US 4,773,636 AGrant
Clamping Apparatus
Issue Date:1988-09-27
•3 Claims
•6 Drawing Sheets
Abstract
A clamping apparatus comprises a clamping unit having a pair of clamping plates and clamping plate drive unit, and a fixing unit for fixing the clamping unit to an arbitrary position on a base frame. The clamping unit has a sub base to which one clamping plate and drive unit for driving the other plate are fixed. The drive unit has a leadscrew fixed at its one end to the other plate, and an outer cylindrical member rotatably provided on the sub base and holding the other end of the leadscrew. An inner cylindrical member and a piston are provided in the bore of the outer member. The inner member is threadably fitted over the other end of the leadscrew, and is rotated integrally with the outer one so as to move the leadscrew for a relatively long distance in the longitudinal direction. The outer member is connected to a pressurized fluid supplying devices for supplying fluid to the bore of the outer member, so that the piston is moved by the pressurized fluid for a relatively short distance in the longitudinal direction. This movement of the piston causes the inner member to move outwardly in the longitudinal direction in the bore of the outer member, and the leadscrew, together with the other plate, moves to approach one plate.
Metadata
Assignee
- Man Design Co., Ltd.
Inventor
- Shiro Takahashi
Application Information
Application Number:US 0794139
Filing Date:1987-07-30
Priority Date:1987-07-30
Art Unit:323
Classifications
IPC:
B23Q 308
Field of Search:
26920;25;32;82-84;221;246
Patent Drawings (6 sheets)
Description
BACKGROUND OF THE INVENTION
The present invention relates to a clamping apparatus for clamping an article by a pair of clamping plates and, more particularly, to such a clamping apparatus having a clamping unit, which has a pair of clamping plates and clamping plate driving means and which is movably placed on a base frame, and enabling to make additional tightening of the clamping force of the clamping plates and free change of the position where the clamping unit is fixed on the base frame by utilizing fluid pressure.
In a conventional clamping apparatus for clamping an article by a pair of clamping plates, the pair of clamping plates are mounted on a base frame so as to approach or move away one another. A pair of feed threads spirally wound in opposite directions and formed at separate positions on one leadscrew shaft are engaged with the pair of clamping plates so as to move the pair of clamping plates on the base frame by the rotation of the leadscrew shaft.
The above-mentioned clamping apparatus is used, for example, on a bed of a machine tool to fix a workpiece. The clamping apparatus is placed on the bed, and is fixed on the bed with bolts.
In the conventional clamping apparatus, the pair of clamping plates cannot be moved on the base frame while clamping an article by the pair of clamping plates. Therefore, when the above-described clamping apparatus is used, for example, in a machine tool, such as a small-sized drilling machine, which cannot move the position of a cutting tool in the back and forth, and lateral directions on a bed, to form holes at a plurality of positions of the workpiece, the position of the clamping apparatus must be moved on the bed whenever the position of drilling is changed, and clamping and unclamping works of clamping bolts is required for changing the position of drilling. Since a plurality of clamping bolts are provided in the clamping apparatus, a large quantity of labor and time is required to execute clamping and unclamping works of the bolts, thereby reducing working efficiency. A machine tool, which can move the position of a cutting tool in the back and forth, and lateral directions and can raise the working efficiency in the above-mentioned work, is expensive.
In the above-mentioned clamping apparatus, the workpiece is clamped only by the force loaded to the pair of clamping plates from the leadscrew shaft. Therefore, the clamping tends to be loosened due to the vibration produced at the workpiece in case of working, thereby causing the working accuracy to decrease and the workpiece to be removed from the clamping apparatus. The latter largely causes an accident resulting in injury or death.
Summary of the Invention
The present invention has been made in consideration of this and has for its object to provide a clamping apparatus which can readily change a position for fixing an article on a bed of a machine tool while clamping the article by a pair of clamping plates, does not cause a workpiece to be released from the clamping due to a vibration during the working, thereby surely preventing the working accuracy from decreasing and the workpiece from dropping from the clamping apparatus and can be readily mounted in an existing machine tool with an inexpensive simple construction.
In order to achieve the above and other objects, there is provided according to the present invention a clamping apparatus having a base frame, a pair of clamping plates provided on the base frame so as to approach or move away from one another, clamping plate driving means for driving the pair of clamping plates, further comprising a clamping unit having the pair of clamping plates and clamping plate driving means; and a fixing unit coupled to the clamping unit for fixing the clamping unit to an arbitrary position on the base frame; and the clamping unit and the fixing unit having the following constitutions.
The clamping unit has a sub base member to which one clamping plate and the clamping plate driving means are fixed, the other clamping plate is driven by the clamping plate driving means to approach or move away from the one clamping plate. The clamping plate driving means has a leadscrew shaft fixed at its one end to the other clamping plate; an outer cylindrical member provided at the sub base member so as to be located concentrically with the leadscrew shaft and to be rotatable to the sub base member and having means for connecting the bore thereof to pressurized fluid supplying means; an inner cylindrical member disposed in the bore of the outer cylindrical member so as to be rotatable integrally with the outer cylindrical member in the circumferential direction of the outer cylindrical member and to be slidable relative to the outer cylindrical member in a direction along the longitudinal center line of the outer cylindrical member, and threadably fitted over the leadscrew shaft; and a piston disposed in the bore of the outer cylindrical member so as to be slidable relative to the outer cylindrical member in a direction along the longitudinal center line of the outer cylindrical member, the piston being slid in the bore of the outer cylindrical member by the pressure of the fluid supplied from the pressurized fluid supplying means into the bore of the outer cylindrical member so that the piston drives the inner cylindrical member to project the leadscrew shaft from the outer cylindrical member. Further, a through hole is formed at the position of the base frame opposing to the sub base member. The fixing unit comprises a casing disposed on the surface area of the base frame, which is opposite to the surface area disposed thereon with the clamping unit, so as to face the through hole and having means for connecting the bore thereof to the pressurized fluid supplying means; an engaging rod disposed in the casing so as to be movable in a direction along the center line of the through hole, and extended from the casing into the through hole to be engaged with the sub base member of the clamping unit in a direction that the sub base member approaches the base frame; urging means disposed in the casing for urging the engaging rod in a direction for engaging the engaging rod with the sub base member of the clamping unit; and a diaphragm member disposed in the casing so as to press the engaging rod against the urging force of the urging means in a direction for releasing the engagement of the sub base member of the clamping unit with the engaging rod by the pressure of the fluid supplied from the pressurized fluid supplying means into the casing.
In the clamping apparatus according to the present invention and constructed as described above, it is preferable that the clamping plate driving means has a pressure regulating unit for controlling the magnitude of the pressure supplied from the pressurized fluid supplying means to the bore of the outer cylindrical member.
With the construction as described above, the clamping force generated from the clamping plate driving means can be freely controlled by the pressure of the pressurized fluid supplied from the pressurized fluid supplying means into the bore of the outer cylindrical member.
When the clamping apparatus according to the present invention has the pressure regulating unit, it is preferable that the pressure regulating unit comprises a body connected to the outer cylindrical member, and having a fluid passage to be connected to the pressurized fluid supplying means connecting means of the outer cylindrical member and means for connecting the fluid passage to the pressurized fluid supplying means; a valve seat formed in the fluid passage; a valve body disposed in the fluid passage so as to be movable between the closed position, where the valve body in seated on the valve seat, and the open position, where the valve body is separated from the valve seat; an actuator member being movable between the first position and the second position in the fluid passage, the actuator member allowing the valve body to be disposed at its closed position at the first position, driving the valve body to the open position by the movement from the first position to the second position, and being urged to the first position by the pressure of the pressurized fluid in the fluid passage; urging means provided in the body so as to urge the actuator member to the second position against the pressure of the pressurized fluid in the fluid passage; and urging force regulating means provided on the body so as to be exposed on the outer surface of the body, and regulating the urging force generated from the urging means.
The construction as described above is simple and compact.
Brief Description of the Drawings
FIG. 1 is a schematic perspective view showing a clamping apparatus according to an embodiment of the present invention;
FIG. 2 is a schematic longitudinal sectional view of clamping plate driving means of the clamping apparatus of FIG. 1, wherein the upper half illustrates the state before receiving pressurized fluid from pressurized fluid supplying means and the lower half illustrates the state when receiving pressurized fluid from pressurized fluid supplying means;
FIG. 3 is a perspective exploded view showing the state that a fourth piston component member, a fourth cylinder member, an end piston and an end cover are separated from the clamping plate driving means to illustrate the construction of a pressurized fluid passage in the clamping plate driving means of FIG. 2;
FIG. 4 is a schematic longitudinal sectional view of a pressure regulating unit coupled with the clamping plate driving means of the clamping apparatus of FIG. 1;
FIG. 5 is a perspective view of a joint member of a part of the body of the pressure regulating unit of FIG. 4;
FIG. 6 is a perspective exploded view of a rear case of a part of the body of the pressure regulating unit, a regulating ring of a part of energizing force regulating means attached to the rear case and a spring retainer ring of FIG. 4; and
FIG. 7 is a schematic longitudinal sectional view of a fixing unit of the clamping apparatus of FIG. 1.
Detailed Description of the Preferred Embodiments
FIG. 1 schematically shows the external appearance of a clamping apparatus according to a first embodiment of the present invention.
The clamping apparatus is fixed at its base frame 10 by fixing bolts on a bed of a machine tool such as a drilling machine, not shown. Clamping unit 18, having a pair of clamping plates 12, 14 and clamping plate driving means 16 for driving clamping plates 12, 14, is placed on base frame 10.
Clamping unit 18 has sub base member 20 to which first clamping plate 12 is fixed. Such base member 20 is placed on base frame 10, and second clamping plate 14 is so placed on sub base member 20 as to approach or move away from first clamping plate 14. Leadscrew shaft 22 of clamping plate driving means 16 is fixed at its one end to second clamping plate 14, and shaft 22 is projected from outer cylindrical member 24 of clamping plate driving means 16 concentrically located with shaft 22 and rotatably provided on sub base member 20. Rotation of outer cylindrical member 24 cause leadscrew shaft 22 to move forward or backward and hence cause second clamping plate 14 to approach or move away from first clamping plate 12. Pressurized fluid supplying means 28 is coupled through pressure regulating unit 26 to outer cylindrical member 24. In this embodiment, pressurized fluid supplying means 28 is a compressor. Leadscrew shaft 22 is movable in the back and forth direction for a relatively short distance in outer cylindrical member 24 irrespective of the rotation of shaft 22 or member 24, and pressurized fluid, i.e., compressed air, supplied from supplying means 28 into cylindrical member 24 acts to shaft 22 so that shaft 22 moves forward in cylindrical member 24. The action of such pressurized fluid reinforces the clamping force to a workpiece by first clamping plate 12 and second clamping plate 14 to be performed by the rotation of cylindrical member 24. Pressure regulating unit 26 maintains the magnitude of the pressure of the pressurized fluid supplied from pressurized fluid supplying means 28 into outer cylindrical member 24 at constant and the rotation of a regulating ring 30 on the outer peripheral surface of outer cylindrical member 24 enables pressure regulating unit 26 to set freely the magnitude of that pressure.
Fixing unit 32 for fixing sub base member 20 at an arbitrary position on the upper surface of base frame 10 is disposed on the lower surface side of base frame 10 and connected to sub base member 20 via a through hole formed in base frame 10. Fixing unit 32 is connected through switching valve 34 to pressurized fluid supplying means 28. When valve 34 is opened to supply the pressurized fluid from supplying means 28 to fixing unit 32, fixing unit 32 releases sub base member 20 from its fixation on base frame 10. When valve 34 is closed to shut off the supply of the pressurized fluid from supplying means 28 to fixing unit 32, fixing unit 32 rigidly fixes sub base member 20 on base frame 10. Sub base member 20 released from it fixation on base frame 10 can freely displace on base frame 10.
FIG. 2 is a longitudinal sectional view showing the detail of clamping plate driving means 26 of clamping unit 18. The longitudinal sectional view of outer cylindrical member 24 shows in the upper portion the state that compressed air has not yet supplied into outer cylindrical member 24 and in the lower portion the state that compressed air has already supplied into outer cylindrical member 24.
As shown in detail in FIG. 2, second clamping plate 14 is screwed on the left end of leadscrew shaft 22.
Outer cylindrical member 24 is fixed to a large-diameter portion of stepped cylindrical housing block 36, and a small-diameter portion of housing block 36 is supported by a holder member 38 fixed on sub base member 20 so that the housing block 36 is located concentrically with shaft 22 and is rotatable relative to sub base member 20. Stop ring 40 is engaged with the outer periphery of small-diameter portion of housing block 36 projected from holder member 38 at second clamping plate side, and stop ring 40 contacts the end face of holder member 38 at the second clamping plate side to prevent housing block 36 from dropping out from holder member 38.
Inner cylindrical member 42 is contained in the bore of housing block 36 so as to be slidable therein, and threadably fitted over leadscrew shaft 22. Keyway 44 is formed on the inner peripheral surface of the bore of block 36 so as to extend in a direction along the center line of the bore of block 36, and key 46 fixed on the outer peripheral surface of inner cylindrical member 42 is contained in keyway 44 so as to be slidable thereto. Key 46 is engaged with keyway 44 in the circumferential direction to integrally rotate outer cylindrical member 24 and inner cylindrical member 42, and the rotation of inner cylindrical member 42 cause leadscrew 22 to move in the back and forth direction. Key 46 also slides in keyway 44 in a direction along the center line of the bore of block 36 to integrally move shaft 22 and inner cylindrical member 42 in the back and forth direction.
Piston 48 for integrally moving inner cylindrical member 42 and shaft 22 in the back and forth direction, and cylinder 50 for slidably contacting piston 48 are contained in the bore of outer cylindrical member 24. Cylinder 50 is constructed by four members 50A, 50B, 50C, 50D of the same structure disposed in series in a direction along the center line thereof, and each member 50A, 50B, 50C or 50D has thin outer peripheral portion 52 fitted to the inner peripheral surface of the bore of outer cylindrical member 24 and inner flange 54 projected radially inward from the inner surface of thin outer peripheral portion 52 at inner cylindrical member side. Piston 48 is also constructed by four members 48A, 48B, 48C, 48D of the same structure disposed in series in a direction along the center line thereof, and each member 48A, 48B, 48C or 48D has cylindrical inner peripheral portion 56 slidably inserted into the corresponding one of the projecting end faces of inner flanges 54 of the four cylinder members 50A, 50B, 50C, 50D and outer flange 58 projected radially outward from the outer surface of inner peripheral portion 56 at the inner cylindrical member side. The projecting end faces of outer flanges 58 of second to fourth members 48B, 48C, 48D of piston 48 are slidably fitted to the inner peripheral surfaces of thin outer peripheral portions 52 of first to third members 50A, 50B, 50C of cylinder 50, and only projecting end face of outer flange 58 of first member 48A of piston 48 is slidably fitted to the inner peripheral surface of the bore of block 36 at the end of the outer cylindrical member side. The bore of each member 48A, 48B, 48C or 48B of piston 48 has a diameter slightly larger than the outer diameter of shaft 22, and the end of shaft 22 projected from inner cylindrical member 42 to outer cylindrical member 24 is inserted into bore 60 of piston 48 formed of the bores of four members 48A, 48B, 48 and 48D.
The peripheral surface of disc-like end piston 62 is slidably fitted to the inner peripheral surface of thin outer peripheral portion 52 of fourth member 50D of cylinder 50, and boss 64 is formed at the side surface of end piston 62 contacted with the free end face of cylindrical inner periphery 56 of fourth member 48D of piston 48, boss 64 being slidably fitted into bore of cylindrical inner peripheral portion 56 of fourth member 48D.
The outer peripheral surface of end cover 66 is fitted to the inner peripheral surface of bore of outer cylindrical member 24 at the end located farther to inner cylindrical member 42, and the outer peripheral area of the inner side face of end cover 66 is contacted with the free end face of thin outer peripheral portion 52 of fourth member 50D of cylinder 50. End cover 66 is fixed to the inner peripheral surface of the bore of outer cylindrical member 24 by stop ring 68. Thus, four members 50A, 50B, 50C, 50D of cylinder 50 are clamped by the outer cylindrical member side end face of housing block 36 and the inside face of end cover 66 to be fixed in the bore of outer cylindrical member 24.
Compression coil spring 70 is wound on the end of inner cylindrical member 42 at outer cylindrical member side. Spring 70 is contacted at both ends with a spring seat formed on the end face of block 36 at the outer cylindrical member side of block 36 and with a spring retainer flange of inner cylindrical member 42 at the outer cylindrical member side, so that inner cylindrical member 42 urges piston 48 and end piston 62 in a direction for approaching end cover 66 of outer cylindrical member 24.
Connecting hole 72 threadably engaged with the outlet of pressure regulating unit 25 in a hermetically sealing manner is formed at end cover 66.
Pressurized fluid passages are formed on the inside surfaces of end cover 66, the outer peripheral surfaces of thin outer peripheral portions 52 of four members 48A, 48B, 48C, 40D of cylinder 50 and the side surfaces of the four members located at the inner cylindrical member side, the pressurized fluid passages making pressurized fluid supplied from pressurized fluid supplying means 28 through pressure regulating unit 26 into outer cylindrical member 24 of clamping plate driving means 16 act on four member 48A, 48B, 48C, 48D of piston 48.
The pressurized fluid passages will be described in more detail. As shown in detail in FIG. 3, axial projections 74, 76 having diameter smaller than the maximum diameter of the inner side surface of end cover 66 are concentrically stepwisely formed on the inner side surface of end cover 66, and radially extended grooves 78 are formed on projections 74, 76. A chamfered portion 80 extended in a direction along the longitudinal center line of cylinder 50 is formed on the outer peripheral surface of thin outer peripheral portions 52 of four members 48A, 48B, 48C, 48D of cylinder 50, and axial projections 82, 84 having diameter smaller than the maximum diameter of each of the four members are concentrically stepwisely formed on the side surface of each of four members located at the inner cylindrical member side, and radially extended grooves 86 are formed on axial projection 84 disposed outward.
The pressurized fluid supplied from pressurized fluid supplying means 28 into outer cylindrical member 24 of clamping plate driving means 16 is acted on the end cover side surface of end piston 62 and is introduced through radial grooves 78 of end cover 66 into a space formed between the outer peripheral surface of axial projection 76 disposed outward and the inner peripheral surface of the bore of outer cylindrical member 24. Compressed fluid in this space is introduced through chamfered portions 80 of four members 50A, 50B, 50C, 50D of cylinder 50 into each space formed between the outer peripheral surface of axial projection 84 of each of the four members and the inner peripheral surface of the bore of outer cylindrical member 24, further introduced through each radial groove 86 into each space formed between the projecting end face of axial projection 84 of each of the four members and the corresponding side surface of the end cover side of outer flange 58 of each of four members 48A, 48B, 48C, 48D of piston 48, and acts on the flanges 58 of four corresponding members 48A, 48B, 48C, 48D.
Piston 48 acted with compressed air to the outer flanges 58 of four members 48A, 48B, 48C, 48D is moved, together with end piston 62, to project inner cylindrical member 42 and shaft 22 from outer cylindrical member 24 against the urging force of compression coil spring 70.
O-rings 88, 90 are mounted on the portion of the outer peripheral surface of housing block 36, the portion being engaged with the inner peripheral surface of outer cylindrical member 24, and on the outer peripheral surface of end cover 66 to prevent compressed fluid from leaking out from gaps between the portion, the outer peripheral surface of end cover 66 and the inner peripheral surface of outer cylindrical member 24. Piston packings 92 such as O-rings are mounted on the outer peripheral surfaces of outer flanges 58 of four members 48A, 48B, 48C, 48D of piston 48 and the outer peripheral surface of end piston 62 to prevent compressed fluid from leaking from gaps between the outer peripheral surface of outer flanges 58 of four members 48A, 48B, 48C, 48D and the inner peripheral surfaces of thin outer peripheral portions 52 of four members 50A, 50B, 50C, 50D of cylinder 50, on which the outer flanges 58 of four members 48A, 48B, 48C, 48D are slidably contacted, and between the outer peripheral surface of end pistons 62 and the end of the inner peripheral surface of housing block 36, the end being located nearer to outer cylindrical member 24.
Exhaust groove 94 is formed on the side surface of outer flange 58 of each of second to fourth members 48B, 48C, 48D of piston 48, the side surface being located nearer to the inner cylindrical member 42 so as to extend from the radially outward position than the outer peripheral surface of inner cylindrical periphery 56 to the inner peripheral surface of inner cylindrical peripheral portion 56. Exhaust groove 96 is formed on the side surface of end piston 62, the side surface being located nearer to inner cylindrical member 42, so as to extend from the radially outward position than the outer peripheral surface of inner cylindrical peripheral portion 56 of fourth member 84D of piston 48 to the side surface of boss 64, the side surface being located nearer to inner cylindrical member 42. Exhaust grooves 94, 96 exhaust air from gaps (see the upper half portion in FIG. 2) between inner cylindrical member side faces of outer flanges 58 of second to fourth members 48B, 48C, 48D of piston 48 and the side faces of end cover sides of inner flanges 54 of first to third members 50A, 50B, 50C, of cylinder 50, and between inner cylindrical member side face of end piston 62 and side face of end cover side of inner flange 54 of fourth member 50D of cylinder 50 when piston 48 is moved, together with end piston 62, by compressed fluid supplied from compressed fluid supplying means to project inner cylindrical member 42 and shaft 22 from outer cylindrical member 24 against the urging force of compression coil spring 70. Therefore, the movement of piston 48 as described above is not prevented. On the contrary, when the supply of the compressed fluid from compressed fluid supplying means is stopped to move piston 48 and end piston 62 to draw shaft 22, together with inner cylindrical member 42, into outer cylindrical member 24 by the urging force of compression coil spring 70, exhaust grooves 94, 96 allow the air to flow into the above-mentioned gaps not to disturb the above-described movement of the piston 48.
When the workpiece is clamped between a pair of clamping plates 12 and 14 by clamping plate driving means 16 composed as described above, the workpiece is first placed between the clamping plates 12 and 14 on the upper surface of Sub base member 20, outer cylindrical member 24 is then rotated to project shaft 22 from outer cylindrical member 24 so that the clamping plates 12 and 14 approaches to each other, thereby lightly contacting the clamping plates 12 and 14 with the work piece. Thereafter, the outer cylindrical member 24 is not necessarily further rotated to increase the clamping force of the workpiece by the clamping plates 12, 14.
Then, pressure regulating unit 26 is operated to introduce pressurized fluid from pressurized fluid supplying means 28 into the bore of outer cylindrical member 24. As a result, the pressure of the pressurized fluid loaded to piston 48 is transmitted through inner cylindrical member 42, and shaft 22 to second clamping plate 24 to thereby increase the clamping force.
To release the clamping of the workpiece by the clamping plates 12, 14, pressure regulating unit 26 is operated to stop the introduction of the pressurized fluid into the bore of outer cylindrical member from pressurized fluid supplying means 28 and to communicate the bore of outer cylindrical member 24 with the atmosphere. Thus, the above-mentioned clamping force applied to the workpiece by the clamping plates 12, 14 is released. Thus, since the clamping plates 12, 14 lightly contact the workpiece, the workpiece can be readily removed from between the clamping plates 12 and 14. Outer cylindrical member 24 may be rotated to draw shaft 22 into outer cylindrical member 24 to move the clamping plates 12 and 14 far away one another, as required.
According to the above-mentioned clamping plate driving means 16, the workpiece can be clamped by a pair of clamping plates 12 and 14 always with a predetermined clamping force irrespective of the magnitude of the clamping torque applied to outer cylindrical member 24. Further, since the clamping force is a total of pressures loaded from the compressed fluid to the end face of end piston 62 at end cover side and outer flanges 58 of four members 48A, 48B, 48C, 48C of piston 48, it is much stronger than the clamping force only generated by the clamping torque of outer cylindrical member 24.
Even if a gap or gaps is produced between the workpiece placed on sub base member 20 and first clamping plate 12 and/or second clamping plate 14, the workpiece can be clamped by a pair of clamping plates 12, 14 always with a predetermined clamping force if the total of the distance of the gap or gaps is slightly shorter than the range of the maximum relative moving distance S of piston 48 to outer cylindrical member 24 and cylinder 50 shown in FIG. 2.
FIG. 4 is a longitudinal sectional view of pressure regulating unit 26.
Pressure regulating unit 26 has joint member 98 hermetically threaded with connecting hole 72 of end cover 66 of clamping plate driving means 16. Stepped cylindrical front case 100 is fitted over the stepped outer peripheral surface of joint member 98, and stepped cylindrical rear case 102 is threadably engaged with the inner peripheral surface of front case 100 to integrally connect front case 100.
Fluid passage 104 substantially extended in a direction along the longitudinal center line of clamping plate driving means 16 is formed on joint member 98, and passage 104 is opened at its one end within outer cylindrical member 24 at the portion threaded to connecting hole 72 of end cover 66 of clamping plate driving means 15, and opened at its other end with the other end face of joint member 98, the other end face being located far away from end cover 66. Passage 104 is bent to extend radially between one end and the other end thereof and conical valve seat 106 opened toward the one end is formed at the radially extending portion of passage 104. A spherical valve body 107 is seated on valve seat 106. A through hole is formed on a portion of the inner surface of passage 104 opposed to valve seat 106 and is extended to the outer peripheral surface of joint member 98. A cylindrical bush 108 with bottom wall is fitted in the through hole in the state that the bottom wall is disposed radially outward. An opening is formed at the bottom wall of bush 108, and rod-like slider 110 is radially slidably inserted into the opening. Slider 110 has outer flange 112 opposed to radially inner end face of the bottom wall of bush 108, and compression coil spring 114 is disposed between outer flange 112 and valve body 107 so as to contact at its both ends outer flange 112 and valve body 107. ring 116 is mounted adjacent to the bottom wall side of bush 108 of outer flange 112 on the outer peripheral surface of slider 110, 0-ring 116 is pressed onto the radially inner end face of the bottom wall of bush 108 by the urging force of coil spring 114, and valve body 107 is pressed on valve seat 106. Cushion member 118 is fixed to the inner end face of slider 110 disposed radially outward of valve body 107.
Groove cam 120 extended circumferentially is formed at the position opposed to the bottom wall of bush 108 on the inner peripheral surface of front case 100, and the radially outer end of slider 110 projected from the outer peripheral surface of joint member 98 is inserted into groove cam 120 to contact the bottom surface of groove cam 120. The bottom surface of groove cam 120 is a cam surface formed of a part of an circle being eccentric to the longitudinal center line of front case 100 and is formed with an exhaust hole 122, as shown in detail in FIG. 5, extended to the outer peripheral surface of front case 110.
In FIG. 4, slider 110 is disposed at the deepest position of the bottom surface of groove cam 120. Cushion member 118 of the inner end face of slider 110 is separated radially outward from valve body 107, and O-ring 116 pressed to the radially inner end face of the bottom wall of bush 108 shuts off the flow of fluid in exhaust hole 122. When the pressurized fluid is supplied from pressurized fluid supplying means 28 to the opening of passage 104 at the rear case side, valve body 107 is separated from valve seat 106 against the urging force of coil spring 114 by the pressure of the pressurized fluid to allow the pressurized fluid to flow from valve seat 106 toward the end of clamping plate driving means. Separation of valve body 107 from valve seat 106 increases the force of coil spring 114 for pressing O-ring 116 toward the radially inner end face of the bot tom wall of bush 108, thereby reliably preventing the pressurized fluid from leading out from passage 104 into the atmosphere via the through hole of the bottom wall of bush 108 and exhaust hole 122.
When front case 100 is rotated around joint member 98 until the outer projecting end of slider 110 is disposed at the most shallow position of the bottom surface of groove cam 120, slider 110 moves radially inward against the pressure of the pressurized fluid loaded to valve body 107 and the urging force compression coil spring 70 to contact cushion member 118 with valve body 107 to press valve body 107 on valve seat 106. Thus, the flow of the pressurized fluid from pressurized fluid supplying means 28 is shut off at valve seat 106 and the pressurized fluid in outer cylinder 24 of clamping plate driving means 16 is exhausted via the through hole of the bottom wall of bush 108 and exhaust hole 122 into the atmosphere so that the pressure in outer cylinder 24 becomes the same as the atmospheric pressure.
An arcuate groove 124 extended circumferentially is formed, as shown in detail in FIG. 5, on the radially extended area of the inner surface of front case 100, and locking recesses 126, 128 are formed at both ends of the bottom surface of the groove 124 in the circumferential direction. A locking ball containing hole 130 is formed at the positions opposite to the groove 124 of front case 100 on the radially extended area of the outer surface of joint member 98, and locking ball 132 and compression coil spring 134 for externally urging locking ball 132 are contained in locking ball containing hole 130. When front case 100 is relatively rotated to joint member 98, locking ball 132 is slidably contacted with the bottom surface of groove 124, and when locking ball 132 contact either one of the end faces of groove 124 in the circumferential direction, ball 132 is seated in either one of recesses 126, 128. When locking ball 132 of joint member 98 is seated in one recess 126 of groove 124 of front case 100, the outward projecting end of slider 110 is disposed at the most shallow position of the bottom surface of cam 120 so that the pressure in outer cylinder 24 becomes the same as the atmospheric pressure. When the locking ball 132 is seated in the other recess 128, the outward projecting end of slider 110 is disposed at the deepest position of the bottom surface of cam 120 to supplying the pressurized fluid from pressurized fluid supplying means 28 into outer cylinder 24 as described above.
As shown in FIG. 4, nipple member 136 is hermetically threadably engaged in the rear end face of rear case 102. Connecting hole 140 opened with the outer end face and valve body containing hole 142 opened with the inner end face and connected with connecting hole 140 are formed at nipple member 136, and the end of pressurized fluid supplying hose 138 from pressurized fluid supplying means 28 is hermetically threadably engaged in connecting hole 140. Cap 144 for covering the inner end face of nipple member 136 is threadably engaged with the outer peripheral surface of nipple member 136 in the area of the bore of rear case 102, and through hole 146 opened with hole 142 is formed at cap 144. Cylindrical cup-shaped valve body 148 is contained in hole 142, and pressing pin 150 formed on the bottom wall of valve body 148 is inserted into through hole 146 of cap 144 to project from through hole 146 into the bore of rear case 102. A plurality of radial ribs 152, 154 extended in a direction along the longitudinal center line are formed on the inner peripheral surfaces of hole 142 and through hole 146 so as to project in the radially inward direction, and the projecting end faces of ribs 152, 154 are contacted with the outer peripheral surfaces of valve body 148 and pressing pi 150 to allow valve body 148 and pin 150 to slide in the axial direction of the pin 150. Annular packing 156 is mounted adjacent to the bottom wall of valve body 148 on the outer peripheral surface of pin 150, and valve body 148 is urged by compression coil spring 158 contained in hole 142 toward through hole 146. Packing 156 of urged valve body 148 is contacted with the peripheral area of the through hole of the bottom wall of cap 144 to close through hole 146. Thus, the peripheral area of the through hole of the bottom wall of cap 144 functions as valve seat 160 for valve body 148.
Through hole 146 communicates through the bore of rear case 102 with fluid passage 104 of joint member 98 and constructs together with fluid passage 104 and valve body containing hole 142, a fluid passage for introducing the pressurized fluid supplied from pressurized fluid supplying means 28 to connecting hole 140 to the end of end case side of fluid passage 104 in the body of pressure regulating unit 26, the body being constructed by joint member 98, front case 100, rear case 102 and nipple member 136.
Cylindrical cup-shaped actuator member 164 is slidably fitted over O-ring 162 mounted on the outer peripheral surface of cap 144 in the bore of rear case 102, and boss 166 projected into the opening of fluid passage 104 of joint member 98 at rear case side is formed at the bottom wall of actuator member 164. O-ring 168 slidably contacted with the outer peripheral surface of boss 166 is mounted on the inner peripheral surface of the opening of fluid passage 104 at rear case side. The projecting end of pin 150 of valve body 148 is contacted with the end face of the bottom wall of actuator member 164 at cap side, and a plurality of through holes 170 are formed on the cap side end face of the bottom wall of boss 166 around the contacting position of pin 150 so as to extend in boss 166.
Spring retainer ring 172 slidably fitted on the inner peripheral surface of rear case 102 is contained in the bore of rear case 102. The inner diameter of ring 172 is larger than the outer diameter of the peripheral wall of actuator member 164 and ring 172 is disposed adjacent to joint member 98.
Compression coil spring 174 is wound on the outer peripheral surface of actuator member 164. One end of spring 174 is abutted against outer flange formed at the end of the outer peripheral surface of actuator member 164 at nipple member side, and the other end is contacted with ring 172.
Annular guide groove 178 is formed adjacent to threaded part 176 to be threadably engaged with front case 100 on the outer peripheral surface of rear case 102, and a pair of guide cutouts 180, 182 are formed at two positions disposed diametrically on the outer peripheral wall of rear case 102. Each of guide cutouts 180, 182 in extended along the longitudinal center line from one end face located near to threaded part 176 to the other end face located far away from threaded part 176. A pair of outer projections 184, 186 formed on the outer peripheral surface of ring 172 are inserted into a pair of guide cutouts 180, 182 so as to be slidable in a direction along the longitudinal center line, and an indicator needle 186 projected in a direction along the longitudinal center line is fixed to the end face of one projection 184, the end face being located far away from threaded part 176. Needle 186 is inserted into longitudinal hole 188 formed on the end face of guide groove 178, the end face being located far away from threaded part 176, and hole 188 is extended to scale showing recess 190 formed at a position located far away from threaded part 176 than guide groove 178 on the outer peripheral surface of rear case 102.
The outer end faces of a pair of outer projections 184, 186 of spring retainer ring 172 are constructed by parts of a circle being concentrically with ring 172, and a threaded part 192 made of part of the same threads as those formed on threaded part 176 is formed on the outer end faces of the projections.
Regulating ring 30 is mounted on guide groove 17 of the outer peripheral surface of rear case 102 so that ring 30 is rotatably in the circumferential direction of rear case 102, and threaded part 194 formed on the inner surface of ring 30 are threadably engaged with threaded parts 192 on the outer end faces of a pair of outer projections 184, 186 of ring 172.
When spring retainer ring 172 is disposed adjacent to the inner end face of joint member 98 as shown in FIG. 4 in pressure regulating unit 26 constructed as described above, the urging force of compression coil spring 174 is smaller than that of compression coil spring 158 of valve body 107. Thus, valve body 148 is disposed at the closed position where packing 56 is placed on valve seat 160 of cap 144 as shown in FIG. 4 by the urging force of coil spring 158, and valve body 148 disposed at the closed position makes actuator member 164 dispose at the first position where actuator member 164 is approached to joint member 98 than cap 144 as shown in FIG. 4 by pressing pin 150. At this time, even if the pressurized fluid from pressurized fluid supplying means 28 is supplied into the fluid passage of pressure regulating unit 26 through connecting hole 140, the pressure of the pressurized fluid acts on valve body 148 to press the packing 156 on valve seat 160. Therefore, the pressurized fluid cannot pass valve seat 160, and the fluid cannot arrive at the bore of outer cylindrical member 24 of clamping plate driving means 16. In other words, pressing force by the pressure of pressurized fluid is not acted on second clamping plate 14.
In order to act pressing force by the pressure of the pressurized fluid on second clamping plate 14, regulating ring 30 is so rotated as to move spring retainer ring 172 in a direction that ring 172 moves away from joint member 98. Thus, compression coil spring 174 is compressed between ring 172 and the outer flange of actuator member 164, and the increased urging force of spring 174 moves actuator member 164 against the urging force of spring 158 of valve body 107 in a direction that actuator member 164 approaches nipple member 136. The movement of actuator 164 transmitted through pin 150 to valve body 170 moves valve body 107 away from cap 144, thereby valve body 107 is disposed at open position where packing 156 is separated from valve seat 160. The position of actuator member 164 at this time is the second position of actuato member 164.
The pressurized fluid supplied from pressurized fluid supplying means 28 to connecting hole 140 of pressure regulating unit 26 is fed, through valve body containing hole 142 of nipple member 136, gap between packing 156 of valve body 107 and valve seat 160, pressing pin insertion hole of cap 144, and through hole 170 of actuator member 164, into fluid passage 104 of joint member 98. The pressurized fluid fed into passage 104 separates valve body 107 from valve seat 106 against the urging force of coil spring 144 and is flowed into the bore of outer cylindrical member 24 of clamping plate driving means 16, if front case 100 is so located at its peripheral position where the radially outer end of slider 110 is disposed in the deepest portion of cam 120 of front case 100.
When the radially outer end of slider 110 is disposed in the deepest portion of cam 120 of front case 100, an increase in the urging force of spring 144 generated by the separation of valve body 107 from valve seat 106 increases the abutting pressure of O-ring 116 of valve body 107 on bush 108. Thus, the pressurized fluid from fluid passage 104 is surely prevented from discharging into the atmosphere through the slider insertion hole of bush 108 of front case 100 and exhaust hole 122.
The pressurized fluid fed into the bore of outer cylindrical member 24 of clamping plate driving means 16 acts on end piston 62 of clamping plate driving means 16 and piston 48 constructed by first to fourth members 48A, 48B, 48C, 48D as described above in the description of the above-mentioned clamping plate driving means 16 with reference to FIGS. 2 and 3, and the pressing force increased by end piston 62 and piston 48 is transmitted through leadscrew shaft 22 to second clamping plate 14.
When the total of pressures loaded from the pressurized fluid to the side face of nipple member side of actuator 164 becomes larger than the urging of coil spring 174 in the pressure regulating unit 26 constructed as described above, actuator member 164 moves farther from the end face of nipple member 136 at the actuator member side against the urging of coil spring 174 to move to the first position where it approaches joint member 98 as shown in FIG. 4. Thus, valve body 148 is returned to the closed position shown in FIG. 4 by the pressure of the pressurized fluid and the urging force of coil spring 158 to shut off the supply of the pressurized fluid from pressurized fluid supplying means 28 into the bore of outer cylindrical member 24 of clamping plate driving means 16. Here, the pressurized fluid in the bore of oute cylindrical member 24 of clamping plate driving means 16 urges valve body 107 in fluid passage 104 of joint member 98 to the closed position on valve seat 106 to prevent the pressurized fluid from flowing out from the bore of outer cylindrical member 24 of driving means 16. Therefore, even after the supply of the pressurized fluid is shut off, the pressing force transmitted by the leadscrew shaft 22 of driving means 16 to second clamping plate 14 is the same as that before shutting off the supply of the pressurized fluid.
When front case 100 is disposed at the circumferential position where the radially outer end of slider 110 is disposed in the most shallow portion of cam 120 of front case 100, slider 110 moves radially inward against the urging force of coil spring 114 to separate O-ring 116 from the bottom wall of bush 108. Thus, the pressurized fluid in the bore of outer cylindrical member 24 of driving means 16 is exhausted into the atmosphere through the slider insertion hole of bush 108 and exhaust hole 122 of front case 100 to eliminate the pressing force caused by the pressure of the pressurized fluid in the bore of outer cylindrical member 24 transmitted through leadscrew shaft 22 to second clamping plate 14.
The magnitude of the pressing force transmitted through shaft 22 to second clamping plate 14 by driving means 16 by utilizing the pressurized fluid supplied into the bore of outer cylinder 24 is proportional to the magnitude of the pressure of the pressurized fluid supplied into outer cylindrical member 24. The magnitude of the pressure of the pressurized fluid supplied into the bore of outer cylindrical member 24 is proportional to the magnitude of the pressurized fluid when actuator member 164 is moved to the first position against the urging force of coil spring 174 to thereby return valve body 148 to its closed position. In other words, the magnitude of pressing force loaded by driving means 16 to second clamping plate 14 by utilizing the pressurized fluid is proportional to the magnitude of the urging force of coil spring 174, and the increase and decrease in the urging force of coil spring 174 causes the increases or decreases in the magnitude of the pressing force at the second clamping plate 14. The increase or decrease in the urging force of coil spring 174 in caused by the relative movement of retainer ring 172 in the bore of rear case 102, and such movement of ring 172 is caused by the rotation of regulating ring 30 on the outer peripheral surface of rear case 102.
As described above, it is understood that the magnitude of the urging force of spring 174 is regulated by regulating ring 30 and retainer ring 172 combined with ring 30. Regulating ring 30 and retainer ring 172 construct urging force regulating means for regulating the magnitude of the urging force of spring 174.
Scale plate 196 which indicates the magnitude of the pressing force generated at second clamping plate 14 proportional to the moving distance of retainer ring 172 is fixed to the bottom surface of scale showing recess 190 on the outer peripheral surface of rear case 102. The scale on scale plate 196 corresponding to the end of indicating needle 186 moving together with retainer ring 172 indicates the magnitude of the pressing force generated at second clamping plate 14 by supplying the pressurized fluid from pressurized fluid supplying means 28 through pressure regulating means 26 to clamping plate driving means 16.
Indicating needle 186 is preferably colored with remarkable color to understand the magnitude of the pressing force indicated by the end of needle 186 at a glance when observing scale plate 196.
In the embodiment described above, pressure regulating unit 26 is cylindrical on the outer appearance, and does not have a projection projected radially outward. Further, pressure regulating unit 26 is connected concentrically linearly to clamping plate driving means 16 similarly having cylindrical shape in the outer appearance. Therefore, pressure regulating unit 26 can be integrally handled with driving means 16, and even if driving means 16 is directed in any direction on base frame 10, regulating ring 30 can be readily operated.
In the embodiment described above, pressure regulating unit 26 has indicating needle 186 for indicating the magnitude of the pressing force loaded on second clamping plate 14 proportionally to the rotation of ring 30, needle 186 moving on scale plate 195 in the longitudinal direction of pressure regulating unit 26 by the rotation of ring 30. The combination of indicating needle 186 and scale plate 196 is easier in observing the scale than the cases that a reference line is formed on the outer peripheral surface of ring 30 and the same content of scale of scale plate 196 of the embodiment is forme on the scale on the outer peripheral surface of front case 100 or rear case 102, or that the same content of the scale of scale plate 196 of the embodiment is, on the contrary, formed on the outer peripheral surface of ring 30 and the reference line is formed on the outer peripheral surface of front case 100 or rear case 102, because a plurality of revolutions of ring 30 is needed to move needle 186 in a range of scale of scale plate 196 of the above embodiment. In the embodiment described above, the above-mentioned combination is only one. However, when combinations are provided on the outer peripheral surface of rear case 102 at every approx. 120.degree. in the circumferential direction, the reading of the scale can be further ready irrespective of the position of driving means 16 on base frame 10.
FIG. 7 schematically shows a longitudinal sectional view of fixing unit 32.
As shown in FIG. 7, engaging groove 200 of substantially T shape in cross-section is formed on the back surface of sub base member 20, and groove 200 is extended in the longitudinal direction of sub bas member 20.
Through holes 202 having relatively large diameter is formed at the center of upper wall of base frame 10 so as to oppose to the back surface of sub base member 20, and a disc-like casing 204 is disposed on the back surface of the upper wall of base frame 10 so as to oppose to hole 202.
Casing 204 is composed of upper and lower case members 208, 210 connected with one another in the state that diaphragm 206 is clamped by case members 208, 210. Annular groove 212 is formed on the inner side surface of lower case member 210 to which diaphragm 206 is contacted with, and a connecting hole 216 is formed in annular groove 212. The end of pressurized fluid supplying hose 214 further extended from pressurized fluid supplying means 28 shown in FIG. 1 on which the abovementioned switching valve 34 is disposed is hermetically and threadably engaged with hole 216. Stepped storage recess 218 is formed on the inner side face of upper case member 208 contacted with diaphragm 206 so as to be concentric with upper case member 208. A through hole is formed at the center of the bottom wall of storage recess 218, and engaging rod 220 for engaging with engaging groove 200 of sub base member 20 of clamping unit 18 is inserted into the through hole so as to be slidable in a direction along the longitudinal center line thereof. Rod 220 has a disc-like pressure receiving portion 222 contained in a large-diameter area of recess 218 so as to be movable in a direction along the longitudinal center line, and boss 224 extended in a direction along longitudinal center line is formed on the upper end face of rod 220. The central hole of engaging plate 226, having substantially T shape cross section and rectangular plane shape and disposed in groove 200 of sub base member 20, is fitted over boss 224. Lower surfaces 228 of both ends of laterally extending portion of engaging plate 226 are engaged with upper surfaces 230 of both shoulder portions of groove 200 of sub base member 20 in a direction along the longitudinal center line. Stop ring 232 for preventing engaging plate 226 from dropping out from boss 224 is fixed by bolts to the upper end face of boss 224, and conical spring 234 for eliminating the fluctuation of engaging plate 226 on boss 224 is mounted on the lower surface of stop ring 232. Paired conical spring 236 is mounted on rod 220 in a small-diameter area of recess 218, and paired conical spring 236 is contacted at both ends with the bottom surface of small-diameter area of recess 218 and the upper surface of pressure receiving portion 222 so as to urge rod 220 in a direction that rod 220 moves away from sub base member 20 of clamping unit 18, i.e., in downward direction. That urging force strengthens the engagement of engaging plate 226 of rod 220 with groove 200 of sub base member 20. At this time, the pressure retaining portion 222 of rod 220 is lightly contacted with diaphragm 206.
Pin 238 is planted on the bottom surface of a large-diameter area of recess 218 so as to project in a direction along the longitudinal center line, and pin 238 is inserted into through hole 240 formed at pressure receiving portion 222 of rod 220. Pin 238 prevents rod 220 from relatively rotating to casing 204.
In fixing unit 32 constructed as described above, when the pressurized fluid is not supplied into groove 212 through pressurized fluid supplying hose 214 from pressurized fluid supplying means 28, engaging plate 226 of rod 220 is rigidly engaged with groove 200 of sub base member 20 by the urging force of paired conical spring 236 as described above. Therefore, sub base member 20 rigidly clamps base frame 10 in cooperation with upper case member 208 of casing 204 of fixing unit 32, so that clamping unit 18 having base member 20 is rigidly fixed on base frame 10.
In fixing unit 32 constructed as described above, when the pressurized fluid is supplied from pressurized fluid supplying means 28 through pressurized fluid supplying hose 214 into groove 212, the total of the pressure of the pressurized fluid loaded to diaphragm 206 becomes larger than the urging force of paired conical spring 236, so that rod 220 move in a direction for approaching rod 220 to sub base member 20 of clamping unit 18 to release the engagement of plate 226 with groove 200 of sub base member 20, i.e., in the upward direction. As a result, clamping unit 18 having sub base member 20 can freely move on base frame 10, in the state that clamping unit 18 is connected with fixing unit 204 by rod 220, and can freely rotate on base frame 10. However, the range that clamping unit 18 can freely move on base frame 10 is defined by a range that rod 220 can move in through hole 202 of base frame 10.
After clamping unit 18 is disposed at a desired position on base frame 10, the supply of the pressurized fluid from pressurized fluid supplying means 28 into the groove 212 of fixing unit 32 is shut off by switching valve 34 on pressurized fluid supplying pipe 214, and groove 212 is communicated with the atmosphere. Thus, the pressure of the pressurized fluid in groove 212 becomes the same as the atmosphere, rod 220 is moved in a direction for rigidly engaging plate 226 with groove 220 of sub base member 20 by the urging force of paired conical springs 236, i.e., in the downward direction, and clamping unit 18 is again rigidly fixed on base frame 10.
Even if the clamping apparatus according to the embodiment of the present invention and using fixing unit 32 constructed as described above is used in a machine tool such as a small-sized drilling machine which cannot move the position of cutting tool on the bed in back and forth, and lateral directions, the clamping apparatus can rigidly fix clamping unit 18 having a pair of clamping plates 12, 14 at the arbitrary position on a bed after base frame 10 is once fixed rigidly on bed of the machine tool. Therefore, whenever a workpiece is attached to or detached from between a pair of clamping plates 12 and 14 and working position of workpiece is changed, complicated releasing work and refixing work of base frame 10 to bed are not necessary. Therefore, the working efficiency of workpiece in the machine tool can be much improved as compared with the conventional machine tool.
Since clamping unit 18 on base frame 10 can be rigidly fixed by the urging force of paired conical spring 236 in fixing unit 32 constructed as described above, the release of workpiece during working can be reliably prevented.
The embodiment described above has been described for the present invention. The present invention is not limited to the particular embodiment described above. Various other changes and modifications may be made within the spirit and scope of the present invention.
For example, the number of members for constructing piston 46 and cylinder 50 in clamping plate driving means 16 may be freely set as required in the magnitude of the pressing force which must be generated by utilizing the compressed fluid in clamping plate driving means 16.
Further, oil may be used as the compressed fluid.
Claims
What is claimed is:
1. A clamping apparatus having a base frame, a pair of clamping plates provided on the base frame so as to approach or move away from one another, and clamping plate driving means for driving the pair of clamping plates, further comprising: a clamping unit having the pair of clamping plates and clamping plate driving means; and a fixing unit coupled to the clamping unit for fixing the clamping unit to an arbitrary position on the base frame; said clamping unit having a sub base member to which one clamping plate and the clamping plate driving means are fixed, the other clamping plate is driven by the clamping plate driving means to approach or move away form the one clamping plate; said clamping plate driving means having: a leadscrew shaft fixed at its one end to the other clamping plate; an outer cylindrical member provided at the sub base member so as to be located concentrically with the leadscrew shaft and to be rotatable to the sub base member and having means for connecting the bore thereof to pressurized fluid supplying means; an inner cylindrical member disposed in the bore of the outer cylindrical member so as to be rotatable integrally with the outer cylindrical member in the circumferential direction of the outer cylindrical member and to be slidable relative to the outer cylindrical member in a direction along the longitudinal center line of the outer cylindrical member, and threadably fitted over the leadscrew shaft; and a piston disposed in the bore of the outer cylindrical member so as to be slidable relative to the outer cylindrical member in a direction along the longitudinal center line of the outer cylindrical member, the piston being slid in the bore of the outer cylindrical member by the pressure of the fluid supplied from the pressurized fluid supplying means into the bore of the outer cylindrical member so that the piston drives the inner cylindrical member to project the leadscrew shaft from the outer cylindrical member; said base frame being provided with a through hole at its position opposing to the sub base member; said fixing unit having: a casing disposed on the surface area of the base frame, which is opposite to the surface area disposed thereon with the clamping unit so as to face the through hole, and having means for connecting the bore thereof to the pressurized fluid supplying means; an engaging rod disposed in the casing so as to be movable in a direction along the center line of the through hole in the casing, and extended from the casing into the through hole to be engaged with the sub base member of the clamping unit in a direction that the sub base member approaches the base frame; urging means disposed in the casing for urging the engaging rod in a direction for engaging the engaging rod with the sub base member of the clamping unit; and a diaphragm member disposed in the casing so as to press the engaging rod against the urging force of the urging means in a direction for releasing the engagement of the sub base member of the clamping unit with the engaging rod by the pressure of the fluid supplied from the pressurized fluid supplying means into the casing.
2. A clamping apparatus according to claim 1, wherein said clamping plate driving means comprises a pressure regulating unit for controlling the magnitude of the pressure supplied from the pressurized fluid supplying means to the bore of the outer cylindrical member.
3. A clamping apparatus according to claim 2, wherein said pressure regulating unit comprises a body connected to the outer cylindrical member, and having a fluid passage to be connected to the pressurized fluid supplying means connecting means of the outer cylindrical member and means for connecting the fluid passage to the pressurized fluid supplying means; a valve seat formed in the fluid passage; a valve body disposed in the fluid passage so as to be movable between the closed position, where the valve body is seated on the valve seat, and the open position, where the valve body is separated from the valve seat; an actuator member being movable between the first position and the second position in the fluid passage, the actuator member allowing the valve body to be disposed at its closed position at the first position, driving the valve body to the open position by the movement from the first position to the second position, and being urged to the first position by the pressure of the pressurized fluid in the fluid passage; urging means provided in the body so as to urge the actuator member to the second position against the pressure of the pressurized fluid in the fluid passage, and urging force regulating means provided on the body so as to be exposed on the outer surface of the body, and regulating the urging force generated from the urging means.