JP2013255950A - Rotation converting mechanism and chuck device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a rotation converting mechanism capable of easily and accurately machining such that a rolling means locking to a helical groove and rolling can smoothly circulate locking to a helical groove and a chuck device enhancing force fastening a base shaft of a rotary jig by chuck pawls and attaining a stable fastening state.SOLUTION: A chuck device is constituted of a helical locking groove 81 formed in an inner peripheral face of an outer nut ring 80, a helical locking groove 71 formed in an outer peripheral surface of an inner nut 70 and formed in a helical shape in the same direction as the helical locking groove 81, and a plurality of locking ball 79 engaging with both the helical locking grooves 71, 81 and rolling, a coupling locking groove 71a coupling end parts themselves of the helical locking groove 71 constituted in a helical shaped less than one turn in a rotational direction is constituted in such a depth that engaging of engaging locking balls 79 to the helical locking groove 81 is released, and is formed in an attaching groove member 72b capable of being attached to a ring body 72 in which the helical locking groove 71 constituted in the helical shape less than one turn is formed.

Description

  The present invention provides, for example, a rotation conversion mechanism that converts and transmits a relative rotation of one of an outer diameter member and an inner diameter member with respect to the other and a relative movement in the axial direction with respect to the other, and the rotation conversion. A chuck equipped with a mechanism and mounted on a drive device having a drive shaft that can rotate on an axis, and grips the base shaft of a rotating jig inserted into the shaft hole on the distal end side by tightening from a circumferential direction with a plurality of chuck claws Relates to the device.

  As a rotation conversion mechanism that converts the relative rotation of one of the outer member and the inner member with respect to the other and the relative movement in the axial direction with respect to the other member, for example, a mechanism called a ball screw device Various techniques have been proposed.

  For example, the ball screw device described in Patent Document 1 includes a screw shaft having a closed loop-shaped raceway groove on the outer peripheral surface, a nut member externally fitted to the screw shaft and having a spiral raceway groove on the inner peripheral surface, A ball group interposed between the raceway groove of the screw shaft and the raceway groove of the nut member is constituted.

  The closed loop raceway groove is formed by forming a part of the closed loop raceway groove formed on the screw shaft to such a depth that the group of balls latched on the raceway groove cannot be engaged with the raceway groove of the nut member. The ball group is configured to be circulated.

  However, it has been difficult to accurately form a part of the closed loop raceway groove to a depth that cannot be locked to the raceway groove of the nut member so that the ball group circulates while smoothly moving.

JP 2004-239417 A

  Therefore, the present invention increases the force of tightening the base axis of the rotating jig with the rotation conversion mechanism and chuck claws that can be processed easily and accurately so that the rolling means that rolls while being locked in the spiral groove can be smoothly circulated. An object of the present invention is to provide a chuck device capable of realizing a stable tightening state.

  The present invention provides a rotation conversion mechanism for converting rotation on an axial center and movement in the axial direction, an outer diameter member having a circular opening formed by a cylindrical inner peripheral surface, and an outer peripheral surface of the inner surface. A cylindrical inner member disposed in the circular opening so as to face the peripheral surface, a relative rotation with respect to one of the outer member and the inner member, and an axis with respect to the other A rotation conversion means that converts and transmits the relative movement in the center direction, and the rotation conversion means is formed in a spiral shape with respect to the axial direction formed on the inner peripheral surface of the outer diameter member. An outer spiral groove, a radially inner spiral groove formed on the outer circumferential surface of the radially inner member and formed in the spiral shape in the same direction as the radially outer spiral groove, the radially outer spiral groove, and the radially inner spiral groove; And a plurality of rolling members that roll while engaging with both, One of the inner spiral grooves is formed in a spiral shape for a plurality of turns in the rotation direction, and the other is formed in a spiral shape for less than one turn in the rotation direction. A connecting groove that connects the ends of the spiral groove formed in a shape is provided to form a closed loop, and the rolling member that engages the connecting groove is disengaged from one spiral groove. And a portion forming the connecting groove is formed of a separate member that can be attached to a member main body formed with a spiral groove having a spiral shape of less than one round. And

  The above-mentioned outer diameter member having a circular opening formed by the cylindrical inner peripheral surface has a polygonal column shape even if the outer diameter is a cylindrical shape as long as it has a circular opening formed by the cylindrical inner peripheral surface. The cylindrical inner member disposed in the circular opening so that the outer peripheral surface faces the inner peripheral surface, the outer peripheral surface is an outer member. It may be a columnar shape or a cylindrical shape facing the inner peripheral surface.

  Relative rotation with respect to one of the outer member and the inner member described above is the rotation of the inner member with respect to the outer member whose rotation has stopped and the inner member with which rotation has stopped. It is a concept that includes the rotation of the outer member or the rotation of both the outer member and the inner member in a state where the speed difference and the rotation direction are different. Similarly, the relative movement in the axial direction with respect to one of the outer member and the inner member is the movement of the inner member with respect to the stopped outer member, and the stopped inner member. It is a concept that includes the movement of the outer member relative to the material, or the movement of both the outer member and the inner member with different speed differences and moving directions.

Further, the rotation conversion means for converting the relative rotation and the relative movement in the axial direction to transmit the relative rotation of the outer member and the inner member relative movement of the outer member and the inner member. Or a concept including a mode in which relative movement of the outer member and the inner member is converted into relative rotation of the outer member and the inner member.
The above-mentioned rolling member can be composed of a sphere or a roller body.

  According to the present invention, the rolling means that rolls while being locked in the spiral groove is smoothly circulated, the relative rotation with respect to one of the outer member and the inner member, and the axial center with respect to the other member. A rotation conversion mechanism that converts and transmits the relative movement in the direction can be easily and accurately processed.

  Specifically, it is a rotation conversion mechanism that converts rotation on the axial center and movement in the axial direction, an outer diameter member having a circular opening formed by a cylindrical inner peripheral surface, and an outer peripheral surface of the inner peripheral surface. A cylindrical inner member disposed in the circular opening so as to face the surface, a relative rotation with respect to one of the outer member and the inner member, and an axis with respect to the other A rotation converting means for converting the relative movement in the direction and transmitting the rotation, and the rotation converting means is formed in a spiral shape with respect to the axial direction formed on the inner peripheral surface of the outer diameter member. Both a spiral groove, a radially inner spiral groove formed on the outer peripheral surface of the radially inner member and formed in the spiral shape in the same direction as the radially outer spiral groove, the radially outer spiral groove, and the radially inner spiral groove A plurality of rolling members that engage and roll with the outer spiral groove and the diameter One of the side spiral grooves is formed in a spiral shape for a plurality of turns in the rotation direction, and the other is formed in a spiral shape for less than one turn in the rotation direction. A connecting groove that connects the ends of the spiral groove formed in a shape is provided to form a closed loop, and the rolling member that engages the connecting groove is disengaged from one spiral groove. By configuring the depth, the relative rotation with respect to the other one of the outer diameter member and the inner diameter member and the relative movement in the axial direction with respect to the other one can be converted.

  In addition, since the portion that forms the connection groove is formed of a separate member that can be attached to the member main body formed with the spiral groove having a spiral shape of less than one round, the connection can be accurately performed with easy processing. Grooves can be formed.

  Specifically, in order to form the connection groove in a separate member that can be attached to the member body in which the spiral groove is formed, compared to the case of processing the closed loop spiral groove of varying depth in the member body, Workability is improved, and the connecting groove can be formed with high accuracy by easy processing.

  As a result, the rolling member engaged with the spiral groove smoothly circulates in the closed loop spiral groove, and the relative rotation with respect to one of the outer member and the inner member and the shaft with respect to the other member. The relative movement in the heart direction can be converted smoothly.

As an aspect of the present invention, the other spiral groove formed in a spiral shape with less than one turn is formed on the outer peripheral surface of the inner diameter member, and the one spiral groove formed in a spiral shape with a plurality of turns in the rotation direction is formed. , And can be formed on the inner peripheral surface of the outer diameter member.
According to the present invention, the inner member can be largely moved in the axial direction with respect to the outer member.

  The present invention also relates to a chuck device to be mounted on a drive device having a drive shaft that can rotate on an axial center, which is disposed on the axial center and allows insertion of a base shaft of a rotating jig on the distal end side. A chuck body having a substantially cylindrical shape, and is connected to the shaft hole on the front end side of the chuck body and is inserted into an inclined hole that opens to the side of the chuck body on the rear end side. A plurality of chuck claws arranged so as to be movable with respect to the chuck body and rotatably held by the chuck body, and the plurality of chuck claws are synchronized with each other by being screwed to the chuck body and the chuck claws. A nut that moves in an inclined direction, a rotation input body that is rotatably attached to the chuck body, and that inputs a rotational force by a rotation operation, and the nut and the rotation input A rotation restricting means for differentially rotating the nut and the rotation input body by a predetermined rotational load, and a differential rotation between the nut and the rotation input body by the rotation restricting means. A rotation converting means for converting to differential to the tip end in the center direction, the nut and the rotation input body are formed in a ring shape, and one of the nut and the rotation input body is the rotation conversion described above. The inner member in the mechanism and the other member are constituted by the outer member.

According to the present invention, it is possible to increase the force for tightening the base shaft of the rotating jig with the chuck claw and realize a stable tightening state.
Specifically, since the chuck main body, the plurality of chuck claws, the nut, the rotation input body, and the rotation restricting means are provided, the gripping the base shaft inserted into the shaft hole allows the inside of the inclined hole. When the rotation of the nut is fixed by using the plurality of chuck claws whose movement in the tilting direction is restricted as a reaction force and the rotational force input from the further rotational input body exceeds the predetermined rotational load, the rotation The rotation input body is differentially rotated with respect to the nut fixedly rotated by the restricting means.

And the differential rotation of the rotation input body with respect to the nut generated by the rotation restricting means can be changed to the differential in the axial direction of the nut by the rotation converting means.
Further, the rotation converting means moves the nut forward in the axial direction with respect to the rotation input body, whereby a plurality of chuck claws synchronized with the nut by screwing are integrally formed on the inner wall surface of the inclined hole. A stable tightening state can be realized by increasing the force of pressing and tightening the base shaft of the rotating jig with the chuck claw.

  As an aspect of the present invention, a rotation input operation body that performs an input operation of a rotational force on the rotation input body, and a rotation restriction that restricts rotation of the tightened rotation input operation body with respect to the chuck body by a frictional force in a rotation direction. Means.

  According to the present invention, it is possible to restrict differential rotation of the rotation input operation body with respect to the rotating chuck body in a tightened state in which the base shaft is gripped by a plurality of chuck claws. The rotation limiting means is configured to limit the differential rotation of the rotation input operation body relative to the chuck body by the frictional force in the rotation direction, that is, the friction force acting in the differential direction of the rotation input operation body relative to the chuck body. Therefore, the differential of the rotary input operation body with respect to the chuck body can be limited more efficiently. Therefore, for example, it is possible to prevent the rotation input operation body from rotating in the loosening direction due to vibration or impact caused by rotating the rotary jig and loosening the tightening state, and maintain a stable tightening state.

  According to the present invention, the rotation means that can be machined easily and accurately so that the rolling means that rolls while being locked in the spiral groove can be smoothly circulated, and the force for tightening the base shaft of the rotating jig with the chuck claw is increased. Thus, it is possible to provide a chuck device that can realize a stable tightening state.

The front view of the electric tool provided with the chuck device. The exploded explanatory drawing which described the front and back of each component of a chuck | zipper apparatus, the side surface, and the cross section together. The exploded perspective view from the front side of each component of a chuck device. The exploded perspective view from the back side of each component of a chuck device. The exploded perspective view of the rotation regulation conversion unit in a chuck device. The longitudinal cross-sectional view of a chuck device. Explanatory drawing by the longitudinal cross-sectional view of the rotation control conversion unit in a chuck | zipper apparatus. Explanatory drawing of the rotation control conversion unit in a chuck | zipper apparatus. Sectional drawing of the rotation control conversion unit in a chuck | zipper apparatus. The perspective view about the assembly | attachment of the rotation control conversion unit in a chuck | zipper apparatus. Explanatory drawing about the outer nut ring and rotation regulation conversion unit U in a chuck | zipper apparatus. Explanatory drawing about the holding | grip of the base shaft by a jaw. Explanatory drawing about a rotation conversion mechanism. Sectional drawing about a rotation conversion mechanism.

An embodiment of the present invention will be described below in detail with reference to the drawings.
FIG. 1 shows a front view of an electric power tool K provided with a chuck device 1, and FIG. 2 shows an exploded explanatory view in which front and rear surfaces, side surfaces and cross sections of each component of the chuck device 1 are shown.
In the present specification, the front side and the front side coincide with the front end side of the chuck device, and the back side, the rear side and the rear end side coincide with the base end side of the chuck device, so that it can be easily understood in the description in the text. The terms are used as appropriate, but there is no significant difference in meaning.

  2, the rear outer sleeve 10, the lock washer 40, the outer nut ring 80, the dish spring 90, the slide ring 121, and the O-ring 122 show a front view and a sectional view, and show a chuck body 30, a W bearing ball 52, And the W bearing inner 53 has shown the front view and the side view.

  The inner nut 70 shows a front view, a side view, and a sectional view, the nut spring 100 shows a rear view and a side view, and the W bearing outer 51, the front outer sleeve 110, and the tip cap 130 show a rear view and a sectional view. . In addition, the jaw 20 has shown the side view of the state arrange | positioned in three directions.

  3 shows an exploded perspective view from the front side of each component of the chuck device 1, FIG. 4 shows an exploded perspective view from the back side of each component of the chuck device 1, and FIG. FIG. 6 shows an exploded perspective view of the rotation regulation conversion unit U in FIG.

  Further, FIG. 7 is an explanatory view of the rotation restriction conversion unit U in the chuck device 1 by a longitudinal sectional view, FIG. 8 is an explanatory view of the rotation restriction conversion unit U in the chuck device 1, and FIG. FIG. 10 shows a perspective view of the assembly of the rotation restriction conversion unit U in the chuck device 1, and FIG. 11 shows the outer nut ring 80 and the rotation restriction conversion unit U in the chuck device 1. FIG. 12 is an explanatory diagram for gripping the base shaft J by the jaw 20.

  As shown in FIG. 1, for example, the chuck device 1 mounted on the spindle S arranged at the distal end portion of the electric power tool K has a base end side (rear side: upper left in FIG. 3) as shown in FIGS. 4, from the lower right) to the front end side (front: lower right in FIG. 3, upper left in FIG. 4), rear outer sleeve 10, jaw 20, chuck body 30, lock washer 40, W bearing 50, rotation The conversion mechanism 60, the dish spring 90, the nut spring 100, the front outer sleeve 110, the sleeve rotation restriction mechanism 120, and the cap 130 are arranged and assembled, and the base shaft J is gripped by the jaw 20.

  The rear outer sleeve 10, the lock washer 40, the W bearing 50, the rotation conversion mechanism 60, the dish spring 90, the nut spring 100, the front outer sleeve 110, the sleeve rotation restriction mechanism 120, and the cap 130 are formed in a ring shape. It arrange | positions on the axial direction AL parallel to a longitudinal direction.

The rear outer sleeve 10 includes a ring portion 12 having a center hole 11 at the center of the front view that allows press-fitting of a rear body portion 31 of the chuck body 30 described later, and a chuck body at the inner peripheral edge portion and the outer peripheral edge portion of the ring portion 12. It is comprised with the flange parts 13 and 14 which protrude toward 30 side.
A plurality of ribs parallel to the axial direction AL are provided on the outer peripheral surface of the flange portion 14 on the outer peripheral side.

  The chuck body 30 allows mounting of the rear body part 31, the first flange part 32, the rear middle body part 33, the second flange part 34, and the W bearing 50 that are press-fitted into the center hole 11 of the rear outer sleeve 10 described above. A center hole 30a that is configured in this order from the rear with the front middle barrel portion 35 and the front barrel portion 36 that allows press-fitting of the cap 130, and that allows insertion of the base axis J of the mounting jig is formed in the center in a front view. And penetrates in the longitudinal direction.

  Furthermore, from the outside of the chuck body 30 toward the center hole 30a, that is, in the axial direction AL, over the first flange portion 32, the rear middle barrel portion 33, the second flange portion 34, the front middle barrel portion 35, and the front barrel portion 36. Three jaw mounting holes 37 in the direction intersecting with each other are arranged at equal intervals in the circumferential direction, and the jaws 20 are inserted in the jaw mounting holes 37 so as to be slidable.

  The jaw 20 is formed in a substantially cylindrical shape having a screw groove 21 to be screwed with a helical screw groove 73 formed on the inner surface of an inner nut 70 in a W bearing 50 to be described later. . Further, the front inner side surface of the jaw 20 forms a pressing surface 22 that is substantially parallel to the axial direction AL in a direction crossing the substantially cylindrical axial direction, and the center of the pressing surface 22 in the width direction is formed. Is equipped with a chip 23 made of carbide.

  In the state where the rear inner peripheral surface 24 and the front outer peripheral surface 25 of the jaw 20 formed in a substantially cylindrical shape as described above are slid on the inner peripheral surface 37a (see FIG. 7) of the jaw mounting hole 37, the shaft The jaw 20 is inserted into the jaw mounting hole 37 in a posture in which the pressing surface 22 is parallel to the axial direction AL in three directions in the circumferential direction with respect to the central direction AL.

  In the assembled state, the lock washer 40 that comes into contact with the second flange portion 34 of the chuck body 30 includes a ring-shaped gear ring portion 41 in which radial engagement gears 41 a are arranged in the circumferential direction, and an outer periphery of the gear ring portion 41. A projecting spring portion 42 projecting forward, and a stop semicircular convex portion 43 projecting in a semicircular shape in front view from the inner peripheral edge of the gear ring portion 41 to the inside of the diameter.

  In addition, the protrusion spring part 42 is provided with three places at equal intervals with respect to the gear ring part 41 in the circumferential direction. Further, the diameter stop semicircular convex portion 43 has a shape that fits into a semicircular diameter stop concave portion 34 a formed inside the second flange portion 34 of the chuck body 30, and is provided at three locations in the circumferential direction.

  In the assembled state, the W bearing 50 sandwiched with the lock washer 40 between the second flange portion 34 of the chuck body 30 and the rotation conversion mechanism 60 allows the front middle barrel portion 35 to be inserted into the chuck body 30. A ring body formed with a diameter larger than that of the second flange portion 34, and includes a W bearing outer 51, a W bearing ball 52, and a W bearing inner 53.

  The W bearing outer 51 has a central opening 51a that allows the front middle barrel portion 35 to be inserted in the center in a front view, a rear ring surface 51b that constitutes a rear surface on the base end side of the W bearing 50, and a rear ring surface The outer peripheral surface 51c protrudes forward from the outer peripheral edge of 51b. In addition, the corner portion formed by the rear ring surface 51 b and the outer peripheral surface 51 c is formed by a curved surface corresponding to the W bearing ball 52.

  Further, as shown in FIG. 4, a meshing gear 51 d that meshes with a meshing gear 41 a formed on the front surface of the gear ring portion 41 of the lock washer 40 is disposed on the rear surface of the rear ring surface 51 b in the circumferential direction. Further, an inner peripheral edge forming the central opening 51a in the rear ring surface 51b is provided with an axial gear 51e that meshes with a rear end side axial gear portion 76 of an inner nut 70 described later so as to be slidable in the axial direction. Arranged in the direction.

  Furthermore, on the inner peripheral surface of the outer peripheral surface 51c, there is formed a connection groove 51f that allows fitting of the rear end side connection convex portion 86 provided at the rear end that is the base end side of the outer nut ring 80 described later. A plurality of slits 51g for facilitating the fitting of the rear end side connecting convex portion 86 to the connecting groove 51f are formed at equal intervals in the circumferential direction.

  The W bearing inner 53 has a central opening 53a that allows the front middle barrel portion 35 to be inserted at the center in a front view, a front ring surface 53b that constitutes a front surface of the W bearing 50, and an inner peripheral edge of the front ring surface 53b. And an inner peripheral surface 53c protruding rearward. In addition, the corner | angular part comprised by the front ring surface 53b and the internal peripheral surface 53c is comprised by the curved surface corresponding to the W bearing ball | bowl 52 mentioned later.

In a state where the W bearing outer 51 and the W bearing inner 53 are assembled, the corner portion constituted by the rear ring surface 51b and the outer peripheral surface 51c in the W bearing outer 51, and the front ring surface 53b and the inner peripheral surface in the W bearing inner 53 A plurality of W bearing balls 52 sandwiched between the corners formed by 53c are arranged in a ring shape.
A W bearing 50 is configured by assembling the W bearing outer 51, the W bearing ball 52, and the W bearing inner 53 configured in this way.

  The rotation conversion mechanism 60 attached to the front middle body portion 35 of the chuck body 30 includes an outer nut ring 80, an inner nut 70, and a locking ball 79 sandwiched between opposing surfaces of the inner nut 70 and the outer nut ring 80. It is a configured ring-shaped body.

  The inner nut 70 has a helical locking groove 71 that allows the locking ball 79 to be locked on the outer peripheral surface, and a screwing groove 73 that engages with the screw groove 21 of the jaw 20 on the inner peripheral surface. A ring main body 72, a front-end protruding gear portion 75 that protrudes forward from the front surface that is the front end side of the ring main body 72, and a rear-end-side axial gear that protrudes rearward from the rear surface that is the base end side of the ring main body 72. It is comprised with the part 76. FIG.

The front end side protruding gear portion 75 includes an axial ratchet gear 74 that allows the engagement of a meshing claw portion 105 of the nut spring 100, which will be described later, on the outer peripheral surface, and the rear end side axial gear portion 76 has a W It is the structure which meshes with the axial direction gear 51e of the bearing outer 51 in the state which can be slid in an axial direction.
Further, the ratchet gear 74 is constituted by a single inclined gear having a radial direction surface on the tightening rotation direction R side and an inclined surface inclined on the loose rotation direction L side with respect to the radial direction.

  The spiral locking groove 71 is opposed to a helical locking groove 81 of the ring body 82, which will be described later, in the assembled state of the rotation conversion mechanism 60, and has one turn in the spiral direction at the same spiral angle as the helical locking groove 81. It is formed with a length of less than. Further, the ends of the spiral locking grooves 71 having less than one turn in the spiral direction are connected by a connection locking groove 71a in a direction intersecting the spiral direction of the spiral locking groove 71, and the spiral locking groove 71 is connected. Constitutes a closed loop.

As shown in FIG. 7A, the spiral locking groove 71 is formed as an arc-shaped groove having a depth of about 1/3 with respect to the radius of the locking ball 79.
Further, as shown in FIG. 5, the connection locking groove 71 a is formed in an attachment groove member 72 b configured to be attachable to an outer peripheral recess 72 a in which a part of the outer peripheral surface of the ring body 72 is recessed. . Further, the connection locking groove 71 a is formed in a 4/5 circular cross section covering the portion other than the top of the locking ball 79 locked in the spiral locking groove 71. In addition, since the groove bottom portion of the connection locking groove 71a is formed deeper inside the diameter than the spiral locking groove 71, as shown in FIG. It will be located inside the diameter from the locking ball 79 locked in the connection locking groove 71a. In addition, the broken line shown in FIG. 9 has shown the edge part of the helical locking grooves 71 and 81. FIG.

  Moreover, since the attachment groove member 72b in which the connection locking groove 71a is formed is formed of deformable rubber, the connection locking groove 71a having a 4/5 circular cross section is formed by pressing using a die. It can be formed with high accuracy.

  The screwing groove 73 is inclined in the diameter reducing direction toward the front according to the angle of the screw groove 21 of the jaw 20 to be screwed. More specifically, the screwing groove 73 and the screw groove 21 are set to the lower limit of 16 threads / inch within a thread range generally set at 16 to 24 threads / inch based on the tightening speed and the tightening force. However, the number of peaks may be less than this, and of course, it may be more than this.

The outer nut ring 80 includes a ring main body 82 having a helical helical locking groove 81 that allows the locking ball 79 to be locked on the inner peripheral surface, and a loose fitting recess 83 in the circumferential direction on the front surface of the ring main body 82. Are arranged at equal intervals through the protruding wall portion 84 protruding forward. Note that a locking recess 85 that locks a locking protrusion 106 of the nut spring 100 described later is provided on the inner peripheral surface 84 a of the protruding wall portion 84. In addition, the rear end side of the ring body 82 is formed with a small diameter, and the rear end edge is formed with a slightly larger diameter to form a rear end side connection convex portion 86 that fits into the connection groove 51f of the W bearing outer 51. ing.
As shown in FIG. 7A, the spiral locking groove 81 is formed as an arc-shaped groove having a depth of about 1/3 with respect to the radius of the locking ball 79.

  The inner nut 70 and the outer nut ring 80 configured as described above are configured so that the helical locking grooves 71 and 81 are opposed to each other, and the locking balls 79 are locked between the opposed helical locking grooves 71 and 81. The rotation converting mechanism 60 (see FIG. 10) is configured.

  At this time, the helical locking grooves 71 and 81 face each other with a slight clearance between the inner nut 70 and the outer nut ring 80. In this way, the helical locking grooves 71 and 81 facing each other with a slight clearance are formed at a depth of about 1/3 with respect to the radius of the locking ball 79 as shown in FIG. Since it is formed by the arc-shaped groove, the locking ball 79 is locked to both the spiral locking grooves 71 and 81 as shown in FIG.

  On the other hand, as described above, the coupling locking groove 71a formed in a 4/5 circular cross section covering the portion other than the top of the locking ball 79 and deeper inward than the helical locking groove 71 is engaged. Since the locking ball 79 to be stopped is positioned inside the diameter, the locking ball 79 is not locked to the opposing spiral locking groove 81. Therefore, the locking ball 79 can circulate in the spiral locking groove 71 through the connecting locking groove 71 a in the direction intersecting the spiral direction of the spiral locking grooves 71, 81.

  Therefore, as shown in FIG. 8, the outer nut ring 80 and the inner nut 70 can be rotated relative to each other via the locking balls 79 locked in the spiral locking grooves 71, 81, and the inner nut relative to the outer nut ring 80 can be rotated. The relative rotation of the nut 70 can be converted into a differential in the front-rear direction of the inner nut 70 with respect to the outer nut ring 80.

  Further, since the locking ball 79 circulates in the closed loop helical locking groove 71, the inner nut 70 is connected to the outer nut ring 80 in the front-rear direction without depending on the number of the locking balls 79. Dynamic conversion.

  The dish spring 90 is a ring shape having a rectangular cross section inclined inward in the radial direction, and has an inner diameter smaller than the inner diameter of the distal end side protruding gear part 75 and an outer diameter of the distal end side protruding gear part 75, and the nut spring 100. The outer diameter is smaller than the inner diameter. In addition, a plurality of concave portions 91 facing inwardly of the diameter are formed on the outer periphery of the dish spring 90 at predetermined intervals in the circumferential direction. In addition, since the dish spring 90 is comprised with the metal plate which has elasticity, it can be urged | biased to an axial direction with respect to the twist where a cross section becomes flat. Moreover, since the recessed part 91 is formed in the outer peripheral side, the twist property is improving.

  The nut spring 100 includes a ring portion 101 on the distal end side, a T-shaped arm portion 102 formed in a substantially T shape in a sleeping position in which a radially outer side of the ring portion 101 is bent toward the proximal end and laid backward in a side view. It consists of.

  The T-shaped arm portion 102 is provided at three locations in the circumferential direction. As shown in the enlarged view of FIG. 2B, the distal end of the front outer sleeve 110 described later is provided at the distal end of the T-shaped arm portion 102 in the tightening rotation direction R. Among the locking recesses 112 formed in the pressing block 113 disposed on the inner periphery of the side, there is a rotation position restriction locking projection 103 protruding outward in the diameter locked to the unlocking rotation position restriction locking recess 112a.

  As shown in the enlarged view of FIG. 2b, the tip end of the T-shaped arm portion 102 in the loosening rotation direction L has a meshing claw portion 105 that meshes with the ratchet gear 74 of the tip side protruding gear portion 75 of the inner nut 70. Yes. Further, in the middle part of the loose rotation direction L in the T-shaped arm portion 102, the ratchet release locking recess 112 b among the locking recesses 112 formed in the pressing block 113 disposed on the inner peripheral edge of the front outer sleeve 110 described later. And a ratchet release locking convex portion 104 protruding outward in diameter to be locked to the ratchet engagement diameter stopping concave portion 112c.

Further, at the center of the T-shaped arm portion 102, there is provided a locking convex portion 106 that stops at a locking concave portion 85 formed on the inner surface of the protruding wall portion 84 of the outer nut ring 80.
In the present embodiment, the integrated nut spring 100 is used. However, the first nut spring and the second nut spring may be assembled.

  The front outer sleeve 110 has a rear end side that is the same diameter as the outer peripheral flange portion 14 of the rear outer sleeve 10 and is substantially bell-shaped in a side view in which the front end side that allows insertion of a cap 130 described later is narrowed on the front end side. It is formed in a cylindrical shape.

  On the inner peripheral side of the front outer sleeve 110, as shown in the enlarged view of FIG. 2 a, a locking recess for locking the above-described rotation position regulating locking projection 103 and ratchet release locking projection 104 of the nut spring 100. The pressing block 113 is provided with 112 (112a, 112b, 112c).

  Specifically, a pressing block 113 formed with an unlocking rotation position restriction locking recess 112a that is locked by a rotation position restriction locking protrusion 103 formed at the tip of the T-shaped arm portion 102 in the tightening rotation direction R; The ratchet release locking recess 112b and the press block 113 formed with the ratchet engagement diameter locking recess 112c, which are latched by the ratchet release locking projection 104 formed at an intermediate position in the loose rotation direction L of the arm portion 102, are the circumferential direction. Are alternately arranged at three locations.

  In the pressing block 113, the concave depth is shallow, and the ratchet release locking projection 104 stops the diameter so that the meshing claw 105 is pressed radially inward and meshes with the ratchet gear 74 of the tip-side protruding gear part 75. The diameter stopping recess 112c is tightened by the ratchet release locking recess 112b in which the ratchet release locking projection 104 stops the diameter so that the engagement between the ratchet gear 74 of the distal side protruding gear portion 75 and the engagement claw portion 105 is released. It is arranged behind the rotation direction R.

  The spacing between the ratchet release locking recess 112b and the ratchet engagement diameter stop recess 112c is the clearance in the circumferential direction when the pressing block 113 is loosely fitted into the loose fitting recess 83 of the outer nut ring 80 in the assembled state of the chuck device 1. The ratchet release locking projection 104 is fixed to the ratchet engagement diameter stopping recess 112c in a state where the rotation position control locking projection 103 is fixed to the unlocking rotation position control locking recess 112a. Part 105 meshes with ratchet gear 74.

The sleeve rotation restricting mechanism 120 includes a slide ring 121 that is rotationally fixed with respect to the front outer sleeve 110 and is slidable in the axial direction AL, and an O-ring 122 disposed in front of the slide ring 121.
The slide ring 121 is a convex ring body in a side-view inverted configuration with an L-shaped one cross section, and is inserted from the front of the front outer sleeve 110, and the rear end portion is via a dish spring 90. It is in contact with the front end of the inner nut 70.

  The O-ring 122 is a rubber ring body having a circular cross section, is fitted into an insertion portion 132 of the cap 130 described later, and is in contact with the back surface of the substantially truncated cone-shaped cap body 130a.

  The sleeve rotation restricting mechanism 120 is rotationally fixed with respect to the chuck body 30 by sliding the slide ring 121 that is rotationally fixed with respect to the front outer sleeve 110 and slidable in the axial direction AL and presses the O-ring 122. This is a mechanism for applying a circumferential frictional force to the cap 130.

  The cap 130 has an insertion hole 131 that allows the jaw 20 to be inserted in the center in a front view, and has a substantially truncated cone-shaped cap body 130a that is laid down forward, and the above-described front outer portion on the back side of the cap body 130a. It is comprised with the insertion part 132 inserted in the front-end | tip of the sleeve 110. FIG.

Subsequently, the assembly of the chuck device 1 in which each component is configured as described above will be described below.
First, as shown in FIG. 7A, a lock washer 40, a W bearing 50 in which a W bearing outer 51, a W bearing ball 52 and a W bearing inner 53 are assembled, an outer nut ring 80, a locking ball 79 and an inner. The rotation regulation conversion unit U is assembled by assembling the rotation conversion mechanism 60 assembled with the nut 70, the dish spring 90, and the nut spring 100.

  At this time, since the locking projection 106 of the nut spring 100 is fixed to the locking recess 85 of the outer nut ring 80, the nut spring 100 and the outer nut ring 80 are rotationally fixed, and the axial direction Is also fixed and integrated. Then, as shown in FIG. 11A, from the loose fitting recess 83 between the projecting wall portions 84, the rotational position restricting locking projection 103 and the ratchet release locking projection 104 formed on the T-shaped arm portion 102. Is exposed.

  Further, as shown in FIG. 10, since the connecting groove 51f of the W bearing outer 51 constituting the W bearing 50 and the rear end side connecting convex portion 86 of the outer nut ring 80 are fitted, the W bearing outer 51 is The outer nut ring 80 is connected to the outer nut ring 80 in a freely rotatable state with the axial direction restricted.

  On the other hand, since the axial gear 51e of the W bearing outer 51 and the rear end side axial gear portion 76 of the inner nut 70 mesh with each other, the W bearing outer 51 moves the inner nut 70 in the axial direction. It is constrained in the direction of rotation while being freely movable.

  Moreover, the inner nut 70 rotatably assembled to the outer nut ring 80 via the locking ball 79 by locking the locking ball 79 in the opposing spiral locking grooves 71, 81 is shown in FIG. As shown, it is urged toward the proximal end side in the axial direction by a dish spring 90 that uses the ring portion 101 of the nut spring 100 integrated with the outer nut ring 80 as a reaction force.

  Furthermore, since the tip of the L-shaped protruding spring portion 42 in the side view of the lock washer 40 is in contact with the rear side corner portion of the W bearing outer 51 with a biasing force, the meshing gear 41a of the gear ring portion 41 and the W bearing It is separated from the meshing gear 51d formed on the rear ring surface 51b of the outer 51.

  In order to assemble the rotation regulation conversion unit U configured as described above to the chuck body 30, the diameter semicircular convex portion 43 of the lock washer 40 is fitted into the semicircular radial concave portion 34a of the second flange portion 34, and the gear The ring portion 41 is mounted so that the back surface thereof is in contact with the front surface of the second flange portion 34. As a result, the lock washer 40 is sandwiched between the second flange portion 34 and the rear ring surface 51 b of the W bearing outer 51 while being rotationally fixed to the chuck body 30.

  Then, the front outer sleeve 110 and the cap 130 are attached to the outer nut ring 80 of the rotation restriction conversion unit U attached to the chuck body 30 and the chuck device 1 is assembled. At this time, the cap 130 is press-fitted into the front body portion 36 of the chuck body 30, and the cap 130 is mounted while being rotationally fixed to the chuck body 30. Further, the pressing block 113 is loosely fitted into the loose fitting recess 83 between the protruding wall portions 84, and the ratchet release locking projection 104 is fixed to the ratchet release locking recess 112b as shown in FIG. 11B. To do.

  Therefore, the rotational position restricting projection 103 does not stop at the unlocking rotational position restricting recess 112 a, and the meshing claw 105 does not mesh with the ratchet gear 74 of the tip side protruding gear 75. Therefore, the outer nut ring 80 becomes an unregulated state in which the rotation with respect to the inner nut 70 is not regulated via the integrated nut spring 100.

  In the chuck device 1 assembled in this way, when the front outer sleeve 110 is rotated in the tightening rotation direction R and the rotational force in the tightening rotation direction R is input, the inner nut 70 is integrated as described above. Although it is in an unregulated state with respect to the outer nut ring 80 via the nut spring 100, the outer nut ring 80 is urged toward the base end side by the dish spring 90, and thus rotates integrally with the outer nut ring 80.

  As described above, the inner nut 70 is integrally rotated by the dish spring 90 by the rotational force from the outer nut ring 80, and the jaw 20 is moved forward in the inclined direction in the jaw mounting hole 37 to grip and fix the base shaft J. Next, the outer nut ring 80 is moved to the base end side by further rotation in the tightening rotation direction R with respect to the inner nut 70 temporarily fixed by using the jaw 20 holding the base shaft J as a reaction force. The inner nut 70 is rotated and fixed to the chuck body 30 by the lock washer 40 and the W bearing outer 51 that mesh with the meshing gears 41 a and 51 d against the urging force.

  Then, by further rotating the outer nut ring 80 moved to the proximal end side in the tightening rotation direction R, the inner nut 70 fixed to the chuck body 30 is moved together with the jaw 20 to the distal end side. The gripping force of the base shaft J can be improved. Therefore, the force of tightening the base shaft J with the jaw 20 can be increased, and a stable tightening state can be realized.

  Specifically, the outer nut ring 80, the plurality of jaws 20 inserted in the jaw mounting hole 37, the inner nut 70 that moves the plurality of jaws 20 in the inclined direction in synchronization with each other, and the inner nut And a dish spring 90 that biases and controls the base 70 of the chuck body 30 toward the base end side, and the helical locking grooves 71 and 81 are different from each other in the tightening rotation direction R of the outer nut ring 80 with respect to the inner nut 70. Due to the dynamic rotation, the inner nut 70 is formed in a spiral direction that makes a differential to the tip end side in the axial direction, so that the outer nut ring 80 can be moved from the outer nut ring 80 in a state where the outer nut ring 80 is not rotated by the nut spring 100 with respect to the inner nut 70. The shaft center is set by the dish spring 90 by the input rotational force. The inner nut 70 in which the differential of the direction AL is regulated is rotated integrally with the outer nut ring 80, and the jaw 20 is synchronized to move in the jaw mounting hole 37 toward the tip end side in the inclined direction to grip the base shaft J ( (See FIG. 12). Then, by gripping the base shaft J inserted into the center hole 30a, the rotation of the inner nut 70 can be temporarily fixed using the jaw 20 whose movement in the tilt direction within the jaw mounting hole 37 is restricted as a reaction force. .

  In addition, a rotation unrestricted state in which the outer nut ring 80 is rotatable relative to the inner nut 70 and a rotation in the loose rotation direction L of the outer nut ring 80 relative to the inner nut 70 are restricted by a rotational load in a predetermined tightening rotation direction R. By providing the nut spring 100 that switches between the rotation restriction states to be performed, the inner nut of the outer nut ring 80 is driven by the nut spring 100 when the rotational force input from the outer nut ring 80 exceeds a predetermined rotational load. The rotation in the loose rotation direction L with respect to 70 can be restricted. Therefore, even in an operating state in which vibration or impact occurs, the tightened state can be reliably maintained without being loosened.

  In addition, the outer nut ring 80 is connected to the outer nut ring 80 while restricting the axial direction AL, and the inner nut 70 is differentially and rotationally restricted to the axial direction AL to rotate the chuck body 30 in the rotational direction. W bearing outer 51 having a meshing gear 51d that permits the meshing, and a meshing gear 41a that is rotationally fixed to chuck body 30 and meshes with meshing gear 51d of W bearing outer 51, and second flange portion 34 As a reaction force, the W bearing outer 51 is urged toward the distal end side, and a lock washer 40 having a protruding spring portion 42 that separates the meshing gear 51d and the meshing gear 41a, and the proximal end side of the outer nut ring 80 with respect to the chuck body 30 And the second flange portion 34 for restricting movement to the outer With the inner nut 70 whose rotation is temporarily fixed by the jaw 20 whose movement in the tilt direction is restricted by the rotation of the tightening rotation direction R of the nut ring 80 as a reaction force, the outer nut ring 80 is, as shown in FIG. Against the urging force of the projecting spring portion 42 of the lock washer 40, it moves to the base end side together with the W bearing outer 51, meshes the meshing gear 51d and the meshing gear 41a, and connects the inner nut 70 to the chuck body 30. Rotate and fix.

  Further, the rotation of the outer nut ring 80 in the tightening rotation direction R continues to cause the inner nut 70 to move toward the distal end side in the axial direction AL with respect to the outer nut ring 80 against the urging of the dish spring 90 toward the base end side. Differential. A plurality of jaws 20 synchronized with the inner nut 70 differential with respect to the outer nut ring 80 can be integrally pressed against the inner wall surface of the jaw mounting hole 37 to improve the gripping force of the jaw 20 against the base shaft J. .

  In order to operate smoothly as the chuck device 1, a combination is provided in each combination of components, but a plurality of jaws 20 integrated by screwing with the inner nut 70 are pressed against the inner wall surface of the jaw mounting hole 37. Therefore, asobi is absorbed and a firm tightening state can be realized.

  Further, since the plurality of jaws 20 are pressed against the inner wall surface of the jaw mounting hole 37 together with the inner nut 70 integrated by screwing, the pitch of the screw thread where the inner nut 70 and the jaw 20 are screwed, that is, the thread A firm tightening state can be maintained regardless of the interval.

  Specifically, the angle between the screw groove and the screw groove of the jaw in the chuck device is generally set to 16 to 24 threads / inch based on the tightening speed and the tightening force. Increasing the number of threads per unit length, that is, decreasing the thread pitch and loosening the spiral angle of the thread groove slows the jaw in the tilt direction with respect to rotation, but increases the tightening force accordingly. .

  Conversely, if the number of threads per unit length is reduced, that is, the pitch of the threads is increased and the spiral angle of the thread groove is tightened, movement of the jaw in the inclination direction with respect to rotation is accelerated and operability is improved. However, the tightening force is reduced accordingly.

  Therefore, the number of threads per unit length, that is, the pitch of the threads, is set based on the balance between the movement of the jaw in the tilt direction with respect to the rotation and the tightening force. Since the plurality of jaws 20 are pressed together with the inner nut 70 against the inner wall surface of the jaw mounting hole 37, the number of screw threads with which the inner nut 70 and the jaw 20 are screwed, that is, the pitch of the threads is not affected. A firm tightening state can be realized.

  Further, by providing the locking balls 79 that are locked between the helical locking grooves 71 and 81, the helical locking grooves 71 and 81 can be more reliably locked in the spiral direction.

  In addition, since the plurality of locking balls 79 are arranged along the spiral locking grooves 71 and 81, in the locking in the spiral direction with the spiral locking grooves 71 and 81, there is no resistance. The differential rotation generated by the nut spring 100 can be efficiently and smoothly changed to the differential in the axial direction AL of the inner nut 70 relative to the outer nut ring 80.

  Further, the spiral locking groove 71 is formed in a spiral shape of less than one round, and the ends of the spiral locking groove 71 are connected in a direction intersecting the spiral direction of the spiral locking grooves 71 and 81. The locking groove 71a is connected to form a closed loop shape, and the locking ball 79 that locks the connection locking groove 71a to the connection locking groove 71a does not lock the opposing spiral locking groove 81. Therefore, the locking ball 79 can circulate through the spiral locking groove 71 and the spiral locking groove 71. Therefore, a small number of the locking balls 79 circulate between the spiral locking groove 71 and the spiral locking groove 81, and the rotation input by the outer nut ring 80 is rotated in the axial direction AL of the inner nut 70. It can be converted to a movement of direction.

  Further, since the connection locking groove 71a is formed by a circular groove having a cross section of 4/5 so that the upper portion of the locking ball 79 to be locked is exposed, the connection locking groove 71a is engaged with the connection locking groove 71a in the direction intersecting the spiral direction. The stop ball 79 is not carelessly removed, and the rotation of the inner nut 70 relative to the outer nut ring 80 in the rotation conversion mechanism 60 is not prevented from being converted into the differential in the front-rear direction of the inner nut 70 relative to the outer nut ring 80. .

  The mounting groove member 72b is formed of a highly deformable rubber, so that the connection locking groove 71a formed of a circular groove having a 4/5 cross section can be easily press-molded using a mold. It may be a method, and may be composed of resin or metal,

  In addition, the W bearing outer 51 is formed in a ring shape having a rear ring surface 51b that disposes the meshing gear 51d in the circumferential direction on the proximal end side, and the lock washer 40 is disposed in the circumferential direction on the distal end side. By arranging a plurality of ring-shaped gear ring portions 41 and a plurality of projecting spring portions 42 that protrude from the outer periphery of the gear ring portion 41 toward the front end side and urge the W bearing outer 51 toward the front end side at equal intervals in the circumferential direction. The rotation / fixation of the inner nut 70 relative to the body 30 can be reliably switched with a simple structure.

  Specifically, the W bearing outer 51 is formed in a ring shape having a rear ring surface 51b in which the meshing gear 51d is disposed in the circumferential direction on the base end side, the lock washer 40 is disposed in the circumferential direction on the distal end side. And a plurality of projecting spring portions 42 that protrude from the outer periphery of the gear ring portion 41 toward the front end side and bias the W bearing outer 51 toward the front end side at equal intervals in the circumferential direction. Thus, the W bearing outer 51 is urged toward the tip by the projecting spring portion 42 to separate the W bearing outer 51 and the meshing gears 51d and 41a of the lock washer 40, and the deflection of the projecting spring portion 42 causes the W bearing to be separated. The outer 51 and the meshing gears 51d and 41a of the lock washer 40 can be meshed. Accordingly, the separation and engagement of the W bearing outer 51 and the meshing gears 51d and 41a of the lock washer 40 can be controlled and switched by the number, shape or elasticity of the protruding spring portion 42.

  Further, in this manner, the nut spring 100 is in a locked state in which the nut body 100 is rotationally fixed with respect to the chuck body 30. Further, in the state where the base shaft J is gripped by the jaw 20, the sleeve rotation restricting mechanism 120 causes the front outer sleeve 110 to move. The rotation is restricted with respect to the chuck body 30 and, for example, the front outer sleeve 110 is prevented from inadvertently rotating in the loosening direction due to vibration or impact caused by the use of a rotating jig.

  Specifically, as described above, the distal end of the axial direction AL with respect to the outer nut ring 80 against the urging of the base end side by the dish spring 90 due to the rotation of the outer nut ring 80 in the tightening rotation direction R. The inner nut 70 that is differential to the side presses the slide ring 121 of the sleeve rotation restricting mechanism 120 forward (see arrow A in the enlarged view of FIG. 6a). The slide ring 121 that slides forward by pressing the inner nut 70 presses the O-ring 122 against the back surface of the cap body 130 a of the cap 130. The friction between the O-ring 122 pressed against the back surface of the cap main body 130a and the circumferential direction of the cap main body 130a, and the periphery of the O-ring 122 and the slide ring 121 slidably and rotationally restrained with respect to the front outer sleeve 110 The friction in the direction increases, and the front outer sleeve 110 is press-fitted into the front body portion 36 of the chuck body 30 and is attached to the chuck body 30 via a cap 130 that is mounted while being rotationally fixed to the chuck body 30. On the other hand, rotation is restricted.

  Accordingly, the rotational position restriction locking projection 103 of the nut spring 100 is held by being locked by its own urging force with respect to the unlocking rotation position restriction locking recess 112a of the pressing block 113 of the front outer sleeve 110. In the locked state of the rotation restriction conversion unit U, the front outer sleeve 110 whose rotation direction differential is restricted with respect to the chuck body 30 due to friction in the rotation direction of the sleeve rotation restriction mechanism 120 is inadvertently rotated in the loosening direction. Thus, it is possible to prevent the rotation regulation conversion unit U from being inadvertently released. That is, since the rotation restriction conversion unit U and the sleeve rotation restriction mechanism 120 cooperate to hold the locked state, it is possible to establish a stable locked state that is not inadvertently released.

  As described above, the chuck device 1 including the sleeve rotation restriction mechanism 120 can stably maintain the gripping state of the base shaft J by the jaw 20 by the rotation restriction conversion unit U.

  When the chucking state by the chuck device 1 is released and the base shaft J is removed, the front outer sleeve 110 is loosened via the front outer sleeve 110 and rotated in the rotation direction L. At this time, since the pressing block 113 is loosely fitted in the loose fitting recess 83, the front outer sleeve 110 is loosened relative to the outer nut ring 80 and differentially rotates in the rotation direction L.

  Due to the differential rotation of the front outer sleeve 110 in the loose rotation direction L with respect to the outer nut ring 80, the ratchet release locking projection 104, which has been stopped by the ratchet engagement diameter locking recess 112c, has a diameter at the ratchet release locking recess 112b. It stops, and it returns to an outer diameter side by the elastic force of the T-shaped arm part 102, and the meshing | engagement with the ratchet gear 74 of the meshing claw part 105 is cancelled | released. Further, the outer nut ring 80 is rotated and fixed in the rotational direction L of the outer nut ring 80, so that the pressing state of the inner nut 70 that is fixed to the chuck body 30 and pressed to the distal end side together with the integrated jaw 20 is eliminated. Therefore, the inner nut 70 rotates integrally with the outer nut ring 80 again in the loose rotation direction L by the urging force toward the proximal end of the dish spring 90, and the jaw 20 screwed with the inner nut 70 has the jaw mounting hole 37. The inner shaft moves to the proximal end side, the gripping of the base shaft J by the jaw 20 is eliminated, and the base shaft J can be taken out from the center hole 30a.

  Further, when the outer nut ring 80 is rotated in the loose rotation direction L, the pressing state of the inner nut 70 is also eliminated, so that the rotation restriction of the sleeve rotation restricting mechanism 120 is also eliminated, and the front outer sleeve 110 is smoothly loosened. The base shaft J can be taken out from the center hole 30a by rotating in the direction to cancel the gripping of the base shaft J by the jaw 20.

As described above, in the chuck device 1, the rotation conversion mechanism 60 is used to move the jaw 20 forward in the tilt direction and forward in the axial direction AL, but separately from the chuck device 1, for example, As shown in FIGS. 13 and 14, the rotation conversion mechanism K may be used alone.
13A is an exploded perspective view of the rotation conversion mechanism K, and FIG. 13B is a perspective view of the rotation conversion mechanism K.

  The rotation converting mechanism K includes an inner diameter member Ki having a helical locking groove KiA on the outer peripheral surface, an outer diameter member Ko having a helical locking groove KoA on the inner peripheral surface, a helical locking groove KiA, It is comprised by the latching ball B latched to both KoA.

  The spiral locking grooves KiA and KoA are spiral grooves having the same direction and the same spiral angle, and the helical locking groove KoA is formed with a length corresponding to a plurality of circumferences in the spiral direction. KiA is formed with a length of less than one round in the spiral direction. The ends of the spiral locking groove KiA are connected by a connecting locking groove KiA2 in a direction intersecting with the spiral direction to form a closed loop shape.

  The connection locking groove KiA2 is formed in an attachment groove member Ki2 configured to be attachable to a recess formed in the outer peripheral surface of the inner diameter member Ki. As shown in FIG. Since it is formed deeper than the helical locking groove KiA, the locking ball B locked to the connection locking groove KiA2 does not lock to the helical locking groove KoA of the outer diameter member Ko. The material of the mounting groove member Ki2 and the depth of the connection locking groove KiA2 with respect to the locking ball B are the same as those of the rotation conversion mechanism 60 described above.

  Therefore, the rotation conversion mechanism K is configured so that the rotation conversion mechanism K of the rotation conversion mechanism 60 in the above-described chuck device 1 can circulate through the helical engagement groove KiA that forms a closed loop shape by the coupling engagement groove KiA2. The same effects as the effects can be achieved.

In the correspondence between the configuration of the present invention and the above-described embodiment, the outer diameter member of the present invention corresponds to the outer nut ring 80 and the outer diameter member Ko,
Similarly,
The inner member and the nut correspond to the inner nut 70 and the inner member Ki,
The outer radial spiral groove corresponds to the helical locking groove 81, KoA,
The inner diameter spiral groove corresponds to the spiral locking groove 71, KiA,
The rolling member corresponds to the locking balls 79 and B,
The connecting groove corresponds to the connecting locking groove 71a, KiA2,
Another member corresponds to the mounting groove member 72b, Ki2,
The chuck body corresponds to the chuck body 30,
The inclined hole corresponds to the jaw mounting hole 37,
The chuck claw corresponds to the jaw 20,
The rotary input operating body corresponds to the front outer sleeve 110,
The rotation limiting means corresponds to the sleeve rotation restricting mechanism 120,
The slide member corresponds to the slide ring 121,
The rotating friction member corresponds to the O-ring 122,
The present invention is not limited only to the configuration of the above-described embodiment, and many embodiments can be obtained.

  For example, in the rotation conversion mechanism 60, a helical spiral locking groove 81 for a plurality of rounds is formed on the inner peripheral surface of the outer nut ring 80, and a closed loop shape is formed by the connection locking groove 71a in the inner nut 70. The connection locking groove 71a of the inner nut 70 is formed in a spiral shape for a plurality of turns, the nut 280 forms a helical locking groove 81 of less than one turn, and the ends of the helical locking groove 81 are connected and locked together. While connecting with the groove | channel 71a, you may comprise the part which forms the helical locking groove 81a with another member attached to the main body inner peripheral surface side of the outer nut ring 80. FIG. Further, although the rotation conversion mechanism 60 is moved forward, a configuration may be adopted in which the sleeve rotation restriction mechanism 120 and the sleeve rotation restriction mechanism 220 are operated by moving backward.

DESCRIPTION OF SYMBOLS 1 ... Chuck apparatus 20 ... Jaw 30 ... Chuck body 30a ... Shaft hole 37 ... Jaw mounting hole 60 ... Rotation conversion mechanism 70 ... Inner nut 71 ... Spiral locking groove 71a ... Connection locking groove 72b ... Mounting groove member 79 ... Engagement Stop ball 80 ... Outer nut ring 81 ... Spiral locking groove 110 ... Front outer sleeve 120 ... Sleeve rotation regulating mechanism 121 ... Slide ring 122 ... O-ring B ... Locking ball K ... Rotation conversion mechanism K
Ki ... inner diameter member KiA ... spiral locking groove KiA2 ... connection locking groove Ki2 ... mounting groove member Ko ... outer diameter member KoA ... spiral locking groove

Claims (4)

A rotation conversion mechanism that converts rotation on the axis and movement in the axis direction,
An outer diameter member having a circular opening formed by a cylindrical inner peripheral surface;
A cylindrical inner member disposed in the circular opening such that an outer peripheral surface faces the inner peripheral surface;
A rotation converting means for converting and transmitting a relative rotation with respect to the other one of the outer diameter member and the inner diameter member and a relative movement in the axial direction with respect to the other one;
The rotation converting means;
A radially outer spiral groove formed spirally with respect to the axial direction formed on the inner peripheral surface of the outer member;
An inner diameter spiral groove formed on the outer peripheral surface of the inner diameter member and formed in the spiral shape in the same direction as the outer diameter spiral groove;
It comprises a plurality of rolling members that engage and roll in both the outer radial spiral groove and the inner radial spiral groove,
One of the radially outer spiral groove and the radially inner spiral groove is configured in a spiral shape for a plurality of turns in the rotation direction, and the other is configured in a spiral shape for less than one turn in the rotation direction,
In the other spiral groove, it is configured in a closed loop with a connecting groove that connects the ends of the spiral groove formed in a spiral shape less than one round,
The connecting groove is formed with a depth at which the rolling member that engages with the connecting groove is released from the engagement with one spiral groove, and a portion that forms the connecting groove is formed with a spiral less than one round. The rotation conversion mechanism comprised with the separate member which can be attached with respect to the member main body in which the spiral groove comprised by the shape was formed. While forming the other spiral groove formed in a spiral shape less than one round on the outer peripheral surface of the inner diameter member,
The rotation conversion mechanism according to claim 1, wherein one spiral groove configured in a spiral shape for a plurality of circumferences in the rotation direction is formed on an inner circumferential surface of the outer diameter member. A chuck device to be mounted on a drive device having a drive shaft rotatable on an axis,
A substantially cylindrical chuck body that is disposed on the axis and has a shaft hole that allows insertion of the base shaft of the rotating jig on the tip side;
In the chuck main body, a plurality of holes are arranged on the front end side so as to communicate with the shaft hole, and are inserted into inclined holes opened to the side of the chuck main body on the rear end side so as to be movable with respect to the chuck main body. Chuck nails,
A nut that is rotatably held by the chuck body, and that moves the inside of the inclined hole in an inclined direction by synchronizing the plurality of chuck claws by screwing with the chuck body and the chuck claws;
A rotary input body that is rotatably mounted on the chuck body and inputs a rotational force by a rotating operation;
Rotation restricting means for rotating the nut and the rotation input body together and rotating the nut and the rotation input body differentially by a predetermined rotation load;
Rotation conversion means for converting differential rotation between the nut and the rotation input body by the rotation restricting means into differential toward the front end side in the axial direction;
While forming the nut and the rotary input body in a ring shape,
3. A chuck device in which one of the nut and the rotation input body is constituted by the inner diameter member in the rotation conversion mechanism according to claim 1 or 2, and the other is constituted by the outer diameter member. A rotational input operating body for performing rotational force input operation on the rotational input body;
A chuck device comprising: a rotation restricting means for restricting rotation of the rotation input operation body in a tightened state with respect to the chuck body by a frictional force in a rotation direction.

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