JPS5976737A - Holder for tool tip position adjustable cutting tool - Google Patents

Abstract

PURPOSE:To permit the adjusting of the tool tip position and a highly accurate work by preventing the existence of minute clearances between each members by a constitution wherein the fitting protuberance of a socket is fitted into the fitting hole of a holder member tightly through an eccentric ball sleeve. CONSTITUTION:The circular fitting hole 12 is formed on the end face 10 of the main body 2 of the holder, having an adaptor shaft 4 with a taper, while a cylindrical ball retainer 18 equipped with a flange is fitted into the hole 12. Each one rows of a group of ball holding holes 22 are formed on the wall of the ball retainer 18 at two positions spaced with about 60 deg. while the center O2 of the inner peripheral surface of the retainer 18 is provided eccentrically with respect to the center O1 of the outer peripheral surface thereof so as to enlarge the thickness of the retainer 18 at the part formed with the groups of the ball holding holes. The eccentric ball sleeve 26 is constituted by accommodating the balls 24 in the hold-holes 22. The socket 30 may be fitted tightly by fitting the fitting protuberance 34 of the socket 30 into the eccentric ball sleeve 26 and rotating both parts 2, 30 relatively.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a cutting tool holding device for holding a cutting tool.
In particular, it relates to a holding device that allows the position of the tool cutting edge to be adjusted.

One type of tool holding device is one in which the position of the cutting tool edge can be adjusted in a direction perpendicular to the center line of rotation by rotating an eccentric sleeve. In this kind of holding device, the tool holder is usually fitted into a fitting hole with a circular cross section provided in the holder body via an eccentric sleeve, but in the conventional holding device, 1. Since the eccentric sleeve must be able to slide and rotate within the fitting hole, it is unavoidable that minute clearances occur between the eccentric sleeve, the holder body, and the tool holder. This has the drawback that the tool holding accuracy and the positional accuracy of the cutting edge become distorted, making it difficult to perform high-precision cutting.

Against this background, the present invention was made for the purpose of providing a cutting tool holding device that allows for adjustment of the cutting edge position, does not have minute clearances between functional members, and provides high machining dimensional accuracy. It is something.

To achieve this objective, the holding device according to the invention comprises:
(a) a first member having a j-mounting hole with a circular cross section on the first end surface; and (b) a plurality of balls arranged along the inner periphery of the fitting hole and parallel to the center line of the hole. one or more rows of balls, and a ball retainer that is cylindrical and holds the ball rows so that each ball belonging to the ball rows slightly protrudes from the outer circumferential surface and the inner circumferential surface and can move in the radial direction. With provision, all or all of the above ball rows.

(C) An eccentric ball sleeve in which an inscribed cylinder and an external cylinder that are inscribed and circumscribed in and around all of the ball rows and the above-mentioned pole retainer are eccentric to each other; and (C) an eccentric ball sleeve that fits into the fitting hole through the eccentric ball sleeve. (d) a second member having a circular cross-section fitting protrusion protruding from the second end surface;
urging the second end of the member and the first end surface of the first member into close contact with each other with or without a radially outward flange provided on the eccentric ball sleeve; (e) relative rotation preventing means for preventing relative rotation of the first member and the second member about the center line of the fitting hole; and (f) a first member and a second member whose relative rotation is prevented. a rotating means for rotating the eccentric ball sleeve by a desired angle between the first member and the second member, one of the first member and the second member is attached to a tool attachment part of a machine tool, and a cutting tool is attached to the other. The present invention is characterized in that the relative position of the cutting edge of the cutting tool with respect to the tool mounting portion of the machine tool can be adjusted in a direction perpendicular to the center line of the fitting hole by rotating the eccentric ball sleeve.

In such a tool holding device, the fitting protrusion of the second member is tightly fitted into the fitting hole of the first member through the eccentric ball sleeve, so that the ball row of the eccentric ball sleeve is fitted in the assembled state. Each of the balls belonging to the ball is preloaded and becomes elastically compressed and deformed. In other words, the ball is used as a type of spring member, and its compression reaction force (elastic force) causes the first member, second member, and eccentric ball sleeve to exert force on each other, so that the three members There is no occurrence of minute clearance, or in other words, no backlash. Therefore, tool holding accuracy during cutting is extremely high, and machining dimensions can be maintained with high accuracy. Moreover, when adjusting the position of the cutting edge, each compressed ball moves along the inner periphery of the fitting hole of the first member, allowing rotation of the eccentric ball sleeve. The position adjustment function is not hindered.

Embodiments of the present invention will be described in detail below with reference to the drawings.

Figures 1 to 3 are diagrams showing an embodiment in which the present invention is applied to a tool holding device that holds rotary cutting tools such as drills, reamers, 7-milling tools, and boring tools. Reference numeral 2 indicates the boulder body. The holder main body 2 corresponds to a first member and includes a tapered mounting shaft portion 4, which is fitted into a fitting hole of a spindle, which is a tool mounting portion of a rotary cutting machine (not shown). At the same time, the fitting protrusion on the spindle side fits into the fitting groove 8 on the holder main body 2 side shown in FIG. Relative rotation is prevented.

An end surface 10 of the holder main body 2 on the opposite side to the mounting shaft portion 4 corresponds to a first end, and a fitting hole 1 with a circular cross section is formed in the end surface 10.
2 is formed. The fitting hole 12 is provided concentrically with the mounting shaft portion 4, and a counterbore hole 14 is formed at the bottom thereof, and a through hole 16 is further provided following the counterbore hole 14 and continuing to the screw hole 16. ing. A cylindrical ball retainer 18 with seven lances is fitted into the fitting hole 12 of the holder main body 2 .

As shown in FIGS. 4 and 5, the ball retainer 18 has a center line O1 of the outer circumferential cylindrical surface (in FIG. 4, it is shown as a projected point).

) and the center line 02 of the inner cylindrical surface are eccentric by a dimension α, and the wall of the ball retainer 18 has
Above center line 01. O1! symmetrical position with respect to the plane containing,
In other words, based on the point where the inner circumferential surface and the outer circumferential surface are closest, each angle is equal in both directions (approximately 60 degrees in this implementation).
A row of groups of ball holding holes 22 each having a circular cross section are provided at spaced apart locations. As is clear from FIG. 5, the ball holding holes 22 in each row are located at the center line 0. ．． 0. ,
A plurality of pieces (six pieces in this embodiment) are provided at equal intervals in a direction parallel to the ball cage 18 and penetrate in the radial direction from the inner circumferential surface to the outer circumferential surface of the ball retainer 18. It has a slightly larger hole diameter. As shown in FIG. 3, one steel ball 24 is accommodated in each of the ball holding holes 22 in each row, so that the steel balls 24 are held along the inner peripheral surface of the fitting hole 12 of the holder main body 2. Six balls 24 are arranged parallel to the center line of the hole 12, and these balls 24 form two rows of balls, and each ball row and a ball retainer 18 that holds the ball rows are arranged. The eccentric ball sleeve 26 is configured by. An eccentric ball sleeve means that the entire sleeve with the balls has an eccentric shape.

The balls 24 are all of the same size and have a diameter slightly larger than the length of the ball holding hole 22, while the ball retainer 18 is arranged such that each ball 24 belonging to the two ball rows is separated from the outer circumferential surface and the inner circumferential surface. slightly (e.g. 0.05
It holds each ball row so that it can protrude (approximately 0.008 mm to 0.008 mm), and has an outer diameter dimension that allows it to fit into the fitting hole I2 of the holder main body 2 with high precision. As is clear from FIG. 6, which schematically shows the eccentric ball sleeve 26, there is an inscribed cylinder cIs inscribed in all two rows of balls made up of a plurality of balls 24 and the ball retainer 18, and an inscribed cylinder cIs inscribed in the ball retainer 18; Assuming a circumscribed cylinder c2, their centers ti O+' and 02' force 5 are eccentric from each other by an eccentric amount a', and the characteristic parts are exaggerated in the figure for ease of understanding. However, in the case of this embodiment, the eccentricity Ma' is closer to the center line of the inner and outer peripheral surfaces of the pole retainer I8 itself. ．． This means that the f seedling is smaller than the eccentricity α of 02.

As shown in FIG. 1 etc., a circular 7 flange 28 is formed radially outward at one end of the ball retainer I8, in other words, at one end of the eccentric ball sleeve 26, and this flange 28 is fitted. The amount of fitting of the eccentric ball sleeve 26 is determined by surface contact with the opening end surface of the matching hole 12, that is, the end surface 1o of the holder main body 2.

An eccentric ball sleeve 2 is inserted into the fitting hole 12 of the holder body 2.
A socket 30 is fitted through the socket 6. socket 3
0 serves as a second member for the holder main body 2 which is the first member, and is provided at the center of the end surface 32 (this corresponds to the second end surface) of the circular base at a right angle to the end surface 32. It has a protruding fitting protrusion 34 with a circular cross section, and if you look at it from a different perspective, it has seven radially outward flange 36.
It has a cylindrical shape with one end. The outer diameter of the fitting protrusion 34 of the socket 30 is slightly larger than the diameter of the inner cylinder CI of the eccentric ball sleeve 26 shown in FIG. The fitting protrusion 34 is tightly fitted to the inside of the eccentric ball sleeve 26, that is, the inner cylinder CI, and is inserted into the fitting hole 12 of the holder body 2. While being held, the socket flange 36 is seated on the flange 28 of the eccentric ball sleeve 26, thereby defining the fitting amount of the socket 30.

When the socket fitting protrusion 34 is tightly fitted, there is a gap between the outer circumferential surface of the socket fitting protrusion 34 and the inner circumferential surface of the fitting hole 12. Due to the elastic (spring) action of the balls 24 functioning as elastic bodies, the socket fitting protrusion 34 is actively urged in the direction of the resultant force of the ball elastic forces and pressed against the inner circumferential surface of the ball retainer 18. Therefore, action and reaction forces act between the holder main body 2, the eccentric ball sleeve 26, and the socket 30, and there is no room for clearance between these three members, resulting in a stable state with no play between them. In addition, the socket fitting protrusion 34
For tight fitting, it is possible to fit the eccentric ball sleeve 26 into the fitting hole 12 of the holder main body 2 and then push the socket 36 into the sleeve 26 by an appropriate method, or it is possible to fit the socket 30 into the eccentric ball sleeve 26 in advance. It is also possible to fit them into the ball sleeve 26 and then press fit them into the fitting hole 12.

A tool holding hole 88 with a bottom is formed in the socket 30 from the end face on the flange 36 side concentrically with the axis thereof, and a shaft portion of a boring tool or the like is inserted into the holding water 38, and the screw hole 40 The middle 7 flange of the tool is tightened into the screw hole 42 against the 7 flange 36 of the socket 30 with the tool main body having the cutting edge protruding from the socket 30 by a certain distance. Fastened with bolts.

A spring receiving member 44 is fixed by a bolt 46 to the end surface of the socket 30 on the opposite side to the side where the tool holding hole 38 is provided. A disc spring 48 is installed between the spring receiving member 44 and the holder body 2 with a certain compression preload, and its elastic force causes the socket 30 to be pulled into the fitting hole 12 of the holder body 2 in the direction. is energized by In other words, the countersunk spring 48 urges the end surface 32 of the socket 30 and the end surface 10 of the holder body 2 to come into close contact with each other via the seven flange 28 of the eccentric ball sleeve 26, It serves as a biasing means.

The end face 32 of the socket 30 is formed with a U-shaped notch 50 extending radially inward from the outer periphery, while the end face 10 of the holder body 2 has a pin hole parallel to the center line of the fitting hole 12. 52 is provided, and the pin 54 press-fitted into the pin hole 52 passes through the arc-shaped elongated hole 56 provided in the seventh flange 28 of the eccentric ball sleeve 26 to form the U-shaped notch 5.
It is set to 0. Bin 54 as shown in FIG.
are engaged with almost no gap between the mutually parallel side walls of the notch 50, and their engagement prevents the holder body 2 and the socket 30 from relative rotation around the center line of the fitting hole 12, The pin 54 and the notch 50 constitute relative rotation prevention means. On the other hand, eccentric ball sleeve 2
The long hole 56 in the shape of a 60-circular arc is formed along an arc approximately semicircular with a width slightly wider than the diameter of the pin 54.
Therefore, the holder body 2 and the socket 3 are prevented from relative rotation.
0, the rotation of the eccentric ball sleeve 26 is caused by the rotation of the elongated hole 56.
An angular range of approximately 180° from one end to the other is permitted.

On the outer peripheral surface of the seven flange 28 of the eccentric ball sleeve 26,
As shown in FIG. 1, etc., a wrench engagement hole 58 is provided for rotating the eccentric ball sleeve 26 by a desired angle, and in this embodiment, this functions as a means for rotating the eccentric ball sleeve 26. As shown in FIG.
0 is engraved, and a reference line 62 is engraved on the outer peripheral surface of the sleeve 7 flange 28, and these lines together indicate the amount of rotation of the eccentric ball sleeve 26.

In the tool holding device as described above, as schematically shown in FIG.
0 is approximately equal angular interval 3 between each ball 24 of the two ball rows and the inner circumferential surface of the ball retainer 18 in the non-cutting state.
Since the ball 24 can be held with no clearance in the fitting hole 12 of the holder main body 2 while receiving the elastic force of each ball 24, the holding accuracy is very high. Furthermore, when a particularly large cutting load is applied to the tool during cutting, each of the balls 24 is further elastically compressed and deformed, collaborating with the inner and outer peripheral surfaces of the ball retainer 18 in the vicinity of the balls 24. Since the cutting load is received by the two surfaces in contact with each other, the positioning accuracy of the tool edge is high even during heavy cutting, and highly accurate machining dimensions can be obtained.

If it is necessary to adjust the position of the cutting tool to compensate for wear on the cutting tool, or to replace the cutting blade or the tool itself, insert the wrench into the wrench engagement hole 58 and adjust the position while checking the scale m60, etc. By rotating the eccentric ball sleeve 26 by the required angle, the relative position of the cutting edge relative to the spindle center line of the rotary cutting machine will be adjusted to the position of the holder body 2 based on the eccentricity between the inscribed cylinder C1 and the circumscribed cylinder C2. It is displaced in a direction perpendicular to the center line of the fitting hole I2, and its cutting radius is appropriately adjusted. When the eccentric ball sleeve 26 is rotated, each ball 24 belonging to the ball row and the pole retainer 18 are rotated while sliding between the holder body 2 and the socket 30. Since the contact area of the sleeve 26 is small, the operating force required to overcome the frictional force is not very large. Note that the inner circumferential surface of the fitting hole 12 of the holder body 2, the outer circumferential surface of the socket 30, the inner and outer circumferential surfaces of the eccentric ball sleeve 26, etc. must be surface hardened by appropriate means such as carburizing. is desirable.

Next, another embodiment of the present invention will be described based on FIGS. 8 to 10.

In this embodiment, the eccentric ball sleeve 64 does not have a radially outward flange, so that the end surface 10 of the boulder body 2 and the end surface 32 of the socket 30 directly connect to the elasticity of the disc spring 48 without going through the 7 flange. They are held together by force. Instead, worm gear teeth 68 are formed on the outer peripheral surface of the pole retainer 66 over the entire circumferential direction so that the pole retainer 66 functions as a worm wheel, as is clear from FIG. The balls 24 are arranged so as to avoid the part where the worm gear teeth 68 are arranged in a J configuration. On the other hand, the holder main body 2 is provided with a worm accommodation hole 70, the center line of the hole 70 intersects the center line of the fitting hole 12 of the main body 2 at a right angle, and the accommodation hole 70 and the fitting hole 12 are connected to each other. They are communicated with each other by partially interfering with each other, and a worm 72 is accommodated in the accommodation hole 70 thereof. In the worm 70, a threaded sleeve 76 having worm teeth 74 on the outer periphery is fitted onto a worm shaft 78, and is integrated with the worm shaft 78 so as not to rotate relative to each other by a set screw 80 or the like.
The head 84 of the worm shaft 78 is rotatably held by bearings 82° 82 provided at both ends with axial movement restricted in the substantially tangential direction of the fitting hole 12.
A wrench engagement hole 86 is formed in the. Then, the teeth 74 of the worm 72 and the ball retainer 660
The worm gear device is configured by meshing with the eccentric ball sleeve 64 and the eccentric ball sleeve 64 in this embodiment.
When the worm 72 is rotated through the wrench that is engaged with the wrench engagement hole 86, each rotation of the worm 72 causes the socket 30, which is prevented from relative rotation, to rotate. The eccentric ball sleeve 64 is rotated by minute angles between the holder body 2 and the holder body 2.

Since the other parts are the same as those in the above embodiment,
The same reference numerals will be used in the drawings and the explanation will be omitted.

In the tool holding device configured in this manner, the same effects as in the above embodiment can be obtained, and in addition, the amount of rotation of the eccentric ball sleeve 64 can be controlled more precisely, and the accuracy of adjusting the position of the cutting edge can be improved. There is also the advantage that the eccentric ball sleeve 64 can be rotated with a small rotational operating force.

Although two embodiments of the present invention have been described above, they are literally illustrative, and the present invention can be implemented in other embodiments. For example, in the previous embodiments, one ball was housed in each of the plurality of ball holding holes provided in the pole retainer, but the ball holding holes are arranged in an appropriate number of stages in the shape of an elongated hole or notch. There is no problem even if the ball row is formed by storing two or more balls therein. As for the balls themselves, steel balls were used as an example in the above embodiments, but they are not necessarily limited to that. However, even if there is only one ball row, a corresponding effect can be obtained, and on the other hand, three or more ball rows can also be formed. In that case, the diameters of the balls belonging to each ball row are changed, and the balls belonging to each row are gradually moved from the ball row having relatively large diameter poles to the ball row having relatively small diameter poles. As a result, the inscribed and circumscribed cylinders that inscribe and circumscribe all of the ball rows, respectively, are made eccentric with respect to each other. That is, in order to make both cylinders eccentric, it is possible to make the inner peripheral surface and the outer peripheral surface of the ball retainer eccentric to each other, and also by changing the ball diameters of the plurality of ball rows.

Furthermore, in the above embodiment, a fitting hole is provided in the holder body to be attached to the king machine, and a socket 1 to which the cutting tool is attached.
Although one fitting protrusion was provided, it is also possible to reverse this and provide a fitting protrusion on the holder body and a fitting hole into which the protrusion fits on the socket t. In this case, the holder body corresponds to the second member, and the socket corresponds to the first member. This will happen.

Further, for example, the first embodiment shown in FIGS.
If a lamp device is added as shown in FIG. 1, not only the tool holding precision but also the tool holding rigidity will be increased, and it will be possible to carry out rough machining or semi-finishing machining to finishing machining in one step. In the figure, 90 is a clamp shaft,
It extends through the bottom wall of the socket 30. A nut 92 is screwed onto the tip of the clamp shaft 90, and a disc spring 94 is disposed between the nut 92 and the bottom wall of the socket 30. The rear end of the clamp shaft 90 is fitted into the clamp shaft hole 96 of the holder main body 2.
This rear end has a round hole 98 with a constant depth in the direction perpendicular to the axis.
A first tapered hole portion 100 is formed in which the inner diameter gradually decreases from the bottom of the round hole 98 toward the back.

Perpendicular to the axis from the opposite side of this round hole 98 and rearward from the first tapered hole 100, that is, the clamp shaft 90
A second tapered hole portion 102 whose inner diameter gradually decreases as it goes from the outside to the back at a position eccentrically located a certain distance toward the rear end.
are formed, the first tapered hole part 100 and the second tapered hole part 1
02 is provided. The center line of this connecting hole 104 is set between the center line of the first tapered hole part 100 and the center line of the second tapered hole part 102, and the center line of these center lines and the center line of the connecting hole 104 are is arranged to lie on one plane passing through the axis of the clamp shaft 90.

Holder body 2? A through hole 110 is provided at right angles to the axis of the clamp shaft hole 96, and a screw hole portion 112 having a right-hand thread is formed in this through hole 10. A clamp screw 114 is screwed together. The clamp screw 114 is inserted into the screw hole portion 112.
A right-handed threaded portion 116 that is screwed into the right-handed threaded portion 116, a straight portion 118 having a diameter slightly smaller than the root diameter of the right-handed threaded portion 116, a Taber shaft portion 120 whose diameter gradually decreases toward the tip, and a left-handed threaded portion having a left-handed thread. 122 and a hexagonal hole 124 for rotating the clamp screw 114.
The diameter of the hole 20 is smaller than the diameter of the first Taper hole 100, and the Taper angle of the two is the same.

An extrusion metal 126 is slidably and rotatably fitted into the through hole 110f of the holder body.
26 is formed with a taber shaft portion 128 that functions to push out the clamp shaft 9o. The Taber angles of the Taber shaft portion 128 and the second Taber hole portion 1o2 are the same. A screw hole 130 having a left-hand thread is formed in the extrusion metal 126, and the left-hand thread portion 122 of the clamp screw 114 is screwed into the screw hole 130, and is tightened by a lock screw 132 to lock the clamp screw 114. Integral. It is designed to rotate. Connect the clamp screw 114 to the hexagonal hole 124
When the clamp screw 114 is rotated clockwise with
Push the rear part of the inner surface of the taper hole 100 backward, pull in the clamp shaft 90, and conversely tighten the clamp screw 114.
When rotated counterclockwise, the extrusion metal 126 rotates and moves, and the tapered shaft portion 12g moves into the second tapered hole portion 102.
Push the front part of the inner surface forward and tighten the clamp shaft 90.
It is strained so that it is pushed out. In this case, the extrusion metal 126 and the clamp screw 114 are screwed together with a left-hand thread, so when the clamp screw 114 is rotated counterclockwise during use, the extrusion metal 126 tightens easily, preventing loosening. be done.

In such a tool holding device equipped with a lamp device, the internal light position is adjusted by rotating the eccentric ball sleeve 64 while pressing the clamp shaft 90 and weakening the spring force of the disc spring 94. Clamp shaft 9
0 to increase the spring force of the disc spring 94, the end surface 10 of the holder main body 2 and the end surface 32 of the socket 30
It is possible to make a strong connection between the two. After that, the socket 80 and the holder main body 2 move slightly relative to each other in the direction of the center line of the fitting hole 12 of the main body 2, but in the direction perpendicular to the center line, there is no change in the position of the cutting edge. A highly accurate clamping condition can be obtained that is the same as immediately after position adjustment.

In addition, although specific explanations are omitted, it goes without saying that the present invention can be embodied in various improvements and modifications without departing from the scope of the claims.

[Brief explanation of the drawing]

FIG. 1 is a longitudinal cross-sectional view of a cutting tool holding device according to an embodiment of the present invention, FIG. 2 is a front view thereof, and FIG. 3 is a cross-sectional view taken along the line -■ in FIG. FIG. 4 is a front view of the ball retainer of this device, and FIG.
−■Cross-sectional view. FIG. 6 is an explanatory view schematically showing the eccentric ball sleeve in this device, and FIG. 7 is a perspective view showing the rough side state of the socket of this device and the above-mentioned pole retainer. FIG. 8 is a longitudinal sectional view showing another embodiment of the present invention, FIG. 9 is a partially cutaway front view thereof, and FIG. 10 is a sectional view taken along line XX in FIG. 9. FIG. 2: Holder body (first member) 10: End face (first end) 12: Fitting hole 18.66:
Pole retainer 22: Ball holding hole 24: Ball 26.64: Eccentric ball sleeve 28: Flange 30: Socket (second member) 32: End face (second end face) 34: Fitting protrusion 48.94
- Belleville spring (biasing means) 50: Notch 54: Pin 56: Elongated hole 68: Worm gear teeth 72: Worm 7
8: Worm shaft 90: Clamp shaft 114: Clamp screw Applicant Fuji Seiko Co., Ltd. Figure 4 Figure 5] 11 (J

Claims (1)

[Scope of Claims] A first member having a fitting hole with a circular cross section on a first end surface, and a plurality of balls arranged parallel to the center line of the hole along the inner peripheral surface of the fitting hole. a ball retainer that is cylindrical and holds the ball row so that each ball belonging to the ball row protrudes slightly from an outer circumferential surface and an inner circumferential surface and can move in a radial direction; , an eccentric ball sleeve in which an inscribed cylinder and a circumscribed cylinder that are inscribed and circumscribed, respectively, in and around all of the ball rows or all of the ball rows and the pole retainer are eccentric from each other; and the eccentric ball sleeve. a second fitting protrusion protruding from the second end surface and having a circular cross section that is tightly fitted into the fitting hole through the second fitting protrusion;
a member, a second end surface of the second member and a first end surface of the second member;
a biasing means for biasing the first member and the second member to come into close contact with each other through or without a radially outward flange provided on the eccentric ball sleeve; and the fitting between the first member and the second member. Relative rotation means 11 for preventing relative rotation around the center line of the hole, and rotation means for rotating the eccentric ball sleeve by a desired angle between the first member and the second member whose relative rotation is prevented. one of the first member and the second member is attached to a tool attachment part of a machine tool, a cutting tool is attached to the other, and the cutting edge of the cutting tool is attached by rotation of the eccentric ball sleeve. 11. A cutting tool holding device capable of adjusting the position of a cutting edge, characterized in that the relative position of the tool to the tool mounting portion of the machine tool can be adjusted in a direction perpendicular to the center line of the fitting hole.