JPS6341711B2 - - Google Patents

Description

[Detailed Description of the Invention] (Technical Field) The present invention relates to a vise device for clamping a work (clamped article) between a fixed jaw and a movable jaw, and in particular to a vise device that firmly clamps a work using hydraulic pressure. The present invention relates to a hydraulic vise device that can be used as a normal mechanical vise device if necessary.

(Background Art) Conventionally, in a general vise device, when a spindle is rotated by operating a handle, the movable jaw is directed toward the fixed jaw by the action of a screw mechanism provided between the spindle and the movable jaw. In the past, it was moved forward (approximately), and a predetermined article (work) was then sandwiched between the movable jaw and the fixed jaw.

By the way, when a large load is applied to the clamped workpiece when performing a predetermined work, depending on the content of the work,
It becomes necessary to increase the clamping force against the workpiece. However, in the above-mentioned conventional device in which the workpiece is tightened via a screw mechanism provided between the spindle and the movable jaw, a large operating force is required to tighten the workpiece, and the tightening operation is difficult. It has become hard labor. Moreover, with this device, it is not possible to check whether the workpiece has been clamped with sufficient clamping force, so work may be carried out with insufficient clamping force. . In such a case, troubles such as the workpiece falling off during work are likely to occur, and especially when precision machining is applied to the workpiece, such falling off of the workpiece may cause damage to the workpiece. This also causes problems such as deterioration of pressurization accuracy.

For this reason, in recent years, in order to obtain sufficient clamping force, hydraulic vise devices have been developed that clamp the workpiece based on hydraulic pressure. However, this hydraulic vise device uses a boosting mechanism that boosts the applied operating force based on the action of hydraulic pressure, so although it can obtain a large clamping force, it does not reduce the movement stroke of the movable jaw. A problem arises in that it is difficult to make it sufficiently large.

In addition, such hydraulic vise devices include pumps, etc.
A predetermined hydraulic pressure is generated from an external hydraulic pressure source, and this hydraulic pressure is guided into the equipment through piping such as hoses, which inevitably increases costs, as well as the cost of those piping. This impedes the work and worsens work efficiency.Also, since there are many piping connections, liquid leakage occurs at these connections, causing a sudden decrease in clamping force, which causes the workpiece to be removed from the equipment. There was also a risk that it would fall off.

Furthermore, in conventional hydraulic vise devices, the clamping force for clamping the workpiece was generated based only on the action of hydraulic pressure, so in the event of a liquid leak, the clamping force is generated. There was also the problem that it became impossible to use it as a vise device.

(Problem to be Solved) The present invention was made against the background of the above, and its purpose is to be able to generate a large clamping force and to take a large movement stroke of the movable jaw. It satisfies two conflicting demands at the same time, has good workability, is hard to cause liquid leakage, and can be used as needed even in the event of liquid leakage or even when no liquid leakage occurs. It is an object of the present invention to provide a hydraulic vise device that can be used as a normal mechanical vise device.

(Solution Means) In order to achieve this object, the hydraulic vise device according to the present invention includes a fixed jaw and a movable jaw that is movable forward and backward toward the fixed jaw, as described above. and a spindle which is provided parallel to the moving direction of the movable jaw and is screwed to the movable jaw for moving the movable jaw forward and backward toward the fixed jaw, and the spindle screws the movable jaw toward the fixed jaw. In a vice device that clamps a predetermined article between the movable jaw and the fixed jaw by moving the jaw forward toward the fixed jaw, a coupling mechanism provided rotatably and immovably relative to the fixed jaw in the axial direction of the spindle, and connected to the spindle in a relatively immovable manner and movable relative to the axial direction;
(b) A rotary operating force is applied to the connecting mechanism, which is concentrically connected to the connecting mechanism via a screw mechanism and is movable relative to the connecting mechanism in the axial direction by relative rotation with respect to the connecting mechanism. (c) a rotating shaft that is fitted to the rotating shaft in a state that is rotatable relative to the rotating shaft and movable relative to the rotating shaft in the axial direction, and that is not rotatable relative to the coupling mechanism; a transmission member connected to the coupling mechanism in a state of being relatively movable in a direction, and a spring means for biasing the transmission member in the forward movement direction of the movable jaw; Consisting of a cam protrusion provided on one side and a cam surface provided on the other side, when the rotational load on the transmission member is small, the rotation shaft is rotated based on the engagement between the cam protrusion and the cam surface. While preventing the transmission member from rotating relative to the member, in a state where the rotational load of the transmission member is larger than a certain level, the transmission member is moved by the spring means by the cam action of the cam projections and the cam surface. a clutch means equipped with a cam mechanism that is moved backward against the urging force of the clutch member to release the engagement between the cam protrusions and the cam surface, and to allow the rotating shaft to rotate relative to the transmission member; and (d) a lock provided on the coupling mechanism so as to be movable between a position that prevents the transmission member from moving in the backward direction due to the cam action and a position that allows the transmission member to move in the backward direction. (e) a hydraulic pressure chamber formed in a sealed state in the coupling mechanism, and a pressurizing surface facing the hydraulic pressure chamber, and the rotating shaft is connected to the coupling mechanism by the action of the screw mechanism. a first piston that moves together with the rotating shaft to advance the pressurizing surface toward the hydraulic pressure chamber; and a pressure receiving surface that faces the hydraulic chamber and has a larger area than the pressurizing surface. and a second piston that is moved in the forward direction of the movable jaw based on the hydraulic pressure acting on the pressure receiving surface; (f) the second piston and the spindle; and disc spring means interposed between the movable jaws and a disc spring means for pressing the spindle in the forward direction of the movable jaw based on the forward movement of the second piston.

(Function/Effect) In such a vise device, when the lock member is moved to a position where it prevents the transmission member of the clutch means from moving backward, the cam protrusion of the cam mechanism of the clutch means and the cam surface are in contact with each other. Since it is always held in the engaged state, the operating force of the rotating shaft is always transmitted directly to the coupling mechanism and further to the spindle through the transmission member, and as a result, the movable jaw is always
It is moved by the action of a screw mechanism provided between it and the spindle. In other words, when the locking member is moved to a position that prevents the transmission member from moving backward, the workpiece can be clamped based only on the rotational action of the spindle, similar to a normal mechanical vise device.

On the other hand, when the lock member is moved to a position that allows the transmission member of the clutch means to move backward, the workpiece is not caught between the fixed jaw and the movable jaw, and while the rotational load on the transmission member is still small, Based on the urging force of the spring means that urges the transmission member in the forward direction, the cam protrusion and the cam surface constituting the cam mechanism of the clutch means are held in an engaged state. Therefore, during that time, the operating force of the rotary shaft is directly transmitted to the spindle via the transmission member and eventually the coupling mechanism, and as a result, the movable jaw is
It is moved forward by the action of a screw mechanism between it and the spindle.

However, as a result of the forward movement of the movable jaw, a workpiece is caught between the fixed jaw and the movable jaw, and as a result of the pinching of the work, the rotational load on the transmission member becomes larger than a certain level. The transmission member is moved backward by the cam action between the cam projection and the cam surface, and the engagement between the cam projection and the cam surface is released. Therefore, from then on, the rotating shaft will be rotated relative to the transmission member, that is, the coupling mechanism, and the screw mechanism provided between it and the coupling mechanism will cause the rotating shaft to rotate relative to the coupling mechanism. This will lead to relative progress.

When the rotating shaft is moved forward by the action of the screw mechanism, the first piston is also moved forward, and as a result, the hydraulic pressure in the hydraulic pressure chamber is increased, and the second piston is moved forward. . The forward movement of the second piston causes the disc spring means to be compressed between it and the spindle, and a pressing force acting as a reaction force of the compression force of the disc spring means is applied to the spindle and eventually to the movable jaw. It will be done. Here, since the area of the pressure-receiving surface of the second piston is larger than the area of the pressure-applying surface of the first piston, when force is transmitted via the hydraulic pressure of the hydraulic pressure chamber, the boosting force is increased. As a result, a large clamping force based on hydraulic pressure is generated between the movable jaw and the fixed jaw.

In other words, if the locking member is moved to a position that allows the backward movement of the transmission member and a rotational operating force is applied to the rotating shaft, the work can be clamped with a large clamping force based on hydraulic pressure. The device can be used as a hydraulic vice.

Thus, the hydraulic vise device according to the invention comprises:
By moving the locking member to a position that allows the backward movement of the transmission member, it can be used as a hydraulic vise device, while by moving the locking member to a position that prevents the backward movement of the transmission member, it can be used as a normal vise. It can be used as a mechanical vise device, so even if a leak occurs,
Even if the function as a hydraulic vise device is impaired, simply change the movement position of the locking member.
It can be used as a normal mechanical vise device, and it can be used as a normal mechanical vise device as needed, regardless of the presence or absence of liquid leakage.

In addition, when such a device is used as a hydraulic vise device, as described above, the action of the screw mechanism between the spindle and the movable jaw is limited until the workpiece is caught between the fixed jaw and the movable jaw. The movable jaw is moved by
Only when the movable jaw reaches the position where it clamps the workpiece and a large clamping force is required, the operating force boosted by the boost mechanism is transmitted to the spindle, so the movement of the movable jaw is stopped. A large clamping force can be generated regardless of the stroke, and therefore a large clamping force can be generated while setting a large movement stroke of the movable jaw.

Moreover, in such a device, when used as a hydraulic vise device, switching between the force transmission path via the clutch means and the coupling mechanism and the transmission path via the hydraulic booster mechanism is performed by the transmission member. Since this is automatically done based on the magnitude of the rotational load that is applied, there is no need to worry about the hassle of changing the handle or installing a predetermined switching mechanism and operating that switching mechanism. No work is required.

In addition, since the above-mentioned device does not require piping to introduce hydraulic pressure, these piping may become an obstacle and make work difficult, or fluid may leak from piping connections, resulting in insufficient clamping force. Furthermore, when used as a hydraulic vise device, the force boosted by the boost mechanism is transmitted to the spindle via the disk spring means, so the clamping force is reduced. It is always kept at a stable size, effectively avoiding excessive clamping force being applied to the workpiece, and even in the unlikely event that fluid leaks while clamping the workpiece.
Another advantage is that an immediate drop in clamping force can be avoided.

(Example) In order to further clarify the features of the present invention, examples thereof will be described in detail below based on the drawings.

First, in FIG. 1, reference numeral 10 denotes a main body having a longitudinal shape, on the upper side of which a fixed jaw 12 and a movable jaw 14 are arranged. The fixed jaw 12 is attached to the main body 10 by a bolt 16.
1, and the movable jaw 14 can be moved from side to side in FIG. 1 by means of a moving block 18. A recess 20 is formed inside the movable jaw 14, into which a part of the moving block 18 is inserted. The rear end of the protruded part is brought into contact with a pin 22 screwed into a female screw hole of the movable jaw 14, while the ball part 24 provided at the front part is brought into contact with the inclined wall part 26 of the recess 20. It is housed in a hemispherical hole formed in the. As a result, when the movable jaw 14 clamps and tightens a workpiece between the movable jaw 14 and the fixed jaw 12, a downward pressing force is applied to the inclined wall portion 26 of the movable jaw 14, and the movable jaw 14 14 is prevented from rising from the main body 10.

Further, a female threaded hole 28 is formed in the lower part of the moving block 18 and passes through this in the direction of movement of the movable jaw 14, and a spindle 30 is installed in this female threaded hole 28 so as to be movable in the axial direction. It's embedded. The spindle 30 has a female threaded hole 2 in a male threaded portion formed in its large diameter portion 32.
The rotation of the spindle 30 causes the moving block 18 and the movable jaw 14 to move forward and backward.

A rotating shaft 34 for rotating the spindle 30 or sliding it in the axial direction is arranged behind the spindle 30 (on the right side in FIGS. 1 and 2), and this rotating shaft 34 and the spindle 30
are connected by a connecting mechanism 44 that includes a first cylindrical member 36, a second cylindrical member 38, a sleeve 40, a lock ring 42, and the like.

The first cylindrical member 36 has a bottom portion 46, and both sides of the bottom portion 46 are cylindrical portions 48, 50, and one of the cylindrical portions 48 is rotated into a fitting hole formed in a bearing portion 51 of the main body 10. possible to be mated. An engagement protrusion 52 that protrudes in the axial direction is formed at the end of the cylindrical portion 48.
The first cylindrical member 36 is engaged with the engagement groove 56 formed in the large diameter portion 54 at the rear end of the spring 30, that is, the first cylindrical member 36 rotates integrally with the spindle 30 and does not move relative to the spindle 30 in the axial direction. It is connected to the spindle 30 in the state in which it is obtained. In addition,
The spindle 30 spaced apart from the first cylindrical member 36 in the axial direction is moved to its original position by a disc spring 60 housed inside the spring chamber 58 of the spindle large diameter portion 54.
That is, it is returned to the position where it contacts the end surface of the first cylindrical member 36. The disc spring 60 has one end in contact with the bottom surface of the spring chamber 58 and the other end in contact with the back surface of the head of a bolt 62 screwed into the first cylindrical member 36.
The spindle 30 is urged in the backward direction (rightward in the figure).

The other cylindrical portion 50 of the first cylindrical member 36 has a male threaded portion formed on the outer circumferential side and a female threaded portion formed on the inner circumferential side, and the small diameter threaded portion 64 of the second cylindrical member 38 is screwed into this female threaded portion. A lock ring 42 as a rotation preventing member is attached to this small diameter threaded portion 64.
are screwed together. The lock ring 42 has one end in the axial direction in contact with the first cylindrical member 36 and the second cylindrical member 38, respectively, and presses them in opposite directions, whereby the first cylindrical member 36 and the second cylindrical member 38 are prevented from relative rotation.

On the other hand, a sleeve 40 is screwed onto the external male threaded portion of the cylindrical portion 50, and this sleeve 40 has the following features:
Together with the large-diameter flange portion 65 formed on the first cylindrical member 36, the bearing portion 51 of the main body 10 is sandwiched from both front and rear sides, thereby preventing movement of the first cylindrical member 36 in the axial direction. In addition, 66, 68
is a thrust washer.

A transmission member 70 is disposed between the rear end of the second cylindrical member 38 and the rotation shaft 34, and the operating force applied to the rotation shaft 34 is transmitted through the transmission member 70. The signal is transmitted to the second cylindrical member 38. The transmission member 70 is a cylindrical member having a small-diameter fitting portion 72 that is fitted into the second cylindrical member 38 and a large-diameter engagement portion 74, and its inner peripheral surface is connected to the rotating shaft 34. They are fitted so that they can move relative to each other in the axial and circumferential directions. Engagement part 7
4 has an engagement groove 76 extending in the axial direction, and a part of the front side (left side in the figure) of this engagement groove 76 is connected to the fifth As shown in the figure, the projection 78 (see FIGS. 3 and 4) formed at the rear end of the second cylindrical member 38 is engaged with the transmission member 70 and the second cylindrical member 38. The member 38 can be rotated integrally with the member 38. The engagement between the engagement groove 76 and the protrusion 78 is as follows.
The transmission member 70 is removed by being moved to the right in the figure, but the transmission member 70 is urged to the left in the figure by the coil spring 80, so it is normally not engaged. The groove 76 and the protrusion 78 are in an engaged state. coil spring 80
has one end attached to the back surface of the head of the bolt 82 protruding from the second cylindrical member 38, and the other end attached to the transmission member 70.
When the transmission member 70 is moved to the right in the figure, it is elastically deformed.

On the other hand, a notch (cam part) 84 is formed at the front end of the fitting part 72 of the transmission member 70, and inside this cam part 84, a circular cross-section as a cam protrusion provided on the rotating shaft 34 is formed. Pin 86 is fitted. A part of the cam portion 84 is a cam surface 88 that intersects the rotation locus of the pin 86, and when the pin 86 is rotated, the pin 86 and the cam portion 8
Due to the cam action with the cam surface 88 of 4, the transmission member 7
0 is pushed backwards (to the right in the figure). That is, the cam surface 88 is formed as a surface that approaches the rotation locus of the pin 86 as it moves forward in the rotational direction of the pin 86.

A cover 90 is disposed at the rear end portion of the second cylindrical member 38 connected to the rotation shaft 34 via the transmission member 70 to cover the connecting portion. The cover 90 is
As shown in FIGS. 2, 7, and 8, it is a cylindrical member with a bottom, and the opening side is the second cylindrical member 38.
a groove formed in the second cylindrical member 38, and a ball 9 that also serves as a bearing and fits into this groove.
2 prevents it from detaching from the second cylindrical member 38. The cover 90 can rotate relative to the second cylindrical member 38, and is provided with an operating section 94 for applying a rotational operating force to the outer circumference. This cover 90 is provided with an engagement hole 100 into which a ball 98 urged by a spring 96 partially enters. Engagement hole 10
0 and the ball 98 are provided to provide a sense of moderation when the cover 90 is rotated. On the other hand, the bottom of the cover 90 is provided with a plurality of locking projections 102 that fit into the engagement groove 76 of the transmission member 70. The protrusion 102 is for allowing or prohibiting the backward movement of the transmission member 70. When the protrusion 102 is positioned at the same phase angle as the engagement groove 76, the backward movement of the transmission member 70 is allowed;
Also, when the transmission member 7 is located at different phase angles,
0's backward movement is prohibited. When the protrusion 102 is located at the same phase angle as the engagement groove 76, the protrusion 10
2 enters the engagement groove 76 to allow the transmission member 70 to move backward, and when the transmission member 70 is located at a different phase angle, it comes into contact with the rear end surface of the transmission member 70 and prevents the backward movement. . The position of the protrusion 102 can be adjusted by rotating the cover 90.

The forward end of the rotating shaft 34 has a threaded portion 104.
This threaded portion 104 is connected to the second cylindrical member 3.
The rotating shaft 34 is screwed into the threaded portion 39 on the inner circumferential side of the rotary shaft 34, and the end on the retreating side is an operating portion 106 having a hexagonal cross section. It is now possible to operate the rotation. In addition, the rotation axis 3 when not clamped
4 protruding from the cover 90, annular grooves 108 for measuring the amount of advance of the rotating shaft 34 are provided at regular intervals.

A hole 110 with a circular cross section extending in the axial direction is formed in the threaded portion 104 of the rotating shaft 34.
A rod-shaped first piston 112 with a small diameter is inserted into the piston. The first piston 112 is supported by the bottom portion 46 of the first cylindrical member 36, and its rear end is brought into contact with the bottom portion of the hole 110 via a thrust washer 114. As a result, it is being pushed forward.

A second piston 116 is arranged in front of the first piston 112.
12, second piston 116 and first cylindrical member 36
A hydraulic chamber 118 is formed by the inner wall surface of the hydraulic chamber 118 . The area of the pressure receiving surface 120 of the second piston 116 is made larger than the area of the pressure applying surface 122 of the first piston 112, so that the forward force in the first piston 112 is boosted and transmitted to the second piston 116. It's becoming like that. Second piston 11
6 is a fitting part 124 on the retreating side and a body part 126 in the center
and a threaded portion 128 on the advancing side, and is slidably fitted to the inner circumferential surface of the first cylindrical member 36 at the fitting portion 124. A disc spring 130 is fitted in the body 126, and the second piston 116
The force acting on the disc spring 130 is transmitted to the spindle 30 via the disc spring 130 and the collar 132 disposed in front of the disc spring 130. The disc spring 132 has an adjustment nut 134 screwed onto the threaded portion 128.
A certain amount of preload is applied by operating the second piston 116, and when the force acting on the second piston 116 becomes larger than this preload, it is elastically deformed in the compression direction.

Note that the first piston 112 is attached to the fitting portion 124.
A recess 136 is formed into which the material is inserted. In addition, in FIG. 2, 138 is a plug for blocking the air vent hole, and 140, 142
is an O-ring for sealing.

Next, the operation when the vise device having such a configuration is used as a hydraulic vise device will be explained. That is, when using a vise device with such a configuration as a hydraulic vise device, first rotate the cover 90 to a position that allows the backward movement of the transmission member 70, and in this state, the fixed jaw 12 and the movable jaw A predetermined workpiece to be held is placed between the handle 144 (the first
(see figure) and rotate it. In this state, since the workpiece is not yet sandwiched between the fixed jaw 12 and the movable jaw 14, the rotational load on the spindle 30, that is, the transmission member 70, is small, and therefore the rotational force of the rotating shaft 34 is transmitted to the pin 86. is transmitted to the transmission member 70 based on the engagement of the cam portion 84 with the cam surface 88, and is further transmitted to the second cylindrical member 38,
The signal is transmitted to the coupling mechanism 44 including the first cylindrical member 36 and the like, and to the spindle 30, so that the spindle 30 is rotated in the same direction as the rotating shaft 34. When the spindle 30 is rotated, the movable jaw 14 is moved forward to the left in FIG. Insert the workpiece in between.

When the movable jaw 14 sandwiches a workpiece with the fixed jaw 12, the rotational load on the spindle 30, the coupling mechanism 44, and the transmission member 70 increases, and when this reaches a certain level, the pin 86 and the rotational load increase. The force that pushes the transmission member 70 in the backward direction based on the cam action with the cam surface 88 of the cam portion 84 is
The urging force of the coil spring 80 is overcome, and the transmission member 70 is moved rearward. That is, as shown in FIG. 9, the pin 86 rides on the front end surface of the transmission member 70, and the engagement between the pin 86 and the cam surface 88 of the cam portion 84 is released. Note that at this time, the protrusion 102 of the cover 90
enters into the engaging groove 76 as the transmission member 70 retreats.

When the pin 86 rides on the front end surface of the transmission member 70, the transmission member 70 is no longer connected to the rotation shaft 3.
4 cannot be transmitted to the coupling mechanism 44, and therefore only the rotating shaft 34 is rotated independently from now on. That is, this transmission member 7
0, furthermore, a coil spring 80, a bolt 82,
The pin 86, cam portion 84, cam surface 88, etc. constitute a clutch 146 that transmits and interrupts the rotational force to the coupling mechanism 44 and, ultimately, the spring 30.

In such a state, when a rotational operation force is continuously applied to the rotating shaft 34, the rotating shaft 34 will be damaged by the threaded portions 104, 3 of the rotating shaft 34 and the second cylindrical member 38.
By the feeding action of 9, it is moved forward relative to the coupling mechanism 44. Along with this, the first piston 112
is pushed forward, increasing the hydraulic pressure in the hydraulic chamber 118 and causing the hydraulic pressure to act on the second piston 116. At this time, the boosting effect described above takes place. The second piston 116, which has been subjected to the hydraulic pressure, is connected to the spindle 3 via the disc spring 130.
0 and causes it to move in parallel in the forward direction. This forward movement of the spindle 30 brings the movable jaw 14 closer to the stationary jaw 12, thereby increasing the clamping force on the workpiece.

After a predetermined process has been performed on the workpiece, in order to release the clamp on the workpiece, use the handle 1 fitted into the operating part of the rotating shaft 34.
44 may be rotated in the opposite direction to that described above. The operation then is also opposite to that described above. That is, when the rotating shaft 34 is rotated in the opposite direction, the rotating shaft 34 is returned to the backward direction by the action of the threaded portions 104 and 39, and together with this, the first piston 11
2 is returned in the same direction by the hydraulic pressure in the hydraulic chamber 118. As a result, the hydraulic pressure in the hydraulic chamber 118 becomes weaker, so that the second piston 116, the spindle 30, and the movable jaw 14 move in the backward direction due to the reaction force of the clamping action on the workpiece and the biasing force of the disc spring 60. be returned. Then, when the pin 86 on the rotating shaft 34 reaches a position corresponding to the cam portion 84 of the transmission member 70, the pin 86 is fitted into the cam portion 84 again, and the rotational force of the rotating shaft 34 is applied to the transmission member 70. The state is such that the signal is transmitted to the coupling mechanism 44 via the linking mechanism 44. As a result, the rotational force of the rotating shaft 34 is directly transmitted to the spindle 30, and hence the movable jaw 14 is moved backward by the action of the screw mechanism provided between the spindle 30 and the moving block 18. being brought back in the direction. Note that at the time when the pin 86 is fitted into the cam portion 84, the clamping force on the workpiece is weak, and therefore the rotational load on the spindle 30 and the coupling mechanism 44 is also small, so the rotational force of the rotating shaft 34 is reduced. is smoothly transmitted to the coupling mechanism 44 and spindle 30 via the transmission member 70.

In this way, when the device of this embodiment is used as a hydraulic vise device, the rotary axis is fixed until the movable jaw 14 reaches the position where it clamps the workpiece, that is, in the range where there is no need to generate strong clamping force. The rotational operating force applied to the movable jaw 34 is directly transmitted to the spindle 30 via the transmission member 70 and the coupling mechanism 44, and therefore
4 is moved largely in the forward direction by the action of a screw mechanism between the spindle 30 and the moving block 18. On the other hand, when it is necessary to generate a large clamping force, the operating force applied to the rotating shaft 34 is transmitted to the spindle 30 and the movable jaw 14 via the booster mechanism, and the workpiece is It is tightened.

Therefore, in such a device, it is possible to have a large movement stroke of the movable jaw 14 and to generate a strong clamping force. Since it is automatically switched, there is no need to separately provide a mechanism for switching and operate it, and there is no need for any troublesome work.

Further, as is clear from the above description, the hydraulic chamber 118 in the above device is formed by sealing hydraulic oil in a sealed space, and does not require piping for introducing hydraulic pressure. Therefore, in the above-mentioned apparatus, these piping parts do not become an obstacle and make it difficult to work, and oil leakage does not occur at the connecting parts of these piping parts. Since it is relatively easy to ensure sealing inside the device, the device as a whole has a structure that does not easily cause oil leakage, and even if oil leakage occurs while clamping a workpiece, Also, since the disc spring 130 has a function as an accumulator that stores clamping force, the clamping force does not immediately decrease due to oil leakage. Therefore, the risk of the workpiece falling off during work is significantly reduced, and problems such as damage to the workpiece or reduction in machining accuracy due to the workpiece falling off will not occur. Furthermore, since the disc spring 130 has the function of a limiter that regulates the maximum value of the clamping force, it is possible to always clamp the workpiece with a stable clamping force. Damage caused by force can also be effectively avoided.

In addition, in the event that an oil leak occurs in the hydraulic chamber 118, or in a case where there is no need to generate a large clamping force, if you wish to use the above device in the same way as a conventional mechanical vise device, The cover 90 may be rotated by a certain angle to prevent the transmission member 70 from moving in the backward direction, and the rotating shaft 34 may be rotated in this state. Rotate the cover 90 to expose the protrusion 102 formed on the bottom thereof, as shown in FIG.
If the transmission member 70 faces the rear end surface of the transmission member 70, the transmission member 70 will be prevented from moving in the backward direction, so that the operating force applied to the rotation shaft 34 will always be applied to the transmission member 70. 70 and the coupling mechanism 44 to the spindle 30, so that the movable jaw 14 is always moved only by the action of a screw mechanism provided between the spindle 30 and the movable jaw 14 (transfer block 18). , and can be advanced, providing the same functionality as a conventional mechanical vise device.

Although the embodiments of the present invention have been described in detail above, the present invention should not be construed as being limited to such specific examples, and in the above embodiments, the pin 86 and the cam portion 84 (cam surface 88) are Various modifications can be made based on the knowledge of those skilled in the art without departing from the spirit of the invention, such as providing it on the opposite member.

[Brief explanation of drawings]

FIG. 1 is a partially cutaway front view showing a hydraulic vise device according to an embodiment of the present invention, and FIG. 2 is a sectional view of a main part of the device. 3 and 4 are a longitudinal sectional view and a side view, respectively, of the second cylindrical member in FIG. 2. 5 and 6 are a side view and a front view of the transmission member in FIG. 2, respectively. 7 and 8 are a longitudinal sectional view and a front view of the cover in FIG. 2, respectively. 9th
1 and 10 are sectional views of essential parts showing different operating states of the apparatus shown in FIGS. 1 and 2, respectively. 10: Main body, 12: Fixed jaw, 14: Movable jaw, 28: Female screw hole, 30: Spindle, 3
2: Large diameter part, 34: Rotating shaft, 39: Threaded part, 4
4: Connection mechanism, 52: Projection, 56: Engagement groove, 6
4: Threaded portion, 70: Transmission member, 76: Engagement groove, 7
8: Projection part, 80: Coil spring, 84: Cam part, 86: Pin (cam projection), 88: Cam surface,
90: Cover (lock member), 102: Projection, 1
12: first piston, 116: second piston, 1
18: Hydraulic chamber, 120: Pressure receiving surface, 122: Pressure applying surface, 130: Belleville spring, 146: Clutch.

Claims (1)

[Scope of Claims] 1. A stationary stationary stationary stationary stationary stationary stationary stationary stationary stationary stationary stationary stationary stationary stationary stationary station‐‐ 1 1. It has a spindle screwed onto the movable jyo, which moves the movable jyo forward and backward toward the fixed jyo. a vise device configured to clamp a predetermined article between the clamps, the vise device being rotatable around an axis parallel to the spindle and immovable relative to the fixed jaw in the axial direction of the spindle; a coupling mechanism coupled to the spindle in a manner that is non-rotatable and movable relative to the spindle; a rotating shaft to which a rotational operation force is applied, which is provided so as to be movable relative to the coupling mechanism in the axial direction; a transmission member coupled to the coupling mechanism in a state in which the transmission member is fitted into the coupling mechanism and is not rotatable relative to the coupling mechanism and movable in the axial direction; and the transmission member is moved in the forward direction of the movable jaw. a cam projection provided on one of the transmission member and the rotating shaft, and a cam surface provided on the other;
When the rotational load on the transmission member is small,
Based on the engagement between the cam protrusions and the cam surface, the rotating shaft is prevented from rotating relative to the transmission member, while in a state where the rotational load on the transmission member is greater than a certain level, The transmission member is moved backward against the biasing force of the spring means by the cam action of the cam projections and the cam surface, and the engagement between the cam projections and the cam surface is released, and the rotation shaft is rotated. a clutch means including a cam mechanism that allows relative rotation with respect to the transmission member; a position that prevents the transmission member from moving in the backward direction due to the cam action; and a position that allows the transmission member to move in the backward direction. a locking member provided on the coupling mechanism so as to be movable between positions; a hydraulic chamber formed in a sealed state in the coupling mechanism; and a pressurizing surface facing the hydraulic pressure chamber; a first piston that moves together with the rotating shaft to advance the pressurizing surface toward the hydraulic pressure chamber when the piston is moved forward relative to the coupling mechanism by the action of the screw mechanism; a second piston having a pressure-receiving surface facing the pressure chamber and having a larger area than the pressure-receiving surface, the second piston being moved in the forward direction of the movable jaw based on the hydraulic pressure acting on the pressure-receiving surface; a mechanism; and a disc spring means interposed between the second piston and the spindle and pressing the spindle in the forward direction of the movable jaw based on the forward movement of the second piston. Hydraulic vise device.