JPWO2018159171A1 - Impact working machine - Google Patents

Impact working machine Download PDF

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Publication number
JPWO2018159171A1
JPWO2018159171A1 JP2018002444A JP2019502510A JPWO2018159171A1 JP WO2018159171 A1 JPWO2018159171 A1 JP WO2018159171A1 JP 2018002444 A JP2018002444 A JP 2018002444A JP 2019502510 A JP2019502510 A JP 2019502510A JP WO2018159171 A1 JPWO2018159171 A1 JP WO2018159171A1
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JP
Japan
Prior art keywords
portion
holding
center line
direction
tip tool
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Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
JP2018002444A
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Japanese (ja)
Inventor
康平 脇田
康平 脇田
Original Assignee
工機ホールディングス株式会社
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Priority to JP2017037163 priority Critical
Priority to JP2017037163 priority
Application filed by 工機ホールディングス株式会社 filed Critical 工機ホールディングス株式会社
Priority to PCT/JP2018/002444 priority patent/WO2018159171A1/en
Publication of JPWO2018159171A1 publication Critical patent/JPWO2018159171A1/en
Granted legal-status Critical Current

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    • BPERFORMING OPERATIONS; TRANSPORTING
    • B25HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25DPERCUSSIVE TOOLS
    • B25D17/00Details of, or accessories for, portable power-driven percussive tools
    • B25D17/08Means for retaining and guiding the tool bit, e.g. chucks allowing axial oscillation of the tool bit

Abstract

Provided is a striking work machine capable of suppressing radial movement of a tip tool relative to a holder. A cylindrical holder 23 for holding the held portion 86 of the tip tool 83, and a striker capable of moving in the direction of the center line A1 of the holder 23 and striking the tip tool 83 held by the holder 23 And the holder 23 is a first holding portion 73 for holding the held portion 86 in a state that the tip tool 83 can be hit with a striker, and the first holding portion 73 in the direction of the center line A1. A second holding portion 74 which is disposed at a position different from the portion 73 and which holds the held portion 86 such that the tip tool 83 can not be hit by the striker, and contacts the held portion 86 and which is held And a restricting portion 91 which restricts the movement of the second holding portion 74 from the second holding portion 74 to the first holding portion 73. The restricting portion 91 rotates the held portion 86 about the center line A1. Moving the held portion 86 from the second holding portion 74 to the first holding portion 73 Tolerated.

Description

The present disclosure relates to an impact working machine that applies an impact force to a tip tool with a striker.

An impact working machine that applies an impact force to a tip tool with a striker is described in Patent Document 1. The striking work machine described in Patent Document 1 includes a holder, an intermediate element, a cylinder, an impact element, a piston, a retainer, and an air chamber. The holder holds the tip tool, and the cylinder movably supports the meson. The striker is movably disposed in the cylinder, and the piston is movably disposed in the cylinder. An air chamber is formed in the cylinder between the piston and the striker. A retainer is provided on the holder. The tip tool has a convex portion. The holder has a holding hole, and the holding hole is provided with a step. In the case of the driving machine described in Patent Document 1, when the end tool hits the stopper and the spring rises, the convex portion abuts on the step, and the moving speed of the end tool is reduced.

JP-A-58-120474

However, in the striking work machine described in Patent Document 1, since the inner diameter of the holding hole of the holder needs to be a size that allows the convex portion to move, the tip tool moves in the radial direction in the holding hole to work There was a possibility that the sex would decline.

An object of the present disclosure is to provide a striking work machine capable of suppressing radial movement of a tip tool relative to a holder.

A striking work machine according to one embodiment includes a cylindrical holder for holding a held portion of a tip tool, and the tip tool movable in the direction of the center line of the holder and held by the holder. An impact working machine having an impacting element for impacting, wherein the holder is a first holding portion for holding the held portion so that the tip tool can be struck with the impacting element; A second holding portion disposed at a position different from the first holding portion and holding the held portion such that the tip tool can not be struck by the striker; and the object to be held by the second holding portion And a restricting portion that restricts the movement of the held portion from the second holding portion to the first holding portion by contacting the holding portion, the restricting portion including the held portion. By rotating around the center line, the held portion is in front of the second holding portion. It allows to move the first holding unit.

According to the striking operation machine of one embodiment, it is possible to suppress the radial movement of the tip tool relative to the holder.

It is a front sectional view showing an embodiment of a striking operation machine of the present invention. It is a partial front sectional view of the striking working machine of FIG. It is side surface sectional drawing in the D1-D1 line of FIG. FIG. 3 is a partial cross-sectional view of FIG. FIG. 3 is a partial cross-sectional view of FIG. It is side surface sectional drawing in the D2-D2 line | wire of FIG. It is side surface sectional drawing in D3-D3 line | wire of FIG. It is side surface sectional drawing in D3-D3 line | wire of FIG. It is side surface sectional drawing in the D4-D4 line | wire of FIG. It is a front view showing an example of a tip tool which can be used with a striking operation machine. It is a state which hold | maintained the front-end tool of FIG. 10 by the front cover, and is side surface sectional drawing in D2-D2 line | wire of FIG. It is a state which hold | maintained the front-end tool of FIG. 10 by a front cover, and is side surface sectional drawing in D4-D4 line | wire of FIG. It is a partial front sectional view which shows the other example of a striking operation machine. It is a partial front sectional view which shows the other example of a striking operation machine. It is side surface sectional drawing in D7-D7 line | wire of FIG. It is side surface sectional drawing in the D5-D5 line | wire of FIG. It is a front view of the tip tool used with the striking operation machine of FIG. It is side surface sectional drawing in the D6-D6 line of FIG. It is front sectional drawing to which the principal part of the striking operation machine of FIG. 14 was expanded.

Hereinafter, an embodiment of a striking operation machine of the present disclosure will be described based on the drawings. In each of the drawings, the same members are denoted by the same reference numerals.

The striking work machine 10 shown in FIG. 1 is a hammer drill. The striking work machine 10 has a casing 11, a crank mechanism 12 and an electric motor 13. The casing 11 has a gear case 14, a crankcase 15, a cover 16, a motor case 17, a handle 18 and a front case 19. The gear case 14 is disposed between the crankcase 15 and the motor case 17. The cover 16 is attached to the outside of the crankcase 15. The handle 18 is fixed to the gear case 14, and the motor case 17 is fixed to the gear case 14. A trigger 20 is provided on the handle 18. Further, the power cable 21 is attached to the handle 18. The power cable 21 is connected to a power source, for example, an AC power source.

The crankcase 15 is made of metal, and the front case 19 is fixed to the crankcase 15. The front case 19 has a cylindrical shape, and the cylinder 22 is disposed in the crankcase 15 and in the front case 19. A front cover 23 is attached to the front case 19. The front case 19 is disposed between the front cover 23 and the crankcase 15 in a direction along the center line A 1 of the front case 19. The center line A1 is common to the center of the cylinder 22.

A piston 24 is provided in the cylinder 22. The piston 24 is operable relative to the cylinder 22 in the direction of the center line A1. A seal member 25 is attached to the outer peripheral surface of the piston 24, and the seal member 25 contacts the inner peripheral surface of the cylinder 22 to form a seal surface.

The electric motor 13 is provided in a motor case 17. The electric motor 13 has an annular stator 26 and a rotor 27 disposed inside the stator 26. The output shaft 28 is fixed to the rotor 27, and the output shaft 28 and the rotor 27 are rotatable around a center line A2. The output shaft 28 is rotatably supported by bearings 29 and 30, and a drive gear 31 is provided on the outer peripheral surface of the output shaft 28.

Further, a storage chamber 32 is formed between the gear case 14 and the crankcase 15. The crank mechanism 12 is provided in the crankcase 15. The crank mechanism 12 is a motion conversion mechanism that converts the rotational force of the output shaft 28 into the operating force of the piston 24. The crank mechanism 12 has a driven gear 33 meshing with the drive gear 31, a crankshaft 34 to which the driven gear 33 is fixed, and a connecting rod 35 connecting the crankshaft 34 and the piston 24. The crankshaft 34 is rotatably supported by bearings 36 and 37 about a center line A3. The crankshaft 34 has a crank pin 38. The crank pin 38 is disposed at a position eccentric to the center line A3. The crank pin 38 revolves around the center line A3 when the crankshaft 34 rotates. The connecting rod 35 is connected to the crank pin 38.

An annular bevel gear 39 is attached to the outer peripheral surface of the cylinder 22. The bevel gear 39 rotates integrally with the cylinder 22. A rotational force transmission shaft 40 is provided across the storage chamber 32 and the crankcase 15. The rotational force transmission shaft 40 is rotatably supported by the gear case 14 and the crankcase 15 via the bearings 41 and 42. The center line A4 of the rotational force transmission shaft 40 is parallel to the center line A3. The rotational force transmission shaft 40 is an element for transmitting the rotational force of the output shaft 28 to the bevel gear 39, and a pinion gear 43 is provided on the rotational force transmission shaft 40. The pinion gear 43 meshes with the bevel gear 39. Further, the driven gear 44 is fixed to the rotational force transmission shaft 40, and the driven gear 44 meshes with the drive gear 31.

The cylinder 22 and the bevel gear 39 are rotatably supported by the crankcase 15 via a bearing 45. The bevel gear 39 is positioned relative to the crankcase 15 by a bearing 45 in the direction of the center line A1. The cylinder 22 is rotatably supported by the front case 19 via a bearing 46. Air passages 47 and 48 are provided in the cylinder 22. The air passages 47, 48 are provided to penetrate the cylinder 22 in the radial direction. The air passage 47 and the air passage 48 are disposed at different positions in the direction of the center line A1. The air passage 47 is disposed between the center line A3 and the air passage 48 in the direction of the center line A1.

An elongated hole 49 penetrating the cylinder 22 in the radial direction is provided. The long hole 49 is provided between the front cover 23 and the air passage 48 in the direction of the center line A1. An annular stopper 50 is provided on the inner peripheral surface of the cylinder 22. The stopper 50 is provided between the front cover 23 and the long hole 49 in the direction of the center line A1.

As shown in FIG. 2, a driver 51 is provided in the cylinder 22 and the front cover 23. The driver 51 has a cylindrical shape, and the driver 51 rotates integrally with the cylinder 22. The driver 51 has a first cylindrical portion 75 and a second cylindrical portion 76. The second cylindrical portion 76 has a guide hole 52, and the second cylindrical portion 76 has a holding hole 53. The outer diameter of the second cylindrical portion 76 is larger than the outer diameter of the first cylindrical portion 75. The guide hole 52 and the holding hole 53 are provided around the center line A1. The guide hole 52 is provided between the holding hole 53 and the stopper 50 in the direction of the center line A1. The inner peripheral surface of the guide hole 52 has a circular cross-sectional shape in a plane perpendicular to the center line A1. The inner circumferential surface of the holding hole 53 has a polygonal sectional shape in a plane perpendicular to the center line A1. The inner peripheral surface shape of the holding hole 53 is a hexagon as shown in FIG. The inner diameter of the guide hole 52 is larger than the maximum inner diameter of the holding hole 53. A stopper surface 54 is provided on the inner surface of the driver 51. The stopper surface 54 is an annular tapered surface inclined with respect to the center line A1.

A bumper 55 and two spacers 56 and 57 are disposed between the driver 51 and the stopper 50. The bumper 55 is disposed between the spacer 56 and the spacer 57 in the direction of the center line A1. The bumper 55 is an annular synthetic rubber, and the spacers 56 and 57 are made of metal and are annular.

An intermediate striker 58 is disposed in the driver 51 and in the cylinder 22. The middle striker 58 is movable along the guide hole 52 in the direction of the center line A1. The intermediate striking element 58 has its movement range in the direction of the center line A1 restricted by the stopper surface 54 and the spacer 56. The middle striker 58 has a first shaft 93, a second shaft 60 and a third shaft 59. The second shaft portion 60 is provided between the third shaft portion 59 and the first shaft portion 93 in the center line A1 direction. The outer diameter of the second shaft portion 60 is larger than the outer diameter of the third shaft portion 59 and smaller than the outer diameter of the first shaft portion 93. The first shaft portion 93 is disposed in the guide hole 52 of the second cylindrical portion 76. The first shaft 93 is movable in the guide hole 52 in the direction of the center line A1.

The biasing force transmission element 61 is attached to the outer peripheral surface of the third shaft portion 59. The biasing force transmitting element 61 is made of metal and is annular as shown in FIG. An engagement protrusion 62 radially protrudes from the outer peripheral surface of the biasing force transmission element 61 is provided. The engagement protrusion 62 is disposed in the elongated hole 49. The engagement protrusion 62 is movable in the elongated hole 49 in the direction of the center line A1. A ring 63 and a bumper 64 are provided between the biasing force transmission element 61 and the second shaft portion 60. The ring 63 is made of metal, and the bumper 64 is made of synthetic rubber.

A resin sleeve 65 is attached to the outer peripheral surface of the cylinder 22. The sleeve 65 is movable relative to the cylinder 22 in the direction of the center line A1. An engagement groove 66 is provided at an end of the sleeve 65 in the direction of the center line A1, and the engagement protrusion 62 is disposed in the engagement groove 66. A metal collar 67 is attached to the outer peripheral surface of the cylinder 22. The collar 67 has a cylindrical shape and is disposed between the collar 67 and the bevel gear 39 in the direction of the center line A1. The collar 67 is movable relative to the cylinder 22 in the direction of the center line A1.

A metal spring 68 is attached to the outer peripheral surface of the cylinder 22. The spring 68 is a compression spring, and is provided between the collar 67 and the bevel gear 39 in a compressed state. The biasing force of the spring 68 in the direction of the center line A 1 is transmitted to the sleeve 65 via the collar 67. The biasing force applied to the sleeve 65 is transmitted to the intermediate striker 58 via the biasing force transmitting element 61, the bumper 64 and the ring 63. That is, the intermediate striker 58 receives an urging force from the spring 68 in a direction toward the stopper surface 54 in the direction of the center line A1.

A striker 69 is provided in the cylinder 22 so as to be movable in the direction of the center line A1. The striker 69 is disposed between the piston 24 and the middle striker 58 in the direction of the center line A1. A seal member 70 is attached to the outer peripheral surface of the striker 69, and the seal member 70 contacts the inner peripheral surface of the cylinder 22 to form a seal surface. An air chamber 71 is provided in the cylinder 22 between the striker 69 and the piston 24. The air passage 47 and the air passage 48 lead to the air chamber 71. When the piston 24 operates, the pressure in the air chamber 71 fluctuates.

The front cover 23 has an accommodation hole 72, a first holding hole 73, and a second holding hole 74, as shown in FIGS. The first holding hole 73 is disposed between the second holding hole 74 and the housing hole 72 in the direction of the center line A1. The first holding hole 73 and the second holding hole 74 extend in the direction of the center line A1. The accommodation hole 72, the first holding hole 73, and the second holding hole 74 are disposed around the center line A1. The first cylindrical portion 75 is disposed in the housing hole 72.

In the plane perpendicular to the center line A1, the inner peripheral surface shape of the accommodation hole 72 is circular. The inner peripheral surface shape of the first holding hole 73 is a polygon in a plan view perpendicular to the center line A1. The 1st holding hole 73 shown in FIG. 6 shows the example whose inner peripheral surface shape is a hexagon. That is, the six first holding surfaces 77 are formed by the inner peripheral surface of the first holding hole 73. Corners 87 are respectively formed between the adjacent first holding surfaces 77. The diameter L 2 of the circumscribed circle of the first holding hole 73 shown in FIG. 8 is smaller than the inner diameter of the accommodation hole 72 and larger than the diameter of the inscribed circle of the holding hole 53.

As shown in FIGS. 7 and 8, the inner circumferential surface of the second holding hole 74 has a plurality of curved surfaces 78 and a plurality of flat surfaces 79. 7 and 8 show an example in which six curved surfaces 78 are provided and six flat surfaces 79 are provided. The flat surface 79 is formed to overlap the first holding surface 77 of the first holding hole 73 in a plan view perpendicular to the center line A. The plurality of curved surfaces 78 bulge outward in the radial direction of the second holding hole 74. The curved surface 78 and the flat surface 79 are alternately arranged in the circumferential direction of the second holding hole 74. The curved surface 78 and the flat surface 79 are connected to each other. The diameter L1 of the circumscribed circle of the six curved surfaces 78 is larger than the diameter L2. The diameter L3 of the inscribed circle of the flat surface 79 is smaller than the diameter L2. The diameter L3 of the inscribed circle of the first holding hole 73 shown in FIG. 6 is equal to the diameter L3 of the inscribed circle of the flat surface 79 shown in FIG. Further, an end surface 80 connecting the inner surface of the first holding hole 73 and the six curved surfaces 78 is provided. The end surface 80 is a flat surface perpendicular to the center line A1. An edge 91 is formed at the boundary between the end face 80 and the first holding surface 77. The edge 91 is an edge.

A holder 81 is attached to the front cover 23 as shown in FIGS. 4 and 5. The holder 81 has an engaging portion 82. The holder 81 is made of metal. The tip tool 83 can be attached to the front cover 23, and the tip tool 83 can be removed from the front cover 23. The tip tool 83 is used when transmitting the striking force of the striking working machine 10 to the object and not transmitting the rotational force to the object.

The tip tool 83 has a first shaft 84, a second shaft 85, and a large diameter portion 86. The center line A1 is also the center of the tip tool 83, and the large diameter portion 86 is disposed between the first shaft portion 84 and the second shaft portion 85 in the direction of the center line A1. The length in the center line A1 direction of the first shaft portion 84 is larger than the sum of the length of the first holding hole 73 and the length of the second holding hole 74. The cross-sectional shape of the first shaft portion 84 is circular as shown in FIG. 9, and the cross-sectional shape of the large diameter portion 86 is hexagonal as shown in FIG. As shown in FIG. 9, the diameter of the first shaft portion 84 is smaller than the diameter of the inscribed circle of the holding hole 53 of the driver 51. As shown in FIG. 8, the diameter L4 of the circumscribed circle of the large diameter portion 86 is larger than the diameter L3 and smaller than the diameter L2. As shown in FIG. 7, the large diameter portion 86 has six surfaces 88, and corner portions 89 are formed at the connection points between the adjacent surfaces 88, respectively.

As shown in FIGS. 4 and 5, an edge 90 is formed at the boundary between each surface 88 and the surface of the first shaft 84. Each edge 90 is annularly formed around the entire circumference of the tip tool 83. Each edge 90 is curved in a plane cross section including the center line A1. In the tip end tool 83, an engagement portion 92 is provided between the second shaft portion 85 and the large diameter portion 86. The engaging portion 92 is provided on the entire circumference of the tip tool 83, and the diameter of the engaging portion 92 is larger than the diameter L4 of the large diameter portion 86 shown in FIG.

Next, a usage example of the striking work machine 10 will be described. The biasing force of the spring 68 is transmitted to the intermediate striker 58 through the collar 67, the sleeve 65, the biasing transmission element 61, the bumper 64 and the ring 63, and the first shaft 93 is pressed against the stopper surface 54 to perform an intermediate strike. Child 58 stops.

The operator positions the tip tool 83 and the front cover 23 concentrically with respect to the center line A1, and brings the first shaft portion 84 close to the front cover 23. Then, the first shaft portion 84 enters the holding hole 53 through the second holding hole 74 and the first holding hole 73, and the large diameter portion 86 enters the second holding hole 74. Then, as shown in FIG. 8, when the edge 90 contacts the edge 91, the movement of the tip tool 83 is restricted, and the tip tool 83 stops.

When the tip tool 83 held by the front cover 23 is pressed against the object to increase the moving force in the center line A1 direction applied to the tip tool 83, a part of the moving force in the center line A1 direction is the edge 90 At the point of contact between the edge portion 91 and the edge portion 91, the force component is converted into a component force in the direction along the edge portion 91, and the force component rotates the tip tool 83 about the center line A1. In the example shown in FIG. 8, the tip tool 83 rotates clockwise. Then, when the difference between the position of the corner 89 and the position of the corner 87 becomes smaller than a predetermined angle in the circumferential direction around the center line A1, the large diameter portion 86 is held in the first holding state as shown in FIG. The hole 73 is entered. The predetermined angle at which the large diameter portion 86 can enter the first holding hole 73 is represented by a predetermined angle θ1 in FIG.

Furthermore, when the end of the first shaft 84 comes in contact with the end of the first shaft 93 of the intermediate striker 58, the intermediate striker 58 is separated from the stopper surface 54 against the biasing force of the spring 68. Then, when the first shaft 93 comes in contact with the spacer 56 as shown in FIG. 2 and the intermediate striker 58 is stopped, the tip tool 83 is also stopped.

Next, when the operator applies an operating force to the trigger 20, power is supplied to the electric motor 13 and the output shaft 28 rotates. The rotational force of the output shaft 28 is converted into the reciprocating power of the piston 24 by the crank mechanism 12. When the piston 24 moves away from the center line A3 in the cylinder 22, the pressure in the air chamber 71 rises to generate a striking force, and the striker 69 strikes the intermediate striker 58. The striking force is transmitted to the object via the tip tool 83. Thus, when the first holding hole 73 holds the large diameter portion 86, the intermediate striker 58 can hit the tip tool 83.

Further, the rotational force of the output shaft 28 is transmitted to the bevel gear 39 via the driven gear 44, the rotational force transmission shaft 40 and the pinion gear 43. The cylinder 22 rotates with the bevel gear 39, and the driver 51 rotates. The cross-sectional shape of the first shaft portion 84 of the tip tool 83 is circular, and as shown in FIG. 9, the diameter of the first shaft portion 84 is smaller than the diameter of the inscribed circle of the hexagonal holding hole 53. Further, as shown in FIG. 6, the corner 89 of the large diameter portion 86 contacts the first holding surface 77. Therefore, the tip tool 83 is not rotated by the rotational force of the cylinder 22, and only the striking force in the direction of the center line A1 is applied to the tip tool 83.

Thereafter, when the piston 24 reciprocates in the cylinder 22, the striking force of the striker 69 is continuously applied to the tip tool 83. While the distal end tool 83 is pressed against the object and a striking force is applied to the distal end tool 83, the large diameter portion 86 is in both the first holding hole 73 and the second holding hole 74 as shown in FIG. To position.

When the operator releases the operation force on the trigger 20, the electric motor 13 is stopped. In addition, when the worker separates the end tool 83 from the object and inclines the center line A1 with respect to the vertical line, the end tool 83 is positioned below the front case 19. Then, the tip end tool 83 descends along its center line A1 by its own weight, and the large diameter portion 86 retreats from the first holding hole 73 as shown in FIG. Then, the engagement portion 92 comes into contact with the engagement portion 82, and the tip tool 83 stops with respect to the front cover 23. Thus, the holder 81 prevents the tip tool 83 from inadvertently coming out of the front cover 23.

On the other hand, when the end tool 83 separates from the object while the electric motor 13 is rotating, and the striking force is applied to the end tool 83, the end tool 83 moves away from the front case 19 along the center line A1. Moving. Then, as shown in FIG. 5, the large diameter portion 86 retreats from the first holding hole 73, and the engaging portion 92 collides with the engaging portion 82, and the tip tool 83 approaches the front case 19 by reaction. To move.

Then, the edge 90 collides with the edge 91 as in the case where the operator presses the tip tool 83 against the object. Then, a part of the moving force in the direction of the center line A1 of the tip tool 83 is converted into a component force in the direction along the edge 91 at the contact point between the edge 90 and the edge 91, and the tip force Is rotated about the center line A1, the moving force in the direction of the center line A of the tip tool 83 is reduced. For this reason, from the time the edge 90 contacts the edge 91, movement of the tip tool 83 in the direction approaching the intermediate striker 58 is suppressed or moves away from the intermediate striker 58.

As described above, the edge portion 91 allows the tip tool 83 to move in the direction of the center line A1 to enter the first holding hole 73, but reduces the amount of movement. Therefore, it is possible to prevent the idle operation of the striking work machine 10. The blanking means that the striking force of the striker 69 is transmitted to the tip tool 83 in a state where the tip tool 83 is not pressed against the object. When the end tool 83 separates from the object while the electric motor 13 is rotating and an impact force is applied to the end tool 83, the end tool 83 moves away from the front case 19 in the direction of the center line A1. Then, the engaging portion 92 collides with the engaging portion 82 to repel, and the tip tool 83 moves in a direction approaching the front case 19 in the direction of the center line A1. Then, the end of the first shaft 84 collides with and repels the end of the first shaft 93 of the intermediate striker 58, and the tip tool 83 moves away from the front case 19 in the direction of the center line A1. . As described above, the tip tool 83 repeatedly moves back and forth in the direction of the center line A1, and the tip tool 83 is repeatedly hit by the middle striker 58, and a blank run occurs continuously. .

However, the striking work machine 10 according to the present disclosure reduces the moving force of the tip tool 83 moving in the direction of the center line A1 and entering the first holding hole 73. For this reason, the increase in the range in which the tip tool 83 reciprocates in the direction of the center line A1 is suppressed. Therefore, the tip end tool 83 finally stops in a state where the large diameter portion 86 is not held by the first holding hole 73. When the second holding hole 74 holds the large diameter portion 86 and the first holding hole 73 does not hold the large diameter portion 86, the intermediate striker 58 can not hit the tip tool 83, so the empty state is empty. Repeated hitting is suppressed.

The striking work machine 10 of the present disclosure converts a part of the moving force of the tip tool 83 in the direction of the center line A1 into the rotational force of the tip tool 83, thereby suppressing the tip tool 83 from approaching the intermediate striker 58. Do. Therefore, the diameter L3 of the inscribed circle of the first holding hole 73 and the diameter L3 of the inscribed circle of the flat surface 79 of the second holding hole 74 can be equalized. That is, the amount of gap in the radial direction formed between the outer periphery of the large diameter portion 86 of the tip tool 83 and the inner periphery of the second holding hole 74 can be made as small as possible. Therefore, it is possible to suppress the central axis of the tip tool 83 from being inclined so as to intersect the center line A1 of the front case 19, and the workability is improved.

Further, in the striking work machine 10, the collar 67 opens the air passage 48 in a state where the tip tool 83 is separated from the object and the middle striker 58 is pressed against the stopper surface 54 by the biasing force of the spring 68. There is. That is, the air chamber 71 is connected to the outside of the cylinder 22 via the air passage 48. Therefore, even if the piston 24 reciprocates in the cylinder 22, the air in the air chamber 71 is discharged from the air passage 48, and the increase in the air pressure of the air chamber 71 is suppressed. Therefore, blanking can be further reduced while the tip tool 83 is separated from the object.

Furthermore, when the tip tool 83 is pressed against the object and the intermediate striker 58 is released from the stopper surface 54 as shown in FIG. 2, the collar 67 blocks the air passage 48. Therefore, when the piston 24 moves in the cylinder 22 in a direction away from the center line A3, the pressure of the air chamber 71 rises and a sufficient striking force can be obtained.

An example of another tip tool that can be held by the front cover 23 will be described with reference to FIG. The tip tool 94 shown in FIG. 9 has a first shaft 84, a second shaft 85, a large diameter portion 86, and an engagement portion 92. The cross-sectional shape of the large diameter portion 86 is circular as shown in FIG. 11, and the diameter of the large diameter portion 86 is smaller than the diameter of the inscribed circle of the first holding hole 73. The cross-sectional shape of the first shaft portion 84 is hexagonal as shown in FIG. 12, and the diameter of the circumscribed circle of the first shaft portion 84 is smaller than the maximum inner diameter of the holding hole 53 and the minimum inner diameter of the holding hole 53. Greater than.

Next, an operation of attaching the tip tool 94 of FIG. 10 to the front cover 23 shown in FIG. 2 will be described. The operator causes the first shaft portion 84 to enter the first holding hole 73 via the second holding hole 74, and then causes the first shaft portion 84 to enter the holding hole 53 as shown in FIG. When the first shaft portion 84 is positioned in the holding hole 53, the front cover 23 and the tip tool 94 become concentric. When the first shaft portion 84 contacts the intermediate striker 58, the tip tool 94 is stopped.

Then, when the operator presses the end tool 94, the reaction force causes the intermediate striker 58 to move away from the stopper surface 54 against the biasing force of the spring 68. Further, since the front cover 23 and the tip tool 94 are concentric, and the diameter of the large diameter portion 86 is smaller than the diameter of the inscribed circle of the first holding hole 73, the large diameter portion 86 is The large diameter portion 86 moves from the second holding hole 74 to the first holding hole 73 without contact. When the first shaft 93 comes in contact with the spacer 56 and the intermediate striker 58 stops, the tip tool 94 also stops.

Next, when the operator applies operating force to the trigger 20 and the output shaft 28 of the electric motor 13 rotates, the striker 69 reciprocates within the cylinder 22 in the same manner as described above, and the striker 69 The tip tool 94 is indirectly hit through.

Further, as shown in FIG. 12, the cross-sectional shape of the holding hole 53 is hexagonal, and the cross-sectional shape of the first shaft portion 84 is hexagonal, and the diameter of the circumscribed circle of the first shaft portion 84 is the holding hole. It is smaller than the maximum inner diameter 53 and larger than the minimum inner diameter of the holding hole 53. Therefore, when the rotational force of the output shaft 28 is transmitted to the driver 51, the rotational force of the driver 51 is transmitted to the tip tool 94. In this manner, both the striking force and the rotational force are transmitted to the tip tool 94.

Further, when the tip tool 94 is released from the object, the biasing force of the spring 68 presses the intermediate striker 58 against the stopper surface 54, and the collar 67 opens the air passage 48. Therefore, even if the piston 24 reciprocates in the cylinder 22, it is possible to suppress the impact force being applied to the tip tool 94.

Another example of the striking work machine will be described with reference to FIGS. 13 and 14. The striking work machine 10 shown in FIGS. 13 and 14 has a retainer sleeve 95 made of metal. The retainer sleeve 95 has a tubular shape and is disposed in the front case 19. The retainer sleeve 95 has a first cylindrical portion 96, a second cylindrical portion 97, and a third cylindrical portion 98. The second cylindrical portion 97 is provided between the first cylindrical portion 96 and the third cylindrical portion 98 in the direction along the center line A1. The inner diameter of the second cylindrical portion 97 is smaller than the inner diameter of the first cylindrical portion 96 and larger than the inner diameter of the third cylindrical portion 98.

A stepped portion 99 is provided at the connection between the first cylindrical portion 96 and the second cylindrical portion 97. The stepped portion 99 is annularly provided on the inner periphery of the retainer sleeve 95. A portion of the cylinder 22 is disposed in the first cylindrical portion 96. The cylinder 22 is connected to rotate integrally with the retainer sleeve 95. The bumper 55 and the spacers 56 and 57 are disposed between the end of the cylinder 22 and the step 99. A stopper surface 100 is provided at the connection point between the second cylindrical portion 97 and the third cylindrical portion 98. The stopper surface 100 is annularly provided on the inner periphery of the retainer sleeve 95. The middle striker 58 is provided in the second cylindrical portion 97, and is movable in the direction of the center line A1. The middle striker 58 does not include the third shaft 59 shown in FIG.

An annular rib 101 is provided on the inner peripheral surface of the front case 19. The rib 101 supports the slide bearing 102. The slide bearing 102 is mounted against rotation with respect to the rib 101 and the slide bearing 102 has an outwardly facing flange 103. The flange 103 contacts the rib 101, and the movement of the slide bearing 102 in the direction of the center line A1 is restricted. The second cylindrical portion 97 is disposed in the slide bearing 102, and the slide bearing 102 rotatably supports the retainer sleeve 95.

An outwardly facing flange 104 is provided on the outer peripheral surface of the first cylindrical portion 96. An annular spacer 105 and an annular bumper 106 are provided between the flange 103 and the flange 104.

The clutch 107 is attached to the outer peripheral surface of the cylinder 22. The clutch 107 rotates integrally with the cylinder 22 and is movable relative to the cylinder 22 in the direction of the center line A1. The crank case 15 is provided with an operating member, and when the operator operates the operating member, the clutch 107 moves in the direction of the center line A1 with respect to the cylinder 22. When the operation member is operated, the hammer drill mode and the hammer mode can be switched.

An elastic member 108 is provided between the first cylindrical portion 96 and the clutch 107. The elastic member 108 biases the clutch 107 toward the bevel gear 39 in the direction of the center line A1. The elastic member 108 can use, for example, a metal compression coil spring. The bevel gear 39 shown in FIGS. 13 and 14 is rotatable relative to the cylinder 22.

A lock 109 is provided on the inner peripheral surface of the crankcase 15. The detent 109 is annular and attached so as not to rotate relative to the crankcase 15. When the clutch 107 moves in the direction of the center line A 1 and stops, the clutch 107 engages with either the bevel gear 39 or the detent 109. An air passage 48 is provided in the cylinder 22. The air passage 48 is disposed between the first cylindrical portion 96 and the clutch 107 in the direction of the center line A1.

A cap 110 is attached to an end of the third cylindrical portion 98. The cap 110 has an axial hole 111. A front cover 112 is attached to the cap 110. The front cover 112 is annular. An annular plate 113 is attached to the outer peripheral surface of the retainer sleeve 95. An annular holder 114 is attached to the third cylindrical portion 98. The holder 114 is movable relative to the third cylindrical portion 98 in the direction of the center line A1. An elastic member 115 is provided between the plate 113 and the holder 114, and the elastic member 115 biases the holder 114 in the direction of the center line A1 and presses the holder 114 against the front cover 112. The elastic member 115 is, for example, a compression coil spring made of metal.

The third cylindrical portion 98 has a holding hole 116 as shown in FIGS. 15 and 19. The holding hole 116 penetrates the third cylindrical portion 98 in the radial direction. A plurality of holding holes 116 are arranged at different positions in the circumferential direction of the third cylindrical portion 98. A bit lock 117 is disposed in the holding hole 116. The bit lock 117 is made of metal, and the bit lock 117 is movable in the radial direction of the third cylindrical portion 98 in the holding hole 116. The holder 114 is located outside the bit lock 117 in the radial direction of the third cylindrical portion 98, and the holder 114 prevents the bit lock 117 from coming out of the holding hole 116.

As shown in FIG. 19, a rail 118 is provided on the inner surface of the axial hole 126 of the third cylindrical portion 98. The rails 118 are linearly arranged along the center line A1. A plurality of rails 118 are provided in the circumferential direction of the third cylindrical portion 98 as shown in FIG. The rail 118 has a first guide portion 119 and a second guide portion 120 as shown in FIG. The second guide portion 120 is disposed between the first guide portion 119 and the stopper surface 100 in the direction of the center line A1. In the circumferential direction of the third cylindrical portion 98, the width L5 of the first guide portion 119 is smaller than the width L6 of the second guide portion 120.

Further, a connection portion 121 for connecting the first guide portion 119 and the second guide portion 120 is provided. The connection portion 121 is disposed between the first guide portion 119 and the second guide portion 120 in the direction of the center line A1. In the shaft hole 126 of the third cylindrical portion 98, the region where the second guide portion 120 is disposed in the direction of the center line A1 is the first holding hole 127. In the axial hole 126, the area where the first guide portion 119 is disposed in the direction of the center line A1 is the second holding hole 128.

As shown in FIG. 13, FIG. 14 and FIG. 19, a tip tool 122 which can be attached to and detached from the retainer sleeve 95 is provided. The tip tool 122 is different in shape from the tip tool 83. The end tool 122 has an axial shape, and the end tool 122 has a guide groove 123 and a holding groove 124 as shown in FIG. 16, FIG. 17 and FIG. The guide groove 123 and the holding groove 124 are linearly arranged along the longitudinal direction of the tip tool 122. A plurality of guide grooves 123 are arranged at intervals in the circumferential direction of the end tool 122. A plurality of holding grooves 124 are arranged at intervals in the circumferential direction of the end tool 122. When the end tool 122 is held by the retainer sleeve 95, the rail 118 is disposed in the guide groove 123, and a part of the bit lock 117 is disposed in the holding groove 124.

A usage example of the striking work machine 10 shown in FIGS. 13 and 14 will be described. When the impact working tool 10 is held so that the end tool 122 is lower than the intermediate striker 58 and the center line A1 is inclined relative to the horizontal, the bit lock 117 is attached to the retainer sleeve 95 by its own weight. The bit lock 117 is at a position closest to the rear end 125 of the end tool 122 in the holding groove 124 as shown in FIG. Then, the bit lock 117 engages with the end tool 122 to prevent the end tool 122 from coming out of the retainer sleeve 95. Here, the first guide portion 119 is located in the guide groove 123, and the second guide portion 120 is located outside the guide groove 123.

In addition, when the piston 24 is stopped, the striker 69 is also stopped. The middle striker 58 is pushed by the striker 69 and comes into contact with the stopper surface 100 to stop. When the middle striker 58 contacts the stopper surface 100 and the second guide portion 120 is located outside the guide groove 123, the middle striker 58 and the tip tool 122 are separated. For this reason, even if the piston 24 reciprocates and the striker 69 strikes the intermediate striker 58, the striking force is not transmitted to the tip tool 122, and it is possible to prevent the idle strike.

When the tip tool 122 is pressed against the object and moved in the direction of the center line A1, the end of the tip tool 122 contacts the connecting portion 121 as shown in FIG. A component force is generated at the contact point between the tip tool 122 and the connection portion 121, and a part of the moving force in the direction of the center line A1 is converted into a force in the direction of rotating the tip tool 122. The tip tool 122 rotates, for example, in the range of the predetermined angle θ1 clockwise in FIG. 15, and when the center of the guide groove 123 and the center of the second guide portion 120 coincide in the rotation direction of the tip tool 122, the tip tool 122 moves in the direction of center line A1. That is, both the first guide portion 119 and the second guide portion 120 are accommodated in the guide groove 123. Then, the tip tool 122 contacts the intermediate striker 58, and the intermediate striker 58 moves in the direction of the center line A1. Then, as shown in FIG. 14, when the first shaft 93 comes in contact with the spacer 56, the intermediate striker 58 and the tip tool 122 stop.

When the piston 24 moves away from the air passage 48 in the cylinder 22 and moves in the direction of the center line A1, the striker 69 moves away from the intermediate striker 58, and the seal member 70 moves to the air passage 48 and the air chamber 71. And shut off. When the piston 24 moves toward the center line A1 in the cylinder 22 so as to approach the air passage 48, the striker 69 strikes the intermediate striker 58 as shown in FIG. The striking force applied to the middle striker 58 is transmitted to the tip tool 122. Thus, when the first holding hole 127 holds the tip tool 122, the middle striker 58 can strike the tip tool 122.

When the operation member is operated to select the hammer drill mode, the clutch 107 is engaged with the bevel gear 39 and released from the detent 109 as shown in FIG. The rotational force of the bevel gear 39 is transmitted to the retainer sleeve 95 via the clutch 107 and the cylinder 22. The rotational force of the retainer sleeve 95 is transmitted to the distal end tool 122 by the engagement force between the bit lock 117 and the distal end tool 122 and the engagement force between the rail 118 and the distal end tool 122. For this reason, the tip tool 122 receives an impact force from the middle striker 58, and rotates about the center line A1.

On the other hand, when the operation member is operated and the hammer mode is selected, the clutch 107 engages with the detent 109 and is released from the bevel gear 39. For this reason, the rotational force of the bevel gear 39 is not transmitted to the cylinder 22, and the detent 109 prevents the cylinder 22 from rotating. Therefore, the rotational force is not transmitted to the tip tool 122, and the striking force is transmitted to the tip tool 122.

Next, an operation when the tip tool 122 is separated from the object while the tip tool 122 is pressed against the object and the piston 24 is reciprocated in the cylinder 22 will be described. The tip tool 122 is hit by the intermediate striker 58, moves in the direction of the center line A1 in a direction away from the first cylindrical portion 96, and the point closest to the rear end 125 of the tip tool 122 as shown in FIG. It collides with the lock 117. At this time, the first guide portion 119 is positioned in the guide groove 123, and the second guide portion 120 is positioned outside the guide groove 123.

Then, the tip tool 122 tries to move in the direction of the center line A1 in the direction approaching the first cylindrical portion 96 by the reaction force that has collided with the bit lock 117. Then, as shown in FIG. 15, the end of the tip tool 122 contacts the connecting portion 121, and a part of the movement force of the tip tool 122 in the direction of the center line A1 is converted to a force in the direction to rotate the tip tool 122. . For this reason, from the time when the tip tool 122 contacts the connection portion 121, the movement in the direction in which the tip tool 122 approaches the intermediate striker 58 is suppressed or moves away from the intermediate striker 58.

As described above, the connection portion 121 allows the tip tool 122 to move in the direction of the center line A1 and enter the first holding hole 127, but reduces the amount of movement. Accordingly, it is possible to prevent the blanking of the tip tool 122 while the tip tool 122 is separated from the object. When the second holding hole 128 holds the tip tool 122 and the first holding hole 127 does not hold the tip tool 122, the intermediate striker 58 can not strike the tip tool 122.

To explain the technical meaning of the elements of the present disclosure, the tip tools 83 and 122, the front cover 23, and the retainer sleeve 95 are an example of a holder, and the center line A1 is an example of a center line. The first holding holes 73 and 127 are an example of a first holding portion, and the second holding holes 74 and 128 are an example of a second holding portion. The large diameter portion 86 is an example of the held portion. The edge part 91 and the connection part 121 are an example of a control part. The plurality of first holding surfaces 77 is an example of the plurality of first holding surfaces. The diameter L1 is an example of the largest inner diameter, and the diameter L2 is an example of the largest inner diameter. The plurality of flat surfaces 79 is an example of the plurality of second holding surfaces. The air passage 48 is an example of an exhaust passage.

The striking work machine is not limited to the embodiment, and various changes can be made without departing from the scope of the invention. For example, the striking work machine includes a hammer driver as well as a hammer drill which performs a drilling operation, a drilling operation, and a crushing operation with concrete or stone as an object. The hammer driver rotates while the tip tool strikes a screw member as an object. The motor includes an electric motor, an internal combustion engine, a hydraulic motor, and a pneumatic motor. Power supplies for supplying power to the electric motor include AC power supplies and DC power supplies. The direct current power supply includes a battery that is removable from the casing.

The motion conversion mechanism for converting the rotational force of the motor into the reciprocating operation force of the piston includes a cam mechanism in addition to the crank mechanism. The striking work machine has a structure in which the center line A1 and the center line A2 are parallel to each other, in addition to a structure in which the center line A2 of the output shaft of the motor and the center line A1 in the direction of movement of the piston are disposed at right angles. including.

In the present disclosure, the end face 80 can also be grasped as a step. Further, although an example in which the tip tool 83 is rotated clockwise in FIG. 8 is described, the tip tool 83 is counterclockwise in FIG. 8 due to the positional relationship between the tip tool 83 and the front cover 23 in the circumferential direction. Sometimes it rotates. Although an example in which the tip tool 122 rotates clockwise in FIG. 15 has been described, the tip tool 122 may also rotate counterclockwise in FIG. 15 due to the positional relationship between the tip tool 122 and the retainer sleeve 95 in the circumferential direction. is there. The cross-sectional shape of the first holding hole and the large diameter portion may be a polygon, and may be a triangle, a pentagon, or an octagon, in addition to a hexagon.

DESCRIPTION OF SYMBOLS 10 ... Impact working machine, 22 ... Cylinder, 23 ... Front cover, 24 ... Piston, 48 ... Air passage, 69 ... Striker, 71 ... Air chamber, 73, 127 ... 1st holding hole (1st holding part), 74 , 128: second holding hole (second holding portion) 77: first holding surface 78: curved surface 79: flat surface 83, 122 tip tool 86: large diameter portion (held portion) 91 ... Edge, 95 ... Retainer sleeve, 121 ... Connection, A1 ... Centerline, L1, L2 ... Diameter.

Claims (7)

  1. It has a cylindrical holder for holding the held portion of the tip tool, and a striker capable of moving in the direction of the center line of the holder and striking the tip tool held by the holder. It is a striking work machine,
    The holder is
    A first holding portion for holding the held portion so that the tip tool can be hit by the striker;
    A second holding unit disposed at a position different from the first holding unit in the center line direction, and holding the held unit so that the tip tool can not be hit by the striker;
    A restricting portion that restricts the movement of the held portion from the second holding portion to the first holding portion by contacting the held portion held by the second holding portion;
    Have
    The impact working machine, wherein the restricting portion allows the held portion to move from the second holding portion to the first holding portion by rotating the held portion around the center line.
  2. The first holding portion includes a first holding hole extending in the centerline direction,
    The second holding portion includes a second holding hole that is disposed continuously with the first holding hole and in the central line direction, and extends in the central line direction.
    The impact working machine according to claim 1, wherein the restricting portion is disposed between the first holding hole and the second holding hole in the center line direction.
  3. The impact working machine according to claim 2, wherein the first holding hole has a plurality of first holding surfaces that prevent the held portion from rotating about the center line.
  4. The first holding hole is hexagonal in plan view perpendicular to the center line,
    The striking work machine according to claim 2 or 3, wherein the maximum inner diameter of the second holding hole is larger than the maximum inner diameter of the first holding hole.
  5. The second holding hole according to any one of claims 2 to 4, wherein the second holding hole has a plurality of second holding surfaces rotatably supporting the held portion within a range of a predetermined angle around the center line. Impact working machine.
  6. The second holding hole is disposed between a plurality of second holding surfaces in a circumferential direction around the center line, and curved outward in a radial direction around the center line. The impact working machine according to claim 5, which has a surface.
  7. A cylinder movably supporting the striker in the direction of the center line;
    A piston movable in the direction of the center line in the cylinder;
    An air chamber disposed in the cylinder between the piston and the striker, the pressure of which is varied by the operation of the piston;
    The pressure of the air chamber is increased when the piston is disposed between the striker and the piston and connected to the air chamber in the direction of the center line, and the piston operates toward the striker. An exhaust passage, which suppresses
    The impact working machine according to any one of claims 1 to 6, comprising:
JP2018002444A 2017-02-28 2018-01-26 Impact working machine Granted JPWO2018159171A1 (en)

Priority Applications (3)

Application Number Priority Date Filing Date Title
JP2017037163 2017-02-28
JP2017037163 2017-02-28
PCT/JP2018/002444 WO2018159171A1 (en) 2017-02-28 2018-01-26 Impact work machine

Publications (1)

Publication Number Publication Date
JPWO2018159171A1 true JPWO2018159171A1 (en) 2019-07-04

Family

ID=63370335

Family Applications (1)

Application Number Title Priority Date Filing Date
JP2018002444A Granted JPWO2018159171A1 (en) 2017-02-28 2018-01-26 Impact working machine

Country Status (2)

Country Link
JP (1) JPWO2018159171A1 (en)
WO (1) WO2018159171A1 (en)

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4340728C1 (en) * 1993-11-30 1995-01-26 Bosch Gmbh Robert Device on powered hand tools for the rotary driving of tools
JP3794419B2 (en) * 1996-12-13 2006-07-05 日立工機株式会社 Impact tool
DE102007000453A1 (en) * 2007-08-20 2009-02-26 Hilti Aktiengesellschaft Changeable tool holder
JP2009142931A (en) * 2007-12-13 2009-07-02 Makita Corp Hammering tool

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