Patent Application
20230364752
This application is based upon and claims the benefit of priority from Japanese Patent Applications No. 2022-078187 and No. 2022-078188, both filed on May 11, 2022, the entire contents of all of which are incorporated herein by reference.
The technology disclosed in the present specification relates to an impact tool.
In a technical field related to impact tools, there is known an impact tool as disclosed in JP 2015-033738 A.
In order to improve workability using an impact tool, a technique for suppressing an increase in size of the impact tool is required.
In addition, the impact tool includes a hammer that impacts an anvil in a rotation direction. The hammer is biased forward by an elastic member such as a coil spring. For example, in a screw fastening operation, when a load applied to the anvil increases, the hammer moves rearward against an elastic force (biasing force) of the elastic member, and rotates while moving forward owing to the elastic force of the elastic member. When an elastic member having a high elastic force is used in a low load operation in which the load applied to the anvil is low, it may be difficult to smoothly perform the screw fastening operation. Similarly, when an elastic member having a low elastic force is used in a high load operation in which the load applied to the anvil is high, it may be difficult to smoothly perform the screw fastening operation.
An object of the present disclosure is to suppress an increase in size of an impact tool.
In addition, an object of the present disclosure is to provide an impact tool capable of smoothly performing both a high load operation and a low load operation.
In one non-limiting aspect of the present disclosure, an impact tool may include: a motor; a spindle that includes a spindle shaft and a flange provided at a rear portion of the spindle shaft and that is rotated by a rotational force of the motor; a tool holding shaft at least a part of which is disposed forward of the spindle; a hammer that is supported by the spindle shaft and impacts the tool holding shaft in a rotation direction; and an elastic member disposed between a front surface of the flange and a support surface of the hammer disposed forward of the flange in the axial direction. The elastic member may include a disk spring.
In one non-limiting aspect of the present disclosure, an impact tool may include: a motor; a spindle that includes a spindle shaft and a flange provided at a rear portion of the spindle shaft and that is rotated by a rotational force of the motor; a tool holding shaft at least a part of which is disposed forward of the spindle; a hammer that is supported by the spindle shaft and impacts the tool holding shaft in a rotation direction; an elastic member disposed between a front surface of the flange and a support surface of the hammer disposed forward of the flange in an axial direction; and an elastic force adjusting mechanism configured to adjust an elastic force of the elastic member in an initial state before the motor is started.
In one or more embodiments, an impact tool includes: a motor; a spindle that includes a spindle shaft and a flange provided at a rear portion of the spindle shaft and that is rotated by a rotational force of the motor; a tool holding shaft at least a part of which is disposed forward of the spindle; a hammer that is supported by the spindle shaft and impacts the tool holding shaft in a rotation direction; and an elastic member disposed between a front surface of the flange and a support surface of the hammer disposed forward of the flange in the axial direction. The elastic member may include a disk spring.
According to the above configuration, since the elastic member includes the disk spring, a predetermined elastic force can be obtained in a state where the dimension in the axial direction is suppressed as compared with a case where the elastic member includes, for example, the coil spring. That is, when a predetermined elastic force is required for the elastic member, the dimension of the elastic member in the axial direction can be shortened in the case of using the disk spring as compared with the case of using the coil spring. As a result, the hammer can impact the tool holding shaft in the rotation direction in a state in which an increase in size of the impact tool is suppressed. In particular, an axial length of the impact tool is shortened. When the impact tool has a motor housing, a rear cover disposed at a rear end portion of the motor housing, and an output assembly disposed at a front portion of the motor housing; the axial length of the impact tool refers to a distance in the axial direction between a rear end portion of the rear cover and a front end portion of the output assembly.
In one or more embodiments, a plurality of disk springs may be disposed in the axial direction.
According to the above configuration, the elastic member can generate a high elastic force.
In one or more embodiments, some disk springs may be disposed around the spindle shaft.
According to the above configuration, an increase in size of the impact tool is suppressed.
In one or more embodiments, the hammer may include: an inner cylindrical portion disposed around the spindle shaft; a front outer cylindrical portion disposed radially outside with respect to the inner cylindrical portion and disposed forward of the inner cylindrical portion; and a rear outer cylindrical portion disposed radially outside with respect to the inner cylindrical portion and disposed rearward of the front outer cylindrical portion. Some disk springs may be disposed around the inner cylindrical portion.
According to the above configuration, an increase in size of the impact tool is suppressed.
In one or more embodiments, the hammer may have a recess recessed forward from the rear surface of the hammer. The recess may be defined by an inner circumferential surface of the rear outer cylindrical portion, an outer circumferential surface of the inner cylindrical portion, and the support surface. At least a part of the elastic member may be disposed in the recess.
According to the above configuration, an increase in size of the impact tool is suppressed.
In one or more embodiments, the impact tool may include a washer disposed in the recess to support a front end of the elastic member. The front end of the elastic member may be connected to the hammer via the washer.
According to the above configuration, the front end portion of the elastic member is stably connected to the hammer via the washer.
In one or more embodiments, the spring constant of the elastic member may be 100 [N/mm] or more.
According to the above configuration, the elastic member can generate a high elastic force.
In one or more embodiments, an impact tool includes: a motor; a spindle that includes a spindle shaft and a flange provided at a rear portion of the spindle shaft and that is rotated by a rotational force of the motor; a tool holding shaft at least a part of which is disposed forward of the spindle; a hammer that is supported by the spindle shaft and impacts the tool holding shaft in a rotation direction; and an elastic member disposed between a front surface of the flange and a support surface of the hammer disposed forward of the flange in the axial direction. The spring constant of the elastic member may be 100 [N/mm] or more.
According to the above configuration, the elastic member can generate a high elastic force.
In one or more embodiments, the spring constant of the elastic member may be 10,000 [N/mm] or less.
According to the above configuration, an increase in size of the elastic member is suppressed.
In one or more embodiments, the elastic member may include a plurality of coil springs disposed about the rotation axis of the spindle.
According to the above configuration, the elastic member can generate a high elastic force.
In one or more embodiments, a front end portion of each of the coil springs may be in contact with the support surface of the hammer.
According to the above configuration, the front end portion of each of the coil springs is stably connected to the hammer.
In one or more embodiments, the impact tool may include support pins respectively disposed inside the coil springs. The support pins may be fixed to the hammer.
According to the above configuration, the coil springs are positioned in both the radial direction and the circumferential direction.
In one or more embodiments, the impact tool may include a movable anvil movably supported by the tool holding shaft. The hammer may impact the movable anvil in the rotation direction without being displaced in the axial direction.
According to the above configuration, since the movable anvil movably supported by the tool holding shaft is provided, the hammer can impact the movable anvil in the rotation direction without being displaced in the axial direction. Since the hammer is not displaced in the axial direction, occurrence of vibration in the axial direction is suppressed in the impact tool.
In one or more embodiments, the movable anvil may move to change between a first state in which at least a part of the movable anvil protrudes radially outward from an outer circumferential surface of the tool holding shaft and a second state in which the movable anvil is positioned radially inside with respect to the outer circumferential surface of the tool holding shaft. The hammer may impact the movable anvil in the first state and rotate around the spindle shaft in the second state.
According to the above configuration, the hammer can impact the movable anvil in the rotation direction without being displaced in the axial direction.
In one or more embodiments, the impact tool may include a cam ring that is coupled to the flange via a ball so as to be rotatable relative to the flange and is coupled to the hammer so as to be movable relative to the hammer in the axial direction but so as not to be rotatable relative to the hammer. The cam ring may be disposed so as to face the front surface of the flange. The elastic member may be disposed between the front surface of the cam ring and the support surface of the hammer in the axial direction.
According to the above configuration, the cam ring is coupled to the flange of the spindle via the ball so as to be rotate relative to the flange. Furthermore, the cam ring is coupled to the hammer so as to be movable relative to the hammer in the axial direction but not to be rotatable relative to the hammer. As a result, the hammer can impact the tool holding shaft in the rotation direction in a state in which the axial length is shortened.
In one or more embodiments, the cam ring may be coupled to a rear portion of the hammer. The elastic member may be disposed in a closed space defined by the spindle shaft, the hammer, and the cam ring.
According to the above configuration, when the hammer impacts the tool holding shaft in the rotation direction via the movable anvil, the cam ring and the elastic member also rotate together with the hammer. That is, when the hammer impacts the tool holding shaft, not only an inertia moment of the hammer but also an inertia moment of the cam ring and an inertia moment of the elastic member are applied to the tool holding shaft. As a result, the tool holding shaft is impacted with a high impacting force.
In one or more embodiments, the ball may be disposed between a spindle groove provided in the flange and a cam groove provided in the cam ring.
According to the above configuration, the ball can move to roll between the spindle groove and the cam groove.
In one or more embodiments, each of the spindle groove and the cam groove may have an arc shape. At least a part of the spindle groove may be inclined rearward toward one side in the circumferential direction. At least a part of the cam groove may be inclined rearward toward the one side in the circumferential direction.
According to the above configuration, when the flange and the cam ring rotate relative to each other, the cam ring can move in a front-rear direction.
In one or more embodiments, the elastic member may generate an elastic force that moves the cam ring rearward.
According to the above configuration, the cam ring can move rearward by the elastic force of the elastic member.
In one or more embodiments, in the relative rotation of the flange and the cam ring, the ball may move toward an end portion on one side in the circumferential direction of the spindle groove, so that the cam ring may move forward. The cam ring may rotate while moving rearward by the elastic force of the elastic member. The hammer may rotate by the rotation of the cam ring to impact the movable anvil in the rotation direction.
According to the above configuration, the cam ring moves rearward by the elastic force of the elastic member, and thus, the hammer can be rotated and can impact the movable anvil in the rotation direction.
In one or more embodiments, an impact tool may include: a motor; a spindle that includes a spindle shaft and a flange provided at a rear portion of the spindle shaft and that is rotated by a rotational force of the motor; a tool holding shaft at least a part of which is disposed forward of the spindle; a hammer that is supported by the spindle shaft and impacts the tool holding shaft in a rotation direction; an elastic member disposed between a front surface of the flange and a support surface of the hammer disposed forward of the flange in an axial direction; and an elastic force adjusting mechanism configured to adjust an elastic force of the elastic member in an initial state before the motor is started.
According to the above configuration, since the elastic force of the elastic member can be adjusted, the impact tool can smoothly perform each of a high load operation and a low load operation. When the low load operation is performed, the elastic force of the elastic member is adjusted so that the elastic force of the elastic member becomes low; and when the high load operation is performed, the elastic force of the elastic member is adjusted so that the elastic force of the elastic member becomes high, whereby the impact tool can smoothly perform both the high load operation and the low load operation.
In one or more embodiments, the elastic force adjusting mechanism may adjust an amount of compression of the elastic member in the initial state.
According to the above configuration, the elastic force of the elastic member is adjusted by adjusting the amount of compression of the elastic member in the initial state. When the amount of compression is small, the elastic force of the elastic member decreases, and when the amount of compression is large, the elastic force of the elastic member increases.
In one or more embodiments, a rear end of the elastic member may be supported on the flange. The elastic force adjusting mechanism may adjust the amount of compression by moving a position of a front end of the elastic member.
According to the above configuration, the amount of compression is adjusted by moving the position of the front end of the elastic member in a state in which the position of the rear end of the elastic member is fixed.
In one or more embodiments, the elastic force adjusting mechanism may include a screw disposed in a screw hole formed in the hammer and connected to the front end portion of the elastic member. The amount of compression may be adjusted by rotation of the screw.
According to the above configuration, the screw is rotated in a state in which the screw is disposed in the screw hole, so that the screw moves in the front-rear direction. As a result, the amount of compression is adjusted.
In one or more embodiments, the impact tool may include a washer that supports the front end of the elastic member. A rear end of the screw may contact a front surface of the washer. The screw may be connected to the elastic member via the washer.
According to the above configuration, the movement of the front end portion of the elastic member is smoothly performed.
In one or more embodiments, a plurality of screw holes may be formed at intervals around a rotation axis of the hammer. A plurality of the screws may be disposed one by one in the plurality of screw holes.
According to the above configuration, the amount of compression of the elastic member is adjusted and the inclination angle of the elastic member with respect to the spindle is adjusted by adjusting the position of each of the screws in the front-rear direction. The inclination angle of the elastic member with respect to the spindle refers to an angle formed by the rotation axis of the spindle and the rotation axis (central axis) of the elastic member.
In one or more embodiments, the hammer may include: an inner cylindrical portion disposed around the spindle shaft; a front outer cylindrical portion disposed radially outside with respect to the inner cylindrical portion and disposed forward of the inner cylindrical portion; and a rear outer cylindrical portion disposed radially outside with respect to the front outer cylindrical portion and disposed rearward of the front outer cylindrical portion. The screw hole may penetrate a front end surface of the rear outer cylindrical portion and the support surface.
According to the above configuration, an assembler or an operator of the impact tool can smoothly bring the screw fastening tool into contact with the screw disposed in the screw hole, and can smoothly rotate the screw.
In one or more embodiments, the impact tool may include: a hammer case that houses the hammer; and a hammer bearing that is held by the hammer case and supports the hammer in a rotatable manner. The hammer bearing may be disposed around the front outer cylindrical portion.
According to the above configuration, after the adjustment of the elastic force by the screw is completed, the hammer bearing is disposed so as to cover the front end portion of the screw hole. This protects the screw with the hammer bearing.
In one or more embodiments, the impact tool may include a hammer case that houses the hammer. The hammer case may have a through hole overlapping the screw hole in both the radial direction and the circumferential direction. The screw may be rotated through the through hole.
According to the above configuration, the operator can smoothly bring the screw fastening tool into contact with the screw disposed in the screw hole via the through hole, and can smoothly rotate the screw. The operator can appropriately adjust the elastic force of the elastic member according to the work content.
In one or more embodiments, the impact tool may include a hammer bearing that is held by the hammer case and supports the hammer in a rotatable manner. The hammer bearing may be disposed around the rear outer cylindrical portion.
According to the above configuration, since the front end of the screw hole is not covered with the hammer bearing, the operator can smoothly bring the screw fastening tool into contact with the screw disposed in the screw hole via the through hole, and can smoothly rotate the screw.
In one or more embodiments, the impact tool may include: a bearing box that holds a spindle; and a hammer case that holds a hammer. The hammer case may be coupled to the bearing box via the screw portion. The hammer case may rotate relative to the bearing box and move in the axial direction, so that the elastic force of the elastic member may be adjusted.
According to the above configuration, the operator can adjust the elastic force of the elastic member by holding and rotating the hammer case by his/her hand. The operator can adjust the elastic force of the elastic member without using a screw fastening tool.
In one or more embodiments, the impact tool may include: a motor housing that houses the motor; and a first rotation-preventing mechanism configured to prevent relative rotation of the motor housing and the bearing box.
According to the above configuration, when the hammer case is rotated, the rotation of the bearing box is prevented by the first rotation-preventing mechanism, so that the operator can smoothly rotate the hammer case with respect to the bearing box.
In one or more embodiments, the impact tool may include: a cover that covers the hammer case; and a second rotation-preventing mechanism configured to prevent relative rotation of the cover and the hammer case. The hammer case may be rotated via the cover.
According to the above configuration, since the relative rotation of the cover and the hammer case is prevented by the second rotation-preventing mechanism, the operator can rotate the hammer case by holding and rotating the cover with his/her hand. When the hammer case is rotated, the elastic force of the elastic member is adjusted. The operator can adjust the elastic force of the elastic member without directly touching the hammer case.
In one or more embodiments, the impact tool may include a positioning mechanism configured to position the cover in the circumferential direction.
According to the above configuration, unnecessary rotation of the hammer case and the cover is suppressed.
In one or more embodiments, the elastic member may include a disk spring.
According to the above configuration, an increase in size of the impact tool is suppressed. When a predetermined elastic force is required for the elastic member, the dimension of the elastic member in the axial direction can be shortened in the case of using the disk spring as compared with the case of using the coil spring, for example. As a result, the hammer can impact the tool holding shaft in the rotation direction in a state in which an increase in size of the impact tool is suppressed. In particular, an axial length of the impact tool is shortened. When the impact tool has a motor housing, a rear cover disposed at a rear end of the motor housing, and an output assembly disposed at a front portion of the motor housing, the axial length of the impact tool refers to a distance in the axial direction between a rear end of the rear cover and a front end of the output assembly.
In one or more embodiments, the impact tool may include a washer that supports the front end portion of the elastic member. The front end portion of the elastic member may be connected to the hammer via the washer.
According to the above configuration, the front end of the elastic member is stably connected to the hammer via the washer.
In one or more embodiments, the impact tool may include a movable anvil movably supported by the tool holding shaft. The hammer may impact the movable anvil in the rotation direction without being displaced in the axial direction.
According to the above configuration, since the movable anvil movably supported by the tool holding shaft is provided, the hammer can impact the movable anvil in the rotation direction without being displaced in the axial direction. Since the hammer is not displaced in the axial direction, occurrence of vibration in the axial direction is suppressed in the impact tool.
In one or more embodiments, the movable anvil may move to change between a first state in which at least a part of the movable anvil protrudes radially outward from an outer circumferential surface of the tool holding shaft and a second state in which the movable anvil is positioned radially inside with respect to the outer circumferential surface of the tool holding shaft. The hammer may impact the movable anvil in the first state and rotate around the spindle shaft in the second state.
According to the above configuration, the hammer can impact the movable anvil in the rotation direction without being displaced in the axial direction.
In one or more embodiments, the impact tool may include a cam ring that is coupled to the flange via a ball so as to be rotatable relative to the flange and is coupled to the hammer so as to be movable relative to the hammer in the axial direction but so as not to be rotatable relative to the hammer. The cam ring may be disposed so as to face the front surface of the flange. The elastic member may be disposed between the front surface of the cam ring and the support surface of the hammer in the axial direction.
According to the above configuration, the cam ring is coupled to the flange of the spindle via the ball so as to be rotatable relative to the flange. Furthermore, the cam ring is coupled to the hammer so as to be movable relative to the hammer in the axial direction but not to be rotatable relative to the hammer. As a result, the hammer can impact the tool holding shaft in the rotation direction in a state in which the axial length is shortened.
According to one or more embodiments, the cam ring may be coupled to a rear portion of the hammer. The elastic member may be disposed in a closed space defined by the spindle shaft, the hammer, and the cam ring.
According to the above configuration, when the hammer impacts the tool holding shaft in the rotation direction via the movable anvil, the cam ring and the elastic member also rotate together with the hammer. That is, when the hammer impacts the tool holding shaft, not only an inertia moment of the hammer but also an inertia moment of the cam ring and an inertia moment of the elastic member are applied to the tool holding shaft. As a result, the tool holding shaft is impacted with a high impacting force.
Hereinafter, embodiments will be described with reference to the drawings. Components of the embodiments described below can be appropriately combined. In addition, some components may not be used.
In the embodiments, the positional relationships among parts will be described using the terms “left”, “right”, “front”, “rear”, “up”, and “down”. These terms indicate the relative positions or directions, using the center of the impact tool as a reference. The impact tool includes a motor 6 as a power supply.
In the embodiment, a direction parallel to a rotation axis AX of the motor 6 is appropriately referred to as an axial direction. A direction around the rotation axis AX is appropriately referred to as a circumferential direction or a rotation direction. A radiation direction of the rotation axis AX is appropriately referred to as a radial direction.
A direction away from or a position far from the center of the impact tool toward a defined direction in the axial direction is appropriately referred to as one side in the axial direction, and a side opposite to the one side in the axial direction is appropriately referred to as the other side in the axial direction. A direction defined in the circumferential direction is appropriately referred to as one side in the circumferential direction, and a side opposite to the one side in the circumferential direction is appropriately referred to as the other side in the circumferential direction. A direction away from or a position far from the rotation axis AX in the radial direction is appropriately referred to as a radial outside. A side opposite to the radial outside is appropriately referred to as a radial inside.
In the embodiment, the axial direction coincides with the front-rear direction. The one side in the axial direction may be regarded as a front side. The other side in the axial direction may be regarded as a rear side.
A first embodiment will be described.
Outline of Impact Tool
In the embodiment, the impact tool 1 is an impact driver, which is a type of screw fastening tool. The impact tool 1 includes a housing 2, a rear cover 3, an output assembly 4, a battery mounting unit 5, a motor 6, a fan 7, a controller 8, a trigger lever 9, a forward/reverse rotation switching lever 10, an interface unit 11, a mode switching switch 12, and a light 13.
The housing 2 houses at least some of the components of the impact tool 1. The housing 2 is made of synthetic resin. In the embodiment, the housing 2 is made of nylon. The housing 2 includes a pair of half-split housings. The housing 2 includes a left housing 14 and a right housing 15 disposed to the right of the left housing 14. The left housing 14 and the right housing 15 are fixed by a plurality of housing screws 16.
The housing 2 includes a motor housing 17, a grip 18, and a battery holder 19.
The motor housing 17 houses the motor 6. The motor housing 17 houses at least a part of the output assembly 4. The motor housing 17 has a tubular shape.
An operator grips the grip 18. The grip 18 extends downward from the motor housing 17.
The battery holder 19 holds a battery pack 20 via the battery mounting unit 5. The battery holder 19 houses the controller 8. The battery holder 19 is connected to a lower end of the grip 18.
The rear cover 3 covers an opening at a rear end of the motor housing 17. The rear cover 3 is disposed rearward of the motor housing 17. The rear cover 3 is made of synthetic resin. The rear cover 3 is fixed to the rear end of the motor housing 17 by two screws. The rear cover 3 houses at least a part of the fan 7.
The motor housing 17 has air-intake ports 21. The rear cover 3 has an air-exhaust ports 22. Air from outside of the housing 2 flows into the internal space of the housing 2 via the air-intake ports 21. Air from the internal space of the housing 2 flows out to the outside of the housing 2 via the air-exhaust ports 22.
The output assembly 4 is disposed forward of the motor 6. The output assembly 4 includes a hammer case 23, a bearing box 24, a speed reduction mechanism 25, a spindle 26, a spindle bearing 27, an impact mechanism 28, an elastic force adjusting mechanism 29, a hammer bearing 30, a tool holding shaft 31, shaft bearings 32, movable anvils 33, and a tool holding mechanism 34.
The hammer case 23 is made of metal. In the embodiment, the hammer case 23 is made of aluminum. At least a part of the hammer case 23 is disposed forward of the motor housing 17. The hammer case 23 has a tubular shape. The bearing box 24 is fixed to a rear end of the hammer case 23. The bearing box 24 and a rear portion of the hammer case 23 are disposed inside the motor housing 17. The bearing box 24 and the rear portion of the hammer case 23 are sandwiched between the left housing 14 and the right housing 15. Each of the bearing box 24 and the hammer case 23 is fixed to the motor housing 17.
The speed reduction mechanism 25, the spindle 26, the impact mechanism 28, the movable anvils 33, the spindle bearing 27, the hammer bearing 30, and the shaft bearings 32 are disposed in the internal space of the output assembly 4 defined by the hammer case 23 and the bearing box 24. At least a part of the tool holding shaft 31 is disposed in the internal space of the output assembly 4.
The battery pack 20 is mounted on the battery mounting unit 5. The battery mounting unit 5 is disposed below the battery holder 19. The battery pack 20 is detachable from the battery mounting unit 5. The battery pack 20 functions as a power source of the impact tool 1. The battery pack 20 is mounted on the battery mounting unit 5 by being inserted into the battery mounting unit 5 from the front of the battery holder 19. The battery pack 20 is detached from the battery mounting unit 5 by being removed forward from the battery mounting unit 5. The battery pack 20 includes one or more secondary batteries. In the embodiment, the battery pack 20 includes one or more rechargeable lithium-ion batteries. The battery pack 20 can supply power to the impact tool 1 by being mounted on the battery mounting unit 5. The motor 6 is driven based on the electric power (current) supplied from the battery pack 20. Each of the controller 8 and the interface unit 11 operates based on the power supplied from the battery pack 20.
The motor 6 is a power supply of the impact tool 1. The motor 6 is an electric motor that is driven based on power supplied from the battery pack 20. The motor 6 is an inner-rotor-type brushless motor. The motor 6 includes a stator 35 and a rotor 36. The motor housing 17 supports the stator 35. At least a part of the rotor 36 is disposed inside the stator 35. The rotor 36 rotates with respect to the stator 35. The rotor 36 rotates about a rotation axis AX extending in the front-rear direction.
The stator 35 includes a stator core 37, a front insulator 38, a rear insulator 39, and coils 40.
The stator core 37 is disposed radially outside with respect to the rotor 36. The stator core 37 includes a plurality of laminated steel plates. The steel plates are plates made of a metal containing iron as a main component. The stator core 37 has a cylindrical shape. The stator core 37 includes teeth that respectively support the coils 40.
The front insulator 38 is fixed to the front portion of the stator core 37. The rear insulator 39 is fixed to the rear portion of the stator core 37. Each of the front insulator 38 and the rear insulator 39 is an electrically insulating member made of a synthetic resin. The front insulator 38 is disposed so as to cover some of the teeth surfaces. The rear insulator 39 is disposed so as to cover some of the teeth surfaces.
The coils 40 are mounted on the stator core 37 via the front insulator 38 and the rear insulator 39. The coils 40 are disposed around the teeth of the stator core 37 via the front insulator 38 and the rear insulator 39. The coils 40 and the stator core 37 are electrically insulated from one another by the front insulator 38 and the rear insulator 39. The coils 40 are electrically connected via a short-circuit member.
The rotor 36 rotates about the rotation axis AX. The rotor 36 includes a rotor core 41, a rotor shaft 42, at least one rotor magnet 43, and at least one sensor magnet 44.
Each of the rotor core 41 and the rotor shaft 42 is made of steel. The rotor shaft 42 is fixed to the rotor core 41. The rotor core 41 has a cylindrical shape. The rotor shaft 42 is disposed radially inside with respect to the rotor core 41. A front portion of the rotor shaft 42 protrudes forward from a front end surface of the rotor core 41. A rear portion of the rotor shaft 42 protrudes rearward from a rear end surface of the rotor core 41.
The rotor magnet 43 is fixed to the rotor core 41. The rotor magnet 43 has a cylindrical shape. The rotor magnet 43 is disposed around the rotor core 41.
The sensor magnet 44 is fixed to the rotor core 41. The sensor magnet 44 has a circular ring shape. The sensor magnet 44 is disposed on the front end surface of the rotor core 41 and the front end surface of the rotor magnet 43.
A sensor substrate 45 is attached to the front insulator 38. The sensor substrate 45 is fixed to the front insulator 38 with at least one screw. The sensor substrate 45 includes a circular circuit board and a magnetic sensor supported by the circuit board. At least a part of the sensor substrate 45 faces the sensor magnet 44. The magnetic sensor detects a position of the rotor 36 in a rotation direction by detecting a position of the sensor magnet 44.
The rear portion of the rotor shaft 42 is rotatably supported by a rotor bearing 46. The front portion of the rotor shaft 42 is rotatably supported by a rotor bearing 47. The rotor bearing 46 is held by the rear cover 3. The rotor bearing 46 is held by the bearing box 24 holds. A front end of the rotor shaft 42 is disposed in the internal space of the output assembly 4 through an opening of the bearing box 24.
A pinion gear 48 is fixed to the front end of the rotor shaft 42. The pinion gear 48 is coupled to at least a part of the speed reduction mechanism 25. The rotor shaft 42 is coupled to the speed reduction mechanism 25 via the pinion gear 48.
The fan 7 generates an air flow for cooling the motor 6. The fan 7 is disposed rearward of the motor 6. The fan 7 is disposed between the rotor bearing 46 and the stator 35. The fan 7 is fixed to at least a part of the rotor 36. The fan 7 is fixed to the rear portion of the rotor shaft 42 via a bush 49. The fan rotates when the rotor 36 rotates. When the rotor shaft 42 rotates, the fan 7 rotates together with the rotor shaft 42. When the fan 7 rotates, air from outside of the housing 2 flows into the internal space of the housing 2 through the air-intake ports 21. The air that has flowed into the internal space of the housing 2 flows through the internal space of the housing 2, thereby cooling the motor 6. The air that has flowed through the internal space of the housing 2 flows out to the outside of the housing 2 via the air-exhaust ports 22 while the fan 7 is rotating.
The controller 8 outputs control signals, which control the motor 6. The battery holder 19 houses the controller 8. The controller 8 changes the control mode of the motor 6 based on the work contents required to be performed by the impact tool 1. The control mode of the motor 6 refers to a control method or a control pattern of the motor 6. The controller 8 includes a circuit board 50 and a case 51. A plurality of electronic components are mounted on the circuit board 50. The case 51 houses the circuit board 50. Examples of the electronic components mounted on the circuit board 50 include: a processor such as a central processing unit (CPU); a nonvolatile memory such as a read only memory (ROM) and a storage; a volatile memory such as a random access memory (RAM); transistors, and resistors.
The trigger lever 9 is operated by an operator to start the motor 6. The trigger lever 9 is provided on the grip 18. The trigger lever 9 protrudes forward from an upper portion of a front portion of the grip 18. Driving and stopping of the motor 6 are switched by operating the trigger lever 9.
The forward/reverse rotation switching lever 10 is operated by an operator for switching the rotation direction of the motor 6. The forward/reverse rotation switching lever 10 is provided at an upper portion of the grip 18. In response to the operation of the forward/reverse rotation switching lever 10, the rotation direction of the motor 6 is changed from one of a forward-rotational direction and a reverse-rotation direction to the other. When the rotation direction of the motor 6, the rotation direction of the spindle 26 is changed. When the forward/reverse rotation switching lever 10 is disposed at a neutral position, the trigger lever 9 cannot be operated.
The interface unit 11 includes a plurality of operation buttons 52 operated by an operator. The interface unit 11 is provided in the battery holder 19. The interface unit 11 is provided, forward of the grip 18, on an upper surface of the battery holder 19. An operation mode of the motor 6 is changed in response to the operation of the operation buttons 52 by an operator.
The mode switching switch 12 is operated by an operator for changing the control mode of the motor 6. The mode switching switch 12 is disposed above the trigger lever 9.
The light 13 emits illumination light. The light 13 illuminates the surroundings of the tool holding shaft 31 and the front of the tool holding shaft 31 with the illumination light.
Output Assembly
The output assembly 4 includes the hammer case 23, the bearing box 24, the speed reduction mechanism 25, the spindle 26, the spindle bearing 27, the impact mechanism 28, the elastic force adjusting mechanism 29, the hammer bearing 30, the tool holding shaft 31, the shaft bearings 32, the movable anvil 33s, and the tool holding mechanism 34.
Each of the rotor 36, the spindle 26, and the tool holding shaft 31 rotates about the rotation axis AX. The rotation axis of the rotor 36, the rotation axis of the spindle 26, and the rotation axis of the tool holding shaft 31 coincide with one another. Each of the spindle 26 and the tool holding shaft 31 is rotated by rotational force generated by the motor 6.
Hammer Case
The hammer case 23 includes a large cylindrical portion 53 and a small cylindrical portion 54. Each of the large cylindrical portion 53 and the small cylindrical portion 54 is disposed so as to surround the rotation axis AX. The small cylindrical portion 54 is disposed forward of the large cylindrical portion 53. The large cylindrical portion 53 has an inner diameter larger than that of the small cylindrical portion 54. The large cylindrical portion 53 has an outer diameter larger than that of the small cylindrical portion 54.
The bearing box 24 is fixed to a rear end of the hammer case 23. The bearing box 24 includes a ring 55, a rear plate 56, and a protrusion 57. The ring 55 is disposed so as to surround the rotation axis AX. The ring 55 is inserted into a rear end of the large cylindrical portion 53. The rear plate 56 is connected to a rear end of the ring 55. An opening is provided in a central portion of the rear plate 56. The protrusion 57 is provided on the rear surface of the rear plate 56. The protrusion 57 protrudes rearward from the rear surface of the rear plate 56. The protrusion 57 is disposed so as to surround the opening of the rear plate 56. Each of the rear plate 56 and the protrusion 57 is connected to the motor housing 17.
Speed Reduction Mechanism
The speed reduction mechanism 25 couples the rotor shaft 42 and the spindle 26. The speed reduction mechanism 25 transmits rotation of the rotor 36 to the spindle 26. The speed reduction mechanism 25 causes the spindle 26 to rotate at a rotational speed that is lower than a rotational speed of the rotor shaft 42. The speed reduction mechanism 25 includes a planetary gear mechanism.
The speed reduction mechanism 25 includes a plurality of planetary gears 58, pins 59, and an internal gear 60. The plurality of planetary gears 58 are disposed around the pinion gear 48. The pins 59 respectively support the planetary gears 58. The internal gear 60 is disposed around the plurality of planetary gears 58. Each of the planetary gears 58 meshes with the pinion gear 48. The planetary gears 58 are rotatably supported on the spindle 26 via the pins 59. The spindle 26 is rotated by the planetary gears 58. The internal gear 60 has internal teeth, which mesh with the planetary gears 58.
The internal gear 60 is fixed to each of the hammer case 23 and the bearing box 24. An O-ring 61 is disposed at a boundary between a rear end of the internal gear 60 and the bearing box 24. Protrusions 62 are provided on the outer surface of the internal gear 60. The protrusions 62 each protrude radially outward from the outer circumferential surface of the internal gear 60. The protrusions 62 are provided at intervals in the circumferential direction. The protrusions 62 are disposed in recesses 63 of the hammer case 23. Relative rotation of the hammer case 23 and the internal gear 60 is suppressed by disposing the protrusions 62 in the recesses 63. The internal gear 60 always cannot rotate with respect to the hammer case 23.
When the rotor shaft 42 rotates in response to the driving of the motor 6, the pinion gear 48 rotates, the planetary gears 58 to revolve around the pinion gear 48. The planetary gears 58 revolve while meshing with the internal teeth of the internal gear 60. Owing to the revolving of the planetary gears 58, the spindle 26, which is connected to the planetary gears 58 via the pins 59, rotates at a rotation speed that is lower than a rotation speed of the rotor shaft 42.
Spindle
The spindle 26 is rotated by rotational force of the motor 6. At least a part of the spindle 26 is disposed forward of the speed reduction mechanism 25. The spindle 26 is disposed rearward of the tool holding shaft 31. The spindle 26 is rotated by the rotor 36. The spindle 6 is rotated by rotational force of the rotor 36 transmitted by the speed reduction mechanism 25. The spindle 26 transmits the rotational force of the motor 6 to the movable anvils 33 via the impact mechanism 28.
The spindle 26 includes a spindle shaft 64, a flange 65, a pin support 66, a coupling portion 67, and a protrusion 68.
The spindle shaft 64 extends in the axial direction. The spindle shaft 64 is disposed so as to surround the rotation axis AX. Spindle projections 69 are provided at a front end of the outer circumferential surface of the spindle shaft 64. The spindle projections 69 each protrude radially outward from the front end of the outer circumferential surface of the spindle shaft 64. Two spindle projections 69 are provided around the rotation axis AX. The two spindle projections 69 are disposed so as to sandwich the rotation axis AX. In the following description, one spindle projection 69 is appropriately referred to as a first spindle projection 691, and the other spindle projection 69 is appropriately referred to as a second spindle projection 692.
A ball groove 70 is formed on the outer circumferential surface of the spindle shaft 64. The ball groove 70 is disposed rearward of the spindle projections 69. The ball groove 70 is formed so as to surround the rotation axis AX. The ball groove 70 is formed so as to be recessed radially inward from the outer circumferential surface of the spindle shaft 64.
The flange 65 is provided at a rear portion of the spindle shaft 64. The flange 65 protrudes radially outward from the rear portion of the spindle shaft 64. Spindle grooves 71 are provided on the front surface of the flange 65. The spindle grooves 71 are provided in the circumferential direction. In the embodiment, three spindle grooves 71 are provided in the circumferential direction.
The pin support 66 is disposed rearward of the flange 65. The pin support 66 has a circular ring shape. A part of the flange 65 and a part of the pin support 66 are coupled via the coupling portion 67. The protrusion 68 protrudes rearward from the pin support 66.
The planetary gears 58 are disposed between the flange 65 and the pin support 66. Front ends of the pins 59 are disposed in support recesses 72 provided in the flange 65. Rear ends of the pins 59 are disposed in support holes 73 provided in the pin support 66. The planetary gears 58 are rotatably supported by the flange 65 and the pin support 66 via the pins 59.
The protrusion 68 is disposed on an inner side of the spindle bearing 27. The protrusion 68 is rotatably supported by the spindle bearing 27. A washer 74 is disposed at a position facing a front end of an inner ring of the spindle bearing 27.
Impact Mechanism
The impact mechanism 28 is driven by the motor 6. The rotational force of the motor 6 is transmitted to the impact mechanism 28 via the speed reduction mechanism 25 and the spindle 26. The impact mechanism 28 impacts (strikes) the movable anvils 33 in the rotation direction owing to the rotational force of the spindle 26, which is rotated by the motor 6.
The impact mechanism 28 includes a hammer 75, a cam ring 76, balls 77, an elastic member 78, a washer 79, and rotation balls 80.
The hammer 75 impacts the movable anvils 33 in the rotation direction. The hammer 75 impact the tool holding shaft 31 in the rotation direction via the movable anvils 33. The hammer 75 is supported by the spindle 26. The hammer 75 is disposed around the spindle shaft 64. The hammer 75 is rotatably supported by the spindle shaft 64. The hammer 75 is disposed forward of the speed reduction mechanism 25.
The hammer 75 does not move in the axial direction with respect to the hammer case 23. In a practical sense, the hammer 75 may slightly move in the axial direction with respect to the hammer case 23 due to, for example, rattle or backlash. The hammer 75 can rotate relative to the spindle 26. The hammer 75 can rotate relative to the spindle shaft 64 in a state of being supported by the spindle shaft 64. The hammer 75 impacts the movable anvils 33 in the rotation direction without being displaced the axial direction with respect to the spindle 26.
The hammer 75 includes a rear outer cylindrical portion 81, a front outer cylindrical portion 82, and an inner cylindrical portion 83. Each of the rear outer cylindrical portion 81, the front outer cylindrical portion 82, and the inner cylindrical portion 83 is disposed so as to surround the rotation axis AX. The rear outer cylindrical portion 81, the front outer cylindrical portion 82, and the inner cylindrical portion 83 are integrated.
The front outer cylindrical portion 82 is disposed forward of the rear outer cylindrical portion 81. A front end of the rear outer cylindrical portion 81 is connected to a rear end of the front outer cylindrical portion 82. The rear outer cylindrical portion 81 has an outer diameter larger than that of the front outer cylindrical portion 82. The rear outer cylindrical portion 81 has an inner diameter larger than that of the front outer cylindrical portion 82.
The inner cylindrical portion 83 is supported by the spindle shaft 64. The inner cylindrical portion 83 is disposed radially inside with respect to the rear outer cylindrical portion 81 and the front outer cylindrical portion 82. A front end of the inner cylindrical portion 83 is connected to the rear end of the front outer cylindrical portion 82. The front outer cylindrical portion 82 is disposed radially outside with respect to the inner cylindrical portion 83 and disposed forward of the inner cylindrical portion 83. The rear outer cylindrical portion 81 is disposed radially outside with respect to the front outer cylindrical portion 82 and is disposed rearward of the front outer cylindrical portion 82.
Hammer projections 84 are provided on the inner circumferential surface of the front outer cylindrical portion 82. The hammer projections 84 each protrude radially inward from the inner circumferential surface of the front outer cylindrical portion 82. Two hammer projections 84 are provided around the rotation axis AX. The two hammer projections 84 are disposed so as to sandwich the rotation axis AX. The two hammer projections 84 are disposed so as to face each other. In the following description, one hammer projection 84 is appropriately referred to as a first hammer projection 841, and the other hammer projection 84 is appropriately referred to as a second hammer projection 842.
The inner cylindrical portion 83 is disposed around the spindle shaft 64. The inner circumferential surface of the inner cylindrical portion 83 faces the outer circumferential surface of the spindle shaft 64. A ball groove 85 is formed on the inner circumferential surface of the inner cylindrical portion 83. The ball groove 85 is formed so as to surround the rotation axis AX. The ball groove 85 is formed so as to be recessed radially outward from the inner circumferential surface of the inner cylindrical portion 83.
Guide grooves 86 are provided on the inner circumferential surface of the rear outer cylindrical portion 81. The guide grooves 86 each extend in the axial direction on the inner circumferential surface of the rear outer cylindrical portion 81. The guide grooves 86 each extend forward from a rear end of the rear outer cylindrical portion 81. The guide grooves 86 are provided at intervals around the rotation axis AX of the hammer 75. In the embodiment, six guide grooves 86 are provided around the rotation axis AX. The six guide grooves 86 are provided at equal intervals in the circumferential direction.
The cam ring 76 is coupled to the flange 65 via the balls 77 so as to be rotatable relative to the flange 65. The cam ring 76 is coupled to the hammer 75 so as to be movable relative to the hammer in the axial direction but so as not to be rotatable relative to the hammer 75. The cam ring 76 is disposed so as to face the front surface of the flange 65. The cam ring 76 is coupled to the rear portion of the hammer 75.
The cam ring 76 is disposed on inner side of the rear outer cylindrical portion 81. The cam ring 76 and the hammer 75 can relatively move in the axial direction. As described above, the hammer 75 does not move in the axial direction with respect to the hammer case 23. In a practical sense, the hammer 75 may slightly move in the axial direction with respect to the hammer case 23 due to, for example, rattle or backlash. The cam ring 76 moves in the axial direction with respect to the hammer case 23 inside the rear outer cylindrical portion 81 of the hammer 75.
Cam slide portions 87 are provided on the outer circumferential surface of the cam ring 76. The cam slide portions 87 each protrude radially outward from the outer circumferential surface of the cam ring 76. The cam slide portions 87 are provided at intervals around the rotation axis AX of the cam ring 76. Six cam slide portions 87 are provided around the rotation axis AX. The six cam slide portions 87 are provided at equal intervals in the circumferential direction. The cam slide portions 87 are disposed in the guide grooves 86. One cam slide portion 87 is disposed in one guide groove 86. The cam slide portions 87 move in the guide grooves 86 in the axial direction. The cam ring 76 can move in the axial direction with respect to the hammer 75 while being guided by the guide grooves 86 via the cam slide portions 87.
The guide grooves 86 of the hammer 75 function as a guide portion that guides the cam ring 76 in the axial direction and that suppresses the relative rotation of the hammer 75 and the cam ring 76.
Cam grooves 88 are provided on the inner circumferential surface of the cam ring 76. The cam grooves 88 are provided in the circumferential direction. In the embodiment, three cam grooves 88 are provided in the circumferential direction.
The cam ring 76 is disposed forward of the flange 65. The cam ring 76 is disposed so as to face the front surface of the flange 65 in a state of being disposed on the inner side of the rear outer cylindrical portion 81 of the hammer 75.
The balls 77 are disposed between the spindle 26 and the cam ring 76. The balls 77 are disposed between the flange 65 and the cam ring 76. The flange 65 of the spindle 26 and the cam ring 76 can relatively rotate via the balls 77.
The ball 77 is made of metal such as iron and steel. The flange 65 has the spindle grooves 71 in which the balls 77 are at least partially disposed. The spindle grooves 71 are provided in a part of the front surface of the flange 65. The spindle grooves 71 each has an arc shape in a plane orthogonal to the rotation axis AX. The cam ring 76 has the cam grooves 88 in which the balls 77 are at least partially disposed. The cam grooves 88 are provided in a part of the inner circumferential surface of the cam ring 76. The cam grooves 88 each has an arc shape in a plane orthogonal to the rotation axis AX. The balls 77 are disposed between the spindle grooves 71 and the cam grooves 88. As described above, three spindle grooves 71 are provided. Three cam grooves 88 are provided. Three balls 77 are provided. One ball 77 is arranged between one spindle groove 71 and one cam groove 88. The balls 77 can roll in the spindle groove 71 and in the cam groove 88. The cam ring 76 can move with the ball 77.
At least a part of the spindle groove 71 is inclined rearward toward one side in the circumferential direction. At least a part of the spindle groove 71 may be inclined rearward toward the other side in the circumferential direction.
At least a part of the cam groove 88 is inclined rearward toward one side in the circumferential direction. At least a part of the cam groove 88 may be inclined rearward toward the other side in the circumferential direction.
In the embodiment, each of the spindle grooves 71 includes a first portion 711 and a second portion 712. The first portion 711 and the second portion 712 are defined at different positions in the circumferential direction. A boundary between the first portion 711 and the second portion 712 is defined at a central portion of the spindle groove 71 in the circumferential direction. The first portion 711 is inclined rearward from the central portion of the spindle groove 71 toward one side in the circumferential direction. The second portion 712 is inclined rearward from the central portion of the spindle groove 71 toward the other side in the circumferential direction. The first portion 711 is defined between the central portion and one end of the spindle groove 71 in the circumferential direction. The second portion 712 is defined between the central portion and the other end of the spindle groove 71 in the circumferential direction.
In the embodiment, each of the cam grooves 88 includes a third portion 881 and a fourth portion 882. The third portion 881 and the fourth portion 882 are defined at different positions in the circumferential direction. A boundary between the third portion 881 and the fourth portion 882 is defined at a central portion of the cam groove 88 in the circumferential direction. The third portion 881 is inclined rearward from the central portion of the cam groove 88 toward one side in the circumferential direction. The fourth portion 882 is inclined rearward from the central portion of the cam groove 88 toward the other side in the circumferential direction. The third portion 881 is defined between the central portion and one end of the cam groove 88 in the circumferential direction. The fourth portion 882 is defined between the central portion and the other end of the cam groove 88 in the circumferential direction.
In the relative rotation of the flange 65 and the cam ring 76, the ball 77 moves through the first portion 711 from the central portion of the spindle groove 71 toward an end of the first portion 711 on one side in the circumferential direction between the first portion 711 of the spindle groove 71 and the third portion 881 of the cam groove 88, so that the cam ring 76 receives force from the ball 77 and moves forward.
In the relative rotation of the flange 65 and the cam ring 76, the ball 77 moves through the first portion 711 from the end of the first portion 711 on the one side in the circumferential direction toward the central portion of the spindle groove 71 between the first portion 711 of the spindle groove 71 and the third portion 881 of the cam groove 88, so that the cam ring 76 receives force from the ball 77 and moves rearward.
In the relative rotation of the flange 65 and the cam ring 76, the ball 77 moves through the second portion 712 from the central portion of the spindle groove 71 toward an end of the second portion 712 on the other side in the circumferential direction between the second portion 712 of the spindle groove 71 and the fourth portion 882 of the cam groove 88, so that the cam ring 76 receives force from the ball 77 and moves forward.
In the relative rotation of the flange 65 and the cam ring 76, the ball 77 moves through the second portion 712 from the end of the second portion 712 on the other side in the circumferential direction toward the central portion of the spindle groove 71 between the second portion 712 of the spindle groove 71 and the fourth portion 882 of the cam groove 88, so that the cam ring 76 receives force from the ball 77 and moves rearward.
The flange 65 of the spindle 26 and the cam ring 76 can relatively move in both the axial direction and the rotation direction within a movable range defined by the spindle groove 71 and the cam groove 88.
The cam ring 76 is coupled to the flange 65 of the spindle 26 via the balls 77. The cam ring 76 can rotate together with the spindle 26 owing to rotational force of the spindle 26 rotated by the motor 6. The cam ring 76 rotates about the rotation axis AX.
The elastic member 78 constantly generates elastic force for moving the cam ring 76 rearward. In the axial direction, the elastic member 78 is disposed between the hammer 75 and the cam ring 76. At least a part of the elastic member 78 is disposed around the spindle shaft 64. In the embodiment, the hammer 75 has a recess 89 recessed forward from the rear surface of the hammer 75. The recess 89 is defined by the inner circumferential surface of the rear outer cylindrical portion 81, the outer circumferential surface of the inner cylindrical portion 83, and a support surface 90 disposed forward of the flange 65 and the cam ring 76. The support surface 90 is disposed so as to connect a front end of the inner circumferential surface of the rear outer cylindrical portion 81 and a front end of the outer circumferential surface of the inner cylindrical portion 83. The support surface 90 has a circular ring shape. At least a part of the elastic member 78 is disposed in the recess 89. In the axial direction, the elastic member 78 is disposed between the front surface of the cam ring 76 and the support surface 90 of the hammer 75 disposed forward of the flange 65 and the cam ring 76.
In the embodiment, a rear portion of the elastic member 78 is disposed around the spindle shaft 64. A front portion of the elastic member 78 is disposed around the inner cylindrical portion 83 in the recess 89. In the embodiment, the elastic member 78 includes a plurality of disc springs 91. The disc springs 91 are disposed in the axial direction. In the embodiment, four disc springs 91 are disposed in the axial direction. The disc springs 91 have a circular ring shape. In the embodiment, some of the disc springs 91 are disposed around the spindle shaft 64, and some of the disc springs 91 are disposed around the inner cylindrical portion 83.
In the embodiment, the elastic member 78 has a spring constant of 100 [N/mm] or more. An upper limit value of the spring constant of the elastic member 78 is not particularly limited. In the embodiment, the elastic member 78 has a spring constant of 10000 [N/mm] or less.
The hammer 75 is disposed around the spindle shaft 64. The cam ring 76 is disposed forward of the flange 65, and coupled to the flange 65 via the balls 77. The cam ring 76 is coupled to a rear portion of the hammer 75 via the cam slide portions 87 and the guide grooves 86. The spindle shaft 64, the hammer 75, and the cam ring 76 define closed space. The closed space is defined by the outer circumferential surface of the spindle shaft 64, the outer circumferential surface of the inner cylindrical portion 83, the support surface 90, the inner circumferential surface of the rear outer cylindrical portion 81, and the front surface of the cam ring 76. The elastic member 78 is disposed in the closed space.
The washer 79 supports a front end of the elastic member 78. The washer 79 is disposed radially outside with respect to the inner cylindrical portion 83. The washer 79 has a circular ring shape. The washer 79 is disposed so as to surround the inner cylindrical portion 83. The washer 79 is disposed in the recess 89. At least a part of the hammer 75 supports the washer 79 in the recess 89. In the embodiment, the washer 79 is disposed in a circular groove 92 provided on the support surface 90.
A rear end of the elastic member 78 is in contact with the front surface of the cam ring 76. The front end of the elastic member 78 is in contact with the washer 79. The front end of the elastic member 78 is connected to the hammer 75 via the washer 79. In the embodiment, the rear end of the elastic member 78 refers to a rear end of a disc spring 91 disposed at a rearmost position among the disc springs 91 disposed in the axial direction. The front end of the elastic member 78 refers to a front end of a disc spring 91 disposed at a foremost position among the disc springs 91 disposed in the axial direction.
The rotation balls 80 are disposed between the spindle shaft 64 and the hammer 75. The rotation balls 80 are disposed between the ball groove 70 and the ball groove 85. The rotation balls 80 are at least partially disposed in the ball groove 70 and are partially disposed in the ball groove 85. The rotation balls 80 are disposed around the rotation axis AX of the spindle 26. As described above, the hammer 75 can rotate relative to the spindle shaft 64. The rotation balls 80 function as a bearing of the hammer 75. The rotation balls 80 enable the hammer 75 and the spindle shaft 64 to relatively rotate smoothly.
Elastic Force Adjusting Mechanism
The elastic force adjusting mechanism 29 adjusts elastic force of the elastic member 78 in an initial state before the motor 6 is started. The elastic force adjusting mechanism 29 adjusts the elastic force of the elastic member 78 by adjusting an amount of compression of the elastic member 78 in the initial state.
The flange 65 supports the rear end of the elastic member 78 via the cam ring 76. The elastic force adjusting mechanism 29 adjusts the amount of compression of the elastic member 78 by moving the position of the front end of the elastic member 78.
The elastic force adjusting mechanism 29 includes screws 93 that are in contact with the washer 79. The screws 93 are connected to the front end of the elastic member 78 via the washer 79. The screws 93 are disposed in screw holes 94 formed in the hammer 75. Each of the screw holes 94 penetrates a front end surface 95 of the rear outer cylindrical portion 81 and the support surface 90. The front end surface 95 has a circular ring shape in a plane orthogonal to the rotation axis AX. The front end surface 95 faces forward. The screw holes 94 are formed at intervals around the rotation axis AX of the hammer 75. One screw 93 is disposed in a corresponding one screw hole 94. In the embodiment, six screw holes 94 are formed at intervals around the rotation axis AX. The six screws 93 are disposed in the six screw holes 94, respectively.
A rear end of each of the screws 93 is in contact with the front surface of the washer 79. The amount of compression of the elastic member 78 is adjusted by rotation of the screws 93. Rotation of the screws 93 in one direction moves the screws 93 rearward with respect to the hammer 75. The rearward movement of the screws 93 moves the front end of the elastic member 78 rearward via the washer 79. Rearward movement of the front end of the elastic member 78 in a state in which the flange 65 supports the rear end of the elastic member 78 via the cam ring 76 compresses the elastic member 78. Rotation of the screws 93 in the other direction moves the screws 93 forward with respect to the hammer 75. Forward movement of the front end of the elastic member 78 in a state in which the flange 65 supports the rear end of the elastic member 78 via the cam ring 76 extends the elastic member 78.
The amount of compression of the elastic member 78 is adjusted in an operation of assembling the impact tool 1. After the spindle 26, the hammer 75, and the cam ring 76 are coupled such that the elastic member 78 is disposed in the closed space defined by the spindle shaft 64, the hammer 75, and the cam ring 76, the screw fastening tool is inserted into the screw hole 94 from the front of the front end surface 95. A tip of the screw fastening tool is inserted into a tool hole of the screw 93 via the screw hole 94. An assembler can adjust the amount of compression of the elastic member 78 by rotating the screw 93 via the screw fastening tool. Furthermore, an angle of inclination of the elastic member 78 with respect to the spindle 26 is adjusted by adjusting the axial position of each of the screws 93.
Hammer Bearing
The hammer bearing 30 supports the hammer 75 in a rotatable manner. The hammer case 23 holds the hammer bearing 30. The hammer bearing 30 is disposed around the hammer 75. In the embodiment, the hammer bearing 30 supports a front end of the hammer 75 in a rotatable manner. In the embodiment, the hammer bearing 30 is disposed around the front outer cylindrical portion 82. At least a part of the rear end of the hammer bearing 30 is in contact with the front end surface 95 of the rear outer cylindrical portion 81. The hammer case 23 has a facing surface 96 facing the front end of the hammer bearing 30. The facing surface 96 faces rearward. The front end of the hammer bearing 30 and the facing surface 96 of the hammer case 23 face each other with a gap or spacing or distance therebetween. The hammer bearing 30 is a ball bearing. An outer ring of the hammer bearing 30 is in contact with the inner circumferential surface of the large cylindrical portion 53 of the hammer case 23. An inner ring of the hammer bearing 30 is in contact with the outer circumferential surface of the front outer cylindrical portion 82 of the hammer 75.
In the embodiment, the hammer bearing 30 is disposed so as to cover a front end of the screw holes 94. In the operation of assembling the impact tool 1, after the screws 93 are rotated with the screw fastening tool to adjust the amount of compression of the elastic member 78, the hammer bearing 30 is disposed around the front outer cylindrical portion 82.
Tool Holding Shaft
The tool holding shaft 31 is an output unit of the impact tool 1 that rotates owing to the rotational force of the rotor 36. At least a part of the tool holding shaft 31 is disposed forward of the spindle 26. The tool holding shaft 31 includes a tool holder 97 and an anvil portion 98 disposed rearward of the tool holder 97. The tool holder 97 has a rod shape extending in the front-rear direction. The anvil portion 98 is connected to a rear portion of the tool holder 97.
The tool holder 97 holds a tool accessory, e.g., a bit. The tool holder 97 has a tool (bit) hole 99 into which a tool accessory is inserted. The tool hole 99 extends rearward from the front end surface of the tool holder 97. The tool accessory is mounted on the tool holding shaft 31.
The anvil portion 98 is disposed rearward of the tool holder 97. The anvil portion 98 is connected to the rear portion of the tool holder 97. The anvil portion 98 is disposed so as to surround the rotation axis AX. The anvil portion 98 has a recess 100 into which a front end of the spindle shaft 64 is inserted. The front end of the spindle shaft 64 including the spindle projections 69 is disposed in the recess 100. The recess 100 is recessed forward from a rear end surface of the anvil portion 98. The recess 100 is defined by an inner circumferential surface 101 of the anvil portion 98 and a facing surface 102 connected to a front end of the inner circumferential surface 101 of the anvil portion 98. The facing surface 102 is a flat surface facing rearward.
The anvil portion 98 has anvil holes 104 each penetrating an outer circumferential surface 103 of the anvil portion 98 and the inner circumferential surface 101 of the anvil portion 98. The anvil holes 104 extend in the radial direction. Two anvil holes 104 are provided around the rotation axis AX. The two anvil holes 104 are disposed so as to sandwich the rotation axis AX.
In the embodiment, a support ball 106 is supported by the front end of the spindle shaft 64. A support recess 105 is provided on the front end surface of the spindle shaft 64. The support recess 105 has an inner surface having a hemispherical shape. The support ball 106 is disposed in the support recess 105. The support ball 106 is in contact with the facing surface 102.
The tool holding shaft 31 is rotatably supported by the shaft bearings 32. The shaft bearings 32 are disposed around the tool holder 97. The shaft bearings 32 are disposed inside the small cylindrical portion 54 of the hammer case 23. The shaft bearing 32 is supported by the small cylindrical portion 54 of the hammer case 23. The shaft bearing 32 supports a front portion of the tool holder 97 in a rotatable manner. In the embodiment, two shaft bearings 32 are disposed in the axial direction. An O-ring 107 is disposed between each of the shaft bearings 32 and a rear holder.
A suppressing member 108 is disposed rearward of the shaft bearing 32. The suppressing member 108 suppresses rearward removal from the shaft bearing 32. The suppressing member 108 is disposed in a groove 109 formed on the inner circumferential surface of the small cylindrical portion 54. Examples of the suppressing member 108 include a snap ring and a C-ring. The suppressing member 108 is disposed so as to be in contact with the rear end surface of the shaft bearing 32. The suppressing member 108 suppresses the shaft bearing 32 from being removed rearward from the small cylindrical portion 54.
Movable Anvil
The movable anvil 33 is movably supported by the tool holding shaft 31. In the embodiment, the movable anvil 33 moves only in the radial direction with respect to the tool holding shaft 31. The movable anvil 33 does not move in the axial direction and the circumferential direction with respect to the tool holding shaft 31.
The movable anvils 33 are movably supported by the anvil portion 98. The movable anvils 33 are disposed in the anvil holes 104. Two movable anvils 33 are disposed in the two anvil holes 104, respectively. Each of the movable anvils 33 is a columnar (pin-shaped) member. Each of the movable anvil 33 is disposed in the anvil hole 104 such that the central axis of the movable anvil 33 is in parallel with the rotation axis AX of the tool holding shaft 31. In the following description, one movable anvil 33 is appropriately referred to as a first movable anvil 331, and the other movable anvil 33 is appropriately referred to as a second movable anvil 332.
The movable anvils 33 can move in the radial direction while being guided by the anvil holes 104. The inner surface of each of the anvil holes 104 functions as a guide surface that guides the movable anvil 33 in the radial direction. The front end of the spindle shaft 64 is disposed in the recess 100 of the anvil portion 98. The spindle projections 69 are disposed at the front end of the spindle shaft 64. When the spindle projections 69 come into contact with the movable anvils 33, the movable anvils 33 move radially outward. When the spindle projections 69 are away from the movable anvils 33, the movable anvils 33 move radially inward.
The movable anvils 33 move so as to change between a first state and a second state. In the first state, at least a part of each of the movable anvils 33 protrudes radially outward from the outer circumferential surface 103 of the anvil portion 98 of the tool holding shaft 31. In the second state, each of the movable anvils 33 is positioned radially inside with respect to the outer circumferential surface 103 of the anvil portion 98 of the tool holding shaft 31. In the rotation of the spindle 26, the spindle projections 69 come into contact with the movable anvils 33, whereby the movable anvils 33 change from the second state to the first state. That is, when the spindle projections 69 come into contact with the movable anvils 33, at least a part of the movable anvil 33 is positioned radially outside with respect to the outer circumferential surface 103 of the anvil portion 98.
When the movable anvils 33 are in the first state, the hammer projections 84 of the hammer 75 can come into contact with the movable anvils 33. The hammer 75 impacts (strikes) the movable anvils 33 when the movable anvils 33 are in the first state. When the movable anvils 33 are in the second state, the hammer projections 84 of the hammer 75 cannot come into contact with the movable anvils 33. The hammer 75 rotates around the spindle shaft 64 when the movable anvils 33 are in the second state.
Tool Holding Mechanism
The tool holding mechanism 34 is disposed forward of the hammer case 23 and disposed around the tool holder 97. The tool holding mechanism 34 holds a tool accessory inserted into the tool hole 99 of the tool holder 97. The tool accessory is detachable from the tool holding mechanism 34.
The tool holding mechanism 34 includes holding balls 110, a leaf spring 111, a sleeve 112, a coil spring 113, and a positioning member 114.
The tool holder 97 has support recesses 115 that support the holding balls 110. The support recesses 115 are formed on the outer surface of the tool holder 97. In the embodiment, two support recesses 115 are formed in the tool holder 97.
The holding balls 110 are movably supported by the tool holder 97. The holding balls 110 are disposed in the support recesses 115. One holding ball 110 is disposed in one support recess 115.
Through holes connecting the inner surface of each of the support recesses 115 and the inner surface of the tool hole 99 are formed in the tool holder 97. Each of the holding balls 110 has a diameter smaller than that of the innermost portion of the through hole in the radial direction. The tool accessary is disposed in the tool hole 99 via at least a part of each of the holding balls 110 in a state in which the holding balls 110 are supported by the support recesses 115. The holding balls 110 can fix the tool accessory inserted into the tool hole 99. The holding balls 110 can move to an engagement position for fixing the tool accessory and a release position for releasing the fixing of the tool accessory.
The leaf spring 111 generates elastic force that moves the holding balls 110 to the engagement position. The leaf spring 111 is disposed around the tool holder 97. The leaf spring 111 generates elastic force that moves the holding balls 110 forward.
The sleeve 112 is a cylindrical member. The sleeve 112 is disposed around the tool holder 97. The sleeve 112 can move around the tool holder 97 in the axial direction. The sleeve 112 can block the holding balls 110 disposed at the engagement position from escaping from the engagement position. The sleeve 112 is moved in the axial direction, whereby the sleeve 112 can change the holding balls 110 into a state in which the holding balls 110 can be moved from the engagement position to the release position.
The sleeve 112 can move along the tool holder 97 from a block position, at which the holding balls 110 are blocked from moving outward in the radial direction, to a permission position, at which the holding balls 110 are permitted to move outward in the radial direction.
Disposing the sleeve 112 at the block position suppresses the holding balls 110 disposed at the engagement position from moving outward in the radial direction. That is, disposing the sleeve 112 at the block position blocks the holding balls 110 disposed at the engagement position from escaping from the engagement position. Disposing the sleeve 112 at the block position maintains a state in which the tool accessory is fixed by the holding balls 110.
Moving the sleeve 112 to the permission position permits the holding ball 110 disposed at the engagement position to move outward in the radial direction. The sleeve 112 is moved to the permission position, whereby the sleeve 112 changes the holding balls 110 into a state in which the holding balls 110 can be moved from the engagement position to the release position. That is, disposing the sleeve 112 at the permission position permits the holding balls 110 disposed at the engagement position to escape from the engagement position. Disposing the sleeve 112 at the permission position can release the state in which the tool accessory is fixed by the holding balls 110.
The coil spring 113 generates elastic force so that the sleeve 112 moves to the block position. The coil spring 113 is disposed around the tool holder 97. The block position is defined rearward of the permission position. The coil spring 113 generates elastic force that moves the sleeve 112 rearward.
The positioning member 114 is a ring-shaped member fixed to the outer surface of the tool holder 97. The positioning member 114 is fixed at a position where the positioning member 114 can face a rear end of the sleeve 112. The positioning member 114 positions the sleeve 112 at the block position. The sleeve 112 is positioned at the block position by coming into contact with the positioning member 114. The sleeve 112 receives elastic force that moves the sleeve 112 rearward from the coil spring 113.
Operation of Impact Tool
Next, operation of the impact tool 1 will be described. Each of
In the embodiment, the spindle projections 69 include the first spindle projection 691 and the second spindle projection 692 as described above. The hammer projections 84 include the first hammer projection 841 and the second hammer projection 842 as described above. The movable anvils 33 include the first movable anvil 331 and the second movable anvil 332 as described above.
When screw fastening operation is performed on an operation target, a tool accessory (driver bit) used for the screw fastening operation is inserted into the tool hole 99 of the tool holding shaft 31. The tool accessory inserted into the tool hole 99 is held by the tool holding mechanism 34. After the tool accessory is mounted on the tool holding shaft 31, an operator grips the grip 18 with, for example, the right hand, and performs pulling operation on the trigger lever 9 with the index finger of the right hand. When the pulling operation is performed on the trigger lever 9, power is supplied from the battery pack 20 to the motor 6. The motor 6 is started (activated), and the light is turned on. The rotor shaft 42 of the rotor 36 rotates in response to start of the motor 6. When the rotor shaft 42 rotates, rotational force of the rotor shaft 42 is transmitted to the planetary gears 58 via the pinion gear 48. The planetary gears 58 revolve around the pinion gear 48 while rotating in a state of meshing with the internal teeth of the internal gear 60. The planetary gears 58 are rotatably supported by the spindle 26 via the pins 59. Owing to the revolving of the planetary gears 58, the spindle 26 rotates at a rotational speed that is lower than that of the rotor shaft 42.
In the screw fastening operation, the tool holding shaft 31 rotates in the forward rotation direction. In the screw fastening operation, a load in the reverse rotation direction is applied to the tool holding shaft 31.
As illustrated in
In the low load state, the movable anvils 33 move outward in the radial direction owing to the contact with the spindle projections 69. At least a part of each of the movable anvils 33 is positioned radially outside with respect to the outer circumferential surface of the anvil portion 98. Since at least a part of each of the movable anvils 33 is positioned radially outside with respect to the outer circumferential surface of the anvil portion 98, each of the hammer projections 84 is in contact with at least a part of the corresponding movable anvil 33 in the low load state.
In the low load state, the movable anvil 33 cannot pass between the spindle projection 69 and the hammer projection 84 due to a wedge effect of the movable anvil 33, and the relative rotation of the spindle 26, the hammer 75, and the tool holding shaft 31 is blocked. The tool holding shaft 31 rotates together with the hammer 75 and the spindle 26 via the movable anvils 33.
The cam ring 76 is coupled to the hammer 75 via the guide grooves 86 and the cam slide portions 87. The cam ring 76 is pressed against the flange 65 of the spindle 26 by elastic force of the elastic member 78. Therefore, in the low load state in which the hammer 75 and the spindle 26 do not relatively rotate, the cam ring 76 rotates together with the spindle 26 and the hammer 75. That is, in the low load state, the spindle 26, the hammer 75, the tool holding shaft 31, and the cam ring 76 rotate together.
As illustrated in
When the load applied to the tool holding shaft 31 increases due to the progress of the screw fastening operation, the rotational speed of the tool holding shaft 31 decreases. Since the hammer 75 is coupled to the tool holding shaft 31 via the movable anvil 33, the rotational speed of the hammer 75 also decreases as the rotational speed of the tool holding shaft 31 decreases. Since the cam ring 76 is coupled to the hammer 75 via the guide grooves 86 and the cam slide portions 87, the rotational speed of the cam ring 76 also decreases as the rotational speed of the hammer 75 decreases. In contrast, since the spindle 26 is rotated by the rotational force of the motor 6, the rotational speed of the spindle 26 does not decrease.
Although the rotational speed of the spindle 26 does not decrease, the rotational speeds of the tool holding shaft 31, the hammer 75, and the cam ring 76 decrease, so that the relative rotation of the tool holding shaft 31, the hammer 75, the cam ring 76 and the spindle 26 is started. The tool holding shaft 31, the hammer 75, and the cam ring 76 rotate together.
As illustrated in
Since the cam ring 76 is coupled to the hammer 75 via the guide grooves 86 and the cam slide portions 87, the rotational speed of the cam ring 76 also decreases as the rotational speed of the hammer 75 decreases. The rotational speed of the spindle 26 does not decrease. When the rotation of the spindle 26 is continued in a state in which the rotational speed of the cam ring 76 decreases, the balls 77 thus move in the spindle grooves 71 and the cam grooves 88.
As illustrated in
As described above, when the tool holding shaft 31 transitions from the low load state to the high load state; the flange 65 and the cam ring 76 start relative rotation due to a decrease in rotational speed of the cam ring 76 in a state in which the flange 65 of the spindle 26 and the cam ring 76 rotate together in the forward rotation direction, and each of the balls 77 moves through the second portion 712 from the central portion of the spindle groove 71 toward an end of the second portion 712 on the other side in the circumferential direction, so that the cam ring 76 receives force from the balls 77 and moves forward.
Owing to continuation of the high load state, rotation of each of the tool holding shaft 31, the hammer 75, and the cam ring 76 is stopped. Even when the rotation of each of the tool holding shaft 31, the hammer 75, and the cam ring 76 is stopped, the spindle 26 continues to rotate by the rotational force of the motor 6.
When the tool holding shaft 31 is in the high load state, the rotation of the spindle 26 is continued in a state in which the rotation of each of the tool holding shaft 31, the hammer 75, and the cam ring 76 is stopped. The cam ring 76 receives force from the balls 77, and moves forward against the elastic force of the elastic member 78.
As illustrated in
The lock on the hammer 75 is released, whereby the cam ring 76 also comes into a state in which the cam ring 76 can rotate with respect to the spindle 26. The cam ring 76 is moved rearward with respect to the hammer 75 by the elastic force of the elastic member 78. The cam ring 76 moves rearward while being guided by the guide grooves 86. The cam ring 76 can rotate with respect to the spindle 26. Thus, the cam ring 76 moves rearward, so that the cam ring 76 receives force from the balls 77, and rotates in the forward rotation direction. That is, the cam ring 76 rotates in the forward rotation direction while moving rearward. Each of the balls 77 moves through the second portion 712 from the end toward the central portion of the spindle groove 71. The hammer 75 is coupled to the cam ring 76 via the cam slide portions 87 and the guide grooves 86. Thus, the cam ring 76 rotates in the forward rotation direction, whereby the hammer 75 also rotates in the forward rotation direction.
As described above, when the cam ring 76 receives elastic force from the elastic member 78 so as to move rearward after the lock on the hammer 75 is released, each of the balls 77 moves through the second portion 712 from the end of the second portion 712 on the other side in the circumferential direction toward the central portion of the spindle groove 71, so that the cam ring 76 receives force from the balls 77, and moves rearward while rotating relative to the flange 65.
As illustrated in
The first hammer projection 841 pivots around the spindle 26 in the forward rotation direction as if to follow the first spindle projection 691. The first spindle projection 691 reaches the second movable anvil 332 earlier than the first hammer projection 841. The second hammer projection 842 pivots around the spindle 26 in the forward rotation direction as if to follow the second spindle projection 692. The second spindle projection 692 reaches the first movable anvil 331 earlier than the second hammer projection 842.
As described above, the first spindle projection 691 reaches the second movable anvil 332 earlier than the first hammer projection 841. The first spindle projection 691 comes into contact with the second movable anvil 332. The second movable anvil 332 moves radially outward owing to the contact with the first spindle projection 691. At least a part of the second movable anvil 332 is positioned radially outside with respect to the outer circumferential surface 103 of the anvil portion 98.
The first hammer projection 841 reaches the second movable anvil 332 after the first spindle projection 691 reaches the second movable anvil 332. That is, the first hammer projection 841 reaches the second movable anvil 332 after the second movable anvil 332 moves radially outward. The first hammer projection 841 impacts, in the rotation direction, the second movable anvil 332 disposed radially outside with respect to the outer circumferential surface 103 of the anvil portion 98. When the first hammer projection 841 impacts the second movable anvil 332, the position of the second movable anvil 332 in the radial direction is restricted by the first spindle projection 691, and the position of the second movable anvil 332 in the circumferential direction is restricted by the inner surface of the anvil hole 104. This enables the first hammer projection 841 to impact the second movable anvil 332.
The second spindle projection 692 reaches the first movable anvil 331 earlier than the second hammer projection 842. The first movable anvil 331 moves radially outward owing to the contact with the second spindle projection 692. The second hammer projection 842 reaches the first movable anvil 331 after the first movable anvil 331 moves radially outward. The second hammer projection 842 impacts, in the rotation direction, the first movable anvil 331 disposed radially outside with respect to the outer circumferential surface 103 of the anvil portion 98. When the second hammer projection 842 impacts the first movable anvil 331, the position of the first movable anvil 331 in the radial direction is restricted by the second spindle projection 692, and the position of the first movable anvil 331 in the circumferential direction is restricted by the inner surface of the anvil hole 104. This enables the second hammer projection 842 to impact the first movable anvil 331.
The first hammer projection 841 impacts the second movable anvil 332 substantially at the same time as the second hammer projection 842 impacts the first movable anvil 331. The hammer projection 84 impacts the movable anvil 33 in a state of the movable anvil 33 being disposed in the anvil hole 104 of the tool holding shaft 31. The hammer 75 impacts the tool holding shaft 31 in the rotation direction via the two movable anvils 33 (331, 332).
Since the tool holding shaft 31 is impacted (struck) in the rotation direction by the hammer 75, the tool holding shaft 31 rotates about the rotation axis AX with high torque. Therefore, a screw is fastened to an operation target with high torque.
As illustrated in
After the impact state ends, the output assembly 4 transitions from the impact state to the low load state.
As described with reference to
In the embodiment, two movable anvils 33 are provided, and two hammer projections 84 are provided. Three movable anvils 33 may be provided, and three hammer projections 84 may be provided. Four movable anvils 33 may be provided, and four hammer projections 84 may be provided. Any plural number of five or more movable anvils 33 and hammer projections 84 may be provided.
Effects
As described above, in the present embodiment, the impact tool 1 may include: the motor 6; the spindle 26 that includes the spindle shaft 64 and the flange 65 provided at the rear portion of the spindle shaft 64 and that is rotated by the rotational force of the motor 6; the tool holding shaft 31 at least a part of which is disposed forward of the spindle 26; the hammer 75 that is supported by the spindle shaft 64 and impacts the tool holding shaft 31 in the rotational direction; and the elastic member 78 disposed between the front surface of the flange 65 and the support surface 90 of the hammer 75 disposed forward of the flange 65 in the axial direction. The elastic member 78 may include the disk spring 91.
According to the above configuration, since the elastic member 78 includes the disk spring 91, a predetermined elastic force can be obtained in a state where the dimension in the axial direction is suppressed as compared with a case where the elastic member includes, for example, a coil spring. That is, when a predetermined elastic force is required for the elastic member 78, the dimension of the elastic member 78 in the axial direction can be shortened in the case of using the disk spring 91 as compared with the case of using the coil spring. As a result, the hammer 75 can impact the tool holding shaft 31 in the rotation direction in a state in which the increase in size of the impact tool 1 is suppressed. In particular, the axial length of the impact tool 1 is shortened. When the impact tool 1 includes the motor housing 17, the rear cover 3 disposed at the rear end portion of the motor housing 17, and the output assembly 4 disposed at the front portion of the motor housing 17; the axial length of the impact tool 1 refers to the distance in the axial direction between the rear end portion of the rear cover 3 and the front end portion of the output assembly 4.
In the present embodiment, the plurality of disk springs 91 may be disposed in the axial direction.
According to the above configuration, the elastic member 78 can generate a high elastic force.
In the present embodiment, some disk springs 91 may be disposed around the spindle shaft 64.
According to the above configuration, an increase in size of the impact tool 1 is suppressed.
In the present embodiment, the hammer 75 may include: the inner cylindrical portion 83 disposed around the spindle shaft 64; the front outer cylindrical portion 82 disposed radially outside with respect to the inner cylindrical portion 83 and disposed forward of the inner cylindrical portion 83; and the rear outer cylindrical portion 81 disposed radially outside with respect to the inner cylindrical portion 83 and disposed rearward of the front outer cylindrical portion 82. Some disk springs 91 may be disposed around the inner cylindrical portion 83.
According to the above configuration, an increase in size of the impact tool 1 is suppressed.
In the present embodiment, the hammer 75 may have the recess 89 recessed forward from the rear surface of the hammer 75. The recess 89 may be defined by the inner circumferential surface of the rear outer cylindrical portion 81, the outer circumferential surface of the inner cylindrical portion 83, and the support surface 90. At least a part of the elastic member 78 may be disposed in the recess 89.
According to the above configuration, an increase in size of the impact tool 1 is suppressed.
In the present embodiment, the impact tool 1 may include the washer 79 disposed in the recess 89 to support the front end of the elastic member 78. The front end of the elastic member 78 may be connected to the hammer 75 via the washer 79.
According to the above configuration, the front end portion of the elastic member 78 is stably connected to the hammer 75 via the washer 79.
In the present embodiment, the spring constant of the elastic member 78 may be 100 [N/mm] or more.
According to the above configuration, the elastic member 78 can generate a high elastic force.
In the present embodiment, the spring constant of the elastic member 78 may be 10,000 [N/mm] or less.
According to the above configuration, an increase in size of the elastic member 78 is suppressed.
In the present embodiment, the impact tool 1 may include the movable anvil 33 movably supported by the tool holding shaft 31. The hammer 75 may impact the movable anvil 33 in the rotation direction without being displaced in the axial direction.
According to the above configuration, since the movable anvil 33 movably supported by the tool holding shaft 31 is provided, the hammer 75 can impact the movable anvil 33 in the rotation direction without being displaced in the axial direction. Since the hammer 75 is not displaced in the axial direction, the occurrence of vibration in the axial direction is suppressed in the impact tool 1.
In the present embodiment, the movable anvil 33 may move so as to change between the first state in which at least a part of the movable anvil 33 protrudes radially outward from the outer circumferential surface of the tool holding shaft 31 and the second state in which the movable anvil 33 is positioned radially inside with respect to the outer circumferential surface of the tool holding shaft 31. The hammer 75 may impact the movable anvil 33 in the first state and rotate around the spindle shaft 64 in the second state.
According to the above configuration, the hammer 75 can impact the movable anvil 33 in the rotation direction without being displaced in the axial direction.
In the present embodiment, the impact tool 1 may include a cam ring 76 that is coupled to the flange 65 via the ball 77 so as to be rotatable relative to the flange 65 and is coupled to the hammer 75 so as to be movable relative to the hammer 75 in the axial direction but not to be rotatable relative to the hammer 75. The cam ring 76 may be disposed so as to face the front surface of the flange 65. The elastic member 78 may be disposed between the front surface of the cam ring 76 and the support surface of the hammer 75 in the axial direction.
According to the above configuration, the cam ring 76 is coupled to the flange 65 of the spindle 26 via the ball 77 so as to be rotatable to the flange 65. Furthermore, the cam ring 76 is coupled to the hammer 75 so as to be movable relative to the hammer 75 in the axial direction but not to be rotatable relative to the hammer 75. As a result, the hammer 75 can impact the tool holding shaft 31 in the rotation direction in a state in which the axial length is shortened.
In the present embodiment, the cam ring 76 may be coupled to the rear portion of the hammer 75. The elastic member 78 may be disposed in a closed space defined by the spindle shaft 64, the hammer 75, and the cam ring 76.
According to the above configuration, when the hammer 75 impacts the tool holding shaft 31 in the rotation direction via the movable anvil 33, the cam ring 76 and the elastic member 78 also rotate together with the hammer 75. That is, when the hammer 75 impacts the tool holding shaft 31, not only the inertia moment of the hammer 75 but also the inertia moment of the cam ring 76 and the inertia moment of the elastic member 78 are applied to the tool holding shaft 31. As a result, the tool holding shaft 31 is impacted with a high impacting force.
In the present embodiment, the ball 77 may be disposed between the spindle groove 71 provided in the flange 65 and the cam groove 88 provided in the cam ring 76.
According to the above configuration, the ball 77 can move so as to roll between the spindle groove 71 and the cam groove 88.
In the present embodiment, each of the spindle groove 71 and the cam groove 88 may have an arc shape. At least a part of the spindle groove 71 may be inclined rearward toward one side in the circumferential direction. At least a part of the cam groove 88 may be inclined rearward toward the one side in the circumferential direction.
According to the above configuration, when the flange 65 and the cam ring 76 rotate relative to each other, the cam ring 76 can move in the front-rear direction.
In the present embodiment, the elastic member 78 may generate an elastic force that moves the cam ring 76 rearward.
According to the above configuration, the cam ring 76 can move rearward by the elastic force of the elastic member 78.
In the present embodiment, in the relative rotation between the flange 65 and the cam ring 76, the ball 77 may move toward the end portion on one side in the circumferential direction of the spindle groove 71, so that the cam ring 76 may move forward. The cam ring 76 may rotate while moving rearward by the elastic force of the elastic member 78. The hammer 75 may rotate by the rotation of the cam ring 76 to impact the movable anvil 33 in the rotation direction.
According to the above configuration, the cam ring 76 moves rearward by the elastic force of the elastic member 78, and thus, the hammer 75 can be rotated and can impact the movable anvil 33 in the rotation direction.
In the present embodiment, the impact tool 1 may include: the motor 6; the spindle 26 that includes the spindle shaft 64 and the flange 65 provided at the rear portion of the spindle shaft 64 and that is rotated by the rotational force of the motor 6; the tool holding shaft 31 at least a part of which is disposed forward of the spindle 26; the hammer 75 that is supported by the spindle shaft 64 and impacts the tool holding shaft 31 in the rotational direction; the elastic member 78 disposed between the front surface of the flange 65 and the support surface 90 of the hammer 75 disposed forward of the flange 65 in the axial direction; and the elastic force adjusting mechanism 29 configured to adjust the elastic force of the elastic member 78 in the initial state before the motor 6 is started.
According to the above configuration, since the elastic force of the elastic member 78 can be adjusted, the impact tool 1 can smoothly perform each of the high load operation and the low load operation. When the low load operation is performed, the elastic force of the elastic member 78 is adjusted so that the elastic force of the elastic member 78 becomes low; and when the high load operation is performed, the elastic force of the elastic member 78 is adjusted so that the elastic force of the elastic member 78 becomes high, whereby the impact tool 1 can smoothly perform both the high load operation and the low load operation.
In the present embodiment, the elastic force adjusting mechanism 29 may adjust the amount of compression of the elastic member 78 in the initial state.
According to the above configuration, the elastic force of the elastic member 78 is adjusted by adjusting the amount of compression of the elastic member 78 in the initial state. When the amount of compression is small, the elastic force of the elastic member 78 decreases, and when the amount of compression is large, the elastic force of the elastic member 78 increases.
In the present embodiment, the rear end portion of the elastic member 78 may be supported by the flange 65. The elastic force adjusting mechanism 29 may adjust the amount of compression by moving the position of the front end portion of the elastic member 78.
According to the above configuration, the position of the front end portion of the elastic member 78 is moved in a state in which the position of the rear end portion of the elastic member 78 is fixed, whereby the amount of compression is adjusted.
In the present embodiment, the elastic force adjusting mechanism 29 may include the screw 93 disposed in the screw hole 94 formed in the hammer 75 and connected to the front end portion of the elastic member 78. The amount of compression may be adjusted by rotation of the screw 93.
According to the above configuration, the screw 93 is rotated in a state in which the screw is disposed in the screw hole 94, so that the screw 93 moves in the front-rear direction. As a result, and the amount of compression is adjusted.
In the present embodiment, the impact tool 1 may include the washer 79 that supports the front end of the elastic member 78. The rear end of the screw 93 may contact the front surface of the washer 79. The screw 93 may be connected to the elastic member 78 via the washer 79.
According to the above configuration, the movement of the front end portion of the elastic member 78 is smoothly performed.
In the present embodiment, the plurality of screw holes 94 may be formed at intervals around the rotation axis of the hammer 75. The plurality of screws 93 may be disposed one by one in the plurality of screw holes 94.
According to the above configuration, by adjusting the position of each of the plurality of screws 93 in the front-rear direction, the amount of compression of the elastic member 78 is adjusted, and the inclination angle of the elastic member 78 with respect to the spindle 26 is adjusted.
In the present embodiment, the hammer 75 may include: the inner cylindrical portion 83 disposed around the spindle shaft 64; the front outer cylindrical portion 82 disposed radially outside with respect to the inner cylindrical portion 83 and disposed forward of the inner cylindrical portion 83; and the rear outer cylindrical portion 81 disposed radially outside with respect to the front outer cylindrical portion 82 and disposed rearward of the front outer cylindrical portion 82. The screw hole 94 may be penetrate the front end surface 95 of the rear outer cylindrical portion 81 and the support surface 90.
According to the above configuration, the assembler or the operator of the impact tool 1 can smoothly bring the screw fastening tool into contact with the screw 93 disposed in the screw hole 94, and can smoothly rotate the screw 93.
In the present embodiment, the impact tool 1 may include: the hammer case 23 that houses the hammer 75; and the hammer bearing 30 that is held by the hammer case 23 and supports the hammer 75 in a rotatable manner. The hammer bearing 30 may be disposed around the front outer cylindrical portion 82.
According to the above configuration, after the adjustment of the elastic force by the screw 93 is completed, the hammer bearing 30 is disposed so as to cover the front end portion of the screw hole 94. Thus, the screw 93 is protected by the hammer bearing 30.
In the present embodiment, the elastic member 78 may include the disk spring 91.
According to the above configuration, an increase in size of the impact tool 1 is suppressed. When a predetermined elastic force is required for the elastic member 78, the dimension of the elastic member 78 in the axial direction can be made shorter in the case of using the disk spring 91 than in the case of using, for example, a coil spring. As a result, the hammer 75 can impact the tool holding shaft 31 in the rotation direction in a state in which the increase in size of the impact tool 1 is suppressed. In particular, the axial length of the impact tool 1 is shortened. When the impact tool 1 includes the motor housing 17, the rear cover 3 disposed at the rear end portion of the motor housing 17, and the output assembly 4 disposed at the front portion of the motor housing 17, the axial length of the impact tool 1 refers to the distance in the axial direction between the rear end portion of the rear cover 3 and the front end portion of the output assembly 4.
In the present embodiment, the impact tool 1 may include the washer 79 that supports the front end portion of the elastic member 78. The front end portion of the elastic member 78 may be connected to the hammer 75 via the washer 79.
According to the above configuration, the front end portion of the elastic member 78 is stably connected to the hammer 75 via the washer 79.
In the present embodiment, the impact tool 1 may include the movable anvil 33 movably supported by the tool holding shaft 31. The hammer 75 may impact the movable anvil 33 in the rotation direction without being displaced in the axial direction.
According to the above configuration, since the movable anvil 33 movably supported by the tool holding shaft 31 is provided, the hammer 75 can impact the movable anvil 33 in the rotation direction without being displaced in the axial direction. Since the hammer 75 is not displaced in the axial direction, the occurrence of vibration in the axial direction is suppressed in the impact tool 1.
In the present embodiment, the movable anvil 33 may move so as to change between the first state in which at least a part of the movable anvil 33 protrudes radially outward from the outer circumferential surface of the tool holding shaft 31 and the second state in which the movable anvil 33 is positioned radially inside with respect to the outer circumferential surface of the tool holding shaft 31. The hammer 75 may impact the movable anvil 33 in the first state and rotate around the spindle shaft 64 in the second state.
According to the above configuration, the hammer 75 can impact the movable anvil 33 in the rotation direction without being displaced in the axial direction.
In the present embodiment, the impact tool 1 may include a cam ring 76 that is coupled to the flange 65 via the ball 77 so as to be rotatable relative to the flange 65 and is coupled to the hammer 75 so as to be movable relative to the hammer 75 in the axial direction but not to be rotatable relative to the hammer 75. The cam ring 76 may be disposed so as to face the front surface of the flange 65. The elastic member 78 may be disposed between the front surface of the cam ring 76 and the support surface of the hammer 75 in the axial direction.
According to the above configuration, the cam ring 76 is coupled to the flange 65 of the spindle 26 via the ball 77 relative to the flange 65. Furthermore, the cam ring 76 is coupled to the hammer 75 so as to be movable relative to the hammer 75 in the axial direction but not to be rotatable relative to the hammer 75. As a result, the hammer 75 can impact the tool holding shaft 31 in the rotation direction in a state where the axial length is shortened.
In the present embodiment, the cam ring 76 may be connected to the rear portion of the hammer 75. The elastic member 78 may be disposed in a closed space defined by the spindle shaft 64, the hammer 75, and the cam ring 76.
According to the above configuration, when the hammer 75 impacts the tool holding shaft 31 in the rotation direction via the movable anvil 33, the cam ring 76 and the elastic member 78 also rotate together with the hammer 75. That is, when the hammer 75 strikes the tool holding shaft 31, not only the inertia moment of the hammer 75 but also the inertia moment of the cam ring 76 and the inertia moment of the elastic member 78 are applied to the tool holding shaft 31. As a result, the tool holding shaft 31 is impacted with a high impacting force.
A second embodiment will be described. In the following description, the same or equivalent components as those of the above-described embodiment are denoted by the same reference signs, and the description of the components is simplified or omitted.
Output Assembly
The output assembly 4B includes a hammer case 123 and a bearing box 24. A hammer 175 is disposed in internal space of the output assembly 4B defined by the hammer case 123 and the bearing box 24.
The hammer case 123 includes a large cylindrical portion 153 and a small cylindrical portion 154. Each of the large cylindrical portion 153 and the small cylindrical portion 154 is disposed so as to surround a rotation axis AX. The small cylindrical portion 154 is disposed forward of the large cylindrical portion 153. The large cylindrical portion 153 has an inner diameter larger than that of the small cylindrical portion 154. The large cylindrical portion 153 has an outer diameter larger than that of the small cylindrical portion 154.
In the embodiment, the hammer case 123 has through holes 116. The hammer case 123 has a front surface 155 facing forward and a rear surface 196 facing rearward. The front surface 155 is provided so as to connect a front end of the outer circumferential surface of the large cylindrical portion 153 and a rear end of the outer circumferential surface of the small cylindrical portion 154. The rear surface 196 is provided so as to connect a front end of the inner circumferential surface of the large cylindrical portion 153 and a rear end of the inner circumferential surface of the small cylindrical portion 154. Each of the front surface 155 and the rear surface 196 has a circular ring shape. Each of the through holes 116 penetrates the front surface 155 and the rear surface 196. The through holes 116 are provided at intervals in the circumferential direction. In the embodiment, six through holes 116 are provided at intervals in the circumferential direction.
Similarly to the above-described embodiment, the output assembly 4B includes screws 93 serving as an elastic force adjusting mechanism 29. The hammer 175 has screw holes 94 in which the screws 93 are disposed. In the radial direction, the distance between the rotation axis AX and the screw hole 94 is substantially equal to the distance between the rotation axis AX and the through hole 116. In the circumferential direction, an interval between the screw holes 94 is equal to an interval between the through holes 116. The positions of the screw holes 94 are made to coincide with the positions of the through holes 116 in the radial direction and the circumferential direction by adjusting the position of the hammer 175 in the rotation direction. That is, the through holes 116 can overlap the screw holes 94 in both the radial direction and the circumferential direction. Adjusting the position of the hammer 175 in the rotation direction enables the screws 93 to face the through holes 116. An operator can insert a screw fastening tool into the through hole 116 to rotate the screw 93. Rotation of the screw 93 moves a washer 79 in a front-rear direction. Movement of the washer 79 in the front-rear direction adjusts an amount of compression of the elastic member 78, and adjusts elastic force of the elastic member 78.
The hammer 175 includes a rear outer cylindrical portion 181, a front outer cylindrical portion 182, and an inner cylindrical portion 183. Each of the rear outer cylindrical portion 181, the front outer cylindrical portion 182, and the inner cylindrical portion 183 is disposed so as to surround the rotation axis AX. The rear outer cylindrical portion 181, the front outer cylindrical portion 182, and the inner cylindrical portion 183 are integrated.
The front outer cylindrical portion 182 is disposed forward of the rear outer cylindrical portion 181. A front end of the rear outer cylindrical portion 181 is connected to a rear end of the front outer cylindrical portion 182.
The rear outer cylindrical portion 181 has an outer diameter larger than that of the front outer cylindrical portion 182. The rear outer cylindrical portion 181 has an inner diameter larger than that of the front outer cylindrical portion 182.
The inner cylindrical portion 183 is disposed radially inside with respect to the rear outer cylindrical portion 181 and the front outer cylindrical portion 182. A front end of the inner cylindrical portion 183 is connected to the rear end of the front outer cylindrical portion 182.
The spindle 26 supports the inner cylindrical portion 183. The front outer cylindrical portion 182 is disposed radially outside with respect to the inner cylindrical portion 183 and forward of the inner cylindrical portion 183. The rear outer cylindrical portion 181 is disposed radially outside with respect to the inner cylindrical portion 183 and the front outer cylindrical portion 182, and is disposed rearward of the front outer cylindrical portion 182.
In the embodiment, the rear outer cylindrical portion 181 includes a front small-diameter portion 181A, a large-diameter portion 181B, and a rear small-diameter portion 181C. The large-diameter portion 181B is disposed rearward of the front small-diameter portion 181A. The rear small-diameter portion 181C is disposed rearward of the large-diameter portion 181B. The large-diameter portion 181B has an outer diameter larger than that of the front small-diameter portion 181A and that of the rear small-diameter portion 181C.
In the embodiment, the hammer 175 is rotatably supported by a first hammer bearing 130A and a second hammer bearing 130B. Each of the first hammer bearing 130A and the second hammer bearing 130B is disposed around the rear outer cylindrical portion 181. The second hammer bearing 130B is disposed rearward of the first hammer bearing 130A. Each of the first hammer bearing 130A and the second hammer bearing 130B is a ball bearing.
The first hammer bearing 130A supports a front portion of the hammer 175. The second hammer bearing 130B supports a rear portion of the hammer 175. In the embodiment, each of the first hammer bearing 130A and the second hammer bearing 130B supports the rear outer cylindrical portion 181. The first hammer bearing 130A supports a front portion of the rear outer cylindrical portion 181. The second hammer bearing 130B supports a rear portion of the rear outer cylindrical portion 181.
The first hammer bearing 130A is disposed around the front small-diameter portion 181A. The inner ring of the first hammer bearing 130A is in contact with the outer circumferential surface of the front small-diameter portion 181A. The outer ring of the first hammer bearing 130A is in contact with the inner circumferential surface of the large cylindrical portion 153. The hammer 175 has a support surface 197 facing a front end of the first hammer bearing 130A. The support surface 197 faces rearward. The front end of the first hammer bearing 130A is in contact with the support surface 197 of the hammer 175. The support surface 197 is disposed radially outside with respect to the rear surface 196. The support surface 197 is disposed rearward of the rear surface 196. The rear end of the first hammer bearing 130A is in contact with at least a part of the front end surface of the large-diameter portion 181B.
The second hammer bearing 130B is disposed around the rear small-diameter portion 181C. The inner ring of the second hammer bearing 130B is in contact with the outer circumferential surface of the rear small-diameter portion 181C. The outer ring of the second hammer bearing 130B is in contact with the inner circumferential surface of the large cylindrical portion 153. A front end of the second hammer bearing 130B is in contact with at least a part of the rear end surface of the large-diameter portion 181B. In the embodiment, a plurality of notches 181D are provided in the rear small-diameter portion 181C. The notches 181D are recessed forward from the rear end of the rear small-diameter portion 181C. The notches 181D enable the rear small-diameter portion 181C to be elastically deformed in the radial direction. Owing to the elastic deformation of the rear small-diameter portion 181C, the second hammer bearing 130B and the rear small-diameter portion 181C are fixed to each other. That is, the rear small-diameter portion 181C generates elastic force that pushes the second hammer bearing 130B radially outward. The second hammer bearing 130B is disposed around the rear small-diameter portion 181C so as to fasten the rear small-diameter portion 181C from radial outside. With this, the second hammer bearing 130B and the rear small-diameter portion 181C are fixed to each other.
Effects A described above, in the embodiment, the hammer 175 may be supported by the first hammer bearing 130A and the second hammer bearing 130B. The second hammer bearing 130B may be disposed rearward of the first hammer bearing 130A.
According to the above-described configuration, the hammer 175 is suppressed from rotating in a state of being inclined with respect to the spindle 26.
In the embodiment, the hammer 175 may include: the inner cylindrical portion 183 supported by the spindle 26; the front outer cylindrical portion 182 disposed radially outside with respect to the inner cylindrical portion 183 and disposed forward of the inner cylindrical portion 183; and the rear outer cylindrical portion 181 disposed radially outside with respect to the inner cylindrical portion 183 and disposed rearward of the front outer cylindrical portion 182. The rear outer cylindrical portion 181 has an outer diameter larger than that of the front outer cylindrical portion 182. Each of the first hammer bearing 130A and the second hammer bearing 130B may support the rear outer cylindrical portion 181.
According to the above-described configuration, the hammer 175 is suppressed from rotating in a state of being inclined with respect to the spindle 26.
In the embodiment, the first hammer bearing 130A may support the front portion of the rear outer cylindrical portion 181. The second hammer bearing 130B may support the rear portion of the rear outer cylindrical portion 181.
According to the above-described configuration, the hammer 175 is suppressed from rotating in a state of being inclined with respect to the spindle 26.
In the embodiment, the rear outer cylindrical portion 181 may include: the front small-diameter portion 181A; the large-diameter portion 181B disposed rearward of the front small-diameter portion 181A; and the rear small-diameter portion 181C disposed rearward of the large-diameter portion 181B. The large-diameter portion 181B may have an outer diameter larger than that of the front small-diameter portion 181A and that of the rear small-diameter portion 181C. The first hammer bearing 130A may be disposed around the front small-diameter portion 181A. The second hammer bearing 130B may be disposed around the rear small-diameter portion 181C.
According to the above-described configuration, an increase in size of the hammer case 123 in the radial direction is suppressed.
In the embodiment, the hammer 175 may have the support surface 197 facing the front end of the first hammer bearing 130A. The front end of the first hammer bearing 130A may be in contact with the support surface 197 of the hammer 175.
According to the above-described configuration, the first hammer bearing 130A is positioned in the axial direction.
In the embodiment, the rear end of the first hammer bearing 130A may be in contact with at least a part of the front end surface of the large-diameter portion 181B.
According to the above-described configuration, the first hammer bearing 130A is positioned in the axial direction.
In the embodiment, the front end of the second hammer bearing 130B may be in contact with at least a part of the rear end surface of the large-diameter portion 181B.
According to the above-described configuration, the second hammer bearing 130B is positioned in the axial direction.
In the embodiment, a plurality of notches 181D may be provided in the rear small-diameter portion 181C. The rear small-diameter portion 181C may be elastically deformed in the radial direction owing to the notches 181D. The second hammer bearing 130B and the rear small-diameter portion 181C may be fixed to each other by elastic deformation of the rear small-diameter portion 181C.
According to the above-described configuration, the inner ring of the second hammer bearing 130B is position in the hammer 175.
In the embodiment, the output assembly 4B may include the hammer case 123 that houses the hammer 175. The hammer case 123 may have the through hole 116 overlapping the screw hole 94 in both the radial direction and the circumferential direction. The screw 93 may be rotated through the through hole 116.
According to the above-described configuration, an operator can smoothly bring a screw fastening tool into contact with the screw 93 disposed in the screw hole 94 via the through hole 116, and can smoothly rotate the screw 93. The operator can appropriately adjust elastic force of the elastic member 78 in accordance with operation contents.
In the embodiment, the output assembly 4B may include the first hammer bearing 130A and the second hammer bearing 130B, which are held by the hammer case 23 and support the hammer 175 in a rotatable manner. The first hammer bearing 130A and the second hammer bearing 130B may be disposed around the rear outer cylindrical portion 181.
According to the above-described configuration, the first hammer bearing 130A and the second hammer bearing 130B do not cover the front end of the screw hole 94, whereby the operator can smoothly bring the screw fastening tool into contact with the screw 93 disposed in the screw hole 94 via the through hole 116, and smoothly rotate the screw 93.
A third embodiment will be described. In the following description, the same or equivalent components as those of the above-described embodiment are denoted by the same reference signs, and the description of the components is simplified or omitted.
Impact Tool
The impact tool 1C includes: a housing 202 including a motor housing 217; and an output assembly 4C.
The output assembly 4C includes a hammer case 223, a bearing box 224, and a cover 119. The hammer 75 and the spindle 26 are disposed in internal space of the output assembly 4C defined by the hammer case 223 and the bearing box 224. The hammer case 223 holds the hammer 75 via the hammer bearing 30. The hammer 75 is connected to the hammer case 223 via the hammer bearing 30. The bearing box 224 holds the spindle 26 via a spindle bearing 27. The spindle 26 is connected to the bearing box 224 via the spindle bearing 27.
In the embodiment, the hammer case 223 is coupled to the bearing box 224 via a screw portion. The hammer case 223 can rotate with respect to the bearing box 224. A screw groove 120 is formed in a rear portion of the inner circumferential surface of the hammer case 223. A screw thread 121 is formed on the outer circumferential surface of the bearing box 224. The screw groove 120 and the screw thread 121 are joined. In response to rotation of the hammer case 223 with respect to the bearing box 224, the hammer case 223 moves in the front-rear direction with respect to the bearing box 224.
The cover 119 is disposed so as to cover the hammer case 223. An operator can rotate the hammer case 223 in a state of gripping the cover 119. An operator can move the hammer case 223 in the front-rear direction with respect to the bearing box 224 by rotating the hammer case 223 via the cover 119.
As illustrated in
As illustrated in
The relative rotation of the cover 119 and the hammer case 223 is prevented by the second rotation preventing mechanism 229, so that an operator can rotate the hammer case 223 via the cover 119. The relative rotation of the motor housing 217 and the bearing box 224 is prevented by the first rotation preventing mechanism 228, so that an operator can rotate the hammer case 223 with respect to the bearing box 224.
As illustrated in
The leaf spring 122 has a protrusion portion 127. The protrusion portion 127 is disposed in any one of the recesses 126. By disposing the protrusion portion 127 in any one of the recesses 126, the cover 119 is positioned in the circumferential direction.
As illustrated in
When the hammer case 223 is rotated by an operator via the cover 119 and moves in the front-rear direction, the hammer 75 connected to the hammer case 223 via the hammer bearing 30 moves in the front-rear direction together with the hammer case 223. The front end of the elastic member 78 is in contact with at least a part of the hammer 75. The rear end of the elastic member 78 is in contact with the cam ring 76. The cam ring 76 is connected to the flange 65 of the spindle 26. The spindle 26 is connected to the bearing box 224 via the spindle bearing 27. Therefore, when the hammer 75 moves in the front-rear direction in response to the rotation of the hammer case 223, the amount of compression of the elastic member 78 changes. Since the distance between the cam ring 76 and the hammer 75 is shortened in the front-rear direction by the hammer case 223 rotating such that the hammer 75 moves rearward, the elastic member 78 is compressed. Since the distance between the cam ring 76 and the hammer 75 is increased in the front-rear direction by the hammer case 223 rotating such that the hammer 75 moves forward, the elastic member 78 is extended.
By disposing the protrusion portion 127 in any one of the recesses 126, the cover 119 is positioned in the circumferential direction. Thus, unnecessary rotation of the cover 119 is suppressed. Furthermore, the leaf spring 122 gives a click feeling to an operator during rotation of the cover 119. The operator rotates the cover 119 such that any index mark 118 among the index marks 118 coincides with the position mark 117. The interval between the recesses 126 coincides with the interval between the index marks 118. Thus, when the cover 119 is rotated such that any index mark 118 coincides with the position mark 117, the protrusion portion 127 is disposed in any one of recesses 126, and the amount of compression of the elastic member 78 is adjusted.
Effects
As described above, in the embodiment, the impact tool 1C may include: the bearing box 224 that holds the spindle 26; and the hammer case 223 that holds the hammer 75. The hammer case 223 may be coupled to the bearing box 224 via the screw portion including the screw groove 120 and the screw thread 121. The hammer case 223 rotates with respect to the bearing box 224 and moves in the axial direction, so that elastic force of the elastic member 78 may be adjusted.
According to the above-described configuration, an operator can adjust the elastic force of the elastic member 78 by gripping and rotating the hammer case 223 with his/her hand. The operator can adjust the elastic force of the elastic member 78 without using a screw fastening tool.
In the embodiment, the impact tool 1C may include: the motor housing 217 that houses the motor 6; and the first rotation preventing mechanism 228 configured to prevent the relative rotation of the motor housing 217 and the bearing box 224.
According to the above-described configuration, when the hammer case 223 is rotated, rotation of the bearing box 224 is prevented by the first rotation preventing mechanism 228. Thus, the operator can smoothly rotate the hammer case 223 with respect to the bearing box 224.
In the embodiment, the impact tool 1C may include: the cover 119 that covers the hammer case 223; and the second rotation preventing mechanism 229 configured to prevent the relative rotation of the cover 119 and the hammer case 223. The hammer case 223 may be rotated via the cover 119.
According to the above-described configuration, the relative rotation of the cover 119 and the hammer case 223 is prevented by the second rotation preventing mechanism 229. Thus, the operator can rotate the hammer case 223 by gripping and rotating the cover 119 with his/her hand. In response to rotation of the hammer case 223, the elastic force of the elastic member 78 is adjusted. The operator can adjust the elastic force of the elastic member 78 without directly touching the hammer case 223.
In the embodiment, the impact tool 1C may include the positioning mechanism 231 configured to position the cover 119 in the circumferential direction.
According to the above-described configuration, unnecessary rotation of the hammer case 223 and the cover 119 is suppressed.
A fourth embodiment will be described. In the following description, the same or equivalent components as those of the above-described embodiment are denoted by the same reference signs, and the description of the components is simplified or omitted.
Output Assembly
The output assembly 4D includes a hammer case 23 and a bearing box 24. A hammer 375 and an elastic member 378 are disposed in internal space of the output assembly 4D defined by the hammer case 23 and the bearing box 24. In
Similarly to the above-described embodiment, the elastic member 378 is disposed in closed space defined by the spindle shaft 64, the hammer 75, and the cam ring 76. The elastic member 378 has a spring constant of 100 [N/mm] or more. Although an upper limit value of the spring constant of the elastic member 378 is not particularly limited, the elastic member 378 has a spring constant of 10000 [N/mm] or less in the embodiment.
The hammer 375 includes a rear outer cylindrical portion 381, a front outer cylindrical portion 382, and an inner cylindrical portion 383. Each of the rear outer cylindrical portion 381, the front outer cylindrical portion 382, and the inner cylindrical portion 383 is disposed so as to surround the rotation axis AX. The rear outer cylindrical portion 381, the front outer cylindrical portion 382, and the inner cylindrical portion 383 are integrated.
The front outer cylindrical portion 382 is disposed forward of the rear outer cylindrical portion 381. A front end of the rear outer cylindrical portion 381 is connected to a rear end of the front outer cylindrical portion 382. The rear outer cylindrical portion 381 has an outer diameter larger than that of the front outer cylindrical portion 382. The rear outer cylindrical portion 381 has an inner diameter larger than that of the front outer cylindrical portion 382.
The inner cylindrical portion 383 is disposed radially inside with respect to the rear outer cylindrical portion 381 and the front outer cylindrical portion 382. A front end of the inner cylindrical portion 383 is connected to the rear end of the front outer cylindrical portion 382.
In the embodiment, the elastic member 378 includes a plurality of coil springs 391 disposed around the rotation axis AX of the spindle 26. A front end of each of the coil springs 391 is in contact with a support surface 390 between a front end of the inner circumferential surface of the rear outer cylindrical portion 381 and a front end of the outer circumferential surface of the inner cylindrical portion 383. The support surface 390 is disposed forward of the flange 65 and the cam ring 76. A rear end of each of the coil springs 391 is in contact with the front surface of the cam ring 76.
Support pins 128 are respectively disposed inside the coil springs 391. The support pins 128 are fixed to the hammer 375. In the embodiment, the support pins 128 are press-fitted into recesses 385 provided on the support surface 390. By disposing the support pins 128 inside the coil springs 391, the coil springs 391 are positioned in both the radial direction and the circumferential direction.
The tool holding shaft 31 supports movable anvils 333 in a movable manner. In the embodiment, each of the movable anvils 333 includes a cylindrical portion 333A and a pin portion 333B disposed inside the cylindrical portion 333A. A front end of the pin portion 333B protrudes forward from the front end surface of the cylindrical portion 333A. A rear end of the pin portion 333B protrudes forward from the rear end surface of the cylindrical portion 333A.
Effects
As described above, in the embodiment, the elastic member 378 may include a plurality of coil springs 391 disposed around the rotation axis of the spindle 26.
According to the above-described configuration, the elastic member 378 can generate high elastic force.
In the embodiment, the front end of the coil spring 391 may be in contact with the support surface 390 of the hammer 375.
According to the above-described configuration, the front end of the coil spring 391 is stably connected to the hammer 375.
In the embodiment, the output assembly 4D may include the support pin 128 disposed inside the coil spring 391. The support pin 128 may be fixed to the hammer 375.
According to the above-described configuration, the coil spring 391 is positioned in both the radial direction and the circumferential direction.
In the above-described embodiments, the impact tool is an impact driver. The impact tool may be an impact wrench.
In the above-described embodiment, the power source of the impact tool may not be the battery pack 20, and may be a commercial power source (AC power source).
Additional aspects of the present teachings include, but are not limited to:
1. An impact tool comprising:
2. The impact tool according to the above aspect 1, wherein
3. The impact tool according to the above aspect 2, wherein
4. The impact tool according to the above aspect 3, wherein
5. The impact tool according to the above aspect 4, further including
6. The impact tool according to the above aspect 4 or 5, wherein
7. The impact tool according to any one of the above aspects 4 to 6, wherein
8. The impact tool according to the above aspect 7, further including:
9. The impact tool according to the above aspect 7, further including
10. The impact tool according to the above aspect 9, further including
11. The impact tool according to the above aspect 1 or 2, further including:
12. The impact tool according to the above aspect 11, further including:
13. The impact tool according to the above aspect 11 or 12, further including:
14. The impact tool according to the above aspect 13, further including
15. The impact tool according to any one of the above aspects 1 to 14, wherein
16. The impact tool according to the above aspect 15, further including
17. The impact tool according to any one of the above aspects 1 to 16, further including
18. The impact tool according to the above aspect 17, wherein
19. The impact tool according to the above aspect 17 or 18, further including
20. The impact tool according to the above aspect 19, wherein
According to the technology disclosed in the present specification, an increase in size of the impact tool is suppressed.
Furthermore, according to the technology disclosed in the present specification, an impact tool capable of smoothly performing each of a high load operation and a low load operation is provided.
Although the invention has been described with respect to specific embodiments for a complete and clear disclosure, the appended claims are not to be thus limited but are to be construed as embodying all modifications and alternative constructions that may occur to one skilled in the art that fairly fall within the basic teaching herein set forth.
| Number | Date | Country | Kind |
|---|---|---|---|
| 2022-078187 | May 2022 | JP | national |
| 2022-078188 | May 2022 | JP | national |
