Note : Les descriptions sont présentées dans la langue officielle dans laquelle elles ont été soumises.
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Clutch mechanism of coat film transfer tool and coat film
transfer tool
BACKGROUND OF 1~ INVENTION
Field of the Invention
The present invention relates to a clutch mechanism
of a coat film transfer tool, and a coat film transfer
tool comprising this clutch mech~n;~m, and more
particularly to a clutch technology for synchronizing the
feed speed and take-up speed of coat film transfer tape in
a feed reel and a take-up reel, in a coat film transfer
tool for transferring a coat film such as corrective paint
layer, adhesive layer or the like on a coat film transfer
tape onto a sheet of paper or the like, and automatically
collecting the coat film transfer tape after use.
Description of the Related Art
An example of structure of this kind of coat film
transfer tool is shown in Fig. 21, and in this transfer
tool, in a case (a) that can be held and manipulated by a
single hand, a feed reel (c) with a coat film transfer
tape (b) wound thereabout and a take-up reel (d) for
collecting the coat film transfer tape (b') after use are
rotatably provided, and a coat film transfer head (f) for
pressing the coat film transfer tape (b) onto the object
2 1 ~3 ~464
of transfer is protruding at the front end of the case
(a). The both reels (c) and (d) are wound up
automatically as being linked by an interlock mechanism
(g) so as to cooperate with each other. In this interlock
mechanism (g), gears (h) and (i) provided on the outer
circumference of the both reels (c) and (d) are engaged
with each other.
When this coat film transfer tool is used as an
erasing tool for correcting a wrong letter or the like,
the case la) is held by one hand, and moved in a desired
direction while pressing the coat film transfer tape (b)
tightly to the correction area (the object of transfer) by
a pressing portion (j) of the head (f). As a result, the
corrective paint layer of the coat film transfer tape (b)
in the pressing portion (j) of the head (f) is applied on
the correction area, and the letter is deleted, and the
coat film transfer tape (b') after use is automatically
wound up and collected by the take-up reel (d).
In this case, as being used, the outer diameter of
the coat film transfer tape (b) on the feed reel (c)
becomes smaller, while the outer diameter of the coat film
transfer tape ~ on the take-up reel (d) becomes larger.
On the other hand, the rotation ratio of the feed reel (c)
and take-up reel (d) (corresponding to the gear ratio of
the interlock mechanism (g)) is always constant.
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Accordingly, the take-up speed of the take-up reel (d)
tends to be faster gradually as compared with the feed
speed of the feed reel (c), and to prevent this,
therefore, it is necessary to synchronize the feed speed
and take-up speed. For this purpose, the feed reel (c) is
provided with a clutch mechanism (k) for synchronizing the
feed speed and take-up speed.
That is, in the feed reel (c), a boss (m) of a drive
gear (h) rotatably supported on a support shaft (n), and a
tape feed core (o) with the coat film transfer tape (b)
wound thereabout is rotatably fitted on the boss (m), and
the clutch mechanism (k) is provided between the boss (m)
and the tape feed core (o).
In this clutch me~h~ni sm (k), elastically deforming
clutch pawls (p), (p) provided on the outer circumference
of the boss (m) are engaged with multiple stopping
portions (q), (q), ... provided in the inner circumference
of the tape feed core (o), elastically.
As the take-up speed is gradually increased as
compared with the feed speed, and the synchronism of the
two speeds is broken to increase the torque acting on the
tape feed core (o), the clutch mechanism (k) causes the
tape feed core (o) to slide and rotate on the boss (m), so
that the feed speed is synchronized with the take-up
speed.
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In such clutch mechanism (k), the engaging and
disengaging action of the clutch pawls (p), (p) and
stopping portions (q), (q), ... is intermittently repea~ed
elastically with a clicking sound, the manipulating hand
of the user may feel discomfort, and rl~nn; ng of the coat
film transfer tape (b) may be uneven, and as the use is
continued further, the engaging and disengaging action
becomes more frequent as the revolution speed of the tape
feed core (o) increases, and the discomfort and uneven
running become more obvious, and further improvements were
~m~n~ed.
Concerning this point, the present inventors already
proposed a clutch mechanism (r) as shown in Fig. 22 (see,
for example, Japanese Laid-open Patent No. 5-S8097). In
this clutch mechanism (r), a circular elastic friction
member (s) such as O-ring is interposed between the
cylindrical outer circumference of the boss (m) and the
cylindrical inner circumference of the tape feed core (o)
in a frictionally engaged state.
According to this clutch mec~n;sm (r), in the
synchronizing action, the three members (m), (s), and (o)
relatively slide smoothly, and hence the discomfort and
uneven running due to such elastic and intermittent
repeating action have been eliminated.
In the structure of this clutch mechanism (r),
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however, since the transmission of power is to make use of-
the frictional force by radial load among the three
members (m), (s), and (o), the design and manufacture
conditions of the friction member (s) are very strict, and
it is hard to manufacture, which was a bottleneck for
reducing the manufacturing cost.
That is, if the frictional force is too strong, the
sense of manipulation tends to be too heavy in the later
phase of use. On the other hand, if the frictional force
is too weak, the sense of manipulation tends to be too
light in the initial phase of use. Hence, considering
their relation, the frictional force must be set at an
optimum value.
To obtain the optimum value of frictional force,
therefore, in design and manufacture of the friction
member (s), it is required to match its inner diameter and
outer diameter respectively with the cylindrical outer
diameter of the boss (m) and the cylindrical inner
diameter of the tape feed core (o), but since the friction
member (s) itself is also elastic, its thickness in the
radial direction or its sectional diameter must be also
taken into consideration. It hence requires an additional
process for fine adjustment of the shape and ~;m~n~ions of
the friction member (s) after assembling the clutch
mechanism (r).
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Still more, since the radial ~;m~n~ions and other
conditions of the friction member (s) are set strictly, to
assemble the friction member (s) between the cylir~ica
outer circumference of the boss (m) and the cylindrical
inner circumference of the tape feed core (o), it was
needed to put in by force, and the assembling work was
difficult.
SUMMARY OF THE INVENTION
It is hence a primary object of the invention to
present a novel clutch mech~n;sm of a coat film transfer
tool solving the problems in the prior art.
It is other object of the invention to present a
clutch mech~n; sm having an inexpensive structure easy to
manufacture, by making use of a frictional force by thrust
load, in a coat film transfer tool of automatic winding
type.
It is other object of the invention to present a
coat film transfer tool of automatic winding type
comprising such clutch mechanism.
The clutch mechanism of the invention is used in a
coat film transfer tool of automatic winding type
comprising a feed reel with a coat film transfer tape
wound thereabout and a take-up reel for collecting the
coat film transfer tape after use, rotatably provided in a
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case that can be held and manipulated by one hand, in
which the take-up reel cooperates with the feed reel, for
synchronizing the feed speed and take-up speed of the coat
film transfer tape in both reels, wherein power
tr~nsm;ssion means between a tape winding portion for
w;n~;ng up the coat film transfer tape and a rotary drive
unit for rotating and driving this tape winding portion is
composed in at least one of the two reels, and power
tr~n~m;ssion of the power tr~n~m;~sion means makes use of
the frictional force by the thrust load between the tape
winding portion and the rotary drive unit, and is
connected and disconnected by the difference in torque
between these two members.
The coat film transfer tool of the invention
comprises a case having shape and dimensions to be held
and manipulated by one hand, a feed reel rotatably
provided in the case and winding a coat film transfer
tape, a take-up reel rotatably provided in the case for
collecting the coat film transfer tape after use, an
interlock mechanism for linking these two reels so as to
cooperate with each other, and a coat film transfer head
protruding at the front end of the case for pressing the
coat film transfer tape onto the object of transfer,
further comprising said clutch mech~n;sm at least in one
of the two reels.
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The coat film transfer tool comprising the clutch
mechanism is classified into the disposable type to be
discarded when the coat film transfer tape is used -~p, and
the refill type that can be used repeatedly only by
replacing the spent coat film transfer tape with a new
one.
In the coat film transfer tool comprising the clutch
mec~nism of the invention as power transmission means,
the take-up speed of the take-up reel gradually becomes
faster as compared with the feed speed of the feed reel,
and their synchronism is broken to increase the torque
acting on the tape winding portion for winding the coat
film transfer tape, and herein the clutch mechanism acts
to cause the tape winding portion to slide and rotate on
the rotary drive unit to eliminate the torque difference
between the two, so that the feed speed is synchronized
with the take-up speed.
In this case, the power tr~n~m;ssion in the clutch
mechanism makes use of the frictional force by thrust load
between the tape winding portion and the rotary drive
unit, and therefore the structual components relatively
slide smoothly in this synchronizing action.
In the structure of the clutch mechanism, by
properly adjusting the ~im~n~ional relation in the thrust
direction between the mutual structual components, the
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frictional force can be set at an optimum value.
These and other objects and features of the
invention will be better appreciated by reading tne
detailed description based on the accompanying drawings
and novel facts indicated in the claims.
BRIEF DESCRIPTION OF THE DRAWINGS
Fig. 1 (a) is a front view showing the appearance of
a coat film transfer type of refill type in embodiment 1
of the invention.
Fig. 1 (b) is a front view showing the internal
structure of the coat film transfer tool by removing the
cover body.
Fig. 2 is a longitudinal sectional view showing an
essential structure of the coat film transfer tool.
Fig. 3 is a longitudinal view showing a disassembled
state of the essential structure of the coat film transfer
tool.
Fig. 4 (a) is a magnified longitudinal sectional
view showing the engaging state of a clutch mechanism
which is an essential part in a tape drive unit of the
coat film transfer tool.
Fig. 4 (b) is a perspective view showing an O-ring
in the clutch mec~n;sm~
Fig. 5 is a perspective exploded view of the coat
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film transfer tool.
Fig. 6 (a) is a perspective view showing a rewinding
operation unit in the tape drive unit.
Fig. 6 (b) is a plan view showing the rewinding
operation unit.
Fig. 7 is a perspective view showing the operating
state of the coat film transfer tool.
Fig. 8 (a) is a longitudinal sectional view showing
essential parts of a tape drive unit in a refill type coat
film transfer tool in embodiment 2 of the invention.
Fig. 8 (b) is a magnified longitudinal sectional
view of a clutch mechanism as the essential part.
Fig. 9 (a) is a longitudinal sectional view showing
essential parts of a tape drive unit in a refill type coat
film transfer tool in embodiment 3 of the invention.
Fig. 9 (b) is a perspective view showing a sheet of
a clutch m~ch~n;sm as the essential part.
Fig. 10 (a) is a longitudinal sectional view showing
essential parts of a tape drive unit in a refill type coat
film transfer tool in embodiment 4 of the invention.
Fig. 10 (b) is a plan view showing a second engaging
portion of a clutch mech~n;sm as the essential part.
Fig. 10 (c) is a magnified longit~l~;n~l sectional
view showing the engaging state of first and second
engaging portions of the clutch mechanism.
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Fig. 11 (a) is a longitudinal sectional view showing
essential parts of a tape drive unit in a refill type coat
film transfer tool in embodiment 5 of the invention.
Fig. 11 (b) is a plan view showing a second engaging
portion of a clutch mechanism as the essential part.
Fig. 11 (c) is a magnified longitudinal sectional
view showing the engaging state of first and second
engaging portions of the clutch mechanism.
Fig. 12 ~a) is a longitudinal sectional view showing
essential parts of a tape drive unit in a refill type coat
film transfer tool in embodiment 6 of the invention.
Fig. 12 (b) is a plan view showing a second engaging
portion of a clutch mechanism as the essential part.
Fig. 12 (c) is a magnified longitudinal sectional
view showing the engaging state of first and second
engaging portions of the clutch mechanism.
Fig. 13 (a) is a longitudinal sectional view showing
essential parts of a tape drive unit in a refill type coat
film transfer tool in embodiment 7 of the invention.
Fig. 13 (b) is a perspective view showing a second
engaging portion of a clutch mechanism as the essential
part.
Fig. 14 (a) is a longitudinal sectional view showing
a clutch mechanism in a tape drive unit in a refill type
coat film transfer tool in embodiment 8 of the invention.
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Fig. 14 (b) is a perspective view showing a first
engaging portion of the clutch mechanism.
Fig. 15 (a) is a longitudinal sectional view show ns
a clutch mechanism in a tape drive unit in a refill type
coat film transfer tool in embodiment 9 of the invention.
Fig. 15 (b) is a perspective view showing a first
engaging portion of the clutch mechanism.
Fig. 16 (a) is a longitudinal sectional view showing
a disposable type coat film transfer tool in embodiment 10
of the invention.
Fig. 16 (b) is a magnified longitudinal sectional
view of a clutch mechanism of the coat film transfer tool.
J Fig. 17 is a longitudinal sectional view showing a
refill type coat film transfer tool in embodiment 11 of
the invention.
Fig. 18 is a perspective exploded view of the coat
film transfer tool.
Fig. 19 is a longitudinal sectional view showing a
disposable type coat film transfer tool in embodiment 12
of the invention.
Fig. 20 (a) is a perspective view corresponding to
Fig. 6 (a) showing a modified example of rewinding
operation unit in the tape drive unit.
Fig. 20 (b) is a plan view corresponding to Fig. 6
(b) showing the rewinding operation unit.
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Fig. 21 ~a) is a partially cut-away perspective view
of a conventional coat film transfer tool.
Fig. 21 (b) is a longitudinal sectiona' view sh^wi..g
an internal structure of the coat film transfer tool.
Fig. 22 (a) is a partially cut-away perspective view
of other conventional coat film transfer tool.
Fig. 22 (b) is a longitudinal sectional view showing
an internal structure of the coat film transfer tool.
DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS
Referring now to the drawings, preferred embodiments
of the invention are described in detail below.
Fig. 1 through Fig. 20 show film transfer tools
according to the invention, and throughout the drawings
the same reference numerals refer to same structual
members or elements.
Embodiment 1
A coat film transfer tool according to the invention
is shown in Fig. 1 through Fig. 7. This coat film
transfer tool 1 is specifically used as an erasing tool
for correcting a wrong letter or the like, and comprises
essential parts, including a tape drive unit D, a
replaceable tape cartridge C, and a coat film transfer
head H, provided in a case 2 to be held and manipulated by
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one hand.
The case 2 is a plastic flat box formed by injection
molding or the like. The case 2 has the front contour
shape and dimensions enough to incorporate the tape drive
unit D and tape cartridge C, and can be decomposed into a
case main body 3 and a cover body 4, and the structual
parts D, C, and H are provided in the case main body 3.
Flat face and back sides 2a, 2b of the case 2 form
gripping surfaces to be held and manipulated by hand as
shown in Fig. 7. Moreover, as described later, an
operation hole 38 for rewinding operation is opened in the
cover body 4.
The tape drive unit D mainly comprises, as shown in
Fig. 2, Fig. 3, and Fig. 5, a feed rotary unit 5 for
rotating and driving a feed reel 10, a take-up rotary unit
6 for rotating and driving a take-up reel 11, an interlock
mechanism 7 for interlocking these rotary units 5, 6, a
clutch mechanism 8, and a tape rewinding mechanism 9.
The feed rotary unit 5 comprises a drive side rotary
gear 20 for composing the interlock mechanism 7, and a
driven member 21 for composing a tape winding portion 12
of the feed reel 10. This driven memb~r 21 composes the
essential parts of the clutch mec~n;sm 8 and tape
rewinding mechanism 9 as described later.
A hollow rotary shaft 2Oa of the drive side rotary
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gear 20 is rotatably supported on a hollow support shaft
22 provided upright on the inner side of the case main
body 3. At the top end of the hollow support shaft 22, a
catch 22a for preventing the rotary shaft 20a from
slipping out is provided.
The driven member 21 is a hollow cylinder, and is
rotatably provided on the rotary shaft 20a of the drive
side rotary gear 20, and a tooth profile engaging portion
21a such as serration or spline is formed on its outer
circumference as shown in the drawing. At the top end of
the rotary shaft 20a, a catch 20b for preventing the
driven member 21 from slipping out is provided.
The take-up rotary unit 6 comprises a follower side
rotary gear 23 for composing the interlock mechanism 7,
and a hollow rotary shaft 23a of the rotary gear 23 is
rotatably supported on a hollow support shaft 24 provided
upright on the inner side of the case main body 3. At the
top end of the hollow support shaft 24, a catch 24a for
preventing the rotary shaft 20a from slipping out is
provided. On the outer circumference of the rotary shaft
23a, a tooth profile engaging portion 25 such as serration
or spline is formed.
The interlock mechanism 7 is composed of the drive
side rotary gear 20 and follower side rotary gear 23, and
they are engaged with each other at a specific gear ratio.
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As a result, the take-up rotary unit 6 is rotated in
cooperation with the feed rotary unit 5 always at a
specific rotation ratio. This rotation ratio, that is,
the gear ratio of the both gears 20, 23 is set properly so
that the coat film transfer tape T may be delivered and
taken up smoothly, in consideration of the winding
diameter of the coat film transfer tape T at the feed reel
10 and take-up reel 11 as mentioned later.
The clutch mechanism 8 is to synchronize the feed
speed and take-up speed of the coat film transfer tape T
in the feed reel 10 and take-up reel 11 described later,
and is provided in the feed rotary unit 5.
A specific constitution of the clutch mech~n;sm 8 is
shown in Fig. 4, which comprises, as a principal part, an
elastomer O-ring (friction member) 30 interposed between
the drive side rotary gear 20 and the driven member 21.
This O-ring 30 composes a power transmission unit
(power transmission means) between the drive side rotary
gear 20 as the rotary drive unit, and the driven member 21
which is the tape winding portion 12, and is made of
silicone rubber having a circular section (see Fig. 4
(b)). The O-ring 30 is repulsively interposed between the
confronting axial ends of the both members 20, 21, and
these three members contact with each other in frictional
engagement state. For this purpose, a recess 31 having a
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flat engaging plane 31a is formed on the outer
circumference of the rotary shaft 20a in the drive side
rotary gear 20, and the lower end of the driven me~ber 21
also a flat engaging plane 21b, and the O-ring 30 is
repulsively engaged by friction with these engaging planes
31a, 21b.
Therefore, power transmission of the clutch
mech~n; sm 8 makes use of frictional force due to thrust
load acting between the engaging planes 3la, 2lb, and this
frictional force is set at an optimum value by properly
adjusting mainly the distance between the engaging planes
31a, 21b, and the sectional diameter of the O-ring 30.
Moreover, a position defining unit 32, for example,
may be provided in the recess 31 (see double dot chain
line in Fig. 4 (a)), and the distance between the engaging
planes 31a, 21b may be defined within a specific value.
In such structure, excessive compressive deforming of the
O-ring 30 may be effectively prevented, and the clutch
mechanism 8 may function always with a stable frictional
force. In particular, considering that the driven member
21 serves also as the operation unit of the tape rewinding
mechanism 9 described later, there is a possibility of
application of excessive thrust load to the O-ring 30, and
hence it is preferred to form such position defining unit
32
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The inner and outer diameters of the O-ring 30 are
set properly within a range allowing the O-ring 30 to be
passed through the rotary shaft 20a in the drive side
rotary gear 20, and to contact with the both engaging
planes 31a, 21b. Therefore, for example, by setting the
inner diameter of the O-ring 30 slightly larger than the
outer diameter of the rotary shaft 20a, the O-ring 30 can
be incorporated into the outer circumference of the rotary
shaft 20a, that is, the recess 31, easily and smoothly.
Further, as shown in Fig. 5, a reverse rotation
preventive mechanism 35 to prevent reverse rotation of the
reels 10, 11 is provided in the take-up rotary unit 6.
This reverse rotation preventive mechanism 35 is composed
of a detent pawl 35a provided in the follower side rotary
gear 23, and multiple reverse rotation preventive pawls
35b, 35b, ... provided on the inner side of the case main
body 3 annularly and concentrically with the hollow
support shaft 24. Accordingly, if the both reels 10, 11
rotate in the arrow direction, the detent pawl 3Sa rides
over while elastically deforming the reverse rotation
preventive pawls 35b, 3Sb, ..., thereby allowing this
normal rotation. On the other hand, when the both reels
10, 11 move to rotate in the opposite direction of the
arrow direction, the detent pawl 35a is engaged with any
one of the reverse rotation preventive pawls 35b, 3Sb,
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..., and blocks the reverse rotation. Alternatively, the
reverse rotation preventive me~h~n;sm 35 may be provided
in the drive side rotary gear 20.
The tape rewinding mechanism 9 is designed to
eliminate and remove the slack of the coat film transfer
tape T between the feed reel 10 and take-up reel 11, and
is provided in the tape winding portion 12 of the feed
reel 10.
More specifically, the tape rewinding mechanism 9
comprises the hollow cylindrical driven member 21 as
principal constituent part as mentioned above, and a top
end 36 of the driven member 21 is extended, and a
rewinding operation unit 37 is integrally formed in the
hollow edge.
The rewinding operation unit 37 faces to the outside
of the case 2 through the operation hole 38 formed in the
cover body 4 of the case 2. The rewinding operation unit
37 is set so as to be flush with or lower than the surface
of the case 2, or the gripping surface 2a (see Fig. 4
(a)). As shown in Fig. 6, the rewinding operation unit 37
is formed in an operation groove, and a plate-shaped
operation member 39 such as a coin may be engaged with
this operation groove 37.
In the illustrated embodiment, since the top end 36
is a hollow cylindrical form, the operation groove 37 is
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formed of a pair of grooves 37a, 37a provided at edges on
one straight line in the top end 36. The depth of the
grooves 37a, 37a is set in a range so as to be engagea
with the operation member 39, in consideration of the
height position of the top end portion of the rotary shaft
20a. The number of operation grooves 37 may be properly
increased. As mentioned above, meanwhile, considering the
appearance of the coat film transfer tool 1, the hollow
support shaft 22 is concealed by the top end portion of
the rotary shaft 20a so as not to be visible from outside.
Correspon~;ng to the operation groove 37, the inner
circumference of the operation hole 38 of the cover body 4
is formed in a taper form as shown in Fig. 4 (a), and it
is designed to engage and operate the operation member,
for example, the coin 39 from outside of the case 2 into
the operation groove 37.
The tape cartridge C is a replaceable constituent
member as a consumable part, and its specific structure is
shown in Fig. 2, Fig. 3, and Fig. 5. In the tape
cartridge C, the feed reel 10 and take-up reel 11 are
rotatably provided on a supporting base plate 40 made of a
thin plate material, and the tape cartridge C is
detachably mounted on the tape drive unit D of the case
main body 3 as shown in Fig. 2 and Fig. 3.
The feed reel 10 and take-up reel 11 are provided
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with hollow drums 45, 46 for winding the coat film
transfer tape T.
These drums 45, 46 have their support ends rotatablv
supported on the support base plate 40. In the inner
circumference of the drums 45, 46, tooth profile engaging
portions 45a, 46a such as serration or spline are formed,
respectively corresponding to the tooth profile engaging
portion 21a of the driven member 21 and the tooth profile
engaging portion 25 of the rotary shaft 23a of the
follower side rotary gear 23.
The drum 45 of the feed reel 10 is detachably
engaged and supported on the driven member 21 through
these tooth profile engaging portions 45a, 21a, and are
hence integrated with the driven member 21 in the rotating
direction to form the tape winding portion 12. On the
other hand, the hollow drum 46 of the take-up reel 11 is
detachably engaged and supported on the rotary shaft 23a
through the tooth profile engaging portions 46a, 25, and
mounted integrally and rotatably with the rotary shaft
23a.
On the outer circumference of the drum 45 of thç
feed reel 10, the coat film transfer tape T is wound, and
the feeding side leading end is connected to the outer
circumference of the drum 46 of the take-up reel 11. As
the coat film transfer tape T, for example, on one side of
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a film base material (about 25 to 38 ~m in thickness) such
as polyester film, acetate film, other plastics, or paper,
a releasing agent layer such as vinyl chloride-vi.ny'
acetate copolymer resin or low molecular weight
polyethylene is formed, and a white corrective paint layer
is formed thereon, and further an adhesive agent (pressure
sensitive adhesive) layer such as polyurethane having a
pressure-sensitive adhesion is formed thereon (specific
structure is not shown). As the corrective paint layer,
so-called dry type is used so as to be able to write
thereon immediately after transfer.
The free end of the drum 45 of the feed reel 10 is
an open end as it is, and a tape running guide flange 47
is provided at the free end of the drum 46 of the take-up
reel 11.
The layout of the reels 10, 11 on the support base
plate 40 is as shown in Fig. 2, in which the drums 45, 46
are set so as to be positioned coaxially with respect to
the feed rotary unit 5 and take-up rotary unit 6 of the
tape drive unit D.
On the support base plate 40 near the mounting
positions of the reels 10, 11, a pair of guide pins 48, 49
for guiding the coat film transfer tape T are provided
upright and integrally. One guide pin 48 is for guiding
the coat film transfer tape T being paid out from the feed
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reel 10, and the other guide pin 49 is for guiding the
coat film transfer tape T' being taken up on the take-up
reel 11, and a flanged guide roller 49a is rotata~ly
supported on the guide pin 49.
In the tape cartridge C, as shown in Fig. 2 and Fig.
3, the reels 10, 11 are engaged with the both rotary units
5, 6 of the tape drive unit D respectively from above, and
the support base plate 40 is mounted on these rotary units
5, 6. As a result, the both reels 10, 11 are instantly
set detachably and integrally rotatably in the both rotary
units 5, 6. On the other hand, by lifting the support
base plate 40 directly to the upper side, the both reels
10, 11 can be instantly detached easily from the both
rotary units 5, 6.
The coat film transfer head H is for pressing the
coat film transfer tape T on the correction area (object
of transfer) such as wrong letter on a sheet of paper, and
it is rotatably fitted on a cylindrical front end 50 of
the case 2. The cylindrical leading end 50 is composed by
assembly of cylindrical halves of the case main body 3 and
cover body 4.
The head H is made of plastics having a certain
elasticity. The leading or front end portion of the head
H is a thin plate slightly wider than the coat film
transfer tape T as shown in Fig. 1, and is formed in a
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taper section to be gradually thinner toward the leading
end, and the leading end Ha of the head H is the pressing
portion for pressing the coat film transfer tape T. Pt
both edges of the leading end portion of the head H, guide
flanges Hb, Hb for guiding running of the coat film
transfer tape T are formed.
The base end portion of the head H is
semicylindrical having a semicircular section, and is
rotatably supported on the cylindrical front end 50 of the
case 2. Reference numeral 51 denotes an arc-shaped flange
for positioning in the axial direction provided at the
base end of the head H, and this flange 51 is rotatably
fitted to an annular groove 52 of the cylindrical front
end 50.
With the tape cartridge C being set on the tape
drive unit D, the coat film transfer tape T is paid out
from the feed reel 10, as shown in Fig. 1 (b), and is
inverted through the pressing portion Ha of the head H
through the guide pin 48, and is further wound around the
take-up reel 11 through the guide pin 49.
In this relation, although not shown specifically,
by rotating and manipulating a cap member 53 detachably
fitted to the cylindrical front end 50, the head H is
selectively positioned at the shown application position
(laterally pulling position), and the orthogonal coat film
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- 21 87464
transfer tape exchange position (also vertically pulling
position).
In the former application position, the pressing
portion Ha of the head H guides the coat film transfer
tape T so that the coat film transfer tape T may be nearly
opposite to the gripping surfaces 2a, 2b of the case
2,that is, the face and back sides of the coat film
transfer tape T may be directed nearly in the same
direction to the gripping surfaces 2a, 2b (that is, nearly
parallel to each other). On the other hand, at the latter
coat film transfer tape exchange position, the pressing
portion Ha of the head H guides the coat film transfer
tape T so that the coat film transfer tape T may remain in
the winding position of the feed reel 10 and take-up reel
11, that is, the face and back sides of the coat film
transfer tape T may be directed nearly in opposite
direction to the gripping surfaces 2a, 2b (that is, nearly
orthogonal to each other).
In thus constructed coat film transfer tool 1, by
the pressing operation of the coat film transfer head H as
mentioned later, a tensile force applied to the coat film
transfer tape T (arrow A direction in Fig. 1) acts on the
feed reel 10 as torque, the drive side rotary gear 20 is
rotated through the tape winding portion 12 of the feed
reel 10, and further through the clutch mechanism 8. This
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torque rotates the follower side rotary gear 23 and
further the take-up reel 11 in cooperation through the
interlock mech~n; sm 7, so that the coat film transfer tape
T' after use is taken up automatically by the take-up reel
11 .
In this case, the rotation ratio of the drive side
rotary gear 20 and follower side rotary gear 23
(corresponding to the gear ratio of the interlock
mechanism 7) is always constant, whereas the ratio of the
outer diameter of the coat film transfer tape T in the
feed reel 10 and the outer diameter of the coat film
transfer tape T~ in the take-up reel 11 varies with the
passing of time and is not constant. That is, as being
used, the outer diameter of the coat film transfer tape T
in the feed reel 10 becomes gradually smaller, while the
outer diameter of the coat film transfer tape T' in the
take-up reel 11 gradually increases to the contrary.
Hence, the take-up speed of the take-up reel 11 is
gradually increased in comparison with the feed speed of
the feed reel 10, and the synchronism of the two speed is
broken, and the torque acting on the feed reel 10
gradually increases. In consequence, this torque
overcomes the frictional force of the clutch mechanism 8,
and the tape winding portion 12 slides and rotates against
the drive side rotary gear 20, and the torque difference
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between the both reels 10, 11 is eliminated, and the feed
speed is synchronized with the take-up speed, so that
smooth running of the coat film transfer tape T is
assured.
As mentioned above, power transmission in the clutch
mechanism 8 makes use of the frictional force by the
thrust load between the tape winding portion 12 and the
drive side rotary gear 20, and in the construction of the
clutch mech~n;.cm 8, the frictional force can be set to an
optimum value by properly adjusting the relative
~;men~ions in the thrust direction among the constituent
members 20, 21, 30.
! Due to wrong handling by the user or the like, if
the coat film transfer tape T is slacked between the feed
reel 10 and take-up reel 11, the operation groove 37 of
the tape rewinding mechanism 9 is rotated and manipulated
in the rewinding direction from outside of the case 2
(rotating in the direction of arrow B in Fig. 1 (b)), and
thereby the slack of the coat film transfer tape T is
eliminated and removed.
In this case, the torque in the rewinding direction
s applied to the driven member 21 through the operation
groove 37 is transmitted to the drum 45 through the tooth
profile engaging portions 21a, 45a, and the drum 45
rotates in the rewinding direction B. On the other hand,
21 ~7464
by the reverse rotation blocking force by the reverse
rotation preventive mechanism 35 and the action of the
clutch mechanism 8, the rotary gears 20, 23 of the 'apc
drive unit D and the drum 46 of the take-up reel 11 are
set in stopped state. As a result, the slack of the coat
film transfer tape T between the both reels 10, 11 is
eliminated and removed.
In the coat film transfer tool 1 of the embodiment,
by selectively positioning the head H at either laterally
pulling position or vertically pulling position, it is
usable in both lateral pull suited to correction of part
of sentence written laterally as in European language, and
in vertical pull suited to correction of part of sentence
written vertically as in Japanese language.
For example, in the use for lateral pull, as shown
in Fig. 7, the gripping surfaces 2a, 2b of the case 2 are
held like a writing tool. In this gripping position, the
pressing portion Ha of the head H is fitted to the
starting end (left end) of the correction area (object of
transfer) on the paper to correct a wrong letter or the
like, and is directly moved laterally, that is, in the
right direction on the paper and stopped at the terminal
end (right end) of the correction area 60.
By this operation, the corrective paint layer
(white) of the coat film transfer tape T in the pressing
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21 87464
portion Ha of the head H is peeled off from the film base
material, and is transferred and applied on the correction
area 60. As a result, the wrong letter is concealed, and
a correct letter can be immediately written over.
Embodiment 2
This embodiment is shown in Fig. 8, and the clutch
mechanism 8 of embodiment 1 is slightly modified.
That is, in the clutch mech~ni ~m 68 of the
embodiment, the engaging plane 21b of the driven member 21
is formed so as to surround the O-ring 30 as shown in a
magnified sectional view in Fig. 6 (b). That is, the
engaging plane 21b is composed of an annular flat surface
70a frictionally engaged with the upper surface of the O-
ring 30 opposite parallel to the engaging plane 31a of the
drive side rotary gear 20, and a cylindrical inner
circumference 70b frictionally engaged with the outer side
of the O-ring 30 opposite to the rotary shaft outer
circumference 71 of the drive side rotary gear 20.
For power transmission of the clutch mechanism 68,
both the frictional force by thrust load acting between
the annular flat surface 70a and engaging plane 31a, and
the frictional force by radial load acting between the
cylindrical inner circumference 70b and rotary shaft outer
circumference 71 are utilized.
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` _ 21 ~7464
In this case, power transmission of the clutch
mechanism 68 is mainly based on the frictional force by
thrust load, and the frictional force by radial load is
only supplementary for adjusting the transmission force,
so that fine adjustment of pressure is enabled.
A lower end portion 72 for forming the cylindrical
inner circumference 70b of the driven member 21 functions,
same as the position defining portion 32 in embodiment 1,
as the position defining portion for suppressing the
distance between the annular flat surface 70a and the
engaging plane 3la within a set value, and hence prevents
the O-ring 30 from being compressed and deformed
excessively in the vertical direction.
The other construction and action are same in
embodiment 1.
Embodiment 3
This embodiment is shown in Fig. 9, and the clutch
mechanism 8 of embodiment 1 is slightly modified.
That is, in the clutch mechanism 78 of the
embodiment, a plastic friction sheet 80 is used as a
friction member interposed between the engaging plane 2lb
of the driven member 21 and the engaging plane 31a of the
drive side rotary gear 20.
This friction sheet 80 is a thin wall plate material
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2 1 & 7464
formed in an annular form as shown in Fig. 9 (b), and its
upper and lower flat surfaces are frictionally engaged
respectively with the engaging planes 31a, 21b.
The inner and outer diameters and thickness of the
annular friction sheet 80 are set in the same conditions
as the inner and outer diameters and sectional diameter of
the O-ring 30 in embodiment 1.
The other construction and action are same in
embodiment 1.
Embodiment 4
This embodiment is shown in Fig. 10, in which the
friction member in the clutch mechanism of embodiments 1
to 3 is omitted, and the driven member 21 and drive side
rotary gear 20 are directly engaged with each other
frictionally.
That is, in the clutch mechanism 88 of the
embodiment, in the confronting axial end surfaces of the
driven member 21 and drive side rotary gear 20, a first
engaging portion 89 and a second engaging portion 90 are
respectively formed, and these engaging portions 89, 90
are engaged frictionally.
These engaging portions 89, 90 are composed of
plural ~nn~ r ribs 89a, 90a provided concentrically with
the driven member 21 and drive side rotary gear 20. These
2 ~ 87464
annular ribs 89a, 90a have both angle sections consisting
of a pair of slopes as shown in Fig. 10 (c), and the
diameters of these confronting annular ribs 89a, 90a are
set slightly different from each other. Consequently,
these annular ribs 89a, 90a are composed so that the
slopes on one side may contact frictionally with each
other as shown in Fig. 10 (c).
Therefore, the frictional force of the clutch
mechanism 88 can be adjusted by increasing or decreasing
the contact area of the annular ribs 89a, 90a or the
contacting force, and in this case, the frictional
coefficient of the constituent materials of the driven
member 21 and drive side rotary gear 20 tfor example, ABS
(acrylonitrile-butadiene-styrene) resin, etc.) is also
taken into consideration.
According to this e-m-bodiment~ as compared with the
foregoing e-m-bodiments~ the number of parts is decreased,
and it is suited to mass production, so that the
manufacturin cost and product cost may be curtailed.
The other construction and action are same in
embodiment 1.
Embodiment 5
This embodiment is shown in Fig. 11, and the clutch
mec~n;sm 88 of embodiment 4 is slightly modified.
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2 ~ ~7464
_
That is, in the clutch mechanism 98 of the
embodiment, a first engaging portion 99 of the driven
member 21 is formed on a flat plane, and a second engaging
portion 100 of the drive side rotary gear 20 is composed
of plural annular ribs lOOa (see Fig. 11 (b)) same as the
second engaging portion 90 of embodiment 4 (see Fig. 10).
As a result, the flat plane 99 and the leading ends of the
annular ribs lOOa, lOOa, ... are formed to contact with
each other frictionally (see Fig. 11 (c)).
Therefore, the frictional force of the clutch
mechanism 98 can be adjusted by increasing or decreasing
the height of the annular ribs lOOa. Although not shown,
moreover, the engaging portions 99, 100 may be formed in
reverse composition of the composition shown in Fig. 11,
that is, the first engaging portion 99 may be composed of
plural annular ribs, and the second engaging portion 100
may be formed on a flat plane.
The other construction and action are same in
embodiment 4.
Embodiment 6
ThiS embodiment is shown in Fig. 12, and the clutch
mechanism 88 of embodiment 4 is slightly modified.
That is, in the clutch mechanism 108 of the
embodiment, a first engaging portion 109 of the driven
~ 218746i-t
member 21 is formed on a flat plane, and a second engaging
portion 110 of the drive side rotary gear 20 is composed
of multiple radial ribs llOa (see Fig.12 (b)), formed at
equal intervals in the circumferential direction,
concentrically with the drive side rotary gear 20. As a
result, the flat plane 109 and the leading ends of the
radial ribs llOa, llOa, ... are formed to contact with
each other frictionally ~see Fig. 12 (c)).
Therefore, the frictional force of the clutch
mechanism 108 can be adjusted by increasing or decreasing
the height of the radial ribs llOa. Although not shown,
moreover, the engaging portions 109, 110 may be formed in
reverse composition of the composition shown in Fig. 12,
that is, the first engaging portion 109 may be composed of
multiple radial ribs, and the second engaging portion 110
may be formed on a flat plane.
The other construction and action are same in
embodiment 4.
Embodiment 7
This embodiment is shown in Fig. 13, and the clutch
mechanism 88 of embodiment 4 is slightly modified.
That is, in the clutch mechanism 118 of the
embodiment, a first engaging portion 119 of the driven
member 21 is formed on a flat plane, and a second engaging
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21 ~746~
portion 120 of the drive side rotary gear 20 is composed
of plural (four in this drawing) engaging protrusions 120a
having elasticity in the axial direction, that is, the
vertical direction.
The engaging protrusions 12Oa are, more
specifically, formed as being extended outward in the
radial direction from the outer circumference of the
rotary shaft 2Oa of the drive shaft rotary gear 20 as
shown in Fig. 13 ~b), and the engaging protrusions 120a
are disposed at equal intervals in the circumferential
direction on the outer circumference of the rotary shaft
2Oa. In this relation, the rotary shaft 2Oa and the outer
circumference of the drive side rotary gear 20 are coupled
by plural (four in this drawing) coupling members 121
disposed between engaging protrusions 120a, 120a.
The flat plane 109 and the leading ends of the
engaging protrusions 120a, 120a, ... are formed to contact
with each other frictionally (see Fig. 13 (a)).
The frictional force of the clutch mechanism 118 can
be adjusted by increasing or decreasing the elastic force
applied to the engaging protrusions 120a, or increasing or
decreasing the number of engaging protrusions 120a.
The other construction and action are same in
embodiment 4.
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21 ~746~
Embodiment 8
This embodiment is shown in Fig. 14, and the clutch
mechanism 88 of embodiment 4 is slightly modified.
That is, in the clutch mechanism 128 of the
embodiment, a first engaging portion 129 of the driven
member 21 is composed of plural engaging protrusions 129a
having elasticity in the axial direction, and a second
engaging portion 130 of the drive side rotary gear 20 is
formed on a flat plane.
The engaging protrusions 129a are specifically
formed by projecting radially downward from the lower end
outer peripheral edge of the driven member 21, and are
disposed at equal intervals on the whole circumference in
the circumferential direction at the lower end outer
peripheral edge of the driven member 21.
The leading ends of the engaging protrusions 129a
and the flat plane 130 are formed to contact with each
other frictionally, and the frictional force of the clutch
mechanism 128 can be adjusted by increasing or decreasing
the elastic force applied to the engaging protrusions
129a, or increasing or decreasing the number of engaging
protrusions 129a.
The other construction and action are same in
embodiment 4.
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2 1 ~7464
E~nbodiment 9
This embodiment is shown in ~ig. 15, and the clutch
me--h~n;.cm 128 of embodiment 8 is slightly modified.
That is, in the clutch mechanism 138 of the
embodiment, a first engaging portion 139 of the driven
member 21 is an annular engaging flange having elasticity
in the axial direction, or the vertical direction, and a
second engaging portion 140 of the drive side rotary gear
20 is formed on a flat plane. The engaging flange 139 is
specifically in a form of conical flange having a
sectional shape projecting radially downward from the
lower end outer peripheral edge of the driven member 21.
The le~l;ng end of the engaging flange 139 and the
flat plane 140 are formed to contact with each other
frictionally, and the frictional force of the clutch
me~h~n;sm 138 can be adjusted by varying the projection
length or inclination angle of the engaging flange 139.
The other constitution and action are same in
embodiment 8.
Embodiment 10
This embodiment is shown in Fig. 16, relating to a
disposable type for discarding the coat film transfer tape
T when used up, as compared with the refill type
illustrated in embodiments 1 to 9.
21 &7464
That is, in the coat film transfer tool of the
embodiment, the feed reel 10 and take-up reel 10 are
rotatably provided in the case 2 respectively, and these
reels 10, 11 are provided with automatic W;n~;ng
mechanism.
More specifically, in the foregoing embodiments, the
tape winding portion 12 of the feed reel 10 was separated
into the driven member 21 and drum 45, whereas they are
formed integrally in this embodiment, and the tape W;n~;ng
portion 12 is rotatably provided on the rotary shaft 20a
of the drive side rotary gear 20. At the support end side
of the tape winding portion 12, a tape running guide
flange 150 is integrally provided. This guide flange 150
is designed to slide on the upper surface of the drive
side rotary gear 20, and functions as a position defining
unit for suppressing the distance between both engaging
planes 31a, 21b of the clutch mechanism 8 within a set
value.
On the other hand, the drum 46 of the take-up reel
11 and rotary shaft 23a of the follower side rotary gear
23, which were in separate structure in the foregoing
embodiments, are integrated in the embodiment, and the
take-up reel 11 and follower side rotary gear 23 are
formed integrally. At the support end side of the take-up
reel 11, a tape running guide flange 151 is also formed
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21 3746~
integrally, and this guide flange 151 is designed to slide
on the upper surface of the drive side rotary gear 20.
Although not shown, the coat film transfer head H
may be provided either rotatably about the axial center or
stationarily, at the cylindrical leading end 50 of the
case 2. The mounting angle of the coat film transfer head
H in the rotating direction may be variable depending-on
the purpose, that is, in the lateral pulling position as
shown in Fig. 1 and Fig. 7 in the case of the coat film
transfer tool 1 for lateral pulling use, or in the
vertical pulling position, orthogonal to the lateral
pulling position, in the case of coat film transfer tool 1
for vertical pulling use.
The other construction and action are same in
embodiment 1.
Embodiment 11
This embodiment is shown in Fig. 17 and Fig. 18,
relating to a double clutch type installing another clutch
mechanism 158 at the take-up rotary unit 6, in the
constitution of the coat film transfer tool of embodiment
1.
The specific construction of this clutch mechanism
158 is same as that of the clutch mechanism 8 of the feed
rotary unit 5. That is, a driven member 159 is interposed
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2 ~ ~7464
between the rotary shaft 23a of the follower side rotary
gear 23 and the drum 46 of the take-up reel 11, and a tape
winding portion 160 of the take-up reel 11 is composed by
this driven member 159 and drum 46. The mutual coupling
structure of the rotary shaft 23a, driven member 159 and
drum 46 is same as in the clutch mechanism 8, and an O-
ring 161 is interposed as friction member between the
engaging planes 159a, 23b of the driven member 159 and
follower side rotary gear 23. The other specific
construction corresponds to the clutch mechanism 8.
In the constitution of such double clutch type,
action of excessive tension on the coat film transfer tape
T during rewinding operation by the tape rewinding
mechanism 9 can be effectively prevented.
That is, as mentioned above, when operated to rewind
by the tape rewinding mechanism 9, the drum 45 rotates in
the rew; n~i ng direction, and the drum 46 is in stopped
state by the action of the reverse rotation preventive
mechanism 35, so that the slack of the coat film transfer
tape T between the both reels 10, 11 is eliminated and
removed.
In this case, if rewinding operation is continued
after the slack of the coat film transfer tape T is
eliminated and removed due to wrong operation or the like,
this time, to the contrary, an excessive tension acts on
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2 1 ~7464
the coat film transfer tape T. If such status should
occur, by the action of the clutch mechanism 158, the tape
winding portion 160 slides and rotates on the follower
side rotary gear 23, so that breakage of the coat film
transfer tape T can be prevented.
The other construction and action are same in
embodiment 1.
Embodiment 12
This embodiment is shown in Fig. 19, and the double
clutch structure of refill type in embodiment 11 is
modified to the disposable type as in embodiment 10.
That is, in the coat film transfer tool of the
embodiment, the construction of the feed reel 10 side is
exactly same as in the construction of embodiment 10 (see
Fig. 16). On the other hand, a tape winding portion 160
of the take-up reel 11 is integrated as shown, and the
tape w;n~;ng portion 160 is rotatably provided on the
rotary shaft 23a of the follower side rotary gear 23. At
the support end side of the tape winding portion 160, a
tape rl~nn;ng guide flange 151 is integrally provided.
This guide flange 151 slides on the upper surfaces of the
follower side rotary gear 23, and function as a position
defining unit for suppressing the distance between two
engaging planes 159a, 23b of the clutch mechanism 158
- 41 -
- 2 1 ~7464
within a set value.
Although not show, the construction of the coat film
transfer head H is same as in embodiment 10, and other
construction and action are same in embodiment 11.
In the foregoing embodiments 1 to 12, the following
modifications are also possible.
(1) The clutch mechanism in embodiments 2 to 9 can
be also applied to the coat film transfer tool of the
disposable type as in embodiment 10.
(2) In embodiments 1 to 10, the clutch mechanism is
disposed at the feed reel 10 side, but it may be also
disposed at the take-up reel 11 side dep~n~; ng on the
purpose.
(3) As the friction member of the clutch mechanism
in embodiments 1 to 3, leaf spring, belleville spring,
other spring member, and various washers having elasticity
in the thrust direction may be used.
(4) The specific structure of the first and second
engaging portions of the clutch mechanism in embodiments 4
to 9 is not limited to the illustrated embodiments alone,
but other structures having similar function may be
employed.
(5) As the coat film transfer tape T, by using the
structure forming an adhesive agent on one side of a base
film through a releasing agent layer, the coat film
- 42 -
- 21 a7464
transfer tool may be used as an applicator for
transferring only the a & esive agent layer on the paper.
(6) The specific structure of the rewinding
operation unit and the driven member formed integrally
therewith is not limited to the illustrated embodiments
alone, but other structures that can be easily manipulated
from outside of the case 2 may be employed.
For example, in the illustrated embodiments, the
driven member 21 or tape winding portion 12 is in a hollow
cylindrical form, and rewinding operation units 37, 57 are
provided in the hollow edge, but the free end of the
driven member 21 or tape rewinding portion 12 may be
closed, and the rewinding operation units 37,57 may be
provided at this closed end. In this case, by the closed
end of the driven member 21 or tape winding portion 12,
the rotary shaft 20a and hollow support shaft 22 are
concealed from outside, so that a simple appearance may be
presented.
Alternatively, the rewinding operation unit 57 as
shown in Fig. 20 may be employed. That is, the rewinding
operation unit 57 has an anti-skid shape that can be
manipulated by finger or the like, and specifically it is
composed of anti-skid undulations 57a, 57a, ... such as
tread pattern.
As described herein, according to the invention, the
- 43 -
21 87464
clutch mechanism for synchronizing the feed speed and
take-up speed of the coat film transfer tape at the feed
reel and take-up reel composes the power transmission unit
between the tape winding portion for winding the coat film
transfer tape and the rotary drive unit for rotating and
driving the tape winding portion, at least in one of the
both reels, and the power transmission of this power
transmission unit makes use of the frictional force due to
thrust load between the tape winding portion and the
rotary drive unit, and therefore each constituent member
slides smoothly and relatively in synchronizing action,
and the sense of manipulation is excellent and uneven
running does not occur.
The construction of the clutch mechanism may be
determined by properly adjusting the ~im~n.sional relation
in the thrust direction among mutual constituent members,
and the frictional force may be set to an optimum value,
and as compared with the conventional structure making use
of frictional force due to radial load (see Fig. 22), the
designing and manufacturing conditions of constituent
members are less strict and the manufacture is easy,
assembling is easy, and hence the manufacturing cost and
device cost may be also lowered.
In the coat film transfer tool having a tape
rewinding mechanism, when the clutch mechanism is provided
- 44 -
- 21 87464
also in the take-up reel as well as in the feed reel, in
rewinding operation by the tape rewinding mechanism,
action of excessive tension on the coat transfer tape can
be effectively prevented.
As the invention may be embodied in several forms
without departing from the spirit of essential
characteristics thereof, the present embodiments are
therefore illustrative and not restrictive, since the
scope of the invention is defined by the appended claims
rather than by the description preceding them, and all
changes that fall within metes and bounds of the claims,
or equivalence of such metes and bounds thereof are
therefore intended to be embraced by the claims.
