Impact tool with adjustable clutch

Information

  • Patent Grant
  • 9289886
  • Patent Number
    9,289,886
  • Date Filed
    Wednesday, October 26, 2011
    13 years ago
  • Date Issued
    Tuesday, March 22, 2016
    8 years ago
Abstract
An impact tool includes a housing, a motor supported in the housing, an output shaft rotatably supported in the housing about a central axis, an impact mechanism coupled between the motor and the output shaft and operable to impart a striking rotational force to the output shaft, and a clutch mechanism coupled between the impact mechanism and the output shaft. The clutch mechanism is operable in a first mode, in which torque from the motor is transferred to the output shaft through the impact mechanism, and a second mode, in which torque from the motor is diverted from the output shaft toward a portion of the impact mechanism.
Description
FIELD OF THE INVENTION

The present invention relates to tools, and more particularly to power tools.


BACKGROUND OF THE INVENTION

Impact tools or wrenches are typically utilized to provide a striking rotational force, or intermittent applications of torque, to a tool element and workpiece (e.g., a fastener) to either tighten or loosen the fastener. Conventional pneumatic impact wrenches include at least two torque settings for rotating the output shaft of the impact wrench in a clockwise or tightening direction to permit the user of the impact wrench to adjust the amount of torque available at the output shaft during use. Such a feature is typically provided by a valve that meters the amount of air entering the air motor, which is directly proportional to the torque output achieved by the air motor.


SUMMARY OF THE INVENTION

The invention provides, in one aspect, an impact tool including a housing, a motor supported in the housing, an output shaft rotatably supported in the housing about a central axis, an impact mechanism coupled between the motor and the output shaft and operable to impart a striking rotational force to the output shaft, and a clutch mechanism coupled between the impact mechanism and the output shaft. The clutch mechanism is operable in a first mode, in which torque from the motor is transferred to the output shaft through the impact mechanism, and a second mode, in which torque from the motor is diverted from the output shaft toward a portion of the impact mechanism.


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 front perspective view of an impact tool according to an embodiment of the invention.



FIG. 2 is an exploded, front perspective view of the impact tool of FIG. 1.



FIG. 3 is an exploded, rear perspective view of the impact tool of FIG. 1.



FIG. 4 is a partially exploded, front perspective view of the impact tool of FIG. 1, illustrating the impact tool in driver mode.



FIG. 5 is a partial cross-sectional view of the impact tool of FIG. 1 along line 5-5 in FIG. 1, illustrating a clutch mechanism in an engaged configuration.



FIG. 6 is a partial cross-sectional view of the impact tool of FIG. 5, illustrating the clutch mechanism in a disengaged configuration.



FIG. 7 is a partially exploded, front perspective view of the impact tool of FIG. 1, illustrating the impact tool in drill mode.



FIG. 8 is a partial cross-sectional view of the impact tool of FIG. 5, illustrating the clutch mechanism in a locked-out configuration.





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 tool 10 including a drive end 14 having a non-cylindrical receptacle or bore 18 within which a fastener or a tool bit may be received. In the illustrated construction of the tool 10, the non-cylindrical bore 18 includes a hexagonal cross-sectional shape. However, the non-cylindrical bore 18 may be shaped in any of the number of different ways to receive any of a number of different fasteners and/or tool bits. The drive end 14 includes an output shaft 22 having a detent 26 (FIG. 2) utilized to lock or axially secure the fastener and/or tool bit to the drive end 14 of the tool 10, a sleeve 30 positioned over the output shaft 22 for actuating the detent 26 between a locked and an unlocked configuration, and a biasing member (e.g., a compression spring, not shown) for biasing the sleeve 30 toward a position in which the detent 26 is in the locked configuration. Alternatively, the detent 26, the sleeve 30, and the spring may be omitted from the output shaft 22, such that the fastener and/or tool bit is not lockable to the drive end 14 of the tool 10.


With reference to FIGS. 2 and 3, the impact tool 10 includes a housing 34, a motor 38 supported in the housing 34, and a transmission 42 operably coupled to the motor 38 to receive torque from the motor 38. The output shaft 22 is rotatable about a central axis 46 and operably coupled to the transmission 42 to receive torque from the transmission 42.


In the illustrated construction of the tool 10, the housing 34 includes a handle 50 in which a battery pack 54 is received. The battery pack 54 is electrically connected to the motor 38 (via a trigger-switch and microcontroller) to provide power to the motor 38. The battery pack 54 is a 12-volt power tool battery pack 54 and includes three lithium-ion battery cells. Alternatively, the battery pack 54 may include fewer or more battery cells to yield any of a number of different output voltages (e.g., 14.4 volts, 18 volts, etc.). Additionally or alternatively, the battery cells may include chemistries other than lithium-ion such as, for example, nickel cadmium, nickel metal-hydride, or the like. Alternatively, the battery pack 54 may be coupled to a different portion of the housing 34 (e.g., a motor support portion of the housing 34). As a further alternative, the tool 10 may include an electrical cord for connecting the motor 38 to a remote electrical source (e.g., a wall outlet).


The motor 38 is configured as a direct-current, can-style motor 38 having an output shaft 58 upon which a pinion 62 is fixed for rotation (FIG. 2). In the illustrated construction of the tool 10, the pinion 62 is interference or press-fit to the motor output shaft 58. Alternatively, the pinion 62 may be coupled for co-rotation with the motor output shaft 58 in any of a number of different ways (e.g., using a spline fit, a key and keyway arrangement, by welding, brazing, using adhesives, etc.). As a further alternative, the pinion 62 may be integrally formed as a single piece with the motor output shaft 58.


With reference to FIGS. 2 and 3, the transmission 42 includes two stages of speed reduction, including a first stage planetary transmission 66 and a second stage planetary transmission 70. The transmission 42 also includes a gear case 74 within which the first and second stage planetary transmissions 66, 70 are received. In the illustrated construction of the tool 10, the gear case 74 is secured to a front portion 78 (FIG. 1) of the housing 34 using a pair of pins 82 received in respective apertures 86, 90 in the gear case 74 and the front portion 78 of the housing 34. Alternatively, the gear case 74 and the front portion 78 of the housing 34 may be coupled in any of a number of different ways (e.g., using snap-fits, using adhesives, by welding, etc.).


With continued reference to FIGS. 2 and 3, the first stage planetary transmission 66 includes an outer ring gear 94, a carrier 98 rotatable about the central axis 46, and a plurality of planet gears 102 rotatably coupled to the carrier 98 about respective axes radially spaced from the central axis 46. The outer ring gear 94 includes a plurality of radially inwardly-extending teeth 106 that are engageable by corresponding teeth 110 on the planet gears 102. The outer ring gear 94 also includes a plurality of radially outwardly-extending protrusions 114, and the gear case 74 includes a corresponding plurality of slots 116 (FIG. 3) within which the protrusions 114 are received to rotationally fix the outer ring gear 94 to the gear case 74, and therefore the housing 34. Alternatively, the outer ring gear 94 may be fixed to the gear case 74 in any of a number of different ways (e.g., using snap-fits, an interference or press-fit, fasteners, adhesives, by welding, etc.) As a further alternative, the outer ring gear 94 may be integrally formed as a single piece with the gear case 74.


With reference to FIG. 2, the carrier 98 includes a sun gear 118 that is co-rotatable with the carrier 98 and the planet gears 102 about the central axis 46. In the illustrated construction of the tool 10, the sun gear 118 is integrally formed as a single piece with the carrier 98. Alternatively, the sun gear 118 may be a separate and distinct component from the carrier 98, and coupled to the carrier 98 for co-rotation with the carrier 98 in any of a number of different ways (e.g., using an interference or press-fit, fasteners, adhesives, by welding, etc.).


With reference to FIGS. 2 and 3, the second stage planetary transmission 70 includes a carrier 122 rotatable about the central axis 46, and a plurality of planet gears 126 rotatably coupled to the carrier 122 about respective axes radially spaced from the central axis 46. The outer ring gear 94 is shared between the first and second stage planetary transmissions 66, 70, such that the teeth 106 on the outer ring gear 94 are engaged with corresponding teeth 130 on the planet gears 126. With reference to FIG. 2, the carrier 122 includes an aperture 134 having a non-circular cross-sectional shape, the purpose of which is discussed below.


With continued reference to FIGS. 2 and 3, the tool 10 includes an impact mechanism 138 including a rotating shaft 142, a hammer 146 supported on the shaft 142 for rotation with the shaft 142, and an anvil 150. The end of the shaft 142 includes a projection 154 having a non-circular cross-sectional shape corresponding to that of the aperture 134 in the carrier 122. The projection 154 on the shaft 142 is received within the aperture 134 such that the shaft 142 and the carrier 122 co-rotate at all times. Alternatively, the shaft 142 may be non-rotatably coupled to the carrier 122 in any of a number of different ways.


The shaft 142 includes two V-shaped cam grooves 158 equally spaced from each other about the outer periphery of the shaft 142. Each of the cam grooves 158 includes a segment that is inclined relative to the central axis 46. The hammer 146 has opposed lugs 162 and two cam grooves 166 equally spaced from each other about an inner periphery of the hammer 146. Like the cam grooves 158 in the shaft 142, each of the cam grooves 166 is inclined relative to the central axis 46. The respective pairs of cam grooves 158, 166 in the shaft 142 and the hammer 146 are in facing relationship such that an engagement member (e.g., a ball 170) is received within each of the pairs of cam grooves 158, 166. The balls 170 and cam grooves 158, 166 effectively provide a cam arrangement between the shaft 142 and the hammer 146 for transferring torque between the shaft 142 and the hammer 146 between consecutive impacts of the lugs 162 upon corresponding lugs 174 on the anvil 150 (FIG. 3). The impact mechanism 138 also includes a compression spring 178 positioned between the hammer 146 and a retainer 182 of the rotating shaft 142 to bias the hammer 146 toward the anvil 150. U.S. Pat. No. 6,733,413, the entire contents of which is incorporated herein by reference, discloses an impact mechanism similar to the impact mechanism 138 disclosed in the present application.


With reference to FIGS. 2 and 3, the tool 10 also includes a clutch mechanism 186 operable to selectively divert torque output by the motor 38 away from the output shaft 22 and toward a portion of the impact mechanism 138 when a reaction torque on the output shaft 22 exceeds a predetermined torque setting of the clutch mechanism 186 (e.g., a reaction torque provided by a fastener and/or tool bit coupled to the drive end 14 of the tool 10). The clutch mechanism 186 includes a first plate 190 coupled for co-rotation with the output shaft 22, a second plate 194 coupled for co-rotation with the anvil 150, and a plurality of engagement members (e.g., balls 198) between the first and second plates 190, 194 through which torque and a rotational striking force are transferred from the anvil 150 to the output shaft 22 when the clutch mechanism 186 is engaged. In the illustrated construction of the tool 10, the first plate 190 is integrally formed as a single piece with the output shaft 22, and the second plate 194 is integrally formed as a single piece with the anvil 150. Alternatively, either of the first and second plates 190, 194 may be formed separately from the output shaft 22 and the anvil 150, respectively, and secured to the output shaft 22 and anvil 150 in any of a number of different ways (e.g., using an interference or press-fit, fasteners, adhesives, by welding, etc.).


With reference to FIG. 2, the second plate 194 includes axially extending protrusions 202 spaced about the central axis 46. Grooves 206 are defined in an end face 210 of the second plate 194 by adjacent protrusions 202 in which the balls 198 are respectively received. The first plate 190 includes apertures 214 radially spaced from the central axis 46. As shown in FIG. 5, the balls 198 are at least partially positioned within the respective apertures 214 in the first plate 190 and are at least partially received within the respective grooves 206 in the end face 210 of the second plate 194.


With reference to FIGS. 2 and 3, the clutch mechanism 186 also includes a thrust bearing assembly 218 and cylindrical pins 222 disposed within corresponding apertures 226 in the front portion 78 of the housing 34 radially spaced about the central axis 46. The pins 222 are engaged with the respective balls 198 via the thrust bearing assembly 218 such that the pins 222, the thrust bearing assembly 218, and balls 198 move together in a direction parallel to the central axis 46 relative to the respective apertures 214, 226 in the first plate 190 and the front housing portion 78 during operation of the tool 10 when the clutch mechanism 186 is enabled.


With reference to FIGS. 2 and 3, the clutch mechanism 186 also includes a washer 230 supported on a nose 234 of the front housing portion 78 coaxial with the central axis 46. The washer 230 is positioned adjacent an axially-facing, exterior face 238 of the front housing portion 78, such that the cylindrical pins 222 disposed within the apertures 226 in the front housing portion 78 are engaged with the washer 230. The clutch mechanism 186 further includes a resilient member (e.g., a compression spring 242) positioned over the nose 234 of the front housing portion 78. The spring 242 is positioned between the washer 230 and a spring retainer 246, which is described in more detail below. The spring 242 is operable to bias the washer 230 toward the exterior face 238 of the front housing portion 78.


With continued reference to FIGS. 2 and 3, the tool 10 also includes a clutch mechanism adjustment assembly 250, of which the spring retainer 246 is also a component, including an adjustment ring or collar 254 threaded to the spring retainer 246. Particularly, the collar 254 includes a threaded inner periphery 258, and the spring retainer 246 includes a corresponding threaded outer periphery 262. Accordingly, relative rotation between the collar 254 and the spring retainer 246 also results in translation of the spring retainer 246 relative to the collar 254 to adjust the preload of the spring 242. The collar 254 is axially secured relative to the front housing portion 78 by a plate 266 which, in turn, is secured to an end of the front housing portion 78 by a plurality of fasteners 270. The plate 266, however, permits the collar 254 to rotate relative to the front housing portion 78. The clutch mechanism adjustment assembly 250 also includes a detent assembly 274 operable to hold the collar 254 in different rotational positions relative to the front housing portion 78 corresponding with different preload values of the spring 242. As is described in more detail below, the clutch mechanism adjustment assembly 250 is operable to set the particular torque at which the clutch mechanism 186 slips.


The tool 10 further includes a mode selection mechanism 278 including a sleeve 282 coupled to the nose 234 of the front housing portion 78. In the illustrated construction of the tool 10, the sleeve 282 is interference-fit to the nose 234. Alternatively, the sleeve 282 may be secured to the nose 234 in any of a number of different ways (e.g., using fasteners, adhesives, by welding, etc.). The sleeve 282 includes axially extending slots 286 in the outer peripheral surface of the sleeve 282 in which respective radially inwardly extending tabs 290 of the spring retainer 246 are received. Therefore, the spring retainer 246 is prevented from rotating relative to the front housing portion 78, yet permitted to translate relative to the front housing portion 78 in response to rotation of the collar 254. The sleeve 282 also includes opposed slots 294 in an end of the sleeve 282 in facing relationship with the washer 230, the purpose of which is discussed in detail below.


The mode selection mechanism 278 also includes a mode selection ring 298 coaxially mounted to the front housing portion 78 for rotation relative to the front housing portion 78. In the illustrated construction of the tool 10, the mode selection ring 298 is sandwiched between the collar 254 and a flange on the front housing portion 78 (FIG. 5). Alternatively, the mode selection ring 298 may be positioned remotely from the collar 254 on another location of the tool 10. With reference to FIG. 2, the mode selection ring 298 includes opposed slots 302 in which corresponding radially outwardly extending tabs 306 of the washer 230 are received. As such, the mode selection ring 298 and the washer 230 are co-rotatable relative to the front housing portion 78.


The washer 230 also includes opposed axially extending tabs 310 that are selectively received within the slots 294 in the sleeve 282. Particularly, the washer 230 is rotatable between a first position (FIG. 7) in which the tabs 310 are inhibited from being received within the respective slots 294, and a second position (FIG. 4) in which the tabs 310 are aligned with the respective slots 294 and receivable within the respective slots 294. Consequently, the clutch mechanism 186 is locked out or disabled when the washer 230 is rotated to the first position, and the clutch mechanism 186 is enabled when the washer 230 is rotated to the second position.


With reference to FIG. 1, the mode selection ring 298 includes icons 314, 318 that provide a visual indication to the user of the tool 10 when the washer 230 is in the first and second positions. Specifically, when aligned with a marking 322 on the front housing portion 78, the icon 314 communicates to the user of the tool 10 that the washer 230 is in the first position to lock out or disable the clutch mechanism 186. Likewise, when aligned with the marking 322 on the front housing portion 78, the icon 318 communicates to the user of the tool 10 that the washer 230 is in the second position to enable the clutch mechanism 186. The mode selection mechanism 278 also includes detents 326 that provide a tactile indicator that the mode selection ring 298 and washer 230 have been rotated between the first and second positions to disable or enable the clutch mechanism 186. In the illustrated construction of the tool 10, the icon 318 is configured as a fastener suggestive of a driver mode of the tool 10 in which the clutch mechanism 186 is enabled, while the icon 314 is configured as a drill bit suggestive of a drill mode of the tool 10 in which the clutch mechanism 186 is disabled. Alternatively, the icons 314, 318 may be configured in any of a number of different ways.


In operation of the tool 10 when the clutch mechanism 186 is enabled (FIGS. 4-6), the shaft 142 and hammer 146 initially co-rotate in response to activation of the motor 38. Upon the first impact between the respective lugs 162, 174 of the hammer 146 and anvil 150, the anvil 150 and the output shaft 22 are rotated at least an incremental amount provided the reaction torque on the output shaft 22 is less than the torque setting of the clutch mechanism 186. Then, the hammer 146 ceases rotation relative to the front housing portion 78; however, the shaft 142 continues to be rotated by the motor 38. Continued relative rotation between the hammer 146 and the shaft 142 causes the hammer 146 to displace axially away from the anvil 150 against the bias of the spring 178.


As the hammer 146 is axially displaced relative to the shaft 142, the hammer lugs 162 are also displaced relative to the anvil 150 until the hammer lugs 162 are clear of the anvil lugs 174. At this moment, the compressed spring 178 rebounds, thereby axially displacing the hammer 146 toward the anvil 150 and rotationally accelerating the hammer 146 relative to the shaft 142 as the balls 170 move within the pairs of cam grooves 158, 166 back toward their pre-impact position. The hammer 146 reaches a peak rotational speed, then the next impact occurs between the hammer 146 and the anvil 150. In this manner, the fastener and/or tool bit received in the drive end 14 is rotated relative to a workpiece in incremental amounts until the fastener is sufficiently tight or loosened relative to the workpiece.


In operation of the tool 10 when the clutch mechanism 186 is enabled and the reaction torque on the output shaft 22 is less than the torque setting of the clutch mechanism 186 (i.e., as determined by the rotational position of the collar 254 and the amount of preload on the spring 242), the clutch mechanism 186 is operable in a first mode in which torque from the motor 38 is transferred through the transmission 42 and the impact mechanism 138, and to the output shaft 22 to continue driving the fastener and/or tool bit received in the drive end 14. Specifically, when the reaction torque on the output shaft 22 is less than the torque setting of the clutch mechanism 186, the spring 242 biases the washer 230, the cylindrical pins 222, the thrust bearing assembly 218, and the balls 198 toward the second plate 194, causing the balls 198 to remain in the grooves 206 in the end face 210 of the second plate 194 and jam against the protrusions 202 on the second plate 194 (FIG. 5). As a result, the second plate 194 and the anvil 150 are prevented from rotating relative to the first plate 190 and the output shaft 22.


However, when the reaction torque on the output shaft 22 reaches the torque setting of the clutch mechanism 186, the clutch mechanism 186 is operable in a second mode in which torque from the motor 38 is diverted from the output shaft 22 toward the second plate 194 and the anvil 150. Specifically, when the reaction torque on the output shaft 22 reaches the torque setting of the clutch mechanism 186, the frictional force exerted on the second plate 194 by the balls 198 jammed against the protrusions 202 is no longer sufficient to prevent the second plate 194 from rotating or slipping relative to the first plate 190, ceasing torque transfer to the output shaft 22. As the anvil 150 and the second plate 194 continue rotation relative to the first plate 190 and the output shaft 22, the balls 198 ride up and over the respective protrusions 202 on the second plate 194, causing the thrust bearing assembly 218, the cylindrical pins 222, and the washer 230 to be displaced axially away from the anvil 150 against the bias of the spring 242 (FIG. 6). The anvil 150 and the second plate 194 will continue to slip or rotate relative to the first plate 190 and the output shaft 22, causing the balls 198 to ride up and over the protrusions 202, so long as the reaction torque on the output shaft 22 exceeds the torque setting of the clutch mechanism 186.


Should the user of the tool 10 decide to adjust the tool 10 to a higher torque setting, the user would grasp the collar 254 and rotate the collar 254 toward a higher torque setting, causing the spring retainer 246 to be displaced along the sleeve 282 toward the washer 230 to increase the preload of the spring 242. The detent assembly 274 would provide tactile feedback to the user of the tool 10 as the collar 254 is rotated between adjacent torque settings.


Should the user of the tool 10 decide to adjust the tool 10 to disable the clutch mechanism 186 to operate the tool 10 in a drill mode, the user would grasp the mode selection ring 298 and rotate the ring 298 from the clutch enable setting toward the drill mode setting as indicated by the drill mode icon 314 (FIG. 7). Because the mode selection ring 298 and washer 230 are coupled for co-rotation as described above, rotation of the mode selection ring 298 toward the drill mode setting also causes the washer 230 to rotate relative to the sleeve 282 which, in turn, misaligns the tabs 310 and the slots 302 on the washer 230 and sleeve 282, respectively. Accordingly, prior to the balls 198 riding up and over the protrusions 202 on the second plate 194 as the reaction torque on the output shaft 22 approaches the torque setting of the clutch mechanism 186, the washer 230 engages the end of the sleeve 282, thereby preventing the washer 230 from being displaced farther from the second plate 194 and anvil 150 (FIG. 8). The balls 198, therefore, remain jammed against the protrusions 202 on the second plate 194 such that rotation or slipping of the second plate 194 relative to the first plate 190 is inhibited. When the clutch mechanism 186 is disabled, the full torque of the motor 38 may be transferred to the output shaft 22.


Various features of the invention are set forth in the following claims.

Claims
  • 1. An impact tool comprising: a housing;a motor supported in the housing;an output shaft rotatably supported in the housing about a central axis;an impact mechanism coupled between the motor and the output shaft and operable to impart a striking rotational force to the output shaft; anda clutch mechanism coupled between the impact mechanism and the output shaft;wherein the clutch mechanism is operable in a first mode, in which torque from the motor is transferred to the output shaft through the impact mechanism, and a second mode, in which torque from the motor is diverted from the output shaft toward a portion of the impact mechanism at a predetermined torque setting of the clutch mechanism.
  • 2. The impact tool of claim 1, wherein the impact mechanism includes an anvil rotatably supported in the housing, anda hammer coupled to the motor to receive torque from the motor and impart the striking rotational force to the anvil.
  • 3. The impact tool of claim 2, wherein the clutch mechanism includes a first plate coupled for co-rotation with the output shaft,a second plate coupled for co-rotation with the anvil, anda plurality of engagement members between the first and second plates through which torque and the striking rotational force are transferred when the clutch mechanism is operable in the first mode.
  • 4. The impact tool of claim 3, wherein the second plate includes a plurality of axially extending protrusions spaced about the central axis, and wherein the engagement members are wedged against the protrusions when the clutch mechanism is operable in the first mode.
  • 5. The impact tool of claim 4, wherein the engagement members are configured to ride over the protrusions in response to rotation of the second plate and the anvil relative to the first plate when the clutch mechanism is operable in the second mode.
  • 6. The impact tool of claim 3, wherein the first plate includes a plurality of apertures, and wherein the engagement members are at least partially positioned within the respective apertures.
  • 7. The impact tool of claim 3, wherein the clutch mechanism further includes a spring configured to impart a biasing force on the engagement members, anda washer positioned between the engagement members and the spring.
  • 8. The impact tool of claim 7, wherein the clutch mechanism further includes a thrust bearing assembly positioned between the engagement members and the washer, and wherein the thrust bearing assembly is operable to permit relative rotation between the first plate and the washer.
  • 9. The impact tool of claim 8, wherein the housing includes a plurality of apertures, wherein the clutch mechanism includes a corresponding plurality of cylindrical pins received within the apertures, and wherein the pins are positioned between the thrust bearing assembly and the washer.
  • 10. The impact tool of claim 7, further comprising a clutch mechanism adjustment assembly including an adjustment ring rotatable in a first direction in which the spring is compressed to increase the biasing force imparted on the engagement members, and in a second direction in which the spring is permitted to expand to decrease the biasing force imparted on the engagement members.
  • 11. The impact tool of claim 7, further comprising a mode selection mechanism including a sleeve coupled to a nose portion of the housing and having a slot defined therein, wherein the washer is rotatable between a first position in which a tab on the washer is inhibited from being received within the slot, and a second position in which the tab is receivable within the slot.
  • 12. The impact tool of claim 11, wherein the mode selection mechanism includes a mode selection ring coupled for co-rotation with the washer.
  • 13. The impact tool of claim 11, wherein the clutch mechanism is operable only in the first mode when the washer is rotated to the first position, and wherein the clutch mechanism is operable in the first and second modes when the washer is rotated to the second position.
  • 14. The impact tool of claim 2, wherein the impact mechanism further includes a rotating shaft that receives torque from the motor, andan engagement member positioned between the hammer and the rotating shaft for transferring torque from the rotating shaft to the hammer.
  • 15. The impact tool of claim 14, wherein the rotating shaft includes a first cam groove in which the engagement member is at least partially positioned, wherein the hammer includes a second cam groove in which the engagement member is at least partially positioned, and wherein the engagement member imparts axial displacement to the hammer in response to relative rotation between the rotating shaft and the hammer.
  • 16. The impact tool of claim 14, further comprising a transmission positioned between the motor and the rotating shaft.
  • 17. The impact tool of claim 16, wherein the transmission includes at least one planetary stage having an output carrier, wherein the impact tool further includes a projection coupled for co-rotation with one of the rotating shaft and the output carrier, and an aperture disposed in the other of the rotating shaft and the output carrier in which the projection is received.
  • 18. The impact tool of claim 17, wherein the projection and the aperture have corresponding non-circular cross-sectional shapes to couple the output carrier and the rotating shaft for co-rotation.
  • 19. The impact tool of claim 1, wherein the output shaft includes a hexagonal receptacle in which a tool bit is removably received.
  • 20. The impact tool of claim 1, further comprising a battery electrically connected to the motor for powering the motor.
CROSS-REFERENCE TO RELATED APPLICATIONS

This application claims priority to U.S. Provisional Patent Application No. 61/410,116 filed on Nov. 4, 2010, the entire contents of which are incorporated herein by reference.

US Referenced Citations (411)
Number Name Date Kind
1341700 Alexander Jun 1920 A
1494891 Elfe May 1924 A
1536157 Slack May 1925 A
1750825 Thompson Mar 1930 A
1811666 Foster Jun 1931 A
1927383 Bardwell Sep 1933 A
1970179 Miller Aug 1934 A
2086261 Douglass Jul 1937 A
2128761 Thomas Aug 1938 A
2140223 Foster Dec 1938 A
2143173 Shaff Jan 1939 A
2160150 Jimerson et al. May 1939 A
2160622 Olson et al. May 1939 A
2196589 Jimerson Apr 1940 A
2212919 Hutchison, Jr. Aug 1940 A
2219865 Fitch Oct 1940 A
2219869 Hutchison, Jr. Oct 1940 A
2219883 Amtsberg Oct 1940 A
2261204 Amtsberg Nov 1941 A
2285638 Amtsberg Jun 1942 A
2285639 Amtsberg Jun 1942 A
2326317 Amtsberg Aug 1943 A
2326347 Forss Aug 1943 A
2341497 Amtsberg Feb 1944 A
2342783 Aron et al. Feb 1944 A
2343332 Shaff Mar 1944 A
2371982 Fitch Mar 1945 A
2373664 Emery Apr 1945 A
2373665 Emery Apr 1945 A
2396498 Fitch Mar 1946 A
2408228 Richards Sep 1946 A
2425427 Fitch Aug 1947 A
2425793 Fosnot Aug 1947 A
2440834 Sims, Jr. May 1948 A
2508997 Fitch May 1950 A
2514914 Van Sittert Jul 1950 A
2515329 Bogart Jul 1950 A
2520920 Fosnot Sep 1950 A
2530915 Stec Nov 1950 A
2533703 Wilhide et al. Dec 1950 A
2543979 Maurer Mar 1951 A
2563711 Fitch Aug 1951 A
2564224 Mitchell Aug 1951 A
2566661 Hamlin Sep 1951 A
2575523 Mitchell Nov 1951 A
2576851 Newman Nov 1951 A
2578279 Bardwell Dec 1951 A
2579278 Thomas Dec 1951 A
2580607 Schmid Jan 1952 A
2580631 Whitledge Jan 1952 A
2581033 Larson et al. Jan 1952 A
2583147 Kaplan Jan 1952 A
2585486 Mitchell Feb 1952 A
2586314 Emery Feb 1952 A
2591323 Webb Apr 1952 A
2600495 Fitch Jun 1952 A
2616322 Spreng Nov 1952 A
2636410 Murrill Apr 1953 A
2636583 Whitledge Apr 1953 A
2637426 Van Sittert May 1953 A
2662434 Burkhardt Dec 1953 A
2684738 Kaplan Jul 1954 A
2691434 Jimerson Oct 1954 A
2693867 Maurer Nov 1954 A
2704952 Mooter Mar 1955 A
2705896 Holmes Apr 1955 A
2707892 Holmes May 1955 A
2711111 Brame Jun 1955 A
2711661 Shaff Jun 1955 A
2711662 Shaff Jun 1955 A
2716475 Mitchell Aug 1955 A
2717672 Maurer Sep 1955 A
2718803 Jimerson Sep 1955 A
2720956 Coombes Oct 1955 A
2725961 Maurer Dec 1955 A
2727598 Mitchell et al. Dec 1955 A
2740508 Shaff Apr 1956 A
2743637 Redmon May 1956 A
2744431 Scime May 1956 A
2745528 Amtsberg May 1956 A
2753072 Mitchell Jul 1956 A
2753965 Kaman Jul 1956 A
2756622 Belle Jul 1956 A
2756853 Madsen Jul 1956 A
2764272 Reynolds Sep 1956 A
2768546 Amtsberg Oct 1956 A
2783863 Shaff Mar 1957 A
2784625 Maurer Mar 1957 A
2784818 Maurer Mar 1957 A
2801718 Kaman Aug 1957 A
2802556 Schmid Aug 1957 A
2808916 Johnson Oct 1957 A
2815834 Mall Dec 1957 A
2825436 Amtsberg Mar 1958 A
2836272 Kaman May 1958 A
2842994 Stine Jul 1958 A
2850128 Van Sittert Sep 1958 A
2881884 Amtsberg Apr 1959 A
2881885 Short Apr 1959 A
2886997 Madsen May 1959 A
2898791 Maurer Aug 1959 A
2900856 Maier Aug 1959 A
2903111 Young Sep 1959 A
2923191 Fulop Feb 1960 A
2940556 Conover, Jr. Jun 1960 A
2952177 Skillin Sep 1960 A
2969660 Dale et al. Jan 1961 A
2973068 Sturrock Feb 1961 A
2973071 Sturrock Feb 1961 A
2974553 Donowick Mar 1961 A
2978936 Orner Apr 1961 A
2980218 Young Apr 1961 A
3000244 Sturrock Sep 1961 A
3001428 Sindelar Sep 1961 A
3001429 Sindelar Sep 1961 A
3012420 Schaedler Dec 1961 A
3016774 Minobe Jan 1962 A
3016775 Calkins Jan 1962 A
3053360 Madsen Sep 1962 A
3088445 Gardner May 1963 A
3100558 Hornschuch Aug 1963 A
3102621 Van Sittert Sep 1963 A
3104743 Reynolds Sep 1963 A
3106274 Madsen Oct 1963 A
3108507 Quarve Oct 1963 A
3129796 Karden Apr 1964 A
3144108 Reynolds Aug 1964 A
3144109 Alajouanine Aug 1964 A
3150725 Hornschuch et al. Sep 1964 A
3157074 Durkee Nov 1964 A
3169585 Maurer Feb 1965 A
3174597 Schaedler et al. Mar 1965 A
3174599 Spyridakis et al. Mar 1965 A
3174606 Hornschuch et al. Mar 1965 A
3180185 Schmidt et al. Apr 1965 A
3180435 McHenry Apr 1965 A
3181672 Swanson May 1965 A
3195704 Linsker Jul 1965 A
3199644 Clapp Aug 1965 A
3203283 Newman Aug 1965 A
3207237 Wanner Sep 1965 A
3208569 Adee Sep 1965 A
3212590 Hoza et al. Oct 1965 A
3220525 Pauley Nov 1965 A
3228486 Kaman et al. Jan 1966 A
3257877 Ulrich et al. Jun 1966 A
3269466 Mitchell Aug 1966 A
3270593 Kaman Sep 1966 A
3276524 Falter Oct 1966 A
3294183 Riley, Jr. et al. Dec 1966 A
3318390 Hoza et al. May 1967 A
3362486 Alajouanine Jan 1968 A
3369615 Maffey, Jr. et al. Feb 1968 A
3380539 Kaman Apr 1968 A
3387669 Wise, Jr. et al. Jun 1968 A
3389756 Kawamoto Jun 1968 A
3407885 Hoza et al. Oct 1968 A
3413876 Shinn Dec 1968 A
3414065 Falter Dec 1968 A
3414066 Wallace Dec 1968 A
3428137 Schaedler et al. Feb 1969 A
3438451 Hayes, Jr. Apr 1969 A
3450214 Bangerter et al. Jun 1969 A
3477521 Kiester et al. Nov 1969 A
3526282 Newman Sep 1970 A
3552499 Maurer Jan 1971 A
3557884 Allen Jan 1971 A
3561543 Ulbing Feb 1971 A
3572447 Pauley Mar 1971 A
3578091 States May 1971 A
3581831 Biek Jun 1971 A
3592087 Pauley Jul 1971 A
3592274 Young Jul 1971 A
3605914 Kramer Sep 1971 A
3606931 Karden Sep 1971 A
3606932 Schoeps Sep 1971 A
3608131 Hornschuch et al. Sep 1971 A
3610344 Schoeps et al. Oct 1971 A
3643749 Pauley Feb 1972 A
3648784 Schoeps Mar 1972 A
3661040 Lesner May 1972 A
3661217 Maurer May 1972 A
3696693 Bosten et al. Oct 1972 A
3703933 Schoeps Nov 1972 A
3710873 Allen Jan 1973 A
3734205 Maurer May 1973 A
3734515 Dudek May 1973 A
3739659 Workman, Jr. Jun 1973 A
3741313 States Jun 1973 A
3744350 Raff Jul 1973 A
3752278 States Aug 1973 A
3759119 Wing Sep 1973 A
3759334 Theurer Sep 1973 A
3774479 Lesner Nov 1973 A
3780603 Whitaker Dec 1973 A
3789934 Schoeps et al. Feb 1974 A
3792737 Bratt Feb 1974 A
3799307 Tate Mar 1974 A
3804180 Gelfand et al. Apr 1974 A
3805645 Jenny Apr 1974 A
3808904 Gotsch et al. May 1974 A
3828863 Bleicher et al. Aug 1974 A
3830316 Volovich et al. Aug 1974 A
3832916 Schoeps Sep 1974 A
3835934 Schoeps et al. Sep 1974 A
3847229 Wanner et al. Nov 1974 A
3868872 Wing Mar 1975 A
3874460 Schmid et al. Apr 1975 A
3886822 Pauley Jun 1975 A
3908766 Hess Sep 1975 A
3908768 Hess Sep 1975 A
3918325 Frost Nov 1975 A
3939924 Grabovac Feb 1976 A
3948328 Hiraoka et al. Apr 1976 A
3952814 Gelfand et al. Apr 1976 A
3955662 Thackston May 1976 A
3960035 Workman, Jr. et al. Jun 1976 A
3970151 Workman, Jr. Jul 1976 A
3974884 Gidlund Aug 1976 A
3990407 Parker et al. Nov 1976 A
4019023 Marzonie et al. Apr 1977 A
4055080 Farr et al. Oct 1977 A
4064948 Bratt et al. Dec 1977 A
4121670 Antipov et al. Oct 1978 A
4147219 Wallace Apr 1979 A
4171651 Dacunto Oct 1979 A
4183265 Pauley Jan 1980 A
4185701 Boys Jan 1980 A
4191264 Antipov et al. Mar 1980 A
4215594 Workman, Jr. et al. Aug 1980 A
4232750 Antipov et al. Nov 1980 A
4243108 Galimov et al. Jan 1981 A
4265320 Tanaka et al. May 1981 A
4265347 Dischler May 1981 A
4287956 Maurer Sep 1981 A
4313505 Silvern Feb 1982 A
4316512 Kibblewhite et al. Feb 1982 A
4321973 Maurer Mar 1982 A
4347902 Wallace et al. Sep 1982 A
4350213 Antipov et al. Sep 1982 A
4358735 Boys Nov 1982 A
4379492 Hiraoka Apr 1983 A
4384622 Koziniak May 1983 A
4418765 Mori et al. Dec 1983 A
4448564 Orszulak May 1984 A
4460049 Shibata Jul 1984 A
4462281 Zils Jul 1984 A
4502549 Hornung et al. Mar 1985 A
4505170 Van Laere Mar 1985 A
4535850 Alexander Aug 1985 A
4544039 Crane Oct 1985 A
4557337 Shibata Dec 1985 A
4609089 Kobayashi et al. Sep 1986 A
4619162 Van Laere Oct 1986 A
4712625 Kress Dec 1987 A
4811797 Antipov et al. Mar 1989 A
4834192 Hansson May 1989 A
4838364 Hansson Jun 1989 A
4869131 Ohmori Sep 1989 A
4881435 Hansson Nov 1989 A
4892013 Satoh Jan 1990 A
4905423 van Laere Mar 1990 A
4919022 Ono et al. Apr 1990 A
4923047 Fink et al. May 1990 A
4966057 Koppatsch Oct 1990 A
4979408 Hayashi Dec 1990 A
4991472 Hollingsworth Feb 1991 A
5011341 DeGroff Apr 1991 A
5019023 Kurosawa May 1991 A
RE33711 Ono et al. Oct 1991 E
5083619 Giardino et al. Jan 1992 A
5095784 Garver Mar 1992 A
5111889 Neumaier May 1992 A
5123313 Andersson Jun 1992 A
5195406 Lindqvist Mar 1993 A
5199505 Izumisawa Apr 1993 A
5269733 Anthony, III Dec 1993 A
5277527 Yokota et al. Jan 1994 A
5315902 Ragland et al. May 1994 A
5328306 Rehm et al. Jul 1994 A
5339908 Yokota et al. Aug 1994 A
5346022 Krivec Sep 1994 A
5377769 Hasuo et al. Jan 1995 A
5535867 Coccaro et al. Jul 1996 A
5544554 Brightly Aug 1996 A
5544710 Groshans et al. Aug 1996 A
5558059 Yashinaga et al. Sep 1996 A
5573074 Thames et al. Nov 1996 A
5592396 Tambini et al. Jan 1997 A
5622230 Giardino et al. Apr 1997 A
RE35617 Krivec Sep 1997 E
5673758 Sasaki et al. Oct 1997 A
5689434 Tambini et al. Nov 1997 A
5699872 Miyakawa et al. Dec 1997 A
5706902 Eisenhardt Jan 1998 A
5738177 Schell et al. Apr 1998 A
5740892 Huang Apr 1998 A
5836403 Putney et al. Nov 1998 A
5881855 Putney et al. Mar 1999 A
5887666 Chen et al. Mar 1999 A
5901794 Schoeps et al. May 1999 A
5941360 Putney et al. Aug 1999 A
5974913 Von Rotz et al. Nov 1999 A
6003618 Wallace Dec 1999 A
6045303 Chung Apr 2000 A
6047779 Wallace Apr 2000 A
6062114 Rahm May 2000 A
6076438 Rahm Jun 2000 A
6102632 Potter et al. Aug 2000 A
6119794 Chen Sep 2000 A
6142243 Mayer Nov 2000 A
6158526 Ghode et al. Dec 2000 A
6178853 Huang Jan 2001 B1
6227308 Ghode et al. May 2001 B1
6247384 Kusu et al. Jun 2001 B1
6283226 Chen Sep 2001 B1
6296427 Potter et al. Oct 2001 B1
6305481 Yamazaki et al. Oct 2001 B1
6311786 Giardino et al. Nov 2001 B1
6318479 Giardino et al. Nov 2001 B1
6321853 Giardino et al. Nov 2001 B2
6354178 Pool et al. Mar 2002 B2
6431289 Potter et al. Aug 2002 B1
6446735 Chen Sep 2002 B1
6457535 Tanaka Oct 2002 B1
6461088 Potter et al. Oct 2002 B2
6491111 Livingston et al. Dec 2002 B1
6502648 Milbourne Jan 2003 B2
6523658 Furuta et al. Feb 2003 B2
6543313 Samudosky Apr 2003 B2
6546815 Yamada et al. Apr 2003 B2
6561284 Taga May 2003 B2
6609577 Beccu Aug 2003 B2
6662882 Hansson Dec 2003 B2
6672183 Johnson Jan 2004 B2
6676557 Milbourne et al. Jan 2004 B2
6708779 Tagai Mar 2004 B2
6719067 Taga Apr 2004 B2
6725943 Ginell Apr 2004 B2
6733413 Lagarde et al. May 2004 B2
6745883 Eto et al. Jun 2004 B2
6789631 Realme, Sr. et al. Sep 2004 B1
6814152 Ginell Nov 2004 B2
6843326 Tambini Jan 2005 B2
6857983 Milbourne et al. Feb 2005 B2
6860341 Spielmann et al. Mar 2005 B2
6883619 Huang Apr 2005 B1
6887176 Sasaki May 2005 B2
6889778 Colangelo, III et al. May 2005 B2
6918325 Chan Jul 2005 B2
6945337 Kawai et al. Sep 2005 B2
6983810 Hara et al. Jan 2006 B2
6984188 Potter et al. Jan 2006 B2
7028784 Breitenmoser Apr 2006 B2
7066691 Doyle et al. Jun 2006 B2
7101300 Milbourne et al. Sep 2006 B2
7124839 Furuta et al. Oct 2006 B2
7198116 Chen Apr 2007 B1
7201235 Umemura et al. Apr 2007 B2
7210541 Miller May 2007 B2
7220211 Potter et al. May 2007 B2
7223195 Milbourne et al. May 2007 B2
7234536 Scholl et al. Jun 2007 B2
7308948 Furuta Dec 2007 B2
7314097 Jenner et al. Jan 2008 B2
7331404 Pusateri Feb 2008 B2
7334646 Hara et al. Feb 2008 B2
7360607 Aeberhard Apr 2008 B2
7380613 Furuta Jun 2008 B2
7395873 Nakamura et al. Jul 2008 B2
7404781 Milbourne et al. Jul 2008 B2
7410007 Chung et al. Aug 2008 B2
7410441 Milbourne et al. Aug 2008 B2
7419013 Sainomoto et al. Sep 2008 B2
7438140 Sterling et al. Oct 2008 B2
7452304 Hagan et al. Nov 2008 B2
7455121 Saito et al. Nov 2008 B2
7455123 Aeberhard Nov 2008 B2
7469753 Klemm et al. Dec 2008 B2
7562720 Seith et al. Jul 2009 B2
7607492 Seith et al. Oct 2009 B2
7673702 Johnson et al. Mar 2010 B2
8887831 Zhang Nov 2014 B2
20020005290 Giardino et al. Jan 2002 A1
20020035876 Donaldson, Jr. Mar 2002 A1
20020192043 Lin Dec 2002 A1
20040045729 Lehnert et al. Mar 2004 A1
20050028997 Hagan et al. Feb 2005 A1
20050263305 Shimizu et al. Dec 2005 A1
20050284265 Baker Dec 2005 A1
20060157262 Chen Jul 2006 A1
20060225903 Sterling et al. Oct 2006 A1
20060237205 Sia et al. Oct 2006 A1
20070022846 Fryatt Feb 2007 A1
20070158090 Sterling et al. Jul 2007 A1
20080083303 Baker Apr 2008 A1
20080230245 Matsunaga Sep 2008 A1
20080308286 Puzio Dec 2008 A1
20090014193 Barezzani et al. Jan 2009 A1
20090020301 Aeberhard Jan 2009 A1
20090102407 Klemm et al. Apr 2009 A1
20090173194 Chen Jul 2009 A1
20090250233 Wallace Oct 2009 A1
20100000749 Andel Jan 2010 A1
20100000750 Andel Jan 2010 A1
20100025063 Kuhnapfel et al. Feb 2010 A1
20100064864 Kobayashi Mar 2010 A1
20100071923 Rudolph et al. Mar 2010 A1
20100071924 Schoeps Mar 2010 A1
20100101815 Kobayashi Apr 2010 A1
20100276168 Murthy et al. Nov 2010 A1
Foreign Referenced Citations (2)
Number Date Country
2210708 Jul 2010 EP
6320435 Nov 1994 JP
Non-Patent Literature Citations (2)
Entry
International Search Report and Written Opinion for Application No. PCT/US2011/057840 dated Jun. 25, 2012 (7 pages).
European Patent Office Extended Search Report for Application No. 11838556.6 dated Mar. 31, 2015 (4 pages).
Related Publications (1)
Number Date Country
20120111592 A1 May 2012 US
Provisional Applications (1)
Number Date Country
61410116 Nov 2010 US