Note: Descriptions are shown in the official language in which they were submitted.
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LINKAGE MECHANISM FOR RECLINING CHAIR
TECHNICAL FIELD
The present invention relates generally to a reclining chair and, more
specifically to a
reclining chair having a compact modular chair frame supported on a swivel
base and an all-
linkage reclining mechanism.
BACKGROUND ART
Reclining chairs are known within the art, and are becoming increasingly
popular as it
becomes more desirable to integrate comfort and reclining functions into
various articles and
styles of furniture including chairs, love seats and sofas. Many of the first
developed designs
were based upon all-linkage mechanisms. However, these all-linkage mechanisms
typically did
not provide a smooth reclining motion and were extremely large. As such the
articles of furniture
which utilized this mechanism were oversized. Moreover, these chairs required
a large amount
of free space to enable operation thereof. The all-linkage reclining chair
mechanisms known
~ivithin the art also did not provide adequate adjustment features for
accommodating seat
occupants of varying stature.
To overcome this problem, alternate reclining mechanisms were developed such
as wall
proximity reclining mechanisms utilizing track and roller assemblies which
provided a smoother
reclining motion. Presently, the reclining mechanisms utilizing track and
toilers are fairly
complex, require numerous components of varying types such as links, tracks
and rollers, and
are thus relatively expensive to manufacture. An exemplary reclining chair
mechanism which
was developed to provide a smoother reclining motion is that disclosed in U.S.
Patent No.
5,011,220, entitled "Chair Mechanism," which is commonly owned by the assignee
of the present
invention. This mechanism utilizes a short inclined track and roller to
provide the recline-away
motion of the wall proximity reclining chair. While this chair mechanism
achieved the goal of
providing smoother reclining operation, the design of this mechanism presents
several
disadvantages. First, this mechanism is limited to only two operative
positions, namely the
upright position, and the fully-reclined position. Additionally, this chair
design does not allow
the chair arms to move along with the seat assembly. Thus, this design
requires a chair frame
having more forwardiy extending arm rests for providing adequate support when
the chair
mechanism is in the fully reclined position.
Another exemplary wall proximity reclining chair is that disclosed in U.S.
Patent
No. 5,217,276, entitled "Chair Mechanism", and which is commonly owned by the
assignee
of the present invention. This chair mechanism design provides several
improvements
over those mechanisms know within the art. However, this mechanism also relies
upon
a track and roller system for providing
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smooth reclining motion. Additionally, this chair is also limited to only two
reclining positions,
and requires manual actuation via a hand operated lever. Accordingly, this
design limits the
types of furniture within which this mechanism can be integrated.
Yet another type of wall proximity reclining chair is that illustrated in U.S.
Patent No.
5,323,526, entitled "Method for Assembling A Modular Wall Proximity Reclining
Chair", which
is commonly owned by the assignee of the present invention. This chair was
developed for
reducing the complexity of the reclining mechanism, and its method of
assembly. This chair
mechanism overcomes the disadvantages of the prior art designs by providing a
side frame and
arm rest assembly that moves in conjunction with the seat assembly for
providing adequate arm
rest support. However, this mechanism design also relies upon a full length
track and roller
assembly for providing the desired smoothness in the reclining operation. The
requirement for
a bearing-based roller assembly also increased the cost of the mechanism.
Additionally, the
design of this mechanism limits this chair to a single reclining chair and
further prevents this
mechanism from being used in large articles of furniture, such as sofas and
modular sofa
assemblies.
In view of the growing popularity of reclining chairs
reclining chairs in a more formal setting, there is a increasing need to
develop a reclining chair
mechanism which can be utilized with various types of furniture, Including
compact reclining
chairs, at a considerably lower cost and that provides the comfort features
demanded by
consumers.- As such, it is desirable to provide an'all-linkage reclining chair
which delivers
smooth reclining motion, which includes an adjustment feature for
accommodating various sized
seat occupants, and which is readily assembled into various sizes and styles
of chairs. It is also
desirable to provide an all-linkage reclining chair mechanism which is
designed to be primarily
gravity driven with the assistance of a spring biasing mechanism, rather than
manually driven
through the use of an externally mounted operating handle. Such a design would
simplify the
operation of the chair. It is further desirable to provide a reclining chair
mechanism in which the
leg rest assembly can be fully extended by actuating a compact trigger release
assembly, and
can be retracted by the occupant merely moving the Leg rest assembly back into
the chair
mechanism by leaning forward and placing a small amount of force onto the leg
rest assembly.
It is also desirable to provide a reclining mechanism in which the leg rest
assembly can be
replaced in the field, if damaged during use, without disassembling the entire
chair and its
associated reclining mechanism. It is further desirable to provide an all-
linkage reclining
mechanism which moves the associated chair frame forwardiy as the seat
assembly is reclined,
thereby allowing for uninhibited operation when the chair is placed in close
proximity to a wall.
DISCLOSURE OF INVENTION
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In accordance with the principles of the present invention, a reclining chair
having a
compact chair frame supported on a swivel base and an all-linkage reclining
mechanism is
disclosed. The reclining chair includes a chair frame operably coupled to a
base frame via a
support linkage assembly. A swivel base assembly is secured to the base frame
to provide a
rotational degree of freedom between the floor and the base frame. A
longitudinal link is
operably interconnected to the support linkage assembly. A recline linkage
assembly is
operably coupled between the longitudinal link and to the base frame for
controlling movement
of the longitudinal link from an upright position to at least one reclined
position. A rotatable drive
shaft is journally supported by the longitudinal link. The reclining
chairfurther includes a leg rest
assembly supported from the longitudinal link and operably coupled to the
drive shaft for
movement from a retracted position to an extended position in response to
rotation of the drive
shaft.
Accordingly, a principle object of the invention is to provide a compact,
smoothly
operating all-linkage reclining mechanism which can be incorporated into
reclining chairs of
varying sizes and styles.
It is another object of the present invention to provide a primary linkage
reclining
mechanism which is positioned under the seat, within the seat tabs, to
appropriately position
the various pivots of the reclining mechanism in correspondence with various
biomechanical
points associated with the seated occupant, thereby enhancing the comfort of
the reclining
mechanism.
It is a further object of the present invention to provide an all-linkage
reclining
mechanism which is readily adjustable to optimize the force required to
initiate and continue the
reclining movement, as well as to retract the leg rest assembly from the fully
extended position.
It is an additional object of the present invention to provide a reclining
mechanism which
supports the chair frame in an extremely stable condition irrespective of its
orientation in the
upright, partially reclined or fully reclined position.
In a broad aspect, then, the present invention relates to a linkage mechanism
for a
reclining chair comprising: a base frame; a support linkage assembly pivotally
supported from
said base frame; a longitudinal link operably coupled to said support linkage
assembly; a recline
linkage assembly operably coupled to said longitudinal link and to said base
frame for
controlling movement of said longitudinal link from an upright position to a
reclined position; a
rotatable drive shaft journally supported by said longitudinal link; a pivot
control assembly
including a second drive arm rotatably supported on the drive shaft and a
control link having a
first end pivotally connected to the second drive arm and a second end
pivotally connected to
the base; and a leg rest assembly supported from said longitudinal link and
operably coupled
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to said drive shaft for movement from a retracted position to an extended
position in response
to rotation of said drive shaft in a first direction.
In another broad aspect, then, the present invention relates to a reclining
chair
comprising: a base frame; a chair frame having a seat frame and a seat back; a
support linkage
assembly pivotally coupled to said base frame, said support linkage assembly
including a first
support link pivotally coupled to said base frame, a second support link
pivotally coupled to said
base frame, an intermediate link pivotally coupled to said first support link
at a first pivot and
pivotally coupled to said second support link at a second pivot, and a base
connecting link
pivotally coupled to said base frame at a first end and operably coupled to
said intermediate
link; a longitudinal link operably coupled to said support linkage assembly,
said seat frame
secured to said longitudinal link such that said support linkage assembly
supports said chair
frame for relative movement above said base frame; a recline linkage assembly
operably
coupled between said longitudinal link and said base from for controlling
reclining movement ,
of said longitudinal link form an upright position to a reclined position,
said recline linkage
assembly having a seat back support link pivotally coupling said seat back to
said longitudinal
link; a rotatable drive rod journally supported by said longitudinal link and
operably coupled
thereto such that reclining movement of said longitudinal link rotates said
drive rod in a first
direction; and a leg rest assembly supported from said longitudinal link and
operably coupled
to said drive rod for movement from a retracted position to an extended
position in response
to rotation of said drive rod in said first direction.
These and other additional objects, advantages and features of the present
invention
will become apparent from the following description and appended claims, taken
in conjunction
with the accompanying drawings.
BRIEF DESCRIPTION OF THE DRAWINGS
Figures 1A through 1C are perspective views of an exemplary wall proximity
reclining
chair showing the various operative positions, including an upright position
with the leg rest
assembly retracted, a partially reclined position with the leg rest assembly
fully extended, and
a fully reclined position with the leg rest assembly extended and the seat
back fully reclined;
Figure 2 is an outside elevational view of an all-linkage assembly in
accordance with a
preferred embodiment of the present invention with the upholstery, springs and
other parts
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removed from the reclining mechanism for illustrating the integrated and inter-
dependent
association of the linkage components;
Figure 3 is an inside elevational view of the all-linkage mechanism shown in
the upright
position in accordance with a preferred embodiment of the present invention;
Figure 4 is an outside elevational view of the all-linkage mechanism in the
partially
reclined position in accordance with a preferred embodiment of the present
invention;
Figure 5 is an inside elevational view of the all-linkage mechanism in the
partially reclined
position in accordance with a preferred embodiment of the present invention;
Figure 6 is an outside elevational view of the all-linkage mechanism shown in
the fully
reclined position;
Figure 7 is an inside elevational view of the all-linkage mechanism shown in
the fully
reclined position, also in accordance with a preferred embodiment of the
present invention;
Figure 8 is a top plan view showing the left and right all-linkage assemblies
interconnected with various cross members in accordance with a preferred
embodiment of the
present invention;
Figure 9 is a perspective view showing the spring assist drive linkage in
accordance with
a preferred embodiment of the present invention;
Figure 10 is a top view of the adjustable seat slide mechanism in accordance
with a
preferred embodiment of the present invention;
Figure 11 is a partial side elevational view of the adjustable seat slide
mechanism, also
in accordance with a preferred embodiment of the present invention;
Figure 12A is a side view of the cable release assembly in the retracted or
locked
position, in accordance with a preferred embodiment of the present invention;
Figure 12B is a side view of the cable release assembly in the fully released
position,
also in accordance with a preferred embodiment of the present invention;
Figure 12C is an exploded perspective view of the trip link assembly in
accordance with
the present invention;
Figures 13A - 13C are perspective views of an alternate preferred embodiment
of a
swivel base reclining chair having an all-linkage reclining mechanism shown in
the various
operative positions, including an upright position with the leg rest assembly
retracted, a partially
reclined position with the leg rest fully extended, and a fully reclined
position with the leg rest
assembly extended and the seat back fully reclined;
Figure 14 is a simplified perspective view of the base frame and swivel base
assembly
utilized in the present invention;
Figure 15 is a cross-sectional view of the base frame taken along line 15-15
shown in
Figure 14;
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Figure 16 is a cross-sectional view of the base frame taken along line 16-16
shown in
Figure 14; and
Figure 17 is a cross-sectional view of the pivot point of the linkage
mechanism taken
along line 17-17 shown in Figure 2 which illustrates a threaded rivet utilized
at various pivot
locations within the all-linkage reclining mechanism.
MODES OF CARRYING OUT THE INVENTION
In accordance with the teachings of the present invention, an all-linkage
reclining chair
adapted for use in various articles of motion furniture is disclosed. In a
first preferred
embodiment, a pair of all-linkage mechanisms are integrated into a love seat
in which each side
defines a wall proximity reclining chair which independently reclines. In a
second preferred
embodiment, an all-linkage mechanism are integrated into a compact reclining
chair having a
swivel base operably associated therewith. While disclosed with reference to
particular
embodiments, it should be understood that the present invention can be
incorporated into a
variety of motion furniture designs. With particular reference now to the
drawings, the structural
and functional aspects of the present invention are described with more
particular detail.
With reference now to Figures 1A through 1 C, wall proximity reclining chair
20 includes
a seat frame 22 having an arm rest or side frame 24, and further includes a
reclinable seat back
26 and movable leg rest assembly 28. Figure 1A illustrates wall proximity
reclining chair 20 in
its upright position, with leg rest assembly 28 retracted within the chair.
Figure 1 B illustrates the
wall proximity reclining chair 20 in its partially reclined or intermediate
position, in which leg rest
assembly 28 is fully extended and seat back 26 is partially reclined. Leg rest
assembly 28 is
positionable between a retracted position shown in Figure 1A and an extended
position as
shown in Figures 1 B and 1 C. Figure 1 B further illustrates the wall
proximity feature in that seat
frame 22, side frame 24, and seat back 26 move forwardly along with leg rest
assembly 28 when
the wall proximity reclining chair 20 is moved from its upright position to
its partially reclined
position. Finally, Figure 1 C illustrates wall proximity reclining chair 20 in
its fully reclined
position. It should be noted that leg rest assembly 28 must be fully extended
before seat back
26 can begin reclining. As will be appreciated from Figure 1C, and the
following detailed
description, when wail proximity reclining chair 20 is in the partially
reclined position, additional
rearward pressure placed against seat back 26 by the occupant, correspondingly
forces the seat
frame 22, side frame 24 and leg rest assembly 28 forward. Accordingly, the all-
linkage
mechanism is designed to allow seat back 26 to be placed within approximately
5-6 inches (12-
- 15 cm) of a wall surtace and achieve a fully reclined position without seat
back 26 making
contact with the proximal wall surface.
Referring now to Figures 2 through 7, a preferred embodiment of the present
invention
is illustrated in more detail. With particular reference to Figures 2 and 3,
wall proximity reclining
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chair 20 includes right and left all-linkage mechanisms 30, 32. Figure 2 is an
outside view of
the right all-linkage mechanism 30 in the upright position, and Figure 3 is an
inside view of the
left all-linkage mechanism 32 in the same position. After viewing Figures 2
through 7, it can be
understood that the all-linkage mechanisms 30, 32 are mirror images of each
other. All-linkage
mechanism 30, 32 are operably coupled to base frame 33. More specifically,
each all-linkage
mechanism 30, 32 is pivotably secured to a longitudinal "L-shaped" base rail
34. Referring
briefly to Figure 8, the pair of longitudinal base rails 34 are then secured
to front and rear "L-
shaped" frame rails 36, 38. Each front and rear frame rail 36, 38 has a series
of three hole
formations 37 bored therein. The three holes 37 allow the spacing between two
adjacent
reclining chairs 20 to be selected for accommodating,various styles of chairs
which may have
different thicknesses of padding and upholstery. The series of three hole
formations 37 also
allow a greater degree of precision and rigidity over a conventional slot and
fastener.
With continued reference to Figure 8, a pair of comer brackets 39 are secured
between
each longitudinal base rail 34 and the rear frame rail 38. The forward end of
each corner
bracket 39 is offset by 45° so that it can be secured to the horizontal
flange 58 of the
longitudinal base rail 34 in two places with suitable fasteners. The opposite
end of each corner
bracket 39 is also secured to the rear frame rail 38 with suitable fasteners.
In view of this
interconnection scheme between the longitudinal base rails 34, the rear frame
rail 38, and the
comer brackets 39, one skilled in the art will readily appreciate the enhanced
rigidity provided
by securing comer brackets 39 with three fasteners as shown. Additionally,
this interconnectiow
scheme provides the precise alignment required by each all-linkage mechanism
30, 32 with
respect to the other. Thus, base frame 33 is a rigid, generally rectangular
support frame defined
by the pair of longitudinal base rails 34, front and rear frame rails 36, 38,
and corner brackets
39. As disclosed, the front and rear frame rails 36, 38 can be sized to a
variety of lengths such
that wall proximity reclining chair 20 can embody a single reclining chair, or
integrated within a
love seat or sofa. Additionally, reclining chair 20 and the all-linkage
mechanisms 30, 32 are
suitable for use in a modular sofa assembly.
Referring now to Figures 2 through 8, the individual components forming each
all-linkage
mechanism are described in more detail. Each aN-linkage mechanism 30, 32 is
generally
supported from its longitudinal base rail 34 by a four-bar linkage assembly
40. More specifically,
the four-bar linkage assembly 40 includes a front support link 42 and a rear
support link 44
which are pivotably coupled at their lower ends to the vertical flange 56 of
the longitudinal base
rail 34 and pivotably coupled at their upper ends tv an intermediate link 60.
The front support
link 42 is connected to the base rail 34 at pivot 46 and the rear support sink
44 is connected to
the base rail 34 at pivot 48. Additionally, the front support link 42 is
pivotably coupled to
intermediate link 60 at pivot 52 and the rear support link 44 is pivotably
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coupled to the intermediate Iink60 at pivot 54 (Figure 5). Intermediate or
secondary longitudinal
link 60 includes two forward apertures 62, 64 for selectively adjusting the
pivotal connection 52
with front support link 42. The right and left all-linkage mechanisms are
interconnected to each
other by a front cross member 152 which connects between the front support
links 42, and a
rear cross member 154 which connects between the rear support links 44.
All linkage mechanisms 30, 32, front cross member 152, and rear cross member
154
together define the support linkage assembly.
The prominent link of each all-linkage mechanism 30, 32 is the main
longitudinal link 50
which supports the seat frame 22 and side frame or frames 24. Main
longitudinal link 50 has
i 0 its forward end directly supported at pivot 52 by the front support link
42, and has its rearward
end indirectly supported by the reGine linkage assembly 100. The main
longitudinal link 50
further includes front and rear flanges 66, 68 which protrude outwardly from
the main longitudinal
link 50 far supporting and securing the seat frame 22 and side frame 24. The
mid portion of the
main longitudinal Link 50 includes an attachment flange 70 for securing the
cable 240 of the trip
link assembly 234. An aperture 72 for joumally supporting the square drive rod
80 is provided
generally below this attachment flange 70. A bearing 74 is provided in
aperture 72 for allowing
the square drive rod 80 to easily rotate within aperture 72.
Referring briefly to Figures 8, 10 and 11, the adjustable seat slide 82
associated with
each all-linkage mechanism 30, 32 is shown in more detail. More specifically,
each main
longitudinal link 50 is provided with an elongated aperture 76 for receiving a
two piece nylon
insert 78, thereby forming the lost motion slot 84 of the adjustable seat
slide 82. Two metal
friction washers 86 are provided on each side of the nylon insert 78. A
threaded slide pin 88
having a head is extended through each friction washer 86 and thus through
lost motion slot 84
for securing to other links of the mechanism. The threaded slide pin 88 also
extends through
the top pivot 52 of front support link 42, through the forward aperture 62 of
the link 60, and
finally through a washer 92. A tensioning spring 94 is retained on the inboard
end of the
threaded slide pin 88 by an adjustable fastener, such as a wing nut 96.
Accordingly, the amount
of compression between friction washers 86 and the nylon insert 78 of the seat
slide assembly
82 can be adjusted by correspondingly adjusting the amount of tension provided
by wing nut
96.
The adjustable seat slide 82 controls how easily the main longitudinal link 50
can move
with respect to pivot 52 of front support link 42. Thus, tha adjustable seat
slide 82 controls the
amount of friction placed on front pivot 52 during the reclining motion
between the upright
position and the intermediate position, and especially controls the amount of
friction placed on
nylon insert 78 as the main longitudinal link 50 moves between the
intermediate and fully
reclined positions. The adjustable seat slide 82 can be most easily accessed
and adjusted from
the front of reclining chair 20 when the leg rest assembly 28 is fully
extended. The unique front
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access feature allows the seat slide 82 to be adjusted without moving the
chair, or turning the
chair over to access the mechanism. The advantage of a front access adjustment
mechanism
becomes even more significant when the wall proximity reclining chair 20 is
incorporated into a
love seat, sofa, or modular sofa, which could not be easily moved to access
the adjustment
feature. By rotating the wing nut 96 of each adjustable seat slide, the motion
of each all-linkage
assembly 30, 32 can be adjusted for various sized seat occupants. Thus, the
advantage of the
adjustable seat slide 82 is that the reclining chair 20 can be adjusted for
very smooth and
consistent operation. Unlike otherwall proximity reclining chairs known to
recline too quickly or
too slowly, which produces an unnatural motion, the reclining chair of the
present invention can
be adjusted to operate evenly throughout the recline phases.
Referring now to Figures 2 through 8, each all-linkage mechanism 30, 32
includes a
recline linkage assembly 100 which is further defined by a first position
recline linkage 102, and
a second position recline linkage 104. With particular reference to Figures 3,
5 and 7, all inside
views, the first position recline linkage 102 of the recline linkage assembly
100 is disclosed.
More particularly, the first position recline linkage 102 includes a first
connecting link 106 which
is pivotally coupled at its top portion to the top of rear support link 44,
and also connected to the
rear portion of the intermediate link 60 at pivot 54. The bottom portion of
first
connecting link 106 is pivotally coupled to a base connecting link 108 at
pivot 110. The opposite
end of the base connecting link 108 is coupled to the vertical flange 56 of
the longitudinal base
rail 34 at pivot 112. Finally, a second connecting link 114 is also pivotally
coupled to both the
base connecting link 108 and the first connecting link 106 at pivot 110. The
top portion of the
second connecting link 114 is pivotally coupled to the rear portion of the
main longitudinal link
50 at pivot 116. The second connecting link 114 further includes a curved
offset top portion 118,
and is preferably formed from heavy gauge steel. Thus, the first position
recline linkage 102 is
formed by the interconnection of first connecting link 106, base connecting
link 108 and second
connecting link 114.
The primary function of the first position recline linkage 102 is to control
the forward
motion of the four-bar linkage 40 supporting the main longitudinal link 50 as
the chair 20 reclines
away from the wall surface into the intermediate position. 1n operation, the
first connecting link
106 allows the four bar linkage 40 to pivot forwardly while the base
connecting link 108 rotates
clockwise about pivot 112 until the base connecting link 108 engages the
horizontal flange 58
of the longitudinal base rail 34 (Figures 3 and 5). Once the base connecting
link 108 is
prevented from further rotating, the four-bar linkage 40 is retained in a
locked position and is
prevented from pivoting and moving forward, thus forming an exceptionally
stable base for
supporting the seat occupant in the intermediate positian. The second
connecting link 114 then
provides additional support to the rear portion of the main longitudinal link
50. As best viewed
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in Figure 8, the second connecting links 114 of each recline linkage assembly
100 are
interconnected by a cross member 156 having attachment flanges at each end.
Cross member
156 is further reinforced by a central strengthening rlb 158, which is
preferably formed during
the stamping process. The combination of the first connecting link 106, base
connecting link 108
and second connecting link 114 form a tripartite linkage assembly 120, with
the base connection
link 108 disposed between the first connecting link 106 and the second
connecting link 114.
This interconnection forming tripartite linkage assembly 120 provides a
connection which
balances the forces placed upon each side of the base connecting link 108,
thereby enhancing
the operation of the all-linkage mechanisms 30; 32.
With reference now to Figures 2 and 7, the second position recline linkage 104
of the
recline linkage assembly 100 is described in more detail. The primary function
of the second
position recline linkage 104 is to control the forward motion of the main
longitudinal link 50 from
the intermediate position to the fully reclined position, and to control the
reclining motion of the
seat back 26. The second position recline linkage includes a seat back support
link 122
having its forward end coupled to the main longitudinal link 50 at pivot 124.
As presently
preferred, pivot 124 is located approximately in line with the biomechanical
hinge point (H-point)
between the torso and the legs of an occupant properly seated in reclining
chair 20. More
specifically, as illustrated in Figure 2 pivot 124 is located forward of line
26' defined by the front
edge of seat back frame 26 and above line 22' defined by the upper edge of
seat frame 22. In
this way, the movement of pivot 124 during reclining movement coincides with H-
point. In
addition, the forward location of pivot 124 minimizes the overall fore-aft
length of all-linkage
reclining mechanisms 30,, 32, thereby enabling the use of this reclining
mechanism in
substantially smaller, compact chair frames than previously required.
A recline connecting link 126 is pivotally coupled at its tap portion to the
seat back
support link 122 at pivot 128. The lower and forward end of the recline
connecting link 126 is
pivotally coupled to ttie lower end of the vertical pivoting drive link 130 at
pivot 132. The vertical
pivoting drive link 130 is connected to the lower middle portion of the main
longitudinal link 50
at pivot 134. The upper end of the vertical pivoting drive link 130 is
pivotally connected to the
forward end of a pivot control link 136 at pivot 138. The rear end of the
pivot control link 136
is commonly connected to pivot 54 of the rear support link 44. A lost motion
slot 140 is formed
within the mid section of the pivot control link 136, which is retained
against the intermediate
link 60 by a stud 142 secured within the intermediate link 60. The combination
of the lost motion
slot 140 and the stud 142 allows for movement between these links, while also
preventing
deflection of the links during the reclining phases.
As previously described, the present invention provides a compact reclining
mechanism
which is particularly well-suited to incorporate reclining motion into a wide
variety of sizes and
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styles of chairs, love seats, and sofas. The geometry and interconnection of
vertical pivoting
drive Link 130 plays an important part in this aspect of the present
invention. More specifically,
pivot 134 between vertical pivoting drive link 130 and main longitudinal link
50 is pushed as far
forwardly as possible while maintaining the desired kinematic relationship
between the various
components of all-linkage reclining mechanisms 30, 32. As a result, vertical
pivoting drive link
130 is positioned and between front and rear support links 42, 44 and remains
so positioned
during the entire range of motion of all-linkage reclining mechanisms 30, 32.
The upstanding portion 144 of the seat back supporting link 122 includes a
rearward
facing notch 146 for receiving the locking cam mechanism 148 of the seat back
connecting
bracket 150. The seat back connecting bracket 150 is secured to the upright
side frame member
of the detachable seat back 26 with suitable fasteners. A more detailed
description of the
components associated with the seat back connecting bracket 150 can be found
in U.S. Patent
No. 5,184,871, entitled "Detachable Chair Back," which is commonly owned by
the Assignee
of the present invention.
With reference now to Figures 2, 3 and 8, the. square drive rod 80 and its
associated
drive assemblies are described in more detail. As best seen in Figure 8,
square drive rod 80
is joumally supported at each end by the main longitudinal (inks 50. A series
of drive links are
secured to the square drive rod 80 which perform various functions associated
with the all-
linkage mechanisms 30, 32. As best viewed in Figure 2, an outboard drive link
160 is rigidly
secured at each end of square drive rod 80. The opposite end of the outboard
drive link 160
is pivotally connected to the outboard pantograph connecting (ink 162 at pivot
164. The
outboard drive link 160 and the outboard pantograph connecting link 162 serve
to initiate the
extension of leg rest assembly 28 via pantograph linkage assembly 260. The
combination of
these links also serve as an over center mechanism to lock the leg rest
assembly 28 in the
retracted .position. The universally shaped outboard drive link 160 can be
used on both ends
of the square drive rod 80, and includes a connecting flange 166 for engaging
a flat surface of
the square drive rod 80. The connecting flange 166 is preferably secured to
the square drive
rod 80 with a threaded fastener 168. The outboard drive link 160 further
includes a recessed
portion 170 for receiving a stopping stud 172 formed on the outboard
pantograph connecting link
162. The stopping stud 172 prevents the over-retraction of the leg rest
assembly 28 when the
outboard drive link 160 is in the over-center position (Figures 2 and 12A).
The square drive rod 80 also includes an inboard drive (ink 180 which is
journally
supported on square drive rod 80. The inboard drive link 180 is supported by
the square drive
rod 80 near the inside face of the main longitudinal link 50 which serves to
reduce the bowing
forces placed on the square drive rod 80. The inboard drive link 180 includes
a first drive arm
182 which is pivotally connected to the inboard pantograph connecting link 192
at pivot 184, and
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a second drive arm 186 which is pivotally connected to the control link 200 at
pivot 188. Second
drive arm 186 and control link 200 operate in conjunction with the remainder
of ail-linkage
mechanisms 30, 32 and base 33 to form a pivot control assembly. In the
preferred embodiment,
various pivots in all-linkage mechanisms 30, 32 such as pivots 116, 124, 134,
184, 204 and 308
are formed using a screw-in or threaded rivet 308 which facilitates easier
manufacturing and
service. However, one skilled in the art will readily recognize that threaded
rivet 308 could be
utilized at other pivots as well.
While any suitable rivet fastener may be utilized for threaded rivet 308, a
presently
preferred threaded rivet is illustrated in Figure 17. With specific reference
thereto, threaded rivet
308 includes headed portion 330 having a drive socket 332 formed in a face
thereof. Shoulder
portion 334 extends from head portion 330 on a side opposite drive socket 332.
Threaded
portion 336 extends from shoulder portion 334 and has a self-tapping thread
formed thereon.
An annular surface 338 extending radially outwardly from threaded portion 336
includes a
serrated self locking surface formed thereon, Threaded rivet 308 further
includes wave washer
340 disposed about shoulder portion 334 and engaging the back side of headed
portion 330.
In this manner, threaded rivet 308 is used to facilitate pivotal coupling of
various components
associated with all-linkage reclining mechanisms 30,, 32. With continued
reference to Figure 17,
threaded rivet 308 pivotally connects main longitudinal support link 50 with
pantograph support
link 264. More specifically, aperture 342 is formed in main support link 50
and provides a
clearance hole for shoulder portion 334 of threaded rivet 308, Pantograph
support link 264 has
an aperture 344 formed therethrough which cooperates with threaded portion 336
of threaded
rivet 308. Upon installation, threaded rivet 308 is driven into and taps
aperture 344 until serrated
face 338 engages a surface of pantograph support link 264 to lockingly retain
threaded rivet 308
thereto. Wave washer 340 biases main longitudinal link 50 against pantograph
support link 264,
thereby removing any looseness in the pivotal coupling provided therebetween.
In addition,
shoulder portion 334 may be provided with a suitable lubricant, such as
lithium grease, to
decrease the friction at pivot 308. In this way, threaded rivet 308 provides
an efficient and
effective means for pivotally coupling various links within the linkage
reclining mechanism without
requiring the difficult task of placing the all-linkage reclining mechanism
within a riveting
apparatus during assembly. Furthermore, threaded rivet 308 facilitates field
service of the
linkage mechanisms by making them removable with a standard drive wrench.
With continued reference to Figures 2 and 8, the first drive arm 182 and the
second drive
arm 186 are preferably welded to a cylindrical connecting ferrule 190 having a
circular inner
portion which slips over the square drive rod 80. The connecting ferrule 190
maintains a rigid
connection between the first drive arm 182 and the second drive arm 186. This
rigid connection
allows power to be transferred from control link 200 and second drive arm 186,
through the first
drive arm 182 and inboard pantograph connecting link 192, and to the
pantograph linkage
assembly 260 for fully extending the leg rest assembly 28. Connecting ferrule
190 is supported
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on square drive rod 80 by a pair of plastic bushings (not shown), preferably
nylon. Accordingly,
inboard drive link 180 is journally supported by, and can move independently
of square drive rod
80.
Turning specifically to Figures 3, 5 and 7, the S-shaped control link 200 of
each all-
y linkage mechanism 30, 32 is connected between the second drive arm 186 of
the inboard drive
link 180 at upper pivot 188, and the vertical flange 56 of the longitudinal
base rail 34 at lower
forward pivot 204. As disclosed, pivot 204 of control link 200 is forward of
pivot 46 of the front
support link 42. The control fink 200 cooperates with the inboard drive link
180, in accordance
with the gravity driven and spring biased operation of this mechanism, to
impart the primary
rotational force on the inboard drive link 180 (about the square drive rod 80)
for extending the
leg rest assembly 28, and to control the reclining of the all-linkage
mechanisms 30, 32 from the
upright position to the intermediate or TV position. More specifically, as the
all-linkage
mechanisms 30, 32 move forwardly and away from the wall into the intermediate
position, the
pair of control links 200 (one for each all-linkage mechanism 30, 32) force
the angular rotation
of the inboard drive link 180. The connection of the first drive arm 182 of
the inboard drive link
180 to the inboard pantograph connecting link 192 forces the extension of the
leg rest assembly
28 via pantograph linkage assembly 260 as the mechanisms 30, 32 and chair 20
recline into the
intermediate position.
However, the geometry of the interconnections between control fink 200, and
the inboard
drive link 180 and base rail 34 contributes to the proper operation of the leg
rest assembly 28.
More specifically, as the all-linkage mechanisms 30, 32 move from the
intermediate position to
the fully reclined position, the leg rest assembly 28 must be maintained in
the fully extended
position. This in turn requires that the inboard drive link 180 and its first
and second drive arms
182, 186 also maintain a constant position as the main longitudinal finks 50
move forwardiy into
the fully reclined position. When comparing Figures 5 and 7, it can be seen
that control link 200
rotates in a clockwise direction about pivot 204 as the main longitudinal link
50 moves forwardly
and upwardly into the fully reclined position. While the purpose of control
link 200 is to impart
a rotational force on inboard drive link 180 for extending the leg rest
assembly 28 during the first
or intermediate recline phase, the control link 200 must keep the inboard
drive sink 180 stationary
during the second or full recline phase as the control link 200 rotates about
lower pivot 204.
This is accomplished through the locations and geometries associated with the
pivots 188 and
204 of the control link 200 in combination with the length of the second drive
arm 186 and the
curvilinear path defined by lost motion slot 84 and pivot 52 associated with
the adjustable seat
slide assembly 82. Accordingly, one skilled in the art will appreciate that as
the lost motion slot
84 moves forwardiy with respect to front pivot 52, control fink 200 can rotate
clockwise about
pivot 204 without causing any further rotation of the inboard drive link 180
through second drive
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arm 186. Thus, the leg rest assembly 28 is maintained in the fully extended
position as the all-
linkage mechanisms 30, 32 move from the intermediate position to the fully
reclined position.
Referring now to Figures 8 and 9, each all-linkage mechanism 30, 32 further
includes a
spring assist drive linkage 210 interconnected between the square drive rod 80
and the front
. 5 frame rail 36. The spring assist drive linkage 210 includes an over-center
drive link 212 which
is rigidly secured to the square drive rod 80 with an attachment flange 214.
The attachment
flange 214 is preferably secured to the square drive rod 80 with a threaded
fastener 216. As
disclosed, fastener 216 is a TORX~ fastener. The opposite or rearward facing
end of the over-
center drive link 212 (when chair 20 is in the upright position, Figures 2 and
3) includes a pivot
218 for connecting to C-shaped over-center connecting link 220. An aperture
222 is formed in
the opposite end of the C-shaped over-center connecting link 220 for retaining
a biasing spring
224 which connects between the over-center connecting link 220 and one of the
spring retaining
tabs 99 formed in the horizontal flange 98 of the front frame rail 36. In
operation, the spring
assist drive linkage 210 imparts a biasing force on square drive rod 80 in
either a clockwise or
counterclockwise direction, depending on which side of the center line the C-
shaped over-center
connecting link 220 is located. The spring assist drive linkage 210 biases
drive rod 80 in a first
direction when the leg rest assembly 28 is extended, and biases drive rod 80
in a second,
opposite direction when the leg rest assembly is retracted. Thus, the spring
assist drive linkage
210 provides square drive rod 80 with a rotational mechanical advantage, while
also providing
a forward force which serves to pull each all-linkage mechanism 30, 32 with
respect to the front
frame rail 36, from the upright position to the intermediate and fully
reclined positions.
The wall proximity reclining chair 20 is also provided with an adjustable
drive spring
assembly 310 which provides a forward bias to the four-bar linkage 40, and
assists in the
reclining of the chair 20. As best illustrated in Figure 8, the adjustable
drive spring 312 extends
generally between the front frame rail 36 and the rear crossmember 154. A
horizontal slot 314
formed in the rear crossmember 154 receives a spring adjustment bracket 316
having a series
of holes 318, preferably seven, formed therein. The forward and lower end of
the drive spring
312 is secured within one of the spring retaining tabs 99 formed in the
horizontal flange 98 of
the front frame rail 36. The opposite end of drive spring 312 is secured
within an aperture 320
formed in the forward end of the spring adjustment bracket 316. A retaining
pin 322 can be
selectively placed within one of the series of holes 318. By changing the
location of retaining
pin 322 within the series of holes 318, the amount of tension on drive spring
312, and thus the
amount forward force provided to the four-bar linkage 40 can be selectively
adjusted.
With reference now to Figures 12A and 12B, the cable release assembly 230
which
initiates the recline function from the upright position to the intermediate
position is described
in more detail. The cable release assembly 230 includes the cable release
mechanism 232,
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mounted to the side frame 24 of the chair 20, and the trip link assembly 234,
which is mounted
to the main longitudinal link 50 at various points. While only one cable
release assembly 230
is required, the cable release assembly 230 can be mounted to either side of
the wall proximity
reclining chair 20. The cable release mechanism 232 includes a release handle
236 pivotally
mounted to handle bracket 238. One end of the release cable 240 is secured to
the release
handle 236, and the other end of the release cable 240 is mounted to the trip
link assembly 234.
The outside sheathing 242 of the release cable 240 is secured between the
handle bracket 238
at one end, 2nd the cable mounting flange 70 of the main longitudinal link 50
at the opposite
end. The end of the outside sheathing 242 which attaches to cable mounting
flange 70 is
provided with a slotted flag 258 that can be easily slipped over cable
mounting flange 70. The
aperture fomled in slotted flag 258 fits snugly around mounting flange 70 and
can be securely
retained without a fastener. This feature allows for ease in manufacturing,
and also facilitates
in-field service because the slotted flag 258 can be easily slipped on and off
mounting flange 70.
The trip link assembly 234 includes an L-shaped trip link 250 coupled to the
main
longitudinal link 50 at pivot 244. 'The L-shaped trip link 250 has an upper
retaining pin 246 and
a lower engaging pin 248 secured thereto. The details of trip link 250 are
best illustrated in
Figure 12C. The upper retaining pin 246 includes.a circular recess 252 for
retaining the release
cable 240 and a biasing spring 254. An eyelet 241, secured to the end of cable
240, slips over
retaining pin 246, and past circular recess 252. The hook end of biasing
spring 254 is placed
into circular recess 252, which serves to secure spring 254 onto retaining pin
246, and also to
lock the eyelet 241 onto retaining pin 246. The opposite end of the biasing
spring 254 is
secured within notch 256 formed on a rearward edge of the main longitudinal
link 50. The
biasing spring 254 retains the trip fink 250 in its upper retracted position.
The biasing spring 254
also helps to secure slotted flag 258 around cable mounting flange 70 because
the release cable
240 is always under tension. The lower engaging pin 248 extends outwardly from
the L-shaped
trip link 250 far engaging the top edge or cam surface 174 of the outboard
drive link 160. The
geometry of cam surface 174 has been designed with a specific slope angle O to
optimize the
release action provided by the cable release assembly 230. As disclosed, the
slope angle O
provides additional mechanical advantage to trip link 250 for rotating
outboard drive Link 160.
The slope angle O of cam surface 174 also enables lower engaging pin 248 to
sufficiently rotate
outboard drive link 160 for initiating extension of the leg rest assembly 28
by utilizing
approximately one half of the stroke of release handle 236. Preferably, slope
angle O is
approximately 10 degrees. However, one skilled in the art will appreciate that
variations in slope
angle O are within the scope of the present invention.
When the wall proximity reclining chair 20 is in its upright position, the
outboard drive link
160 is locked into its retracted and over-center position with respect to the
square drive rod 80.
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In operation, the L-shaped trip link 250 serves to engage and rotate the
outboard drive link 160
downwardly and forwardly, thus rotating the square drive rod 80
counterclockwise, as the release
handle 236 is pulled outwardly from the chair side frame 24. The forward
rotation of outboard
drive link 160 and outboard pantograph connecting link 162 initiates the
extension of the leg rest
assembly 28 through the pantograph linkage assembly 260. As the L-shaped trip
link 250
rotates the outboard drive link 160 counterclockwise, and thus over the center-
line position, the
gravity actuated feature of the wall proximity chair 20 drives the various
reclining linkages into
the intermediate reclined position. -
Referring back to Figures 2 through 7, the leg rest assembly 28 of the wall
proximity
reclining chair 20 is disclosed in more detail. The leg rest assembly 28
includes a pantograph
linkage assembly 260 having a foot rest linkage 262 and an ottoman linkage
290. The
pantograph linkage assembly 260 is pivotally coupled to the main longitudinal
link 50 via
pantograph support link 264 at pivot 266, and pantograph drive link 268 at
pivot 270. In the
preferred embodiment, pivots 266 and 270 are formed using screw-in rivets 308
which secure
the respective links. These screw-in rivets 308 serve a dual purpose. First,
the screw-in rivets
308 make each all-linkage mechanism 30, 32 easier to manufacture because the
pantograph
linkage assembly 260 can be secured to the main longitudinal link 50 after
each sub-assembly
is fabricated. This eliminates the need for specialized fixtures for
supporting the entire
mechanism during assembly at the riveting station. Second, the screw-in rivets
308 allow the
pantograph linkage assembly 260 to be serviced in the field. If for some
reason, the pantograph
linkage assembly 260 becomes inoperable after the chair has been purchased,
the screw-in
rivets 308 allow for replacement in the field without sending the reclining
chair 20 back to the
fa cto ry.
With continued reference to Figures 2 through 7, a forward connecting link 272
is
connected to the forward end of the pantograph support link 264 at pivot 274.
The opposite end
of the forward connecting link 272 is also connected to the foot rest support
link 276 at pivot 278.
A rearward connecting link 280 includes a first pivot 282 for connecting to
the pantograph drive
link 268, an intermediate pivot 284 for connecting to the pantograph support
link 264, and a
forward pivot 286 for connecting to the foot rest support link 276. A foot
rest board 288 is
supported at each end by the foot rest support links 276 of each foot rest
linkage 262.
In the preferred embodiment, the leg rest assembly 28 includes an ottoman
linkage
assembly 290 which provides more continuous leg support to the seat occupant.
The ottoman
linkage 290 includes an ottoman support link 292 which connects to pivot 294
of the pantograph
drive link 268. The opposite end of the ottoman support link 292 includes a
flange 296 for
supporting the mid-ottoman board 298. An ottoman control link 300 is connected
between the
main longitudinal link 50 at pivot 302 and a mid-portion of the ottoman
support link 292 at pivot
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304. As described above, pivot 302 is also preferably a screw-in rivet 308 for
allowing easier
manufacturing and replacement of the pantograph linkage assembly 260. The
upholstered and
cushioned mid-ottoman board 298 rests behind the foot rest board 288, when the
chair 20 is in
the upright position. As the all-linkage mechanisms 30, 32 move from the
upright position into
the intermediate position, the ottoman linkage 290 extends forwardly and
upwardly, thereby
moving the mid-ottoman board 298 between, and in line with the foot rest board
288 and the
upholstered seat cushion, positioned on the seat frame 22. Accordingly, the
upholstered seat
cushion, mid-ottoman board 298 and leg rest board 288 provide a continuous
line of leg support
for enhancing the overall comfort of the reclining chair 20.
The outboard pantograph connecting link 162 and the inboard pantograph
connecting link
192 both connect to the pantograph drive link 268 at common pivot 306. The
opposite ends of
the outboard and inboard pantograph connecting links 162, 192 are respectively
coupled to their
associated drive links 180, 180. As described above, the primary purpose of
outboard drive link
160 and outboard connecting link 162 is to initiate the extension of the
pantograph linkage
assembly 260, and to initiate rotation of the inboard drive link 180 about
square drive rod 80 via
inboard pantograph connecting link 196. Once the inboard drive link 180
rotates to move the
control link 200 past its over center position, the spring assist drive
linkage 210 and the
adjustable drive spring assembly 310 provide additional forward biasing far
transporting the four-
bar linkage 40 into the partially reclined position. As can be appreciated
from the above
description in view of the drawings, inboard drive link 180 and inboard
pantograph connecting
fink 192 provide the primary mechanical force on pantograph drive fink 268 for
extending and
retracting each pantograph linkage assembly. This design feature further
enhances the
operation of the gravity driven recline function of the present invention.
With continued reference to Figures 2 through 7, in view of Figures 1A through
1C, the
functional operation of wall proximity reclining chair 20 is described in more
particular detail.
Each all-linkage mechanism 30, 32 is maintained in its upright position by its
spring assist drive
linkage 210. More specifically, the biasing spring 224 which extends between
the front frame
rail 36 and C-shaped over center connecting link 220 forces square drive rod
80 into its retracted
position through over-center drive link 212, thereby locking the reclining
chair 20 in the upright
position. As discussed above, the outboard drive fink 160 is also held in an
over-center
condition. However, the outboard drive link 160 is prevented from over
retracting the leg rest
assembly 28 by stopping stud 172 of the outboard pantograph connecting link
162. Additionally,
the control link 200 is also designed as a over-center mechanism which also
serves to lock the
reclining chair 20 in the upright position. Pressure from a seated occupant
causes the control
link 200 to impart a clockwise rotational force on inboard drive link 180, and
thus serves to keep
the leg rest assembly 28 retracted, and the chair 20 in the upright position.
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Upon initiating the trip link assembly 234, the leg rest assembly 28 begins to
extend, and
the main longitudinal link 50 then begins moving forwardly via the front and
rear support links
42, 44, which are pivotably coupled to the vertical flange 56 of the
longitudinal base rail 34. As
the main longitudinal link 50 moves forwardiy into the partially reclined
position, the rear portion
of the main longitudinal link 50 moves forwardly and downwardly as the
triangular linkage formed
by the rear support link 44, first connecting link 106, base connecting link
108, and second
connecting link 114, rotates downwardly about pivot 112 until the tripartite
linkage assembly 120
contacts the horizontal flange 58 of the longitudinal base rail 34. The base
connecting link 108
pivots forwardly and downwardly about its base rail pivot 112. Eventually, the
tripartite linkage
assembly 120, and especially the base connecting link 108, bottoms out against
the longitudinal
base rail 34. The mechanism is designed so that the leg rest assembly 28 is
fully extended
when the base connecting link 108 contacts the base rail 34. The forward and
downward motion
of the rear portion of the main longitudinal link 50 causes the seat back 26
to also move
downwardiy and to be tipped rearwardly through the seat back support fink 122
and recline
connecting link 126.
During this initial reclining motion, the control link 200 moves across its
pivotable center
line and into its primary range of operation. Furthermore, the control link
200 forces the
extension of the pantograph linkage assembly 260 through the rotation of
inboard drive link 180
about square drive rod 80 as the mechanism travels forwardly and downwardly in
conjunction
with the main longitudinal fink 50. As discussed above, the first position
recline linkage 102 is
primarily responsible for controlling the motion of the main longitudinal link
50 as the all-linkage
mechanism 30, 32 travels from the upright position to the intermediate
position. It should be
noted that the second position reclining linkage 104 remains essentially
stationary while the main
longitudinal link 50 is transported from the upright position to the
intermediate position. It should
also be noted that the seat back 26 cannot be reclined until the leg rest
assembly 28 is fully
extended. f_ikewise, the seat back 26 must be in the upright position before
the leg rest
assembly 28 can be fully retracted.
The second recline phase is initiated by rearward and downward pressure on the
seat
back 26, which correspondingly pivots the seat back support link 722
downwardiy about its front
pivot 124 with the main longitudinal link 50. The recline connecting link 126
is then driven
forwardly. The forward driving motion of the recline connecting link 126
causes the vertical
pivoting drive fink 130 to rotate in a counter clockwise direction about its
middle pivot 134 with
the lower portion of the main longitudinal fink 50. Accordingly, the force
provided by the seat
occupant leaning back into seat back 26 provides the requisite leveraging
force through recline
control link 104 to the recline connecting link 126 and the vertical pivoting
drive link 130 to
forwardly drive the main longitudinal link 50 with respect to the adjustable
seat slide 82. The
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second position recline linkage 104 and the adjustable seat slide 82 further
allow the seat
occupant to achieve an infinite number of positions within the range of motion
provided by lost
motion slot 84.
The front and rear support links 42, 44 remain completely stationary while the
main
longitudinal link 50 is driven forwardly and upwardly via the front seat slide
82 and second
position recline linkage 104 when the all-linkage mechanism 30, 32 is fully
reclined. Additionally,
the first connecting link 106 and base connecting link 108 of the tripartite
linkage assembly 120
also remain stationary during the second recline phase. However, the second
connecting link
114 pivots about its lower pivotable connection in a forward and upward
movement about this
lower pivot 110 during the second recline phase. This motion correspondingly
drives the rear
portion of the main longitudinal link 50 in a forward and upward direction.
Accordingly, the seat
frame 22 and seat back 26 achieve a flatter reclined position.
The chair20 is moved from the fully reclined position to the intermediate
position by the
seat occupant leaning forward so that the main longitudinal link 50 slides
rearwardly about front
seat slide 82 and second position recline linkage 104. Once in this position,
the leg rest
assembly 28 can be retracted by the seat occupant to move and lock the
reclining mechanisms
30, 32 into the upright position. This is accomplished by the seat occupant
placing downward
and rearward pressure on the leg rest assembly 28, which causes the leg rest
assembly 28 to
retract and the chair 20 to move from the intermediate position to the upright
position. When
the leg rest assembly 28 is fully retracted, the outboard drive link 160 is
moved into its over
center position, thereby locking the all-linkage mechanisms 30, 32 into the
upright position.
Extension of the leg rest assembly 28 can then be initiated by activating the
trip link assembly
234.
With reference now to Figures 13-16, a second preferred embodiment of the
present
invention is illustrated. More specifically, compact reclining chair 410
includes a chair frame 412
operably coupled to a base frame 414 through a pair of all-linkage reclining
mechanisms 416,
418. Swivel base assembly 420 is secured to a bottom portion of base frame 414
to provide a
rotational degree of freedom by a vertical axis of compact reclining chair
410.
With specific reference now to Figures 13A-C; compact reclining chair 410
includes chair
frame 412 having an arm rest or side frame 422, a seat assembly 424 having a
seat frame 426
secured to side frame 422, a reclinable seat back 428 operably coupled to all-
linkage reclining
mechanisms 416, 418, and a movable leg rest assembly 430. Compact reclining
chair 410 is
illustrated Its upright position, with leg rest assembly 430 retracted within
the chair 410 in Figure
13A. Upon manipulation of cable release mechanism 413, reclining chair 410 is
positioned into
a partially reclined or intermediate position, in which leg rest assembly 430
is fully extended and
seat back 428 is partially reclined as illustrated in Figure 13B. Chair frame
412 also tilts
rearwardly and moves forwardly with respect to base assembly 414 when
reclining chair 410 is
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moved from its upright position to its partially reclined position. Upon
pressure being applied to
seat back 428, reclining chair 410 is positioned into its fully reclined
position as illustrated in
Figure 13C. It should be noted that leg rest assembly 430 must be fully
extended before seat
back 428 can begin reclining. As will be appreciated from Figure 13C, when
reclining chair 410
is in the partially reclined position, additional rearward pressure placed
against seat back 428
urges side frame 422, seat 426 and leg rest assembly 430 fonrvardly and
further tilts chair frame
412 rearwardiy. Accordingly, all-linkage mechanism 416 maintains the rearward
most edge of
seat back 428 within approximately five to six inches (twelve to fifteen
centimeters) during the
range of motion achieved by reclining chair 410.
Referring now to Figure 14, only a portion of all-linkage mechanisms 416, 418
are
illustrated. However, it should be readily appreciated that compact reclining
chair 410 includes
right and left all-linkage mechanisms 416, 418 which are identical to right
and left all-linkage
mechanisms 30, 32 illustrated in Figures 2-12 and described in particular
reference to the first
preferred embodiment of the present invention. Accordingly, components of all-
linkage
mechanisms 416, 418 which are identical to all-linkage mechanisms 30, 32 are
given the same
reference numerals with it being understood additional components not shown or
described in
the second preferred embodiment are identical to those described and
illustrated heretofore.
All-linkage mechanisms 416, 418 are operably coupled to base frame 414 which
includes a pair
of inboard longitudinal base rails 432 and a pair of outboard longitudinal
base rails 434. Front
cross rail 436 and rear cross rail 438 are secured to the front and rear ends
of longitudinal base
rails 432, 434, respectively, to define a rigid, generally rectangular support
frame.
More specifically, with reference to Figures 15 and 16, inboard longitudinal
base rails
432, which have a generally "L-shaped" cross-section, form a welded butt joint
at an inboard
location on rear cross rail 438. The forward end 440 of inboard longitudinal
base rail 432 is
positioned above front cross rail 436 and secured thereto with a suitable
fastener. Spacer 442
is disposed between forward end 440 and front cross rail 436 to maintain an
approximately one-
quarter inch gap therebetween. Similarly, a rear end 444 of outboard
longitudinal rail 434 is
disposed beneath and secured to rear cross rail 438 with a suitable fastener.
Rear spacer 446
is disposed between rear end 444 and rear cross rail 438 to provide an
approximately one-
quarter inch space therebetween. A forward end of outboard longitudinal base
rail 434 is
disposed directly on top of front cross rail 436 and secured thereto with
suitable fasteners. In
this way, outboard longitudinal base rail 434 is situated below the remainder
of base frame 414,
thereby positioning all-linkage mechanisms in closer proximity to the floor.
With continued reference to Figure 14, all-linkage mechanisms 416, 418 are
operably
coupled to base frame 414 and support chair frame 412 for reclining movement
thereon. More
specifically, all-linkage mechanisms 416, 418 include front support fink 42,
rear support link 44,
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base connecting link 108 and control link 200, all of which are pivotally
connected to vertical
flange 448 of outboard longitudinal base rail 434 at pivots 46, 48, 110 and
204, respectively.
As previously described, compact reclining chair 410 further includes swivel
base
assembly 420 which is secured to base frame 414 to provide a rotational degree
of freedom of
reclining chair 410 with respect to the floor. In this regard, swivel base
assembly 420 includes
swivel plate 450 having an upper plate 452, secured to inboard longitudinal
base rails 432 at a
forward location and rear cross rail 438 at a rearward location with suitable
fasteners, and a
lower plate 454 secured to floor base 456 with suitable fasteners. A bearing
assembly (not
shown) is operably disposed between upper plate 452 and lower plate 454 to
permit relative
rotational movement therebetween. It should be appreciated that swivel plate
450 is positioned
within base frame 414 as a result of the location of outboard longitudinal
base rails 434 below
inboard longitudinal base rails 436, and front and rear cross rails 436, 438.
While various swivel
base assemblies may be utilized in the present invention, a presently
preferred swivel base
assembly which may optionally include a kick-out feature is presently
preferred and further
described and illustrated in U.S. Patent No. 5,857,744, which is commonly
owned by the
assignee of the present invention.
While all-linkage mechanisms 416, 418 are adapted to receive a wide variety of
sizes and
styles of chair frames, their compact nature makes them particularly well
suited for a compact,
formal reclining chair. More specifically, the compact nature of the space
requirements for all-
linkage reclining mechanisms 416, 418, as well as the limited space
requirement for operation
of compact reclining chair 410 through its range of motion makes it
particularly well suited for
this application.
The foregoing discussion discloses and describes exemplary embodiments ofthe
present
invention. One skilled in the art will readily recognize from such discussion,
and from the
accompanying drawings and claims, that various changes, modifications and
variations can be
made therein without departing from the spirit and scope of the invention as
defined in the
following claims.
