CROSS-REFERENCE TO RELATED APPLICATION
This application claims priority to Japanese patent application serial number 2023-208457, filed on Dec. 11, 2023, the contents of which are incorporated herein by reference in their entirety for all purposes.
TECHNICAL FIELD
The present invention generally relates to a driving tool for driving a driving member into a workpiece.
BACKGROUND
For example, a driving tool which includes a driver for driving a driving member, a lift mechanism for moving a driver to a standby position and a top dead center, and an electric motor as a driving source of the lift mechanism is well known. A main body housing of the driving tool houses the driver, the lift mechanism, and the electric motor. The driving tool further includes a magazine for housing a plurality of driving members and a feed mechanism for feeding (loading) a driving member from the magazine to a driving passage one by one. The driver is configured to move within the driving passage. The magazine, which is formed in a cylindrical shape, is coupled to a driver guide that forms the driving passage on a lower side of the tool main body. The magazine houses, for example, a plurality of nails that are combined to each other and wound in a spiral manner.
The feed mechanism is arranged, for example, between the magazine and the driver guide outside of the main body housing. The feed mechanism includes a feed pawl for feeding a nail to the driving passage one by one and a check pawl for restricting the nail from returning to the magazine. The feed pawl is constantly biased toward the driving passage by, for example, a compression spring. The feed mechanism has a structure for moving the feed pawl in a direction opposite to a biasing direction of the compression spring. For example, the feed mechanism includes a solenoid. When the solenoid is turned on, the feed pawl moves in a direction opposite to a feeding direction (anti-feeding direction) to receive a next nail. When the solenoid is turned off, the feed pawl moves in the feeding direction together with the next nail. In this manner, a nail is supplied to the driving passage one by one.
In the prior art, the solenoid for feeding a driving member is arranged within the magazine or within a housing between the magazine and the driver guide. When the solenoid is turned on, a large current flows through a coil of the solenoid and accordingly the coil is heated. A fan is attached to the electric motor that is housed in the main body housing so as to be rotatable integrally with an output axis of the electric motor. The fan generates cooling air flow to cool off electric components in the tool main body such as, for example, the electric motor. In the prior art, it used to be difficult to cool off the solenoid by rotation of the fan because the solenoid is arranged outside of the main body housing. Accordingly, there is a room for improving a cooling efficiency to cool off the solenoid.
Furthermore, in the prior art, a plunger of the solenoid needs the same stroke length as a moving distance of the feed pawl in the anti-feeding direction. Therefore, there is a room for shortening a reciprocating time of the plunger. When a stroke length of the plunger is long and a protruding length of the plunger is large, a length of the plunger (iron core) that is inserted to the coil becomes short. Accordingly, when the protruding length of the plunger is large, an output of the solenoid decreases. Therefore, there is a room for maintaining a high output of the solenoid.
Thus, there is a need for the driving tool to efficiently cool off the solenoid that loads a driving member within the magazine to the driving passage.
SUMMARY OF THE DISCLOSURES
According to one aspect of the present disclosure, a driving tool comprises a driver driven by an electric motor, and a driver guide for guiding a movement of the driver, and a magazine for housing a plurality of driving members. The driving tool also comprises a feed pawl for feeding (loading) the plurality of driving members from the magazine to the driver guide one by one, a power transmission member being interlocking with a movement of the feed pawl, and a solenoid configured to move the feed pawl via the power transmission member. The solenoid is arranged in a main body housing outside of the magazine.
Because of this configuration, the solenoid for feeding the driving member within the magazine to the driving passage in the driver guide is arranged in the main body housing. Because of this configuration, the solenoid can be arranged on a flow passage of a cooling air for cooling off, for example, the electric motor. Accordingly, the solenoid can be efficiently cooled off, thereby suppressing a temperature rise of the solenoid. Furthermore, the arrangement of the power transmission member between the solenoid and the feed pawl can efficiently transmit the output of the solenoid to the feed pawl 31.
BRIEF DESCRIPTION OF DRAWINGS
FIG. 1 is a perspective view of a driving tool according to a first embodiment of the present disclosure.
FIG. 2 is a right side view of the driving tool without a right housing.
FIG. 3 is a cross-sectional view of the driving tool viewed from the right when a driver is at a standby position.
FIG. 4 is a left side view of the driving tool without a left housing.
FIG. 5 is a longitudinal cross-sectional view of a tool main body when the driver is at the standby position.
FIG. 6 is a longitudinal cross-sectional view of the tool main body when a driving member is supplied to a driving passage.
FIG. 7 is an enlarged right side view of the driving tool without the right housing and a driver guide when the driver is at the standby position.
FIG. 8 is an enlarged right side view of the driving tool without the right housing and the driver guide when a solenoid is turned on.
FIG. 9 is an enlarged right side view of the driving tool without the right housing and the driver guide when the driving member is supplied to the driving passage.
FIG. 10 is an enlarged bottom view of the driving tool without the right housing and the driver guide when the driver is at the standby position.
FIG. 11 is an enlarged bottom view of the driving tool without the right housing and the driver guide when the solenoid is turned on.
FIG. 12 is an enlarged bottom view of the driving tool without the right housing and the driver guide when the driving member is supplied to the driving passage.
FIG. 13 is a perspective view of the solenoid, a power transmission member, and a feeding claw.
FIG. 14 is a bottom view of the solenoid, the power transmission member, and the feeding claw.
FIG. 15 is a perspective view of a driving tool according to a second embodiment of the present disclosure.
FIG. 16 is a cross-sectional view taken along line XVI-XVI of FIG. 5, showing the driving tool according to the second embodiment.
FIG. 17 is a cross-sectional view taken along line XVII-XVII of FIG. 5, showing a driving tool according to a third embodiment of the present disclosure.
FIG. 18 is a perspective view of a driving tool according to a fourth embodiment of the present disclosure.
FIG. 19 is a right side view of the driving tool without a right housing according to the fourth embodiment.
DETAILED DESCRIPTION
The detailed description set forth below, when considered with the appended drawings, is intended to be a description of exemplary embodiments of the present disclosure and is not intended to be restrictive and/or representative of the only embodiments in which the present disclosure can be practiced. The term “exemplary” used throughout this description means “serving as an example, instance, or illustration,” and should not necessarily be construed as preferred or advantageous over other exemplary embodiments. The detailed description includes specific details for the purpose of providing a thorough understanding of the exemplary embodiments of the disclosure. It will be apparent to those skilled in the art that the exemplary embodiments of the disclosure may be practiced without these specific details. In some instances, these specific details refer to well-known structures, components, and/or devices that are shown in block diagram form in order to avoid obscuring significant aspects of the exemplary embodiments presented herein.
According to one aspect of the present disclosure, the power transmission member is supported by the main body housing such that the power transmission member is rotatable around a rotation support, and the power transmission member is coupled to the feed pawl via a pawl coupling portion. A plunger of the solenoid is connected to the power transmission member between the rotation shaft and the pawl coupling portion. In other words, a part of the power transmission member is arranged between the plunger of the solenoid and the feed pawl. Also, the plunger is coupled to the power transmission member between the rotation support and the pawl coupling portion. Because of this configuration, a short stroke of the plunger can move the feed pawl by utilizing the principle of leverage. Also, a rapid movement of the feed pawl can be obtained. Furthermore, the short stroke of the plunger can make a length of the plunger inserted into the coil to be maintained as long as possible even when the plunger is most protruded (and retracted). Accordingly, the output of the solenoid can be highly maintained.
According to another aspect of the present disclosure, the driving tool further comprises a biasing member for biasing the feed pawl toward the driver guide. The solenoid moves the feed pawl in a direction opposite to a biasing direction of the biasing member when the solenoid is turned on. Accordingly, the feed pawl is constantly biased on a side of the driver guide (in a feeding direction) by the compression spring. The solenoid is turned on only when the next driving member is to be received by the feed pawl. Thus, a driving time of the solenoid is made short and also the driving member can be supplied to the driving passage of the driver guide one by one in a reliable manner.
According to another aspect of the present disclosure, the main body housing includes a motor housing for housing the electric motor, and the solenoid is housed in the motor housing between the electric motor and the magazine. The solenoid and the electric motor are housed in the mechanism case. The solenoid and the electric motor can be cooled off by a cooling mechanism such as, for example, the fan. The magazine is arranged with respect to the main body housing in a position where the driving member is supplied within the driver guide. Accordingly, a space is needed between the electric motor and the magazine. The solenoid can be arranged by utilizing the space, thereby making the driving tool compact.
According to another aspect of the present disclosure, the main body housing includes a fan to generate a cooling air flow through an air passage in the main body housing, and the solenoid is arranged in the air passage. The solenoid is arranged in the air passage in which the air flow generated by the fan flows, thereby efficiently cooling off the solenoid in an improved manner.
According to another aspect of the present disclosure, the solenoid is arranged on an upstream side of the air passage with respect to the electric motor. Accordingly, the cooling air flow cools off the solenoid at first and then the electric motor. A driving time of the electric motor in the driving tool is short because the electric motor is activated only when the driver moves to the standby position or to the top dead center. On the contrary, a quantity of heat generated in the coil is large though the driving time of the solenoid is short. The solenoid, which generates a large quantity of heat, is cooled off at first, thereby efficiently cooling off the electric components including the solenoid and the electric motor in an improved manner.
According to another aspect of the present disclosure, the main body housing includes a motor housing for housing the electric motor. The motor housing includes a motor housing compartment for housing the electric motor and a solenoid housing compartment for housing the solenoid. The motor housing compartment communicates with (connects to) the solenoid housing compartment via a communication passage. Because of this configuration, the air passage can be formed such that the cooling air flow for cooling off the electric motor and the solenoid passes through the communication passage. Accordingly, the cooling air flow can be guided such that the electric motor and the solenoid are efficiently cooled off in an improved manner.
According to another aspect of the present disclosure, the main body housing includes an inlet ports arranged either in a first wall through which a plunger of the solenoid passes or in a second wall facing a coil of the solenoid. In other words, the inlet ports are formed such that the outside air taken from the inlet ports easily flows to the coil of the solenoid, thereby efficiently cooling off the solenoid in an improved manner.
According to another aspect of the present disclosure, the air passage includes a first air passage for the cooling air flow passing through to cool off outside of the electric motor and a second air passage for the cooling air flow passing through to cool off inside of the electric motor. The first air passage communicates with the second air passage. Accordingly, the electric motor is cooled off both from the outside and the inside, thereby efficiently cooling the electric motor.
According to another aspect of the present disclosure, the driving tool further comprises a piston connected to the driver, and a cylinder configured such that the piston is movable within the cylinder. A pressure of a gas in the cylinder increases by a movement of the driver in a direction opposite to the driving direction. Accordingly, in the so-called gas-spring type driving tool, the solenoid for feeding the driving member can be arranged in a position where the solenoid is efficiently cooled off.
Next, a first embodiment of the present disclosure will be explained with reference to FIGS. 1 to 14. As an example of a driving tool 1, a gas-spring type driving tool, which utilizes a pressure of the gas filled in an accumulation chamber as a thrust force for driving a driving member, is exemplified. In the following explanation, a driving direction of the driving member is a downward direction and a direction opposite to the driving direction is an upward direction. A user of the driving tool 1 is generally situated on a right side of the driving tool 1 in FIG. 1. Also, in FIG. 1, a nearer side of the user is referred to as a rearward direction and a direction opposite to the rearward direction is a forward direction. A leftward/rightward direction is based on the user's position.
As shown in FIGS. 2 and 3, the driving tool 1 includes a tool main body 10 and a main body housing 11 for covering the tool main body 10. The main body housing 11 houses a cylinder 13 extending in an up-down direction. The cylinder 13 houses a piston 15 so as to be reciprocated in the up-down direction. An upper end of the cylinder 13 communicates with (connects to) an accumulation chamber 14. A compressed gas such as, for example, an air, is filled in the accumulation chamber 14. The pressure of the gas filled in the accumulation chamber 14 acts as a thrust force for biasing an upper surface of the piston 15 to move in a downward direction.
As shown in FIGS. 5 and 6, a right portion of the accumulation chamber 14 communicates with (connects to) an air chamber 14a which extends downward along a right side surface of the cylinder 13. The air chamber 14a is mainly arranged above a lift mechanism 23, overlapping with a part of the lift mechanism 23 in a left-right direction. The lift mechanism 23 is discussed later in detail. By arranging the air chamber 14a on the right side of the cylinder 13, a capacity of the accumulation chamber 14 including the air chamber 14a increases without enlarging the tool main body 10 in the up-down direction.
As shown in FIGS. 1 to 6, a driving nose 2 is arranged at a lower portion of the tool main body 10. The driving nose 2 includes a driver guide 4 extending in the up-down direction. Driving passages 2a and 2b extending in the up-down direction are arranged inside of the driver guide 4. An upper-side driving passage 2b is connected to a lower-side driving passage 2a with each other. The upper-side driving passage 2b is formed in approximately a rectangular parallelopiped shape and in a size to insert the driver 16 in the up-down direction. An upper end of the upper-side driving passage 2b communicates with a lower portion of the cylinder 13. The lower-side driving passage 2a is formed in approximately a cylindrical shape such that a circumference of the lower-side driving passage 2a is wider than that of the upper-side driving passage 2b. A diameter of the lower-side driving passage 2a is approximately the same as or slightly larger than a striker 17 that is formed in approximately a cylindrical shape and attached to a tip end (lower end) 16b of the driver 16. A lower end of the lower-side driving passage 2a opens downward and acts as an ejection port 2c.
As shown in FIGS. 2 to 6, the driving nose 2 includes a contact arm 3 contactable to a workpiece W. The contact arm 3 is movable in the up-down direction between a lower position C1 and an upper position C2 relating to the driver guide 4. The contact arm 3 is biased toward the lower position C1 by a compression spring 41b disposed at a front portion of the tool main body 10. When the tool main body 10 approaches the workpiece W with the lower end of the contact arm 3 contacting the workpiece W, the contact arm 3 is pushed by to workpiece W to move from the lower position C1 to the upper position C2. At the upper position C2, the lower end of the contact arm 3 is disposed at approximately the same position as the ejection port 2c.
As shown in FIGS. 5 and 6, the lower end of the driver 16 enters the driving passages 2a, 2b. The driver 16 moves downward by an active gas pressure applied to the upper surface of the piston 15. When the striker 17 attached to the tip end 16b of the driver 16 moves to a driving position, the striker 17 drives a head na of a driving member n supplied to the driving passage 2a. The driving member n is driven by the striker 17 to move downward within the driving passage 2a and ejected from the ejection port 2c. The ejected driving member n is driven into the workpiece W. An approximately tubular-shaped damper 18 is arranged within the cylinder 13 on a lower side thereof so as to absorb an impact at a dead center of the piston 15.
As shown in FIGS. 5 and 6, a plurality of rack teeth (engaged portions) 16a protruding rightward are arranged on a right side of the driver 16. In the first embodiment, six rack teeth 16a are arranged in a longitudinal direction of the driver 16 (in the up-down direction). Each of the plurality of rack teeth 16a is formed in approximately a triangle shape such that a bottom portion of each of the rack teeth 16a is directed downward (driving direction) when viewed from the front. The bottom portion of each of the rack teeth 16a engages a corresponding engaging portion 25 of the lift mechanism 23.
As shown in FIGS. 1 to 4, a grip 5 extending rearward for a user to hold is arranged on a rear side of the tool main body 10. A trigger 6 for a user to pull by his/her finger is arranged on a lower surface of the front portion of the grip 5. A trigger switch 6a turns on or off via the trigger 6 and locates in the grip 5. When the driving nose 2 is pushed by the workpiece W to move from the lower position C1 to the upper position C2 (refer to FIG. 6), the trigger 6 is active.
As shown in FIGS. 1 to 4, a battery attachment portion 7 extending in the up-down direction is arranged on a rear side surface of the grip 5. A battery 8 is removably attachable to the battery attachment portion 7. The battery 8 removed from the battery attachment portion 7 can be recharged by a dedicated charger for repeated use. The battery 8 can be used as a power source for other electric power tools. The battery 8 supplies power to an electric motor 20 etc.
As shown in FIGS. 2 to 4, a controller 9 for mainly controlling the electric motor 20 is housed in the battery attachment portion 7. The controller 9 includes a shallow box-shaped rectangular case that housed a control circuit board. The controller 9 is arranged in front of the battery 8 attached to the battery attachment portion 7 such that the longest side of the controller 9 extends approximately in the up-down direction and the shortest side in the front-rear direction. An inlet port 7a is arranged above the controller 9 and on an upper surface of the battery attachment portion 7. The inlet port 7a passes through between the inside and the outside of the battery attachment portion 7.
As shown in FIGS. 1 to 4, the main body housing 11 includes an approximately tubular-shaped mechanism case (motor housing) 12 extending in the front-rear direction below the grip 5. A rear portion of the mechanism case (motor housing) 12 is combined with a lower portion of the battery attachment portion 7. A motor housing compartment 12a for housing the electric motor 20 is arranged at a rear portion of the mechanism case (motor housing) 12. A gear housing compartment 12h for housing a planetary gear reduction mechanism 22 is arranged in front of the motor housing compartment 12a. Exhaust ports 12f are arranged on both left and right sides of the gear housing compartment 12h such that the exhaust ports 12f pass through the inside and the outside of the gear housing compartment 12h. A lifter housing compartment 12i for housing the lift mechanism 23 is arranged in front of the gear housing compartment 12h. The motor housing compartment 12a, the gear housing compartment 12h, and the lifter housing compartment 12i are arranged in a direction of an output axis line J that extends in the front-rear direction. The grip 5, the battery attachment portion 7, and the mechanism case 12 cooperate with each other to form a loop shape.
As shown in FIGS. 2 to 4, the mechanism case (motor housing) 12 includes a solenoid housing compartment 12b below the motor housing compartment 12a and the gear housing compartment 12h. The solenoid housing compartment 12b houses a solenoid 36 that is discussed later. The solenoid housing compartment 12b is partitioned in the up-down direction by a lower surface of the motor housing compartment 12a and a lower surface of the gear housing compartment 12h with respect to the motor housing compartment 12a and the gear housing compartment 12h. A rear portion of the solenoid housing compartment 12b and a lower portion of the battery attachment portion 7 communicate with (connects to) the motor housing compartment 12a through a communication passage 12g that is arranged at a rear portion of the motor housing compartment 12a. The motor housing compartment 12a communicates with (connects to) the gear housing compartment 12h in the front-rear direction.
As shown in FIGS. 1 to 4, the solenoid housing compartment 12b is formed in approximately a rectangular box shape. A solenoid 36 is housed at a front portion of the solenoid housing compartment 12b. A plunger 36a of the solenoid 36 is tilted downward relating to the output axis line J as it extends in a forward direction. The solenoid housing compartment 12b includes a front-side first wall 12c and a lower-side second wall 12d. The first wall 12c faces the driving nose 2 and the second wall 12d faces the magazine 26. The plunger 36a protrudes from a center of the first wall 12c to the outside of the solenoid housing compartment 12b. The second wall 12d includes inlet ports 12e passing through the inside and the outside of the solenoid housing compartment 12b. The inlet ports 12e and the solenoid 36 are arranged so as to be aligned in the up-down direction. A detailed configuration of the solenoid 36 will be discussed later.
As shown in FIGS. 2 and 3, the electric motor 20 includes an output shaft 20a extending in the front-rear direction along the output axis line J. A rear portion of the output shaft 20a is rotatably supported by a bearing 20b. A front portion of the output shaft 20a is rotatably supported by a bearing (not shown) disposed in the planetary gear reduction mechanism 22. A fan 21 is attached to a front end of the output shaft 20a and behind the planetary gear reduction mechanism 22. By rotation of the fan 21 integrally with the output shaft 20a, a cooling air flows into the motor housing compartment 12a from the rear to the front. The planetary gear reduction mechanism 22 includes a three-staged planetary gear train. A rotation power of the output shaft 20a of the electric motor 20 is reduced by the planetary gear reduction mechanism 22 to be transmitted to the lift mechanism 23.
As shown in FIGS. 5 and 6, the lift mechanism 23 is arranged on a right side of the driving nose 2. The lift mechanism 23 moves the driver 16 and the piston 15 against the pressure of the gas filled in the accumulation chamber 14. The lift mechanism 23 includes a wheel 24 rotatable around the output axis line J. The wheel 24 is configured to be rotatable counterclockwise and to be restricted from rotating clockwise when viewed from the front. A plurality of engaging portions 25 are arranged along an outer circumferential edge of the wheel 24. In the first embodiment, for example, six engaging portions 25 are arranged at equal intervals in a circumferential direction of the wheel 24. For example, a cylindrical-shaped pin extending in the front-rear direction is used for each of the engaging portions 25. When the wheel 24 rotates, each of the engaging portion 25 moves (rotates) around the output axis line J.
As shown in FIGS. 5 and 6, a left portion of the wheel 24 enters the driving passage 2b of the driver guide 4 via a window 12j arranged on the left side of the lifter housing compartment 12i. Each of the engaging portions 25 of the wheel 24 engages a corresponding bottom portion of the rack tooth 16a of the driver 16 within the driving passage 2b. When the wheel 24 rotates counterclockwise when viewed from the front with at least one of the engaging portions 25 engaging a corresponding bottom portion of the rack tooth 16a, the driver 16 and the piston 15 move upward. The upward movement of the piston 15 increases a pressure of the gas filled in the accumulation chamber 14.
As shown in FIG. 4, a dial-type adjuster 41 is arranged in front of the driving nose 2. The adjuster 41 includes a rotation shaft 41a which extends in the up-down direction. The rotation shaft 41a is rotatable and movable in the up-down direction integrally with the adjuster 41. An adjuster coupling member 3a coupled to the adjuster 41 is arranged above the contact arm 3. The contact arm 3 is movable in the up-down direction integrally with the adjuster 41. By rotating the adjuster 41 around its axis, a position of the contact arm 3 can be adjusted in the up-down direction. The adjuster 41 includes a compression spring 41b that is arranged on an outer circumferential side of the rotation shaft 41a and supported by the main body housing 11. The compression spring 41b biases the adjuster 41 and the contact arm 3 in the downward direction. Accordingly, the contact arm 3 is normally positioned in the lower position C1.
As shown in FIG. 4, a contact plate 42 is integrally joined to an upper portion of the adjuster 41. A plate-shaped spring 43 and a switch 44 are arranged above the contact plate 42. When the contact arm 3 moves from the lower position C1 to the upper position C2 (refer to FIG. 6), the contact plate 42 moves upward via the adjuster 41. An upper end of the contact plate 42 pushes a protrusion pin 44a of the switch 44 via the spring 43. Accordingly, the switch 44 is turned on and transmits an on-signal to the controller 9. When the on-signal is transmitted to the controller 9, a pulling operation of the trigger 6 becomes effective. When the contact arm 3 is at the lower position C1, the contact plate 42 does not move upward and thus the protrusion pin 44a of the switch 44 is not pushed. Accordingly, the switch 44 does not transmit the on-signal to the controller 9, and thus, a pulling operation of the trigger 6 does not become effective.
As shown in FIGS. 1 to 4, an approximately cylindrical-shaped magazine 26 is arranged behind the driving nose 2. The magazine 26 is arranged such that an axial direction thereof is directed approximately in the up-down direction. The magazine 26 has a half-split structure including a right portion 26a and a left portion 26b. A support shaft 26c is arranged between a left end of the lower surface of the right portion 26a and a right end of the lower surface of the left portion 26b. The left portion 26b is rotatable around the support shaft 26c so as to be opened and closed with respect to the right portion 26a. By opening the left portion 26b, combined plurality of driving members n can be placed to the magazine 26. By closing the left portion 26b, the combined plurality of driving members n can be held in the magazine 26. The driver guide 4 includes a flat-plate-shaped feed guide 4a extending rearward from the driving nose 2. A front end of the right portion 26a of the magazine 26 is linked to and supported by the feed guide 4a. A rear end of the right portion 26a of the magazine 26 is linked to and supported by a rear end of the mechanism case (motor housing) 12 of the main body housing 11.
As shown in FIGS. 7 to 9, a combined plurality of driving members N, which are wound in a spiral manner, includes a plurality of driving members n and combining members m for combining each of the plurality of driving members n. Each of the plurality of driving members n is a nail having a circular head na. Each of the combining members m is, for example, a metal-made wire. The combining members m are arranged at specified intervals in a direction approximately perpendicular to a longitudinal direction of the plurality of driving members n so as to combine the plurality of driving members n. The combined plurality of driving members N wound in a spiral manner are housed in the magazine 26. An end of the combined plurality of driving members N is guided from the magazine 26 to the front and held in a feed mechanism 30 arranged between the magazine 26 and the driving nose 2.
As shown in FIGS. 7 to 12, the feed mechanism 30 includes a feed pawl 31 for feeding the driving member n to the driving passage 2a in a forward direction. The feed mechanism 30 includes a biasing member 32 for biasing the feed pawl 31 in the forward direction. The biasing member 32 is, for example, a coil-shaped compression spring. A spring receiving portion 26d for holding a rear end of the compression spring 32 is arranged at a front portion of the right portion 26a of the magazine 26. The feed mechanism 30 includes the solenoid 36 for moving the feed pawl 31. Power is supplied or shut off from the battery 8 to the solenoid 36 according to a signal from the controller 9. When power is shut off from the battery 8 to the solenoid 36 for the solenoid 36 to become an off-state, the feed pawl 31 is biased forward to a side of the driving passage 2a by the compression spring 32. On the contrary, when power is supplied from the battery 8 to the solenoid 36 to become an on-state, the feed pawl 21 moves to a side of the magazine against the biasing force of the compression spring 32.
As shown in FIG. 2, the solenoid 36 is housed in the solenoid housing compartment 12b in the mechanism case (motor housing) 12 arranged above the magazine 26. In other words, the solenoid 36 is not arranged in the magazine 26 nor in a feed passage of the driving member n between the magazine 26 and the driver guide 4 in the front-rear direction.
As shown in FIGS. 7 to 9, 13, and 14, the solenoid 36 includes a rectangular box-shaped holder 36c and the plunger 36a protruding from the holder 36c in the forward direction. A penetrating hole through which the plunger 36a passes is arranged in a front surface of the holder 36c. A lower surface and an upper surface of the holder 36c are opened. A coil 36b is housed in the holder 36c. The plunger 36a is inserted into the coil 36b. The coil 36b is arranged in an adjoining area of inlet ports 12e on the second wall 12d of the solenoid housing compartment 12b.
As shown in FIGS. 7 to 9, 13, and 14, the feed mechanism 30 includes a power transmission member 35 that is moved by driving of the solenoid 36. The feed pawl 31 moves in the front-rear direction being interlocking with a movement of the power transmission member 35. The power transmission member 35 is formed in a plate shape extending approximately in the up-down direction. A rotation support 35a around which the power transmission member 35 rotates is arranged at an upper portion of the power transmission member 35. The rotation support 35a is rotatably supported by the driver guide 4 via a shaft member extending in the left-right direction.
As shown in FIGS. 7 to 9, 13, and 14, a pawl coupling portion 35c for coupling with a rear portion of the feed pawl 31 is formed at a lower end of the power transmission member 35. A spring receiving portion 35d for receiving a front end of the compression spring 32 is formed on a rear surface of the pawl coupling portion 35c. The power transmission member 35 and the feed pawl 31 are biased in the forward direction by the compression spring 32 via the spring receiving portion 35d. The power transmission member 35 includes a thick portion 35e behind the pawl coupling portion 35c. The thick portion 35e is formed thicker than the pawl coupling portion 35c and extends in the up-down direction. The thick portion 35e improves rigidity of the power transmission member 35 against the biasing force of the compression spring 32 and a driving force of the solenoid 36.
As shown in FIGS. 7 to 9, 13, and 14, the power transmission member 35 includes a plunger coupling portion 35b for coupling to a front end of the plunger 36a. The plunger coupling portion 35b is arranged at the middle between the rotation support 35a and the pawl coupling portion 35c in the up-down direction. For example, a distance between the rotation support 35a and the plunger coupling portion 35b is approximately half the distance between the rotation support 35a and the pawl coupling portion 35c. Accordingly, a moving distance of the plunger 36a is approximately half of a moving distance of the feed pawl 31.
As shown in FIGS. 10-14, a left end of the feed pawl 31 is formed in approximately a U shape. A tilted surface 31a is formed at a front portion of the left end of the feed pawl 31. The tilted surface 31a is formed so as to be tilted in the forward direction as it extends in the leftward direction. A portion extending from a right end of the tilted surface 31a is directed in the front-rear direction. A receiving surface 31b facing the tilted surface 31a is formed on a rear left side of the feed pawl 31. The receiving surface 31b extends approximately in the left-right direction. A right lower portion of the feed pawl 31 is rotatably connected to the pawl coupling portion 35c of the power transmission member 35 via a rotation support shaft 31c that extends in the up-down direction. The feed pawl 31 includes a torsion spring 31d that biases the feed pawl 31 around the rotation support shaft 31c. The torsion spring 31d biases the feed pawl 31 clockwise when viewed from the bottom.
As shown in FIGS. 7 to 12, the feed mechanism 30 includes a check pawl 33 for preventing a driving member n, which has fed forward by the feed pawl 31, from returning rearward from the driving passage 2a. A tilted surface 33a is formed at a front portion of the check pawl 33. The tilted surface 33a is formed so as to be tilted in the forward direction as it extends in the rightward direction. A right rear portion of the check pawl 33 extends in the front-rear direction. A plate-shaped guide member 34 extending in the front-rear direction and in the up-down direction is arranged between the driving passage 2a and the magazine 26. The guide member 34 is arranged on a left side of the feed guide 4a and extends approximately parallel to the feed guide 4a. A lower portion of the check pawl 33 is rotatably connected by the guide member 34 via a rotation support shaft 33b extending in the up-down direction. The check pawl 33 is biased counterclockwise viewed from the bottom by a spring (not shown in the figures).
As shown in FIG. 1, the feed passage for feeding (loading) a driving member n from the magazine 26 to the driving passage 2a is formed between the feed guide 4a and the guide member 34 in the left-right direction. The feed pawl 31 is inserted into a hole 4b passing through the feed guide 4a in the left-right direction and protrudes from right to left toward the feed passage. The check pawl 33 is inserted into a hole 34a passing through the feed guide 4a in the left-right direction and protrudes from left to right toward the feed passage (refer to FIG. 8).
Next, a series of a driving operation of the driving tool 1 will be explained with reference to FIGS. 3 to 12. FIGS. 3, 5, 7, and 10 show that the driver 16 is at the standby position and that a driving member n is not supplied to the driving passage 2a. FIGS. 6, 9, and 12 show that a driving member n is supplied to the driving passage 2a. The driver 16 at the standby position is slightly below the top dead center. When the driver 16 is at the standby position, a bottom surface of a second rack tooth 16a from the bottom engages a preceding engaging portion 25 preceding the last engaging portion 25a of the lift mechanism 23 (on a counterclockwise side in FIG. 5).
When the contact arm 3 is pushed by the workpiece W, the contact arm 3 moves from the lower position C1 to the upper position C2. The contact plate 42 connected to the adjuster 41 is moved upward in conjunction with the contact arm 3. When the contact plate 42 moves upward, the protrusion pin 44a of the switch 44 is pushed via the spring 43. When the switch 44 is tuned on, the switch 44 transmits an on-signal to the controller 9. When the controller 9 receives the on-signal from the switch 44 and the trigger 6 is pulled from the user, the controller 9 activates the electric motor 20. When the electric motor 20 is activated, the wheel 24 of the lift mechanism 23 starts to rotate. Accordingly, the rack teeth 26a engaging the engaging portions 25 move upward and the driver 16 moves upward from the standby position to the top dead center.
When the driver 16 moves from the standby position to the top dead center, a foremost driving member n is supplied to the driving passage 2a by the feed mechanism 30. Immediately before the lower end of the striker 17 attached to the tip end 16b of the driver 16 moves upward beyond a head na of the driving member n (refer to FIG. 8), power is supplied to the solenoid 36. The plunger 36a moves rearward together with the plunger coupling portion 35b of the power transmission member 35. The power transmission member 35 rotates rearward around the rotation support 35a. The feed pawl 31 moves rearward against the biasing force of the compression spring 32 being interlocking with the rearward movement of the pawl coupling portion 35c of the power transmission member 35.
When the feed pawl 31 moves rearward, the tilted surface 31a of the feed pawl 31 is pushed by the driving member n. Accordingly, the feed pawl 31 moves (retreats) rightward so as to be apart from the driving member n against the biasing force of the torsion spring 31d. When the plunger 36a moves to the rearmost end, the feed pawl 31 rotates leftward to a position where the next driving member n is placed by the biasing force of the torsion spring 31d. Accordingly, the next driving member n is held by the tilted surface 31a and the receiving surface 31b of the feed pawl 31. The driving member n at the foremost end is positioned immediately behind the striker 17 and held so as not to be moved rearward by the front surface of the check pawl 33.
When the lower end of the striker 17 moves above the head na of the driving member n (refer to FIG. 9), power to the solenoid 36 is shut off. Accordingly, the power transmission member 35 rotates forward around the rotation support 35a by the biasing force of the compression spring 32. The feed pawl 31 moves forward while holding the second driving member n from the front. The check pawl 33 is pushed by the driving member n that moves from the rear to the front and accordingly the check pawl 33 moves (retreats) leftward so as to be apart from the driving member n against the biasing force of the spring (not shown). Because of this configuration, the feed pawl 31 smoothly moves the combined plurality of driving members N, including the driving member n which is being held, in the forward direction. When the combined plurality of driving members N moves in the forward direction, the driving member n at the foremost end is supplied to the driving passage 2a during the time while the driver 16 moves from the standby position to the top dead center. By the biasing force of the spring (not shown), the check pawl 33 rotates rightward to a position where the driving member n is disposed. Accordingly, the combined plurality of driving members N are restricted from moving (returning) rearward on a side of the magazine 26.
When the driver 16 moves upward to the top dead center before driving the driving member n, the last engaging portion 25a of the wheel 24 disengages from the bottom portion of the lowermost rack tooth 16a. The driver 16 moves downward owing to the active pressure of the gas filled in the accumulation chamber 14, which is applied to the piston 15. The striker 17 drives the head na of the driving member n within the driving passage 2a. The driving member n that is driven by the striker 17 is ejected from the ejection port 2c to the workpiece W. The ejected driving member n is separated (sheared) from the combined plurality of driving members N by an impact of the striker 17 (the driver 16). While the driver 16 moves downward, all of the engaging portions 25 of the wheel 24 move (retreat) rightward of the driving passage 2b. Accordingly, the plurality of rack teeth 16a of the driver 16 moving downward can be prevented from interfering with the engaging portions 25 of the wheel 24, thereby smoothly performing a driving operation.
While the driver 16 moves downward and after the driver 16 reaches a bottom dead center, the wheel 24 continues to rotate. When the driver 16 is at the bottom dead center and the wheel 24 rotates by a predetermined rotation angle, one of the engaging portion 25 of the wheel 24 engages a bottom surface of the uppermost rack tooth 16a of the driver 16. Accordingly, the driver 16 starts to move upward (a rerunning movement of the driver 16 starts). The driving member n next to the ejected driving member n is held between the tilted surface 31a and the receiving surface 31b and on the front surface of the check pawl 33. The next driving member n is positioned immediately behind the driving passage 2a. The striker 17 includes an ark-shaped surface 17a, which is formed in a complementary shape with the head na of the driving member n, at the rear surface thereof. The striker 17 can be prevented from interfering with the head na of the next driving member n by the ark-shaped surface 17a. Accordingly, the next driving member n is held in an adjoining area of the driving passage 2a as close as possible.
When the wheel 24 rotates and a preceding engaging portion 25 preceding to the last engaging portion 25a engages a bottom of the second rack tooth 16a from the bottom, the driver 16 returns to the standby position. When the driver 16 (and the piston 15) returns to the standby position, the electric motor 20 is stopped by, for example, adequately measuring of a time from a activation time of the electric motor 20 or rotation position of the wheel 24. Accordingly, the driver 16 is held at the standby position. As described above, a series of driving operation is completed.
Next, a cooling air flow flowing in the main body housing 11 will be explained with reference to FIG. 2. When the electric motor 20 is activated, the fan 21 rotates integrally with the output shaft 20a. Accordingly, a cooling air flow flowing from the rear to the front in the motor housing compartment 12a of the mechanism case 12 is generated. A negative pressure is generated inside of the solenoid housing compartment 12b, which communicates with the motor housing compartment 12a via the communication passage 12g, and the battery attachment portion 7, thereby flowing the cooling air inside of the solenoid housing compartment 12b and the battery attachment portion 7.
An outside air as the cooling air is taken into the solenoid housing compartment 12b from the inlet ports 12e of the second wall 12d at first. The cooling air flows in an air passage A1, passing through between the coil 36b of the solenoid 36b (refer to FIG. 13) and an inner circumferential surface of the holder 36c, and flowing rearward to the communication passage 12g. The cooling air flowing in the air passage A1 cools off the coil 36b. After that, the cooling air flows through an air passage A2 from the communication passage 12g to the motor housing compartment 12a in the forward direction. The cooling air flowing in the air passage A2 cools off the electric motor 20. The cooling air is discharged to the outside from the exhaust ports 12f in the gear housing compartment 12h in front of the motor housing compartment 12a.
Furthermore, an outside air is taken, as the cooling air, into the battery attachment portion 7 from the inlet ports 7a on an upper side of the battery attachment portion 7. The cooling air flows in an air passage A3, passing in a adjoining area of the controller 9, and flowing downward to the communication passage 12g. The cooling air flowing in the air passage A3 cools off the controller 9. The cooling air flowing in the air passage A3 merges with the cooling air flowing in the air passage A2 in the communication passage 12g. The cooling air is discharged to the outside from the exhaust ports 12f in the gear housing compartment 12h.
As described above, the driving tool 1 includes the driver 20 configured to move in the driving direction and driven by the electric motor 20, as shown in FIGS. 7 to 9. The driving tool 1 includes the driver guide 4 for guiding the driver 16. The driving tool 1 includes the magazine 26 for housing the plurality of driving members n. The driving tool 1 includes the feed pawl 31 for feeding (loading) the driving member n from the magazine 26 to the driver guide 4. The driving tool 1 includes the power transmission member 35 being interlocking with the feed pawl 31. The driving tool 1 includes the solenoid 36 that is configured to move the feed pawl 31 via the power transmission member 35. The solenoid 36 is arranged in the main body housing 11 outside of the magazine 26.
As described above, the solenoid 36 for feeding the driving member n within the magazine 26 to the driving passage 2a in the driver guide 4 is arranged in the main body housing 11. Because of this configuration, the solenoid 36 can be arranged on the flow passage of the cooling air for cooling off, for example, the electric motor 20. Accordingly, the solenoid 36 can be efficiently cooled off, thereby suppressing a temperature rise of the solenoid 36. Furthermore, the arrangement of the power transmission member 35 between the solenoid 36 and the feed pawl 31 can efficiently transmit the output of the solenoid 36 to the feed pawl 31.
As shown in FIGS. 7 to 9, the power transmission member 35 is supported by the main body housing 11 such that the power transmission member 35 is rotatable around the rotation support 35a and coupled to the feed pawl 31 via the pawl coupling portion 35c. The plunger 36a of the solenoid 36 is coupled to the power transmission member 35 between the rotation support 35a and the pawl coupling portion 35c. In other words, a part of the power transmission member 35 is arranged between the plunger 36a of the solenoid 36 and the feed pawl 31. Also, the plunger 36a is coupled to the power transmission member 35 between the rotation support 35a and the pawl coupling portion 35c. Because of this configuration, a short stroke of the plunger 36a can move the feed pawl 31 by utilizing the principle of leverage. Also, a rapid movement of the feed pawl 31 can be obtained. Furthermore, the short stroke of the plunger 36a can make a length of the plunger 36a inserted into the coil 36b (refer to FIG. 13) to be maintained as long as possible even when the plunger 36a is most protruded (and retracted). Accordingly, the output of the solenoid 36 can be highly maintained.
As shown in FIGS. 7 to 9, the driving tool 1 includes the compression spring (biasing member) 32 for biasing the feed pawl 31 toward the driver guide 4. When the solenoid 36 is turned on, the feed pawl 31 moves in a direction opposite to the biasing direction of the compression spring 32. Accordingly, the feed pawl 31 is constantly biased on a side of the driver guide 4 (in a feeding direction) by the compression spring 32. The solenoid 36 is turned on only when the next driving member n is to be received by the feed pawl 31. Because of this configuration, a driving time of the solenoid 36 is made short and also the driving member n can be supplied to the driving passage 2a of the driver guide 4 one by one in a reliable manner.
As shown in FIGS. 2 and 7 to 9, the main body housing 11 includes the mechanism case (motor housing) 12 for housing the electric motor 20. The solenoid 36 is housed in the mechanism case 12 (motor housing) and also arranged between the electric motor 20 and the magazine 26. The solenoid 36 and the electric motor 20 are housed in the mechanism case (motor housing) 12, and accordingly both the solenoid 36 and the electric motor 20 can be cooled off by a cooling mechanism such as, for example, the fan 21. The magazine 26 is arranged with respect to the main body housing 11 in a position where the driving member n is supplied within the driver guide 4. Accordingly, a space is needed between the electric motor 20 and the magazine 26. The solenoid 36 can be arranged by utilizing the space, thereby making the driving tool 1 compact.
As shown in FIG. 2, the driving tool 1 includes the fan 21 for generating the air flow in the main body housing 11. The solenoid 36 is arranged in the air passage A1 in which the air flow generated by the fan 21 flows, thereby efficiently cooling off the solenoid 36 in an improved manner.
As shown in FIG. 2, the solenoid 36 is arranged on an upstream side of the air passage (air passage A1) with respect to the electric motor 20. Accordingly, the cooling air flow cools off the solenoid 36 at first and then the electric motor 20. A driving time of the electric motor 20 in the driving tool 1 is short because the electric motor 20 is activated only when the driver 16 moves to the standby position or to the top dead center. On the contrary, a quantity of heat generated in the coil 36b (refer to FIG. 13) is large though the driving time of the solenoid 36 is short. The solenoid 36, which generates a large quantity of heat, is cooled off at first, thereby efficiently cooling off the electric components including the solenoid 36 and the electric motor 20 in an improved manner.
As shown in FIG. 2, the main body housing 11 includes the mechanism case (motor housing) 12 that houses the electric motor 20. The mechanism case (motor housing) 12 includes the motor housing compartment 12a for housing the electric motor 20 and the solenoid housing compartment 12b for housing the solenoid 36. The motor housing compartment 12a communicates with the solenoid housing compartment 12b via the communication passage 12g. Because of this configuration, the air passage can be formed such that the cooling air flow for cooling off the electric motor 20 and the solenoid 36 passes through the communication passage 12g. Accordingly, the cooling air flow can be guided such that the electric motor 20 and the solenoid 36 are efficiently cooled off in an improved manner.
As shown in FIGS. 1 and 2, the main body housing 11 includes the inlet ports 12e in the second wall 12d facing the coin 36c of the solenoid 36 (refer to FIG. 3). In other words, the inlet ports 12e are formed such that the outside air taken from the inlet ports 12e easily flows to the coil 36b of the solenoid 36, thereby efficiently cooling off the solenoid 36 in an improved manner.
As shown in FIGS. 3, 5, and 6, the driving tool 1 includes the piston 15 connected to the driver 16. The driving tool 1 includes the cylinder 13 that is configured such that the piston 15 is movable within the cylinder 13. When the driver 16 moves in a direction opposite to the driving direction by the electric motor 20, the pressure of the gas in the cylinder 13 increases. Accordingly, in the so-called gas-spring type driving tool 1, the solenoid 36 for feeding the driving member n can be arranged in a position where the solenoid 36 is efficiently cooled off.
Next, a second embodiment of the present disclosure will be explained with reference to FIGS. 15 and 16. The main body housing 11 of a driving tool 50 in the second embodiment includes a mechanism case (motor housing) 51 instead of the mechanism case (motor housing) 12 shown in FIG. 1. In the following explanation, descriptions which are not in common with the first embodiment will be explained in detail. The mechanism case (motor housing) 51 is formed in approximately a tubular shape extending in the front-rear direction below the grip 5. The mechanism case (motor housing) 51 includes a motor housing compartment 51a, a gear housing compartment 51h, a lifter housing compartment 51i, a solenoid housing compartment 51b, and a communication passage 51g. These configurations are formed similar to the motor housing compartment 12a, the gear housing compartment 12h, the lifter housing compartment 12i, the solenoid housing compartment 12b and the communication passage 12g of the mechanism case 12 shown in FIG. 2.
As shown in FIGS. 15 and 16, the solenoid 36 is housed in a front portion of the solenoid housing compartment 51b formed in an approximately rectangular box shape. The plunger 36a of the solenoid 36 is tilted downward with respect to the output axis line J as it extends in the forward direction. The solenoid housing compartment 51b includes a first wall 51c on a front side and a second wall 51d on a lower side. The first wall 51c faces the driving nose 2 and the second wall 51d faces the magazine 26. The plunger 36a protrudes from a middle of the first wall 51c to the outside of the solenoid housing compartment 51b. The first wall 51c includes inlet ports 51e around the plunger 36a which pass through the inside and the outside of the solenoid housing compartment 51b. The inlet ports 51e are aligned with the solenoid 36 approximately in the front-rear direction. The exhaust ports 51f passing through the inside and the outside of the gear housing compartment 51h are formed on both the left and right sides of the gear housing compartment 51h.
A cooling air flow for cooling off the solenoid 36 will be explained with reference to FIG. 2. When the electric motor 20 is activated, the fan 21 rotates integrally with the output shaft 20a. Accordingly, a cooling air flow flowing from the rear to the front in the motor housing compartment 51a of the mechanism case 51 is generated. A negative pressure is generated inside of the solenoid housing compartment 51b, which communicates with the motor housing compartment 51a via the communication passage 51g, thereby flowing the cooling air inside of the solenoid housing compartment 51b. An outside air as the cooling air is taken into the solenoid housing compartment 51b from the inlet ports 51e of the first wall 51c at first. The cooling air flows in an air passage A1, passing through between the coil 36b of the solenoid 36b and an inner circumferential surface of the holder 36c, and flowing rearward to the communication passage 51g. The cooling air flowing in the air passage A1 cools off the coil 36b. After that, the cooling air flows in an air passage A2 from the communication passage 51g to the motor housing compartment 51a in the forward direction. The cooling air flowing in the air passage A2 cools off the electric motor 20. The cooling air is discharged to the outside from the exhaust ports 51f in the gear housing compartment 51h.
As shown in FIGS. 15 and 16, the main body housing 11 includes the inlet ports 51e in the first wall 51c through which the plunger 36a of the solenoid 36 passes. In other words, the inlet ports 51e are formed such that the outside air taken from the inlet ports 51e easily flows to the coil 36b of the solenoid 36, thereby efficiently cooling off the solenoid 36 in an improved manner.
Next, a third embodiment of the present disclosure will be explained with reference to FIG. 17. The main body housing 11 of a driving tool 60 in the third embodiment includes a mechanism case (motor housing) 61 instead of the mechanism case (motor housing) 12 shown in FIG. 1. In the following explanation, descriptions which are not in common with the first embodiment will be explained in detail. The mechanism case (motor housing) 61 is formed in approximately a tubular shape extending in the front-rear direction below the grip 5. The mechanism case (motor housing) 61 includes a motor housing compartment 61a, a gear housing compartment 61i, a lifter housing compartment 61j, a solenoid housing compartment 61b, and a communication passage 51g. These configurations are formed similar to the motor housing compartment 12a, the gear housing compartment 12h, the lifter housing compartment 12i, the solenoid housing compartment 12b and the communication passage 12g of the mechanism case 12 shown in FIG. 2.
As shown in FIG. 17, the solenoid 36 is housed in a front end of the solenoid housing compartment 61b formed in an approximately rectangular box shape. The plunger 36a of the solenoid 36 is tilted downward with respect to the output axis line J as it extends in the forward direction. The solenoid housing compartment 61b includes a first wall 61c on a front side and a second wall 61d on a lower side. The first wall 61c faces the driving nose 2 and the second wall 61d faces the magazine 26. The plunger 36a protrudes from a middle of the first wall 61c to the outside of the solenoid housing compartment 61b. The second wall 61d includes inlet ports 61e which pass through the inside and the outside of the solenoid housing compartment 61b. The inlet ports 61e are aligned with the solenoid 36 approximately in the up-down direction. The exhaust ports 61f passing through the inside and the outside of the gear housing compartment 61i are formed on both the left and right sides of the gear housing compartment 61i.
As shown in FIG. 17, a rear portion of the solenoid housing compartment 61b communicates with a rear portion of the motor housing compartment 61a via the communication passage 61g. An exposed portion 61h which exposes an outer surface of a stator of the electric motor 20 to a rear portion of the solenoid housing compartment 61b is formed on a right half area of the lower surface of the motor housing compartment 61a. A cooling air is taken from the inlet ports 61e and enters the solenoid housing compartment 61b. After passing through the adjoining area of the coil 36b, the cooling air passes through a first air passage A1 which is directed to the communication passage 61g in the rearward direction. At this time, the cooling air cools off an outer surface of the stator of the electric motor 20 via the exposed portion 61h. After that, the cooling air passes through a second air passage A2 which is directed from the communication passage 61g toward the motor housing compartment 61a in the forward direction. At this time, the cooling air passes through the inside of the electric motor 20 to cool off an inner surface of the stator and a rotor of the electric motor 20. The cooling air passing through the second air passage A2 is discharged to the outside from the exhaust ports 61f of the gear housing compartment 61i.
As described above, the air passage includes the first air passage A1 and the second air passage A2. As shown in FIG. 17, the cooling air in the first air passage A1 cools off the electric motor 20 from outside. The cooling air in the second air passage A2, which is connected to the first air passage A1, passes through the inside of the electric motor 20. Accordingly, the electric motor 20 is cooled off both from the outside and the inside, thereby efficiently cooling off the electric motor 20.
Next, a fourth embodiment of the present disclosure will be explained with reference to FIGS. 18 and 19. The main body housing 11 of a driving tool 70 in the fourth embodiment includes a mechanism case (motor housing) 73 instead of the mechanism case (motor housing) 12 shown in FIG. 1. In addition to the electric motor 20, a sub-motor 71 for cooling off is arranged in a mechanism case (motor housing) 73. In the following explanation, descriptions which are not in common with the first embodiment will be explained in detail. The mechanism case (motor housing) 73 is formed in approximately a tubular shape extending in the front-rear direction below the grip 5. The mechanism case 73 includes a motor housing compartment 73a, a gear housing compartment 73j, and a lifter housing compartment 73k. These configurations are formed similar to the motor housing compartment 12a, the gear housing compartment 12h, and the lifter housing compartment 12i shown in FIG. 2.
As shown in FIGS. 18 and 19, the mechanism case (motor housing) 73 includes the motor housing compartment 73a and the solenoid housing compartment 73b below the gear housing compartment 73j. The solenoid 36 is housed in the solenoid housing compartment 73b. Also, the mechanism case (motor housing) 73 includes a sub-motor housing compartment 73i below the motor housing compartment 73a and the gear housing compartment 73j and behind the solenoid housing compartment 73b. The sub-motor 71 is housed in the sub-motor housing compartment 73i.
As shown in FIG. 19, the sub-motor housing compartment 73i communicates with the solenoid housing compartment 73b with each other. The solenoid housing compartment 73b and the sub-motor housing compartment 73i are partitioned from the motor housing compartment 73a and the gear housing compartment 73j by a lower surface of the motor housing compartment 73a and a lower surface of the gear housing compartment 73j. A rear portion of the solenoid housing compartment 73b communicates with the sub-motor housing compartment 73i, and communicates with the motor housing compartment 73a via a communication passage 73h formed in a rear portion of the motor housing compartment 73a. Furthermore, a lower portion of the battery attachment portion 7 communicates with the motor housing compartment 73a and the sub-motor housing 73a via the communication passage 73h. The motor housing compartment 73a communicates with the gear housing compartment 73j in the front-rear direction.
As shown in FIGS. 18 and 19, the solenoid 36 is housed in a front portion of the solenoid housing compartment 73b formed in an approximately rectangular box shape. The plunger 36a of the solenoid 36 is tilted downward with respect to the output axis line J as it extends in the forward direction. The solenoid housing compartment 73b includes a first wall 73c on a front side and a second wall 73d on a lower side. The first wall 73c faces the driving nose 2 and the second wall 73d faces the magazine 26. The plunger 36a protrudes from a middle of the first wall 73c to the outside of the solenoid housing compartment 73b. The second wall 73d includes inlet ports 73e which pass through the inside and the outside of the solenoid housing compartment 73b. The inlet ports 73e are aligned with the solenoid 36 approximately in the up-down direction. The exhaust ports 73f passing through the inside and the outside of the gear housing compartment 73j are formed on both the left and right sides of the gear housing compartment 73j.
As shown in FIGS. 18 and 19, the sub-motor housing compartment 73i is formed in approximately a cylindrical shape. An axial direction of the sub-motor housing compartment 73i is the left-right direction. An output shaft of the sub-motor 71 extends in the left-right direction, i.e., approximately perpendicular to the output axis line J. A fan 72 is attached to a right end of the output shaft of the sub-motor 71. A disc-shaped cover 74 for covering a right side of the fan 72 is attached to a right end of the sub-motor housing compartment 73i. Second exhaust ports 73g is formed between the sub-motor housing compartment 73i and the cover 74. The second exhaust ports 73g are arranged radially outside of a lower area of the fan 72. Exhaust of the air is performed through the second exhaust ports 73g in the downward direction.
A cooling air flow flowing in the main body housing 11 will be explained with reference to FIG. 19. When the electric motor 20 is activated, the fan 21 rotates integrally with the output shaft 20a, generating a cooling air flow flowing from the rear to the front in the motor housing compartment 73a of the mechanism case 73. A negative pressure is generated inside of the battery attachment portion 7 by rotation of the fan 21. When the sub-motor 71 is activated, the fan 72 rotates integrally with the output shaft of the sub-motor 71 and generates a cooling air flow flowing from the left to the right within the sub-motor housing compartment 73i of the mechanism case 73. A negative pressure is generated inside of the solenoid housing compartment 73b and the battery attachment portion 7 by rotation of the fan 72, and accordingly a cooling air flow flows through the solenoid housing compartment 73b and the battery attachment portion 7. The sub-motor 71 is configured to rotate independently from the electric motor 20. A timing of activation of the sub-motor 71 can be arbitrary set. For example, power may be supplied to the sub-motor 71 when the trigger 7 is pull-operated. Instead, for example, power may be supplied to the sub-motor 71 when a movement of the contact arm 3 to the upper position C2 (refer to FIG. 6) is detected. Instead, for example, power supply to the sub-motor 71 may be such that power is shut down when a predetermined time is passed after power supply starts.
An outside air as the cooling air is taken into the solenoid housing compartment 73b from the inlet ports 73e of the second wall 73d at first. The cooling air passes through between the coil 36b of the solenoid 36 (refer to FIG. 13) and the inner circumferential surface of the holder 36c to cool off the coil 36b. The cooling air passes through an air passage A4 that is directed from the rearward sub-motor housing compartment 73i to the fan 72. The cooling air flowing through the air passage A4 is discharged from the second exhaust ports 73f to the outside by rotation of the fan 72.
An outside air as the cooling air is taken into the battery attachment portion 7 from the inlet ports 7a at the upper end of the battery attachment portion 7 at first. The cooling air passes through the adjoining area of the controller 9 and also passes through an air passage A3 directed to the communication passage 73h below the controller 9. The cooling air passing through the air passage A3 cools off the controller 9. The cooling air passing through the air passage A3 flows from the communication passage 73h to the sub-motor housing compartment 73i. The cooling air flowing to the sub-motor housing compartment 73i is discharged from the second exhaust ports 73f to the outside by rotation of the fan 72. Also, a part of the cooling air passing through the air passage A3 branches in the communication passage 73h and is directed to the air passage A2 for flowing to the motor housing compartment 73a. The cooling air passing through the air passage A2 cools off the electric motor 20. The cooling air is discharged from the first exhaust ports of the gear housing compartment 73j to the outside.
The driving tools 1, 50, 60, and 70 according to the above-described embodiments may be modified in various ways. In the above embodiments, the gas-spring type driving tool is exemplified. Instead, the present disclosure may be applied to a mechanical-spring type driving tool in which the driver is driven by utilizing a spring force by a mechanical compression spring which is generated when the driver moves in a direction opposite to the driving direction by the lift mechanism. Instead, for example, the present disclosure may be applied to a flywheel type driving tool in which the driver is driven by utilizing an inertia force of a flywheel. Instead, for example, the present disclosure may be applied to an electric-pneumatic type driving tool in which the driver is driven by utilizing a compression air generated by rotation of a crank owing to an electric motor.
In the above-exemplified embodiments, a ratio of distance between the rotation support 35a and the pawl coupling portion 35c to distance between the rotation support 35a and the plunger coupling portion 35b, which is referred to as a lever ration, is two. Instead, the ratio may be modified as needed. For example, when it is desirable to shorten a moving distance of the plunger 36a with the output of the solenoid 36 increased, or when it is desirable to shorten a drive time of the feed mechanism 30, the lever ratio may be increased. Instead, for example, when it is desirable to reduce the output of the solenoid 36, the lever ratio may be decreased.
For example, the mechanism case 51 of the second embodiment may include the exposed portion 61h in the third embodiment by which the electric motor 20 is cooled of from outside. For example, the mechanism case 51 of the second embodiment may include the sub-motor housing compartment 73i in the fourth embodiment which houses the sub-motor 71 having the fan 72. For example, in the fourth embodiment, it may be configured such that the fan 21 is removed from the output shaft 20a and only the fan 72 of the sub-motor 71 cools off the electric motor 20, the solenoid 36, and the controller 9.
In the first embodiment, the second wall 12d includes inlet ports 12e. Instead, it may be configured such that the first wall 12c also includes the inlet ports.
Patent Application
20250187164
