link groups or sides ) Apply a very large amount of elastic force. In an illustrative embodiment, the aspect ratio is 6: 1 or approximately 6: 1.

These lever arms are still short when adjusting the minimum lifting force, for example by a pin and hole adjustment or a slot (a spring termination pivot can be adjusted along the slot)-the length is reduced by as much as 80% with an aspect ratio of at most 24: 1. An illustrative aspect ratio ranges from 6: 1 to 24: 1. For example, the optimal aspect ratio may depend on the lifting power of the elastic component and the lever arm.

A minimum lift pin position affects the lift angle relative to the spring axis, because the spring now powers a short lever arm, pushing at a low-efficiency lift angle to offset the equivalent caused by lowering the aspect ratio of the lift triangle Deviation in elasticity.

One method for adjusting the lifting mechanism 348 is disclosed, which method comprises selecting the aforementioned parameters in a combined manner so as to generate a proper lifting of a series of payloads throughout the course of the parallelogram.

Various embodiments of lifting a walking chair and a lifting mechanism have been described, each of which has a different combination of elements. The present invention is not limited to the specific embodiments disclosed, and may include different combinations of the disclosed elements or omission of certain elements and equivalents of such structures.

Although illustrative embodiments have been disclosed, those skilled in the art will recognize additional advantages and modifications. Therefore, the invention in its broader aspects is not limited to the specific details shown and described herein. Modifications may be made without departing from the spirit and scope of the invention. Accordingly, the invention is not intended to be limited to the specific illustrative embodiments, but is to be construed within the full spirit and scope of the scope and equivalents of the accompanying patent applications.

1‧‧‧lifting chair / lifting chair

2‧‧‧ with wheeled frame / floor frame / seat frame

3‧‧‧Lift chassis / chassis

4‧‧‧ Attach lifting pillar / lower parallelogram lifting pillar / lifting pillar / curved lifting pillar / parallel quadrangular lifting pillar

4a‧‧‧Lift extension frame

5a‧‧‧ Upper Parallelogram Pillar / Parallelogram Pillar / Curved Parallelogram Pillar

5b‧‧‧ Upper Parallelogram Pillar / Parallelogram Pillar / Curved Parallelogram Pillar

6‧‧‧foldable seat / seat / seat / seat / folded seat / seat

6a‧‧‧Right Folding Seat Wing / Seat Wing / Wing / Folding Seat Wing

6b‧‧‧Left Folding Seat Wing / Seat Wing / Folding Seat Wing / Side Side Wing / Wing

7‧‧‧seat mounting block

7a‧‧‧seat mounting post

8‧‧‧ Armrest / Seat Back Frame / Seat Frame

9a‧‧‧Support armrest assembly / armrest / right armrest assembly / right-hand actuated armrest assembly / armrest assembly / right armrest / actuated armrest assembly

9b‧‧‧Support armrest assembly / armrest / left armrest assembly / armrest assembly / left armrest / actuated armrest assembly

11a‧‧‧ Parallelogram Pillars / Front Parallelogram Deployment Pillars / Front Parallelogram Pillars / Front Handrail Deployment Pillars

11b‧‧‧ Parallelogram Pillar / Rear Parallelogram Deployment Pillar / Rear Parallelogram Pillar / Rear Armrest Deployment Pillar

12a‧‧‧ cover / transparent top cover / arm cover

12b‧‧‧ cover / transparent top cover / arm cover

13‧‧‧ Receiving Rod

13a‧‧‧Axle / Receiving lever wheel axle

14‧‧‧Lift Box / Flexible Lift Box / Box

14a‧‧‧Axle / Box Wheel

14b‧‧‧slot

15a‧‧‧Elastic power unit / gas spring

15b‧‧‧Elastic power unit / gas spring

15c‧‧‧Elastic power unit / gas spring

16a‧‧‧Front caster

16b‧‧‧Front caster

17a‧‧‧ rear wheel

17b‧‧‧ rear wheel

18a‧‧‧Motor mounting plate / armrest support plate / mounting plate

18b‧‧‧Motor mounting plate / armrest support plate / mounting plate

19‧‧‧Lift extension centerline / Extension centerline / Lift frame centerline

21‧‧‧Box Centerline / Flexible Box Centerline

24‧‧‧Maximum height adjustment screw

25‧‧‧Impact board

26a‧‧‧right linear bearing track / linear bearing track

26b‧‧‧left linear bearing track / linear bearing track

27a‧‧‧linear bearing assembly / right linear bearing assembly

27b‧‧‧linear bearing assembly / left linear bearing assembly

28‧‧‧seat bracket assembly / seat bracket

29a‧‧‧Right elastic component / elastic component / gas spring

29b‧‧‧Left elastic component / elastic component / gas spring

30‧‧‧ Roller back fabric or covering

31‧‧‧backrest roller assembly

32a‧‧‧Right back tension pulley assembly

32b‧‧‧Left back tension pulley assembly

33a‧‧‧Right caster steering foot pedal

33b‧‧‧Left foot steering wheel pedal

35‧‧‧ Elastic dynamic payload support arm

36‧‧‧actuated wire / wire / dotted brake cable / brake wire

37a‧‧‧Crankshaft axle

37b‧‧‧Crankshaft axle

38‧‧‧ Wing Deployment Pillar / Right Hand Pillar / Pillar / Telescopic Tube

39‧‧‧ Ball Joint

40a‧‧‧Front Hinge Set / Hinge Set

40b‧‧‧Rear hinge group / hinge group

50a‧‧‧ Pivot

50b‧‧‧ Pivot

50c‧‧‧ Pivot

50d‧‧‧ Pivot

52‧‧‧ Illustrative Joint Arm

54‧‧‧ ring frame tool holder

56a‧‧‧extendable shaft

56b‧‧‧extendable shaft

56c‧‧‧Extendable shaft

58‧‧‧Vertical Centerline

300‧‧‧ Convertible seat / seat

302‧‧‧seat section / seat section

304‧‧‧Rear part / Seat rear part

306‧‧‧ Narrower front section / front section / seat front section / front section

308‧‧‧ thigh section / right thigh section

310‧‧‧ thigh section / left thigh section

312‧‧‧Right thigh hinge

314‧‧‧Left thigh section hinge / thigh section hinge

316‧‧‧cam

320‧‧‧seat support wall

322‧‧‧seat support wall

324‧‧‧ Wheel

326‧‧‧ Wheel

328‧‧‧arm crank

330‧‧‧arm crank

332‧‧‧spring / seat deployment spring / part

334‧‧‧spring / seat deployment spring / part

336‧‧‧Shafts / Thigh Pad Wheel

338‧‧‧Shaft / Thigh Pad Wheel / Left Thigh Pad Wheel / Left Thigh Pad Wheel Section

340‧‧‧Belt

342‧‧‧ Parallelogram pivot to which belt 340 is attached

344‧‧‧Slide

346‧‧‧seat deployment agency

348‧‧‧lifting agency

350‧‧‧Lifting chair / lifting chair

352‧‧‧ Pivot / Main Pivot / Parallel Quadrilateral Pivot / Spring Main Pivot

354‧‧‧ Pivot / Parallel Quadrilateral Pivot

356‧‧‧ Pivot / Parallel Quadrilateral Pivot

358‧‧‧ Pivot / Parallel Quadrilateral Pivot

360‧‧‧ Lower Parallelogram Link

362‧‧‧Lifting Spring / Part / Spring

364‧‧‧Upper Spring Pivot / Upper Spring Pivot

366‧‧‧Lifting spring termination pivot / termination pivot / spring termination pivot

368‧‧‧Slot

370‧‧‧ extension frame

372‧‧‧Drive screw

374‧‧‧cabin

376‧‧‧cabin wall

378‧‧‧cabin wall

380‧‧‧Idler roller / spring receptacle

382‧‧‧ parallelogram

384‧‧‧ Sliding arm

386‧‧‧cam pivot

388‧‧‧Thigh section pivot / thigh section pivot

390‧‧‧Cam Belt / Belt

392‧‧‧Spring wheel shaft

394‧‧‧Lifting angle / Best lifting angle

396‧‧‧Slot angle

398‧‧‧ Parallelogram Short Link Length

400‧‧‧ Parallelogram long link length

402‧‧‧End Pivot Distance / Small End Pivot Distance / Lifting Spring End Pivot 366 and Main Pivot 352 (End Pivot Distance)

A-A‧‧‧ Section

B-B‧‧‧ Section

C-C‧‧‧ Section

D-D‧‧‧ Section

All drawings and descriptions are directed to illustrative embodiments. The specific configuration equivalents of the lifting walk chair and its component parts and mechanisms are intended to be included in the present invention. The following drawings illustrate illustrative embodiments:

FIG. 1 illustrates an isometric view of one of the lifting walking chairs.

2A to 2B are side elevation views of the chair of FIG. 1 showing a seat / seat that is unfolded to form a chair in a lowered position and has a fold to form in a raised position The wing of a car seat.

3A to 3B illustrate an isometric view of a lifting chassis including a parallelogram post and a transparent perspective view of an elastic lifting box.

4A-4B illustrate side elevation views of two alternate positions of a box wheel axle that are generally associated with differences in payload enhancement performance.

5A to 5B are side elevational views of various selected installation angles for raising an extension frame to produce potentially equivalent lifting performance when the lifting frame angle is consistent with the box centerline angle.

FIGS. 6A to 6C show the deployment positions of the left / right armrest assembly. When the user changes from the seat mode to the seat mode and walks, the left / right armrest assembly locks and unlocks the seat height and the rear wheel.

7A to 7D illustrate a stepwise engagement made by a user using an actuated armrest control function when a user is seated and a downward transition to one of the seated heights is achieved.

FIG. 8 illustrates a handrail for stably and partially supporting a walking user who rides on a folding seat / seat and shows a posture for walking, striding and / or sliding.

9A to 9C illustrate an arm / hand-actuated armrest assembly having a top cover and an associated armrest position resulting from the history of front / rear uneven parallelogram pillars.

FIG. 10 shows a folding seat / seat assembly with a wing and a seat mounting block, which shows a way in which a seat mounting post promotes limited dynamic left / right rotation of the seat / seat to provide a path for backward stepping legs.

FIGS. 11A to 11B illustrate a seat / seat and show a manner in which a seat wing is swung up into a seat mode by a wing deployment pillar when the seat is lowered.

FIG. 12A to FIG. 12B illustrate a chair lift assembly that raises and lowers a seat support assembly between a walking height and a sitting height by means of a left / right elastic member and a linear bearing assembly.

13A to 13B show a low seat of an elevated walking chair suitable for industrial use and an isometric view after the deployment of the elevated seat. The elevated walking chair is a worker or other user, a flexible dynamic payload support arm and a ring The combined weight of the rack industrial tool payload provides support.

FIG. 14 illustrates a maximum height adjusting screw and an impact plate assembly for appropriately setting one of the maximum seat heights for a user's crotch seam measurement.

15A to 15C illustrate a seat of a chair lift that changes between a seat shape and a flatter seat shape.

FIG. 16 illustrates a knuckle arm attached to a ring-shaped tool holder.

17A to 17D illustrate an illustrative armrest having one of cam or crankshaft axles, which cam or crankshaft axles actuate braking and lift-lock functions through a sequential deployment position.

18A to 18B illustrate the bottom side of a seat of a lifted walking chair in the seat mode and illustrates a seat rotation function.

19A to 19B illustrate another illustrative embodiment of a seat configuration that can be integrated with any of the disclosed frame and lifting mechanism from a seat configuration to a seat of a seat structure.

20A to 20B illustrate the bottom side of the seat of FIGS. 19A to 19B in a seat configuration and a seat configuration, respectively.

Fig. 21A is a cross-sectional view taken through A-A of Fig. 21B.

FIG. 21B illustrates the bottom side of the seat illustrated in FIG. 19A.

Fig. 22A is a cross-sectional view taken through B-B of Fig. 22B.

FIG. 22B illustrates the bottom side of the seat illustrated in FIG. 19B.

Fig. 23A is a cross-sectional side view of a lift walking chair taken through C-C of Fig. 23B.

Figure 24 is an enlarged view of one of the extension frames of a lifting mechanism.

FIG. 25 illustrates a cabin of a lifting mechanism.

Fig. 26A is a sectional side view taken through D-D of Fig. 26B.

FIG. 26C illustrates a lifting walk chair, which shows a parallelogram of one of the lifting mechanisms with a dotted line.

27A to 27B illustrate a seat with a seat deployment mechanism connected to a lifting mechanism in a lowered position and a raised position.

28A to 28B illustrate illustrative specifications affecting the force and performance of a walking chair.

29A to 29B illustrate illustrative specifications for improving the force and performance of a walking chair according to the impact of another configuration.

FIG. 30 illustrates a lift chair at a higher level than that shown in FIGS. 28A and 29A.

FIG. 31 illustrates a lift chair that is at a higher level than that shown in FIGS. 28A and 29A according to another configuration.

Figure 32 is an isometric view of a linear bearing assembly continuing between a pair of linear bearing tracks.

Claims (11)

A convertible seat comprising: A seat section having a rear section and a narrower front section extending from the rear section; A thigh section which is connected to the saddle section by a hinge and is foldable towards the rear saddle section; The thigh section hinge has a wheel axle disposed therethrough; A seat deployment mechanism configured to change the seat between a folded seat configuration and an unfolded seat configuration; and The seat section is configured to be raised and lowered by a lifting mechanism; The seat deployment mechanism is configured to be activated by the action of the lifting mechanism to raise and lower the seat, thereby causing the seat and the thigh section to automatically move between the folded seat configuration and the deployed seat configuration地 变。 Ground transformation. The convertible seat of claim 1, wherein the thigh section, the thigh section hinge, and the wheel axle include: A right thigh section, which is connected to the saddle section by a right hinge and is foldable toward the rear saddle section; A left thigh section connected to the saddle section by a left hinge; and The left hinge and the right hinge have a wheel axle disposed therethrough. If the convertible seat of item 1 is requested, the seat deployment agency includes: A cam fixed to the axle; A stretched flexible component having a first end and a second end; A first end of the flexible component is configured to be connected to a lifting mechanism; and The second end of the flexible component is connected to the cam; The rotation of the cam around the wheel shaft generated by the lifting mechanism thereby raises the convertible seat, and converts the convertible seat into a seat. If the convertible seat of claim 1, further comprising one or more seat deployment springs, the one or more seat deployment springs are attached at one end to one or more dual-arm cranks and at an opposite end attached to A spring wheel axle, thereby biasing the thigh section to a folded or unfolded position. The convertible seat as claimed in claim 1, wherein in the deployed configuration, the right thigh section, the left thigh section and the seat section form a sitting surface together. A lift walking chair includes: If seat of item 1 is requested; A frame with a plurality of wheels attached; and A lifting mechanism attached to the frame. If the lifting chair of item 6 is requested, the lifting mechanism includes: A parallelogram structure; A lift spring, the force of which lifts the weight of an occupant; A slide arm attached to the parallelogram structure; and The first end of the flexible component is attached to the sliding arm. For example, the lifting walking chair of item 7, wherein the lifting spring is configured to offset the weight of the user, thereby reducing the force required by the occupant to change from a sitting position to a raised seat position. The lift walking chair of claim 6, wherein the seat deployment mechanism further includes one or more seat deployment springs, the one or more seat deployment springs are attached to one or more dual-arm cranks at one end, and The ends are attached to a spring wheel axle, thereby biasing the right thigh section and the left thigh section to a folded or unfolded position. The lifting chair as claimed in claim 6, wherein in the deployed configuration, the thigh section and the seat section together form a sitting surface. A rehabilitation method includes: Provide lifting chair as requested in item 6; Use this lift walking chair for exercise training.