Power tool with shaft deflection limiter

Abstract: The present invention provides an apparatus for limiting deflection of the armature shaft 38, 38f, 103 of an electrically powered tool, such as a hand held saw 10 or drill 91. In saw 10, the armature shaft 38, 381 extends as a cantilever from the motor 14 and has a geared connection 58, 60 to an arbor 44 for driving the saw blade 18. An arrangement for limiting the deflection of the armature shaft 38, 38' comprises a pilot member 72, 84 and a socket 68, 82 associated, respectively, with one and the other of the armature shaft and a motor housing supported wall. The socket 68, 82 is larger in cross-section than that of the pilot member 72, 84 and limits transverse deflection of the armature shaft 38, 38' away from its axis of rotation A. If the saw 10 stalls in the material being cut, force is transmitted from the geared connection 58, 60 to the armature shaft 38, 38'. The socket 68, 82 and pilot member 72, 84 permit the armature shaft 38, 38' to deflect a predetermined amount to counteract torques resulting from the geared connection 58, 60. In one embodiment, the pilot 72 extends from the armature shaft 38 to be received in an aperture 68 formed in the housing wall 66. In another embodiment, the pilot 84 extends from the housing wall 66' to be received in a bore 82 formed in the armature shaft 38'. According to a third embodiment, in drill 91, the shaft deflection limiter is constituted by an armature shaft pilot 111 disposed in a roller bearing aperture 117.

Description: The present invention relates to a power tool, according to the preamble of claim 1. More particularly, the power tool according to the invention is provided with an apparatus for limiting shaft deflection in the gear train of such power tools. An electrically powered tool, such as a portable rotary hand held saw and the like, typically includes an electric motor for providing a source of power which is transmitted through a gear train to the saw blade or other implement for performing the intended work. As can be appreciated, there is a large amount of force exerted on the implement as it is worked through the material. This force, which is generated by the electric motor, is conducted through the gear train to the implement. Therefore, the gear train and the electric motor are necessarily designed to withstand the high stresses resulting from these forces. The loads, and therefore the stresses, experienced by the gear train and the motor vary with the cutting conditions. When the power tool is freewheeling, i.e., the tool is operating but the implement is not cutting through material, the loading of the gear train is fairly low. When the tool is cutting easily through a piece of material, the loading of the gear train is still of fairly low magnitude. However, if the tool bogs down or "stalls" in the material, i.e., the implement is no longer moving smoothly through or is stuck in the workpiece, the loading and stresses acting on the gear train increase. Although the implement may have "stalled" in the workpiece, the driving torque from the electric motor will continue and the force acting on the gear teeth may tend to force the gears apart and drive the armature shaft radially outwardly. If the armature shaft should deflect radially, the loading condition on the gear train will be further aggravated because the driving connection thereon will be via the tips of the gear teeth instead of against the faces of the gear teeth. Therefore, to ensure that the gear teeth do not fracture or otherwise fail under such loading conditions, and hence, to ensure a long reliable life for the power tool, the gears are made from hardened steel. Hardened steel gears, however, are typically more difficult to manufacture and are more expensive as compared to other types of gears such as powdered metal gears. In addition to providing for hardened steel gears, care must also be taken to provide enhanced support bearings for the various elements of the power tool gear train to ensure that they too are not damaged by the adverse loading conditions, and particularly, by shaft deflection. In U.S. Patent No. 3,973,449, it has been suggested that armature shaft deflection may be limited by supporting the distal end of the armature shaft in a bearing. However, this solution has been found to suffer from a number of disadvantages. The armature shaft is typically supported in a pair of bearings located, respectively, at each end of the armature winding. If a third bearing is added to support the distal end of the armature shaft, the armature shaft would then be supported in three bearings at spaced locations. Because of the tolerances inherent in the design of power tools, the accurate alignment of a single shaft in three spaced bearings is difficult. Misalignment will, of course, cause the development of friction and excessive heat in the bearings, leading to poor performance and potential failure of the device. Furthermore, the supporting of the distal shaft end in a bearing is difficult because the bearing is frequently located adjacent to an external housing wall typically made of plastic. The friction and heat generated in the bearing can lead to bearing failure and can lead to melting of the plastic housing in which the bearing is supported. Accordingly, it is, therefore, desirable to develop an improved durable mechanism for limiting shaft deflection with higher tolerances. In Japanese patent JP-49-60085, which corresponds to the preamble of claim 1, it has been suggested that armature shaft deflection may be limited by supporting the distal end of the armature shaft pinion in a bearing with some limited radial play so that said distal end is supported in said bearing when a load is applied, ie during normal use of the tool. This to some extent eases the problem of misalignment of the three spaced bearings for the armature shaft and pinion but will still generate undesirable heat and friction in the bearing. The power tool according to the present invention, comprises the combination of features of claim 1. In particular there is provided a power tool comprising a driving and a driven shaft with parallel axes of rotation. One end of each shaft is supported in a bearing. A support means positions the second end portion of the driven shaft in the housing. The second end portion of the driving shaft extends beyond its bearing. A geared driving connection is provided between the second end portions. A limit means, out of contact with the driving shaft during normal use of the power tool, limits the deflection of the extending portion of the driving shaft in a direction away from the second end driven shaft to counteract torque resulting from the driving connection between the shafts under severe loading conditions. According to certain embodiments, the support means may comprise a member connected to the housing and disposed in a plane transverse to the axes of rotation of the shafts. The limit means comprise (1) an axial pin (or pilot) extending from one of the driving shaft and member and (2) a bore located in the other of the driving shaft and the member. The pin is disposed from movement within the bore. In one embodiment, the axial pin extends from the driving shaft and the bore comprises an opening formed in the member. In a second embodiment, the axial pin extends from the member and the bore is formed in the second end portion of the driving shaft. In embodiments wherein the power tool is a circular saw, the driving shaft is preferably an armature shaft of a motor and the driven shaft is an arbor for driving the blade of the saw. In both embodiments, the pin is slightly smaller in diameter than that of the bore such that during normal operation of the power tool, there is a small clearance between the pin and the bore. When a severe loading condition exists, causing the armature shaft to deflect, the pilot portion will move towards, and in the worst case, into engagement with the wall of the bore. That is, deflection of the pin is limited to an amount equal to the small clearance between the pin and the bore. In this manner, the gears of the power tool are limited from separating, the gear teeth loads are distributed over the face of the gear teeth, not at the tips, and the gear teeth bending load is not adversely increased. In a third preferred embodiment according to the shaft deflection limiter comprises (1) a bearing supported in a power tool housing and (2) a pilot formed on the distal end of the armature shaft and disposed in the bearing aperture. The outer diameter of the pilot and the inner diameter of the bearing are chosen such that there is a small clearance formed in the bearing aperture between the pilot and the inner diameter of the bearing during normal operation of the power tool. This embodiment provides reduced friction and heat generation when the shaft is adversely loaded and the pilot engages the bearing. The invention will now be further described with reference to the accompanying drawings, in which: Figure 1 is a perspective view of a typical portable electric saw configured with an armature shaft deflection limiter according to a first preferred embodiment of the present invention; Figure 2 is a partial cross-sectional view of the electric saw shown in Figure 1 illustrating a gear train for transmitting torque from the armature shaft to a driven shaft; Figure 3 is an exploded perspective view, at least in part, of the gear train, the drive shaft and the armature shaft shown in Figure 2; Figure 4 is an end view taken along line 4-4 of Figure 2; Figure 5 is an end view taken along line 5-5 of Figure 2 illustrating the loading of the gear teeth under an adverse condition; Figure 6 is an enlarged view illustrating the loading of the gear teeth under normal operation and under an adverse condition; Figure 7 is a partial cross-sectional view of the electric saw shown in Figure 1 configured with an armature shaft deflection limiter according to a second preferred embodiment of the present invention; and Figure 8 is a fragmentary cross-sectional view of a hammer drill including a gear train with an armature shaft deflection limiter according to a third preferred embodiment of the present invention. The present invention is described in terms of preferred embodiments adapted to a portable hand held rotary electric saw (Figures 1-7) and to a hammer drill (Figure 8). It will, however, be readily apparent to one skilled in the art that its teachings will find broader applications than those described herein, and particularly, in the field of electrically powered tools. Turning now to the drawings, Figures 1 - 6 show a typical portable electric saw 10 configured with a deflection limiter according to the present invention. The portable saw 10 includes a motor housing 12 which forms an interior chamber, an electric motor 14 supported in the chamber, a gear case 16 secured to the housing in a suitable manner, and a circular saw blade 18 connected to the motor. The portable saw 10 further includes a substantially-flat shoe plate 20 for supporting the motor housing 12 on the surface of a workpiece, a control handle 22 provided with a trigger switch 24 for energising the unit, a front knob 26 for assisting in guiding the saw blade through the workpiece, an upper blade guard 28 and a lower guard 30 which pivots into the upper blade guard 28 upon engagement with the workpiece. A lever 32 is conventionally provided for manually pivoting and or adjusting the lower blade guard 30. The electric motor 14 is conventional and includes a field 34 and an armature 36. As can be seen in Figure 2, an armature shaft 38 extends in a cantilevered fashion from the armature 36 and has a first end portion supported for rotation in a roller bearing 40 and a free end portion 42 spaced from the bearing as is conventional for portable saws of this type. An arbor 44 has first and second end portions 46 and 48 with the first end portion 46 being supported for rotation in a bearing 50 mounted in the gear case 16 and the second end portion 48 being journalled for rotation in a sleeve bearing 52. The saw blade 18 is connected to the second end of the arbor 44 so as to be in a plane substantially perpendicular to the axis of rotation of the arbor and extend below the shoe plate 20 for engaging the workpiece. As shown, the connection of the saw blade 18 to the arbor 44 is by means of a bolt assembly 54. A gear train 56 is utilised to transmit driving torque from the motor 14 to the saw blade 18. In this regard, the gear train includes a pinion gear 58 fixedly connected to the armature shaft 38 for rotation therewith and a spur gear 60 fixedly connected to the arbor 44 for rotation therewith. The pinion gear 58 includes a plurality of radial gear teeth 62 each extending axially from the armature 36 for meshed engagement with respective gear teeth 64 formed about the circumference of the spur gear 60. According to a preferred embodiment of the present invention, a plate member 66 is mounted to the gear case 16. The plate member 66 has upper and lower openings 68 and 70 and the free end portion 42 of the armature shaft 38 is formed with a reduced diameter pilot portion 72. The pilot portion 72 is generally cylindrical and extends axially from the armature shaft 38 into the upper aperture 68 formed in the plate member 64. The aperture 68 is generally circular and slightly larger in diameter than the cross-section of the pilot portion 72 whereby to form a small clearance 69 therebetween. The sleeve member 52 is generally cylindrical and the outer periphery thereof is adapted to fit snugly in the lower aperture 70 formed in the plate member 64. In normal operation of the electric saw 10, there is no contact between the pilot portion 72 and the upper aperture 68. As will be appreciated, the upper aperture 68 will inhibit the free end portion 42 of the armature shaft 38 from undergoing extreme deflection in a direction transverse to its axis of rotation "A" by its engagement with the pilot portion 72. Importantly, the apertures 66 and 68 in the plate member 64 cooperate to maintain the respective axes of rotation "A" and "B" of the armature shaft 38 and the arbor 44 generally parallel to one another. As is known, the highest stresses in gear teeth occur at the point of contact between the mating gear and in the fillet at the base of the gear tooth due to the bending moment created by the contact force. With reference to Figure 6, a force from pinion gear tooth 62 against a spur gear tooth 64 is indicated by the arrow Fn and directed against the faces of the gear teeth. In the event that the saw blade 18 stalls in the material, the torque delivered by the electric motor 14 will continue to act on the gear teeth 62 and 64 and tend to drive the pinion gear 58 and the spur gear 60 apart due to a component of the force opposing the engagement of the gears. The pinion gear 58 will tend to move away from meshed engagement with the spur gear 60 due to deflection of the armature shaft 38. As a result, the armature shaft 38 will tend to deflect away from the arbor 44. This situation causes a severe loading condition between the gear teeth 62 and 64. Figure 5 illustrates the situation where the axis of rotation "A" of the armature shaft 38 moves from its original position to a new point "A"'. Under this condition, the gear teeth 60 and 62 take on the relationship shown in phantom in Figure 6 wherein the contact force between gear 62 and 64 is now applied to the tip of the gear tooth, as indicated by the arrow Fs. Hence, the stresses in the fillets 74 and 76 of the gear teeth 62 and 64, respectively, due to the bending moment, are increased due to the greater moment arm that force Fs acts on. In addition, the contact stress is now concentrated at the tips 78 and 80 of the gear teeth 62 and 64, as opposed to being distributed over the face of the gear tooth as in normal loading conditions. Loading the tips 78 and 80 of the gear teeth 62 and 64 promotes cracking and chipping of the gear teeth while the increased moment causes increased stress at the base of the gear tooth potentially leading to fatigue fracture. In short, repeated loading of the gear train in this fashion will ultimately lead to the failure of the gears requiring service for the power tool. Limiting deflection of the armature shaft 38 to the clearance 69 between the pilot portion 72 and the upper aperture 68 substantially maintains the pinion gear 58 in normal contact with the spur gear 60 and operates to obviate the severe loading condition described. With reference to Figure 7, a second embodiment of the present invention is shown. Primed reference numerals are used to identify elements which are modified from the preceding embodiment. As can be seen in Figure 7, an armature shaft 38' is formed with a blind axial bore 82 and a plate member 66' is formed with a generally cylindrical boss 84. The plate member 66' is suitably secured to the gear case 16 such that the boss 84 extends into the axial bore 82. The cross-section of the bore 82 is dimensioned to be slightly greater than the cross-section of the boss 84 such that a small gap 69' is defined therebetween. In normal operation, the boss 84 does not contact the wall of the bore 82. However, under loading conditions causing deflection of the armature shaft 381,1 the bore 82 engages the boss 84 for preventing deflection of the armature shaft 381 and maintaining substantially normal contact between the pinion gear 58 and the spur gear 60. While the boss 84 is shown integrally formed with the plate member 641 and generally cylindrical in cross-section, the securement and cross-section could be otherwise. For example, the boss could be separately fastened to the plate member 661. In such manner, the amount of armature shaft deflection could be varied, depending on the model. As will be appreciated from the foregoing discussion of the present invention, the pinion gear 58 and the spur gear 60 will no longer be subjected to adverse loading conditions. Therefore, there is no longer a need to specify hardened steel gears, which are typically more difficult and expensive to manufacture, to ensure reliable performance of the power tool. Also, the reliability of the bearings supporting the armature shaft is increased due to elimination of adverse loading due to armature shaft deflection. In Figure 8, a fragmentary axial cross-sectional view of a hammer drill 91 incorporating a gear train 93 with a third embodiment of a shaft deflection limiter 95 is shown. The gear train 93 comprises a pinion 97 and a spur gear 99. For simplicity, pinion 97 and spur gear 99 are illustrated as spur gears. However, helical gears are preferably used. Spur gear 99 is rotatably fixed to an output shaft 100 of hammer drill 91. Pinion 97 is integrally formed on an armature shaft 103 for a drive motor 105. Shaft 103 has a distal end 107 extending as a cantilever from bearing 109 and thus is subject to deflection under adverse loading conditions as explained in the first and second embodiments. To prevent excessive shaft deflection, a shaft deflection limiter 95 is formed by a pilot 111 formed on distal end 107 and a roller bearing 113 for receiving pilot 111. Bearing 113 is supported in pockets 110 (only one shown) formed in each half 114, 116 of clam shell housing 112. Pilot 111 and bearing 113 are sized such that there is a small clearance 115 formed in bearing aperture 117 between the inner diameter of bearing 113 and the outer diameter of pilot 111. As an example, in one embodiment, pilot 111 is 4.5mm in diameter, bearing aperture 117 is 5mm in diameter and clearance 115 is .25mm (radially). Clearance 115 should be dimensioned to be a minimum to permit pilot 111 to rotate freely under normal operating conditions and to engage bearing 113 only under adverse loading conditions to maintain the axis of rotation 119 of shaft 103 substantially parallel to the axis of rotation 121 of gear 99. In accordance with the present invention as explained in the embodiments described herein, the shaft deflection limiter may comprises piloting the armature shaft 38, 38', 103 in an apertured plate 66, on a cylindrical boss 84, or in a roller bearing 113, respectively. The limiter may also be constituted by a sleeve bearing or washer substituted for bearing 113.

Claims: A power tool (10, 91) comprising: a housing (12, 16, 112) having an interior chamber; a driving shaft (38, 38', 103) and a driven shaft (44, 100) each having an axis of rotation (A, B), the axes of rotation of said shafts (38, 38', 103, 44, 100) being generally parallel to one another, and each said shaft having a first end portion (38, 38', 103, 46, 100) supported in a respective stationary bearing (40, 109, 50) in said chamber and a second end portion (42, 107, 48); support means (66, 66') for positioning the second end portion (48) of said driven shaft (44, 100) relative to said housing (12, 16, 112), the second end portion (42, 107) of said driving shaft (38, 38', 103) extending beyond its bearing (40, 109), and a geared driving connection (58, 60, 97, 99) between said second end portions (42, 107, 48), characterised in that : limit means (68, 84, 113), out of contact with the driving shaft (38, 38', 103) during normal use of the power tool, is provided for limiting the deflection of the extending second end portion (42, 107) of the driving shaft (38, 38', 103) in a direction away from the second end portion (48) of said driven shaft (44, 100) to counteract torque resulting from the driving connection between the shafts (38, 38', 103, 44, 100) under severe loading conditions. A power tool according to claim 1 characterised in that said support means comprises a plate member (66, 66') connected to said housing (12, 16) and disposed in a plane transverse to the axes of rotation (A, B) of said shafts (38, 38', 103, 46, 100), said limit means comprises an axial pin (72, 84, 111) extending from one of said driving shaft (38, 103) and plate member (66') and a bore (68, 82, 117) being provided in the other of said driving shaft (38') and plate member (66), and the pin (72, 84, 111) is disposed for movement within said bore (68, 82, 117). A power tool according to claim 2 characterised in that said axial pin (72, 111) extends from said driving shaft (38, 103), and said bore (68) comprises an opening in the plate member (66). A power tool according to claim 2 characterised in that said axial pin (84) extends from said plate member (66') and said bore is formed in the second end portion of said driving shaft (38'). A power tool according to claim 4 characterised in that said axial pin (84) is integrally formed with said plate member (66'). A power tool according to any one of the preceding claims characterised in that the power tool is a circular saw (10); the driving shaft (38, 38') is an armature shaft of a motor (14); the driven shaft (44) is an arbor for driving a blade (18) of the saw (10). A power tool according to any one of claims 1 to 3 characterised in that the limit means is a bearing (113) supported in the housing (112).

Inventors: DIBBERN J E JR, LENTINO L E, STUMPF WILLIAM R, DIBBERN, J.E., JR., LENTINO, L.E., STUMPF, WILLIAM R.
Applicants: BLACK & DECKER INC, BLACK & DECKER INC.
Application year: 1995
Main classification: B23D47
IPC codes: B27B19, H02K7, B23D47, B25F5, B23D45