JP5115753B2 - Work machine with position correction function - Google Patents

Description

  The present invention relates to a work machine with a position correction function in which a tool is attached to a tool holder that can rotate integrally with a spindle.

  In general, various types of tools (work machines) that perform processing on a workpiece through a tool attached to a tool holder, for example, a processing tool, are used. For example, the boring of a cylinder constituting an engine block needs to be machined with high accuracy with an inner cylinder diameter of the order of microns.

  However, in an automobile engine, for example, when machining is performed with the same cutting edge in a mass production process, the cutting edge is worn even with a hard tool such as a CBN tool. Therefore, since the cutting edge of the tool has a reduced processing diameter due to wear, a correction tool holder having a correction function is employed so as to maintain a constant hole diameter.

  For example, a blade edge position adjusting device for a machine tool disclosed in Patent Document 1 is known. This patent document 1 is a machine tool that controls X, Y, and Z axis drive motors on a workpiece and performs machining with a cutting tool at the tip of a spindle. The spindle is rotatably supported by a spindle head. A tool holder is detachably attached to the tip of the tool holder, and the tool holder is rotatably provided with an adjustment shaft at a position eccentric from the spindle rotation axis. By rotating the adjustment shaft, the tool holder is rotated in the radial direction. In the machine tool configured to adjust the radial cutting edge position of the cutting tool provided so as to be displaceable, a rotation preventing member that engages with and disengages from the adjustment shaft is provided on the fixed side of the machine tool, and the spindle head is The X and Y axis drive motors are moved in the X and Y axis directions orthogonal to the spindle axis, and the spindle head is controlled in the X and Y axis directions while the adjustment shaft is locked to the rotation prevention member. And a control means for pivoting the spindle about the axis of the adjusting shaft.

  JP 2002-36009 A

However, in said patent document 1, the slit is provided in the tool holder main body and it is comprised so that a blade edge | tip position may be adjusted by elastically deforming.
For this reason, there exists a problem that the rigidity of tool holder itself falls.

  The present invention is a processing apparatus having a position correction function capable of maintaining a high rigidity and highly accurately correcting a tool attached to the tool holder in the radial direction of the tool holder with a micron order in this type of processing apparatus. The purpose is to provide a machine.

The work machine with position correction function according to the present invention includes a tool holder that can rotate integrally with a spindle, and a ring shape that forms an open end to which one end is fixed to the tool holder and a tool is attached to the other end. an elastic holder having, together with the end portion protrudes axially outward of the elastic holder part, and the actuating shaft member movable axially relative to the tool holder, connected to said actuating shaft member And a conversion mechanism that converts the moving operation of the operating shaft member into a radially expanding / contracting operation of the open end, and a moving mechanism that moves the operating shaft member in the axial direction.

The moving mechanism includes a hydraulic actuator having a first piston provided on an operating shaft member, a second piston having a diameter smaller than that of the first piston, and a second piston having a smaller diameter than the first piston. And a hydraulic pressure generating section that moves the first piston in the axial direction under the moving action of the hydraulic actuator, and the hydraulic actuator and the hydraulic pressure generating section are disposed inside a tool holder .

  The hydraulic pressure generator includes a pressing portion provided on the second piston and a spring that biases the pressing portion toward the outside of the tool holder in order to press the second piston from the outside of the tool holder. It is preferable to provide.

  Further, the hydraulic actuator has a first hydraulic chamber and a second hydraulic chamber divided by a first piston, and the hydraulic pressure generator communicates with the first hydraulic chamber via a first hydraulic path, and an operating shaft. A first hydraulic pressure generating unit that moves the member in one axial direction, and a second hydraulic pressure chamber that communicates with the second hydraulic chamber via a second hydraulic path, and a second hydraulic pressure member that moves the operating shaft member in the other axial direction. It is preferable to include a hydraulic pressure generator.

  Furthermore, the first hydraulic chamber and the second hydraulic chamber communicate with the oil tank via the first hydraulic passage and the second hydraulic passage, and the first hydraulic passage includes the first hydraulic pressure generator. The second hydraulic path is preferably closed when the second hydraulic pressure generator is operated, while being closed when operated.

  The conversion mechanism includes a taper member that is disposed inward of the elastic holder portion and is capable of expanding and contracting the open end portion in the radial direction by moving forward and backward in the axial direction of the elastic holder portion. It preferably has a shape or a rectangular cross section.

  Further, the work machine includes an operation mechanism that operates the hydraulic pressure generating unit from the outside, and the operation mechanism includes a pressing member that presses the second piston, and a spring that biases the pressing member toward the second piston. It is preferable to comprise.

  Furthermore, the work machine is provided in the tool holder, and a position detection sensor that detects the origin position of the operating shaft member, and is detachable from the tool holder, and receives the signal from the position detection sensor and operates the operation machine. It is preferable to include a display unit that displays whether or not the shaft member is arranged at the origin position.

  In the work machine with a position correction function according to the present invention, when the second piston constituting the hydraulic pressure generating unit is pressed (operated), the hydraulic pressure in the hydraulic pressure generating unit is increased. The pressurized hydraulic pressure is sent to a hydraulic actuator through a hydraulic path.

  In that case, the 1st piston which comprises a hydraulic actuator is set larger diameter than a 2nd piston. For this reason, an increase in hydraulic pressure due to the area ratio with the first piston acts on the second piston, and even if the first piston is pressed with a relatively small force, the hydraulic pressure is applied to the second piston. A great force acts through.

  Therefore, even if a large frictional force is acting between the conversion mechanism and the elastic holder, the conversion mechanism is reliably corrected and moved by a desired amount by pressing the first piston with a relatively small force. Can do. Thereby, while maintaining high rigidity, it becomes possible to position-correct the tool attached to the tool holder with high accuracy in the order of microns in the radial direction of the tool holder.

  It is a perspective explanatory view of a machine tool which is a work machine with a position correction function according to the first embodiment of the present invention.   It is principal part cross-sectional explanatory drawing of the said machine tool.   It is front explanatory drawing of the elastic holder part which comprises the said machine tool.   It is a section explanatory view which makes the 1st oil pressure generating part of the tool holder which constitutes the machine tool the principal part.   It is a section explanatory view which makes the 2nd oil pressure generating part of the tool holder which constitutes the machine tool the principal part.   It is explanatory drawing of the operation mechanism which comprises the said machine tool.   It is a side view explaining correction | amendment of a blade tool.   It is a front view explaining correction | amendment of the said blade tool.   It is operation | movement explanatory drawing of the correction | amendment by manual operation.   It is explanatory drawing at the time of confirming the movement amount of the said blade tool by correction | amendment operation | movement.   It is explanatory drawing of the original position detection structure of a tool holder.   It is principal part sectional explanatory drawing of the machine tool which concerns on the 2nd Embodiment of this invention.   It is front explanatory drawing of the elastic holder part which comprises the said machine tool.

  As shown in FIG. 1, a machine tool 10 that is a work machine with a position correction function according to a first embodiment of the present invention includes a main body portion 12, and a main shaft housing 14 is arranged in the X-axis direction on the main body portion 12. , Slidably mounted in the Y-axis direction and the Z-axis direction. As shown in FIG. 2, when a spindle (spindle) 16 is rotatably provided on the spindle housing 14 via a bearing 18, a tool holder (correction tool holder) 20 is detachably attached to the spindle 16. It is done.

  One end of the tool holder 20 is fixed to the tool holder 20, and the other end is provided with a ring-shaped elastic holder portion 24 that forms an open end portion 24a to which tools, for example, blade tools 22a and 22b are attached. The operating shaft member 26 protrudes outward in the axial direction (arrow A direction) of the elastic holder portion 24 and is movable in the axial direction relative to the tool holder 20, and the operating shaft member 26. A conversion mechanism 28 that is connected and converts the movement operation of the operating shaft member 26 into a radial expansion / contraction operation of the open end 24a and a moving mechanism 30 that moves the operation shaft member 26 in the axial direction are mounted. Is done.

  As shown in FIG. 2, the elastic holder portion 24 is provided with a base portion 31 fixed to the tip of the tool holder 20. The base portion 31 is provided with a ring body 32, and a bank portion (deformed apex portion) 34a to which the blade tools 22a and 22b are interchangeably attached to the end portion on the open end portion 24a side of the ring body 32. , 34b and bulged portions 36a, 36b orthogonal to the bank portions 34a, 34b are formed (see FIG. 3).

  The conversion mechanism 28 connected to the end portion of the operating shaft member 26 is disposed inside the elastic holder portion 24, and the open end portion 24a is expanded and contracted in the radial direction when the operating shaft member 26 advances and retracts in the axial direction. A flexible taper member 40 is provided. The taper member 40 has a rectangular cross section and is provided with taper surfaces 44a and 44b that are in sliding contact with the contact surfaces 42a and 42b of the bank portions 34a and 34b constituting the elastic holder portion 24 (see FIGS. 2 and 3).

  As shown in FIG. 4, the moving mechanism 30 includes a hydraulic cylinder portion (hydraulic actuator) 52 having a large-diameter piston (first piston) 50 provided on the operating shaft member 26. The operating shaft member 26 is integrally formed with the large-diameter piston 50 and is provided with a rod portion 48 that is slidably fitted into the guide hole 46.

  In the hydraulic cylinder portion 52, the first hydraulic chamber 52a and the second hydraulic chamber 52b are divided and formed by the large-diameter piston 50. The first hydraulic chamber 52a communicates with the first hydraulic pressure generator 56a via the first hydraulic path 54a, while the second hydraulic chamber 52b is connected to the second hydraulic pressure generator 54a via the second hydraulic path 54b. 56b (see FIG. 5).

  As shown in FIG. 4, the first hydraulic pressure generator 56 a has a small-diameter piston (second piston) 58 a that is smaller in diameter than the large-diameter piston 50. A push button (pressing part) 60a for pressing the small diameter piston 58a is provided. A return spring 62a that urges the push button 60a toward the outside of the tool holder 20, that is, the original position where the stopper 61a is provided, abuts the push button 60a.

  A check valve 64a that allows only the flow of hydraulic pressure from the first hydraulic pressure generator 56a to the first hydraulic chamber 52a is disposed in the first hydraulic path 54a. The second hydraulic chamber 52b communicates with a third hydraulic path 54c for discharging the hydraulic pressure in the second hydraulic chamber 52b to the oil tank 66 when hydraulic pressure is supplied to the first hydraulic chamber 52a.

A check valve 64b is disposed in the third hydraulic path 54c in order to prevent backflow of oil from the oil tank 66. The oil tank 66 and the first hydraulic path 54a communicate with each other via a fourth hydraulic path 54d, and a check valve 64c is provided to prevent back flow to the oil tank 66. The oil tank 66 is urged by a spring 68 to form a tank chamber 72 via a sliding wall 70 that is slidable.
The second hydraulic pressure generator 56b is configured in the same manner as the first hydraulic pressure generator 56a, and the same components are denoted by the same reference numerals, and detailed description thereof is omitted.

As shown in FIG. 5, a check valve 64d that allows only the flow of hydraulic pressure from the second hydraulic pressure generator 56b to the second hydraulic chamber 52b is disposed in the second hydraulic path 54b.
When the hydraulic pressure is supplied to the second hydraulic chamber 52b, a fifth hydraulic path 54e for discharging the hydraulic pressure in the first hydraulic chamber 52a to the oil tank 66 is communicated with the first hydraulic chamber 52a.

  A check valve 64e is disposed in the fifth hydraulic path 54e in order to prevent backflow of oil from the oil tank 66. The oil tank 66 and the second hydraulic path 54b communicate with each other via a sixth hydraulic path 54f, and a check valve 64f is provided to prevent back flow to the oil tank 66.

  The fifth hydraulic path 54e (first hydraulic path) is closed when the first hydraulic pressure generator 56a is operated, while the third hydraulic path 54c (second hydraulic path) is the second hydraulic path 54e (first hydraulic path). The second hydraulic pressure generator 56b is closed when operated. Specifically, as shown in FIG. 4, the first hydraulic pressure generator 56a is provided with a sleeve 74a that is disposed in the first hydraulic path 54a and into which the small diameter piston 58a is slidably fitted. A hole 76a communicating with the fifth hydraulic path 54e passes through the sleeve 74a in the axial direction. When the small-diameter piston 58a is placed in the original position, the hole 76a is opened, while when the small-diameter piston 58a is operated, the hole 76a is closed.

  As shown in FIG. 5, the second hydraulic pressure generator 56b is provided with a sleeve 74b that is disposed in the second hydraulic path 54b and into which the small diameter piston 58b is slidably fitted. A hole 76b communicating with the third hydraulic path 54c penetrates in the axial direction. When the small-diameter piston 58b is placed in the original position, the hole 76b is opened, while when the small-diameter piston 58b is operated, the hole 76b is closed.

As shown in FIG. 1, an operation mechanism 80 for operating the first and second hydraulic pressure generators 56 a and 56 b from the outside is provided outside the tool holder 20. As shown in FIG. 6, the operating mechanism 80 has a housing 84 mounted on a support plate member 82, and a pressure rod (pressing member) 86 for pressing the small diameter pistons 58 a and 58 b is disposed in the housing 84. Is done. A spring 88 is provided in the housing 84 to urge the pressing rod 86 toward the small diameter pistons 58a and 58b. A flange 90 is formed at the rear end of the pressing rod 86, and a proximity sensor 92 that detects the flange 90 is attached to the support plate member 82.
The operation of the machine tool 10 according to the first embodiment configured as described above will be described below.

  First, the first hydraulic chamber 52a and the second hydraulic chamber 52b, the first hydraulic path 54a to the sixth hydraulic path 54f, and the oil tank 66 are filled with oil, respectively. When the cutting edges of the blade tools 22a and 22b are worn, the position of the blade tools 22a and 22b is adjusted (corrected) outward in the radial direction via the conversion mechanism 28.

  Specifically, as shown in FIG. 4, when the push button 60a constituting the first hydraulic pressure generator 56a is pressed in the direction of the arrow B1, the hydraulic pressure in the first hydraulic path 54a increases, and the check The valve 64 a is opened and oil is supplied to the first hydraulic chamber 52 a of the hydraulic cylinder portion 52. In the hydraulic cylinder portion 52, the large-diameter piston 50 is set to have a sufficiently large area as compared with the small-diameter piston 58a, and the large-diameter piston 50 has a volume fraction of the oil amount pushed in by the hydraulic pressure raised by the area ratio. Only moves in the direction of arrow A1.

  When the volume of the second hydraulic chamber 52b is reduced by the movement of the large-diameter piston 50, the hydraulic pressure inside the second hydraulic chamber 52b increases. Accordingly, the check valve 64b disposed in the third hydraulic path 54c is opened, and the oil in the second hydraulic chamber 52b is introduced into the oil tank 66. At this time, the fifth hydraulic path 54e communicating with the first hydraulic chamber 52a is blocked from the oil tank 66 because the hole 76a formed in the sleeve 74a is closed by the small diameter piston 58a. For this reason, it is possible to prevent the hydraulic pressure from being released from the first hydraulic chamber 52a.

  When the large-diameter piston 50 moves in the arrow A1 direction, the operating shaft member 26 attached to the tool holder 20 moves in the axial direction (arrow A1 direction) together with the large-diameter piston 50. As shown in FIG. 7, the conversion mechanism 28 connected to the end of the operating shaft member 26 moves in the direction of the arrow A <b> 1, and the tapered surfaces 44 a and 44 b of the taper member 40 are bank portions that constitute the elastic holder portion 24. It contacts the contact surfaces 42a and 42b of 34a and 34b.

  As a result, the open end 24a is forcibly elastically deformed into an elliptical shape via the taper member 40, and the blade tool is attached to the bank portions 34a and 34b that are the two deformed apex portions of the open end 24a. 22a and 22b move radially outward to increase the machining diameter (see FIGS. 7 and 8).

  As shown in FIG. 4, when the pushing force to the push button 60a is released, the small-diameter piston 58a returns to the original position (position that contacts the stopper 61a) by the elastic force of the return spring 62a. Here, in the first hydraulic path 54a, the hydraulic pressure between the check valve 64a and the first hydraulic pressure generator 56a is temporarily reduced. For this reason, the check valve 64a is closed to prevent the oil in the first hydraulic chamber 52a from flowing back into the first hydraulic path 54a.

  On the other hand, in the oil tank 66, the inside of the tank chamber 72 is maintained at a constant hydraulic pressure under the biasing action of the spring 68. Accordingly, when the hydraulic pressure in the first hydraulic path 54a decreases, the check valve 64c is opened, so that the oil in the oil tank 66 is supplied to the first hydraulic path 54a through the fourth hydraulic path 54d. The Thereby, the pressure balance in the hydraulic system returns to the original state, and one correction operation is completed.

  The elastic holder portion 24 has a sufficiently high spring constant, and in a state where elastic deformation has occurred, the taper member 40 is subjected to a strong grasping force by the taper surfaces 44a and 44b and the contact surfaces 42a and 42b. Is retained. For this reason, the taper member 40 has a function of self-holding its state after sliding in the direction of the arrow A1 with high hydraulic pressure by pushing the small-diameter piston 58a.

  When it is necessary to further expand the blade tools 22a and 22b to appropriate positions, as described above, after pushing the small diameter piston 58a a predetermined number of times and moving and shifting the positions of the blade tools 22a and 22b, What is necessary is just to start a process.

  Here, for example, the outer diameter of the small-diameter piston 58a is 4 mm (diameter), the outer diameter of the large-diameter piston 50 is 50 mm (diameter), and the outer diameter of the shaft portion of the operating shaft member 26 is 22 mm (diameter). When the small-diameter piston 58a is pushed in by 4 mm, an oil amount of 50 cubic mm is sent to the first hydraulic chamber 52a. Since the pressure receiving area of the piston portion is 1583 square mm, the large diameter piston 50 slides by 0.03 mm in the arrow A1 direction.

  When the taper angle of the taper surfaces 44a and 44b is 1/30, the elastic holder portion 24 to which the blade tools 22a and 22b are attached is enlarged by 0.001 mm in the radial direction. That is, when the small-diameter piston 58a is pushed once, the diameter of the blade tools 22a and 22b can be increased by 0.001 mm (0.002 mm in diameter). As described above, the blade tools 22a and 22b perform the blade edge adjustment on the micron order with high accuracy.

  Furthermore, in the first embodiment, the area ratio of the small diameter piston 58a and the large diameter piston 50 is 126 times. Therefore, for example, when the small-diameter piston 58a is pushed with a force of 30N, the acting force for pushing out the large-diameter piston 50 is increased to 3780N. In addition, since this power is increased and expanded at a taper ratio of 1/30 of the taper member 40 at the contact portion of the elastic holder portion 24, sufficient power for forcibly expanding the elastic holder portion 24 is obtained. It is done.

  Further, when the blade tools 22a and 22b are returned inward in the radial direction, as shown in FIG. 5, the push button 60b constituting the second hydraulic pressure generator 56b is pressed. For this reason, the hydraulic pressure in the second hydraulic path 54 b increases, the check valve 64 d is opened, and oil is supplied to the second hydraulic chamber 52 b of the hydraulic cylinder portion 52.

  In the hydraulic cylinder portion 52, the large-diameter piston 50 moves in the arrow A2 direction by the volume of the oil amount pushed in by the hydraulic pressure raised by the area ratio. When the volume of the first hydraulic chamber 52a is reduced by the movement of the large-diameter piston 50, the hydraulic pressure inside the first hydraulic chamber 52a increases. Accordingly, the check valve 64e disposed in the fifth hydraulic path 54e is opened, and the oil in the first hydraulic chamber 52a is introduced into the oil tank 66. At this time, the third hydraulic path 54c communicating with the second hydraulic chamber 52b is blocked from the oil tank 66 because the hole 76b formed in the sleeve 74b is closed by the small diameter piston 58b. For this reason, it is possible to prevent the hydraulic pressure from being released from the second hydraulic chamber 52b.

  As shown in FIG. 2, when the large-diameter piston 50 moves in the arrow A2 direction, the operating shaft member 26 attached to the tool holder 20 is integrated with the large-diameter piston 50 in the axial direction (arrow A2 direction). Moving. The conversion mechanism 28 coupled to the end of the operating shaft member 26 moves in the direction of the arrow A2, and the tapered surfaces 44a and 44b of the tapered member 40 are contact surfaces 42a of the bank portions 34a and 34b constituting the elastic holder portion 24. , 42b is in sliding contact with the direction away from 42b.

  Thereby, the open end 24a is elastically deformed radially inward by its own elastic force, and the blade tool is attached to the bank portions 34a and 34b which are the two deformation apexes of the open end 24a. 22a and 22b move radially inward to reduce the machining diameter.

  When the pushing force to the push button 60b is released, as shown in FIG. 5, the small-diameter piston 58b returns to the original position (position where it abuts against the stopper 61b) by the elastic force of the return spring 62b. Here, in the second hydraulic path 54b, the hydraulic pressure between the check valve 64d and the second hydraulic pressure generator 56b is temporarily reduced. Therefore, the check valve 64d is closed to prevent the oil in the second hydraulic chamber 52b from flowing back into the second hydraulic path 54b.

  On the other hand, in the oil tank 66, the inside of the tank chamber 72 is maintained at a constant hydraulic pressure under the biasing action of the spring 68. Accordingly, when the hydraulic pressure in the second hydraulic path 54b decreases, the check valve 64f is opened, so that the oil in the oil tank 66 is supplied to the second hydraulic path 54b through the sixth hydraulic path 54f. The Thereby, the pressure balance in the hydraulic system returns to the original state, and one correction operation is completed.

  The first hydraulic pressure generator 56 a and the second hydraulic pressure generator 56 b are automatically operated by the operation mechanism 80 in accordance with program control (NC control) of the machine tool 10. The spindle 16 of the machine tool 10 can lock the rotation of the tool holder 20 at a specific phase by an orientation function.

  Therefore, during the orientation, the axial movement direction of the small-diameter piston 58a or 58b of the tool holder 20 and the sliding shaft of the pressing rod 86 are installed in the same direction, and any one of the push buttons 60a and 60b of the tool holder 20 The pressure rod 86 is set to be pushed.

  Since the first hydraulic pressure generator 56a and the second hydraulic pressure generator 56b are controlled in the same manner, only the first hydraulic pressure generator 56a will be described below, and the second hydraulic pressure generator 56b Description is omitted.

  Here, in order to perform the plus correction operation (the diameter expansion correction operation) by automatic operation, after orientation, as shown in FIG. 6, the axis of the small diameter piston 58a and the axis of the pressing rod 86 are aligned by NC control, and the tool The holder 20 is moved in the arrow X1 direction. The pressing rod 86 pushes the small-diameter piston 58a to the stroke end via the push button 60a. Thereby, plus correction is performed.

  At that time, the rear of the pressing rod 86 is supported by a spring 88. The spring 88 has a sufficiently strong rigidity against the sliding action force of the small diameter piston 58a. For this reason, the small diameter piston 58a can be pushed in to the stroke end. On the other hand, when the tool holder 20 slides in the direction of the arrow X1 beyond the stroke end due to a program error or the like, the spring 88 is contracted to absorb the forcing force. Therefore, even if there is a program mistake or the like, the spring 88 functions as a safety valve, so that the collision between the tool holder 20 and the pressing rod 86 can be absorbed.

  Further, the pressing rod 86 and the spring 88 can be used as an automatic correction operation check. In this embodiment, when the elastic value of the spring 88 is set smaller than the operating sliding force of the small-diameter piston 58a and the small-diameter piston 58a is pushed in the direction of the arrow X1 to the dead end of the spring 88, the flange 90 of the pressing rod 86 is moved to the proximity switch. 92 can be operated to confirm that the correction operation has been performed.

  Furthermore, it is also possible to control the first hydraulic pressure generating unit 56a (the same applies to the second hydraulic pressure generating unit 56b) by manual operation. As shown in FIG. 9, by pushing the push button 60a on the side surface of the tool holder 20 from the standby state (no load state) position determined by the action of the return spring 62a and the stopper 61a to the stroke end in the arrow D direction, The amount of hydraulic oil is determined. The manual correction operation is performed by pressing the push button 60a using a T wrench or the like and a long and narrow arbor T or the like.

  The hydraulic oil amount and the correction movement amount (= inching amount) have a correlation, and the correction amount is determined by the product of the amount that moves each time the small-diameter piston 58a is pressed and the number of times it is pressed. For example, if the correction amount is moved by 2 μm (diameter) with a single push, the push button 60a may be pressed three times to correct 6 μm (diameter).

  Further, as shown in FIG. 10, the push button 60a or 60b is placed in a state where the tool holder 20 is placed on the tool presetter 94 and the dial gauge 96 is disposed on the blade tip of the blade tool 22a (or blade tool 22b). If is pressed, the movement amount of the blade tool by the correction operation is confirmed.

  That is, when the tool holder 20 is placed on the tool presetter 94 and the preset work of the machining diameter is performed, the push buttons 60a and 60b can be easily pushed by a human hand with a light force. This is very convenient.

  By the way, when the tool holder 20 is preset, it is preferable that an accurate mark position (so-called original position) serving as a reference for starting the correction movement is provided. In managing only the number of times the push buttons 60a and 60b are pushed, if the correction movement is repeated many times, the starting position may be changed little by little, and there is a possibility that the starting position is deviated.

  As shown in FIG. 11, the work machine 10 is provided in the tool holder 20 and is detachably attached to the tool holder 20 and a micro switch (position detection sensor) 100 that detects the origin position of the operating shaft member 26. And a portable lamp unit (display unit) 102 that receives a signal from the micro switch 100 and displays whether or not the operating shaft member 26 is disposed at the origin position.

  An insulator 104 having a planar contact surface is provided on the side surface of the tool holder 20, and two conductive contact pins 106 are embedded in the insulator 104. Two electric wires 108 are taken out from the contact pins 106 and connected to two terminals of the micro switch 100 which is also mounted in the tool holder 20.

  The micro switch 100 is provided with a contact end 100a, and the contact end 100a is slidably engaged with the long groove 110 of the operating shaft member 26. The microswitch 100 can be turned on and off in microns.

  The lamp unit 102 has a flat surface facing the insulator 104, and the lamp unit 102 is provided with a dry battery 112, an LED lamp 114, and two sliding pins 116 connected by electric wires (not shown). It is done. The sliding pin 116 can be advanced and retracted via a spring 118. The lamp unit 102 is held in a state of being in close contact with the insulator 104 on the side surface of the tool holder 20 via the magnet 120.

  In such a configuration, when the operation shaft member 26 of the tool holder 20 moves in the direction of the arrow A2 and reaches the correction start position, the contact end of the micro switch 100 disposed in the long groove 110 of the operation shaft member 26 is obtained. 100a moves in the direction of arrow E, and the terminal of the micro switch 100 is turned ON. For this reason, the electrical circuit of the portable lamp unit 102 can be electrically coupled, and the LED lamp 114 is lit. By this lighting, the start position can be confirmed accurately.

  On the other hand, when the operation shaft member 26 of the tool holder 20 moves in the arrow A1 direction, the micro switch 100 is turned OFF and the LED lamp 114 is turned off. Thus, the start position can be accurately confirmed from the outside by turning the LED lamp 114 on and off.

  FIG. 12 is an explanatory cross-sectional view of a main part of a machine tool 120 according to the second embodiment of the present invention. The same components as those of the machine tool 10 according to the first embodiment are denoted by the same reference numerals, and detailed description thereof is omitted.

  The machine tool 120 includes a conversion mechanism 122 that is connected to the operation shaft member 26 and converts the movement operation of the operation shaft member 26 into the expansion / contraction operation in the radial direction of the open end 24a. As shown in FIGS. 12 and 13, the conversion mechanism 122 is disposed inside the elastic holder portion 24, and the open end 24 a can be expanded and contracted in the radial direction by moving forward and backward in the axial direction of the elastic holder portion 24. A tapered member 124 is provided. The taper member 124 has a circular cross section, and is set to a conical shape provided with a circular taper surface 128 slidably contacting the arcuate contact surfaces 126a and 126b of the bank portions 34a and 34b constituting the elastic holder portion 24.

  Therefore, in the second embodiment, a tapered member 124 having a circular cross section is employed instead of the tapered member 40 having a rectangular cross section, and the same effect as in the first embodiment can be obtained.

DESCRIPTION OF SYMBOLS 10, 120 ... Machine tool 16 ... Spindle 20 ... Tool holder 22a, 22b ... Blade tool 24 ... Elastic holder part 24a ... Open end part 26 ... Operation shaft member 28, 122 ... Conversion mechanism 30 ... Movement mechanism 34a, 34b ... Bank part 40, 124 ... taper members 42a, 42b, 126a, 126b ... contact surfaces 44a, 44b, 128 ... taper surfaces 50 ... large diameter pistons 52 ... hydraulic cylinders 52a, 52b ... hydraulic chambers 54a-54f ... hydraulic paths 56a, 56b ... Hydraulic pressure generators 58a, 58b ... small-diameter pistons 60a, 60b ... push buttons 62a, 62b ... return springs 64a-64f ... check valves 66 ... oil tanks 68 ... springs 74a, 74b ... sleeves 80 ... operating mechanisms 86 ... pressing rods 100 ... micro Switch 102 ... Lamp unit

Claims (7)

A tool holder that can rotate integrally with the spindle;
An elastic holder part having a ring shape forming an open end part to which one end is fixed to the tool holder and the tool is attached to the other end;
With end protrudes axially outward of the elastic holder part, and the actuating shaft member movable axially relative to the tool holder,
A conversion mechanism that is connected to the operating shaft member and converts a movement operation of the operating shaft member into a radially expanding / contracting operation of the open end;
A moving mechanism for moving the operating shaft member in the axial direction;
With
The moving mechanism includes a hydraulic actuator having a first piston provided on the operating shaft member;
A hydraulic pressure generating portion that communicates with the hydraulic actuator via a hydraulic path, and that has a second piston having a smaller diameter than the first piston, and that moves the first piston in the axial direction under the action of movement of the second piston. When,
Equipped with a,
The hydraulic actuator and the hydraulic pressure generating unit, a position correction function working machine, characterized in Rukoto is disposed within the tool holder. The work machine according to claim 1, wherein the hydraulic pressure generator is configured to press the second piston from the outside of the tool holder;
A spring for urging the pressing portion toward the outside of the tool holder;
A work machine with a position correction function. The work machine according to claim 1 or 2, wherein the hydraulic actuator includes a first hydraulic chamber and a second hydraulic chamber divided by the first piston,
The hydraulic pressure generating unit communicates with the first hydraulic pressure chamber via the first hydraulic pressure path, and moves the operating shaft member in one of the axial directions.
A second hydraulic pressure generating portion that communicates with the second hydraulic pressure chamber via the second hydraulic pressure path and moves the operating shaft member in the other axial direction;
A work machine with a position correction function. The work machine according to claim 3, wherein the first hydraulic chamber and the second hydraulic chamber communicate with an oil tank via the first hydraulic passage and the second hydraulic passage,
While the first hydraulic path is closed when the first hydraulic pressure generator is operated,
The work machine with a position correction function, wherein the second hydraulic path is closed when the second hydraulic pressure generator is operated. 5. The work machine according to claim 1, wherein the conversion mechanism is disposed inward of the elastic holder portion and moves the open end portion forward and backward in an axial direction of the elastic holder portion. Equipped with a taper member that can expand and contract in the radial direction,
The taper member has a circular cross section or a rectangular cross section, and has a position correction function-equipped work machine. The work machine according to any one of claims 1 to 5, further comprising an operation mechanism for operating the hydraulic pressure generating unit from outside.
The operating mechanism includes a pressing member that presses the second piston,
A spring for urging the pressing member toward the second piston;
A work machine with a position correction function. In the work machine according to any one of claims 1 to 6, a position detection sensor that is provided in the tool holder and detects an origin position of the operation shaft member;
A display unit that is detachable from the tool holder, and displays whether or not the operating shaft member is disposed at an origin position in response to a signal from the position detection sensor;
A work machine with a position correction function.

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