CROSS-REFERENCE TO RELATED APPLICATIONS
This application claims priority to U.S. Provisional Patent Application Ser. No. 61/051,119 filed on May 7, 2008, the entire contents of which is incorporated herein by reference.
FIELD OF THE INVENTION
The present invention relates to tools, and more particularly to power tools.
BACKGROUND OF THE INVENTION
Anvil assemblies are typically employed in power tools (e.g., electrically-operated power tools, pneumatic power tools, etc.) to transfer torque from a motor to a tool element to perform work on a workpiece. Particularly, impact wrenches utilize anvil assemblies to transfer a striking rotational force, or intermittent applications of torque, to the tool element and workpiece. As such, impact wrenches are typically used to loosen or remove stuck fasteners (e.g., an automobile lug nut on an axle stud) that are otherwise not removable or very difficult to remove using hand tools.
Depending upon the size and configuration of the impact wrench, a relatively large amount of torque may be transferred through the anvil to the tool element and workpiece. Anvils typically include a square head configured to receive the tool element, and a shoulder against which the tool element is abutted. The shoulder is typically formed by a continuous or non-continuous surface extending substantially perpendicular to one or more flats on the square head. As such, a fillet having a relatively small radius is often employed to transition the respective flats on the square head to the shoulder on the anvil. Such small fillet radii, as a result of the high torsional loads that may be carried through the anvil, often yield an area of high stress at the base of the head.
SUMMARY OF THE INVENTION
The invention provides, in one aspect, an anvil assembly for a tool. The tool includes a tool element for working on a workpiece. The anvil assembly includes an anvil having a body with an outer periphery and a head formed on a distal end of the body. The anvil assembly also includes a sleeve surrounding at least a portion of the outer periphery of the body. The sleeve has a distal end against which the tool element is abutted when the tool element is coupled to the head.
The invention provides, in another aspect, a power tool operable with a tool element for working on a workpiece. The power tool includes a housing, a motor supported by the housing, and an anvil coupled to the motor to receive torque produced by the motor. The anvil includes a body having an outer periphery and a head formed on a distal end of the body. The power tool also includes a sleeve surrounding at least a portion of the outer periphery of the body. The sleeve has a distal end against which the tool element is abutted when the tool element is coupled to the head.
The invention provides, in yet another aspect, a power tool operable with a tool element for working on a workpiece. The power tool includes a housing, a motor supported by the housing, and an anvil coupled to the motor to receive torque produced by the motor. The anvil includes a body having an outer periphery, a head formed on a distal end of the body, and a plurality of radially-extending lugs extending from the body. The power tool also includes a sleeve surrounding at least a portion of the outer periphery of the body. The sleeve includes a distal end against which the tool element is abutted when the tool element is coupled to the head, and a flange spaced from the distal end and abutted against the radially-extending lugs.
Other features and aspects of the invention will become apparent by consideration of the following detailed description and accompanying drawings.
BRIEF DESCRIPTION OF THE DRAWINGS
FIG. 1 is a side view of an impact wrench incorporating an anvil assembly according to one construction of the invention.
FIG. 2 is a partial cutaway view of the impact wrench of FIG. 1, illustrating the anvil assembly in cross-section.
FIG. 3 is an exploded perspective view of the anvil assembly of FIG. 2.
FIG. 4 is a front view of the anvil assembly of FIG. 3.
FIG. 5 is a cross-sectional view of the anvil assembly of FIG. 3, taken along line 5-5 in FIG. 4.
FIG. 6 is a cross-sectional view of the anvil assembly of FIG. 3, taken along line 6-6 in FIG. 4.
FIG. 6
a is a cross-sectional view, similar to that of FIG. 6, of the anvil assembly of FIG. 3 having a differently configured head.
FIG. 7 is an exploded perspective view of an anvil assembly according to another construction of the invention.
FIG. 8 is an exploded, front perspective view of an anvil assembly according to yet another construction of the invention.
FIG. 9 is an exploded, rear perspective view of the anvil assembly of FIG. 8.
FIG. 10 is a partial cutaway view of an impact wrench incorporating the anvil assembly of FIGS. 8 and 9, and illustrating the anvil assembly in cross-section.
Before any embodiments of the invention are explained in detail, it is to be understood that the invention is not limited in its application to the details of construction and the arrangement of components set forth in the following description or illustrated in the following drawings. The invention 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.
DETAILED DESCRIPTION
FIG. 1 illustrates an impact wrench 10 including an anvil assembly 14 and a tool element 18 coupled to the anvil assembly 14. Although the tool element 18 is schematically illustrated, the tool element 18 may include a socket configured to engage the head of a fastener (e.g., a bolt). Alternatively, the tool element 18 may include any of a number of different configurations (e.g., an auger or a drill bit) to perform work on a workpiece. With reference to FIGS. 1 and 2, the impact wrench 10 includes a housing 22 and a reversible electric motor 26 (FIG. 2) coupled to the anvil assembly 14 to provide torque to the anvil assembly 14 and the tool element 18. The impact wrench 10 also includes a switch (e.g., trigger switch 30) supported by the housing 22 and a power cord 34 extending from the housing 22 for electrically connecting the switch 30 and the motor 26 to a source of AC power. Alternatively, the impact wrench 10 may include a battery, and the motor 26 may be configured to operate on DC power provided by the battery. As a further alternative, the impact wrench 10 may be configured to operate using a different power source (e.g., a pneumatic or hydraulic power source, etc.) besides electricity.
With reference to FIG. 2, the impact wrench 10 also includes a gear assembly 38 coupled to an output of the motor 26 and a drive assembly 42 coupled to an output of the gear assembly 38. The gear assembly 38 may be configured in any of a number of different ways to provide a speed reduction between the output of the motor 26 and an input of the drive assembly 42. The drive assembly 42, of which the anvil assembly 14 may be considered a component, is configured to convert the constant rotational force or torque provided by the gear assembly 38 to a striking rotational force or intermittent applications of torque to the tool element 18. U.S. Pat. No. 6,733,414, the entire contents of which is incorporated herein by reference, discloses in detail example configurations of the gear assembly 38 and portions of the drive assembly 42 between the anvil assembly 14 and the gear assembly 38. The impact wrench 10 further includes a bushing 44 secured to the front of the housing 22 to rotatably support the anvil assembly 14. Alternatively, a bearing (e.g., a roller or ball bearing) may be substituted for the bushing 44.
With reference to FIGS. 2 and 3, the anvil assembly 14 includes an anvil 46 and a sleeve 50 supporting the anvil 46 for rotation in the housing 22. The anvil 46 includes a body 54 having a cylindrical outer periphery 58 defining a longitudinal axis 62, and a head 66 formed on a distal end of the body 54. As shown in FIG. 5, the sleeve 50 surrounds the body 54, and in the illustrated construction of the anvil assembly 14, the outer diameter of the cylindrical outer periphery 58 of the body 54 and the inner diameter of the sleeve 50 are sized to provide an interference fit between the sleeve 50 and the body 54. In another construction, different structure (e.g., a key and keyway arrangement) may be utilized to interconnect the sleeve 50 and the body 54 so that the sleeve 50 co-rotates with the body 54 during operation of the impact wrench 10. Further, any of a number of different processes (e.g., welding, brazing, using adhesives, etc.) may also be utilized in addition to or in place of the interference fit between the sleeve 50 and the body 54.
With reference to FIGS. 3 and 4, the head 66 includes a generally square cross-sectional shape as viewed in a direction along the longitudinal axis 62 (FIG. 4), and includes a plurality of substantially flat or planar surfaces 70 that, taken together, form the generally square cross-sectional shape of the head 66. In the illustrated construction of the anvil assembly 14, the head 66 includes four substantially planar surfaces 70, with adjacent substantially planar surfaces 70 oriented substantially normal to each other. Alternatively, the cross-sectional shape of the head 66 may be configured in any of a number of different ways to accept or receive tool elements 18 having corresponding-shaped apertures or recesses to receive the head 66.
With reference to FIGS. 3 and 5, the anvil 46 also includes a plurality of fillets, or curved or substantially arcuate surfaces 74, each of which at least partially transitions a respective substantially planar surface 70 of the head 66 to the cylindrical outer periphery 58 of the body 54. As shown in FIG. 5, each of the arcuate surfaces 74 has a relatively large radius R1 to reduce the stress applied to the anvil 46 at the base of the head 66 during operation of the impact wrench 10. Preferably, the radius R1 of the arcuate surfaces 74 is sized as large as the particular design of the anvil 46 permits. For example, the radius R1 of the arcuate surfaces 74 may be at least about 0.5 inches. Alternatively, the radius R1 of the arcuate surfaces 74 may be at least about 0.375 inches. As a further alternative, the radius R1 of the arcuate surfaces 74 may be at least about 0.25 inches. The radius R1 of the arcuate surfaces 74 may alternatively correlate with the cross-sectional dimensions of the head 66 (i.e., the width of the planar surfaces 70). For example, the radius R1 of the arcuate surfaces 74 may correlate to the width W (FIG. 4) of the head 66, as measured in a direction transverse to the longitudinal axis 62, by a constant “X.” As such, an anvil 46 having a head 66 with a nominal dimension of 0.5 inches for the width W (i.e., a half-inch drive head 66) would include arcuate surfaces 74 having a radius R1 of about 0.5X inches. In the illustrated construction of the anvil assembly 14, the radius R1 of the arcuate surfaces 74 is about equal to (i.e., 1-time) the width W of the head 66. Therefore, for a half-inch drive head 66, the radius R1 of the arcuate surfaces 74 is equal to about 0.5 inches. Likewise, for a three-eighths drive head 66, the radius of the arcuate surface 74 would be equal to about 0.375 inches, and for a quarter-inch drive head 66, the radius of the arcuate surface 74 would be equal to about 0.25 inches.
With reference to FIGS. 3 and 6, the anvil 46 also includes a substantially planar end surface 78 formed on the distal end of the head 66, and a corner 82 disposed at an intersection of each pair of adjacent substantially planar surfaces 70. The corners 82 at least partially transition the substantially planar surfaces 70 to the substantially planar end surface 78 of the head 66. The anvil 46 also includes a chamfer 83 having a first edge 84 shared with the substantially planar end surface 78 and a second edge 85 shared with the corners 82. By providing the corners 82 on the head 66, stress applied near the distal end of the head 66 is more efficiently transferred away from the distal end of the head 66, and toward the base of the head 66 and the substantially arcuate surfaces 74 of the head 66. Particularly, by providing the corners 82 on the head 66, torsional loading near the planar end surface 78 is reduced. As a result, stress surrounding a detent aperture 86 in the head 66 (FIGS. 2 and 3) is reduced and efficiently transferred toward the base of the head 66 and the substantially arcuate surfaces 74.
With reference to FIG. 6, each of the corners 82 defines a radius R2 having a center (one of which is shown with reference numeral “92” in FIG. 6) located rearward of the detent aperture 86 (FIG. 5). For example, the radius R2 of each of the corners 82 may be at least about 1 inch. Alternatively, the radius R2 of each of the corners 82 may be at least about 0.75 inches. As a further alternative, the radius R2 of each of the corners 82 may be at least about 0.5 inches. Like the radius R1, the radius R2 of the corners 82 may alternatively correlate to the width W of the head 66 by a constant “Y.” For an anvil 46 having a head 66 with a nominal dimension of 0.5 inches for the width W (i.e., a half-inch drive head 66), the corners 82 would define a radius R2 of about 0.5Y inches. For example, the radius R2 of the corners 82 may be about 2 times the width W of the head 66 (i.e., about 1 inch for a half-inch drive head 66, about 0.75 inches for a three-eighths drive head 66, and about 0.5 inches for a quarter-inch drive head 66; where Y=2). Alternatively, the radius R2 may be greater or less than 2 times the width W of the head 66. As a further alternative, the radius R2 may be sized as large as the particular design of the head 66 permits.
With reference to FIG. 6a, the anvil assembly 14 may alternatively include corners (denoted by reference numerals 82′) that are tapered rather than defined by a radius. Each of the corners 82′ forms an angle A with a reference plane 90 oriented substantially normal to the planar end surface 78 of the head 66. For example, the angle A may be about 11 degrees. However, the angle A may be greater than or less than about 11 degrees. Generally, the greater the value of the angle A, the more efficiently stress applied near the distal end of the head 66 is transferred toward the base of the head 66.
With reference to FIGS. 1 and 2, the sleeve 50 includes a distal end 94 against which the tool element 18 is abutted when coupled to the head 66. As shown in FIGS. 2 and 5, the distal end 94 of the sleeve 50 extends past an interface between each of the respective substantially planar surfaces 70 and the respective substantially arcuate surfaces 74, such that the sleeve 50 substantially overlies each of the surfaces 74. As such, the extent to which the tool element 18 is engageable with the head 66 is limited by the position of the distal end 94 of the sleeve 50 relative to the head 66, thereby preventing the tool element 18 from engaging the substantially arcuate surfaces 74. The distal end 94 of the sleeve 50 also accurately locates the tool element 18 relative to a detent pin 96 located in the detent aperture 86 (FIG. 2), such that the tool element 18 is securely attached to the anvil 46 upon abutting the distal end 94 of the sleeve 50.
With reference to FIG. 5, the sleeve 50 includes a second distal end 97 opposite the distal end 94 against which the tool element 18 is abutted. The anvil 46 includes a relatively large, continuous flange 98 (FIGS. 2 and 5) against which the second distal end 97 of the sleeve is abutted. By configuring the anvil assembly 14 as two separate and distinct pieces or components (i.e., the anvil 46 and the sleeve 50), the function of providing a shoulder to abut the tool element 18 is shifted to the sleeve 50, which bears against the flange 98 formed on the anvil 46. Consequently, the radii of the respective fillets or arcuate surfaces 74 may be increased to reduce the stress near the base of the head 66 during operation of the impact wrench 10. Because the fillets or arcuate surfaces 74 need not transition the respective substantially planar surfaces 70 of the head 66 to one or more surfaces that are substantially normal to the longitudinal axis 62 of the anvil 46 to provide a shoulder against which the tool element 18 may be abutted, the radii of the respective fillets or arcuate surfaces 74 on the anvil 46 may be increased as large as the design of the anvil 46 allows.
With reference to FIG. 7, a second construction of the anvil assembly 14a is shown, with like components labeled with like reference numerals including the letter “a.” The anvil assembly 14a is substantially similar to the anvil assembly 14 of FIGS. 1-6, however, the sleeve 50a of the anvil assembly 14a is shorter than the sleeve 50 of the anvil assembly 14 of FIGS. 1-6. Rather than bearing against the flange 98a on the anvil 46, the second end 97 of the sleeve 50a bears against an end surface 102 of the cylindrical outer periphery 58a of the body 54a.
With reference to FIGS. 8 and 9, a third construction of the anvil assembly 14b is shown, with like components labeled with like reference numerals including the letter “b.” The anvil assembly 14b is substantially similar to the anvil assembly 14 of FIGS. 1-6, however, the flange 98b is moved from the anvil 46b to the sleeve 50b. The rear of the flange 98b, in turn, is abutted against a plurality of radially-extending, driven anvil lugs 106 on the rear of the anvil 46b. With reference to FIG. 10, an impact wrench 10b incorporating the anvil assembly 14b is shown, with like components labeled with like reference numerals including the letter “b.” The flange 98b is trapped between a front portion of the impact wrench housing 22b and the anvil lugs 106 such that axial movement of the sleeve 50b relative to the housing 22b is substantially constrained. As such, the sleeve 50b need not be attached to the anvil 46b for co-rotation (i.e., by press-fitting, welding, brazing, using adhesives, etc.), but rather may be slip-fit to the anvil 46b to allow the sleeve 50b to rotate relative to the anvil 46b during operation of the impact wrench 10b. Alternatively, the sleeve 50b may be fixed to the anvil 46b for co-rotation with the anvil 46b during operation of the impact wrench 10b.
Yet another embodiment of the anvil assembly (not shown) may omit the separate sleeve (e.g., sleeve 50 in FIG. 2), and the bushing 44 in the front of the impact wrench 10 may extend from the front of the housing 22 to position the distal end of the bushing 44 in the same location where the distal end 94 of the sleeve 50 is shown in FIG. 2. In addition to rotatably supporting the anvil 94 relative to the housing 22, the bushing 44 would also space the tool element 18 from the arcuate surfaces 74 of the anvil and accurately locate the tool element 18 relative to the detent 96. In such an alternative embodiment of the anvil assembly, the bushing 44 could be considered a sleeve.
Various features of the invention are set forth in the following claims.
Patent Grant
8839879
