Reciprocating motion cutting tool

Abstract

A reciprocating cutting tool is provided. A reciprocating saw as the reciprocating cutting tool has a motor (3), a bar-shaped slide (6), a power transmission housing (20), a tool holding portion (102), and a release cylinder (140) as an operation cylinder, wherein the slide (6) is reciprocated in a front-rear direction by a reciprocating motion conversion mechanism (5); the power transmission housing (20) houses the reciprocating motion conversion mechanism (5); the tool holding portion (102) is provided at a front end portion of the slide (6), can detachably hold a tool, and can perform an operation related to detachment of the tool; and the release cylinder (140) operates the detachment operation of the tool holding portion (102) by rotation of itself. The release cylinder is held to the power transmission housing in a rotatable manner via two ring-shaped members (144A, 144B). Accordingly, deterioration of movement of the operation cylinder due to entry of chips between the operation cylinder and the housing can be suppressed.

Description

Technical Field

[0001] This invention relates to a rechargeable reciprocating saw or other reciprocating motion cutting tool. Background Technology

[0002] U.S. Patent No. 8230607 (Patent Document 1) discloses a reciprocating tool 10 having a sleeve 138 (operating sleeve) which is rotatably mounted in a housing 14 for removing a cutter. [Existing Technical Documents] [Patent Literature]

[0003] Patent Document 1: Specification of U.S. Patent No. 8230607 Summary of the Invention [The technical problem that the invention aims to solve]

[0004] The purpose of this invention is to provide a reciprocating cutting tool that suppresses the deterioration of the movement of the operating cylinder due to chips entering between the operating cylinder and the outer casing. [Technical solutions used to solve technical problems]

[0005] To achieve the above objectives, the reciprocating cutting tool of the present invention may include a motor, a rod-shaped slider, a reciprocating motion conversion mechanism, and a power transmission housing. The reciprocating motion conversion mechanism, with the extension direction of the slider as its front-rear direction, converts the rotation of the motor into a front-rear reciprocating motion and transmits it to the slider. The power transmission housing houses the reciprocating motion conversion mechanism. The reciprocating cutting tool may have a tip tool holding portion disposed at the front end of the slider, capable of detaching and attaching a tip tool, and capable of performing actions related to the detachment and attachment of the tip tool. The reciprocating cutting tool may have an operating cylinder, which operates the action of the tip tool holding portion by its own rotation. The operating cylinder is rotatably held in the power transmission housing via one or more annular members. [Invention Effects]

[0006] The reciprocating cutting tool according to the present invention can suppress the deterioration of the operation of the operating cylinder. Attached Figure Description

[0007] Figure 1 This is a 3D view of the reciprocating saw from the upper right front. Figure 2 This is a 3D view of the reciprocating saw from the upper left front. Figure 3 yes Figure 1 The central longitudinal section view of the front part. Figure 4 yes Figure 3 The central longitudinal section view of the front part. Figure 5 yes Figure 3 AA sectional view. Figure 6 yes Figure 3 BB cross-sectional view. Figure 7 Viewed from the upper left rear Figure 1 An exploded three-dimensional view of the sliding component and release mechanism in a reciprocating saw. Figure 8 Viewed from the upper right front Figure 1 An exploded three-dimensional view of the sliding component and release mechanism in a reciprocating saw. Figure 9A yes Figure 6 A central longitudinal section view of the tool holder of the sliding component (tool in standby state). Figure 9B This is a cross-sectional view of the retaining pin of the tool holder (tool in standby state). Figure 10A yes Figure 6 A central longitudinal section view of the tool holder of the sliding component (tool mounted state). Figure 10B This is a cross-sectional view of the retaining pin portion of the tool holder (tool in the installed state). Figure 11A yes Figure 6 A central longitudinal section view of the tool holder of the sliding component (tool removed). Figure 11B This is a cross-sectional view of the retaining pin of the tool holder (tool removed). Figure 12A yes Figure 6 A central longitudinal section view of the tool holder (holding pin in bottom contact state) of the sliding component. Figure 12B This is a cross-sectional view of the retaining pin portion of the tool retaining part (retaining pin in the bottom contact state). Figure 13 Viewed from above Figure 1 An exploded perspective view of the front part of the upper power transmission housing, the release mechanism, and the front part of the lower power transmission housing of a reciprocating saw. Figure 14 Viewed from below Figure 1 An exploded perspective view of the front part of the upper power transmission housing, the release mechanism, and the front part of the lower power transmission housing of a reciprocating saw. [Explanation of reference numerals in the attached figures] 1: Reciprocating saw (reciprocating motion cutting tool); 3: Motor; 5: Reciprocating motion conversion mechanism; 6: Sliding component; 7: Release mechanism; 20: Power transmission housing; 102: Tool holder (top tool holder); 140: Release cylinder (operating cylinder); 140F: Flange; 140G1, 140G2: Groove; 142: Tension spring (elastic body); 144A, 144B: Circular spring (circular component); 148: Inner raised part; 150: Protrusion; 160U: First upper groove (first groove); 160D: First lower groove (first groove); 162U: Second upper groove (second groove); 162D: Second lower groove (second groove); 164U: First upper cylindrical belt (cylindrical belt); 164D: First lower cylindrical belt (cylindrical belt); B: Cutting tool (top tool); BE: Cutting edge (acting part). Detailed Implementation

[0008] In one embodiment of the present invention, the operation of the tip tool holding part can be an action of removing the tip tool, i.e., a removal action. According to this structure, the deterioration of the operability of the operating cylinder associated with the removal action can be suppressed. In one embodiment of the present invention, the tip tool holder has a protrusion, and the operation of the tip tool holder is performed by rotating the protrusion along a front-rear axis. The operating cylinder has an inwardly raised portion and rotates along a front-rear axis, with the rotational movement of the protrusion operated by the inwardly raised portion. According to this structure, the operability deterioration of the operating cylinder, which operates the tip tool holder by rotational movement, can be suppressed. In one embodiment of the invention, the annular component may be an annular spring. Alternatively, in another embodiment, a circular groove may be formed on the outer surface of the operating cylinder, and the radially inner portion of the annular component may enter the groove. Based on these structures, it is easier to provide an annular component for maintaining the operability of the operating cylinder.

[0009] In one embodiment of the present invention, the operating cylinder may have a flange portion. Additionally, the power transmission housing may have a first groove into which the flange portion enters and a cylindrical strip portion that contacts the annular component. According to this structure, it is possible to prevent the operating cylinder from falling off and suppress deterioration of the operating cylinder's operability. In one embodiment of the invention, the first groove portion and the cylindrical belt portion may be adjacent to each other. According to this structure, the operating cylinder and surrounding portions, which suppress deterioration of operability and prevent detachment, can be compactly arranged.

[0010] In one embodiment of the invention, the reciprocating cutting tool may have an elastomer that applies force to the operating cylinder toward the initial rotational position. The elastomer may be disposed on the outside of the operating cylinder. The power transmission housing may have a second groove into which the elastomer enters and a cylindrical band portion in contact with the annular component. According to this structure, it is possible to suppress the deterioration of the operability of the operating cylinder, which can be reset to the initial rotational position. In one embodiment of the invention, the second groove and the cylindrical belt portion can be adjacent to each other. According to this structure, the operating cylinder and its surrounding portions can be compactly arranged to suppress deterioration of operability and to return to the initial rotational position.

[0011] In one embodiment of the invention, two annular components may be provided. Furthermore, the annular components may be disposed at the front and rear of the operating cylinder. According to these structures, the deterioration of the operating cylinder's operability can be further suppressed. In one embodiment of the invention, the width of the annular component can be 4 mm or less. According to this structure, the contact area between the annular component and the power transmission housing is reduced, further suppressing deterioration of the operability of the operating cylinder. In one embodiment of the invention, the tip tool may have an action portion that acts on the workpiece, and may be mounted on the tip tool holder with the action portion positioned on at least one of the lower and upper sides. According to this structure, it is possible to suppress the deterioration of the operability of the operating cylinder associated with more easily operable reciprocating cutting tools.

[0012] In one embodiment of the invention, the annular component can be made of metal, or iron, or an iron alloy. Additionally, the operating cylinder can be made of synthetic resin. Furthermore, the power transmission housing can be made of metal, or aluminum, or an aluminum alloy. Based on these structures, the annular component and the power transmission housing become more robust. Furthermore, the operating cylinder is easier to form and has better resistance to external electric shock. Moreover, when the operating cylinder and the power transmission housing are made of different materials, the annular component uses a material closer to that of the power transmission housing than the operating cylinder, thereby suppressing deterioration of the operating cylinder's operability and extending the lifespan of the operating cylinder, the annular component, and the power transmission housing. [Example]

[0013] Hereinafter, embodiments (including modifications) of the present invention will be suitably described based on the accompanying drawings. This embodiment relates to a reciprocating cutting tool, which is an example of a power tool or a reciprocating tool, and more specifically, to a reciprocating saw. The front, back, up, down, left, and right directions in this embodiment are defined for ease of explanation and may vary depending on at least one of the working conditions and the state of the moving parts.

[0014] Figure 1This is a 3D view of the reciprocating saw 1 from the upper right front. Figure 2 This is a 3D view of the reciprocating saw 1 from the upper left front. Figure 3 yes Figure 1 The central longitudinal section view of the front part. Figure 4 yes Figure 3 The central longitudinal section view of the front part. exist Figure 3 In the diagram, the right side is the front of reciprocating saw 1, and the top side is the top of reciprocating saw 1.

[0015] The reciprocating saw 1 has a main body shell 2, a motor 3, a fan 4, a reciprocating motion conversion mechanism 5, a sliding part as the output part 6, a release mechanism 7, a counterweight mechanism 9, a track mechanism 12, a track switching mechanism 14, and a guide shoe 16.

[0016] The main body shell 2 is a support frame that directly or indirectly holds various components. The main body shell 2 includes a split shell 18, a power transmission shell 20, and a cover 22.

[0017] The front of the split housing 18 is cylindrical. The rear of the split housing 18 is annular. The split housing 18 is made of plastic. The split housing 18 holds the motor 3 within its upper front portion. The split housing 18 has a motor housing section 18M that houses the motor 3. The motor 3 has a motor housing 3a. The motor housing 3a is the outer contour of the motor 3. The motor housing 3a is cylindrical. The front of the motor housing 3a is open. The split housing 18 is connected to the power transmission housing 20 via the motor housing 3a. The split outer casing 18 is split in shape, having a left split outer casing 18a and a right split outer casing 18b. The left split housing 18a has multiple threaded bosses (not shown). The right split housing 18b has multiple threaded holes 24. The arrangement of the threaded holes 24 corresponds to the arrangement of the threaded bosses. The right split housing 18b is secured to the left split housing 18a by inserting multiple screws 28 into the threaded bosses and threaded holes 24 respectively, extending in the left-right direction. The annular rear portion extending vertically within the semi-split housing 18 is the first grip portion 30. The first grip portion 30 is held by the user. Furthermore, the split housing 18 does not have to be split in shape; for example, it can also be a one-piece shape.

[0018] The main switch 32 is located on the upper part of the first grip portion 30. The main switch 32 has a trigger 33 and a main switch body 34. The trigger 33 protrudes from the front of the upper part of the first grip portion 30. The user can operate the trigger 33 by pulling it with their fingertip (moving the trigger 33 backward). The trigger 33 is positioned in front of the main switch body portion 34. The trigger 33 is connected to the main switch body portion 34. The main switch body 34 is disposed within the upper part of the first grip portion 30. The main switch body 34 is switched on and off by operation of the trigger 33. The main switch body 34 is turned on when the trigger 33 is engaged to a predetermined amount or more. In addition, the main switch body 34 sends a signal (e.g., resistance value) that varies according to the engagement amount or more than the predetermined amount. The trigger 33 switches the motor 3 on and off via the main switch body 34. The trigger 33 is a switch operating part that operates the motor 3 on and off.

[0019] A locking button 35 is provided on the upper side of the trigger 33. The locking button 35 is a plate-shaped part that extends in the left-right direction. The left and right portions of the locking button 35 are exposed from the split housing 18. The locking button 35 can slide to the right when its left portion is pressed. In addition, the locking button 35 can slide to the left when its right portion is pressed. When the locking button 35 is slid to the right and is located on the right side, it prevents the trigger 33 from being pulled. Therefore, the motor 3 cannot be activated. When the locking button 35 is slid to the left and is located on the left side, it allows the trigger 33 to be pulled. Therefore, the motor 3 can be activated.

[0020] A speed switching dial 36 is located in front of the locking button 35. The speed switching dial 36 is a disc that extends upwards, downwards, leftwards, and rightwards, and can be rotated. The upper part of the speed switching dial 36 protrudes from the split housing 18. The speed switching dial 36 sends a signal corresponding to the rotation position (angle).

[0021] The split housing 18 holds the control circuit board 42 on the lower side of the motor 3. The control circuit board 42 controls the motor 3. The control circuit board 42 is equipped with at least a microcomputer and multiple (6 or 12) switching elements. The control circuit board 42 is positioned below the motor 3. The control circuit board 42 is tilted, or more specifically, tilted forward and backward.

[0022] The lower rear portion 18E of the split housing 18 is recessed upward relative to the lower front portion 18F of the split housing 18. A battery mounting section 50 is provided at the lower rear part 18E of the split housing 18. The battery 54 is mounted on the battery mounting section 50 by sliding from the rear to the front. The mounted battery 54 is electrically connected to the motor 3 via the control circuit board 42. The battery 54 supplies power to the motor 3.

[0023] The power transmission housing 20 directly or indirectly supports the reciprocating motion conversion mechanism 5, the sliding member 6, the counterweight mechanism 9, the track mechanism 12, and the track switching mechanism 14. The power transmission housing 20 houses the reciprocating motion conversion mechanism 5. The power transmission housing 20 is made of metal. The power transmission housing 20 is connected to the front side of the split housing 18. The power transmission housing 20 is a split-shaped cylindrical structure with openings at the front and rear. The power transmission housing 20 is made of aluminum (including alloys). Since it is equipped with the reciprocating motion conversion mechanism 5, the power transmission housing 20 can also be considered as the conversion mechanism housing. Furthermore, the power transmission housing 20 can also be formed of a metal other than aluminum. The power transmission housing 20 has an upper power transmission housing 20a, a lower power transmission housing 20b, and a bearing cage 20c. The upper power transmission housing 20a is fixed to the lower power transmission housing 20b by a plurality of screws in the vertical direction (not shown). The rear end of the lower power transmission housing 20b is mounted to the front end of the split housing 18 by a plurality of screws (not shown) extending forward from the motor housing 3a in the front direction.

[0024] The cover 22 is cylindrical. The cover 22 is externally mounted on the power transmission housing 20. The cover 22 is disposed on the outside of the power transmission housing 20. The cover 22 is made of an elastomer (rubber) and is disposed on the outside of the power transmission housing 20 as a thermal insulation cover or an electrical insulation cover. Alternatively, the cover 22 may not be included in the structural elements of the main housing 2. Furthermore, the cover 22 may also be formed of plastic. The rear end of the cover 22 covers the front end of the split outer shell 18. The cover 22 is continuous with the split outer shell 18 through its outer surface. Furthermore, a track switching rod hole 58 is provided on the rear left side of the cover 22. Figure 2 The track switching rod extends upwards, downwards, forwards, and backwards via hole 58. On the other hand, the lower part of the cover 22, that is, the front part of the main body shell 2, becomes the second grip part 60. The second grip part 60 is held by the user. Furthermore, at least one of the following can be varied: the number of sections of the main body casing 2, the size of each section of the main body casing 2, and the shape of each section of the main body casing 2. For example, the rear part of the split casing 18 can be formed as a handle casing that is separate from the split casing 18. In addition, the battery mounting part 50 can be formed separately from the split casing 18.

[0025] Furthermore, a lamp 62 is disposed between the upper front portion of the power transmission housing 20 and the upper front portion of the cover 22. The lamp 62 has an LED substrate. The LED substrate is equipped with LEDs. Lamp 62 emits light and projects light forward. Lamp 62 can illuminate the vicinity of the cutting position in front of slider 6.

[0026] The motor 3, the main switch body 34, the speed switching dial 36, and the lamp 62 are electrically connected to the control circuit board 42 via multiple wires (not shown). The main body 64 of the reciprocating saw 1 is formed by the part that holds the motor 3 in the split housing 18 (the outer part of the motor 3), the power transmission housing 20, the various parts held by them, and the cover 22.

[0027] Motor 3 is electric. Motor 3 is a brushless motor. Motor 3 is DC driven. The motor 3 has a motor housing 3a, a stator 66 and a rotor 67.

[0028] The motor housing 3a is held in the split outer casing 18. The stator 66 is cylindrical. The stator 66 has multiple (6) coils 66C. The rotor 67 is located inside the stator 66. The motor 3 is an internal rotor type. The rotor 67 has a motor shaft 68. The motor shaft 68 is cylindrical and extends forward and backward. The motor shaft 68 is made of metal. The motor shaft 68 rotates about its own axis. The front end of the motor shaft 68 reaches the rear end of the power transmission housing 20. A pinion portion 68a is formed at the front end of the motor shaft 68. The pinion portion 68a has multiple teeth.

[0029] Additionally, a front motor bearing 69 is provided behind the pinion section 68a. The front motor bearing 69 is arranged around the front of the motor shaft 68. The front motor bearing 69 supports the motor shaft 68 in a manner that allows it to rotate about its axis. The front bearing 69 of the motor is held at the rear of the lower power transmission housing 20b. A rear bearing (not shown) is provided around the rear end of the motor shaft 68. The rear bearing supports the motor shaft 68 in a manner that allows it to rotate about its axis. The rear bearing is held in the motor housing 3a.

[0030] A fan 4 is disposed around the central periphery of the motor shaft 68, behind the front bearing 69, and in front of the rotor 67 and stator 66. The fan 4 is a centrifugal fan with multiple blades. The fan 4 pushes air radially outward by rotation. The fan 4 is integrally fixed to the motor shaft 68 and is capable of rotating integrally with the motor shaft 68. The fan 4 is mounted on the motor shaft 68. The fan 4 is held in the split housing 18 via the rotor 67 and the lower power transmission housing 20b. A lower power transmission housing 20b is configured on the front side of the fan 4. In addition, fan 4 can also serve as a structural element of motor 3.

[0031] The reciprocating motion conversion mechanism 5 is a power transmission mechanism that transmits the power of the motor 3 to the sliding member 6. The reciprocating motion conversion mechanism 5 transmits the rotational motion of the motor shaft 68 of the motor 3 to the sliding member 6. The reciprocating motion conversion mechanism 5 is held within the power transmission housing 20. The reciprocating motion conversion mechanism 5 is located between the motor 3 and the sliding member 6. The reciprocating motion conversion mechanism 5 has a bevel gear 70, a torque limiting mechanism 72, an intermediate shaft 74, a crank base 76, and a crank cam 78.

[0032] The bevel gear 70 is a disc-shaped gear extending forward, backward, left, and right, with tapered teeth (not shown) around the periphery of its upper surface. The bevel gear 70 meshes with the pinion section 68a. The bevel gear 70 rotates about a virtual axis of rotation in the up and down direction that passes through the center in the front, back, left and right directions.

[0033] The torque limiting mechanism 72 is clamped between the bevel gear 70 and the intermediate shaft 74. The torque limiting mechanism 72 transmits power from the bevel gear 70 to the intermediate shaft 74. For the torque limiting mechanism 72, the upper and lower horizontal plates, which are tightly pressed together by the force of the elastic body, are separated from each other by the excessive load from the side of the intermediate shaft 74, thereby protecting the bevel gear 70 and the motor 3 from the effects of the load.

[0034] The intermediate shaft 74 is a cylindrical component that extends vertically. The intermediate shaft 74 is supported by the upper intermediate bearing 80 and the lower intermediate bearing 82 in a manner that allows it to rotate about the same virtual axis of rotation as the bevel gear 70. Figure 2 , Figure 3 ). The upper intermediate bearing 80 is held in the lower power transmission housing 20b. The lower intermediate bearing 82 is a needle roller bearing. The lower intermediate bearing 82 is held in a disc-shaped bearing cage 20c. The bearing cage 20c is secured by multiple screws 86 in the vertical direction. Figure 3 (Only one shown in the diagram) is fixed to the lower power transmission housing 20b.

[0035] Crank base 76 is a crank-shaped component. The lower part of the crank base 76 becomes a cylindrical part 76A, and the central part of the crank base 76, which is threaded to the upper part of the intermediate shaft 74, becomes a plate-shaped part 76B that extends forward, backward, left and right. The upper part of the crank base 76 is formed as an eccentric disk portion 76C, which extends forward, backward, left and right in a manner in which its center is offset from the virtual central axis of the lower part of the crank base 76.

[0036] The crank cam 78 has a crank cam body 90, an eccentric pin 92, a barrel roller 94, and a bearing 96. The crank cam body 90 is a disc-shaped component extending forward, backward, left, and right. The virtual central axis of the crank cam body 90 in the vertical direction coincides with the same virtual axis of rotation as the bevel gear 70. A connecting portion 97, protruding downward in a cylindrical shape relative to other parts, is formed at the lower part of the crank cam body 90. An eccentric disc portion 76C of the crank base 76 is attached to the connecting portion 97. Furthermore, a cam portion 98 is formed on the periphery of the upper surface of the crank cam body 90. The cam portion 98 protrudes upward relative to adjacent parts. When viewed from above, the cam portion 98 is annular. The height of the cam portion 98 in the vertical direction gradually changes circumferentially. That is, the upper surface of the cam portion 98 becomes a cam surface 99. The eccentric pin 92 is a cylindrical shape extending vertically. The lower part of the eccentric pin 92 is inserted into a vertically oriented hole provided on the crank cam body 90. This hole is radially offset from the virtual central axis of the crank cam body 90. The barrel roller 94 is a cylindrical component. The outer surface of the barrel roller 94 bulges outwards, with the diameter increasing towards the center in the vertical direction. The barrel roller 94 is mounted on the upper part of the eccentric pin 92 via the bearing 96. The barrel roller 94 is supported in a manner that allows it to rotate about a virtual axis of rotation in the vertical direction. The bearing 96 is a needle roller bearing.

[0037] Figure 5 yes Figure 3 AA sectional view. Figure 6 yes Figure 3 BB cross-sectional view. Figure 7 This is an exploded three-dimensional view of the slider 6 and the release mechanism 7, viewed from the upper left rear. Figure 8 This is an exploded perspective view of the slider 6 and the release mechanism 7 from the upper right front. Figure 9A This is a central longitudinal sectional view of the tool holder 102 of the slider 6. Figure 9B This is a cross-sectional view of the central portion of the retaining pin 113 of the tool holder 102. Furthermore, in Figures 1 to 9BIn the middle, the tool holding part 102 is in the tool standby state that puts tool B into standby mode. The slider 6 has a slider body 100 and a tool holder 102 as a top tool holder. The front end of the slider 6 can protrude from the front end of the power transmission housing 20. The slider body 100 is a cylindrical shape extending front to back. A barrel-shaped roller receiving part 104 is provided at the rear of the slider body 100. The barrel-shaped roller receiving part 104 is a long cylindrical shape with a bottom extending left to right. The barrel-shaped roller receiving part 104 opens downward. The barrel-shaped roller receiving part 104 receives the barrel-shaped roller 94. When the crank cam 78 rotates, the barrel roller 94 rotates eccentrically. Based on the front-to-back component of the movement of the barrel roller 94, the slider body 100 reciprocates in the front-to-back direction via the barrel roller bearing portion 104. The left-to-right component of the movement of the barrel roller 94 is the relative movement of the barrel roller 94 within the barrel roller bearing portion 104 and is not transmitted to the slider body 100. The tool holding part 102 holds the tool B, which is the top tool. The tool B holding part 102 automatically holds the tool B simply by inserting the rear end of the tool B (one-click installation). The tool holder 102 bulges outwards and outwards relative to the slider body 100. The slider 6 is the output part. The tool B is a top tool. The tool B is a long plate and extends forward and backward during installation. The tool B has a cutting edge BE on one long side. The cutting edge BE is serrated. The tool B is installed with the cutting edge BE facing downwards. Alternatively, the tool B can also be installed with the cutting edge BE facing upwards. Furthermore, the tool B may have cutting edges BE on both long sides. The top tool may also be a tool other than the tool B.

[0038] The tool holding part 102 of the sliding member 6 has a push pin 110, a compression spring for the push pin 111, a guide sleeve 112, a holding pin 113, a compression spring for the holding pin 114, an auxiliary pin 115, a cam sleeve 116, a retaining ring 117, an auxiliary sleeve 118, and a torsion spring 119.

[0039] A slit 120, a first retaining pin hole 122, a first auxiliary pin hole 123 and a stepped portion 124 are formed at the front end of the slider body 100. The slit 120 extends forward, backward, vertically, and horizontally. The slit 120 has a width (in the left-right direction) slightly larger than the thickness of the tool B. A space enlargement section 120E, which expands to the left compared to other parts, is provided in the central part of the slit 120 in the vertical direction. The first retaining pin hole 122 is disposed on the left side of the slit 120 and communicates with the slit 120. The first retaining pin hole 122 extends to the left and right. The left portion of the first retaining pin hole 122 is enlarged relative to the right portion of the first retaining pin hole 122. The first auxiliary pin hole 123 is located on the right side of the slit 120 and communicates with the slit 120. The first auxiliary pin hole 123 extends to the left and right. The first auxiliary pin hole 123 faces the first retaining pin hole 122. A rib 125 is formed on the left side of the center of the first auxiliary pin hole 123, protruding radially inward relative to the other parts. The outer diameter of the front end of the slider body 100 is smaller than the outer diameter of the rear part, and a stepped portion 124 is formed in the part where the outer diameter of the slider body 100 changes.

[0040] A push pin 110 is disposed within the slit 120, specifically in the central portion of the slit 120 in the vertical direction. The push pin 110 extends forward and backward. The cross-section of the push pin 110 is D-shaped. A recess 110D is provided on the front left portion of the push pin 110, recessed to the right relative to the rear portion. The portion of the push pin 110 that is rearward of the recess 110D is disposed within the spatial expansion portion 120E of the slit 120. A compression spring 111 for the push pin is disposed within the slit 120, specifically in the central portion of the slit 120 in the vertical direction. The left portion of the compression spring 111 is disposed within the enlarged portion 120E of the slit 120. The compression spring 111 is an elastic body and is a helical spring. The compression spring 111 is disposed behind the push pin 110. The rear end of the compression spring 111 is disposed at the bottom of the rear end of the slit 120. The front end of the compression spring 111 contacts the push pin 110. The compression spring 111 is clamped between the push pin 110 and the sliding body 100. The compression spring 111 applies a forward force to the push pin 110.

[0041] The guide sleeve 112 is cylindrical. The guide sleeve 112 is disposed on the outer side of the front end of the sliding body 100. The axial direction of the guide sleeve 112 is the front-to-back direction. A circular recess 112G is formed on the outer surface of the front portion of the guide sleeve 112. The recess 112G is recessed radially inward relative to the surrounding area. The recess 112G is formed in such a way that it surrounds approximately one circumference of the outer surface of the front portion of the guide sleeve 112. In addition, the guide sleeve 112 has a second retaining pin hole 126 and a second auxiliary pin hole 128 in the central part. The second retaining pin hole 126 is located on the left side of the guide sleeve 112. The second retaining pin hole 126 extends laterally. The second retaining pin hole 126 overlaps with the first retaining pin hole 122. The diameter of the second retaining pin hole 126 is greater than the diameter of the left side of the first retaining pin hole 122. The second auxiliary pin hole 128 is located on the right side of the guide sleeve 112. The second auxiliary pin hole 128 extends laterally. The second auxiliary pin hole 128 faces the second retaining pin hole 126. The diameter of the second auxiliary pin hole 128 is equal to the diameter of the right side of the rib 125 of the first auxiliary pin hole 123.

[0042] A retaining pin 113 is disposed inside the first retaining pin hole 122 and the second retaining pin hole 126. The retaining pin 113 is cylindrical and extends to the left and right. The diameter of the central portion of the retaining pin 113 is the same as the size of the right portion of the first retaining pin hole 122. The diameter of the right end of the retaining pin 113 decreases relative to the diameter of the other portions. Therefore, a step 113S (stepped pin) is formed at the left end of the retaining pin 113. The right end of the retaining pin 113 has a tapered tip shape that becomes thinner towards the right. In addition, the diameter of the left end of the retaining pin 113 increases relative to the diameter of the other portions, and the left end of the retaining pin 113 becomes a head 113H with an expanded diameter relative to the other portions. The left surface of the retaining pin 113 becomes a curved surface 113C that bulges to the left. The retaining pin compression spring 114 is an elastic body and is a helical spring. The right end of the retaining pin compression spring 114 contacts the expanded diameter portion of the first retaining pin hole 122. The left end of the retaining pin compression spring 114 contacts the right surface of the head 113H of the retaining pin 113. The retaining pin compression spring 114 is clamped between the retaining pin 113 and the sliding body 100. The retaining pin compression spring 114 applies a force to the right side of the retaining pin 113. An auxiliary pin 115 is disposed inside the first auxiliary pin hole 123 and the second auxiliary pin hole 128. The auxiliary pin 115 is cylindrical and extends to the left and right. The left end of the auxiliary pin 115 can contact the rib 125 of the first auxiliary pin hole 123. The right end of the auxiliary pin 115 protrudes to the right from the second auxiliary pin hole 128 to form an exposed portion 115A. The diameter of the auxiliary pin 115 is the same as the diameter of the right portion of the first auxiliary pin hole 123 and the diameter of the second auxiliary pin hole 128. The auxiliary pin 115 connects the sliding body 100 and the guide sleeve 112.

[0043] The cam sleeve 116 is cylindrical. The axis of the cam sleeve 116 is in the front-to-back direction. The cam sleeve 116 is disposed outside the guide sleeve 112, the retaining pin 113, and the auxiliary pin 115. The cam sleeve 116 is rotatable about the slider body 100 and the guide sleeve 112. A first protrusion 116E is formed from the upper part to the left of the cam sleeve 116. The first protrusion 116E extends radially outward relative to the other parts of the cam sleeve 116. A cam surface 116C is formed on the inner surface of the first protrusion 116E. When viewed from the front, the diameter of the cam surface 116C gradually increases as it moves counterclockwise (installation direction C) from the lower part. The curved surface 113C of the head 113H of the retaining pin 113 contacts the cam surface 116C. When the tool holder 102 is not bearing the tool B (tool standby state), the curved surface 113C contacts the side of the cam surface 116C closest to the maximum diameter portion. Additionally, the cam sleeve 116 has a second extension 116F. The second extension 116F extends from the upper part of the cam sleeve 116 to the right side. The second extension 116F extends radially outward relative to the other parts of the cam sleeve 116. A space is formed between the second extension 116F and the guide sleeve 112. The upper first end portion 116X of the second extension 116F has a surface extending in both radial and longitudinal directions. The lower second end portion 116Y of the second extension 116F has a surface extending in both radial and longitudinal directions. Furthermore, the cam sleeve 116 has a protrusion 134 that projects radially outward. The protrusion 134 is positioned on the outer side of the second extension 116F. In the tool standby state, the protrusion 134 is positioned at the upper right. Furthermore, a plurality of protrusions 116B are formed on the inner surface of the opening at the rear end of the cam sleeve 116, which protrude radially inward more than the other inner surfaces. The protrusions 116B are arranged in the circumferential direction.

[0044] The retaining ring 117 is annular. The retaining ring 117 is fixed to the outside of the guide sleeve 112 through the inlet groove 112G. The retaining ring 117 is disposed on the front side of the cam sleeve 116 to inhibit the forward movement of the cam sleeve 116. The auxiliary sleeve 118 is cylindrical. The axial direction of the auxiliary sleeve 118 is front-to-back. The auxiliary sleeve 118 is disposed on the outer side of the slider body 100 and is rotatable around the slider body 100. The auxiliary sleeve 118 is disposed on the front side of the stepped portion 124. The stepped portion 124 is used to suppress rearward movement of the auxiliary sleeve 118. On the outer surface of the opening at the front end of the auxiliary sleeve 118, a plurality of recesses 118P are formed, which are further radially inward than other inner surfaces. The rear end of the auxiliary sleeve 118 enters the inner side of the opening at the rear end of the cam sleeve 116. Each recess 118P of the auxiliary sleeve 118 enters the corresponding protrusion 116B of the cam sleeve 116. The auxiliary sleeve 118 rotates together with the cam sleeve 116. The torsion spring 119 is annular and is an elastic body. The rear end of the torsion spring 119 forms a vertically extending connecting portion 119A at the center in the left-right direction and enters the slit 120. The connecting portion 119A is positioned between the bottom of the rear end of the slit 120 and the rear end of the compression spring 111 for the push pin. The connecting portion 119A is fixed to the slider body 100. The portion of the torsion spring 119 other than the connecting portion 119A surrounds the front end of the slider body 100 and is positioned on the rear side of the auxiliary sleeve 118. The front end of the torsion spring 119 is inserted into a hole in the front-rear direction of the auxiliary sleeve 118 and is fixed to the auxiliary sleeve 118. The torsion spring 119 applies force to the auxiliary sleeve 118 in the circumferential direction, i.e., counterclockwise (installation direction C) when viewed from the front.

[0045] The tool B has a retaining hole BH at its rear end. The diameter of the retaining hole BH is slightly larger than the diameter of the left end of the retaining pin 113. Additionally, the rear end of tool B has a notch at the corner opposite to the cutting edge BE. The portion of the rear end of tool B on the same side as the cutting edge BE protrudes rearward to form a protruding piece BJ. The rear portion above the protruding piece BJ of tool B forms the shoulder BS. Furthermore, the cutting tool B has a protrusion BB at its rear end. The protrusion BB is positioned on the side opposite to the cutting edge BE. The protrusion BB protrudes upward relative to the rest of the upper edge of the cutting tool B.

[0046] Figure 10A This is a central longitudinal sectional view of the tool holder 102 (tool mounting state). Figure 10B This is a cross-sectional view of the central portion of the retaining pin 113 of the tool retaining part 102 (tool mounting state). Figure 11A This is a central longitudinal sectional view of the tool holder 102 (tool removed state). Figure 11B This is a cross-sectional view of the central portion of the retaining pin 113 of the tool retaining part 102 (tool mounting state). If the rear end of the cutter B does not enter the slit 120 ( Figure 9A , Figure 9B The front end of the push pin 110 enters the left side of the retaining pin 113. The retaining pin 113 moves to the left and enters the retracted state. In addition, the exposed portion 115A of the auxiliary pin 115 is adjacent to the second end 116Y of the second protrusion 116F.

[0047] Furthermore, when the rear end of the tool B enters the slit 120, the push pin 110 is pushed backward by the shoulder BS of the tool B, overcoming the force applied by the compression spring 111. As the rear end of the tool B moves further rearward, positioning the retaining hole BH of the tool B to the right of the retaining pin 113, the cam surface 116C of the cam sleeve 116 overcomes the force applied by the compression spring 114 of the retaining pin, pushing the retaining pin 113 to the left. That is, the cam sleeve 116 is stressed by the torsion spring 119 via the auxiliary sleeve 118. The direction of the torsion spring 119 is the mounting direction C. Then, when the retaining hole BH of the tool B is to the left of the retaining pin 113 and the retaining pin 113 can move to the left, the cam sleeve 116 rotates in the mounting direction C. The curved surface 113C of the retaining pin 113 then contacts a further inwardly protruding portion of the cam surface 116C (a portion with a further reduced diameter, approaching the minimum diameter portion of the cam surface 116C). Therefore, the retaining pin 113 is pushed to the left by the cam surface 116C. The portion of the retaining pin 113 that is pushed to the left, relative to the left side of the step 113S, enters the retaining hole BH of the tool B, thereby retaining (installing) the tool B (tool installed state). Figure 10A , Figure 10B ). Therefore, as long as the tool B is inserted into the slit 120, the tool B can be automatically held in place (one-click installation). With the tool B held in place by the retaining pin 113, the protrusion 134 of the cam sleeve 116 is positioned on the right side by the rotation of the cam sleeve 116. In addition, the exposed portion 115A of the auxiliary pin 115 is adjacent to the first end portion 116X of the second protrusion 116F.

[0048] The protrusion BB of the tool B held in the tool holder 102 abuts against the front end face of the guide sleeve 112. The guide sleeve 112 is fixed by an auxiliary pin 115, which is different from the retaining pin 113, to suppress movement and rotation relative to the sliding body 100 in the front-rear direction. Additionally, the retaining pin 113 is disposed within the first retaining pin hole 122 with an expanded diameter on the left side.

[0049] Furthermore, the tool B held in the tool holding part 102 is removed from the tool holding part 102 by means of the release mechanism 7. The release mechanism 7 has a release cylinder 140, a tension spring 142 as an elastic component, and multiple (two) ring springs, namely ring spring 144A and ring spring 144B.

[0050] The release cylinder 140 is cylindrical and is disposed around the cam sleeve 116. The release cylinder 140 is adjacent to the tool holder 102. The release cylinder 140 is an operating cylinder operated by the user to remove (release) the tool B from the tool holder 102. The release cartridge 140 is made of synthetic resin. Therefore, it offers better resistance to external electric shock compared to cases where the release cartridge 140 and surrounding components are made of metal. Furthermore, even if the release cartridge 140 has a complex shape, it is easier to form.

[0051] The release cylinder 140 has a release cylinder body 140M, an inner raised part 148, an operating plate 150, and a locking part 154. The inner bulge 148 is disposed on the inner surface of the release cylinder 140 and protrudes radially inward more than other portions of the inner surface of the release cylinder 140. The inner bulge 148 is disposed on the right side of the release cylinder 140. The operating plate 150 is positioned on the right side of the release cylinder 140. The operating plate 150 is located radially outward of the inner raised portion 148. The operating plate 150 protrudes radially outward relative to the other outer surfaces. The operating plate 150 has a trapezoidal cross-section. The top of the operating plate 150 is thinner than its root. In the tool standby state, the operating plate 150 extends from the upper left to the lower right, and also extends back and forth. The operating plate 150 is integrally formed with the other parts of the release cylinder 140 (the cylindrical release cylinder body 140M). The operating plate 150 extends to the right from the first operating plate hole 20H of the power transmission housing 20 and the second operating plate hole 22H of the cover 22. A locking portion 154 is disposed on the outer side of the upper right portion of the release cylinder 140. The locking portion 154 protrudes radially outward relative to the other outer surfaces. The locking portion 154 has a hook shape. The locking portion 154 is integrally formed with the main body portion 140M of the release cylinder. Furthermore, a circular groove 140G1 is formed on the front part of the outer surface of the release cylinder body 140M. The groove 140G1 is recessed radially inward relative to the adjacent part in the release cylinder body 140M. The virtual plane containing the groove 140G1 is orthogonal to the virtual central axis of the release cylinder body 140M. On the other hand, a circular groove 140G2 is formed on the rear part of the outer surface of the release cylinder body 140M. The groove 140G2 is recessed radially inward relative to the adjacent part in the release cylinder body 140M. The virtual plane containing the groove 140G2 is orthogonal to the virtual central axis of the release cylinder body 140M. Furthermore, a flange portion 140F is formed at the front end of the release cylinder body portion 140M, which extends radially outward relative to the adjacent portion. A groove 140G on the front side is disposed on the rear side of the flange portion 140F.

[0052] The tension spring 142 is a helical spring. The tension spring 142 is disposed on the circumferential outer side of the release cylinder 140 and extends circumferentially along the main body 140M of the release cylinder. The tension spring 142 is disposed on the upper side of the main body 140M of the release cylinder. The first end of the tension spring 142 has a hook shape and is locked in the locking portion 154 of the release cylinder 140. The second end of the tension spring 142 has a hook shape and is fixed to the upper power transmission housing 20a.

[0053] The annular spring 144A, as a ring component, is an elastic body and a single-turn spring. The width of the annular spring 144A in the front-to-back direction is 1 mm. The annular spring 144A is made of iron (including alloys), more specifically, of stainless steel. When viewed from the front, the annular spring 144A is C-shaped and has a gap; it is not a completely closed ring. The annular spring 144A is embedded in the groove 140G1 of the release cylinder 140. The radially inner portion of the annular spring 144A enters the groove 140G1. The radially outer portion of the annular spring 144A protrudes radially outward from the groove 140G1. The annular spring 144B, as a ring component, is an elastic body and is a single-turn spring. The width (width) of the annular spring 144B in the front-to-back direction is 1 mm. The annular spring 144B is made of iron (including alloys), more specifically, of stainless steel. When viewed from the front, the annular spring 144B is C-shaped and has a gap; it is not a completely closed ring. The annular spring 144B is embedded in the groove 140G2 of the release cylinder 140. The radially inner portion of the annular spring 144B enters the groove 140G2. The radially outer portion of the annular spring 144B protrudes radially outward from the groove 140G2. Furthermore, the configuration of the gaps in at least one annular spring 144A, 144B is not limited to... Figure 4 The configuration is shown. At least one annular spring 144A, 144B can be a fully closed ring or a spring with more than one turn. Furthermore, at least one annular spring 144A, 144B may be non-elastic or may be attached to the release cylinder 140 by adhesive or the like. Moreover, at least one annular spring 144A, 144B can be made of iron other than stainless steel, or a metal other than iron. Furthermore, at least one annular spring 144A, 144B can also be disposed on the inner surface of the power transmission housing 20. There can be one annular spring 144A, 144B, or more than three.

[0054] With the tension spring 142 slightly extended from its natural length, the inner bulge 148 of the release cylinder 140 does not contact the protrusion 134 of the cam sleeve 116 in the tool mounting state. At this time, the operating plate 150 of the release cylinder 140 contacts the lower ends of the first operating plate hole 20H and the second operating plate hole 22H. The rotational position of the release cylinder 140 at this time is the initial rotational position of the release cylinder 140. In addition, the tension spring 142 may also be in other states such as its natural length state at this time. By operating the lower operating plate 150 upwards, the user can cause the release cylinder 140 to rotate about its virtual central axis in the front-rear direction, overcoming the force applied by the tension spring 142. In this case, the operating plate 150 rotates to its maximum position until it contacts the upper ends of the first operating plate hole 20H and the second operating plate hole 22H. This rotation of the release cylinder 140 causes the inner bulge 148 to contact the protrusion 134 of the cam sleeve 116, causing the protrusion 134 to rotate and the cam sleeve 116 to rotate in the opposite direction to the mounting direction C. This rotation of the cam sleeve 116 causes the curved surface 113C of the retaining pin 113 to be positioned inside the larger diameter portion of the cam surface 116C. The retaining pin 113 is retracted to the right by the force applied by the compression spring 114, thus exiting (removing) from the retaining hole BH of the tool B. Therefore, the push pin 110 moves forward by the force applied by the compression spring 111, pushing the removed tool B forward and into the right side of the retaining pin 113. Figure 11A , Figure 11B By pushing the recess 110D at the front end of the push pin 110, the push pin 110 can smoothly enter the right side of the retaining pin 113. Therefore, the release cylinder 140 of the release mechanism 7 is linked to the inner tool holding part 102, and by operating the operating plate 150 upward, the tool B is released from the tool holding part 102. The rotation of the protrusion 134 is the action of removing the tool B from the tool holding part 102, that is, the removal action of the tool holding part 102. The removal action is an action related to the installation and removal of the tool B. The release mechanism 7 (release cylinder 140) operates the removal action of the tool holding part 102 by rotating itself. In addition, the protrusion 134 of the tool holding part 102 can also perform actions related to the installation of the tool B. In addition, the operating cylinder can also operate actions related to the installation of the tool B. When the push pin 110 enters the right side of the retaining pin 113, it inhibits the rightward movement of the retaining pin 113. Therefore, the retaining pin 113 overcomes the force exerted by the torsion spring 119 in the mounting direction C, thereby inhibiting the rotation of the cam sleeve 116 in the mounting direction C. The release cylinder 140 returns downward by the force applied by the tension spring 142. Furthermore, in the reciprocating saw 1 according to the embodiments of the present invention, the user can install the blade B in a single operation. However, as another type of product, there is a known product that requires the operating cylinder to be rotated when the user installs the blade B. In such a product, the component corresponding to the retaining pin 113 that enters the retaining hole BH of the blade B only retracts from the retaining hole BH when the user rotates the operating cylinder. If the user only inserts the blade B for installation, the component corresponding to the retaining pin 113 will not retract. In such a product, since the operating cylinder is operated during the installation and release of the blade B, the operating cylinder operates at a higher frequency than in the reciprocating saw 1. Therefore, compared to the reciprocating saw 1, there is a greater need to suppress the deterioration of the operating cylinder's movement. That is, in products where the operating cylinder is also operated when installing the blade B, there is a greater need to include a mechanism for suppressing the deterioration of the operating cylinder's movement as used in the reciprocating saw 1.

[0055] Figure 12A This is a central longitudinal sectional view of the tool holder 102 (holding pin in bottom contact state). Figure 12B This is a cross-sectional view of the central portion of the retaining pin 113 of the tool retaining part 102 (retaining pin in bottom contact state). Due to factors such as the type of tool B and at least one of the vibrations, sometimes the push pin 110 cannot be pushed to its right side by the retaining pin 113 even though the tool B has not entered the tool holder 102. In this case, the head 113H of the retaining pin 113 is located at the end of the cam surface 116C in the direction opposite to the mounting direction C, and the retaining pin 113 is in a state where it is pushed to the right by the inner surface of the cam sleeve 116 other than the cam surface 116C (bottoming out state). In the bottoming-out state, due to at least one of the following factors, such as wear on the inner surface of the cam sleeve 116 and deviation in installation accuracy, the cam sleeve 116 may... Figure 12A , Figure 12B The state shown further indicates that the pin 113 is rotating freely in the opposite direction to the mounting direction C. If such free rotation occurs, causing the protrusion 134 to move to the left of the inner bulge 148 (the side that moves from the inner bulge 148 towards the mounting direction C) past the inner bulge 148 of the release cylinder 140, the inner bulge 148 will not touch the protrusion 134 even if the operating plate 150 of the release cylinder 140 is operated, thus making it impossible to perform the release operation of the tool B. However, in the reciprocating saw 1, such idling is suppressed by the contact between the exposed portion 115A of the auxiliary pin 115 and the first end 116X of the second extension portion 116F. Therefore, in the reciprocating saw 1, it is possible to suppress the situation where the holding pin 113 becomes bottomed out and spins further, thereby suppressing the situation where the release operation can no longer be performed.

[0056] Figure 13 This is an exploded perspective view of the front of the upper power transmission housing 20a, the release mechanism 7, and the front of the lower power transmission housing 20b, viewed from above. Figure 14 This is an exploded perspective view of the front of the upper power transmission housing 20a, the release mechanism 7, and the front of the lower power transmission housing 20b, viewed from below. The release mechanism 7 is located inside the cylindrical front end of the power transmission housing 20. A first upper groove 160U, extending laterally in a semi-circular arc shape, is formed on the inner surface of the front end of the upper power transmission housing 20a. The first upper groove 160U is recessed radially outward relative to the adjacent portion. Half of the flange portion 140F of the release cylinder 140 enters the first upper groove 160U. Furthermore, a second upper groove 162U, extending laterally in a semi-circular arc shape, is formed behind the first upper groove 160U. The second upper groove 162U is recessed radially outward relative to the adjacent portion. The tension spring 142 enters the second upper groove 162U. A first upper cylindrical strip 164U, in a semi-circular arc shape, is formed between the first upper groove 160U and the second upper groove 162U. Multiple (two locations) weight-reducing portions 165U are provided behind the second upper groove 162U. Furthermore, a second upper cylindrical strip 166U, in a semi-circular arc shape, is arranged behind the weight-reducing portions 165U. Furthermore, an upper semi-circular arc wall 167U and a wall 168 are disposed behind the second upper cylindrical belt portion 166U, wherein the upper semi-circular arc wall 167U protrudes radially inward in a semi-circular arc shape; the wall 168 has a central hole and extends upward, downward, left, and right. A plurality of (two) ventilation holes 169 arranged in a left-right manner are formed between the upper semi-circular arc wall 167U and the wall 168. A first lower groove 160D, extending laterally in a semi-circular arc shape, is formed on the inner front surface of the lower power transmission housing 20b. The first lower groove 160D is recessed radially outward relative to the adjacent portion. Half of the flange portion 140F of the release cylinder 140 enters the first lower groove 160D. A vertically oriented hole 160H is provided at the lower end of the first lower groove 160D. Through the hole 160H, chips and the like that entering the first upper groove 160U and the first lower groove 160D are discharged downward. In addition, a second lower groove 162D, extending laterally in a quarter-circular arc shape, is formed behind the first lower groove 160D. The second lower groove 162D is recessed radially outward relative to the adjacent portion. The second lower groove 162D is disposed on the left side of the lower power transmission housing 20b. The locking portion 154 of the release cylinder 140 enters the second lower groove 162D. A semi-circular arc-shaped first lower cylindrical strip 164D is formed between the first lower groove 160D and the second lower groove 162D. A weight-reducing section 165D is provided behind the second lower groove 162D. Furthermore, a semi-circular arc-shaped second lower cylindrical strip 166D is disposed behind the weight-reducing section 165D. And, a semi-circular arc-shaped lower semi-circular wall 167D protruding radially inward in a semi-circular arc shape is disposed behind the second upper cylindrical strip 166D. The first upper groove 160U and the first lower groove 160D face each other and are continuous. The second upper groove 162U and the second lower groove 162D face each other and are continuous. The first upper cylindrical belt 164U and the first lower cylindrical belt 164D face each other and are continuous. The second upper cylindrical belt 166U and the second lower cylindrical belt 166D face each other and are continuous. The upper semi-circular arc wall 167U and the lower semi-circular arc wall 167D face each other and are continuous. The first upper groove portion 160U and the first lower groove portion 160D, the first upper cylindrical belt portion 164U and the first lower cylindrical belt portion 164D, and the second upper groove portion 162U and the second lower groove portion 162D are adjacent to each other in the front-back direction.

[0057] The main body of the release cylinder 140M is positioned behind the first upper groove 160U and the first lower groove 160D and in front of the upper semicircular arc wall 167U and the lower semicircular arc wall 167D. The front annular spring 144A, made of iron, abuts against the first upper cylindrical belt 164U and the first lower cylindrical belt 164D, made of aluminum. The rear annular spring 144B, made of iron, abuts against the second upper cylindrical belt 166U and the second lower cylindrical belt 166D, made of aluminum. The release cylinder 140 contacts the power transmission housing 20 via the two annular springs 144A and 144B, but essentially does not contact the power transmission housing 20. These contacts are maintained even during rotation of the release cylinder 140. These contact mechanisms prevent chips from intruding behind the front annular spring 144A and in front of the rear annular spring 144B. Furthermore, even if chips exist between the release cylinder body 140M and the power transmission housing 20, the release cylinder body 140M contacts the power transmission housing 20 via the two annular springs 144A and 144B, ensuring the contact area is linear and smaller than in surface contact. This prevents the release cylinder 140 from getting caught in chips and becoming difficult to rotate. Additionally, if the release cylinder 140, made of synthetic resin, has a large contact area with the aluminum power transmission housing 20, the portion of the release cylinder 140 in contact with the power transmission housing 20 may melt over time. However, in the reciprocating saw 1, since the metal annular springs 144A and 144B contact the power transmission housing 20, melting of the release cylinder 140 is prevented. In view of at least one of the viewpoints of reducing the contact area and suppressing the melting of the synthetic resin release cylinder 140, the width of at least one of the annular springs 144A and 144B can be set to less than 4 mm, or less than 3 mm, less than 2 mm, or less than 1 mm. Furthermore, one or more sealing components, such as elastic rings, for inhibiting chip ingress can be provided separately from the annular springs 144A and 144B. Additionally, at least one of the first upper cylindrical belt portion 164U and the first lower cylindrical belt portion 164D, and the second upper cylindrical belt portion 166U and the second lower cylindrical belt portion 166D, can have radial irregularities, and at least one of the annular springs 144A and 144B can also contact the convex portion facing inward. In this case, the contact area is further reduced.

[0058] The counterweight mechanism 9 is combined with the reciprocating motion conversion mechanism 5. The counterweight mechanism 9 has a metal balancer 170 and a ring 172. The balancer 170 is a plate-shaped device extending forward, backward, left, and right, and has an elongated hole 174 extending in the left-right direction at its center. The portion of the balancer 170 that is forward of the elongated hole 174 is heavier than the portion that is backward of the elongated hole 174. The engagement portion 97 of the crank cam 78 enters the elongated hole 174 of the balancer 170 via the ring 172. The balancer 170 reciprocates in the front-to-back direction due to the rotation of the crank cam 78. The connecting portion 97 is positioned on the side opposite to the barrel roller 94, across the center of the crank cam body 90. More specifically, the connecting portion 97 and the barrel roller 94 form an angle of approximately 175° with respect to the front-to-back and left-to-right centers of the crank cam body 90. Therefore, the portion of the balancer 170 forward of the elongated hole 174 moves substantially in the front-to-back direction in the opposite direction to the slider 6. Thus, vibrations generated by the reciprocating motion of the slider 6 are suppressed by the balancer 170. That is, the balancer 170 acts as a counterweight by moving in the opposite direction to the front-to-back movement of the slider 6. Furthermore, the left-to-right component of the movement of the connecting portion 97 becomes a relative movement of the connecting portion 97 within the elongated hole 174 and is not transmitted to the balancer 170. The angle between the connecting portion 97 and the barrel roller 94 can be 180° or other angles.

[0059] The track mechanism 12 has a sliding support body 180, multiple (two) oilless bearings 181 as sliding support bodies, multiple (two) plates 182, a sliding support shaft 183, multiple springs 184 as elastic bodies, bearings 186 and multiple screws 190. The sliding bracket body 180, each oilless bearing 181, each plate 182, bearing 186, and each screw 190 constitute a cylindrical sliding bracket 191. Alternatively, bearings 186 and the like can be removed from the structural elements of the sliding bracket 191. Furthermore, the structural elements of the sliding bracket 191 may include at least one of a sliding bracket shaft 183 and each spring 184.

[0060] The sliding bracket body 180 is made of metal and is box-shaped, extending in the front-to-back direction. The oilless bearing 181 is held at the front and rear sides within the sliding support body 180. The cross-sectional shape of the oilless bearing 181 is square. The sliding member 6 passes through each oilless bearing 181 in a reciprocating manner. An opening is provided in the lower central portion of the sliding member support body 180, in the portion including the area where the barrel roller 94 and the barrel roller bearing portion 104 can be installed. Each oilless bearing 181 is disposed on the front and rear sides of this opening. The rear plate 182 is fixed to the lower rear of the slider bracket body 180 by a plurality of vertical (two horizontal) screws 190 and is fixed to the lower side of the rear oilless bearing 181. The rear plate 182 is made of metal and extends forward, backward, left, and right. The slider bracket body 180 holds the rear oilless bearing 181 from above. The rear plate 182 holds the rear oilless bearing 181 from below. The front plate 182 is fixed to the lower front of the sliding member bracket body 180 and to the lower side of the front oilless bearing 181 by a plurality of vertical (two horizontal) screws 190. The front plate 182 is made of metal and extends forward, backward, left, and right. The sliding member bracket body 180 holds the front oilless bearing 181 from above. The front plate 182 holds the front oilless bearing 181 from below. Additionally, plate 182 and screw 190 can be omitted.

[0061] The slider support shaft 183 passes through the left and right holes 162 located at the lower front part of the slider support body 180. The slider support 191 is able to swing around the slider support shaft 183. Each spring 184 is disposed on the left and right sides of the upper rear part of the sliding member support body 180. Each spring 184 extends in the vertical direction. The upper end of each spring 184 is held on the inner surface of the rear part of the upper power transmission housing 20a.

[0062] The bearing 186 is located behind the opening in the lower part of the sliding member support body 180 and in front of the plate 182. The bearing 186 is a ball bearing. The inner ring of bearing 186 is held against the outer surface of oilless bearing 181. The outer ring of bearing 186 is able to contact the cam portion 98 of crank cam 78.

[0063] The track switching mechanism 14 has a track switching rod 192 as a track switching component. The track switching lever 192 has a lever body 193 as an axle and a gripper 194.

[0064] The main body 193 is a rod extending to the left and right, and is also axial. The track switching lever 192 is held in the upper power transmission housing 20a in a state where it can rotate about the virtual central axis of the lever body 193. The virtual central axis of the lever body 193 is parallel to the plate 182 it contacts. The rod body 193 has a first plane 196 extending left and right as a support surface and a second plane 198 extending left and right as a second track state surface. The first plane 196 and the second plane 198 form a predetermined angle (approximately 100° in this case). The distance from the virtual central axis to the first plane 196 is greater than the distance from the virtual central axis to the second plane 198. With the track in its first state (first track state), the track switching lever 192 is positioned such that the first plane 196 can contact the lower rear part (rear plate 182) of the sliding bracket 191. When the track switching lever 192 contacts the plate 182, the first plane 196 and... Figure 3 The difference lies in the horizontal configuration. On the other hand, when the orbit is in state 2 Figure 3 In the second track state, the track switching lever 192 is horizontally positioned on the second plane 198 and faces the lower rear part of the slider bracket 191 at a distance. In this state, the bearing 186 of the track mechanism 12 is in full circumferential contact with the cam surface 99 of the cam portion 98.

[0065] In the second track state, due to the downward force applied by each spring 184, the bearing 186 also contacts the lowest point of the cam surface 99 in the cam portion 98. Even at this time, the second plane 198 of the rod body 193 is still away from the lower rear part of the slider support 191. Thus, the slider support 191, slider 6, and cutter B face upward (front high, rear low). In addition, the bearing 186 also contacts the highest point of the cam surface 99. Thus, the bearing 186 is pushed upward by the cam surface 99 against the force applied by each spring 184, and the slider support 191, slider 6, and cutter B face downward (front low, rear high). The height of the portion between the lowest and highest points in the cam surface 99 gradually changes in the circumferential direction. Therefore, with the rotation of the crank cam 78, the bearing 186, which follows the cam surface 99, moves up and down relatively. Therefore, the slider bracket 191, the slider 6, and the tool B repeatedly move in the following states: front high and back low, along the front and back direction, front low and back high, and along the front and back direction. The tool holder 102 moves in an elliptical orbit. The orbital motion is correlated with the reciprocating motion of the slider 6 based on the circumferential distribution of the height of the cam surface 99 in the crank cam 78. Here, the height distribution of the cam surface 99 is adjusted so that when the slider 6 moves forward, it is in a forward-high, backward-low state; when the slider 6 switches from a forward-to-backward movement direction (or passes near the switching point), it is in a forward-backward state; when the slider 6 moves backward, it is in a forward-low, backward-high state; and when the slider 6 switches from a backward-to-forward movement direction (or passes near the switching point), it is in a forward-backward state. Even if the orientation of the slider bracket 191 and the slider 6 changes to upward or downward, the slider 6 will still reciprocate fully via the barrel roller 94.

[0066] On the other hand, in the first track state, the rear part of the slider support 191 is lifted by the first plane 196 of the rod body 193, so the bearing 186 does not contact the lowest point and its adjacent part in the cam surface 99. Therefore, compared with the second track state, the front-high-rear-low situation of the slider 6 is suppressed. In contrast, the bearing 186 contacts the highest point and its adjacent part of the cam surface 99. Furthermore, the bearing 186 contacts approximately half of the cam portion 98, but due to the first plane 196 of the rod body 193, the bearing 186 does not contact the remaining portion of the cam portion 98. Therefore, the transition from a state along the front-rear direction to a state with a lower front and higher rear when the slider 6 moves backward (the semi-elliptical track movement of the tool holder 102 when the slider 6 moves backward) occurs in the same way as in the second track state, but when the slider 6 moves forward, the slider 6 maintains a state approximately along the front-rear direction. Therefore, in the first track state, the tool holder 102 performs a semi-elliptical track movement.

[0067] In the first orbital state, the tool holder 102 moves within an orbital range of approximately half a circle (the first range). In contrast, in the second orbital state, the tool holder 102 moves within an orbital range of a full circle (the second range), which is larger than the approximately half-circle range (the first range). Furthermore, in the first orbital state, orbital motion may not occur throughout the entire range, or the range (ratio of presence / absence) of orbital motion may be altered, for example, orbital motion may occur in an elliptical arc within only one-quarter of the range, while orbital motion is absent in the remaining three-quarters. Similarly, in the second orbital state, orbital motion may be absent within a portion of the range. That is, if the range of orbital motion in the first orbital state (first range) is smaller than the range of orbital motion in the second orbital state (second range), the range of orbital motion can be varied.

[0068] The gripper 194 intersects with the main body 193 of the rod, and they are orthogonal here. The gripper 194 is positioned to the left of the power transmission housing 20 and the cover 22, and is exposed to the outside. The gripper 194 is positioned within the track switching rod hole 58 of the cover 22. Users can operate the gripper 194 to rotate the track switching lever 192 around the virtual central axis to switch the track status.

[0069] The guide shoe 16 is disposed adjacent to the tool B mounted on the tool holder 102. The guide shoe 16 is positioned in front of and below the slider 6. The guide shoe 16 has a guide shoe plate 200, a guide shoe bracket 206 and multiple (two) shafts 207. The guide shoe plate 200 can contact the workpiece. The guide shoe bracket 206 is positioned on the upper side of the guide shoe bracket cover 208. The guide shoe bracket 206 is disposed inside the guide shoe bracket cover 208 in a manner that allows it to slide back and forth. The guide shoe bracket cover 208 is fixed to the power transmission housing 20. Alternatively, the main housing 2 may be configured to include the guide shoe bracket cover 208, but it is also possible to treat it as a structure that does not include the guide shoe bracket cover 208. Each shaft 207 is positioned to the left and right of the front end of the guide shoe bracket 206. Each shaft 207 supports the guide shoe plate 200 in a manner that allows it to swing about an axis in the left-right direction. The cross-sections of the guide shoe bracket 206 and the guide shoe bracket cover 208 are both U-shaped. The guide shoe bracket 206 and the guide shoe bracket cover 208 are disposed between the lower front outer surface of the power transmission housing 20 and the lower front inner surface of the cover 22.

[0070] A guide shoe rod 210 is disposed on the outer side of the guide shoe support cover 208. The guide shoe rod 210 has a guide shoe support fixing shaft 212 in the left-right direction, which passes through the upper side of the guide shoe support cover 208 and the guide shoe support 206. The guide shoe rod 210 is rotatable about the guide shoe support fixing shaft 212 and is openable and closed relative to the guide shoe support cover 208. When the guide shoe rod 210 is closed (in the forward / backward direction as shown in the attached figure), the guide shoe bracket fixing shaft 212 secures the guide shoe bracket 206. Conversely, when the guide shoe rod 210 is open (in the up / down direction), the securing shaft 212 to the guide shoe bracket 206 is released. Therefore, the guide shoe bracket 206 and the guide shoe plate 200 can slide in the forward / backward direction, thereby allowing adjustment of the position of the guide shoe 16.

[0071] A vertically extending pin 214 is provided on the rear side of the guide shoe bracket fixing shaft 212. A spring 216, which is an elastic body, is clamped between the upper end of the pin 214 and the power transmission housing 20. The lower end of the pin 214 is located inside the lower surface of the cover 22. The pin 214 can be pushed up by the cover 22 by overcoming the elastic force of the spring 216. The lower part of pin 214 is thinner than the central part. When pin 214 is not raised, the central part of pin 214 interferes with the guide shoe bracket 206 that is to be advanced a predetermined distance, inhibiting the advancement of the guide shoe bracket 206 and thus preventing the guide shoe 16 from falling off. When pin 214 is raised, the interference of the central part of pin 214 with the guide shoe bracket 206 is eliminated, thereby enabling the guide shoe 16 to separate from the other parts of the reciprocating saw 1.

[0072] The action of this reciprocating saw 1 will be explained using an example. The user sets the tool holder 102 of the slider 6 to a stopped state by one-click installation. Typically, in order for the tool B to act on the workpiece from above, the tool B is set with the cutting edge BE (acting part) facing down. However, for example, in cases where the tool B acts on the workpiece from below, the tool B is sometimes set with the cutting edge BE facing up. The user adjusts the length of the guide shoe 16 appropriately so that the front surface of the guide shoe 16 abuts against the workpiece. The user then installs the charged battery 54 into the battery mounting section 50. Furthermore, the user operates the speed switching dial 36 to select the speed. Furthermore, when the user holds the first grip portion 30 (and the second grip portion 60) and pulls the trigger 33 to a predetermined position, the main switch body 34 is activated, supplying power to the motor 3 and causing the motor shaft 68 to rotate. The power supply to the motor 3 is provided by a DC power supply rectified by the control circuit board 42. Additionally, when the trigger 33 is pulled to a certain position or more, the lamp 62 illuminates. This certain position is less than the predetermined amount of power supplied to the motor 3. The microcomputer on the control circuit board 42 acquires the rotational state of the rotor 67. In addition, the microcomputer on the control circuit board 42 controls the switching elements to turn on and off according to the acquired rotational state, so that current flows through each coil 66C of the stator 66 in sequence, thereby causing the rotor 67 to rotate. The motor shaft 68 rotates at a speed corresponding to the signal (trigger 33 engagement amount) of the main switch body 34. The greater the engagement amount of the trigger 33, the higher the rotational speed of the motor shaft 68. In addition, the maximum rotational speed of the motor shaft 68 is controlled by the control circuit board 42 to a value corresponding to the rotational state of the speed switching dial 36. When the motor shaft 68 rotates, the crank cam 78 rotates via the bevel gear 70, torque limiting mechanism 72, intermediate shaft 74, and crank base 76, causing the slider 6 to move back and forth. Additionally, the balancer 170 moves in the opposite direction to the slider 6 in the back-and-forth direction, allowing the slider 6 to move back and forth while vibration is suppressed.

[0073] The slider 6 is guided by the front and rear oilless bearings 81 while it is suppressed in a direction other than that toward the slider support body 180. When the user moves the gripper 194 of the track switching lever 192 forward (refer to...) Figure 1 The second plane 198 of the main body 193 of the rod extends forward, backward, left, and right (see reference). Figure 3 ), and away from the rear plate 182. The bearing 186 of the track mechanism 12 follows relative to the cam surface 99 of the crank cam 78 over a full circumference, and in conjunction with the reciprocating motion of the slider 6, causes the slider support body 180 to oscillate. Thus, the track motion takes place throughout the entire reciprocating motion of the slider 6 (second track state). Furthermore, when the user lowers the gripper 194 of the track switching lever 192 backward, the first plane 196 of the lever body 193 extends forward, backward, left, and right, and is able to lift the rear plate 182. The bearing 186 of the track mechanism 12 follows relative to the cam surface 99 of the crank cam 78 for approximately half a cycle, and in coordination with the reciprocating motion of the slider 6 for only approximately half a cycle, it causes the slider support body 180 to swing, and does not contact the cam portion 98 for the remaining approximately half cycle, maintaining the posture of the slider support body 180. Therefore, the track movement occurs for approximately half of the reciprocating motion of the slider 6 (first track state).

[0074] When the slider 6 or the tool B is in the working state, when the user lowers the tool B toward the workpiece, the cutting edge BE of the back-and-forth moving tool B abuts against the workpiece to cut it. The second track state is suitable for cases where the workpiece is, for example, wood. Conversely, the first track state is suitable for cases where the workpiece is, for example, metal.

[0075] Furthermore, the rotation of the fan 4, which accompanies the rotation of the motor shaft 68, forces the air around the fan 4 radially outward. This generates an airflow (wind) within the main housing 2, cooling the various components within it. In particular, a portion of the airflow reaches the vents 169 via the space between the upper part of the power transmission housing 20 and the upper part of the cover 22, and further passes between the upper semi-circular arc wall 167U and the wall 168, branching into airflow directly downwards and airflow forwards from the lower side of the upper semi-circular arc wall 167U. This forward-facing airflow passes radially inwards through the main body of the release cylinder 140M.

[0076] When the user disconnects the main switch body 34 by operating trigger 33, the motor shaft 68 of motor 3 stops, and all forward and backward movements and airflow cease. Additionally, after a predetermined time, the light 62 turns off.

[0077] When the user operates the operating plate 150 of the release cylinder 140 upward when the slider 6 stops, the protrusion 134 of the tool holder 102 moves in an arc shape via the inner raised portion 148. Therefore, the tool B mounted on the tool holder 102 is removed by operating the operating plate 150.

[0078] Furthermore, the methods and modifications of the present invention are not limited to those described above. For example, the following modifications may be suitably implemented to the methods and modifications of the present invention. The trajectory motion (track motion) of the tool holder 102, etc., is not limited to elliptical and semi-elliptical shapes. For example, the trajectory motion can be a reciprocating (oscillating) motion along a virtual semi-elliptical arc.

[0079] When viewed from above, the cam portion 98 can be arc-shaped, straight, or curved. The cam portion 98 can be disposed on the lower surface of the crank cam 78. The cam portion 98 can also be disposed separately from the crank cam 78. A portion or all of the reciprocating motion conversion mechanism 5 and at least one of the track switching mechanism 14 (track switching rod 192) may be configured above the sliding support 191. The reciprocating motion conversion mechanism 5 can be configured as a mechanism using a crank and a connecting rod (connecting rod type), or it can be configured as a mechanism using a rotating body with an inclined cylindrical surface and a swashplate bearing disposed on the inclined cylindrical surface (swashplate type), instead of a mechanism using a crank cam 78 extending in the front, back, left, and right (horizontal crank type).

[0080] Cover 22 can be a split component having a left cover and a right cover. A needle roller bearing can be used instead of a ball bearing, or vice versa. At least one of the torque limiting mechanism 72 and the intermediate shaft 74 can be omitted. The battery 54 can be installed or removed in a direction other than the front-back direction. The number of installable batteries 54 can be multiple. Furthermore, at least one of the following aspects of the various components—the presence or absence, quantity, material, shape, form, and configuration—can be varied. The tip tool can be any tool other than cutter B. It can be powered by a power cord instead of battery 54. The power cord can be connected to a commercial power supply. The present invention and its variations can be applied to reciprocating cutting tools other than reciprocating saws (e.g., wire saws), as well as to reciprocating tools other than reciprocating cutting tools, power tools, gardening tools, and electric work machines.

Claims

1. A reciprocating cutting tool, characterized in that, It comprises a motor, a rod-shaped slider, a reciprocating motion conversion mechanism, a power transmission housing, a top tool holder, and an operating cylinder, wherein... The reciprocating motion conversion mechanism takes the extension direction of the slider as the front-back direction, converts the rotation of the motor into a reciprocating motion in the front-back direction and transmits it to the slider; The power transmission housing houses the reciprocating motion conversion mechanism; The top tool holding part is disposed at the front end of the slider, which can detach and install the top tool, and can perform actions related to the detachment and installation of the top tool. The operating cylinder is linked to the top tool holding part, and its own rotation operates the movement of the top tool holding part. The operating cylinder is rotatably held within the power transmission housing via an annular spring that contacts the power transmission housing. The contact between the annular spring and the power transmission housing is maintained during the rotation of the operating cylinder. The annular spring is disposed at the front and rear of the outer surface of the operating cylinder.

2. The reciprocating cutting tool according to claim 1, characterized in that, The action of the top tool holding part is the action of removing the top tool, that is, the removal action.

3. The reciprocating cutting tool according to claim 1 or 2, characterized in that, The tip tool holder has a protrusion. The movement of the tip tool holder is achieved by rotating the protrusion along the front-to-back axis. The operating cylinder has an inner bulge that protrudes inward and rotates about the axis in the front-back direction. The rotation of the protrusion is operated by the inner bulge.

4. The reciprocating cutting tool according to claim 1 or 2, characterized in that, A circular groove is formed on the outer surface of the operating cylinder. The radially inner portion of the annular spring enters the groove.

5. The reciprocating cutting tool according to claim 1 or 2, characterized in that, The operating cylinder has a flange portion. The power transmission housing has a first groove into which the flange enters and a cylindrical belt that contacts the annular spring.

6. The reciprocating cutting tool according to claim 5, characterized in that, The first groove and the cylindrical belt are adjacent to each other.

7. The reciprocating cutting tool according to claim 1 or 2, characterized in that, It has an elastic body that applies force to the operating cylinder toward the initial rotational position. The elastomer is disposed on the outside of the operating cylinder. The power transmission housing has a second groove into which the elastomer enters and a cylindrical belt portion into which the annular spring contacts.

8. The reciprocating cutting tool according to claim 7, characterized in that, The second groove and the cylindrical belt are adjacent to each other.

9. The reciprocating cutting tool according to claim 1 or 2, characterized in that, Two ring springs are provided.

10. The reciprocating cutting tool according to claim 9, characterized in that, The annular spring is disposed at the front and rear of the operating cylinder.

11. The reciprocating cutting tool according to claim 1 or 2, characterized in that, The width of the ring spring is less than 4 mm.

12. The reciprocating cutting tool according to claim 1 or 2, characterized in that, The tip tool has an action portion that acts on the workpiece, and is mounted on the tip tool holding portion with the action portion positioned on at least one of the lower and upper sides.

13. The reciprocating cutting tool according to claim 1 or 2, characterized in that, The ring spring is made of metal.

14. The reciprocating cutting tool according to claim 13, characterized in that, The ring spring is made of iron or an iron alloy.

15. The reciprocating cutting tool according to claim 1 or 2, characterized in that, The operating cylinder is made of synthetic resin.

16. The reciprocating cutting tool according to claim 1 or 2, characterized in that, The power transmission housing is made of metal.

17. The reciprocating cutting tool according to claim 16, characterized in that, The power transmission housing is made of aluminum or aluminum alloy.

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