JP2022018216A - Work machine - Google Patents

Abstract

To provide a work machine which enables reduction of vibration and reaction occurring in the work machine while inhibiting increase in the size and mass of the work machine.SOLUTION: A work machine includes: a striking part 17 which is linearly moved in a first direction B1 to perform processing; a slider 43 which is linearly moved in a second direction B2 opposite to the first direction B1 when the striking part 17 is linearly moved in the first direction B1; and a housing which supports the striking part 17 and the slider 43. The work machine includes: a rotational inertia member 44 rotatably provided in the housing; and a conversion mechanism 45 which converts linear energy of the slider 43 in the second direction B2 into rotation energy of the rotational inertia member 44.SELECTED DRAWING: Figure 4

Description

The present invention relates to a working machine including a first movable member capable of linear movement and a second movable member capable of linear movement in the direction opposite to the first movable member.

Patent Document 1 describes a driving machine which is an example of a working machine including a first movable member capable of linear movement and a second movable member capable of linear movement in the direction opposite to the first movable member. There is. The driving machine described in Patent Document 1 has a housing, an electric motor, a drive mechanism, a striking portion as a first movable member, a weight as a second movable member, a spring, a magazine, and an injection portion. The electric motor, drive mechanism, striking part, weight and spring are provided in the housing.

The housing has a handle and a trigger is provided on the handle. The ejection part is attached to the housing. A contact member is provided at the injection portion. The magazine is supported by an ejection section and a housing. The stopper is housed in the magazine, and the stopper is supplied from the magazine to the ejection part. A control board for controlling the rotation and stopping of the electric motor is provided in the housing.

When the contact member is pressed against the mating material and an operating force is applied to the trigger, the control board rotates the electric motor. The rotational force of the electric motor is transmitted to the striking portion by the drive mechanism, and the striking portion is raised. When the striking portion rises, the weight is lowered and the spring is compressed. When the rotational force of the electric motor is no longer transmitted to the striking portion, the striking portion descends and strikes the stopper. When the striking portion descends, the weight is linearly moved in the direction opposite to the striking portion by the urging force of the spring. Specifically, when the spring is extended, linear energy is generated in which the lower end of the spring moves linearly downward to lower the striking portion and the upper end of the spring moves linearly upward. The weight rises while absorbing the linear energy of the upper end of the spring. Therefore, the transmission of linear energy at the upper end of the spring to the housing is suppressed, and vibration and recoil are reduced.

Japanese Unexamined Patent Publication No. 2018-202509

The inventor of the present application increases the mass of the second movable member for absorbing the linear motion energy when the first movable member tries to increase the energy for linear movement in the first direction, or the second movable member causes the second movable member. Recognized the issue of the need to increase the linear stroke.

An object of the present invention is to suppress an increase in the mass of the second movable member and to suppress an increase in the stroke in which the second movable member directly moves, thereby suppressing an increase in the size and mass of the working machine. At the same time, it is an object of the present invention to provide a working machine capable of reducing vibration and recoil generated in the working machine.

The working machine of one embodiment has a first movable member that is directly moved in a first direction to perform processing, and when the first movable member is directly moved in the first direction, it is opposite to the first direction. A work machine having a second movable member that is linearly moved in the second direction, a housing that supports the first movable member and the second movable member, and is rotatably provided in the housing. It has an inertial member and a conversion mechanism that converts the linear motion energy of the second movable member in the second direction into the rotational energy of the rotary inertial member.

The working machine of one embodiment suppresses an increase in the mass of the second movable member and suppresses an increase in the stroke in which the second movable member directly moves, thereby increasing the size of the working machine and increasing the mass. It is possible to reduce the vibration and recoil generated in the working machine while suppressing the vibration and recoil.

It is a left side sectional view of the driving machine which is one Embodiment of a working machine. (A) is a front view of the striking portion and the rotary inertia member of the driving machine, and the striking portion is at top dead center, and (B) is the striking portion and rotation shown in FIG. 2 (A). It is a left side view of the inertial member. (A) is a rear view of FIG. 2 (A), and (B) is a side sectional view taken along the line III-III of FIG. 3 (A). It is a perspective view of the striking part and the rotary inertia member which a driving machine has. (A) is a front view of the striking portion and the rotary inertia member, and the striking portion is at bottom dead center, and (B) is a cross-sectional view of the right side along the VV line of FIG. 5 (A). be. It is a perspective view of a striking part, a rotary inertia member, and a speed-increasing mechanism which a driving machine has. It is a side view of a striking part, a rotary inertia member, and a speed-increasing mechanism shown in FIG. It is a perspective view of the rotary inertia member and the winding transmission device which a driving machine has. It is a side view of the rotary inertia member and the winding transmission device shown in FIG. It is a rear view of the striking part, the rotary inertia member, and the conversion mechanism which a driving machine has. FIG. 10 is a side view showing a state in which the striking portion shown in FIG. 10 is located at the bottom dead center. FIG. 10 is a side view showing a state in which the striking portion shown in FIG. 10 is located at the top dead center.

Next, some embodiments included in the working machine will be described with reference to the drawings.

FIG. 1 shows a driving machine 10 which is an embodiment of a working machine. The driving machine 10 is, for example, a nail driving machine, and the driving machine 10 includes a housing 11, an injection unit 12, an electric motor 13, a speed reducer 14, a gear transmission device 15, a guide frame 16, a striking unit 17, and a spring 18. It has a vibration suppression mechanism 19, a control circuit 20, a battery pack 21, and a magazine 22.

The housing 11 is made of metal and synthetic resin, and the housing 11 has a tubular main body 23, a handle 24 connected to the main body 23, and a motor case 25 connected to the main body 23. Have. The handle 24 extends from the main body 23 in a direction intersecting the center line A2. The meaning of the center line A2 will be described later. The mounting portion 26 is connected to the handle 24 and the motor case 25.

The injection unit 12 is provided outside the main body 23, and the injection unit 12 is fixed to the main body 23. The injection unit 12 has an injection path 27. The magazine 22 is supported by the housing 11 and the ejection portion 12. The magazine 22 accommodates a plurality of fasteners 28 in a row. The stopper 28 is, for example, a rod-shaped nail. The magazine 22 has a feeder. The feeder sends the stopper 28 housed in the magazine 22 to the injection path 27.

The push lever 29 is attached to the injection portion 12. The user can grasp the handle 24 by hand so that the tip of the push lever 29 is brought into contact with the mating material W1 and the tip of the push lever 29 is separated from the mating material W1.

The electric motor 13 is provided in the motor case 25, and the electric motor 13 has a stator 30 and a rotor 31. The rotor 31 is attached to the motor shaft 32. The speed reducer 14 is provided in the motor case 25, and the speed reducer 14 has an input element 33, an output element 34, and a planetary gear mechanism 35. The input element 33 is connected to the motor shaft 32. When the rotational force of the motor shaft 32 is transmitted to the input element 33, the rotational speed of the output element 34 becomes lower than the rotational speed of the input element 33. The electric motor 13 and the speed reducer 14 are arranged concentrically with the center line A1 as the center. The center line A1 is a virtual line indicating the rotation center of the motor shaft 32.

The top holder 36 and the bottom holder 37 are provided in the housing 11, for example, in the main body portion 23. The top holder 36 and the bottom holder 37 are fixed in the main body 23 at intervals. Further, a plurality of, for example, two guide frames 16 are provided in the main body 23. The two guide frames 16 are both rod-shaped as shown in FIGS. 2 (A), 3 and 4, and the two guide frames 16 are provided in parallel. Both ends of the guide frame 16 in the length direction are fixed to the top holder 36 and the bottom holder 37. Further, a guide shaft 38 is provided between the top holder 36 and the bottom holder 37, and both ends of the guide shaft 38 in the length direction are fixed to the top holder 36 and the bottom holder 37.

The striking portion 17 is provided both inside and outside the main body portion 23. The striking portion 17 has a plunger 39 arranged in the main body portion 23 and a driver blade 40 fixed to the plunger 39. The plunger 39 and the driver blade 40 are both made of steel. The plunger 39 is attached to the guide shaft 38, and the plunger 39 has an engaging portion 42. The plunger 39 can reciprocate between the top holder 36 and the bottom holder 37 along the guide shaft 38.

That is, the striking portion 17 can move linearly in the direction along the center line A2 of the guide shaft 38. Further, the guide frame 16 guides the plunger 39 so that the plunger 39 does not move in the direction intersecting the center line A2. The center line A2 is a virtual line passing through the center of the guide shaft 38. The driving machine 10 shown in FIG. 1 is an example in which the center line A1 and the center line A2 are arranged so as to intersect each other, and as an example, they are arranged so as to intersect each other at an angle of about 90 degrees. The bottom holder 37 is provided between the top holder 36 and the injection portion 12 in the direction along the center line A2.

In FIGS. 2B and 3B, the striking portion 17 directly moves so that the plunger 39 approaches the bottom holder 37, the striking portion 17 operates in the first direction B1, or the striking portion 17 operates. It can be defined as a descent. The linear movement of the striking portion 17 so that the plunger 39 is separated from the bottom holder 37 can be defined as the striking portion 17 operating in the second direction B2 or the striking portion 17 rising.

The vibration suppression mechanism 19 has a slider 43, a rotational inertia member 44, and a conversion mechanism 45. The slider 43 is attached to the guide shaft 38, and the slider 43 has an engaging portion 46. The slider 43 is provided between the top holder 36 and the plunger 39 in the direction along the center line A2. The slider 43 can reciprocate between the top holder 36 and the plunger 39 along the guide shaft 38.

That is, the slider 43 can move linearly in the direction along the center line A2 of the guide shaft 38. The linear movement of the slider 43 away from the top holder 36 can be defined as the slider 43 operating in the first direction B1 or the slider 43 descending. The linear movement of the slider 43 toward the top holder 36 can be defined as the slider 43 operating in the second direction B2 or the slider 43 rising. Further, the guide frame 16 guides the slider 43 so as not to move in the direction intersecting the center line A2. The rotary inertia member 44 and the conversion mechanism 45 will be described later.

The first bumper 47 is provided between the plunger 39 and the bottom holder 37 in the direction along the center line A1. A second bumper 48 is provided between the slider 43 and the top holder 36 in the direction along the center line A1. Both the first bumper 47 and the second bumper 48 are made of synthetic rubber.

The spring 18 is provided in the main body 23. The spring 18 is a fixed spring, for example, a metal compression coil spring, and the spring 18 is provided between the plunger 39 and the slider 43 in the direction along the center line A2. The spring 18 can be expanded and contracted in the direction along the center line A2. The first end of the spring 18 in the direction along the center line A2 is in direct or indirect contact with the plunger 39. The second end of the spring 18 in the direction along the center line A2 is in direct or indirect contact with the slider 43. The spring 18 always receives a compressive load in the direction along the center line A2 from the slider 43 and the plunger 39. The spring 18 is a common element that applies a urging force in the direction along the center line A2 to the slider 43 and the plunger 39.

The gear transmission device 15 converts the rotational force of the output element 34 of the speed reducer 14 into the operating force of the striking portion 17 and the operating force of the slider 43. The gear transmission device 15 has a first gear 49, a second gear 50, and a third gear 51 as shown in FIGS. 2 (B), (A), 3 (B), and 4 (B). The material of the first gear 49, the second gear 50 and the third gear 51 may be metal, non-ferrous metal, or steel. The first gear 49 is attached to the output element 34, and the output element 34 is rotatably supported by the holding plate 52. The second gear 50 is rotatably supported by the support shaft 53 and the holding plate 52. The third gear 51 is rotatably supported by the support shaft 54 and the holding plate 52. The holding plate 52 is fixed to the housing 11. The first gear 49, the second gear 50, and the third gear 51 are provided in this order so as to approach the top holder 36 from the 12 ejection portions in the direction along the center line A2.

The second gear 50 can rotate about the axis C2. The third gear 51 is rotatable about the axis C3. The outer diameter of the first gear 49, the outer diameter of the second gear 50, and the outer diameter of the third gear 51 are the same. The second gear 50 meshes with the first gear 49 and the third gear 51. The first gear 49 has a cam roller 55, the second gear 50 has a cam roller 56, and the third gear 51 has a cam roller 57.

Further, a rotation regulation mechanism 90 is provided in the motor case 25. The rotation regulation mechanism 90 allows the output element 34 to be rotated by the rotational force transmitted from the electric motor 13, and prevents the output element 34 from being rotated by the rotational force transmitted from the first gear 49. ..

The battery pack 21 can be attached to and detached from the mounting portion 26. The battery pack 21 is a DC power source, and the battery pack 21 has a storage case 91 and a battery cell 58 housed in the storage case 91. The battery cell 58 is a secondary battery that can be charged and discharged, and the battery cell 58 can use any one of a lithium ion battery, a nickel hydrogen battery, a lithium ion polymer battery, and a nickel cadmium battery. The electric power of the battery pack 21 can be supplied to the electric motor 13.

A trigger 59 is provided on the handle 24, and a trigger switch 60 is provided on the handle 24. The trigger switch 60 detects that the operating force is applied to the trigger 59 and that the operating force applied to the trigger 59 is released, and outputs a signal. The push lever switch 61 is provided in, for example, the magazine 22. The push lever switch 61 detects that the push lever 29 is in contact with the mating material W1 and that the push lever 29 is separated from the mating material W1, and outputs a signal. The slider detection switch 62 is provided in the main body 23. The slider detection switch 62 detects the position of the slider 43 in the direction along the center line A2 and outputs a signal. Although not shown, a phase detection sensor for detecting the position of the motor shaft 32 in the rotation direction is provided in the motor case 25. The inverter circuit 63 is provided in the motor case 25. The inverter circuit 63 has a plurality of switching elements, and connects and disconnects the electric circuit between the battery pack 21 and the stator 30 of the electric motor 13.

The control circuit 20 is provided in the housing 11, for example, in the mounting portion 26. The control circuit 20 is a microcomputer having an input port, an output port, a central processing unit, a storage device, and the like. The control circuit 20 controls the inverter circuit 63 by processing the signal of the trigger switch 60, the signal of the push lever switch 61, the signal of the slider detection switch 62, and the signal of the phase detection sensor. That is, the control circuit 20 controls the rotation, stop, and rotation speed of the electric motor 13. The control circuit 20 estimates the position of the striking portion 17 in the direction along the center line A2 by processing the signal of the phase detection sensor and the signal of the slider detection switch 62.

An example in which the user uses the driving machine 10 is as follows. When the control circuit 20 detects at least one of the fact that the operating force for the trigger 59 is released and the push lever 29 is separated from the mating material W1, the power supply to the electric motor 13 is stopped. .. Therefore, the motor shaft 32 of the electric motor 13 is stopped. When the electric motor 13 is stopped, the striking portion 17 is stopped at the standby position. The standby position of the striking portion 17 is the position of the striking portion 17 in a state where the plunger 39 is separated from the first bumper 47.

The cam roller 55 of the first gear 49 is released from the engaging portion 42, and the cam roller 56 of the second gear 50 is engaged with the engaging portion 42. The plunger 39 is urged by the spring 18 in the first direction B1. The urging force received by the plunger 39 is transmitted to the second gear 50 via the engaging portion 42 and the cam roller 56, and the second gear 50 receives the rotational force. The rotational force received by the second gear 50 is transmitted to the output element 34 via the first gear 49. The rotation regulation mechanism 90 prevents the output element 34 from being rotated by the rotational force transmitted from the first gear 49 to the output element 34. In this way, the striking portion 17 is stopped at the standby position.

Further, when the striking portion 17 is stopped at the standby position, the cam roller 57 of the third gear 51 is engaged with the engaging portion 46. The slider 43 is urged by the spring 18 in the second direction B2. The urging force received by the slider 43 is transmitted to the third gear 51 via the engaging portion 46 and the cam roller 57, and the third gear 51 receives the rotational force. The rotational force received by the third gear 51 is transmitted to the output element 34 via the second gear 50 and the first gear 49. The output element 34 is prevented from rotating by the rotation regulation mechanism 90. Therefore, the slider 43 is stopped at a standby position separated from the second bumper 48.

When the control circuit 20 detects that an operating force is applied to the trigger 59 and that the push lever 29 is in contact with the mating material W1, the battery pack 21 supplies electric power to the electric motor 13. When the motor shaft 32 of the electric motor 13 is rotated, the rotational force of the motor shaft 32 is transmitted to the first gear 49 via the speed reducer 14.

Then, the striking portion 17 is operated in the second direction B2 by the rotation of the second gear 50. Further, the rotation of the third gear 51 causes the slider 43 to be operated in the first direction B1. Then, when the cam roller 56 of the second gear 50 is released from the engaging portion 42, the striking portion 17 is operated in the first direction B1 by the urging force of the spring 18. When the striking portion 17 is operated in the first direction B1, the driver blade 40 strikes the stopper 28 of the injection path 27. The hit stopper 28 is driven into the mating material W1.

After the driver blade 40 hits the stopper 28, the plunger 39 collides with the first bumper 47. The first bumper 47 absorbs a part of the linear motion energy of the striking portion 17. As shown in FIGS. 5A and 5B, the position of the striking portion 17 in the state where the plunger 39 is in contact with the first bumper 47 is the bottom dead center. As shown in FIGS. 2B and 3B, the position of the striking portion 17 in the state where the plunger 39 is most distant from the first bumper 47 is the top dead center.

Further, when the cam roller 57 of the third gear 51 is released from the engaging portion 46, the slider 43 is operated in the second direction B2 by the urging force of the spring 18. Then, the slider 43 collides with the second bumper 48. The second bumper 48 absorbs a part of the linear energy of the slider 43.

Further, the tip of the push lever 29 is separated from the mating material W1 by the reaction of completely driving the stopper 28 into the mating material W1. However, the control circuit 20 keeps the electric motor 13 rotating. Therefore, the cam roller 55 of the first gear 49 is engaged with the engaging portion 42, and the striking portion 17 is operated in the second direction B2 from the bottom dead center. Further, the cam roller 57 of the third gear 51 is engaged with the engaging portion 46, and the slider 43 is operated in the first direction B1. Further, the cam roller 56 of the second gear 50 is engaged with the engaging portion 42 before the cam roller 55 of the first gear 49 is released from the engaging portion 42.

Then, when the cam roller 55 of the second gear 50 is released from the engaging portion 42 and the striking portion 17 reaches the standby position, the control circuit 20 stops the electric motor 13. Therefore, the striking portion 17 is held in the standby position by the rotation regulating mechanism 90. Further, the slider 43 is stopped at a position separated from the second bumper 48.

In the vibration suppression mechanism 19, the spring 18 is extended and the lower end portion of the spring 18 moves directly in the first direction B1. When the striking portion 17 is linearly moved in the first direction B1, the linear motion energy in which the upper end of the spring 18 is linearly moved in the second direction B2 is transmitted to the housing 11 to suppress the housing 11 from vibrating. do. The vibration suppression mechanism 19 is provided inside the housing 11. The slider 43 has an arm portion 64 in addition to the engaging portion 46. A plurality of arm portions 64, for example, two arm portions 64 are provided. The two arm portions 64 are substantially L-shaped in a plane perpendicular to the center line A1. The two arm portions 64 are provided line-symmetrically with respect to the center line A2 in a plane perpendicular to the center line A1. The two arms 64 each have a rack 65. The rack 65 is provided over a predetermined range in the direction along the center line A2.

The support shaft 66 is provided on each of the two guide frames 16. The support shaft 66 is provided so as not to move with respect to the guide frame 16 in either the direction along the center line A2 or the direction intersecting the center line A2. The rotary inertia member 44 is attached to each of the two support shafts 66. The rotational inertia member 44 is rotatable about the support shaft 66, respectively.

The density of the material constituting at least a part of the rotary inertia member 44 is higher than the density of the material constituting at least a part of the slider 43. The material constituting at least a part of the slider 43 is, for example, steel. The material constituting at least a part of the rotary inertia member 44 is, for example, lead or copper. Further, the thickness of the rotational inertia member 44 in the direction along the rotation center line D1 is larger in the thickness T2 of the outer portion 44B than in the thickness T1 of the inner portion 44A. The outer portion 44B is located outside the inner portion 44A in the radial direction of the rotational inertia member 44. The mass of the slider 43 is smaller than the mass of the rotary inertia member 44. The mass of the slider 43 is smaller than the mass of the striking portion 17. The mass of the rotary inertia member 44 is larger than the mass of the striking portion 17.

The rotary inertia member 44 can both be defined as a disk-shaped flywheel or weight. The pinion gear 67 is provided concentrically with the rotary inertia member 44. The pinion gear 67 can rotate around the support shaft 66 integrally with the rotary inertia member 44. The pinion gear 67 meshes with the rack 65. The conversion mechanism 45 is a mechanism that converts the direct power of the slider 43 into the rotational force of the rotational inertia member 44. The conversion mechanism 45 is composed of a rack 65 and a pinion gear 67. In a plane perpendicular to the center line A1, the two guide frames 16 are provided between the two rotational inertia members 44, and the spring 18 is provided between the two guide frames 16. .. Further, a third gear 51 is provided between the second gear 50 and the support shaft 66 in the direction along the center line A2.

The vibration suppressing mechanism 19 suppresses the vibration of the housing 11 as follows. When the slider 43 is linearly moved in the second direction B2 by the urging force of the spring 18, the direct power of the slider 43 is converted into the rotational force of the rotational inertia member 44 by the rack 65 and the pinion gear 67. The rotational inertia member 44 is rotated by the clockwise moment F2 in FIG. That is, a part of the linear energy of the slider 43 is converted into the rotational energy of the rotational inertia member 44. As described above, in the vibration suppression mechanism 19, when the striking portion 17 operates in the first direction B1, the upper end portion of the spring 18 converts the linear motion energy operated in the second direction B2 into rotational energy and absorbs it. Then, it receives the linear energy of the upper end portion of the spring 18. Therefore, it is possible to suppress the housing 11 from vibrating.

Further, the rotary inertia member 44 rotates about the support shaft 66. However, the rotational inertia member 44 does not operate in the direction along the center line A2. That is, it is possible to suppress an increase in the stroke amount in which the slider 43 operates in the direction along the center line A2. Therefore, it is possible to prevent the driving machine 10 from increasing in size in the direction along the center line A2.

Further, as the moment of inertia in the rotational direction of the rotary inertial member 44 increases, the operating energy of the slider 43 is easily absorbed by the rotary inertial member 44. Further, the moment of inertia in the rotational direction of the rotary inertial member 44 is proportional to the square of the outer diameter of the rotary inertial member 44. Therefore, it is possible to suppress an increase in the mass of the rotary inertia member 44. Therefore, it is possible to suppress an increase in the total weight of the driving machine 10.

Further, the housing 11 receives a counterclockwise rotational moment F1 about the center of gravity Q1 shown in FIG. 1 due to a reaction force in which the striking portion 17 operates in the first direction B1 and drives the stopper 28 into the mating material W1. The center of gravity Q1 is located in the plane including the center line A1 and the center line A2, for example, within the arrangement range of the trigger 59. The center of gravity Q1 is located between the rotary inertial member 44 and the push lever 29 in the direction along the center line A2.

On the other hand, the rotational inertia member 44 receives a clockwise rotational moment in FIG. 1 when the striking portion 17 operates in the first direction B1. Therefore, the rotational moment of the rotational inertia member 44 cancels out a part of the rotational moment of the housing 11. Therefore, it is possible to suppress an increase in the amount of rotation of the housing 11 by the counterclockwise rotation moment F1 about the center of gravity Q1 due to the reaction force of the striking portion 17 driving the stopper 28 into the mating material W1. Therefore, it is possible to prevent the tip of the push lever 29 from being separated from the mating material W1 before the stopper 28 is completely driven into the mating material W1.

Further, the two guide frames 16, the two support shafts 66, the two rotational inertia members 44, and the two pinion gears 67 are arranged line-symmetrically, that is, left-right symmetrically with respect to the center line A2. .. Therefore, the mass balance of the driving machine 10 centered on the center line A2 is stable.

6 and 7 show an example in which the speed increasing mechanism 76 is provided in the power transmission path between the slider 43 and the rotational inertia member 44. The speed increasing mechanism 76 is provided on each of the two guide frames 16. The speed-increasing mechanism 76 has a support shaft 68 attached to the guide frame 16 and an intermediate gear 69 rotatably supported by the support shaft 68. The intermediate gear 69 meshes with the rack 65 and the pinion gear 67. Further, the outer diameter of the intermediate gear 69 is larger than the outer diameter of the pinion gear 67. That is, the number of teeth of the intermediate gear 69 is larger than the number of teeth of the pinion gear 67. The conversion mechanism 45 includes a rack 65, an intermediate gear 69, and a pinion gear 67.

When the slider 43 is linearly moved in the second direction B2, the direct power of the slider 43 is converted into the rotational force of the intermediate gear 69, and the rotational force of the intermediate gear 69 is transmitted to the pinion gear 67 and the rotational inertia member 44. .. Therefore, it is possible to suppress the vibration of the housing 11.

Further, the speed increasing mechanism 76 makes the rotation speed of the pinion gear 67 higher than the rotation speed of the intermediate gear 69. Therefore, the torque required to rotate the pinion gear 67 is higher when the intermediate gear 69 is present than when the intermediate gear 69 is not present. Therefore, assuming that the linear energy of the slider 43 is the same, the outer diameter of the rotary inertia member 44 in the presence of the intermediate gear 69 is smaller than the outer diameter of the rotary inertia member 44 in the absence of the intermediate gear 69. Therefore, it is possible to suppress the increase in size of the vibration suppression mechanism 19.

8 and 9 show an example in which the winding transmission device 71 is provided in the power transmission path between the slider 43 and the rotational inertia member. The winding transmission device 71 has a first pulley 72, a second pulley 73, and a belt 75. The first pulley 72 is provided concentrically with the pinion gear 67, and the first pulley 72 and the pinion gear 67 are integrally rotated around the support shaft 66. The support shaft 66 is provided on each of the guide frames 16.

The second pulley 73 is a rotary inertia member. The second pulley 73 is rotatably supported by a support shaft 77 provided on the guide frame 16. The second pulley 73 is provided at a distance from the first pulley 72 in the direction along the center line A2. The second pulley 73 is provided between the first pulley 72 and the first bumper 47 in the direction along the center line A2. The belt 75 is annular, that is, endless, and the belt 75 is wound around the first pulley 72 and the second pulley 73. The density of at least a part of the material constituting the second pulley 73 is higher than the density of at least a part of the material constituting the slider 43. At least a part of the material of the second pulley 73 is made of lead or copper. Further, the thickness of the second pulley 73 in the direction along the rotation center line is larger in the thickness T4 of the outer portion 73B than in the thickness T3 of the inner portion 73A. In the radial direction of the second pulley 73, the outer portion 73B is located outside the inner portion 73A. The conversion mechanism 45 includes a rack 65, a pinion gear 67, a first pulley 72, and a belt 75.

A part of the linear motion energy in the center line A2 direction of the slider 43 is converted into the rotational energy of the pinion gear 67 and the first pulley 72, and the rotational energy of the first pulley 72 is transferred to the second pulley 73 via the belt 75. Be transmitted. In this way, a part of the linear energy of the slider 43 is converted into the rotational energy of the second pulley 73. Therefore, it is possible to suppress the vibration of the housing 11. Further, since the first pulley 72 and the second pulley 73 are connected by a belt 75 so as to be able to transmit power, it is possible to increase the degree of freedom in designing the arrangement position of the second pulley 73 in the direction along the center line A2. can.

The outer diameter of the first pulley 72 may be larger than the outer diameter of the second pulley 73, the outer diameter of the first pulley 72 may be the same as the outer diameter of the second pulley 73, and the first The outer diameter of the pulley 72 may be smaller than the outer diameter of the second pulley 73.

10, 11, and 12 show other examples of the conversion mechanism 45. The conversion mechanism 45 has pins 78, 89 and a link 80. The pin 78 is provided on the slider 43. The pin 79 is provided on the rotary inertia member 44. The link 80 connects the pin 78 and the pin 79. The guide frame 16 is provided with a guide hole 81. When the slider 43 is linearly moved in the direction along the center line A2, the pin 78 moves in the guide hole 81 in the direction along the center line A2. The pin 79 is provided on the rotary inertia member 44 and is provided at a position eccentric from the support shaft 66.

The striking portion 17 is actuated in the first direction B1 after being actuated to the top dead center as shown in FIG. 12, and the striking portion 17 reaches the bottom dead center as shown in FIG. When the striking portion 17 is operated in the first direction and the slider 43 is linearly moved in the second direction B2, the rotational force of the slider 43 is transmitted to the rotational inertia member 44 by the link 80, and the rotational inertia member 44 Is rotated. That is, the linear energy of the slider 43 is converted into the rotational energy of the rotational inertia member 44. Therefore, the vibration suppressing mechanism 19 can suppress the housing 11 from vibrating due to the reaction force that the striking portion 17 operates in the first direction B1.

An example of the technical meaning of the matters disclosed in this embodiment is as follows. The driving machine 10 is an example of a working machine. The first direction B1 is an example of the first direction. The second direction B2 is an example of the second direction. The striking portion 17 is an example of the first movable member and the striking portion. It is an example of the process performed by the first movable member that the striking portion 17 is directly moved in the first direction B1 to strike the stopper 28. The slider 43 is an example of the second movable member. The housing 11 is an example of a housing. The spring 18 is an example of an elastic member, and the rotary inertia member 44 is an example of a rotary inertia member.

The conversion mechanism 45 is an example of the conversion mechanism. The rack 65 is an example of a rack. The pinion gear 67 is an example of a pinion. The intermediate gear 69 is an example of an auxiliary rotating member. The speed-increasing mechanism 76 is an example of the speed-increasing mechanism. The first pulley 72 is an example of a first inertial member, the second pulley 73 is an example of a second inertial member, and the belt 75 is an example of a wound transmission member. The guide frame 16 is an example of a support member. The injection unit 12 is an example of an injection unit. The magazine 22 is an example of a magazine. The electric motor 13 and the gear transmission device 15 are examples of the drive unit.

The engaging portions 42, 46 and the cam rollers 55, 56, 57 are examples of the clutch mechanism. The engaging portion 42 and the cam rollers 55 and 56 are examples of the first path. It is the connection of the first path that at least one of the cam rollers 55 and 56 is engaged with the engaging portion 42. The release of both the cam rollers 55 and 56 from the engaging portion 42 is the interruption of the first path. The engaging portion 46 and the cam roller 57 are examples of the second path. Engaging the cam roller 57 with the engaging portion 46 is the connection of the second path. The release of the cam roller 57 from the engaging portion 46 is the interruption of the second path.

The working machine is not limited to the above-described embodiment, and can be variously changed without departing from the gist thereof. For example, the rotational inertia member may be rotatably supported by a housing. It is also possible to provide fins or blades on the rotary inertia member. If the rotary inertia member is provided with fins or blades, the air resistance when the rotary inertia member is rotated increases. Therefore, the effect that the rotational inertia member body absorbs a part of the operating energy of the slider is increased.

The first timing at which the first movable member starts linear movement in the first direction and the second timing at which the second movable member starts linear movement in the second direction may be the same or different. good. An example of a configuration for changing the first timing and the second timing is to change the position of the cam roller in the rotation direction of the second gear and the position of the cam roller in the rotation direction of the third gear.

Further, even if the clutch mechanism cuts off the second path, the second movable member is locked so as not to move linearly in the second direction immediately, and is synchronized with the timing when the first movable member starts to move linearly in the first direction. It is also possible to provide a lock mechanism for unlocking the second movable member.

Further, a one-way clutch may be provided to connect and disconnect the power transmission path between the slider and the rotational inertia member. The one-way clutch connects the power transmission path when the slider moves linearly in the second direction. The one-way clutch shuts off the power transmission path when the slider operates in the first direction. Therefore, it is possible to prevent a part of the energy in which the slider moves linearly in the first direction from being converted into the rotational energy of the rotational inertia member. That is, when the striking portion is directly moved in the second direction, the load on the electric motor can be reduced.

The first inertial member and the second inertial member may be the first sprocket and the second sprocket, and the winding transmission member may be a chain wound around the first sprocket and the second sprocket. As the speed increasing mechanism, it is possible to use a plurality of rollers having different outer diameters instead of a plurality of gears having different outer diameters. As the conversion mechanism, any of a link mechanism, a crank mechanism, and a cam mechanism can be used instead of the rack and pinion mechanism. The solid spring used as an elastic member includes a synthetic rubber as well as a metal spring. The elastic member also includes a solid spring and a gas spring. The rotating member disclosed in the present embodiment includes a gear train that transmits a rotational force by an engaging force and a roller train that transmits a rotational force by a frictional force.

Stoppers in the driving machine include rod-shaped nails, as well as arch-shaped tackers and studs. The driving machine may be a nail gun, a stapler, or a tacking machine. The standby position of the striking portion may be the bottom dead center. In this case, the plunger comes into contact with the second bumper and is stopped. The power source for supplying electric power to the electric motor may be either a DC power source or an AC power source.

The following driving machine is also disclosed in the present embodiment.

The first driving machine is
The striking part that is directly moved in the first direction of the field and hits the stopper,
A housing that supports the striking part and
A vibration suppression mechanism that suppresses vibration of the housing when the striking portion is directly moved in the first direction.
It is a driving machine with
The vibration suppression mechanism is
A movable member provided in the housing and linearly moved in a second direction opposite to the first direction when the striking portion is linearly moved in the first direction.
A rotary inertial member rotatably provided in the housing and
A conversion mechanism that converts the linear energy in which the movable member is linearly moved in the second direction into the rotational energy of the rotational inertia member.
including.

The second driving machine is, in addition to the configuration of the first driving machine,
A support member that movably supports the striking portion and the movable member,
A common elastic member provided between the striking portion and the movable member and which directly moves the striking portion and the movable member by applying an urging force to the striking portion and the movable member.
Further have.

The working machine of the present embodiment is not limited to the driving machine, and may be a hammer drill or a hammer driver disclosed in Japanese Patent Application Laid-Open No. 2013-212543. The hammer possessed by the hammer drill or hammer driver is an example of the first movable member. The inertial mass pair provided on the hammer or hammer drill as a vibration reducing mechanism is an example of the second movable member. Further, the hammer hitting, crushing, or breaking the mating material at least is an example of the processing performed by the first movable member.

10 ... driving machine, 11 ... housing, 12 ... injection part, 13 ... electric motor, 15 ... gear transmission device, 16 ... guide frame, 17 ... striking part, 18 ... spring, 22 ... magazine, 42, 46 ... engagement Part, 43 ... Slider, 44 ... Rotational inertia member, 45 ... Conversion mechanism, 55, 56, 57 ... Cam roller, 65 ... Rack, 67 ... Pinion gear, 69 ... Intermediate gear, 72 ... First pulley, 73 ... Second pulley, 75 ... belt, 76 ... speed-increasing mechanism, B1 ... first direction, B2 ... second direction

Claims (10)

The first movable member that is directly moved in the first direction to perform processing,
When the first movable member is linearly moved in the first direction, the second movable member that is linearly moved in the second direction opposite to the first direction,
A housing that supports the first movable member and the second movable member,
It is a working machine with
A rotary inertial member rotatably provided in the housing and
A conversion mechanism that converts the linear energy of the second movable member in the second direction into the rotational energy of the rotational inertia member.
Has a working machine. The working machine according to claim 1, further comprising an elastic member for linearly moving the first movable member in the first direction and linearly moving the second movable member in the second direction. The working machine according to claim 1 or 2, wherein the density of the material constituting at least a part of the rotary inertia member is higher than the density of the material constituting at least a part of the second movable member. The conversion mechanism is
The rack provided on the second movable member and
With the pinion meshed with the rack and connected to the rotary inertia member,
The working machine according to any one of claims 1 to 3, comprising the above. The conversion mechanism is
An auxiliary rotating member in which linear energy is transmitted from the second movable member and is rotated, and rotational energy is transmitted to the rotational inertia member.
A speed-increasing mechanism that increases the rotational speed of the rotational inertia member to be higher than the rotational speed of the auxiliary rotating member.
The working machine according to any one of claims 1 to 4, comprising the above. The rotary inertia member is
The first inertial member, which is rotated by transmitting the linear energy of the second movable member,
The second inertial member, which is rotated by transmitting the rotational energy of the first inertial member,
The winding transmission member wound around the first inertial member and the second inertial member, and
The working machine according to any one of claims 1 to 4, comprising the above. A support member for supporting the first movable member and the second movable member in a linear motion with respect to the housing is further provided.
The working machine according to any one of claims 1 to 6, wherein the rotary inertia member and the conversion mechanism are supported by the support member. The injection part provided in the housing and
A magazine provided in the housing and accommodating a stopper to be supplied to the injection portion.
A drive unit that directly moves the first movable member in the second direction,
Is further provided,
The work according to any one of claims 1 to 6, wherein the first movable member is a striking portion that strikes the stopper supplied to the injection portion by being linearly moved in the first direction. Machine. The drive unit
With an electric motor
The gear transmission device rotated by the power of the electric motor and
8. The working machine according to claim 8. A clutch that can connect and disconnect the first path that transmits the power of the drive unit to the first movable member, and can connect and disconnect the second path that transmits the power of the drive unit to the second movable member. Further mechanism is provided,
The first movable member can be linearly moved in the second direction when the clutch mechanism is connected to the first path, and can be linearly moved in the first direction when the clutch mechanism shuts off the first path. And
The second movable member can be linearly moved in the first direction when the clutch mechanism is connected to the second path, and can be linearly moved in the second direction when the clutch mechanism shuts off the second path. The working machine according to claim 8 or 9.

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