The present invention relates generally to hair cutting devices having a bladeset including a moving blade reciprocating relative to a stationary blade and a drive system for powering the bladeset, and more specifically to hair clippers or trimmers used for cutting hair of humans or animals.
Conventional hair cutting devices using a rotary drive system, such as hair trimmers and clippers typically include a drive member powered by the output shaft of the motor. For the purposes of this application, the terms “hair cutting device”, “hair clipper” and “hair trimmer” are considered interchangeable. The drive system converts rotary motion generated by the motor into linear motion in the form of the reciprocating moving blade relative to the stationary blade.
In most drive systems, a driving end of the drive member follows an arcuate or semi-arcuate path as it engages the moving blade of the bladeset. In this case, the term “semi-arcuate” refers to systems where at least part of the working stroke of the driving end follows an arcuate path. One such semi-arcuate conventional drive system employs a resilient parallelogram movement of the drive system. As such, the driving end moves in and out of engagement with the moving blade at least once during each revolution of the output shaft. In time, operational conditions, including heat and friction, combine to cause wear and deterioration of the driving end of the drive element. Such wear decreases operational efficiency of the clipper and often increases operational noise.
Another operational problem of conventional hair cutting devices is that hair clippings tend to accumulate in the area of the bladeset. The accumulation, which is more severe when the hair is wet, impedes the efficiency of the cutting device, since the unit does not move as quickly through the subject's hair. This condition also is more pronounced when clipping or shearing animal hair.
Still another operational problem of many conventional hair cutting devices is that the on/off switch is typically located on the top or side of the housing, where it is often accidentally actuated by the user during use. This may interfere with the cutting operation, especially when the operator is in the midst of styling, and prefers minimum interruption.
Thus, there is a need for a drive system for a hair cutting device which addresses the above-identified problems of conventional units.
The above-listed needs are met or exceeded by the present hair cutting device which overcomes the limitations of the current technology. Among other things, the present cutting device is designed for linear movement of the drive element, which maintains a constant engagement with the moving blade. In contrast to conventional arcuate or semi-arcuate drive systems, the present system provides “true” linear motion of the drive element throughout its stroke as generated by rotation of the motor output shaft. In this application, “true” linear motion refers to the fact that a drive tip of the drive element does not move in or out, or up or down relative to the engagement with the moving blade of the bladeset. Instead, a constant relationship is maintained between the drive element throughout the linear reciprocating stroke of the moving blade. As such, wear of the drive element is reduced and operational life is increased. Another feature of the present hair clipper is that the housing is provided with a configuration shaped for reducing the accumulation of hair clippings in the bladeset area. A spheroidal shape promotes the escape of clippings from this area, thus facilitating the movement of the clipper through a subject's hair. Still another feature of the present hair clipper is the provision of a motor actuator switch handle projecting from an underside of the housing, preferably from a recess in the underside, for promoting more positive operator control of the unit.
More specifically, the present hair clipper includes a motor with a rotary output shaft, a bladeset including a stationary blade and a moving blade configured for reciprocation relative to the stationary blade, a drive system configured for transferring motion from the output shaft to the bladeset, and including a driving member moving linearly along an axis transverse to a longitudinal axis of the clipper.
In another embodiment, a hair clipper includes a motor with a rotary output shaft, a bladeset including a stationary blade and a moving blade configured for reciprocation relative to the stationary blade, a drive system configured for transferring motion from the output shaft to the bladeset and a housing enclosing the motor and at least a portion of the drive system. The housing is provided with a spheroidal shape adjacent the bladeset for promoting flow of cut hair away from the bladeset.
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The bladeset 22 typically includes a biasing element 24 in the form of a spring which causes the moving blade 18 to be slidingly biased against the stationary blade 20 for more effective cutting action. In the present embodiment, the moving blade 18 defines a drive recess 26 (shown hidden) for receiving a blade engagement or driving tip 28 of a driving member 30. A feature of the present hair clipper is a drive system, generally designated 32, which moves the driving member 30 in a true linear fashion relative to the bladeset 22, so that the driving member moves linearly and reciprocally along an axis ‘T’ transverse to a longitudinal axis ‘L’ of the clipper 10 (
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In the driving member 30, the throughbore 50 is preferably located in a central shoulder portion 56. Projecting from the shoulder portion 56 is an elongate neck or gooseneck 58 having at its end 60 the preferably removable driving tip 28. The tip 28 has a radiused end 62 for reducing friction with the moving blade 18. A rear end 64 of the tip 28 defines a socket for receiving the end 60. Optional locking formations such as lugs 66 and openings or recesses 68 facilitate the attachment of the tip 28 upon the gooseneck end 60. The arched configuration of the gooseneck 58 provides an efficient angle of attack of the tip 28 into the moving blade 18.
Extending opposite from the gooseneck 58 is a cage 70 defined in part by the sidewalls 52 and also by upper and lower track members 72, 74. The sidewalls 52, the upper and lower track members 72, 74 and the shoulder portion 56 collectively define a drive chamber 76 within the cage 70. An upper opening 78 provides access to the cage 70 by a cam follower 80. Having spaced walls 82 separated by a back wall 84, the cam follower 80 defines the lateral throw or stroke of a bearing 86 rotatably engaged on a cam lug or pin 88 of an eccentric cam 90. The cam follower 80 also retains the bearing 86, preferably a ball bearing, high wear-resistant sleeve bushing or the like, within the cage 70. As is known in the art, the cam 90 is matingly engaged onto the output shaft 14 and rotates therewith. The cam follower 80, preferably made of high wear-resistant material, is also preferably held in place in the drive chamber 76 by a snap fit engagement achieved between a tab 92 on the shoulder portion 56 and a generally rectangular latch bracket 94. The specific configuration of the attachment of the cam follower 80 in the drive chamber 76 may vary to suit the application, and among other things, threaded fasteners are contemplated for alternative attachment devices.
To prevent relative pivoting of the driving member 30 and the chassis 34, a sleeve 96 is rotatably and coaxially engaged upon the eccentric cam 90. The sleeve 96, preferably made of high wear-resistant material, is held in position between the motor housing 16 and the cam lug 88 by a radially projecting annular ring 98 on the cam 90. Upon assembly of the drive system 32, the sleeve 96 rotates along the upper and lower track members 72, 74, thus supporting the cage 70, preventing pivoting action and maintaining the linear movement of the driving member 30 along the linear drive shaft 46.
In operation, as the motor output shaft 14 turns under power from the motor 12, the eccentric lug 88 and its affixed bearing 86 follow an eccentric path defined by the spaced walls 82 of the cam follower 80. This linear reciprocating movement pushes the bearing 86 against the cam follower 80, which causes the cage 70, and the driving member 30, to move laterally along the linear drive shaft 46. In this manner, true linear motion is provided, without an arcuate component.
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While a particular embodiment of the present rotary motor clipper with linear drive system has been described herein, it will be appreciated by those skilled in the art that changes and modifications may be made thereto without departing from the invention in its broader aspects and as set forth in the following claims.
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Number | Date | Country | |
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20060042093 A1 | Mar 2006 | US |