JPH04250986A - Device for driving fastener - Google Patents

Abstract

PURPOSE: To provide a small and inexpensive fastener driving tool to prevent abrasion in the case of pulling a roof top, etc., convenient for use and without malfunction. CONSTITUTION: Abrasion guards 126, 128, 130 free to convert to support a side surface of a driving tool at three points are provided. A muffler is provided on a top part cap. A buffle is provided on the muffler, and exhaust air is discharged downward. A plural number of feeding holes free to reciprocate are provided on a fastener transfer mechanism, and these holes are supported on an eccentric body free to pivotally move.

Description

[Detailed description of the invention]

0001

[Field of Industrial Application] The present invention relates to a fastener driving machine, and more particularly, the present invention relates to a fastener driving machine, and more particularly, a replacement for supporting the fastener driving machine at three points on the side thereof to protect the cast handle and the magazine housing. The present invention relates to a fastener driving machine with a wearable surface. Other features of the invention include reduced manufacturing costs and improved ergonomics of such fastener driving machines. moreover,
The fastener feeding mechanism has been improved to accommodate relatively large fasteners that were previously spaced too widely and caused the fastener driving machine to malfunction.
It is possible to feed a set of fasteners with heads.

0002

2. Description of the Related Art A fastener driving machine tends to wear only a certain part of its outer surface depending on the habits of the user. especially,
This tendency is noticeable when the fastener driving machine is used for roofing. More specifically, the user often pulls the fastener driver through an external pneumatic hose. When the fastener driver is pulled up with a pneumatic hose, the abrasive nature of the roofing material and the weight of the fastener driver causes the fastener driver to be pulled along the roof surface, which in turn causes the fastener driver to causing excessive wear on the cast handle and magazine housing. Replacing these parts is relatively expensive. Moreover, completing the installation with a hammer requires auxiliary tools in addition to the roof attachment machine.

In the past, fastener driving machine manufacturers have addressed this problem by providing wear surfaces on the sides of the fastener driving machine that provide two-point support for the fastener driving machine. For example, as shown in FIGS. 1 and 2, previous fastener driving machines 20 have included a wear guard 22 in a magazine housing 24. As shown in FIGS. This wear guard 22 consists of a U-shaped metal clip as shown in FIG. The U-shaped clips are clamped into the wall of the magazine housing 24 in staggered positions, as shown in FIG.

[0004] In this way, the U is attached to the magazine housing 24.
By attaching the shaped clip 22, two-point support of the fastener driving machine 20 is achieved. Clip 2
One of the two points of support according to 2 is shown in FIG. The support at the other point is represented by the reference symbol 26, which is the handle casting 28.

While the wear guard 22 provides protection against wear of the magazine housing 24 when the fastener driver 20 is pulled along a roof surface, there is no protection for the handle casting 28.

Additionally, there are several problems with using the U-shaped clip 22 for the magazine housing 24. If the U-shaped clip 22 is used for the magazine housing 24, the magazine housing 24 must be opened when the U-shaped clip 22 is replaced. Also, while the fastener driver 20 is being pulled along the roof surface, the U-shaped clip 22 may move from its desired position. In addition to these,
U-shaped clip 22 to magazine housing 24
In this structure, the U-shaped clip 22 may be installed in the wrong position, causing wear on the magazine housing 24.

In other known fastener driving machines, an elongated L-shaped wear guard 30 (see FIG. 4) is attached to the handle casting 28 at the point of contact. More specifically, one leg 32 of the wear guard 30 is attached to the handle casting 28 and the other leg 34 acts as the wear surface. However, such a structure does not provide protection for the magazine housing 24. Additionally, the elongated L-shaped wear guard 30 may cause other problems. That is, in such an abrasion guard 30, the contact surface of the leg 34 wears away, leaving the other leg 32 with a relatively sharp surface, which is very dangerous to the user.

There are many other problems with conventional fastener driving machines. All of these issues address the need to reduce manufacturing costs of fastener driving machines, improve the ergonomics of fastener driving machines, and fastener feeding mechanisms for batches of fasteners with relatively large fastener heads. It is about improving the.

Regarding manufacturing costs, there are several problems that contribute to the high costs. These problems are, firstly, that there are no standards for fastener driving machine handle castings for different power performances, and secondly, that there are no standards for the drive cylinder assembly parts inside the handle castings. The required tolerances are relatively small.

With respect to the first problem, it is known that the drive force delivered by a fastener driving machine to the fastener head is a function of the respective volumes of the air reservoir and capture air chamber within the handle casting. . These volumes can be adjusted to some extent by the size of the cast handle. For this reason, fastener driving machines that require different driving forces use cast handles of different sizes. Handle castings account for a relatively large portion of the total manufacturing cost of a fastener driving machine, so using handle castings of different sizes can increase the manufacturing cost of a fastener driving machine. ing.

As previously mentioned, the relatively tight tolerances required for the parts of the drive cylinder assembly within the handle casting also result in high manufacturing costs. More specifically, the drive cylinder assembly includes a reciprocating piston within the drive cylinder to which is attached a fastener driver or ram. The drive cylinder assembly is located within the handle molding and is closed by a poppet valve located adjacent the top cap. Axial movement of the drive cylinder assembly within the handle casting must be minimized, if not completely prevented, so each part must be machined to relatively tight tolerances. . For example, the tolerance should be 0.010 inches. These components greatly increase the overall manufacturing cost of the fastener driving machine.

[0012] Various ergonomic features of conventional fastener driving machines also impact how the fastener driving machine is used by the end user. One of the characteristics is the overall shape of the fastener driving machine. The relatively large profile of fastener driving machines is not desirable to the end user. This problem is further exacerbated when the muffler 36 is attached to the fastener driving machine. This muffler 36 is often attached to a top cap 38 of a cast handle, as shown in FIG. As shown in FIG. 5, the height of the top cap 38 is increased by a length indicated by H1 to accommodate the muffler 36. This increased length of the top cap 38 increases the profile of the fastener driver, making it less attractive to prospective purchasers and end users.

Another factor influencing the ergonomic convenience of a fastener driving machine is the location of the exhaust gas outlet. As shown in FIG. 5, conventional fastener driving machines are provided with a muffler 36 at the top of the top cap, and exhaust gas is discharged radially through a discharge port 40. However, many end users believe that it is preferable for the exhaust gas to be directed downwardly from the front portion of the fastener driving machine, ie, in the direction of arrow 42 shown in FIG.

Other known fastener driving machines that are not equipped with a muffler have an outlet 44 in the top cap 38, which exits from the outlet 44 by arrow 4.
Exhaust gas is discharged in the direction of 6. The direction of exhaust gas exit from the top cap shown in both FIGS. 5 and 6 is undesirable from an ergonomic point of view.

Finally, a conventional fastener feeding mechanism 48 as shown in FIG. 7 (usually used in conjunction with a relatively low density array of fasteners 50 as shown in FIG. 8)
There are many problems. If such a fastener feeding mechanism, as shown in FIG.
For example, problems such as malfunction of the fastener driving machine or clogging of the fastener may occur.

Such a dense array of fasteners typically includes a web 54, an upper tab 56, and a lower tab 5.
8, and the upper tab 56 and lower tab 58 are provided with a fastener support opening 60 for removably receiving a fastener shank 62. Special fastener 64 with a relatively large diameter head portion 66
If a fastener head (for example, a roofing nail) is used, the fastener head may interfere with the fastener feeding mechanism 48, causing malfunction of the fastener driving machine. More specifically, U.S. Pat.
The known fastener feeding mechanism described in US Pat. The fastener 64 is fed through the opening 70. However, because the spacing between the fastener head 66 and the web 54 is not sufficient, the upper tab 56 bends over the feed pawl 68 during the fastener drive process, thereby causing the fastener 64 to be axially relative to the drive blade. This prevents directional alignment. This, in turn, causes the drive blade to drive the fastener head 66 at a point other than its center, causing the fastener to become jammed within the fastener drive mechanism 48 .

[0017]

OBJECTS OF THE INVENTION It is an object of the present invention to solve the problems with previous fastener driving machines.

Another object of the present invention is to provide a fastener driving machine having a mechanism for supporting the fastener driving machine at three points on its sides.

Still another object of the present invention is to provide a means for preventing wear of the handle casting and magazine housing when pulling the fastener driver over abrasive surfaces such as roof surfaces. .

Still another object of the present invention is to reduce the manufacturing cost of fastener driving machines.

Still another object of the present invention is to standardize handle castings for use in fastener driving machines having different power performance.

Yet another object of the present invention is to alleviate the tight tolerances to internal components of the drive assembly.

Yet another object of the invention is to improve the ergonomic convenience of fastener driving machines.

Still another object of the present invention is to reduce the overall size of the fastener driving machine.

Still another object of the present invention is to provide a fastener driving machine with an exhaust gas outlet located at an ergonomically desirable location.

Yet another object of the present invention is to improve fastener feeding mechanisms for use with known arrays of fasteners having relatively large diameter heads.

[0027]

SUMMARY OF THE INVENTION The present invention relates to a fastener driving machine that supports three points on the side of the fastener driving machine and is equipped with a replaceable wear guard. The three-point support mechanism protects the handle casting and magazine housing from wear even when the fastener driver is dragged over abrasive surfaces such as roof surfaces. The fastener driving machine has a muffler built into a small top cap, which allows the overall size of the fastener driving machine to be reduced. The deflection plate directs the exhaust gases downwardly in front of the fastener driving machine in a direction that is ergonomically desirable for the end user. The fastener driver also includes an improved fastener feeding mechanism that improves the performance of the fastener driver for relatively large diameter uniform fasteners, and that improves the fastener driver's ability to 2, allowing the drive blades to be axially aligned.

The above and other objects and advantages of the present invention will become more apparent from the following description and accompanying drawings.

[0029]

10 to 12 show a fastener driving machine 100 according to the present invention. Specifically, the fastener driving machine 100 has a cast handle 102, and the cast handle 102 has a handle portion 104.
and a drive assembly portion 106. A top cap 108 is attached over the drive assembly portion 106 by fasteners 110. A nosepiece assembly 112 defining a fastener drive passage is fixedly attached to the bottom of the drive assembly section 106 by fasteners 114. Magazine assembly 116 is fixedly attached between the rear of handle portion 104 and nosepiece assembly 112. Trigger assembly 118 energizes a poppet valve (not shown), which controls actuation of drive piston 120 within drive cylinder 124 and drive blade 122 attached to drive piston 120 . U.S. Pat. No. 3,543,98 describes the features of fastener driving machine 100.
No. 7 and No. 4,319,705,
This application shall incorporate the descriptions of these patents.

An important feature of the present invention relates to the wear guards 126, 128, 130 (depicted in FIGS. 13-15) used in the fastener driving machine 100 shown in FIGS. 10, 11, and 12. As is apparent from FIG. 10, the wear guards 126, 1128, 130 allow for three-point support of the fastener driving machine 100 on its side. More specifically, referring to FIG. 10, the three support points are indicated by arrows 132, 134, 136. Protection from wear of the handle casting 102 at the support points indicated by arrows 134, 136 is provided by wear guards 126, 128. Wear guard 130 provides protection from wear at the support point indicated by arrow 132 on the magazine housing forming part of magazine assembly 116 .

Thus, when the fastener driver 100 is dragged over the side of a roof or other wear surface, the handle casting 102 and magazine assembly 116 will be isolated from the wear surface, thereby , wear guards 126, 128, 130 will protect against wear. For this reason, the three-point support mechanism described above provides only two-point support relative to the previous support mechanism, i.e., the fastener driving machine, and only protects either the cast handle 102 or the magazine housing 116 from wear. It can be seen that this arrangement is more advantageous than, for example, the mechanisms shown in FIGS. 2 and 4.

[0032] All wear guards 126, 128, 130 are replaceable. Wear guard 126 is fastener 110
The top cap 108 is adapted to be attached to the top cap 108 to provide protection for the upper portion of the cast handle 102. As best shown in FIG. 12, wear guard 126 is attached to fastener driving machine 100.
Can be attached to each side of the Similarly, wear guard 128 can be attached to the bottom of handle casting 102 and secured to the bottom with fasteners 114. Figure 12
Abrasion guards 128 can also be attached to both sides of fastener driving machine 100, as shown in FIG. Protection against the magazine housing 116 is provided by wear guard 1.
Done by 30. As shown in FIG. 12, two wear guards 130 are provided on each side of the magazine housing 116. However, the wear guard 13 used
The number of zeros varies depending on the shape of the magazine housing 116's surroundings.

Positioning of wear guards 126, 128 is provided by fasteners 110, 114. To position the wear guard 130 relative to the magazine housing 116, the wear guard 130 is further positioned while the fastener driver 100 is dragged over the wear surface.
To prevent movement of the wear guard 130, an L-shaped dependent arm 132 is formed. These L-shaped arms 132 are adapted to be received in slots 134 (see FIG. 12) in the magazine housing 116, thereby positioning the wear guard 130 relative to the magazine housing 116. Furthermore, this positioning prevents movement of the wear guard 130 even as the fastener driver 100 is being dragged over the wear surface.

Wear guard 126, 1 for cast handles
28 is formed as a generally U-shaped member having dependent legs, each dependent leg being provided with an aperture 136;
The holes 136 receive the fasteners 110, 114. These wear guards 126, 128 are constructed from a durable material, preferably hardened steel. Additionally, one or more wear surfaces 137 are formed on the wear guards 126, 128. Figures 13 and 14
The wear guards 126, 128 are provided with alternative wear surfaces 139, 141, as shown in FIG. As best shown in FIG. 10, the wear guard is fixedly attached to the handle casting 102, with the fastener driver 100 laterally contacting the wear surface as shown in FIG. In some cases, one or the other of the wear guards 139, 141 contacts the wear surface.

Wear guard 130 for magazine housing
is formed as a flexible elongated member of a durable flexible material, preferably ultra high molecular weight polyethylene (UHMWP). Forming the wear guard 130 from a flexible material allows the wear guard 130 to be used with magazine housings 116 having a variety of geometries.

Another important feature of the present invention is the small profile top cap 108. This feature is best illustrated in FIGS. 16-18. As shown in FIG. 6, the height of the top cap 38 was previously H2. As is clear from the figure, this top cap 3
8 does not incorporate the muffler 36. When the muffler 36 is assembled into the top cap 38, the overall height of the top cap 38 increases by H1, as shown in FIG. This increases the overall size of the fastener driving machine, which is undesirable.

The height of the top cap 108 according to the present invention is reduced to H3 (see FIG. 18), and a muffler 138 is incorporated therein. 5 and 18, the height H3 of the top cap 108 is substantially less than the height H1 of the top cap 38 shown in FIG. This is because the muffler 138 is not added to the top cap height as in FIG.
This is because it is incorporated inside 8. This reduces the overall size of the fastener driving machine.
Accordingly, the fastener driving machine has become more ergonomically preferable. More particularly, the top cap 108 includes a muffler 138 that includes a plurality of concentrically disposed baffles 140. As shown in FIG. 17, the two concentric rings 141, 143 of the baffle 140 are arranged concentrically with respect to the exhaust air port 142. The annular volume 144 is a baffle 140
forming a groove adjacent to the outer concentric ring 143;
A new flexible sound deadening member can be inserted into this groove. The top cap 108 is formed as a substantially square member and has holes 145 at the four corners, and the top cap 108 can be fixed to the cast handle 102 by passing the fasteners 110 through the holes 145. It looks like this.

Exhaust air exiting the muffler 138 is directed to the exhaust port 146. A redirection plate 148 is provided to direct the exhaust air downwardly, making the fastener driving machine 100 more ergonomically friendly. This redirection plate 148 closes the exhaust air port 142 and directs the exhaust air through the muffler 138 toward the exhaust outlet 146, generally parallel to the longitudinal axis 149 of the top cap 108, as shown by arrow 151 in FIG. Direction downwards.

The direction change plate 148 has an L-shaped leg 14.
9 (see FIG. 16). This L-shaped leg 149 is connected to the discharge port 146.
is located above the muffler 138 and directs exhaust air downward from the muffler 138. The redirection plate 148 has a central opening 150.
is provided, the central opening 150 being aligned with the hole 152 in the top cap 108;
A redirection plate 148 can be attached to the top cap 108.

Another important feature of the invention is the compressible cylinder ring 156. As shown in FIG. 19, this compressible cylinder ring 156 is formed with a stepped cross section, with a relatively large diameter section 158 on one side and a relatively large diameter section 158 on the other side. It has a small diameter portion 160 with a small diameter.

As will become apparent from the following description, the cylinder ring 160 is made of a compressible material, such as compressible plastic, to reduce the tolerances required for components within the drive cylinder assembly. ing. More specifically, it is necessary to eliminate axial movement between the drive cylinder 124 and the handle casting 102. The drive cylinder assemblies are typically interconnected by a top cap 108. More particularly, the top cap 108 is provided with a plurality of vertical walls 162 that are seated against an annular shoulder 164 . As shown in FIG. 5, an annular shoulder 164 is formed on the drive cylinder assembly 124 and makes metal contact. As can be seen, any clearance between the tip of the vertical wall 162 and the shoulder 164 can cause axial movement of the drive cylinder assembly 124, resulting in reduced performance of the fastener driving machine. For this reason, it is common practice, for example, to manufacture components such as the vertical wall 162 and the drive cylinder assembly 124 to relatively tight tolerances to eliminate the gaps described above. However, this has resulted in a significant increase in the manufacturing cost of those parts, and in turn, an increase in the cost of the entire fastener driving machine.

[0042] In order to avoid giving small tolerances to such parts as described above, a compressible ring 156 is provided in the present invention. The ring 156 is located between the vertical wall 162 and a shoulder 164 on the drive cylinder assembly 124. More specifically, a larger diameter section 158 of relatively large diameter is seated on an annular shoulder 164 . The relatively small diameter of the small diameter section 160 is such that the inner surface of the vertical wall 162 can be seated therein. Vertical wall 162, ring 156 and drive cylinder assembly 124 are interconnected in a known manner.

The thickness 165 of the large diameter section 158 is used to accommodate tolerance differences in parts, such as the drive cylinder assembly 124 and vertical walls 162, which are to be machined to standard tolerances. Once the aforementioned assemblies are coupled, the thickness 165 of the cylinder ring 156 is compressed to compensate for tolerance differences and ensure axial stability of the drive cylinder assembly 124 relative to the handle casting 102. do.

Another important feature of the invention is the bulkhead 166, which can be used upside down and is shown in FIGS. 20-23. As previously discussed, the power delivered from drive blade 122 to the fastener head is a function of the volume of air reservoir 167 and capture air chamber 168, only a portion of which is shown in FIGS. 22 and 23. . Both volumes are approximately determined by the size of the cast handle 102. For this reason, different cast handles 102 have been used for fastener driving machines with different power performance.

The inverted bulkhead 166 of the present invention allows the size of the handle casting 102 to be standardized for multiple power capabilities. More specifically, as shown in FIGS. 22 and 23, the bulkhead 166 is located between the drive cylinder assembly 124 and the internal annular shoulder 170 on the handle casting 102.
It is attached via a ring 172. The bulkhead 166 also seats on an annular shoulder 174 formed on the outer periphery of the drive cylinder assembly 124 and provides a separate
It is sealed from annular shoulder 174 by ring 176. The annular shoulder 174 acts as a stop for the bulkhead 166 and at the same time serves to position the bulkhead 166 there.

The bulkhead 166 can be used upside down and attached to the handle casting 102 and drive cylinder assembly 124 in two positions shown in FIGS. 22 and 23. As is apparent from FIGS. 22 and 23, the orientation of the bulkhead 166 can adjust the required volume of the air reservoir 178 relative to the capture air chamber 168. By using the bulkhead 166 that can be used upside down in this way, it becomes possible to standardize the handle molded product 102 used for different power performance simply by turning the bulkhead 166 upside down. .

Bulkhead 166 is made of a cylindrical member having a top lip 178 and an annular groove 180 for receiving an O-ring 172. The upside down bulkhead 166 also includes an annular internal lip that allows the bulkhead 166 to rest against the annular shoulder 1.
74 and can be seated on it.

Another important feature of the present invention is the feed pawl assembly 182 shown in FIGS. 24-26. The feed pawl assembly 182 improves the operation of the fastener driving machine 100 when using a bank of high density fasteners 52 having a relatively large head 66 as shown in FIG.

In known fastener driving machines 50, such as those described in detail in US Pat. No. 4,383,608, fastener feeding mechanism 48 uses a single feeding pawl 68. The fastener strip is then fed into a fastener driving machine 50. Such a fastener feeding mechanism is suitable for a bank of fasteners having a relatively small fastener head, such as that shown in FIG. In such fastener driving machines, the feed pawl 68 delivers the strip from an opening 70 immediately behind the fastener 64 being driven. However, such a fastener feeding mechanism 48 is not suitable when using a set of fasteners 52 as shown in FIG. 9, for example, a fastener 52 having a relatively large fastener head 66. This is because the relatively large diameter fastener head 66 may cause interference. More specifically, when the drive blade 122 is engaged with the fastener head 66,
The upper tab 56 is bent. This in turn causes the upper tab 56 and fastener head 66 combination to contact the feed pawl 68 since the feed pawl 68 is located within the opening 70 immediately behind the fastener being driven. When such contact occurs, drive blade 122 becomes misaligned with the center of fastener head 66. This may cause the fastener 44 to spring up inside the fastener driving machine or cause an accidental firing.

To solve this problem for a set of fasteners having a relatively large fastener head, such as that shown in FIG.
82 are provided. This fastener feeding mechanism 182 eliminates interference between the upper tab 56 and the feeding pawl. This has two feeding pawls, namely a front feeding pawl 184 and a rear feeding pawl 1.
This is achieved by providing 86. As best shown in FIG. 24, the front feed pawl 184 feeds from an aperture 188 immediately in front of the fastener being driven, and the rear feed pawl 186 feeds from an aperture 190 behind the fastener being driven. Perform feeding. By repositioning the feeding pawls 184, 186 relative to the fastener being driven, interference between the upper tab 56 and the feeding pawls can be eliminated. As described below, the two feeding pawls 18
4,186 allows a series of fastener strips to be punched out in a continuous manner,
It also allows the drive blade 122 to engage directly in front of the center of the fastener head 66. Additionally, rear feed pawl 186 is required to feed the last fastener in the strip.

Fastener feeding assembly 182 according to the present invention
is the feeding claw 184 fixedly attached to the eccentric body 192.
, 186. Eccentric body 192 is pivotally mounted about pin 194. A slot 196 provided in the eccentric body 192 is adapted to receive a pin 198 fixedly attached to an axle 203 formed at one end of the feed piston 200. The feed piston 200 is provided inside the feed cylinder 201 so as to be able to reciprocate. As best shown in FIGS. 25 and 26, as the feed piston 200 reciprocates within the feed cylinder 201, the eccentric 192 undergoes rotational movement. As a result, the feeding claws 184, 1
86 feeds a batch of fasteners along feed path 205. The feeding path 205 has a non-linear portion 206 that continuously fires the fastener strip 52.
06 creates a gap between the fastener being driven and the next fastener. When the fastener strip reaches the non-linear portion 206 of the feed path 205, the fastener strip is held by the feed pawls 184, 186.

FIG. 25 shows the relative positions of the parts of the fastener feeding assembly in the static mode, and FIG. 26 shows the relative positions in the drive mode. The feed cylinder 201 is provided with two ports 208 and 210 for controlling the feed piston 200. port 20
8 communicates with the poppet air. Port 210 communicates with the air reservoir. These two ports 208,
210 is arranged to create a pressure difference across the feed piston 200.

In operation, trigger assembly 118
When pressed, a poppet valve (not shown) directs conditioning air into the interior of the drive cylinder assembly 124, which causes the drive piston 120 to drive the fastener into the workpiece. Once the trigger assembly 118 is energized while the fastener delivery mechanism 182 is in the rest position, a poppet valve (not shown) opens to force reservoir air into the interior of the drive cylinder assembly 124 and into the drive piston. 120 to drive the fastener into the workpiece. When the poppet valve opens, poppet air is vented from the right side of the delivery cylinder 201 and, under the influence of reservoir air, resets the eccentric 192 to the position shown in FIG. Then, when the poppet valve closes, the poppet air advances the delivery piston 200 to the left as viewed in Figure 26, advancing the fastener to the next step.

A gate assembly 214 is provided to retain the fastener strip 52 and to retract the feed pawls 184, 186. This gate assembly 2
14 forms a part of the feeding path 205. Gate assembly 214 is pivotally mounted about pin 212 so that feed passage 205 opens and fastener strip 52
It is possible to load. Typically, gate assembly 214 is latched by gate latch 215.

Gate assembly 214 is used to provide clearance to allow feed pawls 184, 186 to retract.
A backup pawl 216 is provided. The backup pawl 216 is pivotally mounted around a pin 218 and allows the feed channel 205 to extend. As shown in FIGS. 25 and 26, the backup claw 216 is urged in its closing direction by a spring 220. Feeding claw 18
4, 186 is being retracted to the position shown in FIG.
2 slides on the fastener strip 52 and the spring 22
The fastener strip 52 is pressed against the backup pawl 216 against a biasing force of 0. Once, feed claw 1
84 and 186 reach the position shown in FIG.
4, 186 are located in the openings 188, 190 of the fastener strip 52 as shown in FIG.
i.e. return to the position shown).

Although the present invention has been described with reference to several embodiments, many modifications and variations will occur to those of ordinary skill in the art that fall within the scope of the principles of the invention. It is.

[Brief explanation of the drawing]

FIG. 1 is a front view of a conventional fastener driving machine.

FIG. 2 is a perspective view of the fastener driving machine shown in FIG. 1, showing a two-point support mechanism.

FIG. 3 is a perspective view of a wear guard used in the fastener driving machine shown in FIG. 1;

FIG. 4 is a perspective view of another known wear guard.

FIG. 5 is a cross-sectional view of a known top cap for use in a fastener driving machine incorporating a muffler.

FIG. 6 is a sectional view of a known top cap without a muffler, showing the forward outlet for exhaust gases;

FIG. 7 is a top plan view of a known fastener delivery mechanism and a set of fastener strips (fasteners removed for clarity);

8 is a front view of a set of fasteners typically used with the fastener feeding mechanism shown in FIG. 7; FIG.

FIG. 9 is a plan view of a fastener strip of a set of fasteners having relatively large diameter heads.

FIG. 10 is a perspective view of the fastener driving machine according to the present invention, showing a three-point support mechanism.

FIG. 11 is a side view of the fastener driving machine according to the present invention.

12 is a front view of the fastener driving machine shown in FIG. 11. FIG.

FIG. 13 is a perspective view of a handle cast wear guard according to the present invention.

FIG. 14 is a perspective view of another embodiment of a handle cast wear guard according to the present invention.

FIG. 15 is a perspective view of a wear guard magazine housing according to the present invention.

FIG. 16 is an exploded perspective view of the top cap and redirection plate according to the present invention.

FIG. 17 is a top view of a compact top cap of the present invention integrated with a muffler.

FIG. 18 is a cross-sectional view of the top cap shown in FIG. 17;

FIG. 19 is a perspective view of a compression cylinder ring according to the invention.

FIG. 20 is a perspective view of a bulkhead that can be used upside down according to the present invention.

FIG. 21 is a cross-sectional view of the bulkhead shown in FIG. 20.

FIG. 22 is a partial cross-sectional view of the handle housing, drive cylinder, and upside down bulkhead in a first position;

Figure 23: Figure 2 except that the bulkhead is in an alternate position
FIG. 2 is a partial cross-sectional view similar to FIG.

FIG. 24 is a partial front view of a set of fasteners located inside the fastener feeding mechanism according to the present invention, showing the position of the feeding pawl.

FIG. 25 is a cross-sectional view of the fastener feeding mechanism according to the present invention, showing the fastener feeding mechanism in a first position.

FIG. 26 is a cross-sectional view of the fastener feeding mechanism according to the present invention, showing the fastener feeding mechanism in a second position.

[Explanation of symbols]

20 Fastener driving machine 22 Wear guard 24 Magazine housing 28　Handle cast product 30 L-shaped wear guard 36 Muffler 38 Top cap 40 Discharge port 44 Discharge port 46 Fastener feeding mechanism 68 Feeding claw 50 Low density zipper set 52 A set of high-density zippers 54 Web 56 Upper tab 58 Lower tab 64 Zipper 66 Large diameter head part 100 Fastener driving machine 102　Handle cast product 106 Drive assembly 108 Top cap 112 Nose piece assembly 116 Magazine assembly 120 Drive piston 122 Drive blade 126 Wear guard 128 Wear guard 130 Wear guard 132 Support point 134 Support point 136 Support point 137 Wear surface 138 Muffler 140 Baffle 142 Exhaust air port 146 Exhaust port 148 Direction change plate 156 Cylinder ring 166 Bulkhead 167 Air reservoir 168 Capture air chamber 170 Annular shoulder 182 Feeding claw assembly 184 Front feeding claw 186 Rear feeding claw 192 Eccentric body 200 Feeding piston 201 Feeding cylinder 205 Feeding route 214 Gate assembly 216 Backup claw 220 Spring 222 Angled surface

Claims (15)

[Claims] Claim 1: A fastener driving machine that forms a first side surface and a second side surface when placed with a predetermined surface down, comprising: a cast handle having a top and a bottom; and a fastener placed on a workpiece. a drive assembly disposed within the handle casting for driving; a nose piece coupled to the handle casting forming a drive path; A fastener driving machine comprising: a magazine assembly for feeding the fastener driving machine; and means for supporting the fastener driving machine at three points on either the first side surface or the second side surface. 2. The fastener driving machine of claim 1, wherein the three-point support means comprises one or more rigid members having one or more predetermined wear surfaces. 3. The three-point support means comprises a plurality of distinct wear surfaces, of which only one wear surface is
3. The fastener driver of claim 2, wherein the fastener driver is adapted to engage the predetermined surface when the fastener driver is placed on either the first side or the second side. 4. The three-point support means includes one or more rigid, generally U-shaped members, each member having a pair of dependent legs and a connecting leg. The fastener driving machine according to claim 2, characterized in that: 5. The fastener driving machine according to claim 1, wherein said three-point support means includes means for supporting said magazine assembly. 6. A molded handle, comprising a cast handle, a drive cylinder, and a drive piston reciprocably provided within the cast handle, forming a predetermined first volume and a predetermined second volume. a drive assembly for changing the first and second volumes using the cast handle. 7. The volume changing means includes a bulkhead that can be used upside down and arranged in a first position or a second position between the cast handle and the drive cylinder. , the first position defines first and second predetermined volumes for the handle cast and the drive cylinder, and the second position defines separate first and second predetermined volumes. The fastener driving machine according to claim 6, characterized in that: 8. A handle casting, a drive assembly disposed within the handle casting, and a top cap having a predetermined height and closing a portion of the handle casting.
a muffler having exhaust gas exhaust means integrally formed within the top cap to substantially maintain the predetermined height. 9. The fastener driving machine of claim 8, wherein the muffler includes a plurality of baffles arranged in one or more concentric rings. 10. A drive assembly comprising a handle molding and having a drive cylinder adapted to be substantially fixedly disposed within the handle molding, the drive cylinder being a standard It is formed with tolerance,
a top cap having support means for fixedly supporting said drive cylinder with respect to said handle casting, said support means being formed to standard tolerances, and said support means and said drive cylinder being formed with standard tolerances; a fastener driving machine, comprising: adjusting means disposed between the support means and the drive cylinder for adjusting a gap between the support means and the drive cylinder. 11. The adjusting means is formed as a generally circular member with a stepped cross section, the circular member having a predetermined first diameter and a predetermined second diameter. The fastener driving machine according to item 10. 12. A drive assembly for driving fasteners into a workpiece, and a fastener feeding mechanism for feeding a set of fasteners to the drive assembly, wherein the set of fasteners is mounted on each fastener. comprising a relatively large diameter fastener disposed on a strip defining a plurality of adjacent apertures, the fastener feeding mechanism having a plurality of reciprocatingly mounted fasteners relative to the array of fasteners; A fastener driving machine having a feeding claw, the feeding claw advancing the set of fasteners along a fastener feeding path. 13. The fastener driving machine according to claim 12, further comprising an eccentric body pivotally mounted to support the feeding claw. 14. The feed pawl is adapted to be received in an opening directly in front of the fastener being driven and in two locations behind the fastener being driven. The fastener driving machine according to claim 12. 15. A gate assembly forming part of the feed passage having means for enabling expansion of the feed passage such that the feed pawl can be retracted. The fastener driving machine according to claim 12.