Angle impact tool

Abstract

To improve the operability of angle impact tools. [Solution] The angle impact tool comprises a housing including a grip section, a motor housing section, and a battery holder section; a motor disposed inside the motor housing section and having a rotor that rotates around a first rotation axis in the front-rear direction by power supplied from a battery pack; and an impact mechanism that converts a continuous torque input from the motor into intermittent rotational impacts capable of generating a tightening torque of 275 Nm or more to the fastening member. The impact mechanism includes a spindle extending along a second rotation axis in the vertical direction; an anvil disposed below the spindle and having a tip tool holder section at its lower end having a two-sided width of 3 / 8 inch or more and 7 / 8 inch or less in a cross-section perpendicular to the second rotation axis; a hammer that moves up and down relative to the spindle and rotates around the second rotation axis to strike the anvil in the rotational direction; and a spring that biases the hammer toward the anvil.

Description

Technical Field

[0001] The technology disclosed in this specification relates to an angle impact tool.

Background Art

[0002] Pistol-type electric impact tools are known. There is also an angle impact tool that enables fastening work in a narrow place where the tip of a pistol-type electric impact tool cannot enter. The angle impact tool has a rod-like shape with a bent tip, and the tip can be inserted into a narrow working area to perform fastening work.

Prior Art Documents

Patent Documents

[0003]

Patent Document 1

Summary of the Invention

Problems to be Solved by the Invention

[0004] Angle impact tools used for work in narrow places tend to have a lower fastening torque compared to other types of impact tools due to size constraints and the like. There is also a need for a high fastening torque in angle impact tools.

[0005] The technology disclosed in this specification aims to improve the fastening torque of an angle impact tool. [[ID= 41]]

Means for Solving the Problems

[0006] This specification discloses an angle impact tool. The angle impact tool may include a housing that includes a grip portion extending in the front-rear direction, a motor housing portion positioned in front of the grip portion, and a battery holder portion positioned behind the grip portion for detachably holding a battery pack; a motor positioned inside the motor housing portion and having a rotor that rotates around a first rotation axis in the front-rear direction by power supplied from the battery pack; and an impact mechanism that converts a continuous torque input from the motor into intermittent rotational impacts capable of generating a tightening torque of 275 Nm or more to a fastening member. The impact mechanism may include a spindle extending along a second rotation axis in the vertical direction, an anvil positioned below the spindle and having a tip tool holder portion at its lower end having a two-sided width of 3 / 8 inch or more and 7 / 8 inch or less in a cross-section perpendicular to the second rotation axis, a hammer that moves up and down relative to the spindle and rotates around the second rotation axis to strike the anvil in the rotational direction, and a spring that biases the hammer toward the anvil. [Effects of the Invention]

[0007] The above configuration makes it possible to improve the tightening torque of the angle impact tool. [Brief explanation of the drawing]

[0008] [Figure 1] Figure 1 is a perspective view showing an angle impact tool according to an embodiment. [Figure 2] Figure 2 is a side view showing an angle impact tool according to an embodiment. [Figure 3] Figure 3 is a longitudinal cross-sectional view showing an angle impact tool according to an embodiment. [Figure 4] Figure 4 is a longitudinal cross-sectional view showing the middle section of the angle impact tool according to the embodiment. [Figure 5] Figure 5 is a longitudinal cross-sectional view showing the front part of an angle impact tool according to an embodiment. [Figure 6] Figure 6 is a longitudinal cross-sectional view showing a motor according to the embodiment. [Figure 7]Figure 7 is a longitudinal cross-sectional view showing the striking mechanism according to the embodiment. [Figure 8] Figure 8 is a side view showing a spindle according to an embodiment. [Figure 9] Figure 9 is a perspective view showing a hammer according to an embodiment. [Figure 10] Figure 10 is a perspective view showing an anvil according to an embodiment. [Figure 11] Figure 11 is a cross-sectional view showing the tip tool holder according to the embodiment. [Modes for carrying out the invention]

[0009] In one or more embodiments, the angle impact tool may include a housing comprising a grip portion extending in the front-rear direction, a motor housing portion positioned in front of the grip portion, and a battery holder portion positioned behind the grip portion for detachably holding a battery pack; a motor positioned inside the motor housing portion and having a rotor that rotates about a first rotation axis in the front-rear direction by power supplied from the battery pack; and an impact mechanism that converts a continuous torque input from the motor into intermittent rotational impacts capable of generating a tightening torque of 275 Nm or more to a fastening member. The impact mechanism may include a spindle extending along a second rotation axis in the vertical direction, an anvil positioned below the spindle and having a tip tool holder portion at its lower end having a two-sided width of 3 / 8 inch or more and 7 / 8 inch or less in a cross-section perpendicular to the second rotation axis, a hammer that moves up and down relative to the spindle and rotates about the second rotation axis to strike the anvil in the rotational direction, and a spring that biases the hammer toward the anvil.

[0010] The above configuration includes a grip section extending in the front-to-back direction, a motor housing section positioned in front of the grip section, and a battery holding section positioned behind the grip section for detachably holding the battery pack. This structure can generate a tightening torque of 275 Nm or more on fastening members in an angle impact tool equipped with a tip tool of 3 / 8 inch to 7 / 8 inch. This improves the tightening torque of the angle impact tool.

[0011] In one or more embodiments, the weight of the hammer may be between 135g and 600g.

[0012] The above configuration improves the hammer's impact force, enabling high tightening torque even with angle impact tools.

[0013] In one or more embodiments, the number of strikes per revolution of the hammer may be greater than 1.

[0014] With the above configuration, the number of hammer blows is increased, allowing for high tightening torque to be achieved in a short time even with an angle impact tool.

[0015] In one or more embodiments, the moment of inertia of the hammer is 40 kg·mm 2 Above 500kg·mm 2 The following is also acceptable.

[0016] The above configuration improves the hammer's impact force, enabling high tightening torque even with angle impact tools.

[0017] In one or more embodiments, the diameter of the hammer may be 43 mm or more and 80 mm or less. The overall length of the hammer may be 26 mm or more and 45 mm or less.

[0018] With the above configuration, the impact mechanism in angle impact tools can be kept from becoming too large, improving convenience when working in confined spaces.

[0019] In one or more embodiments, the striking mechanism may include a ball that engages with the spindle and the hammer, causing the hammer to move in the rotational and vertical directions as the spindle rotates. The vertical distance of the hammer relative to the spindle may be 8 mm or more and 16 mm or less.

[0020] In the above configuration, even when achieving high tightening torque, the increase in the vertical travel distance of the hammer can be suppressed. As a result, the vertical dimension of the striking mechanism is shortened, improving convenience when working in confined spaces.

[0021] In one or more embodiments, the striking mechanism may be capable of generating a tightening torque of 300 Nm or more.

[0022] With the above configuration, even angle impact tools can achieve higher tightening torque.

[0023] In one or more embodiments, the striking mechanism may be capable of generating a nut busting torque of 450 Nm or more. Nut busting torque is the torque applied to a fastening member when loosening a fastened fastening member.

[0024] The above configuration makes it possible to achieve the high nut busting torque required when loosening fastening members that have become firmly fixed due to rust or other reasons.

[0025] In one or more embodiments, the weight of the anvil may be 55g or more and 250g or less.

[0026] With the above configuration, high tightening torque can be achieved even with angle impact tools.

[0027] In one or more embodiments, the moment of inertia of the anvil is 3.60 kg·mm 2 The above is 30.00 kg·mm 2 The following is also acceptable.

[0028] With the above configuration, high tightening torque can be achieved even with angle impact tools.

[0029] In one or more embodiments, the angle impact tool may include a case positioned in front of the motor housing, with a tip tool holder protruding downward, and a striking mechanism housing for the striking mechanism. The vertical distance between the lower end of the anvil and the upper surface of the striking mechanism housing may be 85 mm or less.

[0030] In the above configuration, the vertical dimension of the part where the tightening work is performed is shortened, improving convenience when working in confined spaces.

[0031] In one or more embodiments, the distance in the front-rear direction between the central axis of the anvil and the front end surface of the striking mechanism housing may be 30 mm or less.

[0032] In the above configuration, the distance in the front-to-back direction from the front end surface of the impact mechanism housing is shortened. This improves the convenience of inserting the angle impact tool into confined spaces for work.

[0033] In one or more embodiments, the rotor may have a rotor shaft portion extending in the front-rear direction. The angle impact tool may further include a bevel gear provided on the rotor shaft portion, and a reduction mechanism connected to the bevel gear that reduces the rotation of the bevel gear and transmits it to the spindle.

[0034] In the above configuration, the reduction mechanism slows down the motor's rotation, allowing the necessary torque to rotate the spindle to be obtained without increasing the size of the motor.

[0035] In one or more embodiments, the reduction mechanism may include a first reduction unit connected to a bevel gear and rotating by reducing the rotation of the bevel gear, and a second reduction unit that reduces the rotation of the first reduction unit and transmits it to the spindle.

[0036] In the above configuration, multiple reduction stages can be performed during the process of transmitting rotation to the spindle. This makes it possible to achieve a high reduction ratio.

[0037] In one or more embodiments, the battery holder may have a battery mounting portion on its lower surface that can accommodate a battery pack.

[0038] In the above configuration, the battery pack is mounted on the underside of the battery holder, allowing even large battery packs to be installed without increasing the size of the housing.

[0039] In one or more embodiments, the angle impact tool may be provided with a trigger lever on the underside of the grip portion, which is operated to start the motor.

[0040] The above configuration improves the operability of angle impact tools.

[0041] In one or more embodiments, the angle impact tool may include a motor having a rotor that rotates about a first rotation axis extending in the front-rear direction and a stator for rotating the rotor; a motor housing portion for housing the motor; a grip portion located behind the motor housing portion; a battery holder portion located behind the grip portion for detachably holding a battery pack that shares power to the motor; a spindle rotated by the rotor and extending along a second rotation axis in the vertical direction; a hammer rotated by the spindle; and an anvil located below the hammer and including a tool tip holder portion at its lower end having a two-sided width of 3 / 8 inch or more and 7 / 8 inch or less in a cross-section perpendicular to the second rotation axis. The maximum tightening torque of the anvil may be 275 Nm or more.

[0042] The above configuration includes a motor housing, a grip located behind the motor housing, and a battery holder located behind the grip that detachably holds the battery pack. This structure can generate a maximum tightening torque of 275 Nm or more in an angle impact tool fitted with a tip tool of 3 / 8 inch to 7 / 8 inch. This improves the tightening torque of the angle impact tool.

[0043] The embodiments will be described below with reference to the drawings. In the embodiments, the positional relationships of each part will be described using the terms left, right, front, rear, top, and bottom. These terms indicate the relative position or direction with respect to the center of the angle impact tool.

[0044] [First Embodiment] Figure 1 is a perspective view showing an angle impact tool 1 according to an embodiment. Figure 2 is a side view showing an angle impact tool 1 according to an embodiment. Figure 3 is a longitudinal cross-sectional view showing an angle impact tool 1 according to an embodiment. Figure 4 is a longitudinal cross-sectional view showing the middle part of the angle impact tool 1 according to an embodiment. Figure 5 is a longitudinal cross-sectional view showing the front part of the angle impact tool 1 according to an embodiment.

[0045] In this embodiment, the angle impact tool 1 is a power tool having an electric motor 6 as a power source. The direction parallel to the first rotation axis AX of the motor 6 is appropriately referred to as the axial direction, the direction that circles around the first rotation axis AX is appropriately referred to as the circumferential direction or rotational direction, and the radial direction of the first rotation axis AX is appropriately referred to as the radial direction. Furthermore, in the radial direction, the position close to or approaching the first rotation axis AX is appropriately referred to as the radially inner or inner circumferential side, and the position far from or moving away from the first rotation axis AX is appropriately referred to as the radially outer or outer circumferential side. In this embodiment, the first rotation axis AX extends in the front-rear direction. One side in the axial direction is the front side, and the other side in the axial direction is the rear side.

[0046] In this embodiment, the angle impact tool 1 is an angle impact wrench. The angle impact tool 1 comprises a housing 2, a case 4, a motor 6, a reduction mechanism 7, an impact mechanism 9 including a spindle 8 and an anvil 10, a fan 12, a trigger lever 14, a forward / reverse switching lever 15, an operation panel 16, a light unit 17, and a controller 18.

[0047] Housing 2 is made of synthetic resin. Housing 2 consists of a pair of split housings, left and right. The pair of split housings are fixed together by multiple screws 2S.

[0048] The housing 2 includes a motor housing section 21, a grip section 22, and a battery holding section 23.

[0049] The motor housing section 21 constitutes the front part of the housing 2. The motor housing section 21 is positioned in front of the grip section 22. The motor housing section 21 is cylindrical. The motor housing section 21 houses the motor 6. The motor housing section 21 houses the motor 6, the fan 12, and the bearing 38R. The operation panel 16 is provided on the upper part of the motor housing section 21.

[0050] The grip portion 22 extends in the front-rear direction. The grip portion 22 extends rearward from the motor housing portion 21. The grip portion 22 is held by the operator. The grip portion 22 is provided with a trigger lever 14 and a grip 22A. The trigger lever 14 is located at the front of the grip portion 22. The trigger lever 14 is located on the underside of the grip portion 22. The grip 22A is located rearward from the trigger lever 14. The grip 22A is columnar. The grip 22A is the portion of the grip portion 22 that is held by the operator.

[0051] The battery holder 23 is located behind the grip portion 22. The battery holder 23 is connected to the rear end of the grip portion 22. The battery holder 23 detachably holds the battery pack 25. The battery holder 23 has a battery mounting portion 13 on its lower surface into which the battery pack 25 can be attached. The battery pack 25 is attached to the battery mounting portion 13 provided on the lower surface of the battery holder 23. The battery holder 23 also houses the controller 18.

[0052] The motor housing section 21 has an air intake port 19 and an exhaust port 20. The air intake port 19 and the exhaust port 20 are provided on the left and right sides of the motor housing section 21. Air from the external space of the housing 2 flows into the internal space of the housing 2 through the air intake port 19. Air from the internal space of the housing 2 flows out into the external space of the housing 2 through the exhaust port 20.

[0053] The housing 2 and case 4 are aligned in the front-to-back direction. Case 4 is positioned in front of the motor housing section 21. The motor housing section 21 and case 4 are connected in the front-to-back direction. The front of housing 2 and the rear of case 4 are connected. Housing 2 and case 4 are fixed together by screws 70. Case 4 is connected to the front of motor housing section 21. Motor housing section 21 is fixed to the rear of case 4.

[0054] Case 4 houses the bevel gear 35, which is a pinion gear. Case 4 houses the reduction mechanism 7. Case 4 houses the striking mechanism 9. The striking mechanism 9 includes a spindle 8, an anvil 10, a hammer 47, and a spring 49. Case 4 houses the spindle 8. Case 4 houses the hammer 47. Case 4 houses a portion of the anvil 10. Case 4 houses the spring 49. Case 4 is made of metal. In this embodiment, case 4 is made of aluminum.

[0055] Case 4 is hollow and box-shaped. Case 4 includes a case body 4A and a lid 4B. Case body 4A is a hollow box shape with openings at the rear and top. The rear of case body 4A is connected to the motor housing portion 21 of housing 2 and is covered by the motor housing portion 21. The top of case body 4A is covered by the lid 4B. The lid 4B is provided on the top surface of case body 4A, extending from the front end to just before the rear end, and is fixed to case body 4A by screws 4S. Case 4 houses the bevel gear 35, reduction mechanism 7, and impact mechanism 9, which are assembled through the top opening of case body 4A, and the lid 4B is attached to case body 4A to accommodate these components.

[0056] Case 4 has a front, left and right sides, and a bottom surface, all of which are formed by the case body 4A. The light unit 17 and the light cover 60 are positioned on the bottom surface of Case 4. An anvil insertion hole 83 is formed near the front end of the bottom surface of Case 4. The anvil insertion hole 83 communicates with the inside of Case 4. The anvil 10 passes through the anvil insertion hole 83. The anvil 10 protrudes downward from the inside of Case 4 to the bottom of Case 4 through the anvil insertion hole 83.

[0057] Case 4 holds a bearing 38F that rotatably supports the rotor 27 of the motor 6. A reduction gear 7 is positioned in front of the bearing 38F. A striking mechanism 9, including a spindle 8, is positioned in front of the reduction gear 7. An anvil 10 is positioned below the spindle 8.

[0058] Motor 6 is the power source for the angle impact tool 1. Motor 6 generates rotational force. Motor 6 is an electric motor. Motor 6 is an inner rotor type brushless motor. Motor 6 is housed in the motor housing section 21 of the housing 2. Motor 6 is positioned inside the motor housing section 21.

[0059] Figure 6 is a longitudinal cross-sectional view showing a motor 6 according to an embodiment. As shown in Figures 4 and 6, the motor 6 has a stator 26 and a rotor 27 that is rotatable relative to the stator 26. The stator 26 is supported by a motor housing 21. At least a portion of the rotor 27 is positioned inside the stator 26. The rotor 27 rotates relative to the stator 26. The rotor 27 rotates about a first rotation axis AX in the front-rear direction by power supplied from a battery pack 25.

[0060] The stator 26 includes a stator core 28, a front insulator 29, a rear insulator 30, and a coil 31.

[0061] The stator core 28 is positioned radially outward from the rotor 27. The stator core 28 includes multiple steel plates stacked in the axial direction. The steel plates are metal plates mainly composed of iron. The stator core 28 is cylindrical. The stator core 28 has multiple teeth that support the coil 31.

[0062] The front insulator 29 is provided at the front of the stator core 28. The rear insulator 30 is provided at the rear of the stator core 28. Both the front insulator 29 and the rear insulator 30 are electrically insulating members made of synthetic resin. The front insulator 29 is positioned to cover a portion of the surface of the teeth. The rear insulator 30 is positioned to cover a portion of the surface of the teeth.

[0063] The coil 31 is mounted on the stator core 28 via a front insulator 29 and a rear insulator 30. Multiple coils 31 are arranged. The coils 31 are arranged around the teeth of the stator core 28 via the front insulator 29 and the rear insulator 30. The coils 31 and the stator core 28 are electrically isolated by the front insulator 29 and the rear insulator 30.

[0064] The rotor 27 rotates around the first rotation axis AX. The rotor 27 has a rotor core portion 32, a rotor shaft portion 33, and a rotor magnet 34.

[0065] The rotor core portion 32 and the rotor shaft portion 33 are each made of steel. In this embodiment, the rotor core portion 32 and the rotor shaft portion 33 are separate components. The rotor core portion 32 and the rotor shaft portion 33 may be integrally formed. The rotor shaft portion 33 extends in the front-rear direction. The central axis of the rotor shaft portion 33 is the first rotation axis AX. The front portion of the rotor shaft portion 33 protrudes forward from the front end surface of the rotor core portion 32. The rear portion of the rotor shaft portion 33 protrudes rearward from the rear end surface of the rotor core portion 32.

[0066] The rotor magnet 34 is fixed to the rotor core 32. The rotor magnet 34 extends forward and backward so as to penetrate the rotor core 32.

[0067] A sensor board 37 is attached to the rear insulator 30. The sensor board 37 has an annular circuit board and a magnetic sensor supported by the circuit board. At least a portion of the sensor board 37 faces the rotor magnet 34. The magnetic sensor detects the rotational position of the rotor 27 by detecting the magnetic force of the rotor magnet 34.

[0068] As shown in Figures 4 and 5, bearings (38F and 38R) are positioned on the front and rear sides of the rotor 27, respectively. The bearings (38F and 38R) rotatably support the rotor 27. The rear part of the rotor shaft 33 is rotatably supported by bearing 38R. The front part of the rotor shaft 33 is rotatably supported by bearing 38F. Bearing 38R is held in the housing 2. As shown in Figure 4, bearing 38R is housed in a concave rear holding portion 21A provided in the motor housing 21. As shown in Figure 5, bearing 38F is housed in a housing recess 84 provided in the rear of the case 4. The housing recess 84 is recessed forward from the rear surface of the case 4. The rear surface of bearing 38F is supported by the front wall portion 92 of the motor housing 21 via an intermediate support member 91. The intermediate support member 91 is a ring-shaped or C-shaped plate member. The bearing 38F is held in the front-rear direction between the rear surface of the case 4 (the inner bottom surface of the housing recess 84) and the front surface of the housing 2 via an intermediate support member 91. The front end of the rotor shaft portion 33 is positioned in the internal space of the case 4 through the opening at the front of the motor housing portion 21 and the opening at the rear of the case 4.

[0069] In one example, bearing 38F has a diameter (outer diameter) of 28.0 mm. In another example, bearing 38F has a length (front-to-back dimension) of 8.0 mm.

[0070] As shown in Figure 5, a bevel gear 35 is provided on the rotor shaft portion 33. The bevel gear 35 is positioned at the front end of the rotor shaft portion 33. The bevel gear 35 is a pinion gear that rotates integrally with the rotor 27. The bevel gear 35 is connected to at least a part of the reduction mechanism 7. The rotor shaft portion 33 is connected to the reduction mechanism 7 via the bevel gear 35.

[0071] In one example, motor 6 has a nominal diameter of 30 mm or more. In another example, motor 6 has a nominal diameter of 43 mm or more. In yet another example, motor 6 has a nominal diameter of 50 mm or more. As shown in Figure 6, the nominal diameter of motor 6 is specifically the outer diameter D11 of the stator core 28. In one example, the stacking thickness of the stator 26 is 10 mm or more. In another example, the stacking thickness of the stator 26 is 15 mm or more. In yet another example, the stacking thickness of the stator 26 is 20 mm or more. The stacking thickness of the stator 26 is specifically the length L11 along the first rotation axis AX of the stator core 28. For example, motor 6 is a BL44-15 motor, i.e., a brushless motor with a nominal diameter of 44 mm and a stator 26 stacking thickness of 15 mm. In addition, motor 6 may be a BL52-15 motor. Motor 6 may be a BL52-24 motor. The combination of the nominal diameter and stacking thickness of motor 6 may differ from the specific example above, and should include configurations within a range of ±2 mm for both the nominal diameter and stacking thickness.

[0072] As shown in Figure 5, the reduction mechanism 7 is connected to the bevel gear 35, which is a pinion gear. The reduction mechanism 7 reduces the rotation of the bevel gear 35 and transmits it to the spindle 8. In this way, the reduction mechanism 7 transmits the rotational force of the motor 6 to the spindle 8 and the anvil 10.

[0073] The reduction gear 7 is housed in the case 4. The case 4 has a reduction gear housing section 81 that houses the reduction gear 7. The reduction gear housing section 81 constitutes the rear of the case 4. The reduction gear housing section 81 houses at least a portion of the bevel gear 35 and the reduction gear 7 inside. The reduction gear housing section 81 connects to the rear surface of the case 4. The reduction gear housing section 81 opens at the rear surface of the case 4. The front end of the rotor shaft section 33, on which the bevel gear 35 is provided, is inserted into the interior of the reduction gear housing section 81 through the opening at the rear surface of the case 4.

[0074] The reduction mechanism 7 has multiple gears. The reduction mechanism 7 is positioned in front of the motor 6. The reduction mechanism 7 is positioned in front of the bearing 38F. The reduction mechanism 7 connects the rotor shaft 33 and the spindle 8. The gears of the reduction mechanism 7 are driven by the rotor 27. The reduction mechanism 7 transmits the rotation of the rotor 27 to the spindle 8. The reduction mechanism 7 rotates the spindle 8 at a rotational speed lower than the rotational speed of the rotor shaft 33 (i.e., the bevel gear 35).

[0075] The reduction mechanism 7 is composed of multiple reduction sections. The reduction mechanism 7 includes a first reduction section 41 and a second reduction section 42. The first reduction section 41 is connected to a bevel gear 35, which is a pinion gear, and rotates by reducing the rotation of the bevel gear 35. The second reduction section 42 reduces the rotation of the first reduction section 41 and transmits it to the spindle 8.

[0076] The first reduction gear 41 includes a driven gear 41A, a first intermediate gear 41B, and a first intermediate shaft 41C. The first intermediate shaft 41C extends in a direction intersecting the first rotation axis AX. The first intermediate shaft 41C extends along a vertical direction perpendicular to the first rotation axis AX and rotates around a central axis in the vertical direction. Both ends of the first intermediate shaft 41C are rotatably supported by intermediate bearings 41D. The intermediate bearings 41D are held in the case 4. The intermediate bearings 41D are ball bearings. The driven gear 41A and the first intermediate gear 41B are fixed to the first intermediate shaft 41C. In this embodiment, the first intermediate gear 41B and the first intermediate shaft 41C are a single unit. The first intermediate gear 41B and the first intermediate shaft 41C may be separate units. The driven gear 41A is mounted on the lower part of the first intermediate shaft 41C, and the first intermediate gear 41B is mounted on the upper part of the first intermediate shaft 41C. The driven gear 41A, the first intermediate gear 41B, and the first intermediate shaft 41C rotate as a single unit. The driven gear 41A is a bevel gear that meshes with the pinion gear, the bevel gear 35. The first intermediate gear 41B is a spur gear. The first intermediate gear 41B meshes with the second intermediate gear 42A of the second reduction unit 42.

[0077] The second reduction gear 42 is positioned in front of the first reduction gear 41. The second reduction gear 42 has a second intermediate gear 42A and a second intermediate shaft 42B. The second intermediate shaft 42B extends in a direction intersecting the first rotation axis AX. The second intermediate shaft 42B extends along the vertical direction perpendicular to the first rotation axis AX and rotates around a central axis in the vertical direction. The first intermediate shaft 41C and the second intermediate shaft 42B are parallel. Both ends of the second intermediate shaft 42B are rotatably supported by intermediate bearings 42C. The intermediate bearings 42C are held in the case 4. The intermediate bearings 42C are sliding bearings. The second intermediate gear 42A is fixed to the second intermediate shaft 42B. The second intermediate gear 42A is mounted on the upper part of the second intermediate shaft 42B. The second intermediate gear 42A and the second intermediate shaft 42B rotate together. The second intermediate gear 42A is a spur gear. The second intermediate gear 42A meshes with the first intermediate gear 41B. The second intermediate gear 42A rotates by reducing the rotation speed of the first intermediate gear 41B. The second intermediate gear 42A meshes with the spindle gear 8C of the spindle 8. The spindle gear 8C rotates together with the spindle 8. The spindle gear 8C is a spur gear.

[0078] When the rotor shaft section 33 rotates due to the drive of the motor 6, the bevel gear 35 rotates, and the bevel gear 35 rotates the driven gear 41A. Due to the rotation of the driven gear 41A, the first intermediate shaft 41C rotates at a rotational speed lower than the rotational speed of the rotor shaft section 33. When the first intermediate shaft 41C rotates, the first intermediate gear 41B rotates, and the first intermediate gear 41B rotates the second intermediate gear 42A. The second intermediate gear 42A rotates at a rotational speed lower than the rotational speed of the first intermediate shaft 41C. The second intermediate gear 42A rotates the spindle gear 8C. The spindle gear 8C rotates at a rotational speed lower than the rotational speed of the second intermediate gear 42A. As the spindle gear 8C rotates, the spindle 8 rotates. The spindle 8 rotates at a rotational speed lower than the rotational speed of the rotor shaft section 33.

[0079] The reduction mechanism 7 has a predetermined reduction ratio between the bevel gear 35 and the spindle 8. The reduction ratio of the reduction mechanism 7 is, for example, 8 or more and 11 or less. In one example, the reduction ratio of the reduction mechanism 7 is 8.10 or more. In another example, the reduction ratio of the reduction mechanism 7 is 8.20 or more. In yet another example, the reduction ratio of the reduction mechanism 7 is 8.30 or more. In yet another example, the reduction ratio of the reduction mechanism 7 is 10.80 or less. In yet another example, the reduction ratio of the reduction mechanism 7 is 10.60 or less. In yet another example, the reduction ratio of the reduction mechanism 7 is 10.40 or less.

[0080] The striking mechanism 9 is driven by the motor 6. The rotational force of the motor 6 is transmitted to the striking mechanism 9 via the reduction mechanism 7. The striking mechanism 9 strikes the anvil 10 in the rotational direction based on the rotational force of the spindle 8, which is rotated by the motor 6.

[0081] As shown in Figure 5, the striking mechanism 9 includes a spindle 8, a hammer 47, a ball 48, and a spring 49.

[0082] The striking mechanism 9 is housed in the case 4. The case 4 has a striking mechanism housing 82 that houses the striking mechanism 9. The striking mechanism housing 82 constitutes the front part of the case 4. The striking mechanism housing 82 houses at least a part of the spindle 8, the hammer 47, the ball 48, the spring 49, and a part of the anvil 10. The striking mechanism housing 82 is positioned in front of the reduction mechanism housing 81. An anvil insertion hole 83 is formed on the lower surface of the striking mechanism housing 82. The lower end of the anvil 10 passes through the anvil insertion hole 83 and protrudes downward from the lower surface of the striking mechanism housing 82. As a result, the tip tool holder 51, which is located at the lower end of the anvil 10, is positioned below the striking mechanism housing 82.

[0083] Details of the striking mechanism 9 will be described later.

[0084] Fan 12 rotates due to the rotational force of motor 6. As shown in Figure 3, fan 12 is positioned in front of the stator 26 of motor 6. Fan 12 generates airflow to cool motor 6. Fan 12 is fixed to at least a portion of rotor 27. Fan 12 is fixed to the front of rotor shaft portion 33. Fan 12 is positioned between bearing 38F and stator 26. Fan 12 rotates with the rotation of rotor 27. As rotor shaft portion 33 rotates, fan 12 rotates together with rotor shaft portion 33. As fan 12 rotates, air from the external space of housing 2 flows into the internal space of housing 2 through intake port 19. The air that flows into the internal space of housing 2 cools motor 6 by circulating through the internal space of housing 2. As fan 12 rotates, the air that has circulated through the internal space of housing 2 flows out into the external space of housing 2 through exhaust port 20.

[0085] As shown in Figure 4, the control panel 16 is provided on the motor housing 21. The control panel 16 is exposed to the outside through a panel opening 21B formed on the upper surface of the motor housing 21. The control panel 16 is positioned near the boundary between the rear of the motor housing 21 and the grip portion 22. The control panel 16 is positioned in front of the trigger lever 14.

[0086] The control panel 16 is plate-shaped. The control panel 16 has an operation button 16A, an indicator display 16B, and a switch board 16C. The operation button 16A and the indicator display 16B are fixed to the switch board 16C via a frame-shaped bracket 16D. The bracket 16D fits into the panel opening 21B. The switch board 16C has a flat plate shape. The switch board 16C is a circuit board on which the operation button 16A and the indicator display 16B are provided. The switch board 16C is connected to the controller 18 by wiring. The motor housing 21 is provided with a retaining groove 21C that supports the outer circumference of the switch board 16C at a position directly below the panel opening 21B. The control panel 16 is positioned in the front-to-back and left-to-right directions by the bracket 16D fitting into the panel opening 21B. The control panel 16 is positioned in the up-to-down direction by the outer circumference of the switch board 16C fitting into the retaining groove 21C. The switch board 16C is positioned on top of the motor housing 21 and runs along the top surface of the motor housing 21. The operation panel 16 outputs a signal to the controller 18 in response to the input of the operation button 16A, and displays information on the indicator display 16B in response to the signal from the controller 18.

[0087] When the operator operates the operation button 16A, the controller 18 switches the operating mode of the motor 6. The indicator display 16B has a light-emitting element. The light-emitting element is, for example, an LED light-emitting element. The indicator display 16B displays the operating mode of the motor 6 by changing the lighting pattern of multiple light-emitting elements. The operating modes include, for example, three different operating modes for high, medium, and low speed settings of the motor 6, a mode in which the motor 6 is stopped based on the detection that striking by the striking mechanism 9 has started, and a mode in which the motor 6 is stopped or switched to low speed rotation based on the detection of the rotation of the nut when loosening the nut.

[0088] As shown in Figure 3, the battery mounting section 13 is located below the battery holding section 23. The battery pack 25 is mounted in the battery mounting section 13. The battery pack 25 is detachable from the battery mounting section 13. The battery mounting section 13 holds the battery pack 25 so that it can slide in the front-rear direction. When the battery pack 25 slides from the rear to the front of the battery mounting section 13 and reaches the engagement position, the battery mounting section 13 engages with the engagement hook of the battery pack 25 to restrict the rearward sliding movement of the battery pack 25. The battery pack 25 is provided with a release button that moves the engagement hook up and down. When the release button is pressed, the engagement hook retracts downward, releasing the engagement with the battery mounting section 13. This makes it possible to attach and detach the battery pack 25. The battery mounting section 13 holds the battery pack 25 downward from the lower surface of the battery holding section 23.

[0089] The battery pack 25 functions as a power source for the angle impact tool 1. The battery pack 25 includes a secondary battery. In an embodiment, the battery pack 25 includes a rechargeable lithium-ion battery. By being mounted in the battery mounting section 13, the battery pack 25 can supply power to the angle impact tool 1. The motor 6 and the light unit 17 are each driven based on the power supplied from the battery pack 25.

[0090] The rated voltage of battery pack 25 is 14.4V or higher. The rated voltage of battery pack 25 may also be 18V, 36V, or 72V.

[0091] The controller 18 operates based on power supplied from the battery pack 25. The controller 18 is connected to the motor 6, switch board 16C, and trigger lever 14 via wiring. The controller 18 is connected to the battery pack 25 via wiring. The wiring passes inside the grip section 22.

[0092] The controller 18 outputs control signals to control the motor 6. The controller 18 includes a circuit board on which multiple electronic components are mounted. Examples of electronic components mounted on the circuit board include a processor such as a CPU (Central Processing Unit), non-volatile memory such as ROM (Read Only Memory) or storage, volatile memory such as RAM (Random Access Memory), a field-effect transistor (FET), and a resistor. The controller 18 sets the operating mode of the angle impact tool 1 based on the operation of the control panel 16. The setting parameters for the operating mode of the angle impact tool 1 include the current threshold and on / off control conditions of the motor 6. The controller 18 outputs a signal to the control panel 16 to display the setting status of the operating mode.

[0093] The controller 18 is positioned behind the control panel 16. The controller 18 is positioned behind the trigger lever 14. The controller 18 is positioned in the battery holder 23. The controller 18 is positioned above the battery mounting section 13. The controller 18 is oriented in the front-to-back and left-to-right directions. The battery holder 23 has a dome-shaped outer form that forms the housing space for the controller 18.

[0094] The trigger lever 14 is located on the underside of the grip portion 22. The trigger lever 14 is located on the front of the grip portion 22. The trigger lever 14 is located so as to protrude downward from the underside of the grip portion 22. The trigger lever 14 is operated to start the motor 6. A switch body 14A is located above the trigger lever 14. The switch body 14A is located inside the grip portion 22. When the trigger lever 14 is operated, the switch body 14A is operated. When the switch body 14A is operated, a trigger signal is generated. The controller 18 switches between driving and stopping the motor 6 based on the trigger signal.

[0095] The forward / reverse rotation switching lever 15 is provided on the grip portion 22. The forward / reverse rotation switching lever 15 is positioned above the trigger lever 14 on the left and right sides of the grip portion 22. The forward / reverse rotation switching lever 15 is operated by the operator. When the forward / reverse rotation switching lever 15 is operated, the rotation direction of the motor 6 is switched from one direction to the other. When the rotation direction of the motor 6 is switched, the rotation direction of the spindle 8 is switched.

[0096] The light unit 17 emits illumination light. The light unit 17 illuminates the anvil 10 and its surroundings with illumination light. The light unit 17 includes one or more light-emitting elements 53. The light unit 17 includes chip-on-board light-emitting diodes (COB LEDs).

[0097] The light unit 17 is positioned on the underside of the case 4. The light unit 17 is positioned around the anvil 10. In the example of Figure 5, the light unit 17 includes two light-emitting elements 53. The light-emitting elements 53 are held in the case 4. The light-emitting elements 53 are held on the underside of the case 4. Multiple light-emitting elements 53 are provided around the anvil 10. Two light-emitting elements 53 are arranged behind the anvil 10.

[0098] The light unit 17 has a substrate 54 on which a plurality of light-emitting elements 53 are provided, and an optical member 57. The light-emitting elements 53 are arranged on the lower surface of the substrate 54, spaced apart in the front-to-back direction. Power supplied to the electrodes is supplied to the light-emitting elements 53 via the substrate 54. The light-emitting elements 53 emit light based on the power supplied from the battery pack 25. The light unit 17 and the controller 18 are connected via lead wires.

[0099] The light unit 17 has an optical member 57 that covers a plurality of light emitters 53. At least a portion of the optical member 57 is positioned in the direction of light emission from the plurality of light emitters 53 (i.e., downward). The optical member 57 faces the plurality of light emitters 53. The optical member 57 transmits at least a portion of the light emitted from the light unit 17. The light transmittance of the optical member 57 is, for example, 40% to 70%. The optical member 57 diffuses the light from the plurality of light emitters 53.

[0100] A portion of the optical element 57 is covered from below by the light cover 60. The light cover 60 has an opening 60A that exposes a portion of the optical element 57 without covering it. The portion of the optical element 57 that covers the multiple light emitters 53 is exposed through the opening 60A. Light from the multiple light emitters 53 passes through the optical element 57 and is emitted downwards from the opening 60A of the light cover 60 towards the bottom of the case 4. The light cover 60 holds the light unit 17 on the bottom surface of the case 4. The light unit 17 is held between the bottom surface of the case 4 and the light cover 60.

[0101] As shown in Figure 2, the light cover 60 is fixed to the lower surface of the case 4 by screws 60S, which tighten the light cover 60 toward the lower surface of the case 4. The light cover 60 extends rearward along the lower surface of the case 4 toward the motor housing 21. The rear end of the light cover 60 engages with the motor housing 21. The light cover 60 covers the lead wires that extend toward the light unit 17 along the lower surface of the case 4.

[0102] (Striking mechanism) Next, the detailed structure of the striking mechanism 9 will be described. Figure 7 is a longitudinal cross-sectional view showing the striking mechanism 9 according to the embodiment. Figure 8 is a side view showing the spindle 8 according to the embodiment. Figure 9 is a perspective view showing the hammer 47 according to the embodiment. Figure 10 is a perspective view showing the anvil 10 according to the embodiment. Figure 11 is a cross-sectional view showing the tip tool holder 51 according to the embodiment.

[0103] As shown in Figure 5, the spindle 8 is connected to the reduction mechanism 7. The spindle 8 is rotated by the motor 6. The spindle 8 is positioned in front of the motor 6. The spindle 8 is positioned in front of the stator 26. The spindle 8 is positioned in front of the rotor 27. The spindle 8 is positioned in front of the reduction mechanism 7. The spindle 8 is rotated by the rotor 27. The spindle 8 rotates due to the rotational force of the rotor 27 transmitted by the reduction mechanism 7.

[0104] The spindle 8 extends in a direction intersecting the front-rear direction. The spindle 8 extends downward along the second rotation axis BX in the vertical direction. The spindle 8 rotates around the second rotation axis BX. The second rotation axis BX of the spindle 8 and the first rotation axis AX of the motor 6 are non-parallel and intersect each other. The direction of the second rotation axis BX of the spindle 8 may intersect the front-rear direction (i.e., the first rotation axis AX) at an angle of 80 degrees or more and 100 degrees or less. In the embodiment, the second rotation axis BX is perpendicular to the front-rear direction and extends in the vertical direction. In the embodiment, the spindle 8, hammer 47 and anvil 10 are arranged along the second rotation axis BX and rotate around the second rotation axis BX.

[0105] As shown in Figures 5 and 7, the spindle 8 has a flange portion 8A and a spindle shaft portion 8B that protrudes downward from the flange portion 8A. The spindle gear 8C is provided on the outer circumference of the flange portion 8A.

[0106] The spindle 8 is rotatably supported by a spindle bearing 44. The spindle bearing 44 is held in the case 4. The spindle 8 has a cylindrical portion 8D that protrudes upward from a flange portion 8A. The spindle bearing 44 is positioned on the outer circumference of the cylindrical portion 8D. The spindle bearing 44 rotatably supports the outer circumference of the cylindrical portion 8D. The spindle bearing 44 is a sliding bearing. The lower end of the spindle shaft portion 8B is cylindrical and protrudes downward. The lower end of the spindle shaft portion 8B is positioned in an anvil recess 10C formed on the upper surface of the anvil 10. The lower part of the spindle 8 is rotatably supported by an anvil bearing 46 via the anvil 10.

[0107] The spindle shaft portion 8B is inserted inside the hammer 47. The spindle shaft portion 8B passes inside the inner cylinder portion 47E of the hammer 47. The outer circumferential surface of the spindle shaft portion 8B is radially opposite to the inner circumferential surface of the inner cylinder portion 47E of the hammer 47. As shown in Figures 7 and 8, the spindle 8 has a spindle groove 8F in which at least a portion of the balls 48 are arranged. The spindle groove 8F is provided on a part of the outer circumferential surface of the spindle shaft portion 8B. The spindle groove 8F is inclined with respect to the second rotation axis BX.

[0108] For example, the spindle shaft portion 8B has a diameter D21 of 10 mm or more and 25 mm or less. In one example, the spindle shaft portion 8B has a diameter D21 of 11 mm or more. In another example, the spindle shaft portion 8B has a diameter D21 of 12 mm or more. In one example, the spindle shaft portion 8B has a diameter D21 of 24 mm or less. In yet another example, the spindle shaft portion 8B has a diameter D21 of 23 mm or less.

[0109] For example, the spindle groove 8F has a lead angle of 25 degrees or more and 40 degrees or less. The lead angle of the spindle groove 8F is the angle formed by the trajectory drawn by the center of the spindle groove 8F when the trajectory is developed on a plane and approximated by a straight line on the plane with respect to the front-rear direction. In one example, the spindle groove 8F has a lead angle of 28 degrees or more. In another example, the spindle groove 8F has a lead angle of 30 degrees or more. In one example, the spindle groove 8F has a lead angle of 37 degrees or less. In another example, the spindle groove 8F has a lead angle of 35 degrees or less.

[0110] For example, the spindle 8 has a weight of 60 g or more and 260 g or less. In one example, the spindle 8 has a weight of 65 g or more. In another example, the spindle 8 has a weight of 70 g or more. In one example, the spindle 8 has a weight of 250 g or less. In another example, the spindle 8 has a weight of 245 g or less.

[0111] For example, the spindle 8 is 2 6.0 kg·mm 2 or more and 45 kg·mm 2 or less in moment of inertia. In one example, the spindle 8 has a moment of inertia of 6.5 kg·mm 2 or more. In another example, the spindle 8 has a moment of inertia of 7.0 kg·mm 2 or more. In one example, the spindle 8 has a moment of inertia of 42.5 kg·mm 2 or less. In another example, the spindle 8 has a moment of inertia of 40.0 kg·mm

[0112] As shown in FIG. 5, the hammer 47 is disposed forward of the speed reducer 7. The hammer 47 is rotated by the spindle 【8】. The hammer 47 is disposed around the spindle shaft portion 8B. The hammer 47 is held by the spindle shaft portion 8B. The ball 48 is disposed between the spindle shaft portion 8B and the hammer 47. The spring 49 is supported by the flange portion 8A and the hammer 47 respectively.

[0113] As shown in Figure 7, the hammer 47 has a body portion 47D, an inner cylinder portion 47E, a hammer groove 47A, and a hammer projection 47B (see Figure 9). The body portion 47D is arranged around the spindle shaft portion 8B. The body portion 47D is annular. The body portion 47D protrudes outward from the lower end of the inner cylinder portion 47E and then extends vertically in a cylindrical shape. The body portion 47D constitutes the outer circumferential surface of the hammer 47. A recess 47C is provided at the upper part of the body portion 47D. The recess 47C is provided so as to be recessed downward from the upper end of the body portion 47D. The recess 47C is ring-shaped. The recess 47C is interposed radially between the body portion 47D and the inner cylinder portion 47E. The inner cylinder portion 47E extends vertically in a cylindrical shape. The spindle shaft portion 8B is inserted inside the inner cylinder portion 47E. The hammer 47 has a hammer groove 47A in which at least a portion of the ball 48 is positioned. The hammer groove 47A is provided on a portion of the inner circumferential surface of the inner cylinder portion 47E. The hammer projection 47B is provided on the lower surface of the body portion 47D. Two hammer projections 47B are provided. The hammer projections 47B are provided in a pair so as to face each other radially via the second rotation axis BX. In other words, the two hammer projections 47B are provided at a distance of 180 degrees in the rotational direction around the second rotation axis BX.

[0114] The hammer 47 is rotated by the motor 6. The rotational force of the motor 6 is transmitted to the hammer 47 via the reduction mechanism 7 and the spindle 8. The hammer 47 is rotatable together with the spindle 8 based on the rotational force of the spindle 8, which is rotated by the motor 6. The axis of rotation of the hammer 47 coincides with the second axis of rotation BX of the spindle 8. The hammer 47 rotates around the second axis of rotation BX. The hammer 47 moves relative to the spindle 8. The hammer 47 reciprocates along the second axis of rotation BX. That is, the hammer 47 moves relative to the spindle 8 in the vertical direction. The hammer 47 rotates around the second axis of rotation BX while moving vertically relative to the spindle 8, striking the anvil 10 in the rotational direction. The hammer projection 47B is the contact point when striking the anvil 10.

[0115] In this embodiment, the weight of the hammer 47 is between 135g and 600g. In one example, the hammer 47 has a weight of 140g or more. In another example, the hammer 47 has a weight of 145g or more. In yet another example, the hammer 47 has a weight of 150g or more. In one example, the hammer 47 has a weight of 590g or less. In another example, the hammer 47 has a weight of 580g or less. In yet another example, the hammer 47 has a weight of 575g or less.

[0116] In this embodiment, the moment of inertia of the hammer 47 is 40 kg·mm 2 Above 500kg·mm 2 The following is an example: Hammer 47 has a capacity of 42 kg·mm. 2 It has the above moment of inertia. In another example, Hammer 47 has a moment of inertia of 44 kg·mm 2 It has the above moment of inertia. In yet another example, Hammer 47 has a moment of inertia of 45 kg·mm 2 It has the above moment of inertia. For example, Hammer 47 has a moment of inertia of 480 kg·mm 2 It has the following moment of inertia. In another example, Hammer 47 has a moment of inertia of 470 kg·mm 2 It has the following moment of inertia. In yet another example, Hammer 47 has 460 kg·mm 2 It has the following moment of inertia.

[0117] In this embodiment, the diameter D31 of the hammer 47 is between 43 mm and 80 mm, and the total length L31 of the hammer 47 is between 26 mm and 45 mm. The diameter D31 of the hammer 47 is the maximum outer diameter of the hammer 47. The total length L31 of the hammer 47 is the maximum axial dimension of the hammer 47, and is the distance between the lower end and the upper end of the hammer 47. In one example, the hammer 47 has a diameter D31 of 43.2 mm or more. In another example, the hammer 47 has a diameter D31 of 43.4 mm or more. In yet another example, the hammer 47 has a diameter D31 of 43.6 mm or more. In one example, the hammer 47 has a diameter D31 of 77 mm or less. In another example, the hammer 47 has a diameter D31 of 74 mm or less. In yet another example, the hammer 47 has a diameter D31 of 71 mm or less. In one example, the hammer 47 has a total length L31 of 26.2 mm or more. In other examples, the Hammer 47 has an overall length L31 of 26.4 mm or more. In yet another example, the Hammer 47 has an overall length L31 of 26.6 mm or more. In one example, the Hammer 47 has an overall length L31 of 43 mm or less. In yet another example, the Hammer 47 has an overall length L31 of 41 mm or less. In yet another example, the Hammer 47 has an overall length L31 of 39 mm or less.

[0118] The ball 48 is made of a metal such as steel. The ball 48 is positioned between the spindle shaft portion 8B and the hammer 47. The ball 48 is positioned between the spindle groove 8F and the hammer groove 47A. The ball 48 can roll inside the spindle groove 8F and inside the hammer groove 47A, respectively. The hammer 47 is movable along with the ball 48. The spindle 8 and the hammer 47 can move relative to each other in the axial and rotational directions within the range of motion defined by the spindle groove 8F and the hammer groove 47A.

[0119] The ball 48 has a diameter of, for example, 5.0 mm to 9.0 mm. In one example, the ball 48 has a diameter of 5.2 mm to 8.8 mm. In another example, the ball 48 has a diameter of 5.4 mm to 8.6 mm.

[0120] Ball 48 has a weight of, for example, between 0.4g and 2.0g. In one example, ball 48 has a weight of between 0.5g and 1.8g. In another example, ball 48 has a weight of between 0.6g and 1.6g.

[0121] Ball 48 is, for example, 2.00 × 10 -3 kg·mm 2 The above 8.00 x 10 -3 kg·mm 2 It has the following moment of inertia. For example, ball 48 has a moment of inertia of 2.10 × 10⁻⁶. -3 kg·mm 2 The above 7.80 x 10 -3 kg·mm 2 It has the following moment of inertia. In another example, ball 48 has a moment of inertia of 2.15 × 10⁻⁶. -3 kg·mm 2 The above 7.60 x 10 -3 kg·mm 2 It has the following moment of inertia.

[0122] The spring 49 generates an elastic force that moves the hammer 47 downward. The spring 49 is a compression coil spring made by winding metal wires into a coil shape (i.e., a helical shape). The spring 49 biases the hammer 47 toward the anvil 10. The spring 49 is positioned between the flange portion 8A and the hammer 47 in the vertical direction. The lower part of the spring 49 is positioned in a ring-shaped recess 47C provided on the upper surface of the hammer 47. A washer 45 is provided inside the recess 47C. The washer 45 is supported by the body portion 47D via a ball 50. The upper end of the spring 49 is supported by the flange portion 8A. The lower end of the spring 49 is supported by the washer 45. The hammer 47 and the spring 49 are rotatable relative to each other around the second rotation axis BX due to the interposition of the washer 45 and the ball 50.

[0123] The spring 49 is assembled to the impact mechanism 9 in a pre-compressed state. The spring 49 applies a predetermined preload downward to the hammer 47 when the angle impact tool 1 is not in operation. In this specification, the length of the spring 49 when the angle impact tool 1 is not in operation (the length at which the preload is generated) is referred to as the preload length.

[0124] The spring 49 has a wire diameter D41 of, for example, 3.0 mm to 7.5 mm. In one example, the spring 49 has a wire diameter D41 of 3.2 mm to 7.3 mm. In another example, the spring 49 has a wire diameter D41 of 3.4 mm to 7.1 mm. In yet another example, the spring 49 has a wire diameter D41 of 3.5 mm to 7.0 mm.

[0125] The spring 49 has, for example, a coil inner diameter D42 of 20.0 mm to 45.0 mm. In one example, the spring 49 has a coil inner diameter D42 of 21.0 mm to 43.0 mm. In another example, the spring 49 has a coil inner diameter D42 of 22.0 mm to 41.0 mm. In yet another example, the spring 49 has a coil inner diameter D42 of 23.0 mm to 39.0 mm.

[0126] The spring 49 has, for example, a preload length L41 of 20 mm to 52 mm. In one example, the spring 49 has a preload length L41 of 22 mm to 50 mm. In another example, the spring 49 has a preload length L41 of 24 mm to 48 mm. In yet another example, the spring 49 has a preload length L41 of 25 mm to 47 mm.

[0127] The spring 49 applies a preload to the hammer 47, for example, between 250N and 500N. In one example, the spring 49 applies a preload to the hammer 47 between 260N and 480N. In another example, the spring 49 applies a preload to the hammer 47 between 270N and 460N. In yet another example, the spring 49 applies a preload to the hammer 47 between 280N and 440N.

[0128] The spring 49 has a spring constant of, for example, 30.0 N / mm or more and 75.0 N / mm or less. In one example, the spring 49 has a spring constant of 32.0 N / mm or more and 73.0 N / mm or less. In another example, the spring 49 has a spring constant of 34.0 N / mm or more and 71.0 N / mm or less. In yet another example, the spring 49 has a spring constant of 35.0 N / mm or more and 70.0 N / mm or less.

[0129] As shown in Figures 7 and 10, the anvil 10 is the output section of the angle impact tool 1. The anvil 10 rotates due to the rotational force of the motor 6. At least a portion of the anvil 10 is positioned below the spindle 8. At least a portion of the anvil 10 is positioned below the hammer 47. The anvil 10 is struck in the rotational direction by the hammer 47.

[0130] The anvil 10 has a rod-shaped anvil shaft portion 10A and an anvil projection portion 10B. An anvil recess 10C is provided at the upper end of the anvil 10 to receive the projection portion of the spindle shaft portion 8B. The anvil projection portion 10B is provided at the upper end of the anvil 10. The anvil projection portion 10B protrudes radially outward from the upper end of the anvil shaft portion 10A. The anvil shaft portion 10A protrudes downward from the inside of the case 4 through the anvil insertion hole 83 to the outside of the case 4. The lower end of the anvil shaft portion 10A is exposed to the outside of the case 4. A tip tool holder portion 51 is positioned at the lower end of the anvil 10. The tip tool holder portion 51 protrudes downward from the lower surface of the case 4. The tip tool holder portion 51 is provided on the exposed portion of the lower end of the anvil shaft portion 10A. The tip tool holder portion 51 is rotated by the spindle 8. The tip tool holder 51 is rotated by the spindle 8 via the hammer 47 and the anvil 10. The tip tool holder 51 is integrally formed with the anvil shaft 10A.

[0131] In the angle impact wrench according to this embodiment, the tip tool holder 51 is a rectangular prism-shaped engaging portion that engages with the engaging recess of the socket, which is the tip tool. The socket is held in a fitted state within the tip tool holder 51.

[0132] Figure 11 shows a cross-section of the tip tool holder 51 perpendicular to the second rotation axis BX. As shown in Figure 11, the tip tool holder 51 has a width across flats Wd of 3 / 8 inch to 7 / 8 inch in the cross-section perpendicular to the second rotation axis BX. The width across flats Wd of the tip tool holder 51 is the distance between opposite sides in the cross-section of the tip tool holder 51 and represents the engagement size of the engagement part of the compatible tip tool. The cross-sectional shape of the tip tool holder 51 may be a hexagon or other shape other than a square. The tip tool holder 51 may have a width across flats Wd of, for example, 3 / 8 inch, 1 / 2 inch, or 3 / 4 inch.

[0133] In this embodiment, the weight of the anvil 10 is between 55g and 250g. In one example, the anvil 10 has a weight of 58g or more. In another example, the anvil 10 has a weight of 60g or more. In yet another example, the anvil 10 has a weight of 62g or more. In one example, the anvil 10 has a weight of 240g or less. In another example, the anvil 10 has a weight of 230g or less. In yet another example, the anvil 10 has a weight of 225g or less.

[0134] In this embodiment, the moment of inertia of the anvil 10 is 3.60 kg·mm 2 The above is 30.00 kg·mm 2 The following is an example: Anvil 10 is 3.80 × 10 -3 kg·mm 2 It has the above moment of inertia. In another example, anvil 10 has 3.90 × 10 -3 kg·mm 2 It has the above moment of inertia. In yet another example, anvil 10 has 3.95 × 10 -3 kg·mm 2 It has the above moment of inertia. For example, anvil 10 has a moment of inertia of 29.00 × 10⁻⁶. -3 kg·mm 2It has the following moment of inertia. In another example, anvil 10 has 28.00 × 10⁻⁶. -3 kg·mm 2 It has the following moment of inertia. In yet another example, anvil 10 has 27.00 × 10 -3 kg·mm 2 It has the following moment of inertia.

[0135] As shown in Figure 5, in the embodiment, the vertical distance L51 between the lower end of the anvil 10 and the upper surface of the striking mechanism housing 82 is 85 mm or less. Preferably, the distance L51 is 83 mm or less. More preferably, the distance L51 is 82 mm or less. In one example, the anvil 10 has a 1 / 2 inch tip tool holder 51, and the vertical distance L51 between the lower end of the anvil 10 and the upper surface of the striking mechanism housing 82 is 81.0 mm. In another example, the anvil 10 has a 3 / 8 inch tip tool holder 51, and the vertical distance L51 between the lower end of the anvil 10 and the upper surface of the striking mechanism housing 82 is 78.0 mm.

[0136] In the embodiment, the distance L52 in the front-rear direction between the central axis of the anvil 10 and the front end surface of the striking mechanism housing 82 is 30 mm or less. In the embodiment, the central axis of the anvil 10 coincides with the second rotation axis BX. Preferably, the distance L52 is 28 mm or less. More preferably, the distance L52 is 27 mm or less. In one example, the distance L52 in the front-rear direction between the central axis of the anvil 10 and the front end surface of the striking mechanism housing 82 is 26.5 mm.

[0137] The anvil 10 is rotatably supported by an anvil bearing 46. The axis of rotation of the anvil 10 coincides with the second axis of rotation BX of the spindle 8. The anvil 10 rotates around the second axis of rotation BX. The anvil bearing 46 is positioned inside the anvil insertion hole 83. The anvil bearing 46 is positioned inside the anvil insertion hole 83 of the case 4. The anvil bearing 46 is held in the anvil insertion hole 83. The anvil insertion hole 83 is positioned around the anvil shaft portion 10A. The anvil bearing 46 rotatably supports the anvil shaft portion 10A. In this embodiment, the anvil bearing 46 is a sliding bearing. The anvil shaft portion 10A is provided with a ring-shaped groove 46A facing the anvil bearing 46. A ring-shaped sealing member 46B is positioned within the groove 46A. A washer 52 is also provided on the inner bottom surface of the case 4. Washer 52 faces the anvil projection 10B.

[0138] The hammer projection 47B is capable of contacting the anvil projection 10B. When the motor 6 is driven while the hammer projection 47B and the anvil projection 10B are in contact, the anvil 10 rotates together with the hammer 47 and the spindle 8.

[0139] The anvil 10 is struck in the rotational direction by the hammer 47. For example, in screw tightening work, if the load acting on the anvil 10 becomes high, there may be situations where the power generated by the motor 6 alone is insufficient to rotate the anvil 10. When the power generated by the motor 6 alone is insufficient to rotate the anvil 10, the rotation of the anvil 10 and the hammer 47 stops. Even if the rotation of the hammer 47 stops, the rotation of the spindle 8 continues due to the power generated by the motor 6. When the spindle 8 rotates while the rotation of the hammer 47 has stopped, the ball 48 moves upward, guided by the spindle groove 8F and the hammer groove 47A, respectively. The hammer 47 receives force from the ball 48 and moves upward along with the ball 48. In other words, the hammer 47 moves upward as the spindle 8 rotates while the rotation of the anvil 10 has stopped. As the hammer 47 moves upward, contact between the hammer projection 47B and the anvil projection 10B is released.

[0140] The spring 49 generates an elastic force that moves the hammer 47 downward. The hammer 47, having moved upward, moves downward due to the elastic force of the spring 49. As the hammer 47 moves downward, it receives a rotational force from the ball 48. That is, the hammer 47 moves downward while rotating. As the hammer 47 moves downward while rotating, the hammer projection 47B comes into contact with the anvil projection 10B while rotating. As a result, the anvil projection 10B is struck in the rotational direction by the hammer projection 47B. The anvil 10 is subjected to both the power of the motor 6 and the inertial force of the hammer 47. Therefore, the anvil 10 can rotate around the second rotation axis BX with high torque.

[0141] From the moment the hammer 47 begins striking, while the spindle 8 is rotated by the motor 6, the hammer 47 repeats a series of movements: retraction (rise) from the anvil 10, disengagement from the anvil 10, advancement (descendance) towards the anvil 10, and striking the anvil 10 (re-contact with the anvil 10). In this specification, as shown in Figure 7, the vertical travel distance Ls along the second rotation axis BX of the hammer 47 is referred to as the stroke of the hammer 47.

[0142] In this embodiment, the vertical travel distance Ls (stroke) of the hammer 47 relative to the spindle 8 is 8 mm or more and 16 mm or less. In one example, the hammer 47 is movable relative to the spindle 8 with a vertical travel distance Ls of 8.3 mm or more. In another example, the hammer 47 is movable relative to the spindle 8 with a vertical travel distance Ls of 8.6 mm or more. In yet another example, the hammer 47 is movable relative to the spindle 8 with a vertical travel distance Ls of 8.9 mm or more. In one example, the hammer 47 is movable relative to the spindle 8 with a vertical travel distance Ls of 15.5 mm or less. In another example, the hammer 47 is movable relative to the spindle 8 with a vertical travel distance Ls of 15.0 mm or less. In yet another example, the hammer 47 is movable relative to the spindle 8 with a vertical travel distance Ls of 14.5 mm or less.

[0143] In this embodiment, the number of strikes per revolution of the hammer 47 is greater than 1. In one example, the number of strikes per revolution of the hammer 47 is 1.5 or more. In another example, the number of strikes per revolution of the hammer 47 is 1.8 or more. In yet another example, the number of strikes per revolution of the hammer 47 is 2 or more.

[0144] Each time the hammer 47 strikes the anvil 10, an impact torque is applied to the fastening member that engages with the anvil 10 via the tip tool. In screw tightening operations, the fastening member is tightened further each time the impact torque is applied, so the tightening torque applied to the fastening member increases with the number of strikes.

[0145] The impact mechanism 9, with the above configuration, converts the continuous torque input from the motor 6 into intermittent rotational impacts capable of generating a tightening torque of 275 Nm or more to the fastening member. Preferably, the impact mechanism 9 is capable of generating a tightening torque of 280 Nm or more. More preferably, the impact mechanism 9 is capable of generating a tightening torque of 290 Nm or more. Even more preferably, the impact mechanism 9 is capable of generating a tightening torque of 300 Nm or more.

[0146] While the tightening torque achieved by impact is expected to converge to a certain value if the tightening process is carried out over a long period of time, measurement is difficult. Therefore, tightening torque is defined as the maximum value of the tightening torque achieved over a certain measurement period (maximum tightening torque). Maximum tightening torque is the torque achieved when the fastening components are tightened, and generally refers to the torque measured using a torque wrench or similar tool on the fastened components after tightening. It is not measured by loosening the nuts or bolts. Generally, this maximum tightening torque is listed in the manufacturer's catalog.

[0147] In one example, the impact mechanism 9 can generate a tightening torque of 300 Nm or more with a 6-second tightening time (i.e., a measurement time of 6 seconds). In another example, the impact mechanism 9 can generate a tightening torque of 310 Nm or more with a 6-second tightening time. In yet another example, the impact mechanism 9 can generate a tightening torque of 320 Nm or more with a 6-second tightening time.

[0148] In one example, the impact mechanism 9 can generate a tightening torque of 275 Nm or more with a 3-second tightening time (i.e., a measurement time of 3 seconds). In another example, the impact mechanism 9 can generate a tightening torque of 285 Nm or more with a 3-second tightening time. In yet another example, the impact mechanism 9 can generate a tightening torque of 295 Nm or more with a 3-second tightening time.

[0149] On the other hand, in the case of loosening screws, such as when removing a stuck fastener, the torque acting on the fastener peaks at the beginning of its rotation. The torque applied to a fastener during screw loosening is called the nut busting torque. The nut busting torque is the upper limit of the torque that can be used to loosen a fastener.

[0150] In this embodiment, the striking mechanism 9 is capable of generating a nut busting torque of 450 Nm or more. In one example, the striking mechanism 9 is capable of generating a nut busting torque of 460 Nm or more. In another example, the striking mechanism 9 is capable of generating a nut busting torque of 470 Nm or more. In yet another example, the striking mechanism 9 is capable of generating a nut busting torque of 480 Nm or more.

[0151] Table 1 shows the maximum tightening torque and nut busting torque in one example configuration of the embodiment, as well as the hammer configuration. Table 1 shows one example configuration of the embodiment and a comparative example of a conventional angle impact tool. [Table 1]

[0152] In Table 1, "6-second tightening" and "3-second tightening" indicate that the measurement time for the maximum tightening torque was 6 seconds and 3 seconds, respectively. For the angle impact tool 1 in the example configuration, the maximum tightening torque for 3 seconds of tightening is 300 Nm, and the maximum tightening torque for 6 seconds of tightening is 330 Nm. In contrast, the maximum tightening torque for the comparative example is 270 Nm. The maximum tightening torque for the comparative example is a catalog value, and the measurement time is unknown.

[0153] In the example configuration, the nut busting torque is 500 Nm. In contrast, the maximum tightening torque in the comparative example is 300 Nm.

[0154] In the angle impact tool 1 with the configuration example shown in Table 1, the hammer 47 has a torque of 45.9 kg·mm. 2 It has a moment of inertia of 154.1 g, a diameter D31 of 44.0 mm, and an overall length L31 of 26.8 mm. In contrast, the comparative hammer has a moment of inertia of 39.4 kg·mm 2 It has a moment of inertia of , a weight of 130.4 g, a diameter of 42.8 mm, and an overall length of 25.5 mm.

[0155] Table 2 shows several configuration examples for angle impact tools. Table 2 shows configuration examples 1, 2, and 3, which have different maximum tightening torques. [Table 2]

[0156] (Configuration Example 1) In Configuration Example 1, the impact mechanism 9 can generate a tightening torque of 300 Nm or more with a 3-second tightening time. Furthermore, in Configuration Example 1, the impact mechanism 9 can generate a tightening torque of 330 Nm or more with a 6-second tightening time. In Configuration Example 1, the impact mechanism 9 can generate a nut busting torque of 530 Nm or more. The anvil 10 in Configuration Example 1 has a tool holder 51 with a wrench width Wd of 3 / 8 inch. In Configuration Example 1, the wrench width Wd of the tool holder 51 may be 1 / 2 inch. In Configuration Example 1, the number of impacts per revolution of the hammer 47 is 2. In Configuration Example 1, the number of impacts per minute is 4000. In Configuration Example 1, the motor current value is 35A or more and 40A or less.

[0157] The spring 49 in Configuration Example 1 has a wire diameter D41 of 3.8 mm. The spring 49 in Configuration Example 1 has a coil inner diameter D42 of 24.4 mm. The spring 49 in Configuration Example 1 has a preload length L41 of 25.1 mm. The spring 49 in Configuration Example 1 applies a preload of 343 N to the hammer 47. The spring 49 in Configuration Example 1 has a spring constant of 36.3 N / mm.

[0158] The spindle shaft portion 8B of the spindle 8 in Configuration Example 1 has a diameter D21 of 14.0 mm. The spindle groove 8F of the spindle 8 in Configuration Example 1 has a lead angle of 32.0 degrees. The spindle 8 in Configuration Example 1 has a weight of 73.77 g. The spindle 8 in Configuration Example 1 has a load of 7.17 kg·mm. 2 It has a moment of inertia of .

[0159] The ball 48 in Configuration Example 1 has a diameter of 5.6 mm. The ball 48 in Configuration Example 1 has a weight of 0.70 g. The ball 48 in Configuration Example 1 is 2.18 × 10 -3 kg·mm 2 It has a moment of inertia of .

[0160] The hammer 47 in Configuration Example 1 has a weight of 154.1g. The hammer 47 in Configuration Example 1 has a weight of 45.91kg·mm 2It has a moment of inertia of . The hammer 47 in Configuration Example 1 has a diameter D31 of 44.0 mm and an overall length L31 of 26.8 mm. The hammer 47 in Configuration Example 1 is movable relative to the spindle 8 with a vertical travel distance Ls of 9.0 mm.

[0161] Anvil 10 in Configuration Example 1 has a weight of 62.50g. Anvil 10 in Configuration Example 1 has a weight of 3.98kg·mm 2 It has a moment of inertia of .

[0162] In the reduction mechanism 7 of configuration example 1, the reduction ratio between the bevel gear 35 and the spindle 8 is 8.36.

[0163] (Configuration example 2) In Configuration Example 2, the impact mechanism 9 can generate a tightening torque of 600 Nm or more with a 3-second tightening time. Furthermore, in Configuration Example 2, the impact mechanism 9 can generate a tightening torque of 700 Nm or more with a 6-second tightening time. In Configuration Example 2, the impact mechanism 9 can generate a nut busting torque of 1000 Nm or more. The anvil 10 in Configuration Example 2 has a tip tool holder 51 with a wrench width Wd of 1 / 2 inch. In Configuration Example 2, the number of impacts per revolution of the hammer 47 is 2. In Configuration Example 2, the number of impacts per minute is 2700.

[0164] The spring 49 in Configuration Example 2 has a wire diameter D41 of 5.0 mm. The spring 49 in Configuration Example 2 has a coil inner diameter D42 of 33.8 mm. The spring 49 in Configuration Example 2 has a preload length L41 of 32.5 mm. The spring 49 in Configuration Example 2 applies a preload of 290 N to the hammer 47. The spring 49 in Configuration Example 2 has a spring constant of 52.2 N / mm.

[0165] The spindle shaft portion 8B of the spindle 8 in Configuration Example 2 has a diameter D21 of 20.0 mm. The spindle groove 8F of the spindle 8 in Configuration Example 2 has a lead angle of 31.0 degrees. The spindle 8 in Configuration Example 2 has a weight of 149.23 g. The spindle 8 in Configuration Example 2 has a load of 19.27 kg·mm. 2 It has a moment of inertia of .

[0166] The ball 48 in Configuration Example 2 has a diameter of 6.4 mm. The ball 48 in Configuration Example 2 has a weight of 1.05 g. The ball 48 in Configuration Example 2 is 4.23 × 10 -3 kg·mm 2 It has a moment of inertia of .

[0167] The Hammer 47 in Configuration Example 2 has a weight of 293.0g. The Hammer 47 in Configuration Example 2 has a weight of 153.0kg·mm 2 It has a moment of inertia of . The hammer 47 in Configuration Example 2 has a diameter D31 of 56.0 mm and an overall length L31 of 32.0 mm. The hammer 47 in Configuration Example 2 is movable relative to the spindle 8 with a vertical travel distance Ls of 14.0 mm.

[0168] Anvil 10 in Configuration Example 2 has a weight of 89.47g. Anvil 10 in Configuration Example 2 has a weight of 8.64kg·mm 2 It has a moment of inertia of .

[0169] In the reduction mechanism 7 of configuration example 2, the reduction ratio between the bevel gear 35 and the spindle 8 is 9.

[0170] (Configuration Example 3) In Configuration Example 3, the impact mechanism 9 can generate a tightening torque of 800 Nm or more with a 3-second tightening time. Furthermore, in Configuration Example 3, the impact mechanism 9 can generate a tightening torque of 1200 Nm or more with a 6-second tightening time. In Configuration Example 3, the impact mechanism 9 can generate a nut busting torque of 1700 Nm or more. The anvil 10 in Configuration Example 3 has a tip tool holder 51 with a wrench width Wd of 3 / 4 inch. In Configuration Example 3, the number of impacts per revolution of the hammer 47 is 2. In Configuration Example 3, the number of impacts per minute is 2200.

[0171] The spring 49 in Configuration Example 3 has a wire diameter D41 of 6.5 mm. The spring 49 in Configuration Example 3 has a coil inner diameter D42 of 38.0 mm. The spring 49 in Configuration Example 3 has a preload length L41 of 46.0 mm. The spring 49 in Configuration Example 3 applies a preload of 428 N to the hammer 47. The spring 49 in Configuration Example 3 has a spring constant of 65.8 N / mm.

[0172] The spindle shaft portion 8B of the spindle 8 in Configuration Example 3 has a diameter D21 of 22.0 mm. The spindle groove 8F of the spindle 8 in Configuration Example 3 has a lead angle of 31.1 degrees. The spindle 8 in Configuration Example 3 has a weight of 241.93 g. The spindle 8 in Configuration Example 3 has a load of 38.96 kg·mm. 2 It has a moment of inertia of .

[0173] The ball 48 in Configuration Example 3 has a diameter of 7.1 mm. The ball 48 in Configuration Example 3 has a weight of 1.47 g. The ball 48 in Configuration Example 3 is 7.40 × 10 -3 kg·mm 2 It has a moment of inertia of .

[0174] The hammer 47 in Configuration Example 3 has a weight of 570.0g. The hammer 47 in Configuration Example 3 has a weight of 456.0kg·mm 2 It has a moment of inertia of . The hammer 47 in Configuration Example 3 has a diameter D31 of 70.0 mm and an overall length L31 of 37.0 mm. The hammer 47 in Configuration Example 3 is movable relative to the spindle 8 with a vertical travel distance Ls of 14.0 mm.

[0175] Anvil 10 in Configuration Example 3 has a weight of 222.94g. Anvil 10 in Configuration Example 3 has a weight of 26.98kg·mm 2 It has a moment of inertia of .

[0176] In the reduction mechanism 7 of configuration example 3, the reduction ratio between the bevel gear 35 and the spindle 8 is 10.

[0177] (effect) As described above, in the embodiment, the angle impact tool 1 includes a housing 2 which includes a grip portion 22 extending in the front-rear direction, a motor housing portion 21 positioned in front of the grip portion 22, and a battery holding portion 23 positioned behind the grip portion 22 for detachably holding the battery pack 25; a motor 6 which is positioned inside the motor housing portion 21 and has a rotor 27 which rotates around a first rotation axis AX in the front-rear direction by power supplied from the battery pack 25; and an impact mechanism 9 which converts a continuous torque input from the motor 6 into intermittent rotational impacts capable of generating a tightening torque of 275 Nm or more to the fastening member. The striking mechanism 9 includes a spindle 8 extending along a second rotation axis BX in the vertical direction, an anvil 10 positioned below the spindle 8 and including a tool tip holder 51 at its lower end having a two-sided width Wd of 3 / 8 inch or more and 7 / 8 inch or less in a cross section perpendicular to the second rotation axis BX, a hammer 47 that moves up and down relative to the spindle 8 and rotates around the second rotation axis BX to strike the anvil 10 in the rotational direction, and a spring 49 that biases the hammer 47 toward the anvil 10.

[0178] In the above configuration, the angle impact tool 1, which is equipped with a tip tool of 3 / 8 inch to 7 / 8 inch, has a structure that includes a grip portion 22 extending in the front-rear direction, a motor housing portion 21 positioned in front of the grip portion 22, and a battery holding portion 23 positioned behind the grip portion 22 that detachably holds the battery pack 25. This structure can generate a tightening torque of 275 Nm or more on the fastening member. This improves the tightening torque of the angle impact tool 1.

[0179] In this embodiment, the weight of the hammer 47 is between 135g and 600g.

[0180] With the above configuration, the impact force of the hammer 47 is improved, and high tightening torque can be achieved even with the angle impact tool 1.

[0181] In this embodiment, the number of blows per revolution of the hammer 47 is greater than 1.

[0182] With the above configuration, the number of blows from hammer 47 is increased, and high tightening torque can be achieved in a short time even with angle impact tool 1.

[0183] In this embodiment, the moment of inertia of the hammer 47 is 40 kg·mm 2 Above 500kg·mm 2 The following applies:

[0184] With the above configuration, the impact force of the hammer 47 is improved, and high tightening torque can be achieved even with the angle impact tool 1.

[0185] In this embodiment, the diameter D31 of the hammer 47 is between 43 mm and 80 mm. The total length L31 of the hammer 47 is between 26 mm and 45 mm.

[0186] In the above configuration, the impact mechanism 9 in the angle impact tool 1 does not need to be enlarged, improving convenience when working in confined spaces.

[0187] In this embodiment, the striking mechanism 9 includes a ball 48 that engages with the spindle 8 and the hammer 47, and moves the hammer 47 in the rotational and vertical directions as the spindle 8 rotates. The vertical movement distance Ls of the hammer 47 relative to the spindle 8 is 8 mm or more and 16 mm or less.

[0188] In the above configuration, even when achieving high tightening torque, it is possible to suppress an increase in the vertical travel distance Ls of the hammer 47. As a result, the vertical dimension of the striking mechanism 9 is shortened, improving convenience when working in confined spaces.

[0189] In this embodiment, the striking mechanism 9 is capable of generating a tightening torque of 300 Nm or more.

[0190] With the above configuration, even angle impact tool 1 can achieve a higher tightening torque.

[0191] In this embodiment, the striking mechanism 9 is capable of generating a nut busting torque of 450 Nm or more. Nut busting torque is the torque applied to a fastening member when loosening a fastened fastening member.

[0192] The above configuration makes it possible to achieve the high nut busting torque required when loosening fastening members that have become firmly fixed due to rust or other reasons.

[0193] In this embodiment, the weight of the anvil 10 is 55g or more and 250g or less.

[0194] With the above configuration, even angle impact tool 1 can achieve high tightening torque.

[0195] In this embodiment, the moment of inertia of the anvil 10 is 3.60 kg·mm 2 The above is 30.00 kg·mm 2 The following applies:

[0196] With the above configuration, even angle impact tool 1 can achieve high tightening torque.

[0197] In this embodiment, the angle impact tool 1 is positioned in front of the motor housing 21 and includes a case 4 having a striking mechanism housing 82 that houses the striking mechanism 9, with the tip tool holder 51 protruding downward. The vertical distance L51 between the lower end of the anvil 10 and the upper surface of the striking mechanism housing 82 is 85 mm or less.

[0198] In the above configuration, the vertical dimension of the part where the tightening work is performed is shortened, improving convenience when working in confined spaces.

[0199] In this embodiment, the distance L52 in the front-rear direction between the central axis of the anvil 10 and the front end surface of the striking mechanism housing 82 is 30 mm or less.

[0200] In the above configuration, the distance in the front-rear direction from the front end surface of the impact mechanism housing 82 is shortened. This improves the convenience of inserting the angle impact tool 1 into narrow spaces for work.

[0201] In this embodiment, the rotor 27 has a rotor shaft portion 33 that extends in the front-rear direction. The angle impact tool 1 further includes a bevel gear 35 provided on the rotor shaft portion 33, and a reduction mechanism 7 connected to the bevel gear 35 that reduces the rotation of the bevel gear 35 and transmits it to the spindle 8.

[0202] In the above configuration, the reduction mechanism 7 reduces the rotation of the motor 6, thereby obtaining the torque necessary to rotate the spindle 8 without increasing the size of the motor 6.

[0203] In this embodiment, the reduction mechanism 7 includes a first reduction unit 41 connected to a bevel gear 35 that reduces the rotation of the bevel gear 35 and rotates, and a second reduction unit 42 that reduces the rotation of the first reduction unit 41 and transmits it to the spindle 8.

[0204] In the above configuration, multiple reduction stages can be performed during the process of transmitting rotation to the spindle 8. This makes it possible to achieve a high reduction ratio.

[0205] In an embodiment, the battery holder 23 has a battery mounting portion 13 on its lower surface, on which a battery pack 25 can be attached.

[0206] In the above configuration, the battery pack 25 is attached to the lower surface of the battery holding section 23, so even a large battery pack 25 can be attached without increasing the size of the housing 2.

[0207] In one embodiment, the angle impact tool 1 is provided with a trigger lever 14 on the lower surface of the grip portion 22, which is operated to start the motor 6.

[0208] The above configuration improves the operability of the angle impact tool 1.

[0209] In one embodiment, the angle impact tool 1 comprises a motor 6 having a rotor 27 that rotates around a first rotation axis AX extending in the front-rear direction and a stator 26 for rotating the rotor 27; a motor housing portion 21 housing the motor 6; a grip portion 22 positioned behind the motor housing portion 21; a battery holding portion 23 positioned behind the grip portion 22 and detachably holding a battery pack 25 that shares power to the motor 6; a spindle 8 rotated by the rotor 27 and extending along a second rotation axis BX in the vertical direction; a hammer 47 rotated by the spindle 8; and an anvil 10 positioned below the hammer 47 and including a tip tool holding portion 51 at its lower end, having a two-sided width Wd of 3 / 8 inch or more and 7 / 8 inch or less in a cross section perpendicular to the second rotation axis BX. The maximum tightening torque of the anvil 10 is 275 Nm or more.

[0210] In the above configuration, the angle impact tool 1, which is equipped with a tip tool of 3 / 8 inch to 7 / 8 inch, has a structure that includes a motor housing section 21, a grip section 22 positioned behind the motor housing section 21, and a battery holding section 23 positioned behind the grip section 22 for detachably holding the battery pack 25. This structure can generate a maximum tightening torque of 275 Nm or more. This improves the tightening torque of the angle impact tool 1.

[0211] [Other embodiments] In the embodiments described above, the numerical values ​​shown for each configuration example are merely examples and are not limited to these. [Explanation of Symbols]

[0212] 1…Angle impact tool, 2…Housing, 2S…Screw, 4…Case, 4A…Case body, 4B…Lid, 4S…Screw, 6…Motor, 7…Reduction mechanism, 8…Spindle, 8A…Flange, 8B…Spindle shaft, 8C…Spindle gear, 8D…Cylindrical part, 8F…Spindle groove, 9…Impact mechanism, 10…Anvil, 10A…Anvil shaft, 10B…Anvil projection, 10C…Anvil recess, 12…Fan, 13…Battery mounting section, 14…Trigger lever, 14A…Switch body, 15…Forward / reverse rotation switch lever, 16…Operation panel, 16 A...Operation button, 16B...Indicator display, 16C...Switch board, 16D...Bracket, 17...Light unit, 18...Controller, 19...Air intake, 20...Exhaust port, 21...Motor housing section, 21A...Rear retaining section, 21B...Panel opening, 21C...Retaining groove, 22...Grip section, 22A...Grip, 23...Battery retaining section, 25...Battery pack, 26...Stator, 27...Rotor, 28...Stator core, 29...Front insulator, 30...Rear insulator, 31...Coil, 32...Rotor core section, 33...Rotor shaft section, 34...Ro Magnet, 35…Bevel gear, 37…Sensor board, 38F…Bearing, 38R…Bearing, 41…First reduction unit, 41A…Driven gear, 41B…First intermediate gear, 41C…First intermediate shaft, 41D…Intermediate bearing, 42…Second reduction unit, 42A…Second intermediate gear, 42B…Second intermediate shaft, 42C…Intermediate bearing, 44…Spindle bearing, 45…Washer, 46…Anvil bearing, 46A…Groove, 46B…Seal member, 47…Hammer, 47A…Hammer groove, 47B…Hammer projection, 47C…Recess, 47D…Body part, 47E…Inner cylinder part, 48… Ball, 49...Spring, 50...Ball, 51...Tip tool holder, 52...Washer, 53...Light emitter, 54...Substrate, 57...Optical component, 60...Light cover, 60A...Opening, 60S...Screw, 70...Screw, 81...Reduction mechanism housing, 82...Striking mechanism housing, 83...Anvil insertion hole, 84...Housing recess, 91...Intermediate support member, 92...Front wall, D11...Outer diameter, D21...Diameter, D31...Diameter, D41...Wire diameter, D42...Coil inner diameter, L11...Length, L31...Total length, L41...Preload length, L51...Distance, L52...Distance, Ls...Vertical movement distance, Wd...Width across flats.

Claims

1. A housing including a grip portion extending in the front-rear direction, a motor housing portion positioned in front of the grip portion, and a battery holding portion positioned behind the grip portion for detachably holding the battery pack, A motor having a rotor that is disposed inside the motor housing and rotates around a first rotation axis in the front-rear direction by power supplied from the battery pack, The system includes a striking mechanism that converts the continuous torque input from the motor into intermittent rotational impacts capable of generating a tightening torque of 275 Nm or more to the fastening member, The aforementioned striking mechanism is A spindle extending along the second rotation axis in the vertical direction, An anvil positioned below the spindle and including a tip tool holder at its lower end having a cross-sectional width of 3 / 8 inch to 7 / 8 inch in a cross-section perpendicular to the second rotation axis, A hammer that moves up and down relative to the spindle and rotates around the second rotation axis to strike the anvil in the rotational direction, The hammer comprises a spring that biases the hammer toward the anvil, Angle impact tool.

2. The weight of the aforementioned hammer is between 135g and 600g. An angle impact tool according to claim 1.

3. The number of blows per rotation of the aforementioned hammer is greater than 1. An angle impact tool according to claim 1.

4. The moment of inertia of the aforementioned hammer is 40 kg·mm ２ Above 500 kg・mm ２ The following is: An angle impact tool according to claim 1.

5. The diameter of the aforementioned hammer is between 43 mm and 80 mm. The overall length of the aforementioned hammer is between 26 mm and 45 mm. An angle impact tool according to claim 1.

6. The striking mechanism includes a ball that engages with the spindle and the hammer, and moves the hammer in the rotational and vertical directions as the spindle rotates. The vertical movement distance of the hammer relative to the spindle is 8 mm or more and 16 mm or less. An angle impact tool according to claim 1.

7. The aforementioned impact mechanism is capable of generating a tightening torque of 300 Nm or more. An angle impact tool according to claim 1.

8. The striking mechanism is capable of generating a nut busting torque of 450 Nm or more. An angle impact tool according to claim 1.

9. The weight of the anvil is between 55g and 250g. An angle impact tool according to claim 1.

10. The moment of inertia of the anvil is 3.60 kg·mm ２ The above is 30.00 kg・mm ２ The following is: An angle impact tool according to claim 1.

11. The motor housing is positioned in front of the motor housing and has a case that houses the striking mechanism, with the tip tool holder protruding downward, and a striking mechanism housing section for housing the striking mechanism. The vertical distance between the lower end of the anvil and the upper surface of the striking mechanism housing is 85 mm or less. An angle impact tool according to claim 1.

12. The distance in the front-rear direction between the central axis of the anvil and the front end surface of the striking mechanism housing is 30 mm or less. An angle impact tool according to claim 11.

13. The rotor has a rotor shaft portion that extends in the front-rear direction, The bevel gear provided on the rotor shaft, The system further comprises a reduction mechanism connected to the bevel gear, which reduces the rotation of the bevel gear and transmits it to the spindle. An angle impact tool according to claim 1.

14. The aforementioned reduction mechanism is A first reduction unit connected to the bevel gear rotates by reducing the rotation of the bevel gear, The system includes a second reduction unit that reduces the rotation of the first reduction unit and transmits it to the spindle, An angle impact tool according to claim 13.

15. The battery holder has a battery mounting portion on its lower surface into which the battery pack can be attached. An angle impact tool according to claim 1.

16. The lower surface of the grip portion is provided with a trigger lever that is operated to start the motor. An angle impact tool according to claim 1.

17. A motor having a rotor that rotates around a first rotation axis extending in the front-rear direction, and a stator for rotating the rotor, A motor housing section that houses the motor, A grip portion is positioned at the rear of the motor housing portion, A battery holder is located behind the grip portion and detachably holds a battery pack that shares power with the motor, A spindle rotated by the rotor and extending along a second rotation axis in the vertical direction, A hammer rotated by the aforementioned spindle, The anvil comprises an anvil positioned below the hammer and having a tip tool holder at its lower end having a two-sided width of 3 / 8 inch or more and 7 / 8 inch or less in a cross-section perpendicular to the second rotation axis, The maximum tightening torque of the anvil is 275 Nm or more. Angle impact tool.

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