JP6714230B1 - Tool holder - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a tool holder capable of causing a mounted tool to simultaneously perform a rotating operation and a linear reciprocating operation without providing a fixing structure on the machine tool side. A tool holder (1) is supported by an outer ring member (3) so as to be movable in an axial direction (X) of an input shaft (2), an outer ring member (3) that rotates together with the input shaft (2), and the outer ring member (3). And an output member 4 that rotates together with the output member 4. Further, in the tool holder 1, when the input shaft 2 and the outer ring member 3 rotate together, the brake mechanism 50 that lowers the rotation speed of the outer ring member 3 below the rotation speed of the input shaft 2, and the rotation speed of the outer ring member 3. Is lower than the rotation speed of the input shaft 2 and the input shaft 2 and the output member 4 rotate relative to each other, a linear reciprocating motion in the axial direction X is given to the output member 4 which is rotating together with the outer ring member 3. The linear reciprocating motion imparting mechanism 8 is provided. [Selection diagram] Figure 2

Description

The present invention relates to a tool holder interposed between a head of a machine tool and a tool.

A tool holder used by being connected to a head of a spindle of a machine tool is disclosed in Patent Document 1. The tool holder of Patent Document 1 includes an input shaft connected to a head of a machine tool, a holder to which a cutting tool is connected, and a cover rotatably supported by the input shaft. The holder rotates with the input shaft inside the cover. The holder includes pins radially protruding from the outer peripheral surface. The cover is fixed to the machine spindle cover, which is a member on the machine tool side, and does not rotate with the rotation of the input shaft. The cover includes, on the inner peripheral surface thereof, a corrugated cam surface that is uneven in the axial direction along the circumferential direction. The pin of the holder is pressed against the corrugated cam surface by the coil spring.

When the pin moves axially along the corrugated cam surface as the holder rotates with the input shaft, the holder reciprocates in the axial direction while rotating. As a result, the cutting tool connected to the holder vibrates in the axial direction while rotating to perform cutting.

Japanese Utility Model Publication No. 7-27734

When the input shaft connected to the head of the machine tool rotates, the tool holder of Patent Document 1 can cause the holder holding the cutting tool to simultaneously perform the rotational operation and the linear reciprocating operation in the axial direction. However, in order to add a linear reciprocating motion in the axial direction to the rotary motion of the holder, the cover having the corrugated cam surface must be fixed to the member on the machine tool side. Therefore, when using the tool holder, it is necessary to provide a fixing structure for fixing the cover to the member on the machine tool side, and it is necessary to modify the machine tool. Further, when the tool holder is attached to the machine tool, the work of fixing the cover must be performed in addition to the work of connecting the input shaft and the head, which makes the attachment work troublesome.

In view of the above problems, an object of the present invention is to provide a tool holder capable of causing a mounted tool to simultaneously perform a rotating operation and a linear reciprocating operation without providing a fixing structure on the machine tool side. is there.

To solve the above problems, the tool holder of the present invention is an input shaft, rotatably supported by the input shaft, and an outer ring member that rotates together with the input shaft, and is arranged coaxially with the input shaft, When the output member, which is supported by the outer ring member and rotates integrally with the outer ring member in a state of being movable in the axial direction of the input shaft, and the input shaft and the outer ring member rotate together, A brake mechanism that reduces the rotation speed below the rotation speed of the input shaft, and when the rotation speed of the outer ring member falls below the rotation speed of the input shaft and the input shaft and the output member rotate relative to each other, the outer ring A linear reciprocating motion imparting mechanism that imparts a linear reciprocating motion in the axial direction to the output member that is rotating integrally with the member, and the brake mechanism applies a fluid pressure acting in a direction opposite to the rotating direction. The pressure receiving portion is a flap attached to the outer ring member, and the output member includes a tool holding portion for holding a tool.

According to the present invention, when the input shaft connected to the head rotates and the outer ring member rotates together with the input shaft, a fluid pressure in a direction opposite to the rotation direction acts on the pressure receiving portion, so that the outer ring member and the input shaft are separated from each other. There is a difference in rotational speed between them. As a result, the output member that rotates integrally with the outer ring member and the input shaft rotate relative to each other. Therefore, the linear reciprocating motion imparting mechanism imparts a linear reciprocating motion in the axial direction to the output member that is rotating. Therefore, in the present invention, it is not necessary to fix the outer ring member to the machine tool in order to generate the linear reciprocating motion of the rotating output member in the axial direction. Therefore, it is possible to cause the tool to simultaneously perform the rotating operation and the linear reciprocating operation without modifying the machine tool such as providing a fixing structure. Therefore, it is easy to attach the tool holder to the machine tool. Here, the fluid pressure applied to the flap is the pressure of a liquid such as air or water existing around the tool holder.

In the present invention, when the outer ring member is switched from a stopped state to a rotating state, a flap opening operation is performed in which the flap is changed to an open position in which the fluid pressure is received, and the outer ring member is switched from a rotating state to a stopped state. It is desirable that a flap closing operation is performed in which the flap is changed to a closed posture that does not receive fluid pressure. If the opening/closing operation of the flap is automatically performed depending on whether or not the outer ring member is rotated, the flap can be reliably opened during rotation. Further, since the flap is not left open when the rotation is stopped, damage to the flap and interference between the flap and surrounding objects can be suppressed.

In the present invention, it is preferable that the flap swing to the outer peripheral side around a connecting portion connected to the outer ring member and change to the open posture by a centrifugal force that acts when the outer ring member rotates. .. With this configuration, the flap can be opened without providing a drive source for opening the flap.

Further, the brake mechanism may include a flap urging member that urges the flap toward the inner peripheral side, and the flap closing operation may be performed by the urging force of the flap urging member. With this configuration, the flap can be closed without providing a drive source for closing the flap.

In the present invention, the linear reciprocating motion imparting mechanism includes a first magnet unit and a second magnet unit facing the first magnet unit in the axial direction, and the first magnet unit is provided on the input shaft. The second magnet unit is fixed, the second magnet unit is fixed to the output member, and when the first magnet unit and the second magnet unit rotate relative to each other, the second magnet unit is fixed between the first magnet unit and the second magnet unit. A first state in which an attractive force in the axial direction acts and a second state in which the repulsive force in the axial direction acts between the first magnet unit and the second magnet unit may alternately occur. .. With this configuration, the linear reciprocating motion can be imparted to the output member by utilizing the attractive force and the repulsive force generated between the two magnet units.

In the present invention, the linear reciprocating motion imparting mechanism causes the output member to move when the output member moves in a direction away from the input shaft due to a repulsive force between the first magnet unit and the second magnet unit. An output member urging member that exerts an urging force that urges the input shaft can be provided. With this configuration, when the output member moves in the direction approaching the input shaft due to the attractive force between the first magnet unit and the second magnet unit, the output member moves due to the urging force of the output member urging member. Can be assisted.

In the present invention, the linear reciprocating motion imparting mechanism includes a cam surface in which the projections and depressions in the axial direction are arranged in the circumferential direction, a cam follower that abuts the cam surface in the axial direction, and one of the cam surface and the cam follower. An urging member that presses against the other, one of the cam surface and the cam follower is provided on the input shaft, the other of the cam surface and the cam follower is provided on the output member, and the urging member is The output member may be biased toward the input shaft. With this configuration, when the input shaft and the output member rotate relative to each other, the cam follower slides on the cam surface having the unevenness, so that the output member can perform the linear reciprocating motion.

In the present invention, the linear reciprocating motion imparting mechanism includes an input gear that rotates integrally with the input shaft, and an output gear that meshes with the input gear and rotates about an intersecting axis intersecting the axis. And a link member whose one end is connected to a portion deviated from the rotation center of the output gear and whose other end is connected to the output member. With this configuration, when the input shaft and the output member rotate relative to each other, the output member can perform the linear reciprocating operation.

According to the present invention, when the input shaft connected to the head of the machine tool rotates and the outer ring member rotates together with the input shaft, a fluid pressure in a direction opposite to the rotation direction acts on the pressure receiving portion, and the outer ring member and the input shaft. There is a difference in rotation speed between and. As a result, the output member that rotates integrally with the outer ring member and the input shaft rotate relative to each other. Therefore, the linear reciprocating motion imparting mechanism imparts a linear reciprocating motion in the axial direction to the output member that is rotating. Therefore, in the present invention, it is not necessary to fix the outer ring member to the machine tool in order to generate the linear reciprocating motion of the rotating output member in the axial direction. Therefore, it is possible to cause the tool to simultaneously perform the rotating operation and the linear reciprocating operation without modifying the machine tool such as providing a fixing structure.

3 is an external perspective view of the tool holder according to the first embodiment. FIG. It is an AA sectional view of FIG. It is a BB sectional view of FIG. It is a perspective view of a 2nd outer ring member. It is a cross-sectional view of the tool holder with the flap closed. It is a cross-sectional view of the tool holder with the flap open. It is an exploded perspective view of a linear reciprocating motion imparting mechanism. It is explanatory drawing which shows arrangement|positioning of the magnetic pole in a magnet unit. It is sectional drawing of the tool holder in the state which the output member moved to the 2nd direction. It is sectional drawing of the tool holder of Example 2. FIG. 7 is a perspective view of a linear reciprocating motion imparting mechanism according to a second embodiment. 7 is a perspective view of a second outer ring member of Example 2. FIG. It is sectional drawing of the tool holder of Example 3. It is a perspective view of a linear reciprocating motion imparting mechanism of the third embodiment.

An embodiment of a tool holder to which the present invention is applied will be described below with reference to the drawings.

[Example 1]
(overall structure)
FIG. 1 is an external perspective view of the tool holder 1 according to the first embodiment. The tool holder 1 includes an input shaft 2, an outer ring member 3 rotatably supported by the input shaft 2, an output member 4, and a flap 5 attached to the outer ring member 3. The outer ring member 3 includes a cylindrical portion 34 that surrounds the input shaft 2 from the outer peripheral side. The outer ring member 3 rotates together with the input shaft 2. The output member 4 is arranged coaxially with the input shaft 2. The output member 4 is supported by the outer ring member 3 so as to be movable in the axial direction X along the axis L of the input shaft 2. The output member 4 is non-rotatable with respect to the outer ring member 3 and rotates integrally with the outer ring member 3. The output member 4 includes a tool holding portion 11 to which a tool 15 is detachably attached. The flap 5 opens and closes radially on the outer peripheral side of the outer ring member 3. In the state shown in FIG. 1, the flaps 5 are open radially.

The tool holder 1 is used by connecting the input shaft 2 to a head 100 of a machine tool such as a machining center. A tool 15 is held in the tool holding portion 11 of the output member 4. In the example shown in FIG. 1, a brush-shaped grindstone is held as the tool 15 in the tool holding unit 11. When the tool 15 is connected to the head 100 via the tool holder 1, the rotation center line of the head 100 and the axis L of the input shaft 2 coincide with each other. When machining a work, the machine tool is driven to rotate the head 100 around the rotation center line and move the tool 15 in the intersecting direction intersecting with the rotation center line to bring the tool 15 into contact with the work. ..

In the following description, one side of the axial direction X along the axis L of the input shaft 2 is a first direction X1 and the other side of the axial direction X is a second direction X2. The first direction X1 is the side on which the input shaft 2 is located with respect to the output member 4, and the second direction X2 is the opposite side. The input shaft 2 projects from the outer ring member 3 in the first direction X1. The tip portion of the output member 4 projects from the tip of the outer ring member 3 in the second direction X2. A tool holder 11 is provided at the tip of the output member 4.

2 and 3 are cross-sectional views of the tool holder 1 according to the first embodiment. FIG. 2 is a cross-sectional view taken along the line AA of FIG. FIG. 3 is a sectional view taken along line BB in FIG. FIG. 4 is a perspective view of the second outer ring member when viewed from the first direction X1. As shown in FIGS. 2 and 3, the input shaft 2 includes a first shaft portion 21 protruding from the outer ring member 3 in the second direction X2 and a second shaft portion 22 arranged inside the outer ring member 3. Prepare In this example, the second shaft portion 22 has a smaller diameter than the first shaft portion 21. The outer ring member 3 includes a first outer ring member 31 to which the opening/closing flap 5 is attached, a second outer ring member 32 fixed to an end of the first outer ring member 31 in the second direction X2, and a first outer ring member 31. And a disk-shaped end plate member 33 fixed to the end portion in the first direction X1.

As shown in FIGS. 2 and 3, the first outer ring member 31 extends from the inner peripheral side of the flap 5 in the axial direction X to the cylindrical portion 34, and from the end of the cylindrical portion 34 in the second direction X2 to the outer peripheral side. A disk portion 35 is provided. The second shaft portion 22 of the input shaft 2 has the bearing portion 6 arranged inside the end of the cylindrical portion 34 in the first direction X1 and the inside of the end of the cylindrical portion 34 in the second direction X2. Is rotatably supported by. In this example, the bearing portion 6 is a ball bearing. The first shaft portion 21 of the input shaft 2 penetrates a circular opening portion 36 provided in the center of the end plate member 33 and projects from the opening portion 36 in the first direction X1.

As shown in FIG. 4, the contour shape of the second outer ring member 32 when viewed from the first direction X1 side is circular. As shown in FIGS. 1 to 3, the second outer ring member 32 includes a body portion 37 that abuts the disc portion 35 of the first outer ring member 31 from the second direction X2, and a body portion 37 that is coaxial with the body portion 37. Also, a small-diameter body portion 38 having a small outer diameter dimension and a taper portion 39 connecting the body portion 37 and the small-diameter body portion 38 are provided. As shown in FIG. 4, the body portion 37 includes a circular recess 40 on the end face in the first direction X1. The recess 40 is provided coaxially with the body portion 37. Therefore, the end portion of the second outer ring member 32 in the first direction X1 is tubular. As shown in FIG. 2, the first magnet unit 81 is housed in the recess 40. Details of the first magnet unit 81 will be described later.

As shown in FIG. 4, at the center of the bottom surface of the recess 40, a shaft hole 41 that penetrates the body portion 37, the tapered portion 39, and the small diameter body portion 38 in the axial direction X is provided. The linear bush 7 is inserted into the shaft hole 41. The linear bush 7 is fixed to an end portion of the inner peripheral surface of the shaft hole 41 in the second direction X2. The linear bush 7 is located inside the small-diameter body portion 38 in the radial direction.

Further, on the bottom surface of the recess 40, a pair of circular recesses 42 are provided on both sides with the shaft hole 41 interposed therebetween. When viewed from the axial direction X, the shaft hole 41 and each circular recess 42 partially overlap each other in the radial direction. Therefore, the hole portion of the shaft hole 41 on the first direction X1 side of the linear bush 7 and the pair of circular recesses 42 communicate with each other in the radial direction. Disk-shaped stopper members 43 are arranged on the bottom surfaces of the pair of circular recesses 42, respectively. Here, as shown in FIG. 2, the second magnet unit 82 is housed in the hole portion of the shaft hole 41 on the first direction X1 side of the linear bush 7 and in the pair of circular recesses 42. That is, the hole portion of the shaft hole 41 on the side of the linear bush 7 in the first direction X1 and the pair of circular recesses 42 form a second magnet unit housing portion 44 that houses the second magnet unit 82. The second magnet unit housing portion 44 receives the second magnet unit 82 in a state of being movable in the axial direction X. Details of the second magnet unit 82 will be described later.

Further, the bottom surface of the recess 42 is provided with a pair of groove portions 45 extending from the shaft hole 41 to both sides in the radial direction. Each groove 45 extends in a direction orthogonal to the direction in which the pair of circular recesses 42 face each other.

As shown in FIG. 2, the end portion of the body portion 37 in the first direction X1 is screwed to the disc portion 35. The output member 4 extends through the shaft hole 41 of the second outer ring member 32 and the linear bush 7. The linear bush 7 allows the output member 4 to move in the axial direction X and restricts rotation around the axis L. Therefore, the output member 4 is supported by the second outer ring member 32 in a state of being movable in the axial direction X and not rotatable about the axis L. Therefore, when the input shaft 2 rotates and the outer ring member 3 rotates in the same rotation direction as the input shaft 2, the output member 4 rotates together with the linear bush 7 together with the outer ring member 3.

Here, the tool holder 1 includes a brake mechanism 50 that reduces the rotation speed of the outer ring member 3 with respect to the rotation speed of the input shaft 2 when the outer ring member 3 rotates. Further, when the rotation speed of the outer ring member 3 becomes lower than the rotation speed of the input shaft 2 and the input shaft 2 and the output member 4 relatively rotate, the tool holder 1 rotates together with the outer ring member 3. A linear reciprocating motion imparting mechanism 8 that imparts a linear reciprocating motion in the axial direction X to the output member 4 is provided.

(Brake mechanism)
FIG. 5 is a cross-sectional view of the tool holder 1 with the flap 5 closed. FIG. 6 is a cross-sectional view of the tool holder 1 with the flap 5 open. FIG. 5 and FIG. 6 are cross-sectional views when cut at the CC position in FIG.

As shown in FIGS. 1, 5, and 6, the brake mechanism 50 includes a flap 5 attached to the outer ring member 3, and a flap urging member 51 that urges the flap 5 toward the inner peripheral side. The flap 5 is a pressure receiving portion that receives a fluid pressure acting in a direction opposite to the rotation direction when the outer ring member 3 is rotating. The fluid pressure received by the flap 5 is the pressure of air existing around the tool holder 1. The flap urging member 51 is a coil spring hung between the flap 5 and the first outer ring member 31. The flap urging member 51 is not limited to the configuration of this example. For example, a torsion coil spring or the like may be attached to the shaft portion 52 of the flap 5 to urge the flap 5 in the closing direction.

The flap 5 changes to a closed posture 5A shown in FIG. 5 and an open posture 5B shown in FIGS. 1 and 6. The flap 5 has an arcuate shape when viewed from the axial direction X. The flap 5 includes a shaft portion 52 arranged at one end in the circumferential direction. A shaft hole 53 is formed at the center of the shaft portion 52. A support shaft 54 is inserted into the shaft hole 53. An end portion of the support shaft 54 in the first direction X1 is screwed to the end plate member 33, and an end portion in the second direction X2 is locked to the disc portion 35 of the second outer ring member 32. Therefore, the flap 5 can swing about the shaft portion 52.

In the brake mechanism 50, the flap 5 moves from the closed posture 5A shown in FIG. 5 to the opened posture 5B shown in FIG. 6, and when the flap 5 moves from the opened posture 5B shown in FIG. 6 to the closed posture 5A shown in FIG. Performs changing flap opening action. The flap opening operation is performed by the centrifugal force acting on the flap 5 when the outer ring member 3 is switched from the stopped state to the rotated state. That is, when the centrifugal force becomes larger than the biasing force of the flap biasing member 51, the flap 5 swings to the outer peripheral side and the flap opening operation is performed. The flap closing operation is performed when the outer ring member is switched from the rotating state to the stopped state. That is, it is performed when the rotation speed of the outer ring member 3 decreases and the urging force of the flap urging member 51 becomes larger than the centrifugal force.

The brake mechanism 50 suppresses an increase in the rotation speed of the outer ring member 3 due to the fluid pressure acting on the flap 5. That is, the outer ring member 3 rotates together with the input shaft 2 when the input shaft 2 starts to rotate, but when the flap 5 is opened by the centrifugal force, the increase in the rotation speed of the outer ring member 3 is suppressed by the fluid pressure received by the flap 5. It As a result, the rotation speed of the outer ring member 3 becomes lower than the rotation speed of the input shaft 2, so that the outer ring member 3 and the input shaft 2 rotate relative to each other. As a result, the output member 4 which rotates integrally with the outer ring member 3 and the input shaft 2 also rotate relatively.

(Linear reciprocating motion imparting mechanism)
FIG. 7 is an exploded perspective view of the linear reciprocating motion imparting mechanism 8. The linear reciprocating motion imparting mechanism 8 is provided inside the outer ring member 3. As shown in FIGS. 2, 3, and 7, the linear reciprocating motion imparting mechanism 8 faces the first magnet unit 81 that rotates integrally with the input shaft 2 and the first magnet unit 81 from the second direction X2. And a second magnet unit 82. Further, the linear reciprocating motion imparting mechanism 8 includes an output member biasing member 83 that biases the output member 4 in the axial direction X via the second magnet unit 82, as shown in FIGS. 2 and 3.

The first magnet unit 81 is fixed to the input shaft 2. That is, the first magnet unit 81 includes the circular disc 84 screwed to the end of the input shaft 2 in the second direction X2, the four washers 85 screwed to the disc 84, and the washer 85. And four first magnets 86 fixed to the disk 84. The first magnet unit 81 is housed in the recess 40 provided in the body portion 37 of the second outer ring member 32.

The second magnet unit 82 is fixed to the output member 4. Therefore, the second magnet unit 82 rotates around the axis line together with the output member 4 and moves in the axial direction X together with the output member 4. The second magnet unit 82 has a first lever 87 fixed to an end of the output member 4 in the first direction X1 and two pieces fixed to both ends of the first lever 87 with a first headed screw 90. Washer 88, and two second magnets 89 fixed to the first lever 87 via the washer 88. The first lever 87 extends in a direction orthogonal to the input shaft 2. The first headed screw 90 penetrates the first lever 87 from the second direction X2 in the first direction X1. The first lever 87 is non-rotatably connected to the output member 4 by a second headed screw 93 penetrating the central portion thereof. The second headed screw 93 penetrates the first lever 87 from the first direction X1 to the second direction X2. The second magnet unit 82 is housed in the second magnet unit housing portion 44 of the second outer ring member 32. The second magnet unit 82 is movable in the axial direction X integrally with the output member 4 while being housed in the second magnet unit housing portion 44.

FIG. 8A is an explanatory diagram showing the arrangement of magnetic poles in the first magnet unit 81. FIG. 8A shows a case where the first magnet unit 81 is viewed from the second direction X2. FIG. 8B is an explanatory diagram showing the arrangement of magnetic poles in the second magnet unit 82. FIG. 8B shows a case where the second magnet unit 82 is viewed from the first direction X1. The first magnet 86 and the second magnet 89 are polarized and magnetized in the axial direction X. In the first magnet unit 81, the four first magnets 86 are arranged at equal angular intervals around the axis L, and the magnetic poles on the side facing the second magnet 89 (second direction X2) are different magnetic poles (N The poles and the S poles are arranged alternately in the circumferential direction. Meanwhile, the second
In the magnet unit 82, the two second magnets 89 are arranged at equal angular intervals around the axis L, and the magnetic poles on the side facing the first magnet 86 (first direction X1) are the same magnetic pole. For example, in the second magnet unit 82, the magnetic poles facing the first magnet 86 are both N poles or both are S poles.

When a difference in rotational speed occurs between the outer ring member 3 and the input shaft 2 and the output member 4 and the input shaft 2 rotate relative to each other, the first magnet unit 81 (four first magnets) of the linear reciprocating motion imparting mechanism 8 is generated. 86) and the second magnet unit 82 (two second magnets 89) relatively rotate around the axis L. As a result, a state in which the same magnetic poles face each other and a state in which different magnetic poles face each other are alternately generated. Therefore, the first state in which the attractive force in the axial direction X acts between the first magnet unit 81 and the second magnet unit 82 is set. , A second state in which a repulsive force in the axial direction X acts is alternately generated between the first magnet unit 81 and the second magnet unit 82. Therefore, the output member 4 connected to the second magnet unit 82 linearly reciprocates in the axial direction X by the attractive force and repulsive force generated between the first magnet unit 81 and the second magnet unit 82.

Here, as shown in FIGS. 2 and 3, the outer ring member 3 includes therein a first movement restricting portion 9 that restricts movement of the output member 4 and the second magnet unit 82 in the first direction X1. As shown in FIG. 7, the first movement restricting portion 9 is attached to the center of the second lever 91 and the second lever 91 which extends in the direction orthogonal to the first lever 87 and orthogonal to the input shaft 2. And a columnar movement restricting member 92. As can be seen from FIGS. 3 and 4, the second lever 91 is housed inside the shaft hole 41 and the pair of groove portions 45 provided in the bottom surface of the recess 40 of the second outer ring member 32. In addition, as shown in FIG. 3, both ends of the second lever 91 are fixed to the bottom surface of the groove portion 45. As a result, the first movement restricting portion 9 is integrated with the outer ring member 3.

The movement restricting member 92 projects from the center of the second lever 91 in the second direction X2. The movement restricting member 92 faces the second headed screw 93 that fixes the first lever 87 of the second magnet unit 82 to the end portion of the output member 4 in the first direction X1 from the first direction X1.

Further, the outer ring member 3 includes therein a second movement restricting portion 10 that restricts the movement of the output member 4 and the second magnet unit 82 in the second direction X2. As shown in FIGS. 2 and 4, the second movement restricting portion 10 is an end surface of the stopper member 43 fixed to the bottom surface of each of the pair of circular recesses 42 of the second outer ring member 32 in the first direction X1. The second movement restricting portion 10 faces the two first headed screws 90 that fix the washer 88 and the second magnet 89 to both ends of the first lever 87 in the second magnet unit 82, respectively.

The output member biasing member 83 is a coil spring arranged on the outer peripheral side of the output member 4, as shown in FIG. The output member biasing member 83 is disposed between the end of the linear bush 7 in the first direction X1 and the first lever 87. The end of the output member biasing member 83 in the first direction X1 is fixed to the first lever 87, and the end of the output member urging member 83 in the second direction X2 is fixed to the linear bush 7.

The output member biasing member 83 supports the output member 4 at a position where the second magnet unit 82 contacts the first movement restricting portion 9. The output member biasing member 83 biases the output member 4 in the first direction X1 when the output member 4 moves in the second direction X2 due to the repulsive force between the first magnet unit 81 and the second magnet unit 82. Exert a biasing force. In this example, the output member biasing member 83 biases the output member 4 and the second magnet unit 82 toward the first movement restricting portion 9. Therefore, in the second state in which the repulsive force acts between the first magnet unit 81 and the second magnet unit 82, the linear reciprocating motion imparting mechanism 8 resists the output member biasing member 83 and the second magnet. The unit 82 and the output member 4 are moved in the second direction.

Here, when the output member 4 is moved in the first direction X1 (upward) by the linear reciprocating motion imparting mechanism 8 when the rotation center line of the head 100 of the machine tool is oriented in the vertical direction, the output member 4 In comparison with the case of moving in the second direction X2, a force corresponding to the total weight of the own weight of the second magnet unit 82 and the own weight of the output member 4 is required. Further, when the tool 15 is held by the output member 4, a force corresponding to the weight of the tool 15 is further required. Therefore, in order to reciprocate the output member 4 in the vertical direction, the attractive force acting between the first magnet unit 81 and the second magnet unit 82 is set to the self-weight of the second magnet unit 82, the self-weight of the output member 4, It is necessary to take a large value in consideration of the total weight of the tool 15 and its own weight.

On the other hand, in this example, when the second magnet unit 82 and the output member 4 move in the second direction X2 by the repulsive force acting between the first magnet unit 81 and the second magnet unit 82, the coil spring is formed. Since the output member biasing member 83 is compressed, the biasing force by which the output member biasing member 83 biases the second magnet unit 82 and the output member 4 in the first direction X1 increases. Therefore, when the second magnet unit 82 and the output member 4 are moved in the first direction X1 by the attractive force acting between the first magnet unit 81 and the second magnet unit 82, the output member biasing member 83 The biasing force assists the movement of the output member 4 in the first direction X1. Therefore, when the attractive force acting between the first magnet unit 81 and the second magnet unit 82 is considered in consideration of the total weight of the own weight of the second magnet unit 82, the own weight of the output member 4, and the own weight of the tool 15. Can be set smaller than

(motion)
FIG. 9 is a cross-sectional view of the tool holder 1 in a state where the output member 4 has moved in the second direction X2. As shown in FIG. 1, the tool holder 1 is used with an input shaft 2 connected to a head 100 of a machine tool. A tool 15 is held on the output member 4 of the tool holder 1.

When the input shaft 2 rotates integrally with the head 100 by the driving of the machine tool, the output member 4 performs a rotating operation around the axis L and a linear reciprocating operation in the axial direction X. Therefore, the tool 15 held by the output member 4 comes into contact with the surface of the work while simultaneously performing the rotating operation and the linear reciprocating operation.

Specifically, when the head 100 rotates, the input shaft 2 connected to the head 100 rotates and the outer ring member 3 rotates together with the input shaft 2. Here, when the centrifugal force acting on the flap 5 becomes larger than the urging force of the flap urging member 51, the flap opening operation is performed and the flap 5 is in the open posture. When the flap 5 is in the open position, fluid pressure in the direction opposite to the rotation direction acts on the outer ring member 3 via the flap 5. Therefore, a difference in rotational speed occurs between the outer ring member 3 and the input shaft 2. As a result, the output member 4 that rotates integrally with the outer ring member 3 and the input shaft 2 relatively rotate, so that the linear reciprocating motion imparting mechanism 8 linearly reciprocates in the axial direction X to the output member 4 that is rotating. Give action. That is, the linear reciprocating motion imparting mechanism 8 utilizes the attractive force and the repulsive force that are alternately generated between the first magnet unit 81 and the second magnet unit 82 when the input shaft 2 and the output member 4 rotate relative to each other. Then, a linear reciprocating motion is given to the output member 4.

Here, as shown in FIG. 2 and FIG. 9, in the linear reciprocating motion of the output member 4, the output member 4 causes the first movement restricting portion 9 (movement restricting member 92) of the second outer ring member 32 to move to the second magnet unit. The first headed screw 90 of the second magnet unit 82 abuts on the first position 4A where the second headed screw 93 of 82 abuts and the second movement restricting portion 10 (stopper member 43) of the second outer ring member 32. It moves between the second position 4B and. At the first position 4A, a gap is secured between the first magnet unit 81 and the second magnet unit 82. Therefore, the collision between the first magnet 86 and the second magnet 89 is prevented. Moreover, the second magnet 89 is prevented from being attracted to the first magnet 86.

After that, when the processing of the work is completed, the machine tool stops the rotational drive of the head 100. Here, when the rotation speed of the input shaft 2 decreases due to the decrease in the rotation speed of the head 100, the rotation speed of the outer ring member 3 that rotates together with the input shaft 2 decreases along with the decrease in the rotation speed of the input shaft 2. As a result, the centrifugal force acting on the flap 5 becomes smaller, and the urging force by which the flap urging member 51 urges the flap 5 toward the inner peripheral side becomes larger than the centrifugal force. Therefore, the flap closing operation is performed, and the flap 5 is in the closed posture.

Various tools 15 can be attached to the output member 4. As the tool 15, as shown in FIG. 1, a brush-shaped grindstone provided with a bundle of linear abrasives can be used. In this case, a composite material of aggregate yarn of inorganic long fibers and resin can be used. That is, the linear abrasive can be obtained by impregnating the aggregated yarn of inorganic long fibers with a resin and curing the resin. Here, when a brush-like grindstone is used as the tool 15, the surface of the work can be blasted or plateau processed. That is, even when a brush-shaped grindstone used for polishing the surface of a work is used as the tool, the brush-shaped grindstone is rotated and linearly reciprocated in the axial direction while the brush-shaped grindstone intersects the axis L. The surface texture can be applied to the work by moving the work to the surface of the work.

Further, a rotary bar can be used as the tool 15. Further, as the tool 15, a grindstone, a shank portion held by the tool 15 holding portion, a rod-shaped neck portion extending in the axial direction X to connect the grindstone and the shank portion, and a grindstone with a shaft can be used. .. In this case, the grindstone can be an electrodeposition grindstone. Further, the shape of the magnet may be a cylindrical shape or a spherical shape. A buff tool can be used as the tool 15. Further, as the tool 15, a spherical tool with a shaft including a spherical portion and a shaft portion protruding from the spherical portion can be used. In this case, the shaft portion is held by the tool holding portion 11. Also, the spherical portion can be made of ceramic, cemented carbide, copper, glass, or resin.

By changing the rotational speed of the head 100 of the machine tool, the rotational speed and the linear reciprocating cycle of the tool 15 mounted on the output member 4 of the tool holder 1 can be changed flexibly. Therefore, the tool 15 can be used to apply various surface textures to the surface of the workpiece.

(Action effect)
As described above, the tool holder 1 of this example is arranged coaxially with the input shaft 2, the outer ring member 3 that supports the input shaft 2 rotatably, and rotates together with the input shaft 2. The output member 4 is supported by the outer ring member 3 so as to be movable in the axial direction X of the input shaft 2 and rotates integrally with the outer ring member 3. Further, in the tool holder 1, when the input shaft 2 and the outer ring member 3 rotate together, the brake mechanism 50 that lowers the rotation speed of the outer ring member 3 below the rotation speed of the input shaft 2, and the rotation speed of the outer ring member 3. Is lower than the rotation speed of the input shaft 2 and the input shaft 2 and the output member 4 rotate relative to each other, a linear reciprocating motion in the axial direction X is given to the output member 4 rotating together with the outer ring member 3. The linear reciprocating motion imparting mechanism 8 is provided. Therefore, according to the tool holder 1, the tool 15 held by the output member 4 can simultaneously perform two operations, that is, a rotating operation and a linear reciprocating operation.

Further, in the tool holder 1 of this example, it is not necessary to fix the outer ring member 3 to a machine tool or the like in order to generate a linear reciprocating motion in the axial direction X. Therefore, it is not necessary to modify the machine tool to fix the outer ring member 3. Therefore, the tool holder 1 can be easily attached to the machine tool.

Further, in this example, the pressure receiving portion of the brake mechanism 50 is the flap 5 attached to the outer ring member 3. As a result, when the outer ring member 3 is rotated, the fluid pressure is automatically applied to make the rotation speed of the outer ring member 3 slower than the rotation speed of the input shaft 2. For example, when the tool holder 1 is used in air, the rotation speed of the outer ring member 3 can be made lower than the rotation speed of the input shaft 2 by the air pressure acting on the flap 5. Further, when the tool holder 1 is used in a liquid (for example, in water), the rotational speed of the outer ring member 3 can be slower than the rotational speed of the input shaft 2 due to the water pressure acting on the flap 5.

Further, in this example, when the outer ring member 3 is switched from the stopped state to the rotating state, the flap opening operation is performed in which the flap 5 is changed to the open posture in which the fluid pressure is received, and the outer ring member 3 is switched from the rotating state to the stopped state. As a result, the flap closing operation is performed in which the flap 5 changes to the closed posture in which the flap 5 receives no fluid pressure. That is, in this example, the opening/closing operation of the flap 5 is automatically performed depending on whether or not the outer ring member 3 is rotated. Therefore, the flap 5 can be reliably opened when the tool holder 1 rotates. Further, when the tool holder 1 stops rotating, the flap 5 is not left open. Therefore, damage to the flap 5 and surrounding objects can be suppressed.

Further, the flap 5 swings to the outer peripheral side around the shaft portion 52 connected to the outer ring member 3 by the centrifugal force that acts when the outer ring member 3 rotates, and changes to the open posture. Therefore, the flap 5 can be opened without providing a drive source dedicated to the flap 5.

Further, the brake mechanism 50 includes a flap urging member 51 that urges the flap 5 toward the inner peripheral side, and the flap urging force of the flap urging member 51 performs the flap closing operation. Therefore, the flap 5 can be closed without providing a drive source dedicated to the flap 5.

Furthermore, the linear reciprocating motion imparting mechanism 8 includes an output member biasing member 83 that exerts a biasing force that biases the output member 4 in the first direction X1 when the output member 4 moves in the second direction X2. .. Therefore, when the output member 4 moves in the direction approaching the input shaft 2 due to the attractive force between the first magnet unit 81 and the second magnet unit 82, the output member urging member 83 urges the output member 4 to move. You can assist the movement of 4.

Further, the linear reciprocating motion imparting mechanism 8 generates a reciprocating motion in the axial direction X without bringing the first magnet unit 81 and the second magnet unit 82 into contact with each other. Therefore, in the linear reciprocating motion imparting mechanism 8, when the output member 4 is moved in the second direction X2 from the first position 4A by the repulsive force generated between the first magnet unit 81 and the second magnet unit 82. When a load toward the first direction X1 is applied to the tool 15 held by the output member 4, the output member 4 moves in the first direction X1. Therefore, for example, when the output member 4 moves in the second direction X2 from the first position 4A, when the tool 15 passes through a convex portion or the like on the surface of the work W, the head of the machine tool is controlled by the control program. The tool 15 can be moved in the axial direction X by following the shape of the convex portion without moving the 100 in the axial direction X.

The configurations of the first magnet unit 81 and the second magnet unit 82 are not limited to the configurations of the embodiment, and the axes when the first magnet unit 81 and the second magnet unit 82 rotate relative to each other. It is sufficient that the attractive force in the direction X and the repulsive force in the axial direction X are alternately generated. That is, the number of the first magnets 86 and the second magnets 89 is not limited to 4 and 2, but the number of the first magnets 86 is an even number, and the second magnets 89 are arranged at intervals in the circumferential direction. However, it is only necessary to be twice the arrangement interval of the first magnets 86 in the circumferential direction. Alternatively, the number of magnets of the second magnet 89 and the magnetic pole arrangement may be the same as those of the first magnet 86. Further, as the first magnet 86 and the second magnet 89, annular magnets polarized and magnetized in the circumferential direction may be used.

Further, the output member biasing member 83 of the linear reciprocating motion imparting mechanism 8 may be omitted.

[Example 2]
FIG. 10 is a sectional view of the tool holder according to the second embodiment. FIG. 11 is a perspective view of a linear reciprocating motion imparting mechanism of the tool holder according to the second embodiment. FIG. 12 is a perspective view of the second outer ring member of the second embodiment as viewed from the first direction X1. The appearance of the tool holder 1A of this example is the same as that of the first embodiment shown in FIG. 10 is a cross-sectional view taken along the line AA in FIG. In the description of the second embodiment, the same components as those in the first embodiment are designated by the same reference numerals, and the description thereof will be omitted. Further, only the configuration different from that of the first embodiment will be described with reference to the drawings.

The tool holder 1A of this example includes an input shaft 2, an outer ring member 3 rotatably supported by the input shaft 2, an output member 4 that detachably holds a tool 15, and a flap 5 attached to the outer ring member 3. And The outer ring member 3 includes a cylindrical portion 34 that surrounds the input shaft 2 from the outer peripheral side and rotates together with the input shaft 2. The output member 4 is arranged coaxially with the input shaft 2. The output member 4 is supported by the outer ring member 3 so as to be movable in the axial direction X along the axis L of the input shaft 2. The output member 4 is non-rotatable with respect to the outer ring member 3 and rotates integrally with the outer ring member 3. The output member 4 includes a tool holding portion 11 to which a tool 15 is detachably attached. The flap 5 opens and closes radially on the outer peripheral side of the outer ring member 3.

Further, the tool holder 1A includes a brake mechanism 50 that lowers the rotation speed of the outer ring member 3 below the rotation speed of the input shaft 2 when the input shaft 2 and the outer ring member 3 rotate together. Further, when the rotation speed of the outer ring member 3 becomes lower than the rotation speed of the input shaft 2 and the input shaft 2 and the output member 4 rotate relative to each other, the tool holder 1A performs a rotating operation together with the outer ring member 3. The output member 4 is provided with a linear reciprocating motion imparting mechanism 8A that imparts a linear reciprocating motion in the axial direction X.

As shown in FIG. 10, the linear reciprocating motion imparting mechanism 8A includes an annular cam surface 181 extending in the circumferential direction, a cam follower 180 abutting the cam surface 181 in the axial direction X, a cam surface 181 and a cam follower 180. A biasing member 183 that presses one of the two in the axial direction X is provided. In this example, the cam follower 180 is provided on the input shaft 2 and the cam surface 181 is provided on the output member 4. The biasing member 183 biases the output member 4 in the first direction X1.

That is, the input shaft 2 includes the first shaft portion 21, the second shaft portion 22, and the cam follower 180 fixed to the end portion of the second shaft portion 22. As shown in FIG. 11, the cam follower 180 includes a first disc portion 184 and a plurality of shaft-equipped rollers 182 attached to the annular outer peripheral surface of the first disc portion 184. The shape of the first disk portion 184 when viewed from the axial direction X is circular. The roller 182 with each shaft includes a shaft portion 185 screwed into a screw hole that opens in the annular outer peripheral surface of the first disc portion 184, and a roller 186 rotatably attached to the shaft portion 185. The shaft portion 185 extends in the radial direction, and the roller 186 is rotatable about the axis L that faces the radial direction. In this example, as shown in FIGS. 10 and 11, four rollers 182 with shafts are arranged at equal intervals in the circumferential direction.

The output member 4 includes a second disc portion 187 at an end portion in the first direction X1 and a cam portion 188 protruding from the outer peripheral edge of the second disc portion 187 in the first direction X1. The shape of the second disk portion 187 when viewed from the axial direction X is circular. The cam surface 181 is an end surface of the cam portion 188 in the second direction X2. The cam portion 188 includes a plurality of protruding portions 189 having the same shape and protruding in the second direction X2. Therefore, the cam surface 181 is provided with unevenness in the axial direction X arranged in the circumferential direction. The circumferential arrangement of the protruding portion 189 corresponds to the circumferential arrangement of the shaft-equipped roller 182 of the cam follower 180. In this example, four shaft-equipped rollers 182 are arranged at equal intervals in the circumferential direction, and the cam portion 188 includes two protruding portions 189 arranged at equal intervals in the circumferential direction.

The biasing member 183 is a coil spring arranged on the outer peripheral side of the output member 4. The biasing member 183 is disposed between the end of the linear bush 7 in the first direction X1 and the second disc portion 187. The biasing member 183 is arranged in a state compressed more than the free length. Therefore, the biasing member 183 biases the cam surface 181 in the second direction X2 via the second disc portion 187. As a result, the cam surface 181 is pressed against the cam follower 180 from the second direction X2.

Here, as shown in FIG. 10, the second outer ring member 32 of the outer ring member 3 is coaxial with the body portion 37, which is in contact with the disc portion 35 of the first outer ring member 31 from the second direction X2, and the body portion 37. A small-diameter body portion 38 having an outer diameter smaller than that of the body portion 37, and a taper portion 39 connecting the body portion 37 and the small-diameter body portion 38 are provided. As shown in FIG. 12, the body portion 37 includes a circular recess 40 on the end face in the first direction X1. The recess 40 is provided coaxially with the body portion 37. Therefore, the end portion of the second outer ring member 32 in the first direction X1 is tubular. At the center of the bottom surface of the recess 40, a shaft hole 41 that penetrates the body portion 37, the tapered portion 39, and the small diameter body portion 38 in the axial direction X is provided. The linear bush 7 is inserted into the shaft hole 41. The linear bush 7 is fixed to an end portion of the inner peripheral surface of the shaft hole 41 in the second direction X2. The linear bush 7 is located inside the small-diameter body portion 38 in the radial direction. As shown in FIG. 10, the recess 40 accommodates the cam follower 180 of the input shaft 2, the second disc portion 187 and the cam portion 188 of the output member 4. The second disc portion 187 and the cam portion 188 are movable in the axial direction X in the recess 40.

The output member 4 extends through the shaft hole 41 of the second outer ring member 32 and the linear bush 7. The linear bush 7 allows the output member 4 to move in the axial direction X and restricts rotation around the axis L. Therefore, the output member 4 is supported by the second outer ring member 32 in a state of being movable in the axial direction X and not rotatable about the axis L. Therefore, when the input shaft 2 rotates and the outer ring member 3 rotates in the same rotation direction as the input shaft 2, the output member 4 rotates together with the linear bush 7 together with the outer ring member 3.
(Operation of linear reciprocating motion imparting mechanism)
When the brake mechanism 50 functions during rotation of the tool holder 1A, a difference in rotational speed occurs between the outer ring member 3 and the input shaft 2 and the output member 4 and the input shaft 2 rotate relative to each other. As a result, the cam follower 180 provided on the input shaft 2 and the cam surface 181 provided on the output member 4 rotate relative to each other. Therefore, the cam follower 180 moves in the circumferential direction along the cam surface 181. Here, the output member 4 is supported by the outer ring member 3 in a state of being movable in the axial direction X, and the cam surface 181 is biased by the biasing member 183 toward the cam follower 180. Therefore, the output member 4 rotates integrally with the outer ring member 3 and reciprocates in the axial direction X according to the irregularities of the cam surface 181. The stroke of the linear reciprocating motion of the output member 4 matches the depth of the unevenness of the cam surface 181 in the axial direction X. Here, the state shown in FIG. 10 is a state in which the output member 4 is farthest from the input shaft 2 in the second direction X2.

(Action effect)
In the present example, the linear reciprocating motion imparting mechanism 8A includes an annular cam surface 181 extending in the circumferential direction, a cam follower 180 abutting on the cam surface 181 in the axial direction X, and one of the cam surface 181 and the cam follower 180. A biasing member 183 that presses the other in the axial direction X is provided. Further, the cam follower 180 is provided on the input shaft 2, and the cam surface 181 is provided on the output member 4. Therefore, by the relative rotation of the input shaft 2 and the output member 4, the linear reciprocating motion imparting mechanism 8A can impart a linear reciprocating motion in the axial direction X to the rotating output member 4. Therefore, the tool holder 1A can cause the tool 15 held by the output member 4 to simultaneously perform two operations, a rotary operation and a linear reciprocating operation.

Further, in the tool holder 1A of this example, it is not necessary to fix the outer ring member 3 to a machine tool or the like in order to generate a linear reciprocating motion in the axial direction X. Therefore, it is not necessary to modify the machine tool to fix the outer ring member 3. Therefore, the tool holder 1A can be easily attached to the machine tool.

Further, in this example, the pressure receiving portion of the brake mechanism 50 is the flap 5 attached to the outer ring member 3. Thereby, the brake mechanism 50 can automatically apply the fluid pressure when the outer ring member 3 is rotated, and make the rotation speed of the outer ring member 3 slower than the rotation speed of the input shaft 2. Further, the tool holder 1A does not require a drive source for opening and closing the flap 5.

The cam follower 180 may be provided on the output member 4 and the cam surface 181 may be provided on the input shaft 2.

[Example 3]
FIG. 13 is a sectional view of the tool holder according to the third embodiment. The appearance of the tool holder 1B of this example is the same as that of the first embodiment shown in FIG. FIG. 13 is a cross-sectional view of the tool holder 1B taken along the line AA in FIG. In the description of the third embodiment, the same configurations as those of the first and second embodiments are designated by the same reference numerals and the description thereof will be omitted. Further, in the description of the third embodiment, only the configuration different from the first and second embodiments will be described with reference to the drawings.

The tool holder 1B of this example includes an input shaft 2, an outer ring member 3 rotatably supported by the input shaft 2, an output member 4 that detachably holds a tool 15, and a flap 5 attached to the outer ring member 3. And The outer ring member 3 includes a cylindrical portion 34 that surrounds the input shaft 2 from the outer peripheral side and rotates together with the input shaft 2. The output member 4 is arranged coaxially with the input shaft 2. The output member 4 is supported by the outer ring member 3 so as to be movable in the axial direction X along the axis L of the input shaft 2. The output member 4 is non-rotatable with respect to the outer ring member 3 and rotates integrally with the outer ring member 3. The output member 4 includes a tool holding portion 11 to which a tool 15 is detachably attached. The flap 5 opens and closes radially on the outer peripheral side of the outer ring member 3.

Further, the tool holder 1B includes a brake mechanism 50 that lowers the rotation speed of the outer ring member 3 below the rotation speed of the input shaft 2 when the input shaft 2 and the outer ring member 3 rotate together. Furthermore, when the rotation speed of the outer ring member 3 becomes lower than the rotation speed of the input shaft 2 and the input shaft 2 and the output member 4 rotate relative to each other, the tool holder 1B performs a rotating operation together with the outer ring member 3. The output member 4 is provided with a linear reciprocating motion imparting mechanism 8B that imparts a linear reciprocating motion in the axial direction X.

FIG. 14 is a perspective view of the linear reciprocating motion imparting mechanism 8B of the third embodiment. As shown in FIGS. 13 and 14, the linear reciprocating motion imparting mechanism 8B according to the third embodiment includes an input gear 281 that rotates integrally with the input shaft 2 and an output gear 282 that rotates around an axis orthogonal to the input shaft 2. And a link member 290 having one end connected to the output gear 282 and the other end connected to the output member 4.

The input gear 281 is provided integrally with the input shaft 2 at the end of the input shaft 2 in the second direction X2. The input gear 281 is a bevel gear that is coaxial with the input shaft 2. The gear unit 280 includes two output gears 282 that mesh with the input gear 281, a support shaft 283 that rotatably supports the two output gears 282, and a connecting member 284 that connects the support shaft 283 and the outer ring member 3. Prepare

As shown in FIG. 14, the support shaft 283 extends in a direction orthogonal to the axial direction X in the second direction X2 of the input gear 281. The two output gears 282 are arranged at both ends of the support shaft 283 and are arranged symmetrically in the radial direction. The coupling member 284 is orthogonal to the support shaft 283 and extends in a direction orthogonal to the axial direction X, and a circle of the outer ring member 3 extending from both ends of the first arm portion 285 in the first direction X1. It has two second arm portions 286 connected to the plate portion 35. The support shaft 283 is held at the central portion of the first arm portion 285 in the longitudinal direction.

On the other hand, the output member 4 includes a disc portion 287 provided at an end portion of the output member 4 in the first direction X1 and a pair of protrusions 288 that protrude from the disc portion 287 in the first direction X1. The pair of protrusions 288 are arranged on both sides with the axis L interposed therebetween. Each of the protrusions 288 is formed with a pin 289 that protrudes outward in the radial direction. Each link member 290 has one end connected to a pin 291 protruding outward from the output gear 282 in the radial direction, and the other end connected to a pin 289 formed on the protruding portion 288. The pin 291 formed on the output gear 282 is formed at a position closer to the outer peripheral edge than the rotation center of the output gear 282.

Here, the second outer ring member 32 of the outer ring member 3 has the same configuration as that of the second embodiment, as shown in FIG. That is, the body portion 37 that abuts the disc portion 35 of the first outer ring member 31 from the second direction X2, the small-diameter body portion 38 that is coaxial with the body portion 37 and has an outer diameter smaller than that of the body portion 37, and the body portion 37. And a taper portion 39 connecting the small-diameter body portion 38. The body portion 37 includes a circular recess 40 on the end face in the first direction X1. The recess 40 is provided coaxially with the body portion 37. Therefore, the end portion of the second outer ring member 32 in the first direction X1 is tubular. At the center of the bottom surface of the recess 40, a shaft hole 41 that penetrates the body portion 37, the tapered portion 39, and the small diameter body portion 38 in the axial direction X is provided. The linear bush 7 is inserted into the shaft hole 41. The linear bush 7 is fixed to an end portion of the inner peripheral surface of the shaft hole 41 in the second direction X2. The linear bush 7 is located inside the small-diameter body portion 38 in the radial direction.

As shown in FIG. 13, the linear reciprocating motion imparting mechanism 8B is housed in the recess 40. That is, the recess 40 accommodates the gear unit 280 having the input gear 281 and the output gear 282, and the link member 290 having one end connected to the output gear 282 and the other end connected to the output member 4. Further, the disc portion 287 of the output member 4 and the pair of protruding portions 288 are housed in the recess 40.

(Operation of linear reciprocating motion imparting mechanism)
When the input shaft 2 of the tool holder 1B is connected to the head 100 of the machine tool and the input shaft 2 rotates, the linear reciprocating motion imparting mechanism 8B causes the input gear 281 of the gear unit 280 to rotate integrally with the input shaft 2. On the other hand, when the outer ring member 3 rotates with the input shaft 2, the output gear 282 meshing with the input gear 281 has a connecting member 284 fixed to the disc portion 35 of the outer ring member 3 and a support shaft 283 supported by the connecting member 284. At the same time, it moves in the circumferential direction around the axis L. Here, when the input shaft 2 and the outer ring member 3 and the output member 4 rotate relative to each other due to the function of the brake mechanism 50, the two output gears 282 respectively rotate about the support shaft 283. As a result, the pin 291 of the output gear 282 rotates about the support shaft 283, so that the two link members 290 connected to the pin 291 reciprocate in the axial direction X. Therefore, the output member 4 in which the disk portion 287 is connected to the end portion of the link member 290 in the second direction X2 is guided by the linear bush 7 and linearly reciprocates in the axial direction X. The stroke of the linear reciprocating motion of the output member 4 is twice the distance from the rotation center of the output gear 282 to the pin 291. The state shown in FIG. 13 is a state in which the output member 4 is closest to the input shaft 2.

(Action effect)
In this example, the linear reciprocating motion imparting mechanism 8B includes an input gear 281 that rotates integrally with the input shaft 2, and a gear unit 280 that includes an output gear 282 that rotates around an intersecting axis L that intersects the input shaft 2. The output gear 282 includes a link member 290 having one end connected to the output gear 282 and the other end connected to the output member 4. Therefore, by the relative rotation of the outer ring member 3 and the output member 4 and the input shaft 2, the linear reciprocating motion imparting mechanism 8B can impart the linear reciprocating motion in the axial direction X to the rotating output member 4. Therefore, the tool holder 1B can cause the tool 15 held by the output member 4 to simultaneously perform two operations, a rotary operation and a linear reciprocating operation.

Further, in the tool holder 1B of this example, it is not necessary to fix the outer ring member 3 to a machine tool or the like in order to generate a linear reciprocating motion in the axial direction X. Therefore, it is not necessary to modify the machine tool to fix the outer ring member 3. Therefore, the tool holder 1B can be easily attached to the machine tool.

Further, in this example, the pressure receiving portion of the brake mechanism 50 is the flap 5 attached to the outer ring member 3. Thereby, the brake mechanism 50 can automatically apply the fluid pressure when the outer ring member 3 is rotated, and make the rotation speed of the outer ring member 3 slower than the rotation speed of the input shaft 2. Further, the tool holder 1A does not require a drive source for opening and closing the flap 5.

(Modification)
In each of the above embodiments, the brake mechanism 50 has a structure in which the flap 5, which is a pressure receiving portion, opens and closes by a centrifugal force and a spring force. However, the flap 5 has a structure in which the flap 5 is fixed in an open posture 5B that receives fluid pressure. May be.

(Other embodiments)
Here, the output member 4 can hold a work instead of the tool 15. That is, the tool holders 1, 1A, 1B can be work holders that hold the work in the tool holding unit 11 (work holding unit). For example, the output member 4 can hold a bone screw, a bone drill, or the like as a work. In this case, by interposing a work holder (tool holder 1) between the head 100 of the machine tool and the work, and immersing the work in the barrel polishing material while rotating the head 100, the work is rotated and linearly reciprocated. Contact the barrel abrasive while performing the operations simultaneously. Therefore, the barrel polishing can be performed at a higher speed as compared with the case where the barrel polishing is performed only by the rotating operation.

1, 1A, 1B... Tool holder, 2... Input shaft, 3... Outer ring member, 4... Output member, 4A... First position, 4B... Second position, 5... Flap, 5A... Closed posture, 5B... Opened posture, 6... Bearing part, 7... Linear bush, 8,8A, 8B... Linear reciprocating motion imparting mechanism, 9... First movement restricting part, 10... Second movement restricting part, 11... Tool holding part, 15... Tool, 21... 1st shaft part, 22... 2nd shaft part, 31... 1st outer ring member, 32... 2nd outer ring member, 33... End plate member, 34... Cylindrical part, 35... Disc part, 36... Opening part, 37... Body part, 38... Small-diameter body part, 39... Tapered part, 40... Recessed part, 41... Shaft hole, 42... Circular recessed part, 43... Stopper member, 44... Second magnet unit housing part, 45... Groove part, 50... Brake mechanism , 51... flap biasing member, 52... shaft portion, 53... shaft hole, 54... support shaft, 55... flap, 81... first magnet unit, 82... second magnet unit, 83... output member biasing member, 84... Disc, 85... Washer, 86... First magnet, 87... First lever, 88... Washer, 89... Second magnet, 90... First headed screw, 91... Second lever, 92... Movement restricting member, 93... 2nd head screw, 100... Head, 180... Cam follower, 181... Cam surface, 182... Shaft-equipped roller, 183... Energizing member, 184... 1st disc part, 185... Shaft part, 186... Roller, 187... Second disc portion, 188... Cam portion, 189... Projection portion, 280... Gear unit, 281... Input gear, 282... Output gear, 283... Support shaft, 284... Connecting member, 285... First arm portion, 286... 2nd arm part, 287... Disc part, 288... Projection part, 289... Pin, 290... Link member, 291... Pin, L... Axis line, X... Axial direction, X1... 1st direction, X2... 2nd direction

Claims (8)

Input axis,
An outer ring member that is rotatably supported by the input shaft and that rotates together with the input shaft;
An output member that is arranged coaxially with the input shaft, is supported by the outer ring member in a state of being movable in the axial direction of the input shaft, and rotates integrally with the outer ring member;
When the input shaft and the outer ring member rotate together, a brake mechanism that reduces the rotation speed of the outer ring member below the rotation speed of the input shaft,
When the rotation speed of the outer ring member is lower than the rotation speed of the input shaft and the input shaft and the output member rotate relative to each other, the output member that is rotating integrally with the outer ring member is in the axial direction. A linear reciprocating motion imparting mechanism that imparts a linear reciprocating motion of
The brake mechanism includes a pressure receiving portion that receives a fluid pressure acting in a direction opposite to a rotation direction,
The pressure receiving portion is a flap attached to the outer ring member,
The said output member is equipped with the tool holding part for hold|maintaining a tool, The tool holder characterized by the above-mentioned. By switching the outer ring member from a stopped state to a rotating state, a flap opening operation is performed in which the flap is changed to an open position in which fluid pressure is received,
The tool holder according to claim 1, wherein when the outer ring member is switched from a rotating state to a stopped state, a flap closing operation is performed in which the flap is changed to a closed posture in which the fluid pressure is not received. The flap is oscillated toward the outer peripheral side about a connecting portion connected to the outer ring member by the centrifugal force acting when the outer ring member rotates, and changes to the open posture. The tool holder described in 2. The brake mechanism includes a flap biasing member that biases the flap toward the inner peripheral side,
The tool holder according to claim 2 or 3, wherein the flap closing operation is performed by the biasing force of the flap biasing member. The linear reciprocating motion imparting mechanism includes a first magnet unit and a second magnet unit facing the first magnet unit in the axial direction,
The first magnet unit is fixed to the input shaft,
The second magnet unit is fixed to the output member,
When the first magnet unit and the second magnet unit rotate relative to each other, the first state in which the attractive force in the axial direction acts between the first magnet unit and the second magnet unit, and the first magnet unit. The tool holder according to any one of claims 1 to 4, wherein a second state in which the repulsive force in the axial direction acts is alternately generated between the second magnet unit and the second magnet unit. The linear reciprocating motion imparting mechanism causes the output member to move toward the input shaft side when the output member moves in a direction away from the input shaft due to a repulsive force between the first magnet unit and the second magnet unit. The tool holder according to claim 5, further comprising an output member biasing member that exerts a biasing force to bias the output member. The linear reciprocating motion imparting mechanism includes a cam surface on which the irregularities in the axial direction are arranged in the circumferential direction, a cam follower that abuts the cam surface in the axial direction, and one of the cam surface and the cam follower is pressed against the other. And a biasing member,
One of the cam surface and the cam follower is provided on the input shaft,
The other of the cam surface and the cam follower is provided on the output member,
The tool holder according to any one of claims 1 to 4, wherein the biasing member biases the output member toward the input shaft. The linear reciprocating motion imparting mechanism includes an input gear that rotates integrally with the input shaft, and a gear unit that includes an output gear that meshes with the input gear and rotates around an intersecting axis intersecting the axis, and the output unit. The tool holder according to any one of claims 1 to 4, further comprising: a link member having one end connected to a portion deviated from a rotation center of the gear and the other end connected to the output member. ..

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