The present invention relates to shafts that transfer torque through a shaped connection, and more particularly to anvil shafts in rotary power tools such as impact drivers.
Rotary impact power tools are used to tighten or loosen fastening devices such as bolts, nuts, screws, etc. Rotary impact power tools have been developed that use a pneumatic or electric motor to drive a hammer which rotationally impacts an anvil. These anvils typically have a tang portion with a square cross section and are coupled with an output such as a drive socket. The tang portion has a transverse hole on one of the faces to house a spring-loaded detent pin. The detent pin releasably engages a corresponding recess in the drive socket.
Prior art anvils used in impact drivers are subject to fatigue failures. Fatigue is a phenomenon that leads to fracture in a load-bearing member under repeated or fluctuating stresses, even though those stresses may be substantially less than the tensile strength of the member. Fatigue fractures generally start at a point of geometric discontinuity or stress concentration and grow incrementally until a critical size is reached. It has been found that a stress concentration is created at the transverse hole on the face of the anvil tang in prior art anvil designs. This stress concentration at the transverse hole severely weakens the anvil tang, increasing its risk of fatigue failure. Further, when the anvil tang is subject to a fatigue failure, the failure can occur in a catastrophic manner. This potentially results in propelling the socket and broken portion of the anvil at high speed, which may injure an operator or bystander.
For the foregoing reasons, there is a need for an anvil for an impact driver that reduces the stress concentration and fatigue failure at the tang.
Accordingly, embodiments of the present invention provide a new and improved anvil for an impact driver. In one embodiment, the tang portion of the anvil is stepped, with a smaller first tang section transitioning to a larger second tang section. The transverse hole is placed in the smaller first tang section, while the larger second tang section engages the drive socket. This anvil design shifts the stress from the transverse hole to the solid larger tang section, thereby reducing the number of fatigue failures of rotary impact drivers.
According to a first aspect of the invention, a shaft comprises an input portion and a tang. The tang has a first section, a second section, and a bore. The second section is disposed between the first section and the input portion along an axis. A radial cross section of the first section is less than a radial cross section of the second section. The radial bore is disposed on the first section.
According to a second aspect of the invention, an anvil comprises an anvil portion and a tang. The tang has a first section, a second section, and a bore. The second section is disposed between the first section and the anvil portion along an axis. A radial cross section of the first section is less than a radial cross section of the second section. The radial bore is disposed on the first section.
According to a third aspect of the invention, a hand held power tool may include a housing, a motor, a power source, a cam shaft, a hammer, and an anvil. The motor is disposed in the housing. The power source energizes the motor. The cam shaft is driven by the motor and the hammer is driven by the cam shaft. The anvil comprises an anvil portion and a tang. The tang has a first section, a second section, and a radial bore. The second section is disposed between the first section and the anvil portion along an axis. A radial cross section of the first section is less than a radial cross section of the second section. The radial bore is disposed on the first section.
A fourth aspect of the invention is an impact driver and may include a housing, a motor, a power source, a transmission, a cam shaft, a hammer, an anvil, and an output. The motor is disposed in the housing. The power source energizes the motor. The transmission is driven by the motor. The cam shaft is coupled with the transmission. The hammer is axially aligned with the cam shaft and is driven rotationally and axially by the cam shaft. The anvil comprises an anvil portion and a tang. The tang has a first section, a second section, and a radial bore. The second section is disposed between the first section and the anvil portion along an axis. A radial cross section of the first section is less than a radial cross section of the second section. The radial bore is disposed on the first section. An output is coupled with the tang.
Referring now to
Shaft 14 may be coupled with a transmission to adjust the output torque or speed. As best seen in
The third gear 30 is rotatably coupled with cam 40. The cam 40 consists of a cam shaft 42, at least one camming ball 46 located in integrally formed camming grooves 44 on the cam shaft 42, and an impact spring 50. A third bearing 48 journalled on cam shaft 42 and a ball 49 supported by a hardened steel plate 13 of housing 12 and seated within an axial recess 47 in cam shaft 42 provide rotational support for cam shaft 42 at one end. The other end of cam shaft 42, opposite the third gear 30, rotates within an axial recess 73 in anvil 70 to also provide support. Cam shaft 42 rotates about output axis 58. The impact spring 50 is preferably a coil spring, with one end supported by a radial face of third gear 30. Alternately, impact spring 50 may be supported by an integrally formed radially extending flange (not shown) on cam shaft 42. The other end of spring 50 axially biases a rotary hammer 60.
The hammer 60 rotates about cam shaft 42 and is axially slidable relative to cam shaft 42 due to spring 50. The cam forces the hammer 60 axially against the resistance of impact spring 50 during each revolution or portion of a revolution of the hammer 60 so as to bring the radial sides of a pair of hammer lugs 62 that project axially from a forward wall of the hammer 60 into rotary impact with the radial sides of a pair of lugs 72 that project from the integrated anvil-gear 70.
The hammer 60 also has an axial channel (not shown) where a plurality of balls 66 are located. The axial channel is preferably sized so that eighteen stainless steel impact balls 66 of 3.50 mm diameter can be positioned within it, although it may be sized so that other sizes or numbers of balls 66 may be used. A washer 68 is positioned on the balls 66 in the axial channel. Axial or rotational loads on the spring 50 are taken up the roller bearing formed by washer 68 and balls 66.
As shown in
Male tang 78 is preferably sized to be received in a female receptacle of an output (not shown) of like configuration and size. Such outputs may include a drive socket, an adapter, etc. Second section 82, being larger than first section 80, transfers the impact torque from the motor via the hammer 60 to the output, providing for a rotational lock. A retaining means such as a spring-loaded detent is disposed on first section 80 to engage a corresponding recess or groove in the female receptacle of an output and provide an axial lock. The detent may include a coil spring 96 biasing a slotted pin 98, as shown in
As shown in
In operation, as the motor drives the armature shaft 14 about motor axis 18, drive is transmitted through the transmission to the cam shaft 42 about output axis 58. The cam 40 disposed about the cam shaft 42 rotationally and axially displaces hammer 60 along cam shaft 42 to rotationally impact the anvil portion 74 of anvil 70. Torque is transmitted through the anvil by the anvil portion 74 through the torque transfer section 76 into male tang 78. Second section 82 transfers the impact torque to the output, providing for a rotational lock. The detent disposed on first section 80 of male tang 78 provides an axial lock with the output. By reducing the size of first section 80 and by moving transverse bore 92 far from the applied load area, the stress from the impact torque produced by the hammer is evenly distributed throughout the cross-section of second section 82. Without a stress concentration due to the hole to contribute to fatigue failures, the expected operating life of the anvil should be increased.
The present invention is applicable to power driven rotary tools such as impact drivers, angle impact drivers, stall-type angle wrenches, screwdrivers, nutrunners, etc., and provides an anvil that reduces the stress concentration caused by a detent. The anvil reduces a potential failure point in the tang, providing for a more robust transfer of drive torque to the output. While the invention has been described with reference to details of the illustrated embodiment, these details are not intended to limit the scope of the invention as defined in the appended claims. For example, while the invention has been described with reference to an anvil, shafts having other inputs such as gears, keyways, splines, or grooves may also be used. In addition, while the retaining means has been described as it relates to a spring-loaded detent, other retaining means such as a retaining ring may be used. Further, while the anvil has been described with reference to a transverse bore, designs that generate stress concentrations with other shapes, such as grooves, through holes, etc., may also be used. In addition, other anvil or drive means may be used. Also, other shapes and sizes of the male tang and torque transfer section may also be used, such as other polygonal shapes, including hexagons, octagons, etc., or rounded shapes such as circles or ellipses. It is therefore intended that the foregoing detailed description be regarded as illustrative rather than limiting, and that it be understood that it is the following claims, including all equivalents, that are intended to define the spirit and scope of this invention.
Number | Name | Date | Kind |
---|---|---|---|
2525695 | Lombard | Oct 1950 | A |
2801718 | Kaman | Aug 1957 | A |
2954994 | Beers | Oct 1960 | A |
3414065 | Falter | Dec 1968 | A |
3533479 | Madsen | Oct 1970 | A |
3610344 | Schoeps et al. | Oct 1971 | A |
3651720 | Indyk | Mar 1972 | A |
3734515 | Dudek | May 1973 | A |
3752214 | Pertot | Aug 1973 | A |
4277990 | Hall | Jul 1981 | A |
4907476 | Singleton | Mar 1990 | A |
4991470 | Singleton | Feb 1991 | A |
4991472 | Hollingsworth | Feb 1991 | A |
5038869 | Olson | Aug 1991 | A |
5050467 | Brown et al. | Sep 1991 | A |
5152197 | Szymber et al. | Oct 1992 | A |
5485769 | Olson et al. | Jan 1996 | A |
5595099 | Pusateri | Jan 1997 | A |
6038946 | Jackson et al. | Mar 2000 | A |
6070674 | Williamson et al. | Jun 2000 | A |
6367356 | Stepp | Apr 2002 | B1 |
6457535 | Tanaka | Oct 2002 | B1 |
6748828 | Bollinger | Jun 2004 | B2 |
6938526 | Milbourne et al. | Sep 2005 | B2 |
7114418 | Allen | Oct 2006 | B1 |
Number | Date | Country | |
---|---|---|---|
20060118316 A1 | Jun 2006 | US |