FIELD OF THE INVENTION
The present invention relates to rotary power tools, and more particularly to rotary power tools with reciprocating spindles.
BACKGROUND OF THE INVENTION
Some power tools include a spindle that reciprocates while rotating in a housing. The spindle is sometimes supported by a bearing that moves along the housing as the spindle reciprocates.
SUMMARY OF THE INVENTION
The present invention provides, in one aspect, a rotary power tool comprising a drive mechanism including an electric motor and a transmission, a housing enclosing at least a portion of the drive mechanism, a spindle rotatable in response to receiving torque from the drive mechanism, a first ratchet coupled for co-rotation with the spindle, a second ratchet rotationally fixed to the housing, a sleeve bushing on an interior of the housing, and a bearing arranged between the spindle and the sleeve bushing and rotatably supporting the spindle, the bearing having an outer race. The spindle is movable relative to the housing in response to contact with a workpiece, causing the first and second ratchets to engage and the spindle to reciprocate while rotating. The outer race of the bearing moves along the sleeve bushing during reciprocation of the spindle when the first ratchet and second ratchet are engaged.
The present invention provides, in another aspect, a rotary power tool comprising a drive mechanism including an electric motor and a transmission, a housing enclosing at least a portion of the drive mechanism and including a protrusion, a spindle rotatable in response to receiving torque from the drive mechanism, a first ratchet coupled for co-rotation with the spindle, a second ratchet rotationally fixed to the housing, a sleeve bushing on an interior of the housing, the protrusion of the housing extending through the sleeve bushing, and a bearing arranged between the spindle and the sleeve bushing and rotatably supporting the spindle. The bearing has an outer race. The rotary power tool further includes a hammer lockout mechanism adjustable between a first mode and a second mode. The hammer lockout mechanism includes an aperture extending through the protrusion and a ball movable within the aperture between a locking position and an unlocking position. In the first mode, the ball is moveable from the locking position to the unlocking position, such that the spindle is movable relative to the housing in response to contact with a workpiece, causing the first and second ratchets to engage and the spindle to reciprocate while rotating. The outer race of the bearing moves along the sleeve bushing during reciprocation of the spindle when the first ratchet and second ratchet are engaged. In the second mode, the ball is prevented from moving from the locking position to the unlocking position, such that the spindle is blocked by the ball from moving relative to the housing in response to contact with a workpiece and a gap is maintained between the first and second ratchets.
The present invention provides, in yet another aspect, a rotary power tool comprising a drive mechanism including an electric motor and a transmission, a housing enclosing at least a portion of the drive mechanism and including a plurality of protrusions, a spindle rotatable in response to receiving torque from the drive mechanism, a first ratchet coupled for co-rotation with the spindle, a second ratchet rotationally fixed to the housing, a sleeve bushing on an interior of the housing, the protrusions of the housing extending through the sleeve bushing, and a bearing arranged between the spindle and the sleeve bushing and rotatably supporting the spindle. The bearing has an outer race. The rotary power tool further comprises a hammer lockout mechanism adjustable between a first mode and a second mode. The hammer lockout mechanism includes a plurality of apertures. Each of the apertures extends through one of the plurality of protrusions. The hammer lockout mechanism also includes a ball arranged in each aperture. Each ball is moveable between a locking position and an unlocking position. In the first mode, each of the balls is moveable from the locking position to the unlocking position, such that the spindle is movable relative to the housing in response to contact with a workpiece, causing the first and second ratchets to engage and the spindle to reciprocate while rotating. The outer race of the bearing moves along the sleeve bushing during reciprocation of the spindle when the first ratchet and second ratchet are engaged. In the second mode, at least one of the balls is prevented from moving from the locking position to the unlocking position, such that the spindle is blocked by one or more balls from moving relative to the housing in response to contact with a workpiece and a gap is maintained between the first and second ratchets.
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 perspective view of a portion of a hammer drill in accordance with an embodiment of the invention.
FIG. 2 is an enlarged, exploded view of a front portion of the hammer drill of FIG. 1, with a collar rendered transparent to illustrate a selector ring.
FIG. 3 is a longitudinal cross-sectional view of the hammer drill of FIG. 1.
FIG. 4 is an enlarged view of the hammer drill of FIG. 3, with portions removed, illustrating a hammer lock-out mechanism in a disabled mode.
FIG. 5 is a lateral cross-sectional view of the hammer lock-out mechanism of FIG. 4 coinciding with a first rotational position of a collar of the hammer drill.
FIG. 6 is an enlarged view of the hammer drill of FIG. 3, with portions removed, illustrating the hammer lock-out mechanism in an enabled mode.
FIG. 7 is a lateral cross-sectional view of the hammer lock-out mechanism of FIG. 6 coinciding with a second rotational position of the collar.
FIG. 8 is a lateral cross-sectional view of the hammer lock-out mechanism coinciding with a third rotational position of the collar.
FIG. 9 is a lateral cross-sectional view of the hammer lock-out mechanism coinciding with a fourth rotational position of the collar.
FIG. 10 is a lateral cross-sectional view of the hammer lock-out mechanism coinciding with a fifth rotational position of the collar.
FIG. 11 is a lateral cross-sectional view of the hammer lock-out mechanism coinciding with a sixth rotational position of the collar.
FIG. 12 is a lateral cross-sectional view of the hammer lock-out mechanism coinciding with a seventh rotational position of the collar.
FIG. 13 is a lateral cross-sectional view of the hammer lock-out mechanism coinciding with an eighth rotational position of the collar.
FIG. 14 is a lateral cross-sectional view of the hammer lock-out mechanism coinciding with a ninth rotational position of the collar.
FIG. 15 is a lateral cross-sectional view of the hammer lock-out mechanism coinciding with a tenth rotational position of the collar.
FIG. 16 is a lateral cross-sectional view of the hammer lock-out mechanism coinciding with a eleventh rotational position of the collar.
FIG. 17 is a lateral cross-sectional view of the hammer lock-out mechanism coinciding with a twelfth rotational position of the collar.
FIG. 18 is a lateral cross-sectional view of the hammer lock-out mechanism coinciding with a thirteenth rotational position of the collar.
FIG. 19 is a lateral cross-sectional view of the hammer lock-out mechanism coinciding with a fourteenth rotational position of the collar.
FIG. 20 is a lateral cross-sectional view of the hammer lock-out mechanism coinciding with a fifteenth rotational position of the collar.
FIG. 21 is a lateral cross-sectional view of the hammer lock-out mechanism coinciding with a sixteenth rotational position of the collar.
FIG. 22 is a lateral cross-sectional view of the hammer lock-out mechanism coinciding with a seventeenth rotational position of the collar.
FIG. 23 is a lateral cross-sectional view of the hammer lock-out mechanism coinciding with a eighteenth rotational position of the collar.
FIG. 24 is a lateral cross-sectional view of the hammer lock-out mechanism coinciding with a nineteenth rotational position of the collar.
FIG. 25 is a lateral cross-sectional view of the hammer lock-out mechanism coinciding with a twentieth rotational position of the collar.
FIG. 26 is a prospective view of a transmission housing of the hammer drill of FIG. 1, according to another embodiment of the invention.
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
As shown in FIGS. 1-3, a rotary power tool, in this embodiment a hammer drill 10, includes a housing 12, a drive mechanism 14 and a spindle 18 rotatable in response to receiving torque from the drive mechanism 14. As shown in FIG. 3, the drive mechanism 14 includes an electric motor 22 and a multi-speed transmission 26 between the motor 22 and the spindle 18. The drive mechanism 14 is at least partially enclosed by a transmission housing 30. As shown in FIGS. 1 and 3, a chuck 34 is provided at the front end of the spindle 18 so as to be co-rotatable with the spindle 18. The chuck 34 includes a plurality of jaws 38 configured to secure a tool bit or a drill bit (not shown), such that when the drive mechanism 14 is operated, the bit can perform a rotary and/or percussive action on a fastener or workpiece. The hammer drill 10 includes a pistol grip handle 36, a trigger 39 for activating the motor 22, and an auxiliary handle 40 that can be selectively removed from the transmission housing 30. The hammer drill 10 may be powered by an on-board power source such as a battery 41 or a remote power source (e.g., an alternating current source) via a cord (not shown).
With reference to FIGS. 2 and 3, the hammer drill 10 includes a first ratchet 42 coupled for co-rotation with the spindle 18 and a second ratchet 46 axially and rotationally fixed to the transmission housing 30. In other embodiments, the second ratchet 46 is rotationally fixed, but axially moveable relative to the transmission housing 30. As shown in FIGS. 3, 4 and 6, a first bearing 50 with an outer race 52 having an edge 54 is radially positioned between the transmission housing 30 and the spindle 18 and supports a front portion 58 of the spindle 18. In the illustrated embodiment, the edge 54 is chamfered, but in other embodiments, In other embodiments, the chamfered edge 54 is a part separate from the outer race 52. In other embodiments, the
As shown in FIG. 3, the second ratchet 46 includes a bearing pocket 62 defined in a rear end of the second ratchet 46. A second bearing 66 is at least partially positioned in the bearing pocket 62 and supports a rear portion 70 of the spindle 18. In the illustrated embodiment, the second bearing 66 is wholly received in the bearing pocket 62, but in other embodiments the second bearing 66 may at least partially extend from the bearing pocket 62. By incorporating the bearing pocket 62 in the second ratchet 46, the second bearing 66 is arranged about the rear portion 70 of the spindle 18 in a nested relationship within the second ratchet 46, thereby reducing the overall length of the hammer drill 10 while also supporting rotation of the spindle 18.
With reference to FIGS. 1-7, the hammer drill 10 includes a collar 74 that is rotatably adjustable by an operator of the hammer drill 10 to shift between “hammer drill,” “drill-only,” and “screwdriver” modes of operation, and to select a particular clutch setting when in “screwdriver mode.” Thus, the collar 74 is conveniently provided as a single collar that can be rotated to select different operating modes of the hammer drill 10 and different clutch settings. As shown in FIGS. 2 and 3, the hammer drill 10 also includes an electronic clutch 78 capable of limiting the amount of torque that is transferred from the spindle 18 to a fastener (i.e., when in “screwdriver mode”) by deactivating the motor 22 in response to a detected torque threshold or limit. The electronic clutch 78 includes a printed circuit board (“PCB”) 82 coupled to the transmission housing 30 and a wiper (not shown), which is coupled for co-rotation with the collar 74. The PCB 82 includes a plurality of electrical pads 86 which correspond to different clutch settings of the hammer drill 10.
The hammer drill 10 also includes a hammer lockout mechanism 90 (FIGS. 4-7) for selectively inhibiting the first and second ratchets 42, 46 from engaging when the hammer drill 10 is in a “screwdriver mode” or a “drill-only mode.” The hammer lockout mechanism 90 includes a selector ring 94 coupled for co-rotation with and positioned inside the collar 74, and a plurality of balls 98 situated within corresponding radial apertures A1, A2, A3, A4, and A5 asymmetrically positioned around and extending through an annular portion 102 of the transmission housing 30.
As shown in FIGS. 3, 4, and 6, but not shown in FIG. 2, a sleeve bushing 105 is positioned on an inner surface 103 of the annular portion 102. The bushing 105 can be formed or secured along the inner surface 103 of the annular portion 102 in a variety of ways, including but not limited to insert molding, pressing, shrink fitting, or trapping with a retaining ring or screws. The annular portion 102 of the transmission housing 30 is formed of a relatively soft material including but not limited to aluminum or magnesium, whereas the bushing 105 is formed of a relatively harder material than aluminum or magnesium, including but not limited to steel. In some embodiments, the relatively softer material is below 20 HRC and the relatively harder material is equal to or above 20 HRC. In other embodiments, the relatively softer material is less is below 40 HRC and the relatively harder material is equal to or above 40 HRC.
In the illustrated embodiment, the bushing 105 is located along the length of the inner surface 103 of the annular portion 102, which includes a plurality of radially inward-extending protrusions P1-P5 extending through sleeve bushing 105. The apertures A1-A5 respectively extend through the protrusions P1-P5 of the annular portion 102, such that the apertures A1-A5 are defined by the softer material forming the protrusions P1-P5 and the rest of annular portion 102. Specifically, the apertures A1-A5 extend from an inner end of the protrusions P1-P5 to an outer surface of the annular portion 102. In other embodiments, the protrusions P1-P5 are omitted and the apertures A1-A5 are at least partially defined by the sleeve bushing 105. In other embodiments, the protrusions P1-P5 are omitted and the bushing 105 can be located in front of the apertures A1-A5 (i.e., with the chuck 34 located at the front of the hammer drill 10), such that no portion of the bushing 105 intersects or overlaps the apertures A1-A5, as shown in FIG. 26. In some embodiments, the bushing 105 may extend forward along the inner surface 103 toward a distal end 107 of the annular portion 102, as shown in FIG. 26.
In the illustrated embodiment shown in FIGS. 4 and 6, only the ball 98 in aperture A5 is shown, but each of the other apertures A1, A2, A3, and A4 also contains a ball 98. As shown in FIGS. 2, 5 and 7-25, the selector ring 94 includes a plurality of recesses R1, R2, R3, R4, and R5 asymmetrically positioned about an inner periphery 112 of the selector ring 94. The number of recesses R1-R5 corresponds to the number of apertures A1-A5 and the number of balls 98 within the respective apertures A1-A5.
In the illustrated embodiment, five apertures A1-A5, each containing a ball 98, are located in the transmission housing 30 and five recesses R1-R5 are defined in the selector ring 94. However, in other embodiments, the hammer lockout mechanism 90 could employ more or fewer apertures, balls, and recesses. As shown in FIGS. 5 and 7, the five apertures A1-A5 are approximately located at 0 degrees, 55 degrees, 145 degrees, 221 degrees, and 305 degrees, respectively, measured in a counterclockwise direction from an oblique plane 104 containing a longitudinal axis 108 of the hammer drill 10 and bisecting aperture A1. As shown in FIGS. 4 and 6, the first ratchet 42 and the first bearing 50 are set within a cylindrical cavity 106 defined within the annular portion 102 of the transmission housing 30, and the selector ring 94 is radially arranged between the annular portion 102 and the collar 74, surrounding the apertures A1-A5.
In operation, as shown in FIGS. 4 and 5 when the collar 74 and ring 94 are rotated together to a position corresponding to a “hammer drill” mode, all five apertures A1-A5 are aligned with all five recesses R1-R5 in the selector ring 94, respectively. Therefore, when the spindle 18 is slid rearward relative to the transmission housing 30 in response to contact with a workpiece, the chamfered edge 54 of the first bearing 50 displaces the balls 98 situated in the respective apertures A1-A5 radially outward and partially into the recesses R1-R5, thereby disabling the hammer lockout mechanism 90. Thus, the first ratchet 42 is permitted to engage with the second ratchet 46 to impart reciprocation to the spindle 18 as it rotates.
As the spindle 18 reciprocates during “hammer drill” mode, the first bearing 50 reciprocates within the cavity 106, causing the outer race 52 of the first bearing 50 to move along the inner surface 103 of the annular portion 102. Because the outer race 52 slides along the sleeve bushing 105, which is formed of a harder material than the rest of the annular portion 102, the longevity of the transmission housing 30, and the inner surface 103 of the annular portion 102 in particular, is increased compared to a transmission housing 30 without the sleeve bushing 105. Through testing, it has been found that in absence of the bushing 105, the spindle 18 experiences wobble at 6,000 reciprocation cycles of the bearing 50. But, when the bushing 105 is used, the spindle 18 does not experience wobble even after 14,000 reciprocation cycles of the bearing 50. The sleeve bushing 105 wears at a much lower rate than the inner surface 103 of the annular portion 102, thus maintaining alignment of the spindle 18 with the longitudinal axis 108 of the hammer drill 10 throughout a longer period of the useful life of the hammer drill 10.
When the collar 74 and selector ring 94 are incrementally rotated (e.g., by 18 degrees) in a counterclockwise direction to the second rotational position shown in FIGS. 6 and 7, none of the apertures A1-A5 are aligned with the recesses R1-R5. Thus, in this position of the collar 74 and selector ring 94, the balls 98 in the respective apertures A1-A5 are prevented from being radially displaced into the recesses R1-R5 in response to the spindle 18 contacting a workpiece (via the chuck 34 and an attached drill or tool bit). Rather, the chamfered edge 54 of the first bearing 50 presses against the balls 98, which in turn abut against the inner periphery 112 of the selector ring 94 and are inhibited from displacing radially outward. Thus, the spindle 18 is prevented from moving rearward, maintaining a gap 110 between the first and second ratchets 42, 46. Thus, in the second rotational position of the collar 74 and the selector ring 94, the hammer lockout mechanism 90 is enabled, preventing the spindle 18 from reciprocating in an axial manner as it is rotated by the drive mechanism 14, operating the hammer drill 10 in a “drill only” mode.
There are a total of twenty different positions between which the collar 74 and selector ring 94 can rotate, such that the collar 74 is rotated 18 degrees between each of the positions. The wiper is in electrical and sliding contact with the PCB 82 as the collar 74 is rotated between each of the twenty positions. Depending upon which of the electrical pads 86 on the PCB 82 the wiper contacts, the electronic clutch 78 adjusts which clutch setting to apply to the motor 22. In the “hammer drill” mode and the “drill only” mode coinciding with the first and second rotational positions of the collar 74 and selector ring 94, respectively, the electronic clutch 78 operates the motor 22 to output torque at a predetermined maximum value to the spindle 18. In some embodiments, the predetermined maximum value of torque output by the motor 22 may coincide with the maximum rated torque of the motor 22.
As shown in FIG. 5 and the Table below, the “hammer drill” position of the collar 74 corresponds to a “0 degree” or “first rotational position” position of the collar 74, in which the recesses R1, R2, R3, R4, R5 of the selector ring 94 are respectively and approximately located at 0, 55, 145, 221, and 305 degrees counterclockwise from the plane 104, such that the apertures A1, A2, A3, A4, A5 are thereby aligned. When the collar 74 is rotated 18 degrees counterclockwise from the “hammer drill” position to the “drill only” or “second rotational position” as shown in FIG. 7, the recesses R1, R2, R3, R4, R5 are respectively and approximately located at 18 degrees, 73 degrees, 163 degrees, 239 degrees, and 323 degrees counterclockwise from the plane 104.
As shown in the Table below and in FIGS. 8-25, the operator may continue to cycle through eighteen additional rotational positions of the collar 74, each corresponding to a different clutch setting in “screwdriver mode”, by incrementally rotating the collar 74 counterclockwise by 18 degrees each time. The first clutch setting (FIG. 8) provides a torque limit that is slightly less than the predetermined maximum value of torque output by the motor 22 available in the “hammer drill” mode or the “drill only” mode. As the clutch setting number numerically increases, the torque threshold applied to the motor 22 decreases, with the eighteenth clutch setting (shown in FIG. 25) providing the lowest torque limit to the motor 22.
As can be seen in FIGS. 5 and 7-25, and the Table below, the “hammer drill” position in FIG. 5 is the only position in which all five apertures A1-A5 are aligned with all five recesses R1-R5, thereby disabling the hammer lockout mechanism 90 as described above. In every other setting of the collar 74 and selector ring 94, no more than two of any of the apertures A1-A5 are aligned with the recesses R1-R5. Therefore, in “drill-only” mode (FIG. 7) and “screwdriver mode” (FIGS. 8-25, clutch settings 1-18), at least three balls 98 inhibit the rearward movement of the spindle 18, via the first bearing 50, thereby enabling the hammer lockout mechanism 90 and preventing axial reciprocation of the spindle 18 as it rotates.
To adjust the hammer drill 10 between “screwdriver” mode, “drill only” mode, and “hammer drill” mode, the collar 74 may be rotated a full 360 degrees and beyond in a single rotational direction, clockwise or counterclockwise, without any stops which would otherwise limit the extent to which the collar 74 may be rotated. Therefore, if the operator is using the hammer drill 10 in “screwdriver mode” on the eighteenth clutch setting (FIG. 25), the operator needs only to rotate the collar 74 counterclockwise by an additional 18 degrees to switch the hammer drill 10 into “hammer drill” mode, rather than rotating the collar 74 in an opposite (clockwise) direction back through clutch settings 17 to 1 and “drill only” mode.
Various features of the invention are set forth in the following claims.
Patent Application
20190299383
