Reciprocating tool

Abstract

A reciprocating tool includes: a housing having a handle configured to be grasped by a user; a motor supported by the housing and defining a motor axis; a driving gear that is rotated about a motor axis by the motor; a driven gear defining an axis of rotation parallel to the motor axis, the driven gear meshing with the driving gear to rotate about the axis of rotation by the driving gear; a crankshaft coupled to the driven gear and rotatable with the driven gear; a counterweight having a first yoke coupled to the driven gear to convert rotation of the driven gear into reciprocating motion of the counterweight; and a main shaft having a second yoke coupled to the crankshaft to convert rotation of the driven gear into reciprocating motion of the main shaft, in which the counterweight and the main shaft reciprocate opposite each other.

Description

[0001] CROSS-REFERENCE TO RELATED APPLICATIONS

[0002] This application claims priority to co-pending U.S. Provisional Patent Application No. 63 / 593,603 filed on October 27, 2023 and co-pending U.S. Provisional Patent Application No. 63 / 487,669 filed on March 1, 2023, the entire contents of each of which are incorporated herein by reference. Technical Field

[0003] The present application relates to a power tool, and in particular to a reciprocating tool. Background Art

[0004] Reciprocating tools are used to cut a variety of objects made of a variety of materials such as metal pipes, wood, and drywall. Cordless, compact reciprocating tools allow cutting operations in tight spaces or at awkward angles for use in plumbing, electrical, remodeling, and HVAC applications. Utility Model Content

[0005] In one embodiment, a power tool includes: a housing having a handle configured to be grasped by a user; a motor supported by the housing and defining a motor axis; a driving gear that is rotated around the motor axis by the motor; and a driven gear that defines a rotation axis parallel to the motor axis. The driven gear meshes with the driving gear to rotate around the rotation axis through the driving gear. The crankshaft is coupled to the driven gear and can rotate with the driven gear. The counterweight has a first yoke that is coupled to the driven gear to convert the rotation of the driven gear into reciprocating motion of the counterweight. The spindle has a second yoke that is coupled to the crankshaft to convert the rotation of the driven gear into reciprocating motion of the spindle. The counterweight and the spindle reciprocate parallel to each other and in the opposite direction.

[0006] In some embodiments, the spindle defines a reciprocation axis along which the spindle reciprocates, and wherein the center of gravity of the counterweight is located along the reciprocation axis.

[0007] In some embodiments, the spindle defines a reciprocation axis along which the spindle reciprocates, and wherein the center of gravity of the counterweight is vertically offset from the reciprocation axis and positioned within the height of the spindle.

[0008] In another embodiment, a power tool includes: a housing having a handle configured to be grasped by a user; and a motor supported by the housing. A drive assembly includes: a driving gear that is rotated by the motor; a driven gear that meshes with the driving gear to rotate around a rotation axis through the driving gear; a crankshaft that is coupled to the driven gear and can rotate with the driven gear; and a spindle having a yoke that is coupled to the crankshaft to convert the rotation of the driven gear into reciprocating motion of the spindle. A gearbox is supported by the housing and is configured to support the motor and the drive assembly. The gearbox includes a first end, a second end opposite to the first end, and an elastic member positioned at the second end. A support assembly is coupled to the gearbox and can move axially relative to the gearbox. The support assembly is configured to abut the elastic member to absorb impacts due to axial vibrations during operation.

[0009] In another embodiment, a power tool includes: a housing having a handle configured to be grasped by a user; a motor supported by the housing and defining a motor axis; a driving gear that is rotated about the motor axis by the motor; and a driven gear that defines a rotation axis parallel to the motor axis. The driven gear meshes with the driving gear to rotate about the rotation axis through the driving gear. The crankshaft is coupled to the driven gear and can rotate with the driven gear. The counterweight has a first yoke that is coupled to the driven gear to convert the rotation of the driven gear into reciprocating motion of the counterweight, and the counterweight is disposed on a guide rail in the housing. The spindle has a second yoke that is coupled to the crankshaft to convert the rotation of the driven gear into reciprocating motion of the spindle. The counterweight can slide along the guide rail within the housing.

[0010] In another embodiment, the power tool includes: a housing having a handle configured to be grasped by a user; a motor supported by the housing and defining a motor axis; a driving gear, which is rotated around the motor axis by the motor; a driven gear, which defines a rotation axis parallel to the motor axis, and the driven gear is meshed with the driving gear to rotate around the rotation axis through the driving gear; a crankshaft, which is connected to the driven gear and can rotate together with the driven gear; a counterweight, which has a first yoke, which is connected to the driven gear to convert the rotation of the driven gear into reciprocating motion of the counterweight; and a spindle, which has a second yoke, which is connected to the crankshaft to convert the rotation of the driven gear into reciprocating motion of the spindle, wherein the counterweight and the spindle reciprocate in opposite directions to each other.

[0011] In another embodiment, a power tool includes: a housing having a handle configured to be grasped by a user; a motor supported by the housing; a driving gear that is rotated by the motor; a driven gear that defines a rotation axis, the driven gear meshing with the driving gear to rotate around the rotation axis through the driving gear; a crankshaft that is connected to the driven gear and can rotate together with the driven gear; a counterweight that has a first yoke that is connected to the driven gear to convert the rotation of the driven gear into reciprocating motion of the counterweight, the counterweight defining a center of gravity; and a spindle that has a second yoke that is connected to the crankshaft to convert the rotation of the driven gear into reciprocating motion of the spindle, wherein the counterweight and the spindle reciprocate in opposite directions to each other, and wherein the center of gravity of the counterweight is positioned within the height of the spindle.

[0012] In some embodiments, the spindle defines a reciprocation axis along which the spindle reciprocates, and wherein the center of gravity of the counterweight is located along the reciprocation axis.

[0013] In some embodiments, the spindle defines a reciprocation axis along which the spindle reciprocates, and wherein the center of gravity of the counterweight is vertically offset from the reciprocation axis.

[0014] In another embodiment, the power tool includes: a housing; a motor supported by the housing; a driving gear that is rotated by the motor; a driven gear that defines a rotation axis and includes an eccentric shaft, the driven gear meshing with the driving gear to rotate around the rotation axis through the driving gear; a bearing that is movably supported on the eccentric shaft; a crankshaft that is connected to the eccentric shaft and can rotate with the driven gear; a grease channel that is at least partially defined through the crankshaft; a counterweight that has a first yoke through which the eccentric shaft extends so that rotation of the driven gear causes reciprocating motion of the counterweight, the bearing being positioned between the eccentric shaft and the first yoke; and a spindle that has a second yoke that is connected to the crankshaft to convert rotation of the driven gear into reciprocating motion of the spindle, wherein the counterweight and the spindle reciprocate in opposite directions to each other, and wherein the reciprocating motion of the spindle causes grease to pass through the grease channel to lubricate the bearing.

[0015] In another embodiment, a power tool includes: a housing having a handle configured to be grasped by a user; a motor supported by the housing; a drive assembly including: a driving gear rotated by the motor, a driven gear meshed with the driving gear to rotate around a rotation axis through the driving gear, a crankshaft connected to the driven gear and rotatable together with the driven gear, and a main shaft having a yoke connected to the crankshaft to convert the rotation of the driven gear into reciprocating motion of the main shaft; a gear box supported by the housing and configured to support the motor and the drive assembly, the gear box including a first end, a second end opposite to the first end, and an elastic member positioned at the second end; and a support assembly connected to the gear box and axially movable relative to the gear box, the support assembly being configured to abut the elastic member to absorb impact due to axial vibration during operation.

[0016] In another embodiment, the power tool includes: a housing having a handle configured to be grasped by a user; a motor supported by the housing and defining a motor axis; a driving gear, which is rotated around the motor axis by the motor; a driven gear, which defines a rotation axis parallel to the motor axis, and the driven gear is meshed with the driving gear to rotate around the rotation axis through the driving gear; a crankshaft, which is connected to the driven gear and can rotate together with the driven gear; a counterweight, which has a first yoke, which is connected to the driven gear to convert the rotation of the driven gear into reciprocating motion of the counterweight, and the counterweight is arranged on a guide rail in the housing; and a spindle, which has a second yoke, which is connected to the crankshaft to convert the rotation of the driven gear into reciprocating motion of the spindle, wherein the counterweight can slide along the guide rail in the housing.

[0017] Other aspects of the invention will become apparent by consideration of the detailed description and accompanying drawings. BRIEF DESCRIPTION OF THE DRAWINGS

[0018] Figure 1A It is a three-dimensional diagram of a reciprocating saw according to an embodiment of the utility model.

[0019] Figure 1B yes Figure 1A A side view of a reciprocating saw is shown.

[0020] Figure 2 It is the edge of a reciprocating saw. Figure 1A A cross-sectional view taken along line 2--2.

[0021] Figure 3 yes Figure 1A A perspective view of the motor, gearbox, spindle assembly and support assembly of a reciprocating saw.

[0022] Figure 4 yes Figure 1AA side view of the motor, gearbox, spindle assembly and support assembly of a reciprocating saw.

[0023] Figure 5 yes Figure 1A A stereoscopic view of the motor, gearbox, elastic member and spindle assembly of a reciprocating saw.

[0024] Figure 6 yes Figure 1A Front view of the motor, gear box and elastic member of a reciprocating saw.

[0025] Figure 7 It is the part of the reciprocating saw. Figure 3 A cross-sectional view taken along line 7--7.

[0026] Figure 8 It is the part of the reciprocating saw. Figure 3 A cross-sectional view taken along line 8--8.

[0027] Fig. 9 It is the part of the reciprocating saw. Figure 3 A cross-sectional view taken along line 9--9.

[0028] Fig.10 yes Figure 1A A side view of the motor, transmission, counterweight and spindle assembly of a reciprocating saw.

[0029] Fig.11 yes Fig.10 Side view of the transmission.

[0030] Fig. 12A yes Fig.10 The edge of the transmission Fig.10 A cross-sectional view taken along line 12A--12A.

[0031] Fig. 12B yes Fig. 12A Schematic diagram of the bearings and part of the transmission device.

[0032] Fig.13 yes Fig.11 A three-dimensional diagram of the gears of a transmission.

[0033] Fig.14 yes Fig.11 Another perspective view of the gears of the transmission device.

[0034] Fig.15 yes Fig.11 A three-dimensional view of the crankshaft of the transmission.

[0035] Fig.16 yes Fig.11 Another perspective view of the crankshaft of the transmission.

[0036] Fig.17 yes Fig.10 A three-dimensional diagram of the counterweight.

[0037] Fig.18 yes Figure 3 A perspective view of the spindle assembly.

[0038] Fig.19 yes Figure 3 Along the spindle assembly Fig.18 A cross-sectional view taken along line 19--19.

[0039] Fig. 20 yes Fig.10 A side view of the main shaft and the counterweight when in a first position.

[0040] Fig.21 yes Fig.10 A top view of the main shaft and the counterweight when in a first position.

[0041] Fig. 22 yes Fig.10 A side view of the spindle and counterweight in a second position.

[0042] Fig.23 yes Fig.10 A top view of the spindle and counterweight when in the second position.

[0043] Fig.24 yes Figure 5 A three-dimensional view of the gearbox after removing the elastic member.

[0044] Fig.25 yes Figure 5 A three-dimensional view of the elastic member.

[0045] Fig.26 yes Figure 3 Detailed top view of the gearbox, elastic member, main shaft assembly and support assembly.

[0046] Fig. 27 Demonstrates the advantages over traditional reciprocating saws Figure 1A motors, gearboxes and transmissions.

[0047] Fig.28 A motor, gearbox and transmission according to another embodiment relative to a conventional reciprocating saw is shown.

[0048] Fig.29 A first gearbox portion according to an embodiment of the present invention is shown.

[0049] Fig. 30A A perspective view of a reciprocating saw according to another embodiment of the present invention is shown.

[0050] Fig. 30B Shown Fig. 30A A perspective view of a reciprocating saw with the housing removed.

[0051] Fig. 30C Shown Fig. 30A The reciprocating saw is removed along the Fig. 30B A cross-sectional view taken along line 30C--30C.

[0052] Fig.31 yes Fig. 30A A perspective view of the counterweight of a reciprocating saw.

[0053] Fig.32 It is the part of the reciprocating saw. Fig. 30A A cross-sectional view taken along line 32--32.

[0054] Fig.33 The other part of the reciprocating saw Fig. 30A A cross-sectional view taken along line 33--33.

[0055] Fig.34 yes Fig. 30A A side view of a portion of a transmission including an output gear, a first bearing, a crankshaft and a second bearing.

[0056] Fig.35 yes Fig. 30A A perspective view of the output gear.

[0057] Fig.36 yes Fig. 30A Bottom view of the output gear.

[0058] Fig.37 yes Fig.34 A three-dimensional diagram of this part of the transmission.

[0059] Fig.38 yes Fig.34 This part of the transmission along the Fig.37 A cross-sectional view taken along line 38--38.

[0060] Fig.39 yes Fig.34 A bottom view of this portion of the transmission as well as a portion of the spindle assembly and counterweight.

[0061] Fig.40 yes Fig.39 A perspective view of a portion of a spindle assembly.

[0062] Fig.41 The angular position of the spindle assembly and counterweight relative to the linear position during operation is shown.

[0063] Fig.42 The axial speed of the spindle assembly and counterweight during operation is shown.

[0064] Fig.43 The axial acceleration of the spindle assembly and counterweight during operation is shown. DETAILED DESCRIPTION

[0065] Before explaining any embodiment of the utility model in detail, it should be understood that the application of the utility model is not limited to the details of the structure and arrangement of the components set forth in the following description or shown in the following drawings. The utility model can have other embodiments and can be practiced or implemented in many different ways.

[0066] Figure 1A A portable power tool 10 (e.g., a portable reciprocating tool) is shown. In these embodiments, the power tool 10 is a reciprocating saw. In the illustrated embodiment, the saw 10 is powered by a power tool battery pack (not shown). The battery pack can be configured to connect and power a variety of tools in addition to the reciprocating saw 10. In other embodiments, the saw 10 can be a corded power tool. In yet other embodiments, the power tool can be another type of handheld power tool, such as another type of power tool that converts rotary motion into reciprocating motion.

[0067] Figure 1A The saw 10 includes a housing 40. Figure 1A As shown, the housing 40 has a first housing portion 44 and a second housing portion 48. Each housing portion 44, 48 is formed of plastic; however, in some embodiments, the housing portions 44, 48 may be formed of other materials. The housing 40 defines a handle 50, a motor housing portion 56, and a gearbox housing portion 60. The handle 50 includes at least one gripping surface configured to be gripped by a user. In the illustrated embodiment, the handle 50 may also define a battery receiving portion 64 for receiving a battery pack. In other embodiments, the battery receiving portion 64 may be defined elsewhere within the housing 40. The motor housing portion 56 is coupled to the end of the handle 50 opposite the battery receiving portion 64. The gearbox housing portion 60 is also coupled to the end of the handle 50 opposite the battery receiving portion 64. The gearbox housing portion 60 is adjacent to the motor housing portion 56 and is located below the motor housing portion (e.g., Figure 1B The motor housing portion 56 supports the motor 68, and the gearbox housing portion 60 in turn supports the gearbox 72 ( Figures 3 to 9 ).

[0068] Although not shown in detail, the battery receiving portion 64 is configured as a cavity. Figure 1A ) is connected to the saw 10, the battery pack is inserted into the cavity and substantially closes the cavity. Figure 1A to Figure 2As shown, an actuator 80 is positioned on the handle 50 for providing power to the saw 10. In particular, the actuator 80 is electrically coupled to the battery pack and the motor 68 to selectively energize the motor 68 when actuated. As shown, the actuator 80 is an on-off trigger. In other embodiments, the actuator 80 may be a variable speed trigger, a dual speed trigger, a button, or another suitable actuator.

[0069] See also Figure 3 and Figure 4 , the gearbox 72 generally supports the motor 68 and the drive assembly 76. The gearbox 72 includes a first gearbox portion 90 and a second gearbox portion 94 that are coupled to each other and surround the drive assembly 76 of the saw 10. As shown, the motor 68 is positioned above the gearbox 72 (e.g., the first gearbox portion 90) so that the output shaft 104 ( Figure 4 ) extends through the opening of the first gear case portion 90 into the gear case 72. Figure 5 and Figure 6 as well as Figure 24 to Figure 25 , the second gearbox portion 94 has an opening 106, a first recess 108, and a second recess 112. The opening 106 is located in a front wall 114 of the second gearbox portion 94. The opening 106 is configured to receive a portion of the spindle assembly 166, as will be discussed below. Fig.29 As shown, in other embodiments, the first gearbox portion 90 defines the opening 106. In this embodiment, only the first gearbox portion 90 receives and supports the main shaft assembly 166.

[0070] The first recess 108 receives the first elastic member 116, and the second recess 112 receives the second elastic member 120. As shown, the first and second recesses 108, 112 are positioned at the front corners of the second gear box portion 94. Accordingly, the first and second elastic members 116, 120 received in the respective first and second recesses 108, 112 each at least partially define the front corners of the second gear box portion 94. The first elongated protrusion 124 extends from a first side surface of the second gear box portion 94, and the second elongated protrusion 128 extends from an opposite second side surface of the second gear box portion 94. The first circular protrusion 132 extends from the first side surface of the second gear box portion 94, and a second circular protrusion (not shown, but the same as the first protrusion) extends from an opposite second side surface of the second gear box portion 94. As Fig. 9As shown, the second gearbox portion 94 further includes a protrusion 136 and a generally arcuate guide wall 140 extending from an inner bottom surface 144 thereof. Although the illustrated gearbox 72 is described as having certain protrusions in particular areas, in other embodiments, the gearbox 72 may include fewer or more protrusions, the protrusions may have other configurations (e.g., shapes), and / or the protrusions may be located elsewhere on the gearbox 72.

[0071] Fig.10 FIG. 12 shows a drive assembly 76 according to an embodiment of the present invention. The drive assembly 76 shown includes a driving gear 150, an output gear 154 (e.g., a driven gear), a counterweight 158, a crankshaft 162, and a main shaft assembly 166. In other embodiments, the drive assembly 76 may include fewer or more components. The driving gear 150 is coupled to the output shaft 104 of the motor 68 to rotate with the output shaft 104. The output shaft 104 is oriented along the motor axis 170. The driving gear 150 shown is a pinion gear that includes a plurality of teeth 174 and can rotate around the motor axis 170.

[0072] Further references Figures 11 to 14 , the output gear 154 includes a first side 200, a second side 204 opposite the first side 200, a rotation axis 208, a plurality of teeth 212, and an eccentric shaft 216. The rotation axis 208 extends generally centrally through the output gear 154. The rotation axis 208 of the output gear 154 is oriented parallel to the motor axis 170. The teeth 212 of the output gear 154 are positioned on an outer circumference thereof and are configured to mesh with the teeth 174 of the driving gear 150. The eccentric shaft 216 extends from the second side 204 of the output gear 154 and extends along an eccentric axis 220 parallel to the rotation axis 208. Figures 1A to 27 In some embodiments, the motor 68 is positioned forward of the output gear 154, as will be discussed below. Fig.28 In the embodiment of FIG. 1 , the motor 68 is positioned rearwardly of the output gear 154 , as will be discussed below.

[0073] like Fig.10 and Fig.17 As shown, the counterweight 158 ​​is configured as a first scotch yoke mechanism. As will be discussed in more detail below, the counterweight 158 ​​is configured to move along the first reciprocating axis 240 ( Figure 20 to Figure 22) reciprocating motion. The counterweight 158 ​​includes a body having a first end 250 (e.g., a front end), a second end 254 (e.g., a rear end) opposite the first end 250, a first side or top side 258, a second side or bottom side 262 opposite the first side 258, a third side 266, and a fourth side 270 opposite the third side 266. The second side 262 of the body is also defined with a recess 274. The first end 250 is defined with a first yoke including a first elongated aperture 278. In other embodiments, the counterweight 158 ​​may have other configurations. In the illustrated embodiment, the first elongated aperture 278 extends from the third side 266 to the fourth side 270. The first elongated aperture 278 defines a first elongated aperture axis 282. The first elongated aperture axis 282 is oriented perpendicular to the rotational axis 208 of the output gear 154. The eccentric shaft 216 extends through the first elongated aperture 278 and is movable within the first elongated aperture 278. The second elongated aperture 286 is positioned adjacent the third side 266, the third elongated aperture 290 is positioned adjacent the fourth side 270, and the elongated slot 294 is positioned between the second elongated aperture 286 and the third elongated aperture 290. The second elongated aperture 286, the third elongated aperture 290, and the elongated slot 294 all extend between the first end 250 and the second end 254. The second elongated aperture 286, the third elongated aperture 290, and the elongated slot 294 are oriented along respective axes 286', 290', 294', respectively, which are parallel to each other and perpendicular to the first elongated aperture axis 282. In the illustrated embodiment, as shown in FIG. Figure 20 to Figure 21 As shown, the counterweight defines a center of gravity 298 positioned between the first side 258 and the second side 262 and between the third side 266 and the fourth side 270. In the illustrated embodiment, the center of gravity 298 is positioned along the first reciprocating axis 240.

[0074] like Figure 2 , Figure 7 and Figure 8 As shown, in the illustrated embodiment, the first fastener 286" and the second fastener 290" clamp or otherwise stabilize the counterweight 158 ​​relative to the gearbox 72 (e.g., the first gearbox portion 90) while still allowing the counterweight to translate, as will be discussed in more detail below. The first fastener 286" is coupled to the first gearbox portion 90 and extends through the second elongated aperture 286, and the second fastener 290" is coupled to the first gearbox portion 90 and extends through the third elongated aperture 290. The guide pin 294" ( Figure 7 and Figure 8 ) extends from the first gearbox portion 90 toward the second gearbox portion 94 and is received in the elongated slot 294. The fasteners 286", 290" and the guide pin 294" restrict the left-right movement of the counterweight 158 ​​while allowing axial movement (e.g., reciprocating movement) of the counterweight 158.

[0075] like Fig. 12A , Fig.15 and Fig.16 As shown, the crankshaft 162 is coupled to the output gear 154. Thus, the crankshaft 162 can rotate with the output gear 154 about its rotation axis 208. In particular, the center of the crankshaft 162 is coaxial with the rotation axis 208 of the output gear 154. As shown, the crankshaft 162 includes a recess 300 located on the first side 304, which cooperatively receives at least a portion of the eccentric shaft 216 of the output gear 154. In the illustrated embodiment, the crankshaft 162 is coupled to the output gear 154 via a fastener 306 and a first pin 308, each of which extends at least partially through the eccentric shaft 216 from the second side 312 of the crankshaft 162. In other embodiments, the eccentric shaft 216 can be press-fit into the recess 300 of the crankshaft 162. In other embodiments, the output gear 154, the eccentric shaft 216, and the crankshaft 162 can be formed integrally with each other. Accordingly, the eccentric shaft 216 is coupled to the crankshaft 162 so that there is no relative rotation therebetween. The second pin 316 is coupled to the second side 312 of the crankshaft 162 and extends from the second side. The second pin 316 includes a first end coupled to the crankshaft 162 and a second end extending from the second side 312 of the crankshaft 162. The second pin 316 defines a pin axis 318 that is parallel to the rotation axis 208 and the eccentric axis 220. The fastener 306 and the first pin 308 are both positioned on the side of the rotation axis 208 opposite to the second pin 316. Moreover, the eccentric axis 220 of the eccentric shaft 216 is spaced 180 degrees from the pin axis 318. In the illustrated embodiment, the fastener 306, the first pin 308, and the second pin 316 are aligned with each other along an axis 319 that runs through the centers of each. Moreover, the fastener 306 and the first pin 308 are spaced 180 degrees from the second pin 316.

[0076] refer to Fig.11 and Fig. 12A , the first bearing 320 surrounds the eccentric shaft 216 and is positioned between the output gear 154 and the crankshaft 162. In some embodiments, the first bearing 320 is a rolling contact bearing (e.g., a roller bearing). As such, the first bearing 320 includes rollers (not shown) that rotate between an inner race and an outer race to allow the eccentric shaft 216 to rotate. In some embodiments, such as Fig. 12B, the first bearing 320 is a sliding bearing movably coupled to the eccentric shaft 216. In particular, the sliding bearing 320 is configured to rotate relative to the eccentric shaft 216. When the eccentric shaft 216 rotates with the output gear 154, the sliding bearing 320 can rotate relative to the eccentric shaft 216. Accordingly, the inner surface of the sliding bearing 320 performs a non-constant relative sliding motion relative to the outer surface of the eccentric shaft 216, and the outer surface of the sliding bearing 320 is configured to rotate (e.g., roll) relative to the surface of the elongated aperture 278 (e.g., yoke) of the counterweight 158 ​​during the reciprocating motion of the counterweight 158. In the illustrated embodiment, the sliding bearing 320 rotates one circle around the circumference of the eccentric shaft 216 during one rotation of the output gear 154. To complete one rotation, the sliding bearing 320 can rotate relative to the eccentric shaft 216 in a first direction and relative to the eccentric shaft 216 in a second direction in response to various point contacts with the surface of the elongated aperture 278. The first bearing 320 is different from a bearing that cannot move relative to the eccentric shaft 216 and is only configured to slide against the surface of the elongated aperture 278 of the counterweight 158. The benefit of the first bearing 320 is that it reduces system friction and helps reduce component wear to achieve smooth operation of the tool during its service life. The second bearing 324 surrounds the second end of the second pin 316. The second bearing 324 can have any suitable configuration, including a rolling contact bearing or a plain bearing. The retaining surface 326 engages the second end of the second pin 316 so that the retaining surface 326 prevents the second bearing 324 from being disconnected from the second pin 316 (such as Fig. 20 In the illustrated embodiment, the crankshaft 162 may include one or more apertures extending between the first side 304 and the second side 312 , which reduces the overall weight of the crankshaft 162 .

[0077] refer to Figure 18 to Figure 19, the spindle assembly 166 shown is configured as a second yoke mechanism. That is, the spindle assembly 166 includes a second yoke 350, a yoke shaft 354, a spindle shaft 358, a spindle bushing 362, and a blade clamp 366. The blade clamp 366 is opposite to the second yoke 350. In other embodiments, the spindle assembly 166 may include fewer or more components. In the illustrated embodiment, the second yoke 350 and the yoke shaft 354 are separated and coupled with the spindle shaft 358. As shown, the yoke shaft 354 is coupled to the spindle shaft 358. In other embodiments, the second yoke 350 and / or the yoke shaft 354 can be formed as a single piece with the spindle shaft 358. The spindle bushing 362 surrounds at least a portion of the yoke shaft 354 and the spindle shaft 358. The spindle assembly 166 defines a first plane P1 (e.g., an XY plane) and a second plane P2 (e.g., an XZ plane). The spindle assembly 166 defines a second reciprocating motion axis 370 of the saw 10. In the illustrated embodiment, the second reciprocating axis 370 is centrally disposed through the spindle shaft 358. That is, the second reciprocating axis 370 is located at the intersection between the first plane P1 and the second plane P2. Further, in the illustrated embodiment, the second reciprocating axis 370 is located at a height H ( Fig. 20 ) and width W( Fig.21 ) at the center point of the first plane P1 and the second plane P2. In other embodiments, the second reciprocating axis 370 can be offset from one or both of the first plane P1 and the second plane P2, and therefore can be offset from the center point along the height H or the width W. In addition, the center of gravity 372 of the spindle assembly 166 is positioned along the second reciprocating axis 370. Although not shown in detail, a tool element such as a saw blade is connected to the spindle shaft 184 via a blade clamp 366. The blade clamp 366 may include a blade clamp assembly shown and described in U.S. Patent No. 6,725,548, entitled "Keyless Blade Clamp Mechanism," issued on April 27, 2004, the contents of which are incorporated herein by reference. The blade clamp 366 can also be configured to accept a variety of different reciprocating saw blades, jig saw blades, and / or bow saw blades. During operation, the tool element reciprocates along the second reciprocating axis 370. Reference Fig.19 The second yoke 350 has an elongated aperture 374 extending therethrough. The elongated aperture 374 defines an elongated aperture axis 378 . The elongated aperture axis 378 is perpendicular to the second reciprocating motion axis 370 .

[0078] like Fig.10 and Figure 20 to Figure 23As shown, when assembled, the counterweight 158 ​​is at least partially positioned between the output gear 154 and the crankshaft 162. The counterweight 158 ​​is also at least partially positioned between the output gear 154 and the gearbox 72. In the illustrated embodiment, the first elongated aperture 278 is positioned between the output gear 154 and the crankshaft 162 such that the eccentric shaft 216 extends through the first elongated aperture 278. The crankshaft 162 is positioned within the recess 274 of the counterweight 158. Moreover, the main shaft assembly 166 is positioned within the recess 274 of the counterweight 158 ​​and is movable therein. Figure 2 and Fig. 9 As shown, the second side 262 of the counterweight 158 ​​is positioned adjacent to the bottom inner surface of the second gear case portion 94. In addition, the third and fourth sides 266, 270 are positioned on opposite sides of the arcuate guide wall 140.

[0079] like Fig.10 , Fig. 20 and Fig. 22 As shown, the spindle assembly 166 generally extends through the counterweight 158. That is, the spindle assembly 166 is generally positioned between the first side 258 and the second side 262 of the counterweight 158 ​​and between the third side 266 and the fourth side 270 of the counterweight 158. Accordingly, a portion of the counterweight 158 ​​is located above the spindle assembly 166, and a portion of the counterweight 158 ​​is located below the spindle assembly 166. The counterweight 158 ​​also has portions located on both sides of the spindle assembly 166. In the illustrated embodiment, the center of gravity 298 of the counterweight 158 ​​is preferably located within the height H of the spindle assembly 166. In some embodiments, such as those discussed in more detail below, Fig. 30B and Fig. 30C , the center of gravity 298 is located in both the first plane P1 and the second plane P2. In this case, the center of gravity 298 is located along the second reciprocating axis 370, so the first reciprocating axis 240 and the second reciprocating axis 370 coincide with each other. Figures 1A to 27 In the illustrated embodiment, the center of gravity 298 is vertically offset from the first plane P1 by a distance D1 and is located in the second plane P2. In this case, the first reciprocating axis 240 and the second reciprocating axis 370 are parallel to each other, wherein the first reciprocating axis 240 is offset from the second reciprocating axis 240 by a distance D1. In the illustrated embodiment, the distance D1 is less than the distance D2 between the first plane P1 and the outer surface OS of the shaft 358 of the spindle. In other embodiments, the distance D1 is less than the distance between the first plane P1 and the inner surface of the spindle bushing 362. In other embodiments, the distance D1 is less than the distance between the first plane D1 and the outer surface of the spindle bushing 362. As shown in FIG. Fig. 20As shown, the center of gravity 298 is vertically offset from above the first plane P1 (and in this case the second reciprocating axis 370), but in other embodiments, the center of gravity 298 can be vertically offset from below the first plane P1. The associated axes 240, 370 and the center of gravity 298, 372 can reduce or eliminate vibrations in the x-direction (e.g., along the x-axis), the y-direction (e.g., along the y-axis), and the z-direction (e.g., the z-axis), as well as pitch vibrations (e.g., rotations around the y-axis), roll vibrations (e.g., rotations around the x-axis), and yaw vibrations (e.g., rotations around the z-axis).

[0080] In addition, the second pin 316 and the second bearing 324 are received by the elongated aperture 374 in the second yoke 350 of the main shaft assembly 166. The elongated aperture axis 378 is perpendicular to the rotation axis 208 of the output gear 154. Moreover, the elongated aperture axis 378 is parallel to the first elongated aperture axis 282 of the counterweight 158. The second yoke 350 is positioned between the crankshaft 162 and the plate 400 coupled to the gearbox 72 and is vertically constrained by them. Fig. 9 As shown, the plate 400 is coupled to the second gearbox portion 74 by fasteners 404 and the protrusions 102 of the second gearbox portion 94 extending through the apertures 412 of the plate 400. In addition, the arcuate guide wall 140 receives and supports the spindle shaft 358. As shown, the spindle shaft 358 extends through the opening 106 of the second gearbox portion 94 so that the spindle shaft 358 and the blade clamp 366 protrude from the gearbox 72. The spindle bushing 362 is positioned within the gearbox 72 and supports relative movement of the spindle shaft 358 relative to the gearbox 72.

[0081] When the motor 68 rotates the driving gear 150 about the output shaft 104, the output gear 154 rotates about the rotation axis 208. The rotation of the output gear 154 rotates the eccentric shaft 216 about the rotation axis 208. Because the eccentric shaft 216 is received in the first elongated aperture 278 of the counterweight 158, the rotation of the eccentric shaft 216 causes the counterweight 158 ​​to reciprocate along the first reciprocating axis 240. Moreover, the rotation of the eccentric shaft 216 causes the crankshaft 162 to rotate together about the rotation axis 208, which causes the second pin 316 to rotate about the rotation axis 208. Because the second pin 316 is received in the elongated aperture 374 of the main shaft assembly 166, the rotation of the second pin 316 causes the main shaft assembly 166 to reciprocate along the second reciprocating axis 370. As described above, the first reciprocating axis 240 can be coincident with or parallel to the second reciprocating axis 370. Because the eccentric shaft 216 and the second pin 316 are offset 180 degrees from each other, the counterweight 158 ​​and the spindle assembly 166 reciprocate in opposition to each other. The stroke length of the counterweight 158 ​​may be at least 70% of the stroke length of the spindle assembly 166.

[0082] In some embodiments, such as in Fig. 27 In the embodiment of the present invention, the motor 68 (and thus its motor output shaft 104 and motor axis 170) is positioned between the output gear 154 (and thus its rotation axis 208) and the blade clamp 366. This configuration reduces the size of the drive assembly 76 relative to conventional drive assemblies while maintaining the same stroke as the spindle assembly 166 of the drive assembly of a conventional reciprocating mechanism. In other embodiments, such as in Fig.28 In the embodiment of the present invention, the output gear 154 (and its rotation axis 208) can be positioned between the motor 68 (and thus its motor output shaft 104 and motor axis 170) and the blade clamp 366. Regardless of how the motor 68 (and thus the motor output shaft 104) is positioned relative to the output gear 154, the rotation axis 208 of the output gear 154 and the motor axis 170 of the motor 68 are offset from each other in the direction of the second reciprocating motion axis 370. With respect to conventional drive assemblies and Figures 1A to 27 The drive assembly 76 of the embodiment of the present invention is configured to reduce the size of the drive assembly 76. Accordingly, reducing the size of the drive assembly 76 allows the size of the housing 40 to be correspondingly reduced. In the embodiment shown, the length of the motor housing portion can be reduced by between 10% and 20%, while the length of the gearbox housing portion can be reduced by between 5% and 10%. In addition, the overall height of the motor housing portion and the gearbox portion can be reduced by between 10% and 20%.

[0083] like Figure 1A and Figure 1B As shown, the saw 10 also includes a stand assembly 500. The stand assembly 500 is coupled relative to the front end of the housing 40 opposite the battery pack. In the illustrated embodiment, the stand assembly 500 is a movable (e.g., pivotable) stand assembly. The stand assembly 500 includes a front surface or front plate 504 that engages or rests on a workpiece. Figure 3 As shown, the front plate 504 also defines an opening 508 for the tool element to pass through. The front plate 504 is movably or pivotably coupled to two connecting legs 512 that connect the support assembly 500 relative to the housing 40. The front plate 504 can pivot about an axis 520. In other embodiments (not shown), the support assembly 500 can be an adjustable support assembly or a fixed support assembly in other ways.

[0084] At least a portion of the connecting legs 512 are positioned on and coupled (via fasteners) to opposite sides of the gearbox 72. In addition, the spindle shaft 358 and the blade clamp 366 extend between the connecting legs 512. Figure 4As shown, the connecting legs 512 each include a first end coupled to the gear box 72 and a second end coupled to the front plate 504. Moreover, the connecting legs 512 each include a first portion 524 extending from the first end toward the second end, a second portion 528 coupled to the first portion 524, and a third portion 532 coupled to the second portion 528 and extending from the second portion 528 to the second end. The first and second portions 524, 532 are both straight portions, while the second portion 528 is a curved portion. The distance between the first portions 524 of each connecting leg 512 is greater than the distance between the second portions 532 of each connecting leg 512. An elongated slot 536 runs through each first portion 524, and a recess 540 runs through each first portion 524. The elongated slot 536 receives the corresponding first protrusion or second protrusion 124, 128 of the gear box 72, respectively. The length of each elongated slot 536 parallel to the second reciprocating axis 370 is greater than the length of the corresponding protrusion 124, 128, so that there is a gap between the corresponding elongated slot 536 and the elongated protrusion 124, 128. Similarly, the length of the recess 540 parallel to the second reciprocating axis 370 is longer than the size (e.g., diameter) of the protrusion 132, so that there is a gap between the corresponding recess 540 and the protrusion 132. As shown in the figure, the support assembly 500 can therefore move axially relative to the gearbox 72 due to axial vibration. When the support assembly 500 moves axially, each connecting leg 512 (e.g., its curved portion 528) axially abuts the gearbox 72. The axial vibration is absorbed by the elastic members 116, 120 to reduce the load borne by the gearbox 72, which is ultimately borne by the user. Therefore, the gearbox 72 is configured as a shock absorber to prevent vibration in the application caused by cutting loads and the fixation of the tool to the workpiece.

[0085] FIG. 30A to FIG. 40 A saw 610 according to another embodiment of the present invention is shown. The saw 610 is similar to the saw 10 described above. As such, like parts are given like reference numerals plus 600, and only the differences between the saw 10 and the saw 610 are described below.

[0086] refer to Fig.31 and Fig.32, similar to the saw 10, the saw 610 includes a counterweight 758 configured as a first scotch yoke mechanism within the gear box 672. Similar to the counterweight 158, the counterweight 758 includes a body having a first end 850 (e.g., a front end), a second end 854 (e.g., a rear end) opposite the first end 850, a first side or top side 858, a second side or bottom side 862 opposite the first side 858, a third side 866, and a fourth side 870 opposite the third side 866. The fourth side 870 defines a wall 1000 having a first hole 1004 extending between the first end 850 and the second end 854. The first hole 1004 defines a circular cross-sectional shape. In other embodiments, the first hole 1004 may include a rectangular, oblong, or similar cross-sectional shape. The first hole 1004 is sized to receive a first guide rail 1008 (e.g., a first guide rail 1008) disposed within the gear box 672. Fig.32 shown).

[0087] refer to Fig.31 , the third side 866 defines a wall 1012 having an inner edge 1016. The inner edge 1016 is defined between the third side 866 and the first side 858. The inner edge 1016 is curved. In other embodiments, the inner edge 1016 can be defined as an alternative shape. The shape of the inner edge 1016 is such that the inner edge 1016 can receive the second guide rail 1020 (such as Fig.32 ). In other words, the second rail 1020 partially supports the counterweight 758 by being positioned at the inner edge 1016. In other embodiments, the second rail 1020 can be disposed within a second hole formed in the wall 1012. In some embodiments, the second hole can be a mirror image of the first hole 1004. In other embodiments, the second hole can be different from the first hole 1004. When the counterweight 758 is disposed within the gearbox 672, the first rail 1008 is disposed in the first hole 1004 and the gearbox 672 is positioned on the second rail 1020 at the inner edge 1016. The counterweight 758 is supported by the first and second rails 1008, 1020 and can slide within the gearbox 672 along the first and second rails 1008, 1020. The first rail and the rails 1008, 1020 provide the counterweight 758 with increased axial balance within the gearbox 672. Although not shown, it should be understood that Figures 1A to 28 Examples may include Figures 34 to 40 Gear box 972 and guide rails 1008, 1020.

[0088] like Fig. 30B and Fig. 30CAs shown, the spindle assembly 766 extends generally through the counterweight 758. That is, the spindle assembly 766 is generally positioned between the first side 858 and the second side 862 of the counterweight 758 and between the third side 866 and the fourth side 870 of the counterweight 758. Accordingly, a portion of the counterweight 758 is located above the spindle assembly 766, and a portion of the counterweight 758 is located below the spindle assembly 766. The counterweight 758 also has portions located on both sides of the spindle assembly 766. As described above, the center of gravity 898 of the counterweight 758 is preferably located within the height H of the spindle axis 958. As shown in FIG. Fig. 30B and Fig. 30C As shown, the center of gravity 898 is located in both the first plane P1 and the second plane P2. In this case, the center of gravity 898 is located along the second reciprocating axis 970, so the first reciprocating axis 840 and the second reciprocating axis 970 coincide with each other. In other embodiments, the center of gravity 898 of the counterweight 758 can be vertically offset from the first plane P1, as described above with reference to Figures 1A to 28 discussed.

[0089] refer to Fig.33 Similar to the saw 10, the saw 610 includes a crankshaft 762 coupled to the output gear 754. A first bearing 920 surrounds the eccentric shaft 816 positioned between the output gear 754 and the crankshaft 762. A second bearing 924 surrounds the second end of the second pin 916. The second pin 916 includes a retaining shoulder 1024 disposed at the second end of the second pin 916. Thus, the retaining shoulder 1024 (rather than the retaining surface 326 of the saw 10) prevents the second bearing 924 from being disconnected from the second pin 916. A gap is formed between the retaining shoulder 1024 and the second bearing 924, thereby allowing the second bearing 924 to move without being disconnected from the second pin 916. The gap reduces unnecessary friction between the second bearing 924 and the retaining shoulder 1024. Although not shown, it should be understood that Figures 1A to 28 Examples may include Figures 34 to 40 A retaining shoulder 1024 is provided.

[0090] like Figures 34 to 40 As shown, the output gear 754 and the crankshaft 762 can be configured to guide the grease contained in the gear box 672 to the eccentric shaft 816 and the first bearing 920 along one or more grease channels. In this case, the outer surface of the eccentric shaft 816 may include a first groove 816a and a second groove 816b. The first groove 816a and the second groove 816b both extend parallel to the eccentric axis 820. Fig.39808 and the eccentric axis 820 both extend into and out of the page. The first axis 822 extends along the diameter of the output gear and intersects both the rotation axis 808 and the eccentric axis 820. As shown, the first groove 816a and the second groove 816b are located on opposite sides of the eccentric axis 820 and on opposite sides of the first axis 822. Moreover, the first groove 816a and the second groove 816b are positioned on a second axis 824 that intersects both the eccentric axis 820 and the first axis 822. As shown, the first bearing 920 surrounds the first and second grooves 816a, 816b.

[0091] The crankshaft 762 includes a first aperture 762a and a second aperture 762b extending therethrough. The first aperture 762a and the second aperture 762b are both parallel to the rotation axis 808 and the eccentric axis 820. The first groove 816a is configured to dock with the first aperture 762a, and the second groove 816b is configured to dock with the second aperture 762b. In addition, the second yoke 950 of the main shaft assembly 766 includes fan-shaped or concave surfaces 950a, 950b located on opposite sides thereof.

[0092] In use, when the main shaft assembly 766 reciprocates along the second reciprocating axis 970, grease is directed through the crankshaft 762 to lubricate the surface of the eccentric shaft 816 and the surface of the first bearing 920. In particular, the movement of the second yoke 950 causes the grease to reach the grooves 816a, 816b through the orifices 762a, 762b in the crankshaft 762. In other words, the abutting first orifice 762a and the first groove 816a can be considered as a first grease channel, while the abutting second orifice 762b and the second groove 816b can be considered as a second grease channel. The first grease channel and the second grease channel are configured to allow grease to flow through to lubricate the outer surface of the eccentric shaft 816 surrounded by the first bearing 920. As Figure 41 to Figure 43 As shown, the grease passage is located at a position where the counterweight 758 has no acceleration (e.g., no inertial force) under nominal conditions, so that the first bearing 920 is subjected to negligible contact forces when it is not supported by the eccentric shaft 816. The sector surfaces 950a, 950b of the second yoke 950 promote the upward movement of grease through the grease passage toward the output gear 754. In other embodiments, the grease passage (and thus the grooves 816a, 816b and orifices 762a, 762b to which it abuts) may be located elsewhere. In addition, while there are two grease passages in the illustrated embodiment, there may be a single grease passage or more than two grease passages in other embodiments. Regardless, the grease passage helps to reduce friction, reduce wear, and improve smoothness of operation. Although not shown, it should be understood that Figures 1A to 28 Examples may include Figures 34 to 40grease passages.

[0093] In some embodiments, the saw 10 further includes multiple modes that allow the user to change the output reciprocating speed of the tool element. These modes can allow the reciprocating speed to be changed by adjusting the motor speed or by adjusting the physical transmission. In addition, the user can change between modes via an actuator on the housing, a remote device, or an application on a smart phone or tablet.

[0094] Although the invention has been described in detail with reference to certain preferred embodiments, variations and modifications exist within the scope and spirit of one or more independent aspects of the invention described.

[0095] Various features and advantages of the invention are set forth in the following claims.

Claims

1. A reciprocating tool, characterized in that include: a housing having a handle configured to be grasped by a user; a motor supported by the housing and defining a motor axis; A driving gear, which is rotated around the motor axis by the motor; A driven gear defining a rotation axis parallel to the motor axis, the driven gear meshing with the driving gear to rotate about the rotation axis via the driving gear; a crankshaft coupled to the driven gear and rotatable together with the driven gear; a counterweight having a first yoke coupled to the driven gear to convert rotation of the driven gear into reciprocating motion of the counterweight; as well as a main shaft having a second yoke coupled to the crankshaft to convert the rotation of the driven gear into reciprocating motion of the main shaft, The counterweight and the main shaft reciprocate in opposite directions.

2. The reciprocating tool according to claim 1, characterized in that The center of the crankshaft is coaxial with the rotation axis of the driven gear.

3. The reciprocating tool according to claim 1, characterized in that The main shaft and the counterweight are offset 180 degrees from each other.

4. The reciprocating tool according to claim 1, wherein: The motor axis is positioned between the rotational axis and a blade holder coupled to the spindle.

5. The reciprocating tool according to claim 1, wherein: The rotational axis is positioned between the motor axis and a blade holder coupled to the spindle.

6. The reciprocating tool according to claim 1, wherein: The motor axis is perpendicular to the reciprocating axis of the spindle.

7. The reciprocating tool of claim 1, wherein Further included is a gear box that encloses the driving gear, the driven gear, the crankshaft, the counterweight, and at least a portion of the main shaft.

8. The reciprocating tool of claim 7, wherein Further included is a fastener extending inwardly from the gear housing, the fastener being configured to be received in the elongated aperture of the counterweight to guide reciprocating motion of the counterweight.

9. The reciprocating tool according to claim 1, wherein: The spindle defines a reciprocation axis along which the spindle reciprocates, and wherein a center of gravity of the counterweight is located along the reciprocation axis.

10. The reciprocating tool of claim 1, wherein: The spindle defines a reciprocation axis along which the spindle reciprocates, and wherein the center of gravity of the counterweight is vertically offset from the reciprocation axis and positioned within the height of the spindle.

11. The reciprocating tool of claim 1, wherein Further includes a gear box, the gear box enclosing the driving gear, the driven gear, the crankshaft and the counterweight; as well as A fastener extends inwardly from the gear housing, the fastener being configured to be received in the elongated aperture of the counterweight to guide reciprocating motion of the counterweight.

12. The reciprocating tool of claim 1, wherein Further comprising a gear box enclosing the driving gear, the driven gear, the crankshaft and the counterweight, wherein the counterweight is disposed on a first guide rail and a second guide rail within the gear box and is movable along the first guide rail and the second guide rail.

13. A reciprocating tool, characterized in that include: a housing having a handle configured to be grasped by a user; a motor supported by the housing; A driving gear, which is rotated by the motor; a driven gear defining a rotation axis, the driven gear meshing with the driving gear to rotate about the rotation axis via the driving gear; a crankshaft coupled to the driven gear and rotatable together with the driven gear; a counterweight having a first yoke coupled to the driven gear to convert rotation of the driven gear into reciprocating motion of the counterweight, the counterweight defining a center of gravity; as well as a main shaft having a second yoke coupled to the crankshaft to convert the rotation of the driven gear into reciprocating motion of the main shaft, wherein the counterweight and the main shaft reciprocate in opposite directions to each other, and Therein, the center of gravity of the counterweight is positioned within the height of the main axis.

14. The reciprocating tool of claim 13, wherein: The spindle defines a reciprocation axis along which the spindle reciprocates, and wherein a center of gravity of the counterweight is located along the reciprocation axis.

15. The reciprocating tool of claim 13, wherein: The spindle defines a reciprocation axis along which the spindle reciprocates, and wherein the center of gravity of the counterweight is vertically offset from the reciprocation axis.

16. The reciprocating tool of claim 13, wherein: A portion of the counterweight is located above the main shaft, and a portion of the counterweight is located below the main shaft.

17. A reciprocating tool, characterized in that include: case; a motor supported by the housing; A driving gear, which is rotated by the motor; a driven gear defining a rotation axis and including an eccentric shaft, the driven gear meshing with the driving gear to rotate about the rotation axis via the driving gear; a bearing movably supported on the eccentric shaft; a crankshaft coupled to the eccentric shaft and rotatable together with the driven gear; a grease passage at least partially defined through the crankshaft; Counterweight , the counterweight has a first yoke, the eccentric shaft extends through the first yoke, so that rotation of the driven gear causes reciprocating motion of the counterweight, and the bearing is positioned between the eccentric shaft and the first yoke; as well as a main shaft having a second yoke coupled to the crankshaft to convert the rotation of the driven gear into reciprocating motion of the main shaft, wherein the counterweight and the main shaft reciprocate in opposite directions to each other, and The reciprocating motion of the main shaft causes the grease to pass through the grease channel to lubricate the bearing.

18. The reciprocating tool of claim 17, wherein: The grease passage is at least partially defined by a bore extending through the crankshaft.

19. The reciprocating tool of claim 17, wherein: The grease passage is defined by a bore extending through the crankshaft and a groove in the outer surface of the eccentric shaft that interfaces with the bore.

20. The reciprocating tool of claim 17, wherein: The second yoke includes a sector-shaped surface that guides the grease to the grease channel.

21. The reciprocating tool of claim 17, wherein: The grease channel extends parallel to the axis of rotation.

22. The reciprocating tool of claim 17, wherein: The motor defines a motor axis, wherein the driving gear is rotated about the motor axis by the motor, and wherein the motor axis is parallel to the rotation axis.

23. A reciprocating tool, characterized in that include: a housing having a handle configured to be grasped by a user; a motor supported by the housing; A drive assembly comprising: A driving gear is rotated by the motor. A driven gear meshing with the driving gear to rotate about a rotation axis through the driving gear, a crankshaft coupled to the driven gear and rotatable together with the driven gear, and a main shaft having a yoke coupled to the crankshaft to convert rotation of the driven gear into reciprocating motion of the main shaft; a gear box supported by the housing and configured to support the motor and the drive assembly, the gear box comprising a first end, a second end opposite the first end, and a resilient member positioned at the second end; as well as A mount assembly is coupled to the gearbox and is axially movable relative to the gearbox, the mount assembly being configured to abut the resilient member to absorb shock due to axial vibration during operation.

24. A reciprocating tool, characterized in that include: a housing having a handle configured to be grasped by a user; a motor supported by the housing and defining a motor axis; A driving gear, which is rotated around the motor axis by the motor; A driven gear defining a rotation axis parallel to the motor axis, the driven gear meshing with the driving gear to rotate about the rotation axis via the driving gear; a crankshaft coupled to the driven gear and rotatable together with the driven gear; a counterweight having a first yoke coupled to the driven gear to convert a rotation of the driven gear into a reciprocating motion of the counterweight, the counterweight being disposed on a guide rail within the housing; as well as a main shaft having a second yoke coupled to the crankshaft to convert the rotation of the driven gear into reciprocating motion of the main shaft, The counterweight can slide along the guide rail in the housing.

25. The reciprocating tool of claim 24, wherein Further included is a gear box that surrounds the driving gear, the driven gear, the crankshaft, the counterweight, the guide rail, and at least a portion of the main shaft.

Images