JP2022109455A - Torque generator and oil pulse tool - Google Patents

Abstract

To provide a technology that increases torque generated on a shaft.SOLUTION: An inner peripheral surface 610 of an oil space 580 included in a case has: a cam surface which first movable members 100 slidably contact with while getting into/out from an oil space through first openings 541a included in a shaft 50; and a restriction surface which restricts outflow/inflow of an oil from/into the oil space through at least one second opening 531a included in the shaft. In a restriction state in which the restriction surface restricts the outflow/inflow of the oil from/into the oil space, the first movable members are restricted from getting into/out from the oil space. In a case where the case is rotationally driven to rotate relative to the shaft, when each first movable member slidably contacts with a first area of the cam surface in the restriction state, force of the cam surface which pushes the first movable members to the oil space side becomes larger to generate torque on the shaft.SELECTED DRAWING: Figure 6

Description

The present disclosure relates to technology for generating torque on a shaft.

Patent Literature 1 describes a technique for generating torque on a shaft using oil.

JP 2012-30327 A

When using oil to generate torque on the shaft, it is desirable that a large amount of torque be generated on the shaft.

A torque generator and oil pulse tool are disclosed. In one embodiment, the torque generator has an oil chamber filled with oil and is rotatably driven, and at least a portion of the torque generator is supported in the oil chamber and is rotatable relative to the case. A shaft and a first moving member movable in and out of the shaft are provided. The shaft is positioned inside the shaft, is filled with oil, and opens toward an oil space through which the first moving member moves in and out, and an inner peripheral surface of the oil chamber, through which the first moving member moves in and out of the oil space. It has a first opening and at least one second opening that opens toward the inner peripheral surface of the oil chamber and allows oil to flow into and out of the oil space. The inner peripheral surface of the oil chamber has a cam surface and a restricting surface. As the case rotates relative to the shaft, the first moving member moves in and out of the oil space through the first opening and comes into sliding contact with the cam surface. The restricting surface restricts oil from flowing into and out of the oil space through at least one of the second openings when the case and the shaft are in a predetermined positional relationship in the rotational direction of the case. In the restricted state in which the restriction surface restricts the inflow and outflow of oil to and from the oil space, the first moving member is restricted from entering and exiting the oil space. The cam surface has a first region. In a first rotational state in which the case is rotationally driven in the first rotational direction and rotates relative to the shaft, when the first moving member comes into sliding contact with the first region in the regulated state, the cam surface undergoes the first movement. The force that pushes the member toward the oil space increases, and torque in the first rotation direction is generated in the shaft.

In one embodiment, an oil pulse tool includes the above torque generator, a tip tool attached to a shaft of the torque generator, and a motor for rotating a case of the torque generator.

Torque generated in the shaft can be increased.

It is a schematic diagram showing an example of the appearance of an oil pulse tool. It is a schematic diagram showing an example of the appearance of an oil pulse tool. 1 is a schematic diagram showing an example of the internal configuration of an oil pulse tool; FIG. It is a schematic diagram showing an example of the section structure of an oil pulse tool. It is a schematic diagram showing an example of a cross-sectional structure of a unit. It is a schematic diagram showing an example of a cross-sectional structure of a torque generator. It is a schematic diagram showing an example of a cross-sectional structure of a torque generator. It is a schematic diagram showing an example of a cross-sectional structure of a torque generator. FIG. 4 is a schematic diagram showing an example of the appearance of a shaft; FIG. 4 is a schematic diagram showing an example of the appearance of a shaft; It is a schematic diagram showing an example of a cross-sectional structure of a shaft. It is a schematic diagram showing an example of a cross-sectional structure of a shaft. It is a schematic diagram showing an example of the appearance of a liner. It is a schematic diagram showing an example of the appearance of a liner. It is the schematic which shows an example of the cross-sectional structure of a liner. It is the schematic which shows an example of the cross-sectional structure of a liner. It is the schematic which shows an example of the cross-sectional structure of a liner. FIG. 4 is a schematic diagram for explaining an example of the operation of the torque generator; FIG. 4 is a schematic diagram for explaining an example of the operation of the torque generator; FIG. 4 is a schematic diagram for explaining an example of the operation of the torque generator; FIG. 4 is a schematic diagram for explaining an example of the operation of the torque generator; FIG. 4 is a schematic diagram for explaining an example of the operation of the torque generator; FIG. 4 is a schematic diagram for explaining an example of the operation of the torque generator; FIG. 4 is a schematic diagram for explaining an example of the operation of the torque generator; FIG. 4 is a schematic diagram for explaining an example of the operation of the torque generator; FIG. 4 is a schematic diagram for explaining an example of the operation of the torque generator; It is a schematic diagram showing an example of a cross-sectional structure of a torque generator. It is a schematic diagram showing an example of a cross-sectional structure of a torque generator. It is a schematic diagram showing an example of a cross-sectional structure of a torque generator. FIG. 4 is a schematic diagram showing an example of the appearance of a shaft; FIG. 4 is a schematic diagram showing an example of the appearance of a shaft; FIG. 4 is a schematic diagram showing an example of the appearance of a shaft; It is a schematic diagram showing an example of a cross-sectional structure of a shaft. It is a schematic diagram showing an example of a cross-sectional structure of a shaft. It is a schematic diagram showing an example of the appearance of a liner. It is a schematic diagram showing an example of the appearance of a liner. It is the schematic which shows an example of the cross-sectional structure of a liner. It is the schematic which shows an example of the cross-sectional structure of a liner. It is the schematic which shows an example of the cross-sectional structure of a liner. FIG. 4 is a schematic diagram for explaining an example of the operation of the torque generator; FIG. 4 is a schematic diagram for explaining an example of the operation of the torque generator; FIG. 4 is a schematic diagram for explaining an example of the operation of the torque generator; FIG. 4 is a schematic diagram for explaining an example of the operation of the torque generator; FIG. 4 is a schematic diagram for explaining an example of the operation of the torque generator; FIG. 4 is a schematic diagram for explaining an example of the operation of the torque generator; FIG. 4 is a schematic diagram for explaining an example of the operation of the torque generator; FIG. 4 is a schematic diagram for explaining an example of the operation of the torque generator; It is a schematic diagram showing an example of a cross-sectional structure of a unit. It is a schematic diagram showing an example of a cross-sectional structure of a unit. It is the schematic which shows an example of the cross-sectional structure of a liner. It is a schematic diagram showing an example of a cross-sectional structure of a torque generator. It is a schematic diagram which shows an example of the cross-sectional structure of a moving member.

1 and 2 are schematic perspective views showing an example of the appearance of the oil pulse tool 1. FIG. The oil pulse tool 1 is a type of electric power tool, and can rotate the tip tool 2 using a motor. The tip tool 2 is attached to a shaft 50 that is long in one direction, and the tip tool 2 rotates as the shaft 50 rotates. The oil pulse tool 1 is also called rotary tool. The tip tool 2 may be, for example, a screwdriver bit for tightening or loosening screws or bolts. Moreover, the tip tool 2 may be a drill bit for drilling a member such as wood. Further, the tip tool 2 may be a socket bit for tightening or loosening a bolt or nut, or may be another tip tool.

The oil pulse tool 1 includes, for example, a tip tool 2, a housing (also referred to as an exterior case) 3, and a trigger 4. The housing 3 includes, for example, an accommodating portion 30 that accommodates the motor, the shaft 50, and the like, a grip portion 31 that is gripped by a user's hand, and a battery mounting portion 32 that mounts a battery. The accommodating portion 30 has, for example, a substantially cylindrical shape extending along the longitudinal direction of the shaft 50 and closed at one end. The shaft 50 extends, for example, from an opening at one longitudinal end of the housing portion 30 to the outside of the housing portion 30 . The tip tool 2 is inserted into the shaft 50 from the tip side of the shaft 50, for example. Shaft 50 is also called a spindle or an output shaft. The outer diameter and inner diameter of the housing portion 30 generally decrease toward the end tool 2 side.

The grip portion 31 has, for example, a tubular shape extending along a direction perpendicular to the longitudinal direction of the shaft 50 . The housing portion 30 is connected to one end of the grip portion 31 in the longitudinal direction, and the battery mounting portion 32 is connected to the other end of the grip portion 31 in the longitudinal direction. The battery is, for example, detachable from the battery mounting portion 32 . The oil pulse tool 1 operates using the DC voltage output by the battery mounted in the battery mounting portion 32 as the power supply voltage. The trigger 4 is exposed from the grip portion 31, for example. When the trigger 4 is pushed, the motor rotates and the tip tool 2 rotates. Note that the oil pulse tool 1 may operate using an AC voltage supplied from a commercial power source as a power supply voltage instead of operating based on the DC voltage output by the battery.

FIG. 3 is a schematic diagram showing an example of the internal state of the housing portion 30. As shown in FIG. FIG. 4 is a schematic diagram showing an example of a cross-section of the structure shown in FIG. Henceforth, when explaining the structure in the accommodating part 30, the tip tool 2 side may be called a front side, and the other side may be called a rear side. It can be said that the shaft 50 extends along the front-rear direction.

As shown in FIGS. 3 and 4, the housing 30 includes, for example, a motor 5, a cooling fan 6 (also referred to simply as fan 6), a cooling fan 7 (also referred to simply as fan 7), and a planetary gear reducer. 8 (also referred to simply as speed reducer 8) and part of a unit 10 (also referred to as assembly 10) are accommodated. The unit 10 includes, for example, a sleeve 11 and two spheres 13 for fixing the tip tool 2 inside the shaft 50, and a case 12 (also called unit case 12). The unit 10 further comprises a plurality of planetary gears 14 and an annular internal gear 15 of the speed reducer 8 , an annular bearing 16 and 17 and a torque generator 40 . Shaft 50 is included in torque generator 40 .

The unit case 12 has, for example, a cylindrical shape and is fixed to the housing portion 30 . The unit case 12 is relatively non-rotatable with respect to the housing portion 30 . The outer diameter and inner diameter of the unit case 12 generally decrease toward the front. A portion of the torque generator 40 , the plurality of planetary gears 14 , the internal gear 15 , and the bearings 16 and 17 are housed inside the unit case 12 . Bearings 16 and 17 are fixed to unit case 12 . The torque generating device 40 is also called a torque generating unit 40 because it is composed of a plurality of parts. As will be described later, the torque generator 40 can generate pulsed torque on the shaft 50 using oil. Torque generator 40 is also called pulse device 40 or pulse unit 40 .

Motor 5 is, for example, a brushless DC motor. Motor 5 may be other than a brushless DC motor. A motor shaft (also referred to as a rotating shaft) 5a of the motor 5 extends in the front-rear direction. Cooling fan 6, cooling fan 7 and sun gear 9 are fixed to motor shaft 5a. The oil pulse tool 1 has a motor control circuit for controlling the motor 5 . The motor control circuit rotates the motor 5 based on power supplied from the battery when the trigger 4 is pressed. Thus, when the trigger 4 is pressed, the motor shaft 5a rotates, and the cooling fan 6, the cooling fan 7, and the sun gear 9 rotate according to the rotation of the motor shaft 5a.

The fan 6 can cool the motor 5, for example. The fan 6 is, for example, a centrifugal fan, and includes a plurality of blades 6a radially extending along the radial direction of the substantially cylindrical accommodating portion 30. As shown in FIG. The fan 6 is positioned forward of the portion of the motor 5 other than the motor shaft 5a.

The fan 7 can cool the unit 10, for example. It can also be said that the fan 7 can cool the torque generator 40 provided in the unit 10 . The fan 7 is, for example, a centrifugal fan, and includes a plurality of blades 7a radially extending along the radial direction of the substantially cylindrical accommodating portion 30 . The plurality of blades 7a are located on the front side of the plurality of blades 6a.

The housing portion 30 has a partition wall portion 300 erected on its inner peripheral surface. The partition wall 300 is positioned between the plurality of blades 6a of the fan 6 and the plurality of blades 7a of the fan 7 . The partition part 300 has, for example, an annular plate shape. The motor shaft 5 a is inserted through the central opening of the partition wall 300 . The partition wall 300 covers the front end face of each blade 6a and the rear end face of each blade 7a. By covering the front end face of each blade 6a of the fan 6 with the partition wall portion 300, the fan 6 can move the air taken in from the rear side to the centrifugal direction (in other words, the radial direction of the housing portion 30 or perpendicular to the motor shaft 5a). direction). In addition, by covering the rear end face of each blade 7a of the fan 7 with the partition wall 300, the fan 7 can discharge the air taken in from the front side in the centrifugal direction.

As shown in FIGS. 1 and 2 , the accommodation portion 30 includes a plurality of air intake ports 310 for drawing cooling air for cooling the motor 5 into the accommodation portion 30 , and cooling air for cooling the motor 5 . A plurality of exhaust ports 311 for discharging to the outside are provided. A plurality of air inlets 310 are provided, for example, at the rear end of the housing portion 30 . The plurality of exhaust ports 311 are arranged along the circumferential direction of the housing portion 30 so as to follow the arrangement of the plurality of blades 6a of the fan 6, for example. When the fan 6 is rotating, the air taken into the accommodation portion 30 through the plurality of air inlets 310 cools the motor 5 and is then discharged out of the accommodation portion 30 through the plurality of air outlets 311 . Thereby, the motor 5 is appropriately cooled.

In addition, the accommodation section 30 has a plurality of air intake ports 320 for drawing cooling air for cooling the unit 10 into the accommodation section 30 and a plurality of air outlets for discharging the cooling air for cooling the unit 10 to the outside of the accommodation section 30. 321 are provided. The plurality of air inlets 320 are provided at the front end portion of the housing portion 30 (in other words, the end portion of the housing portion 30 on the tip tool 2 side). The plurality of exhaust ports 321 are arranged along the circumferential direction of the housing portion 30 so as to follow the arrangement of the plurality of blades 7 a of the fan 7 . When the fan 7 is rotating, the air taken into the housing portion 30 through the plurality of air inlets 320 cools the unit 10 and is then discharged out of the housing portion 30 through the plurality of air outlets 321 . This allows the unit 10 to be properly cooled.

FIG. 5 is a schematic diagram showing an example of the cross-sectional structure of the unit 10. As shown in FIG. FIG. 6 is a schematic diagram showing an example of the cross-sectional structure of the torque generator 40 included in the unit 10. As shown in FIG. FIG. 7 is a schematic diagram showing an example of a cross-sectional structure taken along line AA in FIG. FIG. 8 is a schematic diagram showing an example of a cross-sectional structure taken along line BB in FIG.

As shown in FIG. 5 and the like, the shaft 50 extends outside the unit case 12 from an opening 120 on the front side of the unit case 12 . The motor shaft 5 a and the sun gear 9 enter the unit case 12 through an opening 121 on the rear side of the unit case 12 .

The torque generator 40 includes, for example, a shaft 50 and a case 60 (also referred to as an inner case 60). A portion of the shaft 50 is supported within the inner case 60 . The shaft 50 is rotatable relative to the inner case 60 . A portion of the shaft 50 and a plurality of other members are accommodated in the inner case 60 .

In this example, the planetary carrier 80 of the speed reducer 8 forms part of the inner case 60 . The inner case 60 includes, for example, a liner 70 , a planetary carrier 80 , and an annular connecting member 90 that connects the liner 70 and the planetary carrier 80 . In the inner case 60, the liner 70 is positioned on the front side and the planetary carrier 80 is positioned on the rear side. The liner 70 has, for example, a tubular shape. The outer shape and inner diameter of the liner 70 generally decrease toward the front.

The shaft 50 extends from the front opening 700 of the liner 70 to the outside of the inner case 60 , and further extends from the front opening 120 of the unit case 12 to the outside of the unit case 12 . The opening 701 on the rear side of the liner 70 is closed by the planet carrier 80 . The liner 70 and planet carrier 80 are connected via an O-ring 95 .

The inner case 60 is rotatably supported within the unit case 12 . The rear portion of the inner case 60 (specifically, the planetary carrier 80 ) is supported by the rear bearing 16 inside the unit case 12 . A portion of the shaft 50 located forward of the inner case 60 is supported by a front bearing 17 inside the unit case 12 . The inner case 60 and the shaft 50 are rotatable relative to the unit case 12 and the housing portion 30 . An annular centering member 96 for aligning the central axis (also referred to as the rotation axis) of the shaft 50 is accommodated in the inner case 60 . Centering member 96 is fixed to inner case 60 . The center axis of shaft 50 is aligned by fitting the rear end of shaft 50 into the central opening of centering member 96 .

The inner case 60 is rotated by the motor 5 . The rotation of the motor 5 (specifically, the rotation of the motor shaft 5 a ) is reduced in speed by the planetary gear reducer 8 and transmitted to the liner 70 . When the inner case 60 is driven in rotation by the motor 5, the shaft 50 rotates together with the inner case 60 when it is unloaded or lightly loaded. On the other hand, when the load applied to the shaft 50 is large, the rotation of the shaft 50 is restricted and the inner case 60 rotates relative to the shaft 50 . The rotation of inner case 60 and shaft 50 will be described later in detail.

When the motor shaft 5a rotates clockwise as viewed from the front side, the inner case 60 also rotates clockwise as viewed from the front side. When the motor shaft 5a rotates counterclockwise as viewed from the front side, the inner case 60 also rotates counterclockwise as viewed from the front side. The rotation direction of the motor shaft 5a is switched by operating a switching lever exposed from the housing 3. FIG. Henceforth, clockwise rotation simply means clockwise rotation when viewed from the front side. In addition, simply saying counterclockwise rotation means counterclockwise rotation when viewed from the front side.

The inner case 60 has an oil chamber 600 filled with oil. A space surrounded by the liner 70 and the planetary carrier 80 is filled with oil and constitutes an oil chamber 600 . A portion of shaft 50 is supported within oil chamber 600 . Oil is also present between the inner case 60 and the shaft 50 .

FIG. 9 is a schematic perspective view showing the appearance of the shaft 50. As shown in FIG. FIG. 10 is a schematic diagram showing an example of how the shaft 50 is viewed from the arrow X in FIG. FIG. 11 is a schematic diagram showing an example of a cross-sectional structure taken along line CC in FIG. FIG. 12 is a schematic diagram showing an example of a cross-sectional structure taken along line DD in FIG.

As shown in FIGS. 5, 6, 9 to 12, etc., the shaft 50 has a rod shape whose diameter changes along its length. Shaft 50 includes, for example, first portion 510 , second portion 520 , third portion 530 , fourth portion 540 and fifth portion 550 .

The first portion 510 has, for example, an elongated, substantially cylindrical shape and an insertion hole 511 into which the tip tool 2 is inserted. The cross-sectional shape of the outer shape of the first portion 510 perpendicular to the front-rear direction (in other words, the longitudinal direction of the shaft 50) is circular, for example. The first portion 510 can also be called an insertion portion 510 into which the tip tool 2 is inserted or an attachment portion 510 to which the tip tool 2 is attached. The insertion hole 511 extends rearward from the front end of the first portion 510 and has an opening 511a at the front end. The tip tool 2 is inserted into the insertion hole 511 through the opening 511a.

A pair of through holes 512 facing each other are provided in the peripheral wall portion of the first portion 510 . As shown in FIG. 5, the above-described two spheres 13 are arranged in the pair of through holes 512, respectively. Each sphere 13 can be retracted into the insertion hole 511 . Each sphere 13 is arranged inside an annular sleeve 11 . Each ball 13 is engaged with the tip tool 2 inserted into the first portion 510 in a state of protruding into the insertion hole 511 . Each sphere 13 is pressed against the tip tool 2 by the inner surface of the sleeve 11 , and the tip tool 2 is held between the two spheres 13 . As a result, the tip tool 2 is fixed within the shaft 50 . On the other hand, in the state where the sleeve 11 is slid forward, the pressing of the balls 13 by the sleeve 11 is released. As a result, the tip tool 2 can be pulled out from the shaft 50 .

The second portion 520 is connected to the first portion 510 on the rear side of the first portion 510 . The outer shape of the second portion 520 is, for example, disk-shaped. In other words, the second portion 520 has a cylindrical shape with a very low height. The cross-sectional shape of the outer shape of the second portion 520 perpendicular to the front-rear direction is, for example, circular. The outer diameter of the second portion 520 is larger than the outer diameter of the first portion 510, for example.

The third portion 530 is connected to the second portion 520 on the rear side of the second portion 520 . The external shape of the third portion 530 is, for example, a columnar shape with a low height. A cross-sectional shape perpendicular to the front-rear direction of the outer shape of the third portion 530 is, for example, substantially circular. The outer diameter of the third portion 530 is larger than the outer diameter of the second portion 520, for example. A hole 531 is provided in the third portion 530 . The hole 531 is, for example, an elongated through hole 531 passing through the third portion 530 along a direction perpendicular to the longitudinal direction of the shaft 50 . The through-hole 531 has a cylindrical shape, for example, and has openings 531a at both longitudinal ends thereof. As shown in FIGS. 5 and 6, each opening 531a opens toward the inner peripheral surface 610 of the oil chamber 600. As shown in FIGS. Specifically, as shown in FIGS. 5, 6 and 8, each opening 531a opens toward the inner peripheral surface 710 of the liner 70 forming the oil chamber 600. As shown in FIGS. Each opening 531 a is connected to a region outside the shaft 50 in the oil chamber 600 .

The fourth portion 540 is connected to the third portion 530 on the rear side of the third portion 530 . The outer shape of the fourth portion 540 is, for example, cylindrical. The cross-sectional shape of the outer shape of the fourth portion 540 perpendicular to the front-rear direction is, for example, substantially circular. The outer diameter of the fourth portion 540 is larger than the outer diameter of the third portion 530, for example. A hole 541 is provided in the fourth portion 540 . The hole 541 is, for example, a through hole 541 passing through the fourth portion 540 along the direction perpendicular to the longitudinal direction of the shaft 50 . The through-hole 541 has, for example, a cylindrical shape, and has openings 541a at both longitudinal ends thereof. The through hole 541 is arranged parallel to the through hole 531 on the rear side of the through hole 531, for example. As shown in FIGS. 5 and 6, each opening 541 a opens toward inner peripheral surface 610 of oil chamber 600 . Specifically, as shown in FIGS. 5, 6 and 7, each opening 541a opens toward the inner peripheral surface 710 of the liner .

The shaft 50 has a connection hole 560 that connects the insertion hole 511, the through hole 531, and the through hole 541 to each other. The connection hole 560 has a columnar shape, for example. The connection hole 560 is provided from the second portion 520 to the fourth portion 540 and extends rearward from the rear end of the insertion hole 511 to reach the through hole 541 . The connection hole 560 has a front portion connecting the insertion hole 511 and the through hole 531 and a rear portion connecting the through hole 531 and the through hole 541 .

In this example, the through hole 531 , the through hole 541 , and the rear portion of the connection hole 560 connecting the through holes 531 and 541 are filled with the oil in the oil chamber 600 . The through hole 531, the through hole 541, and the rear portion of the connection hole 560 form an oil space 580 (also referred to as a shaft oil space 580) filled with oil.

As shown in FIGS. 5 and 6, the front portion of the connection hole 560 and the insertion hole 511 connected thereto are provided with a seal screw 98 for preventing the oil in the shaft oil space 580 from leaking out of the shaft 50 from the insertion hole 511 . is provided. By screwing the seal screw 98 into the front portion of the connection hole 560 from the insertion hole 511 side, the oil in the oil space 580 is prevented from leaking to the insertion hole 511 side.

As shown in FIGS. 5 and 6, an O-ring 97 is provided between the inner peripheral surface 710 of the liner 70 and the outer peripheral surface of the shaft 50 to prevent the oil in the oil chamber 600 from leaking from the front side. is provided. The O-ring 97 is positioned between the outer peripheral surface of the first portion 510 of the shaft 50 and the inner peripheral surface 710 of the liner 70 so as to surround the outer peripheral surface of the rear end portion of the shaft 50 . In this example, a portion of the space surrounded by the inner case 60 on the rear side of the O-ring 97 serves as an oil chamber 600 .

Torque generator 40 includes a plurality of moving members 100 that can move in and out of shaft 50 . Each moving member 100 is accessible in and out of the shaft oil space 580 . Here, the movement of the moving member 100 into and out of the shaft 50 and the like includes not only the complete movement of the moving member 100 into and out of the shaft 50 and the like, but also the partial movement of the moving member 100 into and out of the shaft 50 and the like. It also includes entering. The movement of the moving member 100 into and out of the shaft 50 and the like can be said to change the amount of protrusion (in other words, the distance of protrusion) of the moving member 100 from the shaft 50 and the like. It can also be said that moving member 100 entering shaft 50 or the like reduces the amount of protrusion of moving member 100 from shaft 50 or the like, and moving member 100 coming out of shaft 50 or the like means that shaft 50 of moving member 100 It can also be said that the amount of protrusion from etc. increases. When the moving member 100 enters the shaft 50 or the like, the amount of entry of the moving member 100 into the shaft 50 or the like (in other words, the penetration distance) increases. the amount of entry into the

The torque generator 40 of this example includes, for example, two moving members 100 . One moving member 100 can enter and exit the shaft oil space 580 through one opening 541a of the through hole 541, for example. The other moving member 100 can move in and out of the shaft oil space 580 through the other opening 541a of the through hole 541, for example. It can be said that the opening 541 a is an opening for the moving member 100 to enter and exit the shaft oil space 580 . Each moving member 100 is, for example, a sphere. When the moving member 100 is a sphere, all the surfaces of the protruding portions of the moving member 100 that protrude from the shaft 50 form a partial spherical surface (that is, part of a spherical surface). Hereinafter, the moving member 100 that is a sphere may be referred to as a sphere 100 .

Two mounting members 101 on which two spheres 100 are respectively mounted, and one spring 103 are arranged in the through hole 541 . The mounting member 101 is also called a mounting table or a pedestal. One mounting member 101 is positioned closer to one opening 541 a of the through hole 541 , and the other mounting member 101 is positioned closer to the other opening 541 a of the through hole 541 . The mounting surface of the mounting member 101 on which the spherical body 100 is mounted is a partially spherical surface according to the surface shape of the spherical body 100 . An O-ring 102 is positioned between the inner peripheral surface (in other words, inner wall) of the through hole 541 and the outer peripheral surface of the mounting member 101 on the one opening 541a side. Similarly, an O-ring 102 is positioned between the inner peripheral surface of the through hole 541 and the outer peripheral surface of the mounting member 101 on the side of the other opening 541a. The O-ring 102 is fitted in an annular groove provided on the outer peripheral surface of the mounting member 101 . The O-ring 102 is in contact with the inner peripheral surface of the through hole 541 and the outer peripheral surface of the mounting member 101 .

Spring 103 is, for example, a compression coil spring. The two mounting members 101 are connected by a spring 103 . One end of the spring 103 is engaged with one mounting member 101 and the other end of the spring 103 is engaged with the other mounting member 101 .

Each sphere 100 , each mounting member 101 and each O-ring 102 move within the through hole 541 according to the extension of the spring 103 . The sphere 100, the mounting member 101 and the O-ring 102 slide through the through hole 541, for example. That is, the sphere 100 , the mounting member 101 and the O-ring 102 move inside the through-hole 541 while rubbing against the inner peripheral surface of the through-hole 541 . Since the through hole 541 extends along the direction perpendicular to the rotation axis of the inner case 60, the sphere 100, the mounting member 101 and the O-ring 102 move along the direction perpendicular to the rotation axis of the inner case 60. do.

In the above example, the large-diameter hole 541 in which the spring 103 and the like are arranged is located behind the small-diameter hole 531 , but may be located forward of the hole 531 . Also, the holes 541 do not have to be arranged parallel to the holes 531 . Further, the diameter of the portion of the hole 541 where the spring 103 is arranged may be smaller than the diameter of the portion where the ball 100 and the mounting member 101 are arranged. In this case, the spring 103 stably expands and contracts along the direction perpendicular to the axial direction of the shaft 50 .

The shaft oil space 580 includes a partial space 581 (also referred to as partial oil space 581) in which the pressure of the oil changes. The partial oil space 581 is composed of, for example, the space between the two mounting members 101 in the through hole 541, the rear portion of the connection hole 560 connected to the space, and the through hole 531 connected thereto. In other words, the partial oil space 581 is composed of the space in the through hole 541 where the spring 103 exists, the rear side portion of the connection hole 560 connected to the space, and the through hole 531 . In this example, since the O-ring 102 is positioned between the inner peripheral surface of the through hole 541 and the outer peripheral surface of the mounting member 101 , the oil in the partial oil space 581 flows out of the shaft 50 from the opening 541 a of the through hole 541 . less likely to leak.

The oil in the oil chamber 600 can flow into and out of the shaft oil space 580 through each opening 531 a of the through hole 531 . It can be said that the opening 531 a is an opening for the oil to flow into and out of the shaft oil space 580 . The pressure of the oil in the partial oil space 581 is such that, for example, the sphere 100 is pushed toward the shaft oil space 580 in a state in which the flow of oil into and out of the oil space 580 from each opening 531a of the through hole 531 is regulated. is canceled or changed. This point will be explained in detail later.

The inner peripheral surface 610 of the oil chamber 600 has a cam surface 720 (see FIG. 7) with which the ball 100 slides in and out of the shaft oil space 580 through the opening 541a of the through hole 541 as the inner case 60 rotates relative to the shaft 50. reference). Further, the inner peripheral surface 610 of the oil chamber 600 is such that when the inner case 60 and the shaft 50 are in a predetermined positional relationship in the rotational direction of the inner case 60, the oil flows from the openings 531a of the through holes 531 into the shaft oil space 580. It has a regulation surface 780 (see FIG. 8) that regulates the inflow and outflow. In this example, for example, the inner peripheral surface 710 of the liner 70 of the inner case 60 forming the oil chamber 600 forms the cam surface 720 and the restricting surface 780 . Hereinafter, the direction of rotation means the direction of rotation of the inner case 60 unless otherwise specified.

The spring 103 is located within the through hole 5341 in a compressed state. Each sphere 100 is biased against cam surface 720 by spring 103 and is in contact with cam surface 720 . When the inner case 60 is rotationally driven and rotates relative to the shaft 50 , each ball 100 slides on the cam surface 720 while entering and exiting the shaft oil space 580 through the opening 541 a of the shaft 50 . touch. When the inner case 60 is driven to rotate, each spherical body 100 moves in and out of the shaft oil space 580 according to the shape of the cam surface 720 and comes into sliding contact with the cam surface 720 . As the inner case 60 rotates relative to the shaft 50 , the ball 100 rotates and comes into sliding contact with the cam surface 720 .

When the sphere 100 enters the shaft oil space 580 and the amount of the sphere 100 entering the shaft oil space 580 increases, the shaft oil space 580 (in other words, partial oil space 581 ) is released from each opening 531 a of the third portion 530 of the shaft 50 . ) oil will flow out. On the other hand, when the sphere 100 comes out of the shaft oil space 580 and the amount of the sphere 100 entering the shaft oil space 580 becomes small, the oil enters the shaft oil space 580 (in other words, the partial oil space 581) from each opening 531a of the shaft 50. Oil flows in.

FIG. 13 is a schematic perspective view showing the appearance of the liner 70. FIG. FIG. 14 is a schematic diagram showing an example of how the liner 70 is viewed from the opening 701 side. FIG. 15 is a schematic diagram showing an example of a cross-sectional structure taken along line EE in FIG. FIG. 16 is a schematic diagram showing an example of a cross-sectional structure taken along line FF in FIG. FIG. 17 is a schematic diagram showing an example of a cross-sectional structure taken along line GG in FIG. In FIG. 15, the outer shape of the sphere 100 is indicated by a chain double-dashed line. In FIG. 16, the outline of the third portion 530 of the shaft 50 is indicated by a two-dot chain line. In FIG. 17, the outline of the fourth portion 540 of the shaft 50 is indicated by a two-dot chain line.

As shown in FIGS. 7, 8 and 13-17, the inner peripheral surface 710 of the tubular liner 70 has a cam surface 720 and a restraining surface 780. As shown in FIG. Cam surface 720 surrounds fourth portion 540 of shaft 50 in the rotational direction. The restricting surface 780 surrounds the third portion 530 of the shaft 50 in the rotational direction. It can be said that the cam surface 720 and the restricting surface 780 are annular curved surfaces.

As shown in FIGS. 8, 16, etc., the restricting surface 780 includes, for example, a plurality of concave surfaces 781 having the same shape (also referred to as a first concave surface 781) and a plurality of concave surfaces 782 having the same shape. Also referred to as a second concave curved surface 782). In this example, the regulation surface 780 has, for example, two concave curved surfaces 781 and two concave curved surfaces 782 .

One first concave curved surface 781, one second concave curved surface 782, the other first concave curved surface 781, and the other second concave curved surface 782 are arranged in this order in the rotation direction. One first concave curved surface 781 is connected to two second concave curved surfaces 782 on both sides thereof. The other first concave curved surface 781 is connected to two second concave curved surfaces 782 on both sides thereof. In the direction of rotation, one first concave curved surface 781 is separated from the other first concave curved surface 781 by 180°, and one second concave curved surface 782 is separated from the other second concave curved surface 782 by 180°. be. The two first concave surfaces 781 face each other, and the two second concave surfaces 782 face each other.

Each first concave curved surface 781 is curved according to the outer peripheral surface of the third portion 530 of the shaft 50 and faces the outer peripheral surface. In the drawings of the present application, it appears that the first concave curved surface 781 and the outer peripheral surface of the third portion 530 are in contact with each other, but there is a slight gap between the first concave curved surface 781 and the outer peripheral surface of the third portion 530. gap exists. In the rotational direction, when the inner case 60 (in other words, the liner 70) and the shaft 50 are in a positional relationship such that the two openings 531a of the shaft 50 face the two first concave curved surfaces 781 respectively, the two openings 531a are substantially closed by the two first concave curved surfaces 781 respectively. As a result, the restricting surface 780 restricts oil from flowing into and out of the shaft oil space 580 through each opening 531a. The partial oil space 581 is generally connected to the space outside the shaft 50 in the oil chamber 600 only through the openings 531a. The inflow and outflow of oil to and from the oil space 581 is regulated. Hereinafter, a state in which oil is restricted from flowing into and out of the shaft oil space 580 through each opening 531a (in other words, a state in which oil is restricted from flowing into and out of the partial oil space 581) may be referred to as a restricted state. .

Each second concave curved surface 782 is curved according to the outer peripheral surface of the third portion 530 of the shaft 50 and faces the outer peripheral surface. A relatively large gap exists between the second concave curved surface 782 and the outer peripheral surface of the third portion 530 . As shown in FIG. 8, when the inner case 60 and the shaft 50 are in a positional relationship in the rotational direction such that the two openings 531a of the shaft 50 face the two second concave curved surfaces 782, each opening 531a is far away from the inner peripheral surface 710 of the liner 70 . As a result, the oil in the oil chamber 600 can relatively freely flow into and out of the shaft oil space 580 through each opening 531a. In other words, the flow of oil into and out of the shaft oil space 580 through each opening 531a is not restricted. In other words, the flow of oil into and out of the partial oil space 581 is not restricted. Hereinafter, a state in which the inflow and outflow of oil to the shaft oil space 580 from each opening 531a is not restricted (in other words, a state in which the inflow and outflow of oil to the partial oil space 581 is not restricted) may be referred to as a non-restricted state. be.

In the restricted state, entry and exit of each sphere 100 into and out of the shaft oil space 580 is restricted. In the regulated state, since oil is regulated from flowing into and out of the partial oil space 581 included in the shaft oil space 580, each sphere 100 becomes difficult to move. As a result, the movement of each sphere 100 into and out of the shaft oil space 580 is restricted. On the other hand, in the non-restricted state, entry and exit of each sphere 100 with respect to the shaft oil space 580 is not restricted.

The cam surface 720 generates torque on the shaft 50 when the inner case 60 is rotationally driven and the inner case 60 is rotating relative to the shaft 50, as shown in FIGS. It has a plurality of concave curved surfaces 730 for aligning. The plurality of concave curved surfaces 730 have, for example, the same shape. In this example, the cam surface 720 has two concave curved surfaces 730, for example. One concave curved surface 730 is located 180° away from the other concave curved surface 730 in the rotational direction. The two concave surfaces 730 face each other.

The cam surface 720 further has two connecting surfaces 740 connecting the two concave curved surfaces 730 . One connecting surface 740 connects one end of one concave curved surface 730 and one end of the other concave curved surface 730 in the rotational direction. The other connecting surface 740 connects the other end of one concave curved surface 730 and the other end of the other concave curved surface 730 in the rotational direction.

Each concave curved surface 730 includes a partial area 731 (also referred to as a first partial area 731), a partial area 732 (also referred to as a second partial area 732), and a partial area 733 (also referred to as a third partial area 733). Each of the partial regions 731, 732, 733 is, for example, a concave curved surface. Partial regions 732 and 733 have, for example, the same shape as each other. The second partial area 732, the first partial area 731, and the third partial area 733 are arranged in this order in the clockwise rotation direction. In other words, the third partial area 733, the first partial area 731, and the second partial area 732 are arranged in this order in the counterclockwise rotation direction. Partial region 731 is connected to partial regions 732 and 733 .

In the direction of rotation, the first partial area 731 of one concave curved surface 730 is located 180° apart from the first partial area 731 of the other concave curved surface 730 . In the direction of rotation, the second partial area 732 of one concave curved surface 730 is located 180° apart from the second partial area 732 of the other concave curved surface 730 . In the direction of rotation, the third partial area 733 of one concave curved surface 730 is located 180° apart from the third partial area 733 of the other concave curved surface 730 .

As shown in FIG. 17, the first partial region 731 forms a concave curve 731a (also referred to as a first concave curve 731a) in a cross-sectional view (also referred to as a vertical cross-sectional view) perpendicular to the rotation axis CA of the inner case 60. . The rotation axis CA of the inner case 60 coincides with the central axis (in other words, rotation axis) of the shaft 50 . The second partial region 732 forms a concave curve 732a (also referred to as a second concave curve 732a) in a vertical cross-sectional view. The third partial region 733 forms a concave curve 733a (also referred to as a third concave curve 733a) in a vertical cross-sectional view. The concave curve 731a is connected to the concave curves 732a and 733a.

The first concave curve 731a and the second concave curve 732a are tangentially continuous, for example. The first concave curve 731a and the third concave curve 733a are tangentially continuous, for example. When two curves are connected, if the line tangent to one curve at the point of connection with the other curve coincides with the line tangent to the other curve at the point of connection to the other curve, then the two curves are It is said to be tangent continuous. In other words, when two curves are connected, if the tangent line of one curve at the endpoint of the other curve coincides with the tangent line of the other curve at the endpoint of the other curve, then the two curves It is said to be tangent continuous. Tangent continuity is also called G1 continuity.

Each of the concave curves 731a, 732a, 733a is, for example, an arc of a perfect circle. The radius of curvature of the first concave curve 731a is, for example, greater than the radius of curvature of the second concave curve 732a and the third concave curve 733a. The radii of curvature of the second concave curve 732a and the third concave curve 733a are, for example, the same. The center of curvature of the first concave curve 731a is located on the rotation axis CA of the inner case 60, for example. It can also be said that the center of curvature of the first concave curve 731 a is positioned on the rotation axis of the shaft 50 .

In this example, since the center of curvature of the first concave curve 731a is positioned on the rotation axis CA, the distance d1 between each point on the first concave curve 731a and the rotation axis CA is constant in a vertical cross-sectional view. Become. The distance d1 can also be said to be the distance between a certain point on the first partial region 731 and the rotation axis CA in a vertical cross-sectional view. The first concave curve 731 a curves along the rotation direction of the shaft 50 .

On the other hand, the centers of curvature of the second concave curve 732a and the third concave curve 733a are not located on the rotation axis CA. In a vertical cross-sectional view, the distance d2 between a point on the second concave curve 732a and the rotation axis CA increases as the point approaches the first concave curve 731a. In other words, the distance d2 between a point on the second concave curve 732a and the rotation axis CA in a vertical cross-sectional view is smaller as the point is farther from the first concave curve 731a. Further in other words, the distance d2 between a certain point on the second partial area 732 and the rotation axis CA in the vertical cross-sectional view becomes smaller as the certain point is farther from the first partial area 731 . Similarly, in a vertical cross-sectional view, the distance d3 between a point on the third concave curve 733a and the rotation axis CA becomes smaller as the point is farther from the first concave curve 731a. In other words, the distance d3 between a certain point on the third partial area 733 and the rotation axis CA in the vertical cross-sectional view becomes smaller as the certain point is farther from the first partial area 731 .

Further, since the second concave curve 732a and the first concave curve 731a are tangentially continuous, the distance d2 between the end point of the second concave curve 732a on the first concave curve 731a side and the rotation axis CA is It coincides with the distance d1 between the end point of the first concave curve 7321 on the second concave curve 732a side and the rotation axis CA. Therefore, the distance d2 between a certain point on the second partial area 732 and the rotation axis CA in a vertical cross-sectional view gradually becomes smaller than the distance d1 as the certain point moves away from the first partial area 731. go.

Similarly, since the third concave curve 733a and the first concave curve 731a are tangentially continuous, the distance d2 between the end point of the third concave curve 733a on the first concave curve 731a side and the rotation axis CA is It matches the distance d1 between the end point of the first concave curve 7321 on the side of the third concave curve 733a and the rotation axis CA. Therefore, the distance d2 between a certain point on the third partial area 733 and the rotation axis CA in a vertical cross-sectional view gradually becomes smaller than the distance d1 as the certain point moves away from the first partial area 731. go.

The first partial region 731 forms a concave curve 731b (see FIG. 15) in a cross-sectional view (also referred to as an axial cross-sectional view) of the inner case 60 along the rotation axis CA. The concave curve 731b (also referred to as the fourth concave curve 731b) is, for example, an arc of a perfect circle. The fourth concave curve 731b is curved along a spherical surface forming the surface of the spherical body 100, for example. Specifically, the fourth concave curve 731b is curved along a partial spherical surface formed by the surface of a portion of the sphere 100 that protrudes from the shaft 50 in the form of a spherical segment. The radius of curvature of the fourth concave curve 731b matches the radius of the sphere 100, for example. In other words, the radius of curvature of the fourth concave curve 731b matches the radius of the spherical surface forming the surface of the sphere 100 . Furthermore, in other words, the radius of curvature of the fourth concave curve 731b matches the radius of curvature of the partial spherical surface formed by the surface of the portion of the sphere 100 that protrudes from the shaft 50 in the form of a spherical segment. For example, the fourth concave curve 731b is in contact with the sphere 100 as a whole.

Similarly, the second partial region 732 forms a concave curve (also referred to as a fifth concave curve) in axial cross-sectional view. The fifth concave curve is, for example, an arc of a perfect circle. The fifth concave curve, like the fourth concave curve 731b, is curved along the spherical surface forming the surface of the sphere 100, for example. The radius of curvature of the fifth concave curve matches the radius of the sphere 100, for example. The fifth concave curve, for example, contacts the sphere 100 as a whole.

Similarly, the third partial region 733 forms a concave curve (also referred to as a sixth concave curve) in axial cross-sectional view. The sixth concave curve is, for example, an arc of a perfect circle. The sixth concave curve is, for example, curved along the spherical surface forming the surface of the sphere 100, like the fourth concave curve 731b. The radius of curvature of the sixth concave curve matches the radius of the sphere 100, for example. The sixth concave curve, for example, contacts the sphere 100 as a whole.

In the torque generator 40 having the above configuration, when the inner case 60 is rotationally driven by the motor 5 and no load is applied to the shaft 50, or when the load applied to the shaft 50 is small, , the inner case 60 and the shaft 50 rotate together. On the other hand, when the inner case 60 is rotationally driven by the motor 5 and the load applied to the shaft 50 is large, the rotation of the shaft 50 is restricted and the inner case 60 moves relative to the shaft 50. rotates. The torque generator 40 can generate a large torque on the shaft 50 when the inner case 60 rotates relative to the shaft 50 . As a result, a large torque is generated in the tip tool 2, and the torque performance of the oil pulse tool 1 is improved.

Hereinafter, a state in which the inner case 60 is driven to rotate clockwise and rotates relative to the shaft 50 may be referred to as a clockwise rotation state. Also, the state in which the inner case 60 is driven to rotate counterclockwise by the motor 5 and rotates relative to the shaft 50 is sometimes referred to as a counterclockwise rotation state.

When the inner case 60 is rotated clockwise, the spherical body 100 is connected to the connecting surface 740 on one side, the third partial area 733 of the concave curved surface 730 on the one side, the first partial area 731, the second partial area 732, and the connecting surface on the other side. The surface 740 , the third partial area 733 , the first partial area 731 , and the second partial area 732 of the concave curved surface 730 come into sliding contact with the cam surface 720 in this order and return to the one connecting surface 740 .

On the other hand, when the inner case 60 is rotated counterclockwise, the sphere 100 is rotated on one connecting surface 740, on one concave curved surface 730, on the second partial area 732, the first partial area 731, and the third portion. The area 733 , the other connecting surface 740 , the second partial area 732 , the first partial area 731 , and the third partial area 733 of the other concave curved surface 730 come into sliding contact with the cam surface 720 in this order and return to the one connecting surface 740 . .

18 to 25 are schematic diagrams showing an example of how the inner case 60 rotates clockwise and rotates relative to the shaft 50. FIG. 18 to 25, an example of a cross-sectional view taken along line AA in FIG. 6 is shown on the left side, and an example of a cross-sectional view taken along line BB of FIG. 6 is shown on the right side. In the examples of FIGS. 18 to 25, one sphere 100 is designated as sphere 100a, and the other sphere 100 is designated as sphere 100b so that the state of rotation of inner case 60 can be easily understood. Similarly, in the examples of FIGS. 18 to 25, the two concave curved surfaces 730 are concave curved surfaces 730a and 730b, respectively, and the two connecting surfaces 740 are connecting surfaces 740a and 740b, respectively.

In the state of FIG. 18, the spherical bodies 100a and 100b are in sliding contact with the first partial regions 731 of the concave curved surfaces 730a and 730b of the cam surface 720, respectively. Also, the two openings 531a of the third portion 530 of the shaft 50 face the two second concave curved surfaces 782 of the restricting surface 780, respectively. In the state of FIG. 18, the torque generating device 40 is in a non-restricted state in which the inflow and outflow of oil is not restricted.

As described above, the distance d1 between each point on the first partial region 731 and the rotation axis CA of the inner case 60 in vertical cross-sectional view is constant. Therefore, when the sphere 100 is in sliding contact with the first partial region 731, the amount of projection of the sphere 100 from the shaft oil space 580 (in other words, the amount of projection of the sphere 100 from the shaft 50) is constant. Therefore, when the spherical body 100 is in sliding contact with the first partial region 731, the contact resistance between the spherical body 100 and the cam surface 720 is constant. As the inner case 60 rotates relative to the shaft 50 , the ball 100 rotates and comes into sliding contact with the cam surface 720 .

When the inner case 60 rotates clockwise from the state of FIG. 18, the two openings 531a of the shaft 50 come to face the two first concave curved surfaces 781 of the restricting surface 780, respectively, as shown in FIG. , the torque generator 40 is in a regulated state in which the inflow and outflow of oil is regulated. In the state of FIG. 19, the spheres 100a and 100b are in contact with the first partial regions 731 of the two concave curved surfaces 730a and 730b, respectively. In this example, for example, the torque generator 40 changes from the non-restricted state to the restricted state immediately before the sliding contact destination of the ball 100 moves from the first partial region 731 to the second partial region 732 . The timing at which the torque generator 40 changes from the non-restricted state to the restricted state is not limited to this example. For example, when the spherical body 100 is in sliding contact with the first partial region 731, the torque generator 40 may change from the non-restricted state to the restricted state. In this case, the torque generating device 40 may change from the non-restricted state to the restricted state immediately before the sliding contact destination of the ball 100 changes from the first partial region 731 to the second partial region 732 .

When the inner case 60 rotates clockwise from the state shown in FIG. 19, the sliding contact destination of each ball 100 changes from the first partial area 731 to the second partial area 732 as shown in FIG. When the sphere 100 is in contact with the second partial area 732, the torque generator 40 is in the regulated state. Therefore, when the spherical bodies 100 are in contact with the second partial region 732, the spherical bodies 100 are restricted from entering and exiting the shaft oil space 580. As shown in FIG. That is, when sphere 100 is in contact with second partial region 732, movement of sphere 100 is restricted.

As described above, the distance d2 between a point on the second partial area 732 and the rotation axis CA in a vertical cross-sectional view gradually becomes smaller than the distance d1 as the point moves away from the first partial area 731. To go. On the other hand, when the sphere 100 is in contact with the second partial region 732, the movement of the sphere 100 into and out of the shaft oil space 580 is restricted. Therefore, when the sphere 100 slides on the second partial region 732, the force of the cam surface 720 pushing the sphere 100 toward the shaft oil space 580 increases, and the contact resistance between the cam surface 720 and the sphere 100 increases. Become. In this case, when the load applied to the shaft 50 is small, the shaft 50 and the inner case 60 rotate together clockwise while the sphere 100 is in contact with the second partial region 732 . On the other hand, when the load applied to the shaft 50 is large, the clockwise rotation of the shaft 50 is restricted, the inner case 60 rotates relative to the shaft 50, and the sphere 100 comes into sliding contact with the second partial region 732. .

A slight gap exists between the opening 531 a of the shaft 50 and the first concave curved surface 781 of the liner 70 in the restricted state. Therefore, even in the restricted state, some oil in the shaft oil space 580 can flow into and out of the shaft 50 through the opening 531a. In other words, the sphere 100 can move somewhat even in the restricted state. As a result, when the inner case 60 attempts to rotate further clockwise after the sliding contact destination of the sphere 100 changes from the first partial area 731 to the second partial area 732 , the spherical body 100 moves toward the second partial area of the cam surface 720 . Depending on the shape of 732 , it can move into shaft 50 and come into sliding contact with second partial region 732 . That is, the inner case 60 can rotate relative to the shaft 50 so that the ball 100 can come into sliding contact with the second partial region 732 . Since the movement of the sphere 100 is restricted when the sphere 100 contacts the second partial area 732, when the inner case 60 rotates relative to the shaft 50 and the sphere 100 slides on the second partial area 732, the movement of the sphere 100 is restricted. , the force with which the cam surface 720 pushes the ball 100 toward the shaft oil space 580 increases. This increases the contact resistance between the cam surface 720 and the sphere 100 . The two spheres 100 slidably contact the second partial regions 732 of the two concave curved surfaces 730 at the same timing. When the ball 100 is in sliding contact with the second partial region 732 , the farther the sliding contact point of the ball 100 is from the first partial region 731 , the smaller the projection amount of the ball 100 from the shaft oil space 580 .

When the cam surface 720 presses the ball 100 toward the shaft oil space 580 in the restricted state, the pressure of the oil in the partial oil space 581 increases. Therefore, when the spherical body 100 is in sliding contact with the second partial area 732, the oil in the partial oil space 581 is at high pressure.

Thus, when the ball 100 is in sliding contact with the second partial region 732, the force of the cam surface 720 pushing the ball 100 toward the shaft oil space 580 increases, and the contact resistance between the cam surface 720 and the ball 100 increases. . Therefore, the rotational energy of the inner case 60 is transmitted to the shaft 50 to generate a clockwise torque on the shaft 50 . When the spherical body 100 is in sliding contact with the second partial area 732 , the shaft 50 rotates behind the inner case 60 .

When the inner case 60 rotates further relative to the shaft 50, as shown in FIG. 21, the sliding contact point of the spherical body 100a changes from the second partial region 732 of the concave curved surface 730a to the connecting surface 740a, and the spherical body 100b is changed from the second partial region 732 of the concave curved surface 730b to the connecting surface 740b. In the state of FIG. 21, the torque generator 40 is in the regulated state.

When the inner case 60 further rotates, the sliding contact point of the spherical body 100a changes from the connecting surface 740a to the third partial region 733 of the concave curved surface 730b, and the sliding contact point of the spherical body 100b changes from the connecting surface 740b to the third portion of the concave curved surface 730a. Change to area 733 . When the inner case 60 rotates further, as shown in FIG. 22, the sliding contact destination of each ball 100 changes from the third partial area 733 to the first partial area 731 . In the state of FIG. 22, the two openings 531a of the shaft 50 face the two second concave curved surfaces 782 of the restricting surface 780, respectively. In this example, for example, immediately after the sliding contact destination of the ball 100 changes from the third partial area 733 to the first partial area 731, the torque generating device 40 changes from the regulated state to the non-regulated state. When the torque generating device 40 changes from the regulated state to the non-regulated state, the pressure of the oil in the partial oil space 581, which has been at high pressure, decreases.

Note that the timing at which the torque generator 40 changes from the restricted state to the non-restricted state is not limited to the above example. For example, when the ball 100 is in sliding contact with the connection surface 740, the torque generator 40 may change from the regulated state to the non-regulated state. Further, when the ball 100 is in sliding contact with the third partial region 733 of the concave curved surface 730, the torque generator 40 may change from the regulated state to the non-regulated state.

As described above, the distance d3 between a certain point on the third partial area 733 and the rotation axis CA in a vertical cross-sectional view gradually decreases as the certain point moves away from the first partial area 731 . Therefore, when the spherical body 100 is in sliding contact with the third partial region 733 , the closer the sliding contact point of the spherical body 100 is to the first partial region 731 , the more the spherical body 100 protrudes from the shaft oil space 580 (in other words, from the shaft 50 ). the amount of protrusion) increases.

As the inner case 60 rotates further, the sliding contact destination of each ball 100 changes from the first partial area 731 to the second partial area 732 as shown in FIG. In the state of FIG. 23, the torque generating device 40 is in the regulated state. When spherical body 100 is in sliding contact with second partial region 732 in the restricted state, cam surface 720 presses spherical body 100 toward shaft oil space 580 , and clockwise torque is generated in shaft 50 . The shaft 50 rotates behind the inner case 60 .

When the inner case 60 rotates further, as shown in FIG. 24, the sliding contact point of the spherical body 100a changes from the second partial region 732 of the concave curved surface 730b to the connecting surface 740b, and the sliding contact point of the spherical body 100b changes to the concave curved surface 730a. from the second partial region 732 to the connecting surface 740a. In the state of FIG. 24, the torque generator 40 is in the regulated state.

When the inner case 60 further rotates, the sliding contact point of the spherical body 100a changes from the connecting surface 740b to the third partial area 733 of the concave curved surface 730a, and the sliding contact point of the spherical body 100b changes from the connecting surface 740a to the third portion of the concave curved surface 730b. Change to area 733 . When the inner case 60 rotates further, as shown in FIG. 25, the sliding contact point of each sphere 100 changes from the third partial area 733 to the first partial area 731, and then the inner case 60 moves toward the shaft 50. Rotate 360° relative to each other. Thereafter, the torque generator 40 operates similarly.

As can be understood from the above description, the torque generator 40 applies a pulse to the shaft 50 while the inner case 60 rotates 360° relative to the shaft 50 when the inner case 60 rotates clockwise. torque is generated twice. When the inner case 60 rotates relative to the shaft 50, the oil pressure in the partial oil space 581 changes.

When the inner case 60 rotates counterclockwise, the sphere 100 slides against the third partial region 733 in the restricted state, increasing the contact resistance between the cam surface 720 and the sphere 100 and rotating the shaft 50 counterclockwise. of torque is generated. FIG. 26 is a schematic diagram showing an example of how the inner case 60 rotates counterclockwise from the state shown in FIG. Even when the inner case 60 rotates counterclockwise, in the torque generator 40 , pulse-like torque is applied to the shaft 50 while the inner case 60 rotates 360° relative to the shaft 50 . Occurs twice.

As described above, in this example, when the inner case 60 rotates clockwise and the moving member 100 slides on the second partial region 732 of the cam surface 720 in the restricted state, the cam surface 720 moves the moving member 100. The force of pushing toward the shaft oil space 580 increases. Thereby, the contact resistance between the cam surface 720 and the moving member 100 is increased, and the rotational energy of the inner case 60 can be sufficiently transmitted to the shaft 50 . As a result, the clockwise torque generated in the shaft 50 can be increased.

In this example, when the inner case 60 rotates counterclockwise and the moving member 100 slides against the third partial region 733 of the cam surface 720 in the restricted state, the cam surface 720 moves the moving member 100 toward the shaft oil. The force of pushing toward the space 580 increases. Thereby, the contact resistance between the cam surface 720 and the moving member 100 is increased, and the rotational energy of the inner case 60 can be sufficiently transmitted to the shaft 50 . As a result, counterclockwise torque generated in the shaft 50 can be increased.

Further, in this example, a large torque can be generated in the shaft 50 regardless of whether the inner case 60 rotates clockwise or counterclockwise.

In addition, in this example, since torque is generated in the shaft 50 by the sliding contact of the moving member 100 on the cam surface 720, it is quieter than an impact tool in which a hammer hits the anvil to generate torque in the shaft. can be improved.

Further, the cam surface 720 of this example is provided with a plurality of second partial regions 732 for generating a clockwise torque on the shaft 50 . Therefore, while the inner case 60 rotates 360 degrees relative to the shaft 50 , pulsed clockwise torque can be generated multiple times on the shaft 50 . Thereby, for example, the workability of tightening a wood screw can be improved.

Further, the cam surface 720 of this example is provided with a plurality of third partial regions 733 for generating counterclockwise torque on the shaft 50 . Therefore, while the inner case 60 rotates 360 degrees relative to the shaft 50 , it is possible to generate counterclockwise pulsed torque on the shaft 50 multiple times. Thereby, for example, the workability of tightening a wood screw can be improved.

Further, in this example, when the inner case 60 rotates clockwise and the two moving members 100 come into sliding contact with the two second partial regions 732 at the same timing in the restricted state, the cam surface 720 makes two movements. The force pushing the material of the member 100 toward the shaft oil space 580 increases, and clockwise torque is generated in the shaft 50 . Thereby, the load when clockwise torque is generated in the shaft 50 can be distributed to the two moving members 100 . Therefore, wear of the moving member 100 can be reduced.

Further, in this example, when the inner case 60 is rotated counterclockwise and the two moving members 100 are brought into sliding contact with the two third partial regions 733 at the same timing in the regulated state, the cam surface 720 is moved to the two positions. The force pushing the material of the moving member 100 toward the shaft oil space 580 increases, and counterclockwise torque is generated in the shaft 50 . Thereby, the load when counterclockwise torque is generated in the shaft 50 can be distributed to the two moving members 100 . Therefore, wear of the moving member 100 can be reduced.

Further, in this example, since the ball 100 is in sliding contact with the cam surface 720 while rotating, wear of the ball 100 can be reduced.

Also, in this example, a first concave curve 731a formed by the first partial region 731 in vertical cross-section and a second concave curve 732a formed by the second partial region 732 in vertical cross-section are tangentially continuous. As a result, the first partial area 731 and the second partial area 732 are smoothly connected, so that when the inner case 60 rotates clockwise, the moving member 100 moves from the first partial area 731 to the second partial area. 732 can smoothly come into sliding contact with the cam surface 720 . Therefore, noise is less likely to be generated when the moving member 100 starts sliding contact with the second partial region 732 . As a result, quietness is improved.

Further, in this example, a first concave curve 731a formed by the first partial region 731 in vertical cross-section and a third concave curve 733a formed by the third partial region 733 in vertical cross-section are tangentially continuous. As a result, the first partial area 731 and the third partial area 733 are smoothly connected, so that the moving member 100 moves from the first partial area 731 to the third partial area when the inner case 60 rotates counterclockwise. The area 733 can be smoothly brought into sliding contact with the cam surface 720 . Therefore, noise is less likely to be generated when the moving member 100 starts sliding contact with the third partial region 733 . As a result, quietness is improved.

Further, in this example, the radius of curvature of the first concave curve 731a formed by the first partial region 731 in vertical cross-section is larger than the radius of curvature of the second concave curve 732a formed by the second partial region 732 in vertical cross-section. It's getting bigger. That is, when viewed in the direction of rotation, the first partial area 731 curves more gently than the second partial area 732 . Thereby, as in this example, the length of the first partial region 731 in the rotational direction can be made longer than the length of the second partial region 732 in the rotational direction.

Here, consider a case where the length of the first partial region 731 in the direction of rotation is small. In this case, when the inner case 60 rotates clockwise and the rotation speed of the inner case 60 is high, the moving member 100 does not come into sliding contact with the first partial region 731 and is moved out of the opening 541 a of the shaft 50 . There is a possibility that sliding contact with the second partial region 732 will start in a non-protruding state.

On the other hand, as in this example, when the length of the second partial region 732 in the rotational direction is large, the moving member 100 is moved relative to the first partial region 731 regardless of the rotational speed of the inner case 60 . can be brought into slidable contact with each other. Therefore, the moving member 100 can sufficiently protrude from the opening 541 a of the shaft 50 before the moving member 100 starts sliding contact with the second partial region 732 . Thereby, the moving member 100 can be slidably contacted with the second partial region 732 in a state where the moving member 100 is sufficiently protruded from the shaft 50 . Therefore, when moving member 100 slides on second partial region 732, the contact resistance between cam surface 720 and moving member 100 can be increased more reliably. As a result, the clockwise torque generated in the shaft 50 can be increased more reliably.

Further, in this example, the curvature radius of the first concave curve 731a formed by the first partial region 731 in vertical cross section is larger than the curvature radius of the third concave curve 733a formed by the third partial region 733 in vertical cross section. It's getting bigger. Thereby, as in this example, the length of the first partial region 731 in the rotational direction can be made longer than the length of the third partial region 733 in the rotational direction. Therefore, when the inner case 60 rotates counterclockwise, the moving member 100 should be sufficiently protruded from the opening 541 a of the shaft 50 before the moving member 100 starts sliding contact with the third partial region 733 . can be done. As a result, the counterclockwise torque generated in the shaft 50 can be increased more reliably.

The radius of curvature of the second concave curve 732 a formed by the second partial region 732 in vertical cross-section may be larger than the radius of curvature of the sphere 100 . In other words, the radius of curvature of the second concave curve 732a may be larger than the radius of the spherical surface forming the surface of the sphere 100. FIG. Furthermore, in other words, the radius of curvature of the second concave curve 732a may be larger than the radius of curvature of the partial spherical surface formed by the surface of the protruding portion of the sphere 100 protruding from the shaft 50 . As described above, when the radius of curvature of the second concave curve 732a is large, that is, when the second partial region 732 bends gently in the rotational direction, the inner case 60 rotates clockwise and moves. Sound is less likely to occur when the member 100 slides on the second partial region 732 . Therefore, quietness is further improved.

Similarly, the radius of curvature of the third concave curve 733a formed by the third partial region 733 in a vertical cross-sectional view may be larger than the radius of curvature of the sphere 100. FIG. In this case, noise is less likely to be generated when the inner case 60 rotates counterclockwise and the moving member 100 comes into sliding contact with the third partial region 733 . Therefore, quietness is further improved.

The radius of curvature of the second concave curve 732 a formed by the second partial region 732 in vertical cross-section may be smaller than the radius of curvature of the sphere 100 . As described above, when the radius of curvature of the second concave curve 732a is small, that is, when the second partial region 732 bends sharply in the direction of rotation, the inner case 60 rotates clockwise to form a spherical shape. The force with which the cam surface 720 pushes the ball 100 toward the shaft oil space 580 when the ball 100 is in sliding contact with the second partial region 732 can be increased. As a result, the clockwise torque generated in the shaft 50 can be further increased.

Similarly, the radius of curvature of the third concave curve 733 a formed by the third partial region 733 in vertical cross-section may be smaller than the radius of curvature of the sphere 100 . In this way, when the radius of curvature of the third concave curve 733 a is small, the cam surface 720 moves the sphere 100 against the shaft when the inner case 60 rotates counterclockwise and the sphere 100 slides against the third partial region 733 . The force for pushing toward the oil space 580 side can be increased. As a result, the counterclockwise torque generated in the shaft 50 can be further increased.

The radius of curvature of the second concave curve 732 a may be the same as the radius of curvature of the sphere 100 . Also, the radius of curvature of the third concave curve 733 a may be the same as the radius of curvature of the sphere 100 .

In the above example, as shown in FIG. 15 , the fourth concave curve 731b formed by the first partial region 731 in axial cross-section curves along the spherical surface forming the surface of the spherical body 100 . Thereby, the contact area between the sphere 100 and the first partial region 731 can be increased. Therefore, wear of the sphere 100 can be reduced. Similarly, the fifth concave curve formed by the second partial region 732 in axial cross section curves along the spherical surface forming the surface of the spherical body 100 . Thereby, the contact area between the sphere 100 and the second partial region 732 can be increased. Therefore, wear of the sphere 100 can be reduced. Similarly, the sixth concave curve formed by the third partial region 733 in axial cross section curves along the spherical surface forming the surface of the spherical body 100 . Thereby, the contact area between the sphere 100 and the third partial region 733 can be increased. Therefore, wear of the sphere 100 can be reduced.

In this example, as described above, the oil in oil space 580 may be at high pressure. Specifically, the oil in the partial oil space 581 may be at high pressure. When the oil is at high pressure, the temperature of the oil increases and the viscosity of the oil may decrease. When the viscosity of the oil in the partial oil space 581 decreases, the oil may leak out of the shaft 50 from places other than the opening 531 a of the third portion 530 of the shaft 50 . For example, oil may leak out of the shaft 50 from the opening 541 a of the fourth portion 540 of the shaft 50 . As a result, the torque generated in shaft 50 may decrease.

Therefore, the amount of oil outside the shaft 50 in the oil chamber 600 may be greater than the amount of oil in the shaft oil space 580 . This makes it difficult for the temperature of the oil in the partial oil space 581, which becomes high pressure when torque is generated in the shaft 50, to rise. Therefore, the viscosity of the oil in the partial oil space 581 is less likely to decrease, and the amount of oil that unintentionally leaks out of the shaft 50 is reduced. As a result, the torque generated in shaft 50 can be increased.

The configuration of the oil pulse tool 1 is not limited to the above example. The configuration of the unit 10 is not limited to the above example. The configuration of the torque generator 40 is not limited to the above example. For example, the torque generator 40 may generate pulse-shaped torque to the shaft 50 three times or more while the inner case 60 rotates 360 degrees relative to the shaft 50 . An example of a torque generator 40 (also referred to as a torque generator 40A) capable of generating pulse-shaped torque three times will be described below.

FIG. 27 is a schematic diagram showing an example of the cross-sectional structure of the torque generator 40A. FIG. 28 is a schematic diagram showing an example of a cross-sectional structure taken along line HH in FIG. FIG. 29 is a schematic diagram showing an example of a cross-sectional structure taken along line II of FIG. 6, the torque generator 40A has only one set of a moving member 100, a mounting member 101 and an O-ring 102, with the shaft 50 and the liner 70 being changed. In other words, the torque generator 40A has only one moving member 100, one mounting member 101 and one O-ring 102, respectively.

30 and 31 are schematic perspective views showing the appearance of the shaft 50 (also referred to as shaft 50A) provided in the torque generator 40A. FIG. 32 is a schematic diagram showing an example of the shaft 50A viewed from arrow Y in FIG. FIG. 33 is a schematic diagram showing an example of a cross-sectional structure taken along line JJ in FIG. FIG. 34 is a schematic diagram showing an example of a cross-sectional structure taken along line KK in FIG. FIG. 35 is a schematic perspective view showing the appearance of a liner 70 (also referred to as liner 70A) provided in torque generator 40A. FIG. 36 is a schematic diagram showing an example of how the liner 70A is viewed from the opening 701 side. FIG. 37 is a schematic diagram showing an example of a cross-sectional structure taken along line LL in FIG. FIG. 38 is a schematic diagram showing an example of a cross-sectional structure taken along line MM in FIG. FIG. 39 is a schematic diagram showing an example of a cross-sectional structure taken along line NN in FIG.

As shown in FIGS. 27, 28, 30 to 34, etc., in the torque generator 40A, for example, one end of the hole 531 (also referred to as hole 531A) of the shaft 50A is closed. Therefore, hole 531A has one opening 531a. Also, one end of the hole 541 (also referred to as hole 541A) of the shaft 50A is closed. Therefore, hole 541A has one opening 541a. In the rotational direction of the shaft 50A, the opening 541a of the hole 541A is located 180 degrees apart from the opening 531a of the hole 531A. In the torque generator 40A, one end of the spring 103 is engaged with the mounting member 101, and the other end of the spring 103 is in contact with the bottom wall 541b of the hole 541 closed at one end. The sphere 100 can move in and out of the shaft oil space 580 through the opening 541a of the hole 541A.

The oil in the oil chamber 600 can flow into and out of the shaft oil space 580A through the opening 531a of the hole 531A of the third portion 530. As shown in FIG. The restricting surface 780 of the liner 70 restricts oil from flowing into and out of the shaft oil space 580A from the opening 531a of the hole 531A when the inner case 60 and the shaft 50A are in a predetermined positional relationship in the rotational direction of the inner case 60.

As shown in FIGS. 27, 29, 35 to 38, etc., the regulating surface 780 of the liner 70A includes, for example, three first concave curved surfaces 781 and three second concave curved surfaces 782. As shown in FIG. In the direction of rotation, the first concave surfaces 781 and the second concave surfaces 782 are alternately arranged. In the direction of rotation, the first concave curved surface 781 is connected to the second concave curved surfaces 782 on both sides thereof. In other words, in the direction of rotation, the second concave curved surface 782 is connected to the first concave curved surfaces 781 on both sides thereof. In the direction of rotation, the three first concave surfaces 781 are arranged at intervals of 120°, for example. In the direction of rotation, the three second concave curved surfaces 782 are arranged at intervals of 120°, for example.

In the torque generator 40A, the inner case 60 (in other words, the liner 70) and the shaft 50 have a positional relationship in which the opening 531a of the shaft 50 faces at least one of the three first concave curved surfaces 781 in the rotational direction. At this time, the opening 531a is substantially closed by the first concave curved surface 781. As shown in FIG. As a result, the restricting surface 780 restricts the flow of oil into and out of the shaft oil space 580 through the opening 531a. The partial oil space 581 is generally connected to the space outside the shaft 50 in the oil chamber 600 only through the opening 531a. The inflow and outflow of oil to and from the space 581 is restricted. In the torque generator 40A, when the opening 531a faces the first concave curved surface 781, the regulated state is reached.

In the torque generator 40A, when the inner case 60 and the shaft 50 are in a positional relationship in the rotational direction such that the opening 531a of the shaft 50 faces any one of the three second concave curved surfaces 782, the opening 531a is It is far away from the inner peripheral surface 710 of the liner 70 . As a result, the oil in the oil chamber 600 can relatively freely flow into and out of the shaft oil space 580 through the opening 531a. In other words, the inflow and outflow of oil is not regulated. In the torque generator 40A, when the opening 531a faces the second concave curved surface 782, the non-restricted state is reached.

The cam surface 720 of the liner 70A has, for example, three concave curved surfaces 730 and three connecting surfaces 740, as shown in FIGS. In the direction of rotation, the concave surfaces 730 and the connecting surfaces 740 are alternately arranged. Each connecting surface 740 is connected to two concave curved surfaces 730 on both sides thereof. In the direction of rotation, the three concave surfaces 730 are arranged at intervals of 120°, and the three connecting surfaces 740 are arranged at intervals of 120°.

In the rotational direction, the first partial regions 731 of the three concave curved surfaces 730 are arranged at intervals of 120°. In the direction of rotation, the second partial regions 732 of the three concave curved surfaces 730 are arranged at intervals of 120°. In the direction of rotation, the third partial regions 733 of the three concave surfaces 730 are arranged at intervals of 120°.

40 to 47 are schematic diagrams showing an example of how the inner case 60 is driven to rotate clockwise and rotates relative to the shaft 50A. 40 to 47, an example of a cross-sectional view taken along line HH in FIG. 27 is shown on the left side, and an example of a cross-sectional view taken along line II of FIG. 27 is shown on the right side. In the examples of FIGS. 40 to 47, one of the three concave curved surfaces 730 is a concave curved surface 730a, and the concave curved surface 730 next to the concave curved surface 730a in the counterclockwise direction is a concave curved surface 730a for easy understanding of the rotation of the shaft 50A. A concave surface 730b is formed, and the next concave surface 730 is a concave surface 730c. In the direction of rotation, the connecting surface 740 between the concave curved surfaces 730a and 730c is called the connecting surface 740a, the connecting surface 740 between the concave curved surfaces 730a and 730b is called the connecting surface 740b, and the connecting surface between the concave curved surfaces 730b and 730c. 740 is a connecting surface 740c.

In the torque generating device 40A, when the inner case 60 rotates clockwise, the sphere 100 has a connection surface 740a, a third partial area 733, a first partial area 731, a second partial area 732 of the concave surface 730a, and a connecting surface 740a. Surface 740b, third partial area 733, first partial area 731, second partial area 732 of concave curved surface 730b, connecting surface 740c, third partial area 733, first partial area 731, second partial area 732 of concave curved surface 730c , and return to the connecting surface 740a.

On the other hand, when the inner case 60 is rotated counterclockwise, the sphere 100 rotates the connection surface 740a, the second partial area 732 of the concave curved surface 730c, the first partial area 731, the third partial area 733, and the connecting surface 740c. Surface 740c, second partial area 732, first partial area 731, third partial area 733 of concave curved surface 730b, connecting surface 740b, second partial area 732, first partial area 731, third partial area 733 of concave curved surface 730a , and return to the connecting surface 740a.

40, the ball 100 is in sliding contact with the first partial region 731 of the concave curved surface 730a of the cam surface 720. In the state shown in FIG. Also, the opening 531 a of the shaft 50 faces the second concave curved surface 782 of the restricting surface 780 . In the state of FIG. 40, the torque generator 40A is in a non-regulated state.

When the inner case 60 rotates clockwise from the state shown in FIG. 40, the opening 531a of the shaft 50 faces the first concave curved surface 781 of the restricting surface 780 as shown in FIG. becomes regulated. In the state of FIG. 41, the sphere 100 is in contact with the first partial region 731 of the concave curved surface 730a. In this example, the torque generator 40A changes from the non-restricted state to the restricted state, for example, immediately before the sliding contact point of the ball 100 moves from the first partial area 731 to the second partial area 732 . As described above, the timing at which the torque generator 40A changes from the non-restricted state to the restricted state is not limited to this.

When the inner case 60 rotates clockwise from the state of FIG. 41, the sliding contact point of the sphere 100 changes from the first partial area 731 to the second partial area 732 as shown in FIG. When the spherical body 100 is in contact with the second partial area 732, the torque generator 40A is in the regulated state. As described above, when the sphere 100 is in sliding contact with the second partial region 732 in the restricted state, the cam surface 720 presses the sphere 100 toward the shaft oil space 580 side, and clockwise torque is generated in the shaft 50 . . At this time, the shaft 50 rotates behind the inner case 60 .

As the inner case 60 rotates further, as shown in FIG. 43, the sliding contact point of the spherical body 100 changes from the second partial region 732 of the concave curved surface 730a to the connecting surface 740b. In the state of FIG. 43, the torque generator 40A is in the regulated state.

When the inner case 60 rotates further, the sliding contact point of the spherical body 100 changes from the connection surface 740b to the third partial area 733 of the concave curved surface 730b. When the inner case 60 rotates further, the sliding contact point of the ball 100 changes from the third partial area 733 to the first partial area 731 as shown in FIG. In the state of FIG. 44, the opening 535a of the shaft 50 faces the second concave curved surface 782 of the restricting surface 780, and the torque generating device 40A is in a non-restricting state. In this example, for example, immediately after the sliding contact point of the ball 100 changes from the third partial area 733 to the first partial area 731, the torque generating device 40A changes from the restricted state to the non-restricted state. As described above, the timing at which the torque generator 40A changes from the regulated state to the non-regulated state is not limited to this.

When the inner case 60 rotates further, the sliding contact point of the ball 100 changes from the first partial area 731 to the second partial area 732 as shown in FIG. In the state of FIG. 45, the torque generating device 40A is in the regulated state. When the sphere 100 slides against the second partial region 732 of the concave surface 730b in the restricted state, the cam surface 720 presses the sphere 100 toward the shaft oil space 580 side, generating torque in the shaft 50 in the clockwise direction. At this time, the shaft 50 rotates behind the inner case 60 .

As the inner case 60 rotates further, the sliding contact point of the spherical body 100 changes from the second partial region 732 of the concave curved surface 730b to the connecting surface 740c. When the inner case 60 rotates further, the sliding contact point of the spherical body 100 changes from the connection surface 740 to the third partial area 733 of the concave curved surface 730c. As the inner case 60 rotates further, as shown in FIG. 46, the sliding contact point of the spherical body 100 changes from the third partial area 733 to the first partial area 731 of the concave curved surface 730c. As the inner case 60 rotates further, as shown in FIG. 47, the sliding contact point of the spherical body 100 changes from the first partial area 731 to the second partial area 732 of the concave curved surface 730c. In the state of FIG. 47, the torque generating device 40A is in the regulated state. When the sphere 100 slides against the second partial region 732 of the concave curved surface 730c in the restrained state, the force of the cam surface 720 pushing the sphere 100 toward the shaft oil space 580 increases, generating torque in the shaft 50 in the clockwise direction. At this time, the shaft 50 rotates behind the inner case 60 .

As the inner case 60 rotates further, the sliding contact point of the spherical body 100 changes from the second partial region 732 of the concave curved surface 730c to the connecting surface 740a. When the inner case 60 rotates further, the sliding contact point of the spherical body 100 changes from the connection surface 740a to the third partial area 733 of the concave curved surface 730a. As the inner case 60 rotates further, the sliding contact point of the spherical body 100 changes from the third partial area 733 to the first partial area 731 of the concave curved surface 730a. As a result, the inner case 60 rotates 360° relative to the shaft 50 . Thereafter, the torque generator 40A operates similarly.

As can be understood from the above description, in the torque generator 40A, clockwise torque is generated in the shaft 50 when the spherical body 100 slides on the second partial regions 732 of the three concave curved surfaces 730 . When the inner case 60 rotates clockwise, the torque generator 40A generates pulse-like torque on the shaft 50A three times while the inner case 60 rotates 360° relative to the shaft 50A.

When the inner case 60 rotates counterclockwise, the sphere 100 slides against the third partial region 733 in the restricted state, increasing the contact resistance between the cam surface 720 and the sphere 100 and rotating the shaft 50A counterclockwise. of torque is generated. In the torque generator 40A, counterclockwise torque is generated in the shaft 50A when the ball 100 slides on the third partial regions 733 of the three concave curved surfaces 730. As shown in FIG. Even when the inner case 60 rotates counterclockwise, the torque generator 40A applies pulsed torque to the shaft 50A while the inner case 60 rotates 360° relative to the shaft 50A. Generate 3 times.

As in the torque generator 40A, even in the torque generator 40 shown in FIG. good.

Torque generator 40 may not include O-ring 102 . In this case, since the moving member 100 and the mounting member 101 are in contact with the inner peripheral surface of the hole 541, the oil in the partial oil space 581 is less likely to leak out of the shaft 50 through the opening 541a. Further, the torque generating device 40 may not be provided with the mounting member 101 and the end of the spring 103 may be in contact with the moving member 100 . In this case, since the moving member 100 is in contact with the inner peripheral surface of the hole 541, the oil in the partial oil space 581 is less likely to leak out of the shaft 50 through the opening 541a.

As described above, when the inner case 60 rotates relative to the shaft 50, the pressure of the oil in the partial oil space 581 increases and the temperature of the oil may rise. The high-temperature oil in the partial oil space 581 is less likely to flow out of the shaft 50 through the narrow holes 531, and the pressure of the oil in the partial oil space 581 may become higher than necessary. For this reason, it becomes difficult for the moving member 100 to move more than necessary, and there is a possibility that the spherical body 100 cannot properly slide on the cam surface 720 .

Therefore, when the pressure in the partial oil space 581 becomes higher than necessary, the torque generating device 40 automatically causes the oil in the partial oil space 581 to flow out of the shaft 50 to reduce the pressure of the oil. A reducing hydraulic pressure relief mechanism 99 may be provided.

FIG. 48 is a schematic diagram showing an example of a cross-sectional structure of the unit 10 including the torque generator 40 (also referred to as torque generator 40B) having the hydraulic relief mechanism 99. As shown in FIG. FIG. 48 shows how the torque generator 40 shown in FIG. 6 is provided with a hydraulic relief mechanism 99 . The hydraulic relief mechanism 99 may be provided in the torque generator 40 shown in FIG.

The hydraulic relief mechanism 99 includes, for example, a moving pin 990, a fixed member 991 to which the moving pin 990 is fixed, and a spring 992 that biases the fixed member 991 forward. A moving pin 990 , a fixing member 991 and a spring 992 are provided inside the oil chamber 600 . The moving pin 990 has, for example, a substantially cylindrical shape and extends in the front-rear direction. One end of the moving pin 990 is fixed to a fixing member 991 .

Spring 992 is, for example, a compression coil spring, and is provided in oil chamber 600 in a compressed state. The spring 992 can expand and contract in the front-rear direction. One end of the spring 992 is in contact with the fixed member 991 and the other end of the spring 992 is in contact with the inner surface of the planetary carrier 80 . When the pressure of the oil in the partial oil space 581 is small, as shown in FIG. and the rear surface of the centering member 96 .

The hydraulic relief mechanism 99 has holes 993 , 994 , 995 provided in the shaft 50 . Hole 993 extends along the length of shaft 50 . One end of the hole 993 is connected to the hole 541 of the fourth portion 540, and the other end of the hole 993 is open rearward. Hole 993 is connected to partial oil space 581 . The moving pin 990 is inserted from the rear opening of the hole 993 and slides through the hole 993 . A portion of the hole 993 is closed with a moving pin 990 . A hole 993 is provided in the shaft 50 from the fourth portion 540 to the fifth portion 550 .

Holes 994 and 995 are connected to hole 993 and are provided in fifth portion 550 of shaft 50 . Holes 994 and 995 extend along a direction perpendicular to the longitudinal direction of shaft 50 . One ends of holes 994 and 995 are connected to hole 993 . The other ends of the holes 994 and 995 are open and connected to the portion of the oil chamber 600 outside the shaft 50 . Hole 994 is positioned 180° apart from hole 995 in the direction of rotation of shaft 50 . Holes 994 and 995 are filled with oil. Also, the portion of the hole 993 that is not blocked by the moving pin 990 is filled with oil.

When the oil pressure in the partial oil space 581 is low, the openings of the holes 994 and 995 on the side of the hole 993 are blocked by the moving pin 990 as shown in FIG. Therefore, when the pressure of the oil in the partial oil space 581 is low, the oil in the partial oil space 581 is prevented from flowing out of the shaft 50 through the holes 994 and 995 .

On the other hand, when the oil pressure in the partial oil space 581 increases, the moving pin 990 is pushed rearward by the oil pressure. At this time, the spring 992 contracts and the moving pin 990 and the fixing member 991 move rearward. When the pressure of the oil in the partial oil space 581 reaches or exceeds a predetermined value, as shown in FIG. As a result, the oil in the partial oil space 581 flows through the holes 993 , 994 , 995 and out of the shaft 50 . As a result, the pressure of the oil in the partial oil space 581 decreases. When the pressure of the oil in the partial oil space 581 decreases, the biasing force of the spring 992 moves the moving pin 990 and the fixed member 991 forward. When the pressure of the oil in the partial oil space 581 becomes less than a predetermined value, the openings of the holes 994 and 995 on the side of the hole 993 are blocked by the moving pin 990 as shown in FIG. This prevents the oil in the partial oil space 581 from flowing out of the shaft 50 through the holes 994 and 995 .

When such a hydraulic relief mechanism 99 is provided in the torque generator 40, the possibility that the pressure of the oil in the partial oil space 581 becomes higher than necessary is reduced. This makes it difficult for the moving member 100 to move more than necessary, and reduces the possibility that the spherical body 100 cannot properly slide on the cam surface 720 .

In the above example, while the inner case 60 rotates 360° relative to the shaft 50, the pulse-shaped torque is generated multiple times in the shaft 50, but the pulse-shaped torque is generated only once. may In the above example, the pulse-shaped torque is generated in the shaft 50 whether the inner case 60 rotates clockwise or counterclockwise. A pulsed torque need not be generated in the shaft 50 when it rotates clockwise. Also, when the inner case 60 rotates counterclockwise, the shaft 50 does not need to generate pulse-like torque.

Further, the shape of the concave curved surface 730 for generating pulse-like torque on the shaft 50 is not limited to the above example. For example, the second concave curve 732a formed by the second partial region 732 of the concave surface 730 in a vertical cross-sectional view may be an elliptical arc (also referred to as an elliptical arc). Also, the third concave curve 733a formed by the third partial region 733 of the concave curved surface 730 in a vertical cross-sectional view may be an elliptical arc.

FIG. 50 schematically shows an example of a cam surface 720 having an elliptical arc second concave curve 732a (also referred to as a second concave curve 732aa) and an elliptical arc third concave curve 733a (also referred to as a third concave curve 733aa). 1 is a schematic diagram shown in FIG.

Also in the example of FIG. 50, each of the second concave curve 732aa and the third concave curve 733aa is tangentially continuous with the first concave curve 731a, for example. Also, in a vertical cross-sectional view, the distance d2 between a point on the second concave curve 732aa and the rotation axis CA of the inner case 60 is smaller as the point is farther from the first concave curve 731a. Similarly, in a vertical cross-sectional view, the distance d3 between a point on the third concave curve 733aa and the rotation axis CA becomes smaller as the point is farther from the first concave curve 731a.

The radius of curvature of the second concave curve 732aa is, for example, smaller than the radius of curvature of the first concave curve 731a. Also, the radius of curvature of the third concave curve 733aa is, for example, smaller than the radius of curvature of the first concave curve 731a. The radius of curvature of the second concave curve 732 aa may be larger than or smaller than the radius of the sphere 100 or may be the same as the radius of the sphere 100 . Also, the radius of curvature of the third concave curve 733 aa may be larger than or smaller than the radius of the sphere 100 , or may be the same as the radius of the sphere 100 .

Here, since the second concave curve 732aa is an elliptical arc, the radius of curvature of the second concave curve 732aa is not constant. Similarly, the radius of curvature of the third concave curve 733aa is not constant. Thus, when the radius of curvature of a concave curve is not constant, the fact that the radius of curvature of the concave curve is smaller than a certain value means that all the values of the radius of curvature at each point on the concave curve are larger than the certain value. means small. In other words, when the radius of curvature of a concave curve is not constant, the fact that the radius of curvature of the concave curve is smaller than a certain value means that the maximum value of the radii of curvature at each point on the concave curve is larger than the certain value. means small. In addition, when the radius of curvature of a concave curve is not constant, the fact that the radius of curvature of the concave curve is greater than a certain value means that all the values of the radius of curvature at each point on the concave curve are greater than the certain value. means That is, when the radius of curvature of the concave curve is not constant, the fact that the radius of curvature of the concave curve is larger than a certain value means that the minimum value of the radius of curvature of the concave curve is larger than the certain value.

In the example of FIG. 50, the radius of curvature of a point on the second concave curve 732aa increases as it gets closer to the first concave curve 731a. That is, the radius of curvature at the end point of the second concave curve 732aa on the side of the first concave curve 731a is maximum. Therefore, in the example of FIG. 50, the fact that the radius of curvature of the second concave curve 732aa is smaller than the radius of curvature of the first concave curve 731a means that the radius of curvature at the end point of the second concave curve 732aa on the first concave curve 731a side is It means that it is smaller than the radius of curvature of the first concave curve 731a.

Also, in the example of FIG. 50, the radius of curvature of a point on the third concave curve 733aa increases as it gets closer to the first concave curve 731a. That is, the radius of curvature at the end point of the third concave curve 733aa on the side of the first concave curve 731a is maximum. Therefore, in the example of FIG. 50, the fact that the radius of curvature of the third concave curve 733aa is smaller than that of the first concave curve 731a means that the radius of curvature at the end point of the third concave curve 733aa on the side of the first concave curve 731a is It means that it is smaller than the radius of curvature of the first concave curve 731a.

The concave curved surface 730 of the cam surface 720 may form an arc in a vertical cross-sectional view. FIG. 51 is a schematic diagram schematically showing an example of a cam surface 720 having a concave curved surface 730 (also referred to as a concave curved surface 730X) forming one circular arc in vertical cross-sectional view.

As shown in FIG. 51, the concave curved surface 730X has a partial area 735 (also referred to as a first partial area 735) and a partial area 736 (also referred to as a second partial area 736). Each of the first partial area 735 and the second partial area 736 is a concave curved surface. The first partial area 735 and the second partial area 736 have, for example, the same shape. In the clockwise rotation direction, the first partial regions 735 and the second partial regions 736 are arranged in this order. The first partial area 735 is connected to the second partial area 736 . In the rotational direction, the first partial region 735 of one concave curved surface 730X is located 180° away from the first partial region 735 of the other concave curved surface 730X. In the rotational direction, the second partial region 736 of one concave curved surface 730X is located 180° away from the second partial region 736 of the other concave curved surface 730X.

The first partial region 735 forms a concave curve 735a in a vertical cross-sectional view. The second partial region 736 forms a concave curve 736a in a vertical cross-sectional view. A concave curve 735a (also referred to as a first concave curve 735a) connects to a concave curve 736a (also referred to as a second concave curve 736a). Each of the concave curves 735a and 736a is, for example, an arc of a perfect circle. The radii of curvature of concave curves 735 a and 736 a are greater than the radius of sphere 100 . In a vertical cross-sectional view, the distance between a point on the first concave curve 735a and the rotation axis of the inner case 60 is smaller as the point is farther from the first concave curve 731a. Similarly, in a vertical cross-sectional view, the distance between a point on the second concave curve 736a and the rotation axis of the inner case 60 is smaller as the point is farther from the first concave curve 731a. The concave curves 735a and 736a constitute, for example, one arc of a perfect circle.

When the inner case 60 rotates clockwise, the torque generator 40 is in a regulated state when the ball 100 contacts the first partial region 735 . For example, immediately before the sliding contact destination of the ball 100 changes from the second partial area 736 to the first partial area 735, the non-restricted state changes to the restricted state. Then, for example, immediately after the sliding contact destination of the sphere 100 changes from the connection surface 740 to the second partial region 736, the restricted state changes to the non-regulated state. When the inner case 60 rotates relative to the shaft 50 and the sphere 100 comes into sliding contact with the first partial region 735, the force of the cam surface 720 pushing the sphere 100 toward the shaft oil space 580 increases, The contact resistance between 720 and sphere 100 increases. As a result, the rotational energy of the inner case 60 is transmitted to the shaft 50 to generate clockwise torque on the shaft 50 . When the spherical body 100 is in sliding contact with the first partial region 735 , the shaft 50 rotates behind the inner case 60 . In the example of FIG. 51, since the cam surface 720 has two concave curved surfaces 750X, when the inner case 60 rotates clockwise, while the inner case 60 rotates 360° relative to the shaft 50, , a pulsed torque is generated on the shaft 50 twice.

When the inner case 60 rotates counterclockwise, the torque generating device 40 is in a regulated state when the ball 100 contacts the second partial region 736 . For example, immediately before the sliding contact destination of the sphere 100 changes from the first partial area 735 to the second partial area 736, the non-restricted state changes to the restricted state. Then, for example, immediately after the sliding contact destination of the ball 100 changes from the connection surface 740 to the first partial region 735, the restricted state changes to the non-restricted state. When the inner case 60 rotates relative to the shaft 50 and the sphere 100 comes into sliding contact with the second partial region 736, the force of the cam surface 720 pushing the sphere 100 toward the shaft oil space 580 increases, The contact resistance between 720 and sphere 100 increases. As a result, the rotational energy of the inner case 60 is transmitted to the shaft 50 to generate counterclockwise torque in the shaft 50 . When the spherical body 100 is in sliding contact with the second partial area 736, the shaft 50 rotates behind the inner case 60. As shown in FIG. When the inner case 60 rotates counterclockwise, two pulse-like torques are generated in the shaft 50 while the inner case 60 rotates 360° relative to the shaft 50 .

Note that the concave curves 735a and 736a may form one circular arc of an ellipse. In this case, each of the concave curves 735a and 736a becomes an elliptical arc.

In this way, when the first concave curve 735a formed by the first partial region 735 in vertical cross-section and the second concave curve 736a formed by the second partial region 736 in vertical cross-section form one circular arc, The first partial area 735 and the second partial area 736 are smoothly connected. As a result, when the inner case 60 rotates clockwise, the moving member 100 can smoothly come into sliding contact with the cam surface 720 from the second partial area 736 to the first partial area 735 . Therefore, noise is less likely to be generated when the moving member 100 starts sliding contact with the first partial region 735 . As a result, quietness is improved. Similarly, when the inner case 60 rotates counterclockwise, the moving member 100 can smoothly slide on the cam surface 720 from the first partial area 735 to the second partial area 736 . Therefore, noise is less likely to be generated when the moving member 100 starts sliding contact with the second partial region 736 . As a result, quietness is improved.

In the example above, the moving member 100 is a sphere, but the moving member 100 may have a shape other than a sphere. In this case, for example, as shown in FIG. 52, the surface of at least part of the protruding portion 110 of the moving member 100 that protrudes from the shaft 50 may form a partial spherical surface. In the example of FIG. 52, the surface of the tip of the moving member 100 forms a partial spherical surface 110a. The partial spherical surface 110a is, for example, a hemispherical surface. The partial spherical surface 110 a is in sliding contact with the cam surface 720 . In the example of FIG. 52, it can be said that the surface of the protruding portion 110 has a partial spherical surface 110a having a portion in sliding contact with the cam surface 720. As shown in FIG.

The radius of curvature of the second concave curve 732a formed by the second partial area 732 of the concave curved surface 730 of the cam surface 720 in a vertical cross-sectional view may be larger or smaller than the radius of curvature of the partial spherical surface 110a. Also, the radius of curvature of the second concave curve 732a may be the same as the radius of curvature of the partial spherical surface 110a.

The radius of curvature of the third concave curve 733a formed by the third partial region 733 of the concave curved surface 730 of the cam surface 720 in vertical cross-section may be larger or smaller than the radius of curvature of the partial spherical surface 110a. Also, the radius of curvature of the third concave curve 733a may be the same as the radius of curvature of the partial spherical surface 110a.

A fourth concave curve 731b formed by the first partial region 731 in an axial cross-sectional view may match or differ from the radius of curvature of the partial spherical surface 110a. Also, the fifth concave curve formed by the second partial region 732 in an axial cross-sectional view may match or differ from the radius of curvature of the partial spherical surface 110a. Also, the sixth concave curve formed by the third partial region 733 in an axial cross-sectional view may be the same as or different from the radius of curvature of the partial spherical surface 110a.

Although the oil pulse tool 1, the unit 10, and the torque generator 40 have been described in detail as above, the above description is illustrative in all aspects, and the present disclosure is not limited thereto. Also, the various examples described above can be applied in combination as long as they do not contradict each other. And it is understood that countless examples not illustrated can be envisioned without departing from the scope of this disclosure.

Reference Signs List 1 oil pulse tool 5 motor 6, 7 cooling fan 40, 40A, 40B torque generator 50, 50A shaft 60 case 100 moving member 110 projecting portion 110a partial spherical surface 531, 531A, 541, 541A hole 531a, 541a opening 580 oil space 600 Oil chamber 610 Inner peripheral surface 720 Cam surface 730, 730a, 730b, 730c, 730X Concave surface 731, 732, 733, 735, 736 Partial region 731a, 731b, 732a, 733a, 735a, 736a Concave curve 780 Regulating surface

Claims (14)

a case having an oil chamber filled with oil and driven to rotate;
a shaft at least partially supported in the oil chamber and rotatable relative to the case;
a first moving member that can move in and out of the shaft;
The shaft is
an oil space located inside the shaft, filled with the oil, and entering and exiting the first moving member;
a first opening that opens toward the inner peripheral surface of the oil chamber and allows the first moving member to enter and exit the oil space;
at least one second opening that opens toward the inner peripheral surface and allows the oil to flow into and out of the oil space;
The inner peripheral surface is
a cam surface with which the first moving member slides in and out of the oil space through the first opening as the case rotates relative to the shaft;
a restricting surface that restricts the flow of the oil into and out of the oil space from the at least one second opening when the case and the shaft are in a predetermined positional relationship in the rotational direction of the case;
In a regulated state in which the regulating surface regulates the inflow and outflow of the oil to and from the oil space, the first moving member is regulated from entering and exiting the oil space,
the cam surface has a first region;
In a first rotational state in which the case is rotationally driven in a first rotational direction and rotates relative to the shaft, when the first moving member is in sliding contact with the first region in the restricted state, the A torque generating device, wherein a force of a cam surface pressing the first moving member toward the oil space increases to generate torque in the first rotational direction in the shaft. A torque generator according to claim 1,
the cam surface has a second region in contact with the first region, which is in sliding contact with the first moving member prior to the first region in the first rotational state;
The first region forms a first concave curve in a first cross-sectional view perpendicular to the rotation axis of the case,
The second region forms a second concave curve in the first cross-sectional view,
The torque generating device, wherein the first concave curve is tangentially continuous with the second concave curve, or the first concave curve and the second concave curve form one circular arc. A torque generator according to claim 1,
the cam surface has a second region in contact with the first region, which is in sliding contact with the first moving member prior to the first region in the first rotational state;
The first region forms a first concave curve in a first cross-sectional view perpendicular to the rotation axis of the case,
The second region forms a second concave curve in the first cross-sectional view,
The torque generator, wherein the radius of curvature of the second concave curve is greater than the radius of curvature of the first concave curve. The torque generator according to claim 2 or 3,
a surface of at least a part of a protruding portion of the first moving member protruding from the shaft forms a partial spherical surface;
The torque generator, wherein the radius of curvature of the first concave curve is greater than the radius of curvature of the partial spherical surface. The torque generator according to claim 2 or 3,
a surface of at least a part of a protruding portion of the first moving member protruding from the shaft forms a partial spherical surface;
The torque generator, wherein the radius of curvature of the first concave curve is smaller than the radius of curvature of the partial spherical surface. The torque generator according to any one of claims 1 to 5,
a surface of at least a part of a protruding portion of the first moving member protruding from the shaft forms a partial spherical surface;
the first region forms a third concave curve in a second cross-sectional view along the rotation axis of the case;
The torque generator, wherein the third concave curve curves along the partial spherical surface. The torque generator according to any one of claims 2 to 6,
a surface of at least a part of a protruding portion of the first moving member protruding from the shaft forms a partial spherical surface;
the second region forms a fourth concave curve in a second cross-sectional view along the rotation axis of the case;
The torque generator, wherein the fourth concave curve curves along the partial spherical surface. The torque generator according to any one of claims 1 to 7,
The first moving member is a sphere,
The torque generating device, wherein the spherical body rotates and comes into sliding contact with the cam surface as the case rotates relative to the shaft. The torque generator according to any one of claims 1 to 8,
further comprising a second moving member that can move in and out of the shaft;
the shaft has a third opening that opens toward the inner peripheral surface and allows the second moving member to enter and exit the oil space;
the second moving member slides in contact with the cam surface while entering and exiting the oil space through the third opening as the case rotates relative to the shaft;
In the restricted state, entry and exit of the first moving member and the second moving member with respect to the oil space are restricted,
the cam surface has a third region;
When the first moving member and the second moving member are brought into sliding contact with the first area and the third area at the same timing in the restricted state in the first rotation state, the cam surface moves the first movement. A torque generating device, wherein a force for pushing the member and the second moving member toward the oil space increases to generate torque in the first rotational direction in the shaft. The torque generator according to any one of claims 1 to 8,
the cam surface has a third region;
In the case of the first rotation state, when the first moving member slides against the third area in the regulated state, the force of the cam surface pressing the first moving member toward the oil space increases, and the first moving member increases. A torque generator, wherein torque in one rotation direction is generated on the shaft. A torque generator according to any one of claims 1 to 10,
the cam surface has a fourth region;
When the case is in a second rotational state in which the case is rotationally driven in a second rotational direction opposite to the first rotational direction and rotates relative to the shaft, the first moving member is moved to the fourth rotational direction in the restricted state. A torque generating device, wherein a force of the cam surface pushing the first moving member toward the oil space increases when slidingly contacting the region, and torque in the second rotational direction is generated in the shaft. A torque generator according to any one of claims 1 to 11,
A torque generating device, wherein the amount of oil outside the shaft in the oil chamber is greater than the amount of oil in the oil space of the shaft. A torque generator according to any one of claims 1 to 12;
a tip tool attached to the shaft included in the torque generator;
and a motor that rotationally drives the case of the torque generator. 14. The oil pulse tool of claim 13, comprising:
a first cooling fan for cooling the motor;
and a second cooling fan for cooling the torque generator.

Images