NZ622337B2 - Screwdriver tool with improved corner fit function - Google Patents
Screwdriver tool with improved corner fit function Download PDFInfo
- Publication number
- NZ622337B2 NZ622337B2 NZ622337A NZ62233712A NZ622337B2 NZ 622337 B2 NZ622337 B2 NZ 622337B2 NZ 622337 A NZ622337 A NZ 622337A NZ 62233712 A NZ62233712 A NZ 62233712A NZ 622337 B2 NZ622337 B2 NZ 622337B2
- Authority
- NZ
- New Zealand
- Prior art keywords
- feed tube
- drive
- slide body
- nosepiece
- subassembly
- Prior art date
Links
- 239000000789 fastener Substances 0.000 claims abstract description 97
- 150000002500 ions Chemical class 0.000 claims description 12
- 238000006073 displacement reaction Methods 0.000 claims description 10
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- 238000004891 communication Methods 0.000 claims description 4
- 239000000463 material Substances 0.000 claims description 2
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- 238000005516 engineering process Methods 0.000 description 26
- 210000003811 Fingers Anatomy 0.000 description 11
- 239000004033 plastic Substances 0.000 description 8
- 229920003023 plastic Polymers 0.000 description 8
- 239000007787 solid Substances 0.000 description 5
- 210000003128 Head Anatomy 0.000 description 4
- 238000010304 firing Methods 0.000 description 4
- 230000004048 modification Effects 0.000 description 3
- 238000006011 modification reaction Methods 0.000 description 3
- 230000037250 Clearance Effects 0.000 description 2
- 210000001331 Nose Anatomy 0.000 description 2
- 239000004809 Teflon Substances 0.000 description 2
- 210000003813 Thumb Anatomy 0.000 description 2
- 230000035512 clearance Effects 0.000 description 2
- 230000001808 coupling Effects 0.000 description 2
- 238000009432 framing Methods 0.000 description 2
- 229920001343 polytetrafluoroethylene Polymers 0.000 description 2
- 230000003245 working Effects 0.000 description 2
- NLZUEZXRPGMBCV-UHFFFAOYSA-N Butylhydroxytoluene Chemical compound CC1=CC(C(C)(C)C)=C(O)C(C(C)(C)C)=C1 NLZUEZXRPGMBCV-UHFFFAOYSA-N 0.000 description 1
- 229940035295 Ting Drugs 0.000 description 1
- 230000001010 compromised Effects 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 229920002457 flexible plastic Polymers 0.000 description 1
- 239000002783 friction material Substances 0.000 description 1
- 238000003780 insertion Methods 0.000 description 1
- 230000004301 light adaptation Effects 0.000 description 1
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- 238000004513 sizing Methods 0.000 description 1
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Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
- B25B—TOOLS OR BENCH DEVICES NOT OTHERWISE PROVIDED FOR, FOR FASTENING, CONNECTING, DISENGAGING OR HOLDING
- B25B23/00—Details of, or accessories for, spanners, wrenches, screwdrivers
- B25B23/02—Arrangements for handling screws or nuts
- B25B23/04—Arrangements for handling screws or nuts for feeding screws or nuts
- B25B23/045—Arrangements for handling screws or nuts for feeding screws or nuts using disposable strips or discs carrying the screws or nuts
Abstract
automatic fastener driving tool, or an attachment, has a narrow front-end profile so that it is capable of driving screws that are in hard-to-reach positions, such as corners or channel members. The slide body subassembly has an extending mechanism, so that the fastener drive elements extend farther away from the main body structure of the tool/attachment, while still providing a stable and rugged overall tool structure to drive larger screws. The "lick-out" dimension is increased without also increasing the length and width of the feed tube. her away from the main body structure of the tool/attachment, while still providing a stable and rugged overall tool structure to drive larger screws. The "lick-out" dimension is increased without also increasing the length and width of the feed tube.
Description
SCREWDRIVER TOOL WITH IMPROVED CORNER FIT FUNCTION
CROSS-REFERENCE To RELATED APPLICATIONS
The present application claims priority to patent application Serial No.
13/288,982, titled DRIVER TOOL WITH ED CORNER FIT
FUNCTION," filed on November 4, 2011; and claims priority to patent application Serial No.
13/288,985, titled "SCREWDRIVER TOOL WITH IMPROVED LINEAR TRACKING,"
filed on November 4, 2011.
TECHNICAL FIELD
The technology disclosed herein relates generally to automatic screw driving
equipment and is particularly directed to an automatic screw driving tool or an attachment of
the type which has a narrow front—end profile so that it is e of driving screws (or other
rotatable fasteners) that are in hard—to—reach positions, such as s or angled members.
Embodiments are specifically disclosed as having an extending mechanism within an
elongated slide body subassembly, so that the drive elements extend r away from the
main body structure of the tool/attachment, while still providing a stable and rugged l
tool structure to ly drive screws. One embodiment uses a timing belt structure; another
embodiment uses a gear train structure.
Another feature of the technology disclosed herein is an external depth of
drive adjustment subassembly that is mounted external to the feed tube housing, yet has a
simple adjustment that does not lose its setpoint easily. By g the depth of drive
mechanism outside of the interior areas of the feed tube, the slide body subassembly can be
shortened while still maintaining an easily adjustable depth of drive capability.
A r feature of the technology disclosed herein is the use of a dovetail
shape on certain surfaces of the slide body subassembly, which allows the slide body
subassembly to be robustly mounted so that it is capable of operating with long fasteners
while also having the ece mounted in an extended position for use with those fasteners.
STATEMENT REGARDING FEDERALLY SPONSORED RESEARCH OR
PMENT
None.
BACKGROUND
Conventional automatic fastener driving tools that work with strips of collated fasteners
lly have a movable slide body subassembly that can slide into an open internal area of a
feed tube or feed housing. Unfortunately, the conventional automatic fastener driving tools
typically have a problem fitting into relatively small areas so as to be able to drive a rotatable
fastener into one of those small areas. Mainly this is because the feed tube housing is rather
large in size, and as the slide body subassembly “collapses” into the feed tube, the narrower
nosepiece becomes insignificant with respect to the size of the feed tube itself. In essence, the
tool will not be able to fit into a small area, because the feed tube is , and that limitation
will not allow the er to be driven while the tool is attempting to fit into that small area.
Accordingly, there is a need to e an automatic fastener driving tool or attachment
that has an extending mechanism to increase the “lick-out” characteristic of the tool so it can fit
into smaller areas for driving rotatable fasteners.
There is also a need to provide an automatic fastener driving tool or attachment that
includes a timing belt drive within its slide body subassembly, to increase the distance that the
tool’s drive bit can extend past the feed housing while maintaining a relatively small crosssectional
area of the slide body subassembly.
There is also a need to provide an automatic fastener driving tool or attachment that
es a gear-driven sprocket within its slide body subassembly, to increase the distance that
the tool’s drive bit can extend while maintaining a relatively small cross-sectional area of the
slide body subassembly.
There is also a need to e an tic fastener driving tool or attachment that has
a slide body subassembly that moves along linear guides, in which the surfaces of the slide body
subassembly are dovetailed to e a stronger, more durable surface along the guide rails to
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support an extending mechanism within the slide body subassembly, thereby having an
ed linear tracking capability.
There is also a need to provide an automatic fastener driving tool or attachment that has
an external depth of drive adjustment mounted at the rear portion of the feed tube g, to
allow for an extended e for the slide body subassembly to act t the linear guides of
the feed tube.
OBJECT
It is an object of the present ion to substantially y one or more of the above
needs.
SUMMARY
[0011a] There is disclosed herein a drive apparatus for a rotatable fastener driving tool, said
drive apparatus comprising:
an elongated feed tube;
a rotatable drive bit; and
an extending mechanism that is actuated by relative movement, and that has an output
member which creates an indexing motion;
wherein said elongated feed tube has a first end and a second, opposite end along a
longitudinal axis, said feed tube having an open volume ithin, said first end being open
and sized and shaped to receive said extending mechanism, said second end having an opening
to receive said rotatable drive bit that extends through said open volume, said feed tube having a
slidable surface, said drive bit having a distal end that, along said udinal axis, is located a
distance P from said first end of the feed tube, said feed tube having a maximum outer width
dimension W and a maximum outer height dimension H;
wherein:
(a) during operation, said extending mechanism is movable with respect to said feed
tube, along said slidable surface of the feed tube, which is relative movement that actuates said
extending mechanism; and
(b) a ratio P/W is in the range of 0.50 to 1.50.
AH26(10257301_1):TCW
[0011b] There is also sed herein a drive apparatus for a rotatable fastener driving tool,
said drive apparatus comprising: an elongated feed tube, and a slide body structure;
wherein:
said slide body structure is actuated by relative movement, and has an output member
which creates an indexing motion, said slide body structure having a dovetail shaped body
; and
said elongated feed tube having a first end and a second, te end along a
longitudinal axis, said feed tube having an open volume therewithin, said first end being open
and sized and shaped to receive said slide body structure, said feed tube having an elongated
slidable surface at an interior location, said slidable surface having a shape that corresponds to
mate against said dovetail shaped body member, wherein during operation, said slide body
structure is movable with respect to said feed tube along said slidable surface of the feed tube,
which relative movement actuates said slide body structure.
[0011c] There is further disclosed herein a drive apparatus for a ble fastener g tool,
said drive tus comprising:
an elongated feed tube,
a slide body subassembly;
wherein:
said slide body subassembly is actuated by relative movement, and has an output
member which creates an indexing motion;
said elongated feed tube has a first end and a second, opposite end along a longitudinal
axis, said feed tube having an open volume therewithin, said first end being substantially open
and sized and shaped to receive said slide body subassembly, said feed tube having an elongated
slidable surface and, during operation, said slide body subassembly is e with t to
said feed tube, which relative movement actuates said slide body subassembly;
an elongated nosepiece that is adjustably affixed to said slide body subassembly, said
nosepiece having a third end and a fourth, opposite end along an axis of nt that is
substantially parallel to said longitudinal axis, said third end extending past said first end of the
feed tube so as to contact a surface of a workpiece, said fourth end extending toward said second
end of the feed tube and having a first contact e; and
a depth of drive subassembly that is mounted proximal to the second end of said feed
tube, said depth of drive subassembly including a e member that has a second contact
AH26(10257301_1):TCW
surface, said first contact surface of the fourth end of the nosepiece coming into mechanical
communication with said second t surface at the end of a fastener driving cycle.
[0011d] There is also disclosed herein a drive apparatus for a rotatable fastener driving tool,
comprising:
a slide body subassembly that is actuated by relative movement, and that has an output
member which creates an indexing motion;
an elongated feed tube having a first end and a second, opposite end along a
longitudinal axis, said feed tube having an open volume therewithin, said first end being
substantially open and sized and shaped to receive said slide body subassembly, said feed tube
having an elongated le surface and, during operation, said slide body subassembly is
movable with respect to said feed tube, which relative movement actuates said slide body
subassembly;
an elongated nosepiece that is adjustably affixed to said slide body subassembly, said
nosepiece having a third end and a fourth end at opposite positions along an axis of movement
that is substantially parallel to said longitudinal axis, said third end extending past said first end
of the feed tube so as to contact a surface of a workpiece, said fourth end ing toward said
second end of the feed tube; and
a depth of drive subassembly that is mounted at an al location with respect to said
feed tube, said depth of drive subassembly having an adjustable mechanism that engages with
said fourth end of the ece.
In accordance with one aspect, a slide body subassembly for a rotatable fastener g
tool apparatus is provided, the slide body embly comprising: (a) a drive gear having a first
axis of rotation, the drive gear having a first set of engagement ions along one of its
surfaces at a first position along the first axis of rotation, the drive gear having a set of ratchet
teeth at a second position along the first axis of rotation; (b) a sprocket having a second axis of
rotation that is substantially parallel to the first axis of rotation, and that is spaced-apart from the
drive gear, the et having a first plurality of spaced-apart protrusions along an outer curved
surface at a third on along the second axis of rotation, the sprocket having a second set of
engagement extensions at a fourth position along the second axis of rotation; (c) a drive belt that
runs between the drive gear and the sprocket, the drive belt having a second plurality of spacedapart
protrusions along one of its surfaces, the second plurality of -apart protrusions being
in mechanical engagement with the first set of engagement extensions of the drive gear and
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being in mechanical engagement with the second set of engagement extensions of the sprocket,
the drive belt being caused to move if the drive gear rotates, and the drive belt then causing the
sprocket to rotate; and (d) a displacement action mechanism that causes the drive gear to rotate
by way of the set of ratchet teeth; and a feed tube with at least one sliding e, which allows
the slide body subassembly to move with respect to the feed tube, which movement es the
displacement action mechanism.
AH26(10257301_1):TCW
In accordance with another aspect, a slide body subassembly for a rotatable
fastener driving tool apparatus, the slide body subassembly comprising: (a) a drive gear
having a first axis of rotation, the drive gear having a first set of gear teeth along one of its
surfaces at a first position along the first axis of rotation, the drive gear having a set of t
teeth at a second position along the first axis of rotation; (b) a et having a second axis
of rotation that is ntially parallel to the first axis of rotation, and that is spaced—apart
from the drive gear, the sprocket having a plurality of spaced—apart protrusions along an outer
curved surface at a third position along the second axis of rotation, the sprocket having a
second set of gear teeth along one of its surfaces at a fourth position along the second axis of
rotation; (c) at least one intermediate gear having at least one intermediate axis of rotation,
the at least one intermediate gear having at least one third set of gear teeth that are in
mechanical engagement with the first set of gear teeth of the drive gear and being in
ical engagement with the second set of gear teeth of the sprocket, the at least one
intermediate gear being caused to move if the drive gear rotates, and the at least one
intermediate gear then causing the et to rotate; (d) a displacement action mechanism
that causes the drive gear to rotate by way of the set of ratchet teeth; and a feed tube with at
least one sliding surface, which allows the slide body subassembly to move with respect to
the feed tube, which movement actuates the displacement action mechanism.
In accordance with yet another aspect, a drive apparatus for a rotatable
fastener driving tool is provided, which comprises: an extending mechanism that is actuated
by relative movement, and that has an output member which creates an indexing motion; and
an elongated feed tube having a first end and a second, opposite end along a longitudinal axis,
the feed tube having an open volume therewithin, the first end being open and sized and
shaped to receive the extending mechanism, the second end having an g to receive a
rotatable drive bit that extends h the open volume, the feed tube having a slidable
e, the drive bit having a distal end that, along the longitudinal axis, is located a ce
P from the first end of the feed tube, the feed tube having a m outer width dimension
W and a maximum outer height dimension H; wherein: (a) during operation, the extending
mechanism is movable with respect to the feed tube, along the slidable surface of the feed
tube, which is relative movement that actuates the extending mechanism; and (b) a ratio P/W
is greater than or equal to 0.5.
In accordance with still another aspect, a drive apparatus for a rotatable
fastener driving tool is ed, which comprises: an extending mechanism that is ed
by relative nt, and that has an output member which creates an indexing motion; and
an elongated feed tube having a first end and a , opposite end along a longitudinal axis,
the feed tube having an open volume therewithin, the first end being open and sized and
shaped to receive the extending mechanism, the second end having an opening to receive a
rotatable drive bit that extends through the open volume, the feed tube having a slidable
surface, the drive bit having a distal end that, along the longitudinal axis, is located a distance
P from the first end of the feed tube, the feed tube having a maximum outer width dimension
W and a maximum outer height dimension H; wherein: (a) during operation, the extending
mechanism is movable with t to the feed tube, along the le surface of the feed
tube, which is relative nt that actuates the extending mechanism; and (b) a ratio P/H
is greater than or equal to 0.5.
In accordance with a further aspect, a drive apparatus for a rotatable fastener
g tool is provided, which comprises: a slide body structure that is actuated by ve
movement, and that has an output member which creates an indexing motion, the slide body
structure having a dovetail shaped body member; and an elongated feed tube having a first
end and a second, opposite end along a longitudinal axis, the feed tube having an open
volume therewithin, the first end being open and sized and shaped to receive the slide body
structure, the feed tube having an elongated slidable surface at an interior location, the
slidable surface having a shape that corresponds to mate against the il shaped body
member, wherein during operation, the slide body structure is movable with respect to the
feed tube along the slidable surface of the feed tube, which relative movement es the
slide body structure.
In accordance with a yet further aspect, a drive apparatus for a rotatable
fastener driving tool is provided, which ses: a slide body subassembly that is actuated
by relative movement, and that has an output member which creates an indexing motion; an
elongated feed tube having a first end and a second, opposite end along a longitudinal axis,
the feed tube having an open volume therewithin, the first end being substantially open and
sized and shaped to receive the slide body subassembly, the feed tube having an elongated
slidable surface and, during operation, the slide body embly is movable with respect to
the feed tube, which relative movement actuates the slide body subassembly; an elongated
nosepiece that is adjustably affixed to the slide body subassembly, the nosepiece having a
third end and a fourth, opposite end along an axis of movement that is substantially parallel to
the longitudinal axis, the third end ing past the first end of the feed tube so as to
contact a surface of a workpiece, the fourth end extending toward the second end of the feed
tube and having a first contact surface; and a depth of drive subassembly that is mounted
al to the second end of the feed tube, the depth of drive subassembly including a
movable member that has a second contact surface, the first contact surface of the fourth end
of the nosepiece coming into mechanical communication with the second contact surface at
the end of a fastener driving cycle.
In ance with a still further aspect, a drive apparatus for a rotatable
fastener driving tool is provided, which ses: a slide body subassembly that is ed
by relative movement, and that has an output member which creates an indexing motion; an
elongated feed tube having a first end and a , te end along a longitudinal axis,
the feed tube having an open volume therewithin, the first end being ntially open and
sized and shaped to receive the slide body subassembly, the feed tube having an elongated
slidable surface and, during operation, the slide body subassembly is e with respect to
the feed tube, which relative movement actuates the slide body subassembly; an elongated
nosepiece that is adjustably affixed to the slide body subassembly, the nosepiece having a
third end and a fourth end at te positions along an axis of nt that is
ntially parallel to the longitudinal axis, the third end extending past the first end of the
feed tube so as to contact a surface of a workpiece, the fourth end extending toward the
second end of the feed tube; and a depth of drive subassembly that is mounted at an external
location with respect to the feed tube, the depth of drive subassembly having an adjustable
mechanism that engages with the fourth end of the nosepiece.
Still other advantages will become apparent to those skilled in this art from the
following description and drawings wherein there is described and shown a preferred
embodiment in one of the best modes plated for carrying out the technology. As will
be realized, the technology disclosed herein is capable of other different embodiments, and its
several details are capable of modification in various, obvious aspects all without departing
from its principles. Accordingly, the drawings and descriptions will be regarded as
illustrative in nature and not as restrictive.
BRIEF DESCRIPTION OF THE DRAWINGS
Preferred embodiments of the invention will be described hereinafter, by way of
examples only, with reference to the accompanying drawings.
is a ctive view of a full assembly of the attachment tool technology
disclosed herein as it is mounted to a conventional screwdriver gun.
is an exploded view in perspective of the assembly illustrated in
is a perspective view of the drive gear of the tool of
is an elevational view of the drive gear of
is a perspective view of the sprocket of showing the sprocket from the
“gear side.”
is a perspective view of the sprocket of showing the sprocket from the
“detent side.”
is a side elevational view of the sprocket of showing its “gear side.”
is a side elevational view of the sprocket of showing its t side.”
is a side view of the detent finger used in the tool of
is perspective view of the detent finger of
is a perspective view of the feed pawl of showing its m side.”
is a perspective view of the feed pawl of , g its “top side.”
is a top elevational view of the feed pawl of .
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is a perspective view of the slide body t used in the tool of FIG.
is a side elevational view of the slide body support of .
is a perspective view of the slide body cover used in the tool of FIG.
is a side ional view of the slide body cover of .
is a perspective view of the drive belt subassembly of the tool of g the ents from the “belt side.”
is a perspective view of the drive belt subassembly of ,
showing its “detent side.”
is a perspective view of the slide body support subassembly, used in
the tool of
is a perspective view from the front comer of the tool of
showing the nosepiece, slide body subassembly, feed tube housing, and linear guides.
is a top plan view of the front end of the tool of showing the
tool in its unactuated position, with the nosepiece extended.
is a cross—section view from the front of the tool of , taken
along the section line 23—23.
is a top plan view of the front portion of the tool of showing
the tool in its actuated position, with the nosepiece pushed somewhat into the feed housing.
is a cross—section view of the front of the tool of , taken along
the section line 25—25.
shows two views of a prior art automatic screwdriver tool, shown in
its unactuated state: A, which is a top plan view in cross—section; and B,
which is a side elevational view taken from the right side of the tool.
shows two views of a prior art automatic screwdriver tool, shown in
its actuated state: A, which is a top plan view in cross—section; and B, which is
a side elevational view taken from the right side of the tool.
is a side elevational view of the tool of in its unactuated state.
is a side elevational view of the tool of in its actuated state.
is a side elevational view of a front portion of the tool of
showing details of the slide body embly with the slide body support d, with the
tool in its unactuated state.
is a side elevational view of a front portion of the tool of
showing details of the slide body subassembly with the slide body t removed, with the
tool in a partially actuated state, such that the drive bit is about to engage the head of the
fastener that is in the drive position.
is a perspective view of an alternative embodiment tool of the
technology disclosed herein, showing the extending mechanism as being completely gear—
driven, rather than belt—driven.
is a perspective view of the adjustable depth of drive subassembly
used in the tool of
is an exploded view of the depth of drive subassembly of .
is side—elevational view of the depth of drive subassembly of ,
with the subassembly on its side.
is a cross—section view of the depth of drive subassembly of ,
taken along the section line 36—36 of .
is a perspective view of the front portion of the tool of with
part of the feed tube housing ay, to show the arrangement of the depth of drive
subassembly of and the rear portion of the ece.
is a perspective view of the technology disclosed herein as it would be
used in an integral tic screwdriving tool.
DETAILED DESCRIPTION
Reference will now be made in detail to the t preferred ment, an
example of which is illustrated in the accompanying drawings, wherein like numerals
indicate the same elements throughout the views.
It is to be understood that the technology disclosed herein is not limited in its
ation to the details of construction and the arrangement of components set forth in the
following description or illustrated in the drawings. The technology disclosed herein is
capable of other embodiments and of being practiced or of being carried out in various ways.
Also, it is to be understood that the phraseology and terminology used herein is for the
purpose of description and should not be regarded as limiting. The use of “including,”
“comprising,’ 9 or “having” and variations thereof herein is meant to encompass the items
listed thereafter and equivalents thereof as well as additional items. Unless d otherwise,
the terms “connected,” “coupled,” and “mounted,” and variations f herein are used
broadly and encompass direct and indirect connections, couplings, and mountings. In
addition, the terms “connected” and “coupled” and variations thereof are not restricted to
physical or mechanical connections or couplings.
Referring now to the drawings, shows a hand—held fastener g tool
combination, generally designated by the reference l 5. In this embodiment, there is
an attachment assembly 10 (the “attachment,” or sometimes referred to as the “tool” or the
“attachment tool”), a te screw gun 6, and an adapter 8. This type of separate screw gun
6 is available from many different manufacturers, including Senco Products, Inc. and
DeWalt. The screw gun 6 has an output bit (not visible in this view) that can drive the head
of a screw or other type of ble fastener.
The attachment 10 mates to the front end of the screw gun 6 by use of a
separate adapter 8. Once the ment 10 has been mounted to the screw gun 6, a collated
strip of screws can be used with the screw gun 6, via this attachment 10. ment
assembly 10 includes a housing portion 20, a front end portion 30, a feed rail portion 40, and
a screw feed portion 50. Fastener driving tool 10 is designed for use with a flexible strip of
collated screws, and the flexible collated screw strip subassembly is generally designated by
the reference numeral 60.
The housing portion 20 of the tool includes a front “feed housing” outer shell
structure 22, and bottom ng surface 24. Housing portion 20 is also sometimes referred
to herein as an "elongated housing. H Toward the front of housing portion 20 is an elongated
“feed tube” 26, which houses certain movable portions of the tool 10, as discussed below. In
the illustrated embodiment, the feed tube 26 is fixedly attached to the housing portion 20, and
is also sometimes referred to herein as a "first member." It will be understood that feed tube
26 can be of any desirable cross—sectional shape while performing its functions (e.g.,
rectangular, square), and that it is ntially square in cross—section in the illustrated
ments. The feed tube 26 has a longitudinal axis that runs between a substantially open
front end and a substantially open rear end, which are at opposite ends of the feed tube; a
drive bit 66 fits through the rear end of the feed tube, and is substantially parallel to the
longitudinal axis. The feed tube 26 is mainly hollow, that is, it has an interior volume that is
mostly empty space, to allow the slide body subassembly to move in and out of the front end
of the feed tube.
The collated strip 60 subassembly slides through a feed rail 42 that is mounted
onto pedestals 46 and 48 that are mounted to the upper surface of the housing 22. On the
lower surface of the housing 22 is a grip area 24, for placement of the user's hand.
Attachment 10 includes an innovative external depth of drive ment subassembly 80 (see
, and typically will have a depth of drive indicator (not . The housing 22 thus
exhibits a "mating end" near the adapter 8, which receives the front end of the screw gun 6.
The front end portion 30 includes a moveable nosepiece 32, which is attached
to a slide body embly 34. Both the ece 32 and slide body subassembly 34 are
moveable in a longitudinal direction of the tool 10, and when the nosepiece 32 is pressed
against a solid object, the fastener driving tool 10 will be actuated to physically drive one of
the screws into the solid object, also referred to herein as the "workpiece." Nosepiece 32 has
a front surface 36, which preferably has a rough texture such as sandpaper, so that it will not
easily slide while pressed against the surface of the workpiece when the tool is to be utilized.
In the illustrated embodiment of the nosepiece 32 is detachable from
the slide body subassembly 34 so that the nosepiece can be itioned for different lengths
of ers, and then ached. The ece 32 has a ity of screw length
positioning holes 38 (see , which are used to attach nosepiece 32 to the slide body
subassembly 34 at different ve positions to one another. The nosepiece is thus
adjustably affixed (i.e., mounted) to the slide body subassembly. Slide body subassembly 34
is also sometimes referred to herein as a "second member," or an “elongated slide body.”
The nosepiece 32 also has a rear inclined edge 119, which works against another inclined
surface 95 that is part of a depth of drive subassembly 80, which is described in greater detail
below, in conjunction with the description of FIGS. 33—36. Nosepiece 32 is elongated, and
has two opposite ends: a front end at 36 and a rear end at the inclined edge 119. As the tool
is actuated (during a fastener driving event), nosepiece 32 has an axis of movement that is
substantially parallel to the longitudinal axis of the feed tube 26.
The slide body embly 34 is y “attached” to the feed tube 26,
such that slide body subassembly 34 essentially slides along predetermined surfaces proximal
to feed tube 26. In addition, an angled slot 28 is formed in feed tube 26 to e a
g action surface (essentially a slotted opening having a curved portion and a straight
portion) for a cam roller (or “cam follower”) 70 (see to traverse as the slide body
subassembly 34 moves, relative to the feed tube 26. This action is used to cause the "next"
fastener of the collated strip (see below) to index to a "firing position" (or “drive position”),
by way of an indexing action of the slide body subassembly 34 (which ng action is
internal to the slide body subassembly).
The guide rail portion 40 includes a straight guide member 42, and an angled
“front n” guide member 44, that each can e a flexible collated strip of ers,
in this case the collated screw embly 60. The collated screw subassembly 60 mainly
consists of a plastic strip 62 that has several openings to receive individual screws 64. The
overall collated screw subassembly is flexible to a certain degree, as can be seen in FIGS. 30
and 31 by the curved orientation of the plastic strip 62 as it is fed through the slide body
subassembly 34.
Some of the mechanical mechanisms described above for the portable fastener
g tool 10 have been available in the past from Senco Products, Inc. and Senco Brands,
Inc., including such tools as the Senco Model Nos. DS162—14V and DS200—14V. These
r tools utilized a fixed feed tube, a movable slide body, and nosepiece structure, without
the “extended nose” feature of the technology disclosed herein. Some of the components
used in the technology disclosed herein have been disclosed in commonly—assigned patents or
patent applications, ing a United States Patent No. 5,988,026, titled SCREW FEED
AND DRIVER FOR A SCREW DRIVING TOOL; a United States Patent No. 7,032,482,
titled TENSIONING DEVICE APPARATUS FOR A BOTTOM FEED SCREW DRIVING
TOOL FOR USE WITH COLLATED ; and a United States Patent No. 7,082,857,
titled SLIDING RAIL CONTAINMENT DEVICE FOR LE ED SCREWS
USED WITH A TOP FEED SCREW DRIVING TOOL. These patent properties have been
assigned to Senco Brands, Inc., and their sures are incorporated herein by reference in
their ties.
The main purpose of tool 10 is to drive rotatable fasteners (e.g., screws or
bolts) that are ed in the form of the flexible ed strip subassembly 60. The
individual screws 64 are held in place by a flexible plastic strip 62, and as the screws traverse
through the guide members 42 and 44, they are ultimately directed toward the front end
portion of the tool 30 until each of the screws 64 reaches the "drive" position at 68. When
viewing the tool 10 at its front—most portion, the left—most screw 64 has been indexed to the
drive position at 68 (see , for example), and thus is now essentially co—linear with the
main drive components of the tool 10. As the collated screw subassembly 60 is moved
through the screw feed portion 50, the plastic strip 62 will eventually make contact with a
sprocket 130 (see that acts as a rotary indexer, and which is located inside the slide
body subassembly 34. The sprocket moves each of the portions of the plastic strip 62 into a
proper rotary position so that their attached screws 64 eventually end up in the front—most
drive position 68. The sprocket is sometimes referred to herein as the “output member” of
the slide body subassembly, which s an indexing motion.
When the nosepiece 32 is actuated by being pressed against a workpiece, then
a drive bit 66 will push the screw at 68 into the workpiece, and the drive bit 66 will also then
be turned in a rotary motion to twist the screw at 68 in the normal manner for driving a screw
64 into a solid object. Once the screw at 68 has been successfully driven into the solid object,
then the tool 10 is withdrawn from the surface of the solid object, and of course the screw 64
remains behind and has now broken free from the plastic strip 62 (see : the “lead
screw” at 68 will break free from the plastic strip 62). In one mode of the technology
disclosed herein, the tool 10 will now be free to allow the sprocket to perform its rotary
indexing function and to bring forth the next screw 64 into the front—most drive position at
68. This type of feed actuation can be ed to as "indexed on return," since the
"lead screw" is moved into the "firing position" at 68 as the nosepiece 32 is released (or
"returned") from the surface of the workpiece.
The tool 10 can also be configured in an ative screw—feed actuation
mode, in which the lead screw is moved into the firing position at 68 as the nosepiece 32 is
pressed against the surface of a workpiece; this type of screw—feed actuation can be referred
to as "indexed on e." If tool 10 is configured for indexed on advance, then the lead
screw would not yet be in the position at 68 at the moment the nosepiece 32 is "relaxed" or
"free," in its ring state. Instead, the lead screw is not indexed into the firing position at
68 until the ece 32 is "pushed in" (or "advanced") toward the main body portion of the
tool 10 (e.g., toward the adaptor 8), which is discussed below in greater detail. Note that the
d on advance configuration is a preferred mode of operation for tool 10. It will be
understood that both the indexed on advance and indexed on return feed actuation
modes of operation can work with the technology disclosed herein.
Referring now to many of the components of the tool 10 are rated
in an exploded view, which allows most of the internal components of the slide body
subassembly 34 to be viewed. A slide body cover 104 is mated to a slide body support 102,
and these two rather large structures will contain the mechanical components that make the
slide body subassembly operate. Assembled into the slide body cover is a detent pin 108,
which travels through a detent housing 106, through a detent spring 110, into an opening of
the cover 104. Detent pin 108 mates into an opening of a slide body subassembly plate 120.
There is a nosepiece adjustment subassembly that fits through one of the
openings 38 in the nosepiece 32, and also is operatively connected to the slide body cover
104. This nosepiece adjustment subassembly is made up of a r 114, a cap 112, and a
spring 116. A pair of ers 122 and 124 are used to hold the plate 120 in place with
respect to the slide body cover 104. There is a stop member 118 that prevents the nosepiece
32 from extending past a certain point.
also illustrates an “extending mechanism” that is positioned between
the plate 120 and the slide body t 102. There are several major components in this
extending mechanism, including a sprocket 130, a drive gear 140, a timing belt 150, and a
feed pawl 160. There also is a detent finger 162, a torsion spring 164, and a locating pin 166,
which operate with the drive feed pawl 160. The operations of these mechanisms will be
described in greater detail, below.
The sprocket 130 is mounted between locating bushing holes on the slide body
support and cover (102 and 104). The drive gear 140 is mounted to a bushing e (or
bearing surface) on the feed pawl 160, and is held in place between that and the slide body
support 102, and a pilot hole in the plate 120. The drive feed pawl 160 is allowed to pivot
within a slot of the plate 120 and the combination of a cam follower 70 and a cam screw 72,
that fit within r slot in slide body t 102, holds the feed pawl in its proper
orientation. The plate 120 is held in place with respect to the slide body support 102 by the
fasteners 122, 124, and 126.
As noted above, the slide body subassembly 34 is movable within the “feed
tube” 26 and “feed housing” 22. There are two linear guides 170 and 172 that are mounted
within the feed housing 22, and the slide body subassembly 34 has specific es that slide
t the linear guides. This will be described in greater detail below. Linear guides 170
and 172 are preferably made of a very low friction material, such as TEFLON.
The drive bit 66 also fits through a main portion of the feed housing 22,
through a spring post 194. The spring post 194 is attached to the feed housing 22 by two
fasteners 190 and 192. A large coil spring 67 fits around the circular bearing surface of
spring post 194, and s against a rear surface of the slide body subassembly 34, thereby
biasing the slide body subassembly toward the front of the tool (i.e., toward the nosepiece
portion of the tool).
also shows more details about the feed guide rail portion 40. The linear
guide rail 42 is attached to ts 46 and 48. Those brackets are positioned on a mounting
rail 180, and that rail is affixed to the top portion of the feed housing 22 by fasteners 182,
184, and 186.
Referring now to FIGS. 3 and 4, the drive gear 140 is illustrated in some
detail. The larger diameter portion of drive gear 140 es a relatively circular profile,
with multiple extensions at 142 and multiple depressions 144 that are spaced—apart
etween. The depressions 144 are sized and shaped to receive “bumps” 152 on the
timing belt 150, and thus this drive gear also acts as a timing gear.
The smaller diameter portion of drive gear 140 is also mainly circular in
profile, but with multiple extensions 146. Each of these extensions has an uppermost edge
148, which is used for a function that will be explained below in greater detail. In general,
the feed pawl has an attached detent finger that mates with these extensions 146 and 148, and
acts as a ratchet.
Referring now to FIGS. 5 and 7, the et 130 is illustrated, showing its
timing belt side. The larger diameter portion of sprocket 130 includes several protrusions
136 that extend d from an otherwise relatively circular diameter outer profile. These
extensions 136 engage the openings in collated strip of fasteners, and acts as a primary
mechanism for driving the strip of fasteners through the front end of the tool.
The r diameter portion of this side of the sprocket has a vely
circular profile with multiple extensions at 132 and multiple depressions at 134, which are
spaced—apart there between. The depressions 134 are sized and shaped to engage the bumps
in the timing belt 150.
Referring now to FIGS. 6 and 8, the sprocket 130 is illustrated, showing its
feed pawl side. The sprocket teeth 136 are again depicted, and the other major feature on the
site of the sprocket are a series of spaced—apart sions 138. These depressions are sized
and shaped to engage the distal end of the detent pin 108. This action tends to hold the
sprocket and collated strip grouping in their proper locations as the drive bit 66 pushes
s) the fastener (typically a screw) from the collated strip as that fastener is driven into a
workpiece.
Referring now to FIGS. 9 and 10, the detent finger 162 is illustrated. This pin
has a circular portion with a circular opening that can rotate about the ng pin 166.
Detent pin 162 also has an extension with a distal end 163. This distal end es a t
surface and mechanically interfaces with an opening of the feed pawl 160. Detent pin 162
also contains a mechanical stop at 161 which holds the n spring 164 in place. These
features will be illustrated in greater detail in . These components are used as a
“displacement action mechanism,” in that they are used to convert linear motion into
rotational motion.
Referring now to FIGS. 11, 12, and 13, the feed pawl 160 is illustrated in
greater detail. Feed pawl 160 has a large circular area with a large arcuate depression at 159.
It also has an extension arm 157 that has a cylindrical opening at its distal end, and that
opening allows it to pivot about the cam screw 72. There is a “feed post” 158 near the distal
end of the extension arm 157. The other end of the torsion spring 164 will rest against that
post (see ).
Referring now to FIGS. 14 and 15, the slide body support 102 is illustrated.
There are circular openings and circular bearing—type surfaces for ng the sprocket and
the drive gear elements, and also a near—oval structure that provides a pathway for the time
belt. In addition, there is a cam er clearance slot 101 that the cam follower 70 travels
within, which also positions the feed pawl element.
Referring now to FIGS. 16 and 17, the slide body cover 104 is illustrated,
which includes various openings for elements such as ers and the detent spring 110. In
addition, there are locating structures for the nosepiece adjustment subassembly, which
es the plunger 115, cap 112, and spring 116. This ece adjustment subassembly is
used for different screw lengths, which can be accommodated by a single tool 10.
Referring now to FIGS. 18 and 19, the belt drive subassembly is illustrated,
showing the main components of the drive gear 140, sprocket 130, and timing belt 150. The
feed pawl 160 is also rated, along with its associated detent finger 162. The cam
follower 70 is illustrated on , as fitting into an opening at the distal end of the
extension of the feed pawl 160.
It will be understood that the timing belt 150 has multiple raised “bumps” (or
protrusions) 152, and that these bumps fit into the depressions 144 of the drive gear 140, and
also into the depressions 134 of sprocket 130. However, only a few of these multiple
“bumps” 152 are illustrated on FIGS. 18 and 19, for the sake of clarity. But it will be
understood that the raised, spaced—apart bumps 152 are actually in place along the entire inner
surface of the timing belt 150. The other views of the logy disclosed herein that show
the timing belt 150 do not show any of these bumps 152 except at the locations where they
actually engage depressions of the et and the timing gear, again for the sake of clarity.
Referring now to , the belt drive subassembly is again illustrated, this
time as it would be assembled into the slide body support 102. As in FIGS. 18 and 19, the
sprocket 130 and the timing gear 140 are illustrated as engaging bumps of the timing belt
150. The interior edge 148 of the drive gear 140 can be seen as engaging the detent finger
162 at its distal end, while the extension 157 of the of the feed pawl can be seen as having its
associated cam follower resting inside the curved slot 101.
In addition to the other elements illustrated in , the torsion spring 164
is illustrated, and its two extending arms can be seen on . The torsion spring is
centered about a locating pin 166, which holds the detent finger 162 in place in an opening of
the feed pawl 160.
When the nosepiece of the tool is pushed against a workpiece surface, this
causes a cam arm (or extension) of the feed pawl 160 to rotate about a predetermined radial
position for the cam profile until it reaches the dwell slot in the housing (which is the
elongated horizontal portion of the slot 28 in the housing 22). The detent finger 162, while
engaged into the t teeth of the drive sprocket, causes the drive gear to rotate. This
movement causes the timing belt to move, and ore, the drive sprocket 130 is also
rotated simultaneously. This causes the collated strip of screws 60 to move into position so
that a fastener can be driven into the workpiece. As noted above, this design acts as a
“displacement action mechanism” by converting linear motion (or displacement) into
onal motion.
Once the “lead screw” has been d into the drive position 68 during a
drive sequence, the slide body subassembly will begin to “compress” (because of the action
of pushing the nosepiece against the workpiece surface) to the full drive distance of a given
fastener, and this provides a given amount of comerfit clearance. This term rfit
nce” is defined as the ce from the front of the nosepiece to the front of the
outermost housing portion when the tool is completely ssed (i.e., the slide body has
been completely pushed into the feed tube). This distance (the cornerfit nce) is needed
for driving a framing square into standard commercial channels while clearing the edges, or
for driving a screw into the corrugated roof decking. During the return stage of movement,
after a fastener has been driven, the drive gear 140 and driven sprocket 130 stay in position
while the ratchet finger 162 rotates about the ratchet teeth and back into position.
It should be noted that the overall design of the illustrated tool allows for an
“advance on return” mode of ion, in which the screw or fastener is indexed to the drive
position during the return portion of the operating cycle, d of during the advance
portion of that cycle. In this return mode (or “advance on return” mode), as the operator
releases the mechanism, the fastener moves into place (at the drive position). The push
stroke will reset the mechanism for the next feed stroke.
The operation of this type of screw—driving slide body subassembly is smooth
and effortless when g a fastener, because there are no momentary tions in the
drive elements themselves.
Referring now to , the attachment tool 10 is illustrated in a ctive
view that is mainly from the front, which is the end of the tool that makes contact with the
ece. As can be seen in this view, the “lead fastener” 68 is visible, as if it were about to
be emplaced into the workpiece. The orientation of the nosepiece 32 with respect to the right
side of the housing 22 can be seen, and this also illustrates the linear guides 170 and 172,
which will be discussed below in greater detail.
Referring now to , a top plan view of the attachment tool 10 is
illustrated, in which the tool is in its non—actuated condition. The “lead” fastener 68 is
illustrated, along with some of the other fasteners 64 that are still connected to the collated
strip. (In reality, the “lead” fastener 68 will no longer be attached to the collated strip if this
tool was an “index on advance” tool.)
shows a section line 23—23, and is a cross—section view of
the tool 10 taken along the section line. Referring now to , the feed tube 26 outer
ork can be seen, as a largely square—shaped structure. Within the square frame 26 are
the slidable workings of the slide body embly 34. In the middle of the slide body
subassembly is the drive bit at 66. Above the slide body subassembly is the collated screw
strip 62, with a n of one of the fasteners 64 still attached. These would be ng at
the drive position by sliding along the guide rails 42 and 44.
Certain details can be easily discerned in . The feed tube 26 is easily
seen, as having a square profile and shape. Within that feed tube are the linear guides 171
and 172. These guides make contact with the nosepiece 32 and angled portions of the
nosepiece designated at the reference numerals 174 and 176. This is referred to herein as a
“dove—tail” shape, and provides fairly rigid support for the nosepiece 32 as it slides forward
and backwards along the bearing surfaces of the linear guides 170 and 172. It can be seen
that the angled nosepiece portions 174 and 176 slide along similarly angled surfaces of the
linear guides 170 and 172. This is an important feature of the logy disclosed ,
because it provides strong support for the movable nosepiece and movable slide body
subassembly 34, especially along the “right—hand side” (which is to the left in this view)
where the nosepiece is positioned toward the front of the tool attachment 10.
Referring now to , the front portion of the attachment tool 10 is
illustrated in a top plan view, and this time it has been actuated so that the slide body
subassembly 34 has been pushed into the feed housing 22. The “lead fastener” 68 has been
torn away from the ed strip 62, and the screws (or fasteners) 64 that are visible on have not yet reached the drive position, and they are still attached to the screw strip 62.
A section line 25—25 is depicted on , and is a cross—section
view taken along that line. In , the attachment 10 is illustrated, and shows the
components of slide body subassembly 34 essentially surrounded by the feed tube 26. Just to
the outside of the feed tube, along the “right—hand side” of the tool, is the nosepiece 32 (to the
left in this view). There are two linear guides 170 and 172 that make a low—friction contact
with two extensions 174 and 176 of the nosepiece 32. This is the same ation that was
illustrated in . The linear guides 170 and 172 act essentially as linear bearings for the
movement of the nosepiece 32 proximal to and just inside the right—hand interior surface of
the feed tube 26. As noted above, this provides a firm structure for the combination of the
nosepiece 32 and the slide body subassembly 34, as they move inside the feed tube 26.
The dovetail shape of the nosepiece 32 is evident, in which the outer corners
along the right—hand side are broader, or spaced—apart at a greater distance, than the distal
ends of the extensions 174 and 176. The nosepiece 32 is tracked (guided) within the feed
tube 26, primarily on one side. There are additional features 177 and 178 on the slide body
support to e the load. Most conventional automatic feed screw systems use the slide
body subassembly as the sole means of support within the feed housing. Sizing of the inside
g dimensions s critical with those previous designs.
The dovetailed slide body cover at 179 allows the nosepiece 32 to slide and
track smoothly along the slide body cover when making screw length adjustments, by
adjusting the nosepiece position holes 38. As noted above, this dovetailed e is also the
primary t for the slide body embly 34. r to the nosepiece 32, there are
portions (at 179) that have outer s that are broader (i.e., —apart at a greater
distance) than their more interior outer surfaces. When fastened together, the combination of
the slide body cover at 179 and the nosepiece portions 174 and 176 create a single body
structure during normal ion of the tool 10, for driving a fastener into a ece; the
nosepiece portions 174 and 176 are sometimes referred to herein as a “dovetail shaped body
member.”
The upper and lower linear guides (or bearings) 170 and 172 are made of a
material having a low cient of friction, such as TEFLON. They support the nosepiece,
inside the feed housing 22. The tapers on these linear guides “lock in” the nosepiece 32, and
bias it to one side. As can be seen on , the angled shape (the taper) of linear guides
170 and 172 correspond to the angled shape of the dovetail outer surface of the nosepiece 32,
specifically at their outer sliding surfaces at the ns 174 and 176. In this manner the
dovetailed surfaces of the slide body subassembly provide a stronger, more durable surface
along the guide rails and support the extending ism within the slide body
subassembly, thereby having an improved linear tracking capability.
Referring now to , a prior art automatic screwdriver, generally
designated by the reference numeral 200, as two views: A, which is a top, plan view
in cross—section, and B, which is a side elevational view. This is a representation of
an existing prior art sold by Senco Brands, Inc., which is the model number DS200—AC. This
is an integral tool, which includes all of the motorized and r ents, as well as the
final drive components, including the collated strip ng components.
The “front end” of the tool 200 is on the right side of the view in .
This includes a feed tube 222, a movable slide body subassembly 234, and the movable
nosepiece 232. A screw strip subassembly 260 is visible in B, which has a plurality
of individual screws 264.
As best seen in the section view A, there is a drive bit 266 that extends
from the motorized gearbox portion of the tool toward the front end of the tool, so that it will
engage with one of the screws 264 when the tool is actuated.
There are certain ions of ance that are depicted on . In
the side view B, the dimension “H1” represents the height of the outer dimension of
the feed tube 222. In the section view A, the dimension “W1” represents the width of
the outer portion of the feed tube 222. A dimension “P1” represents the distance from the
further—most end (the “distal” end) of the drive bit 266 to the further—most end (or “distal”
end) of the feed tube 222. This Pl dimension is also referred to as the “lick—out”
characteristic of the tool.
The lick—out teristic of a power tool is important, and in general, it is
better to have a longer lick—out dimension than a shorter one. This is because a longer lick—
out dimension will allow a tool to reach into r, tighter places to drive a fastener than a
tool that has a shorter lick—out dimension. Since the automated screwdriver tools using
ed strips of fasteners tend to be ed with a front—end portion that “collapses” into a
feed tube, it usually is the outer dimensions of the feed tube that becomes the controlling
factor as to whether a given tool can reach into a small working area, or not. Therefore, the
longer the lick—out dimension compared to the overall size of the feed tube, the more “small”
areas the tool can be used with. This can be sed as a ratio: either P/H (the lick—out
divided by the feed tube height) or P/W (the ut divided by the feed tube width) for a
square or rectangular feed tube.
This characteristic described in the previous paragraph is better illustrated in
. A illustrates a top, plan view in cross—section of the same prior art tool,
model DS200—AC, after the tool has been “collapsed” because its nosepiece has been pushed
against the surface of a workpiece, which means the tool was used to drive a fastener into that
workpiece. B is a right side elevational view of the same tool, under the same
ions. As can be seen, the slide body subassembly 234 has been pushed quite far into
the feed tube 222, and the nosepiece 232 has been pushed back almost all the way to the outer
edge of the feed tube 222. This “outer edge” of the feed tube 222 is also referred to herein as
its “distal end.” In this condition, the drive bit 266 is the ent of the tool that is
furthermost to the front end of the tool.
In this “collapsed” ion of the tool 200 depicted in , the lick—out
dimension P1 is easily seen as the distance between the distal end of the drive bit 266 and the
distal end of the feed tube 222. This dimension does not change for a particular tool as the
tool is operated. It merely looks different, because the slide body and nosepiece have been
pushed into the inner open spaces of the feed tube 222.
The actual dimensions for a Senco model DS200—AC are as follows:
Dimension P1 = 11.89 mm
Dimension H1 2 38.1 mm
Dimension W1 2 38.1 mm
While it might seem a simple task to merely extend the lick—out dimension
(i.e., dimension P1 of FIGS. 26 and 27), this cannot be merely extended without considering
how it will affect the operation of the tool. If the slide body and ece are merely
pushed farther forward without sed support from the feed tube, then the operation of
the tool will become unstable, and the fasteners ally, ), will start having misfires,
and the reliability of the tool will be compromised. On the other hand, if the feed tube is also
enlarged to make for a more robust and stronger design, then that defeats the purpose of
extending the lick—out dimension, because the larger feed tube itself will prevent the tool
from being used in small areas. Therefore, the ratio of the lick—out dimension over the length
(or width) of the feed tube is an important quantity. In the Senco model AC, this
ratio is as follows:
P1/H1 = 11.89 mm/38.1 mm = 0.312
P1/W1= 11.89 mm/38.1 mm = 0.312
The greater this ratio P/H, or P/W, then typically the better the capability of
such an automatic screwdriver tool for operation into small areas, such as for driving a
rotatable fastener (e.g., a screw) into the interior corner of a ure, or for g a framing
screw into standard commercial channels while ng the edges of the channel, or for
driving a screw into deep corrugated roof decking.
ing now to , a left—side elevational view of the technology
disclosed herein is illustrated, showing the front end portions in greater detail. This includes
the nosepiece 32, the movable slide body subassembly 34, and the feed tube 26, with its
camming surface or slot 28. Also visible are the guide rail 42 and its forward extension 44,
and the collated strip of screws 60, in which the strip itself is at 62, and the screws at 64.
y, the depth of drive subassembly 80 is visible, having an inclined surface 95. This
tool is shown in the unactuated position, in which the nosepiece and the slide body
subassembly are fully extended, away from the feed tube 26.
Referring now to , the same tool is seen in the same type of view,
except now the tool has been collapsed by which the ece has been pushed in (to the
right) due to an operation for driving a fastener. In this view, it can be seen that the e
nosepiece 32 and movable slide body subassembly have been pushed into the feed tube 26 as
far as is possible, and therefore, most of the slide body subassembly is not visible, except for
the fact that this view is in partial cut—away. Note that the angled rear edge 119 of the
ece 32 has contacted surface 95 of the depth of drive subassembly 80.
Referring now to , the tool’s front end 10 is again ed in an
elevational view, but this time the cover of the slide body subassembly has been removed.
In essence, this is the same view as , without the slide body cover.
The sprocket 130 and the drive gear 140, along with the timing belt 150 are
now visible, along with the drive bit 66. A portion of the sprocket 130 has been cut away, so
that the distal end of the drive bit can be seen. A dimension “P2” is illustrated, which is the
“lick—out” dimension of this tool 10; it is the distance n the forward—most distal end of
the drive bit 66 and the forward—most distal end of the feed tube 26. Also visible on
is the height ion “H2”, which is the height of the outer surfaces of the feed tube 26.
The width dimension of this feed tube was illustrated on , by the dimension “W2”.
] shows the same structure, but in the condition in which both the
nosepiece 32 and the slide body subassembly 34 have been partially pushed into the feed tube
26. The distance the nosepiece has been pushed into the feed tube is sufficient to move the
outer or distal end of the drive bit 66 much closer to the head of the lead screw 68, as seen in
the cut—away area in the sprocket region. The camming roller 70 has been displaced by an
amount sufficient to index the sprocket 130, so that the “next” fastener 64 will be indexed to
that drive location 68.
The lick—out dimension P2 is again visible on , and extends from the
distal end of the feed tube 26 to the distal end of the drive bit 66. In the tool 10, exemplary
dimensions that are illustrated on FIGS. 30 and 31 (and also ) are as follows:
P2 = 45.88 mm
H2 2 38.1 mm
W2 2 38.1 mm
Using the above figures, the ratio of the lick—out dimension compared to the
height (or width) dimension is as follows:
P2/H2 = 45.88 1 mm = 1.204
P2/W2 = 45.88 mm/38.1 mm = 1.204
As can be seen, this ratio value (1.204) is much higher than the ratio of the
prior art tool discussed above, which was the ratio P1/H1 (and P1/W 1). This allows the tool
to fit into smaller areas for driving rotatable ers, such as screws or bolts.
It will be understood that the feed tube that is illustrated and described herein
need not be square; rectangular feed tubes are also common in these types of tools. However,
the internal workings of the slide body subassembly must still fit within such feed tubes, no
matter their exact shape or size, and a robust slide body subassembly will always require
some minimum front profile, having a maximum height or width dimension, which would
also be true for a circular or elliptical feed tube. In any feed tube shape, there will always be
a discernable width or height dimension (or a diameter dimension) that becomes the limiting
factor in allowing the fastener driving tool to fit within a given small area and have the
capability of driving a rotatable fastener. Those discernable width or height dimensions will
be equivalent to the “W” and “H” dimensions discussed herein.
] It would be an improvement to provide a design that provides a ratio of P/W
and/or P/H that is at least 0.5; a more preferred design would provide a ratio of P/W and/or
P/H that is at least 0.75; a yet more preferred design would provide a ratio of P/W and/or P/H
that is at least 1.0; and a still more preferred design would e a ratio of P/W and/or P/H
that is at least 1.2.
Referring now to , an alternative embodiment of a fastener driving tool
is illustrated, generally designated by the reference numeral 300. In this view, there is a
fixed feed tube 326, and a movable slide body embly 334. (The nosepiece is not
shown, for es of y.) There is a et 330 to index the collated strip of screws
(not seen in this view), and a drive—gear equivalent, which is the feed pawl 360 in this
embodiment. The driving feed pawl 360 has an associated drive gear with external teeth (not
visible in this view) that causes another rotatable gear 340 to rotate, which in turn causes yet
another rotatable gear 342 to be rotated, and which in turn, causes yet another rotatable gear
344 to be rotated. The teeth of the gear 344 will engage the teeth of the sprocket 330, on the
opposite side of the sprocket from what is e in .
The feed pawl 360 has a large opening that is actuated by the detent finger
326, so that this subassembly acts as a ratchet. It will be seen that, as the feed pawl 360
rotates, so do the gears 340, 342, and 344, which then causes the sprocket 330 to rotate, and
thereby to indeX the collated strip of screws. This can be built as a sturdy “extending
mechanism”, and the multiple drive gears can be made as large as necessary, so long as they
fit within the confines of the or spaces of the slide body subassembly 334.
On , the lick—out dimension is designated as “P3” which is the distance
from the distal end of the drive bit 366 to the front (or distal) end of the feed tube 326. Once
again, this is a rather long ion, as ed to the length and width of the feed tube
itself. This will provide improved characteristics for fitting within small areas for driving
rotatable fasteners, such as screws or bolts.
Referring now to FIGS. 33—36, a depth of drive subassembly is illustrated,
generally designated by the reference numeral 80. This subassembly includes several
components, such as a adjusting screw bushing 81, a housing 82, an adjustable stop block 83
which is threaded, a threaded ing screw 84 having a large knob, a retaining clip 85, a
locking latch pin 86, a compression spring 87, and a latch pin er 88. The latch pin 86
has a protruding tab 93, the adjusting knob/screw 84 has recesses 94 on the bottom surface of
the knob, and there is an angled (or inclined) surface 95 on the stop block 83. shows
the assembled depth of drive embly, while is an exploded view.
shows the led components, and is a cross—section view along the section line
36—36 on .
In order to make adjustments to the depth of drive unit 80, the user should
depress and hold down the latch pin tab 93. While holding the latch pin down, the user
should rotate the adjustment screw 84. A clockwise on is for a higher (or “up”) setting,
which will cause the fastener to penetrate shallower, and a counterclockwise is for a lower (or
“down”) setting, which will cause the fastener to penetrate deeper. Rotating the adjustment
screw 84 causes the adjustable stop block 83 to travel up or down. This up and down travel is
in a direction that is transverse to the longitudinal axis of the feed tube, which is substantially
dicular to that longitudinal axis.
As can be seen on , there is an area at 90 of threaded engagement
between the adjustable stop block 83 and the larger thumb wheel/screw 84. When the
thumbwheel 84 is turned, its threaded engagement with the stop block 83 will cause that stop
block to be displaced, either up or down. This movement affects the depth to which the
fastener will be driven by the tool 10. This stop block action is bed below in greater
detail, in reference to .
r actions of the depth of drive unit 80 allow the desired fastener setting
to be checked by releasing the tab 93 on the latch pin 86. The unit can then be adjusted
again, if needed. The locking latch pin 86 is biased upward by a compression spring 87. The
top portion of latch pin 86 will lock into one of the slots 94, located on the bottom surface of
the head of the adjustment screw 84, and prevents further adjustments. The locking latch pin
retainer 88 prevents accidental movement of the adjustable stop block 83.
As noted above, and as can be seen on FIGS. 33 and 34, the adjustable stop
block 83 includes an inclined surface 95. As the position of the stop block 83 is moved up or
down by action of the ing knob 84, the positioning of the tapered face 95 (i.e., the
inclined surface) will determine how deep or how high the screw head will be placed into a
given substrate of the workpiece. There are matching taper angles on the rear of the
nosepiece 32 (at 119) and on the stop block 83 (at the inclined or tapered surface 95). The
operation of these surfaces causes the depth of drive g to be effective.
Referring now to , some of the major components of the tool 10 are
visible, ing the nosepiece 32, the sliding block subassembly 34, the feed tube 26, and
the depth of drive embly 80. The guiding surfaces (i.e., longitudinal protrusions) 177
and 178 of the slide body subassembly and feed tube are visible, as is the end of one of the
linear guides 170.
rates the orientation of the inclined surface 95 of the adjustable
stop block 83 with respect to the angled rear edge 119 of the nosepiece 32. In this view, the
stop block 83 is depicted at about its midpoint position, with t to its top—most position
and its bottom—most position, as it travels along the threaded thumbscrew 84 (see ).
During a ner driving event” (or “fastener driving ), the nosepiece 32 is pushed
rearward, which is to the right in , and the rear edge 119 of nosepiece 32 will
eventually come into contact with the ed surface 95 of the stop block 83. When that
occurs, the clutch of the motorized driving tool (not shown) will be aged, and the drive
bit 66 (not shown in this view) will stop turning. ore, the position of the stop block 83
becomes the controlling factor as to when the tool stops trying to drive a rotatable fastener
(such as a screw), and in effect, acts as a ical “depth of drive” controller.
The above action is illustrated on FIGS. 28 and 29. In , the nosepiece
32 is extended, as it has not been actuated. Its rear angled edge 119 is seen to the left (on this
view) of the inclined surface 95 of the stop block 83. In , the nosepiece 32 has been
actuated all the way to its right—most movement (on this view), and its rear angled edge 119
has made contact with the inclined surface 95 of the stop block 83. Note that in these two
views, the stop block 83 has been placed near its bottom—most travel position.
The midpoint position of the stop block 83 that is illustrated on will
cause the rotatable fastener to be driven to a “midpoint depth” of the tool’s l lity.
The following example discusses what occurs when the stop block is moved to other
positions, from this midpoint location. If the moveable stop block 83 is adjusted all the way
to its top—most position, then rear edge 119 will come into contact with ed surface 95
sooner during the rearward travel of the nosepiece 32 (because the angled edge 119 extends
farther to the rear (to the right on ) at a higher position along the vertical surface of
the nosepiece 32, and the clutch of the motorized tool will be disengaged sooner in its drive
cycle. Therefore, the drive bit 66 will not be as far forward when its rotation stops, and thus
the rotatable fastener will not be driven as far into the workpiece.
Alternatively, if the moveable stop block 83 is adjusted all the way to its
bottom—most position, then rear edge 119 will come into contact with inclined surface 95 later
during the rearward travel of the nosepiece 32 (because the angled edge 119 extends less far
to the rear (to the right on ) at a lower position along the vertical surface of the
nosepiece 32, and the clutch of the zed tool will be disengaged later in its drive cycle.
Therefore, the drive bit 66 will be farther d when its rotation stops, and thus the
rotatable er will be driven deeper into the workpiece.
Note that, in conventional automatic feed screwdriver systems, the depth of
drive adjustable thumb screw typically is located directly inline with the back of the
nosepiece, i.e., within the feed housing. Therefore, the overall length of the nosepiece must
be shortened to accommodate the added mechanisms. And when using the longest screw
length, with the nosepiece set at the longest length, if the feed system is in its home
(unactuated) position (i.e., when the nosepiece is fully extended), then more than half (almost
three—quarters) of the bearing support between the housing and the back end portion of
nosepiece is lost. In addition, virtually all the depth of drive range is lost. The lack of
support bearing surface sometimes will cause alignment and stability problems; this is due to
premature wear of the linear slide bearings.
The current embodiment takes advantage of this fact by mounting the depth of
drive adjusting mechanism assembly on the e of the housing, thereby maximizing the
available bearing ratio in front and rear. The depth of drive subassembly 80 is mounted
external to the feed tube housing 22 which allows for an improved bearing ratio between the
nosepiece 32 and the feed tube housing. This also allows for a greater insertion distance of
the nosepiece into the feed tube housing 22. There is a small opening in the side of the feed
tube to allow a portion of the able stop block 83 to extend therethrough; this is the
inclined surface 95 portion, which makes contact with the rear edge 119 of the ece
along the inner surface of the feed tube. In essence, by moving the depth of drive
subassembly 80 outside the feed tube, portions of the slide body and nosepiece subassemblies
are able to travel back past the depth of drive components, thus ting a length increase
on the overall feed , while providing more g e between the nosepiece and
frame while at the extended (at rest) position.
The logy sed herein may be used both on attachments for
screwdrivers, and with integral automatic er driving tools. An e of an
attachment embodiment is illustrated on An example of an integral tool is illustrated
on .
Referring now to , an integral automatic fastener driving tool is
generally designated by the reference numeral 400. A handle portion 410 includes a set of
bottom gripping surfaces 412 that can be used by a person's hand to readily grip the handle
and not easily slide along the bottom surface of the housing portion 420. Handle n 410
also includes a trigger 414, which is used to actuate an ical switch to operate the internal
drive mechanisms of the hand—held portable tool 400. In the illustrated embodiment, a power
cord 416 is attached at the bottom area of handle portion 410, which provides electrical
power to the internal drive mechanism of the tool 400. Note that some fastener—driving tools
have a battery embly to provide the electrical power, which of course can be used with
the technology disclosed .
Handle portion 410 also includes a guide member (or rail) 442 that can receive
a flexible collated strip of screws, in this case the collated screw subassembly 60. The
collated screw subassembly 60 mainly consists of a plastic strip 62 that has several openings
to receive individual screws 64. The overall collated screw subassembly is flexible to a
certain degree, as can be seen in by the curved orientation of the plastic strip 62. The
strip 62 (not shown on ) is fed through a guide portion, which includes the guide rail
442 and possibly an al second guide member as a tensioning device (not shown), then
up toward the nosepiece 32 and the slide body subassembly 34. The optional second guide
member can be added for longer screwdriver tools, if desired; such a design is disclosed in
U.S. Patent No. 7,032,482, titled: TENSIONING DEVICE APPARATUS FOR A BOTTOM
FEED SCREW DRIVING TOOL FOR USE WITH COLLATED SCREWS.
It will be understood that the words “screw” and ner” are essentially
interchangeable, as used herein. The technology disclosed herein is designed to drive
rotatable fasteners, which typically are actual screws. However, other types of fasteners,
such as bolts, could be used with the tools/attachments of this technical field. A “collated
strip of fasteners,’ 9 as discussed herein, could carry screws or bolts, or some other type of
rotatable device; a “collated strip of screws” has ially the same features and meaning as
a “collated strip of fasteners.”
Some of the mechanical mechanisms described above for the portable er
driving tool 400 have been available in the past from Senco ts, Inc. or Senco Brands,
Inc., including such tools as the Senco Model Nos. DSl62—14V and DS200—14V. These
earlier tools utilized a fixed feed tube, a e slide body 34, and ece 32 ure,
without the “extended nose” feature of the technology sed herein. Some of the
components used in the technology disclosed herein have been disclosed in commonly—
assigned patents or patent applications, including a United States Patent No. 5,988,026, titled
SCREW FEED AND DRIVER FOR A SCREW DRIVING TOOL; a United States Patent
No. 7,032,482, titled TENSIONING DEVICE APPARATUS FOR A BOTTOM FEED
SCREW DRIVING TOOL FOR USE WITH COLLATED ; and a United States
Patent No. 7,082,857, titled G RAIL CONTAINMENT DEVICE FOR FLEXIBLE
COLLATED SCREWS USED WITH A TOP FEED SCREW DRIVING TOOL. These
patent properties have been assigned to Senco Brands, Inc., and their sures are
incorporated herein by reference in their entireties.
] As used herein, the term "proximal" can have a meaning of closely positioning
one physical object with a second physical object, such that the two objects are perhaps
adjacent to one r, although it is not necessarily required that there be no third object
positioned therebetween. In the technology sed herein, there may be instances in which
a "male locating structure" is to be positioned "proximal" to a "female locating structure." In
general, this could mean that the two male and female structures are to be physically abutting
one another, or this could mean that they are "mated" to one another by way of a particular
size and shape that essentially keeps one structure oriented in a predetermined direction and
at an X—Y (e.g., horizontal and vertical) position with respect to one another, regardless as to
whether the two male and female structures actually touch one another along a continuous
surface. Or, two structures of any size and shape (whether male, , or otherwise in
shape) may be located somewhat near one another, regardless if they physically abut one
another or not; such a relationship could still be termed "proximal." er, the term
"proximal" can also have a meaning that s strictly to a single object, in which the single
object may have two ends, and the "distal end" is the end that is positioned somewhat farther
away from a subject point (or area) of reference, and the mal end" is the other end,
which would be positioned somewhat closer to that same t point (or area) of nce.
It will be understood that the various components that are described and/or
illustrated herein can be fabricated in various ways, including in multiple parts or as a unitary
part for each of these components, without departing from the principles of the logy
disclosed herein. For example, a component that is included as a recited element of a claim
hereinbelow may be fabricated as a unitary part; or that component may be fabricated as a
combined structure of several individual parts that are assembled together. But that “multi—
part component” will still fall within the scope of the claimed, recited element for
infringement purposes of claim interpretation, even if it appears that the d, recited
element is bed and illustrated herein only as a unitary structure.
All documents cited in the Background and in the Detailed Description are, in
relevant part, incorporated herein by reference; the citation of any document is not to be
construed as an ion that it is prior art with respect to the technology disclosed herein.
The foregoing description of a red embodiment has been presented for
purposes of ration and description. It is not intended to be exhaustive or to limit the
logy disclosed herein to the precise form disclosed, and the technology disclosed
herein may be further ed within the spirit and scope of this disclosure. Any examples
described or illustrated herein are intended as non—limiting examples, and many modifications
or variations of the examples, or of the preferred embodiment(s), are possible in light of the
above teachings, without ing from the spirit and scope of the logy disclosed
herein. The embodiment(s) was chosen and described in order to illustrate the principles of
the technology disclosed herein and its practical application to thereby enable one of ordinary
skill in the art to utilize the technology disclosed herein in various embodiments and with
various modifications as are suited to particular uses contemplated. This application is
ore intended to cover any variations, uses, or adaptations of the technology disclosed
herein using its general principles. Further, this application is intended to cover such
departures from the present disclosure as come within known or customary practice in the art
to which this technology disclosed herein pertains and which fall within the limits of the
appended claims.
I/WE
Claims (13)
1. A drive apparatus for a rotatable fastener driving tool, said drive apparatus comprising: an elongated feed tube; a rotatable drive bit; and an extending mechanism that is actuated by relative movement, and that has an output member which creates an indexing ; and wherein said ted feed tube has a first end and a second, opposite end along a longitudinal axis, said feed tube having an open volume therewithin, said first end being open and sized and shaped to receive said ing mechanism, said second end having an opening to e said rotatable drive bit that extends through said open volume, said feed tube having a slidable surface, said drive bit having a distal end that, along said longitudinal axis, is located a distance P from said first end of the feed tube, said feed tube having a maximum outer width ion W and a maximum outer height dimension H; (a) during operation, said extending mechanism is movable with respect to said feed tube, along said slidable surface of the feed tube, which is relative nt that actuates said extending mechanism; and (b) a ratio P/W is in the range of 0.50 to 1.50.
2. The drive apparatus of claim 1, n (a) said ratio P/W is in the range of about 0.75 to 1.2; (b) said ratio P/W is substantially equal to 1.2; (c) said extending mechanism comprises a slide body subassembly which includes: (i) a drive gear having a first set of engagement extensions; (ii) said output member, which ses a sprocket that is spaced-apart from said drive gear, said sprocket having a second set of engagement extensions; (iii) a drive belt that runs between said drive gear and said sprocket, said drive belt having a plurality of spaced-apart protrusions along one of its surfaces that are in mechanical engagement with said first set of engagement extensions of said drive gear and being in mechanical engagement with said second set of engagement extensions of said sprocket, said drive belt being caused to move if said drive gear rotates, and said drive belt then causing said sprocket to rotate; and (iv) a displacement action mechanism that causes said drive gear to rotate; AH26(10257301_1):TCW (d) said extending mechanism comprises a slide body subassembly which includes: (i) a drive gear having a first set of gear teeth; (ii) said output member, which comprises a sprocket that is spaced-apart from said drive gear, said sprocket having a second set of gear teeth; (iii) at least one ediate gear having at least one third set of gear teeth that are in mechanical engagement with said first set of gear teeth of said drive gear and being in mechanical engagement with said second set of gear teeth of said sprocket, said at least one intermediate gear being caused to move if said drive gear rotates, and said at least one intermediate gear then causing said sprocket to rotate; and (iv) a displacement action mechanism that causes said drive gear to rotate.
3. A drive apparatus for a rotatable fastener driving tool, said drive apparatus comprising an elongated feed tube, and a slide body structure; wherein: said slide body ure is actuated by relative movement, and has an output member which creates an indexing motion, said slide body structure having a dovetail shaped body member; and said elongated feed tube has a first end and a second, opposite end along a longitudinal axis, said feed tube having an open volume therewithin, said first end being open and sized and shaped to receive said slide body structure, said feed tube having an elongated slidable surface at an interior location, said le surface having a shape that corresponds to mate against said dovetail shaped body member, wherein during operation, said slide body structure is movable with respect to said feed tube along said slidable surface of the feed tube, which relative movement actuates said slide body structure.
4. The drive apparatus of claim 3, n: (a) said slide body structure comprises a slide body subassembly and a nosepiece that adjustably d to said slide body embly; and said nosepiece includes said dovetail shaped body member, said ece having a distal end that extends past said first end of the feed tube, and said nosepiece distal end being used to contact a surface of a ece; (b) said slide body structure comprises a slide body subassembly, wherein said slide body subassembly comprises: (i) a drive gear having a first axis of on, said drive gear having a first set of engagement extensions along one of its surfaces at a first position along said first axis of rotation, said drive gear having a set of ratchet teeth at a second position along said first axis AH26(10257301_1):TCW of rotation; (ii) said output member, which comprises a et having a second axis of rotation that is substantially parallel to said first axis of rotation, and that is spaced-apart from said drive gear, said sprocket having a first plurality of spaced-apart protrusions along an outer curved surface at a third position along said second axis of rotation, said sprocket having a second set of engagement extensions at a fourth position along said second axis of rotation; (iii) a drive belt that runs n said drive gear and said sprocket, said drive belt having a second plurality of spaced-apart protrusions along one of its surfaces, said second plurality of spaced-apart protrusions being in mechanical engagement with said first set of engagement ions of said drive gear and being in mechanical engagement with said second set of engagement extensions of said sprocket, said drive belt being caused to move if said drive gear rotates, and said drive belt then causing said sprocket to rotate; and (iv) a cement action mechanism that causes said drive gear to rotate by way of said set of ratchet teeth; (c) said slide body structure comprises a slide body subassembly, n said slide body subassembly comprises: (i) a drive gear having a first axis of rotation, said drive gear having a first set of gear teeth along one of its surfaces at a first position along said first axis of rotation, said drive gear having a set of ratchet teeth at a second position along said first axis of rotation; (ii) a sprocket having a second axis of rotation that is substantially parallel to said first axis of rotation, and that is spaced-apart from said drive gear, said sprocket having a plurality of spaced-apart protrusions along an outer curved e at a third on along said second axis of rotation, said et having a second set of gear teeth along one of its surfaces at a fourth position along said second axis of rotation; (iii) at least one intermediate gear having at least one intermediate axis of rotation, said at least one intermediate gear having at least one third set of gear teeth that are in mechanical engagement with said first set of gear teeth of said drive gear and being in mechanical engagement with said second set of gear teeth of said et, said at least one ediate gear being caused to move if said drive gear rotates, and said at least one intermediate gear then causing said sprocket to rotate; and (iv) a displacement action mechanism that causes said drive gear to rotate; (d) said elongated slidable surface of the feed tube comprises at least one linear bearing strip, made of a material having a low coefficient of friction. AH26(10257301_1):TCW
5. The drive apparatus of claim 4, further comprising: (a) a le collated strip of fasteners that slides over an end portion of said slide body embly, said flexible strip having a ity of spaced-apart openings that engage with said first plurality of spaced-apart protrusions of the et, and are thereby sequentially d into a drive position by rotation action of said sprocket about said second axis of rotation; (b) a flexible collated strip of fasteners that slides over an end portion of said slide body subassembly, said flexible strip having a plurality of spaced-apart openings that engage with said plurality of spaced-apart protrusions of the sprocket, and are thereby sequentially indexed into a drive position by rotation action of said sprocket about said second axis of on; (c) at least one elongated guiding surface located on a first side of said slide body subassembly, wherein said at least one linear bearing strip is located on a second, opposite side of said slide body subassembly, and both said at least one elongated guiding surface and said at least one linear bearing strip tend to support and guide said slide body subassembly as it slides inward and outward with respect to said feed tube.
6. A drive apparatus for a rotatable fastener driving tool, said drive apparatus comprising: an elongated feed tube, a slide body embly; wherein: said slide body subassembly is actuated by ve movement, and has an output member which creates an indexing motion; said elongated feed tube has a first end and a second, opposite end along a udinal axis, said feed tube having an open volume therewithin, said first end being ntially open and sized and shaped to receive said slide body subassembly, said feed tube having an elongated slidable surface and, during operation, said slide body subassembly is movable with respect to said feed tube, which ve movement actuates said slide body subassembly; an elongated nosepiece that is adjustably affixed to said slide body subassembly, said nosepiece having a third end and a fourth, opposite end along an axis of movement that is substantially parallel to said longitudinal axis, said third end extending past said first end of the feed tube so as to contact a surface of a workpiece, said fourth end extending toward said second end of the feed tube and having a first contact surface; and AH26(10257301_1):TCW a depth of drive subassembly that is mounted proximal to the second end of said feed tube, said depth of drive subassembly including a movable member that has a second contact surface, said first t e of the fourth end of the nosepiece coming into mechanical communication with said second contact surface at the end of a fastener driving cycle.
7. The drive apparatus of claim 6, wherein: (a) said first contact surface comprises an edge portion of said fourth end of the nosepiece that is angled; and said second t surface comprises an inclined n of said e member that is adjustable in a direction that is substantially dicular to said longitudinal axis; (b) said depth of drive subassembly ses: (i) a housing; (ii) an adjusting screw having a hand-adjustable knob, said adjusting screw extending in a direction that is substantially perpendicular to said longitudinal axis, said adjusting screw having first mating screw threads; and (iii) said movable member with said second contact surface, in which said second t surface is angled so as to not be parallel or perpendicular to said longitudinal axis, said movable member having second mating screw threads that engage said first mating screw threads, so that if said hand-adjustable knob is rotated, then said movable member is moved along said substantially perpendicular direction; (c) (i) if said movable member is adjusted in a first substantially perpendicular direction, then said first contact surface of the nosepiece will come into contact with said second t surface of the movable member at a point earlier during said fastener driving cycle, thereby leaving the fastener at a higher position in the workpiece; and (ii) if said movable member is adjusted in a second substantially perpendicular direction that is opposite to said first substantially dicular direction, then said first t surface of the nosepiece will come into contact with said second contact surface of the movable member at a point later during said fastener driving cycle, thereby leaving the fastener at a deeper position in the workpiece;
8. The drive apparatus of claim 6, r comprising: a locking latch member with a hand-actuated tab, a compression spring to bias said locking latch member in a linear direction, and a latch retainer; wherein: (i) said djustable knob has a plurality of recesses that engage with said locking latch member to hold a position of said adjusting screw, so as to prevent unintentional movement of said movable member; (ii) said tab is used to depress said compression spring to AH26(10257301_1):TCW e said locking latch member from said djustable knob, so as to allow the adjusting screw to be rotated to a new position.
9. A drive apparatus for a rotatable er driving tool, comprising: a slide body subassembly that is actuated by relative movement, and that has an output member which creates an indexing motion; an elongated feed tube having a first end and a second, opposite end along a longitudinal axis, said feed tube having an open volume therewithin, said first end being substantially open and sized and shaped to receive said slide body subassembly, said feed tube having an elongated slidable surface and, during operation, said slide body subassembly is movable with respect to said feed tube, which relative nt actuates said slide body subassembly; an elongated nosepiece that is adjustably affixed to said slide body subassembly, said nosepiece having a third end and a fourth end at opposite positions along an axis of movement that is substantially parallel to said longitudinal axis, said third end extending past said first end of the feed tube so as to contact a surface of a workpiece, said fourth end extending toward said second end of the feed tube; and a depth of drive subassembly that is mounted at an external location with respect to said feed tube, said depth of drive embly having an able mechanism that engages with said fourth end of the nosepiece.
10. The drive apparatus of claim 9, wherein: (a) said fourth end of the ece has a first t e; said adjustable mechanism of the depth of drive subassembly comprises a movable member that has a second contact surface; and said first contact surface of the fourth end of the nosepiece coming into mechanical communication with said second contact surface at the end of a fastener driving cycle; (b) wherein said depth of drive subassembly comprises: (i) a housing that is mounted al to said feed tube; (ii) an adjusting screw having a hand-adjustable knob, said adjusting screw extending in a direction that is substantially perpendicular to said longitudinal axis, said adjusting screw having first mating screw s; (iii) said movable member, in which said second contact surface is angled so as to not be parallel or perpendicular to said longitudinal axis, said movable member having second mating screw threads that engage said first mating screw threads, so that if said hand-adjustable knob is rotated, then said movable member is moved along said substantially perpendicular direction; and (iv) said adjusting screw is mounted AH26(10257301_1):TCW al of said feed tube; however, a portion of said movable member is positioned to extend h an opening of said feed tube so as to engage with said fourth end of the nosepiece.
11. The drive apparatus of claim 10, wherein: (a) if said e member is adjusted in a first substantially perpendicular direction, then said first contact surface of the nosepiece will come into contact with said second t surface of the movable member at a point earlier during said fastener driving cycle, thereby leaving the fastener at a higher position in the workpiece; and (b) if said movable member is adjusted in a second substantially perpendicular direction that is opposite to said first substantially perpendicular direction, then said first contact surface of the nosepiece will come into contact with said second t surface of the movable member at a point later during said fastener driving cycle, thereby g the fastener at a deeper position in the workpiece.
12. The drive tus of claim 10, further comprising: a locking latch member with a hand-actuated tab, a compression spring to bias said locking latch member in a linear direction, and a latch retainer; wherein: (i) said hand-adjustable knob has a plurality of recesses that engage with said locking latch member to hold a position of said adjusting screw, so as to t unintentional movement of said movable member; (ii) said tab is used to depress said compression spring to release said locking latch member from said hand-adjustable knob, so as to allow the adjusting screw to be rotated to a new position.
13. A drive apparatus substantially as hereinbefore described with reference to
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
NZ709288A NZ709288B2 (en) | 2011-11-04 | 2012-10-31 | Screwdriver tool with improved corner fit function |
Applications Claiming Priority (5)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US13/288,982 | 2011-11-04 | ||
US13/288,982 US8869656B2 (en) | 2011-11-04 | 2011-11-04 | Screwdriver tool with improved corner fit function |
US13/288,985 US8726765B2 (en) | 2011-11-04 | 2011-11-04 | Screwdriver tool with improved linear tracking |
US13/288,985 | 2011-11-04 | ||
PCT/US2012/062650 WO2013066913A2 (en) | 2011-11-04 | 2012-10-31 | Screwdriver tool with improved corner fit function |
Publications (2)
Publication Number | Publication Date |
---|---|
NZ622337A NZ622337A (en) | 2015-09-25 |
NZ622337B2 true NZ622337B2 (en) | 2016-01-06 |
Family
ID=
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