KR100216685B1 - Clamp apparatus - Google Patents

Abstract

The first piston 11 is inserted into the second piston 12 in the housing 4, and the working point A, the point C, and the wedge hydraulic pressure surface B are inserted into the first piston 11. It is installed in order from the front, and the first swing interval 37 and the second swing interval 38 are installed in the lower space of the front part of the first piston 11 and the upper space of the rear part, respectively, and the second piston 12 In the above pressure receiving surface (B) is provided a pressing surface (F) facing from the bottom, and at the time of clamping advances both pistons (11) (12) to the fluid pressure of the first operating chamber (21) and then A clamp device configured to oscillate downward with respect to the point portion (C) by operating the second piston (12) relative to the first piston (11).

Description

Clamp device

1 to 6 show a first embodiment of the present invention, and FIG. 1 is an explanatory view of the operation of the clamp device.

1 (a) shows the clamp state,

1 (b) shows the temporary clamp state,

Figure 1 (c) shows the state of the clamp,

2 is a longitudinal side view of the clamp device.

3 is a cross-sectional view taken along the line III-III of FIG.

4 is a cross-sectional view taken along the line IV-IV of FIG.

5 is a cross-sectional view taken along the line V-V in FIG.

6 is a schematic diagram illustrating the operation of the clamp device.

7-8 show a second embodiment,

7 is a view corresponding to FIG.

8 is a cross-sectional view taken along the line VIII-VIII of FIG.

9 shows a third embodiment, which corresponds to FIG.

FIG. 10 shows the fourth embodiment and corresponds to FIG.

FIG. 11 shows the fifth embodiment and corresponds to FIG.

FIG. 12 shows the sixth embodiment and corresponds to FIG.

13 to 15 show a seventh embodiment,

13 is a view corresponding to FIG.

14 is a sectional view taken along line XIV-XIV in FIG.

FIG. 15 is a sectional view taken along the line XV-XV in FIG.

The present invention relates to a clamp device that presses a fixed object such as a mold, a work pallet, a work piece, etc. by a fluid pressure such as compressed air or hydraulic pressure, to a fixture of a processing machine such as an injection molding machine or a complex machine tool. In other words, the wedge type mechanism It relates to a technique that can obtain a strong clamping force by means of.

Clamping devices equipped with this type of wedge-powered mechanism are described in US Pat. No. 4,365,792. The clamp device of this conventional structure operates as follows.

First, the clamp tool is advanced from the retracted position to the advanced position by advancing the piston by the advance stroke. Then, the piston is advanced by the clamp stroke, and the wedge member ( I move forward. The wedge member then swings the clamp tool from the advance position to the clamp position and engages the mold. Subsequently, the piston is pushed further by this clamp stroke, so that the wedge mechanical force of the wedge member By clamping, the clamp tool is strongly clamped to the clamp position seen from the clamp position.

The above conventional structure has the following problems.

The clamp device needs to have a temporary clamp stroke between the advancing stroke and the main clamp stroke. Since the stroke for the temporary clamp is performed by the wedge member having a narrow end to the clamping position of the clamp tool, a relatively long stroke is required. For this reason, the entire stroke of the clamp device becomes long, and as a result, the length of the front-back direction of a housing becomes large and a clamp device becomes large. In addition, the entire stroke of the clamping device is long, and the clamp operation time is also long, resulting in poor clamping efficiency.

The first object of the present invention is to downsize the clamp device and the second object of the present invention is to shorten the clamp operation time.

In order to achieve the above object, the clamp device is constructed as follows. In the housing 4, the first piston 11 for the provisional clamp and the second piston 12 for the clamp are installed in the front-rear direction so as to be able to move in a longitudinal direction. According to the fluid pressure of the first operating chamber 21 formed behind these pistons 11.12, the sheepskin 11.12 is advanced, and the second piston 12 is moved forward with respect to the first piston 11. Configure it to In contrast to this, the first piston is provided via the second piston 12 by the fluid pressure of the second operating chamber 22 for the unclamp, which is formed in front of the second piston 12. (11) is configured to retreat. The acting point part A, the point part C, and the wedge-type hydraulic pressure surface to the first piston 11 described above ( Install B in order from the front. It is provided in the rear part of the said 1st piston 11 so that the unclamping manual part E may face front. The unclamping drive part which faces the said passive part E from the front while providing the said wedge-type pressure surface F which faces the said wedge-type hydraulic pressure surface B from the bottom to the said 2nd piston 12 above. Install (D). The first swing interval 37 is installed in the lower space in front of the first piston 11, and the second swing interval 38 is installed in the rear upper space of the first piston 11.

Hereinafter, the operation of the present invention.

When switching from the unclamped state to the clamped state after passing the clamped state, pressure fluid is supplied to the first operating chamber 21. Then, by the fluid pressure, both pistons 11.12 advance forward by the advance stroke, and the working point A of the first piston 11 is directly or indirectly engaged with the fixed object 2 such as a mold from above. The to-be-fixed object 2 is clamped.

Subsequently, the second piston 12 advances by this clamp stroke S with respect to the first piston 11 which is prevented from moving forward, and then the second piston 12 is formed on the pressure receiving surface B of the first piston 11. The pressing surface F of 12) engages. Then, by the wedge machine force acting on the hydraulic pressure surface B on the pressure surface F, the hydraulic pressure surface B swings upward slightly around the point portion C and at the same time, the action point portion A is slightly It swings downward.

In this case, the force acting on the hydraulic pressure surface B on the pressing surface F is increased according to the lever ratio X / Y, and the clamp force, the increased force, is transmitted from the working point portion A to the fixed object 2. do.

When the fluid pressure in the first operating chamber 21 is abnormally lowered or lost due to an accident in the above clamp state, clamp release force such as gravity or work reaction force acting on the fixed object 2 is reduced. Attempt to release the clamp state of the first piston (11). However, at the same time as the frictional force acts on the point portion C of the first piston 11 in the cylinder hole 9 of the housing 4 to counteract the clamp release force, the second cylinder in the other cylinder hole 10. Friction force acts on the outer circumferential surface of the piston 12, and the combined force (force) of these two friction forces prevents the retraction of the first piston 11. In addition, when the first piston (! 1) attempts to retreat even a little, the hydraulic pressure surface (B) of the first piston (11) interlocks with the pressure surface (F) of the frictionally fixed second piston (12). Retraction of the first piston 11 is prevented.

When switching from the main clamp state to the unclamped state, the pressure fluid is sold from the first operating chamber 21 and the pressure fluid is supplied to the second operating chamber 22. As a result, the second piston 12 is retracted with respect to the first piston 11, and the wedge-mechanism between the pressure receiving surface B and the pressing surface F is released. The passive part E of the 1st piston 11 is retracted by the unclamping drive part D of the 2nd piston 12 which retreats continuously, and the 1st piston 11 is unclamped.

The present invention can achieve the following advantages by configuring and acting as described above.

The clamping apparatus of the present invention is different from the conventional example and the entire stroke is shortened because a stroke for swinging the clamp to the clamp position by the wedge member is not necessary. Thereby, the length of the front-back direction of a housing can be shortened and a clamp apparatus can be made small. In addition, as described above, the entire stroke is short, so that the clamp operation time is shortened and the efficiency of the clamping operation can be improved.

In addition, at the time of clamping, a strong clamping force can be obtained by the total action of the wedge machine force and the lever ratio of the first piston.

In addition, even when the fluid pressure in the first operating chamber drops abnormally or disappears, frictional force acts on the point of the first piston against clamp release force such as gravity or processing reaction force. At the same time, a frictional force acts on the outer circumferential surface of the second piston, and the force of these two frictional forces prevents the retraction of the first piston. Further, if the first piston attempts to retreat at all, the hydraulic pressure surface of the first piston is interlocked with the pressure surface of the frictionally fixed second piston, thereby preventing the retraction of the first piston. This can reliably prevent the clamp device from being released.

In addition, since the first piston is unclamped after the wedge-mechanism between the hydraulic pressure surface and the pressure surface is released, the operation force is small. For this reason, the use of the unclamping operation of the clamp device is assured.

[First Embodiment]

1 to 6 show a first embodiment.

As shown in FIG. 2, the metal mold | die 2 is fixed by the pneumatic clamp apparatus 3 to the upper surface of the fixing stand 1 of an injection molding machine. The pneumatic clamp 3 has a left and right pair of side walls 5 of the housing 4 secured to the fixing table 1 by two bolts 6, and is located in front of the front surface 4a of the housing 4. The clamp portion 7 pushed forward is pressed against the die 2 obliquely from above.

In the housing 4, the first hole 9 of a small diameter whose front part is opened to the housing front surface 4a to be drooped behind, and the large diameter second hole arranged coaxially with the first hole 9 ( 10) is formed before and after. In the first hole 9, a normal first piston 11 for temporary clamp is inserted through the zero ring 14 so as to be airtight. The clamp portion 7 is provided at the front of the first piston 11. In addition, the normal second piston 12 for the clamp is inserted into the second hole 10 through the zero ring 15 so as to be airtight. The rear part of the said 1st piston 11 is inserted in the 2nd piston 12 through the 0 ring 16 for airtight movement material. In the rear part of the said 2nd hole 10, the end plate 18 was airtightly fixed through the 0 ring 19. As shown in FIG.

A clamping first operating chamber 21 is formed at the rear of both pistons 11.12, and a second operating chamber 22 for unclamping is formed in front of the second piston. The compressed air supply / exhaust ports 23.24 were opened in these first operating chambers 21 and the second operating chambers 22, respectively. In addition, the end plate 18 is inserted with a clamp and an unclamped state detecting rod 26 through a zero ring 27 to allow airtight movement, and the first piston 11 is inserted into a clamped state holding spring ( 28) was piled up to face to the front via the rod (26).

2 and 3, both pistons 11.12 will be described in more detail. FIG. 3 is a view taken from the arrow III-III in FIG. 2, and shows the state in which the rod 26, the spring 28 and the nut 31 described later are taken out from the first piston 11.

The working point portion A is installed at the lower portion of the clamp portion 7 of the first piston 11, and the wedge-type hydraulic pressure surface B is installed at the rear lower portion of the first piston 11 so that the front portion thereof is more than the rear. do. Moreover, the point part C is provided in the upper part near the front of the 1st piston 11. As shown in FIG. This point portion C is directly supported by the upper circumferential surface of the first hole 9. Moreover, the unclamping manual part E is provided in the nut 31 fixed to the back of the 1st piston 11 toward the front.

An annular spherical groove 33 is formed at the rear of the through hole of the second piston 12. Wedges on the lower surface of the spherical groove 33 34 is fitted. The wedge-type pressing surface F was formed in the upper surface of the wedge 34, and the pressing surface F was made to face the said hydraulic pressure surface B below. Moreover, the unclamping drive part D was provided in the back of the 2nd piston 12, and the drive part D was made to face the said passive part E from the front. Moreover, the 1st oscillation space | interval 37 was provided in the 1st hole 9 in the lower side of the front part of the said 1st piston 11 above. In addition, an annular second swing interval 38 is provided between the rear portion of the first piston 11 and the second piston 12.

As shown in FIG. 2, FIG. 4, and FIG. 5, the slide shuttle member 41 for sliding is provided between the upper surface of the said metal mold | die 2, and the action point part A via the key 42. As shown in FIG. The slide movement was interposed within a predetermined range in the front-rear direction. The shuttle member 41 is plated on the nitrided alloy steel, and is piled up so as to receive pressure toward the front surface by the advance spring 43. The frontal movement of the shuttle member 41 by a predetermined amount or more is prevented by a pair of stopper bolts 45.46 fitted in the flow hole 44. Reference numeral 46 is a support plate.

As shown in FIG. 1 and FIG. 6, the pneumatic clamp device 3 operates as follows.

In the unclamped state shown in FIG. 1 (a), the compressed air in the first operating chamber 21 is discharged from the first rapid defecation (not shown) and is not shown in the second operating chamber 22. Compressed air is supplied from the second emergency bowel movement. Thereby, the 2nd piston 12 opposes the spring 28, and the 1st piston 11 is retracted.

When switching from the unclamped state to the clamped state, compressed air is also supplied to the first operating chamber 21 while supplying compressed air to the second operating chamber 22 as shown in FIG. 1 (b). . Then, the first piston 11 causes the air pressure and the spring of the first operating chamber 21 to be retained in the retracted position by the second piston 12 being opposed to each other in the operating chambers 21.22. It advances by the pressure of shot (28). Thereby, the 1st piston 11 advances by the advancing stroke L, co-driven the 2nd piston 12 through the unclamping manual part E and the drive part D in order (FIG. 6). The lower portion of the peninsula 7) is attached to the upper portion of the mold (2). As a result, the mold 2 is strongly clamped by both the air pressure of the first operating chamber 21 and the spring 28 and does not shift or move. In this case, the action point portion A swings upward due to the reaction force in the mold 2 described above. In addition, the compressed air in the second operating chamber 22 is supplied to the first operating chamber 21 from the second sudden displacement through the first sudden displacement (not shown) as the two pistons 11.12 advance. Therefore, it is possible to save energy by preventing compressed air from being unnecessarily discharged.

Subsequently, as shown in FIG. 1 (c), the extruded air is discharged from the second operation chamber 22 while the compressed air is supplied to the first operation chamber 21. Then, the second piston 12 advances by this clamp stroke S with respect to the first piston 11 whose advance movement is prevented by the mold 2 (see the lower half of Fig. 6). The press surface F of the 2nd piston 12 engages with the press surface B of (11). According to the wedge-mechanical force from the pressing surface F to the hydraulic surface B, the hydraulic pressure surface B oscillates slightly upward and the working point portion A oscillates slightly downward at the same time around the point portion C. will be.

In this case, the force acting on the hydraulic pressure surface B on the pressing surface F is increased in accordance with the ratio of the manual distance X and the operating distance Y, so that a strong clamping force corresponding to the lever ratio X / Y It transfers from the working point part A to the metal mold | die 2 (it shows the clamp reaction force acting on the working point part A in the metal mold | die 2 here.).

Incidentally, the wedge angle of the pressing surface F is preferably in the range of 5 ° to 15 °. For example, in the case where the wedge angle is limited to 10 °, the wedge mechanical force from the pressing surface F to the hydraulic surface B acts on the second piston 12 in the first operating chamber 21. It is about 2.5 to 3 times the driving force. The lever ratio X / Y can be set to a value of about 2 to 3. As a result, the clamping force acting on the mold 2 at the working point portion A becomes about 5 to 9 times the driving force of the second piston 12.

Therefore, a strong clamping force can be obtained even when the working fluid is compressed air having a low pressure of about 7 kgf / cm 2.

When the pressure in the first operating chamber 21 is abnormally lowered or lost due to breakage of the compressed air supply pipe or the like, the clamp releasing force such as gravity or work reaction force acting on the mold 2 is applied. 1 Attempt to release the clamp state of the piston (11). However, the frictional force acts on the point portion C of the first piston 11 from the first hole 9 of the housing 4 so as to counter the clamp release force, and at the same time, the second piston 10 is removed from the second hole 10. A frictional force acts on the outer circumferential surface of 12), and the force of these two frictional forces prevents the retraction of the first piston. Furthermore, when the first piston 11 tries to retreat even a little, the hydraulic pressure surface B of the first piston 11 is interlocked on the pressure surface F of the frictionally fixed second piston 12. Retraction of the first piston 11 is prevented.

In addition, when the first piston 11 swings during clamp driving as described above, the upper surface and the lower surface of the wedge support for rocking support are formed by themselves even in the first hole 9 formed in a straight line. For this reason, it is not necessary to form the support part for the point part C in the 1st hole 9.

Contrary to the above, when switching the pneumatic clamp device 3 from the main clamp state of FIG. 1 (c) to the unclamp state of FIG. 1 (a), the compressed air in the first operating chamber 21 is discharged. Compressed air is supplied to the second operating chamber 22. Then, first, the second piston 12 is retracted by the pressure, and the wedge-mechanism of the pressure receiving surface B and the pressing surface F is released. Subsequently, as shown in FIG. 1 (b), the unclamping drive unit D is attached to the passive unit E. As shown in FIG. Subsequently, as shown in FIG. 1 (a), the second piston 12 retracts the first piston 11 against the spring 28.

In this way, since the first piston 11 is unclamped after the wedge coupling between the pressure receiving surface B and the pressing surface F is released, the operation force is small. For this reason, the unclamping operation of the clamp device 3 is easy and reliable.

The shuttle member 41 shown in FIG. 2 operates as follows at the time of said unclamping. When the first piston 11 is driven backward and backward, slippage occurs between the shuttle member 41 frictionally fixed to the mold 2 and the operation point A, and the shuttle member 41 remains. Only the clamp portion 7 is driven to the rear upper side. The clamping portion 7 and the shuttle member 41 are driven backward by the first piston 11 which is continuously driven back and the mold 2 is unclamped. Therefore, even when the shuttle member 41 is strongly interlocked to the mold 2 at the time of the clamp, sliding occurs between the shuttle member 41 and the working point portion A at the time of unclamping as described above. Unclamping operation can be surely performed.

The pneumatic clamp device 3 of the above configuration can obtain the following advantages.

As shown in the lower half of Fig. 6, at the time of clamping, both pistons 11.12 advance by the advancing stroke L, engage the mold 2, and then only the second piston 12 sees the clamp stroke ( The clamp is completed by advancing further by S). For this reason, the stroke T which moves the clamp tool to the clamp position by the wedge member is omitted (refer to the upper half of FIG. 6), and the entire stroke is shortened. As a result, the clamp device 3 can be made compact by shortening the length in the front-rear direction of the housing 4.

In addition, since the entire stroke of the clamp device 3 is shortened, the clamp operation time is also shortened, which can improve the efficiency of clamping work.

Since the first piston 11 and the second piston 12 are provided substantially coaxially in the housing 4, the height of the housing 4 can be made low. In addition, since the first piston 11 is inserted into the second piston 12, the length of the front and rear directions of the housing 4 can be shortened. Therefore, the clamp device 3 can be made more compact.

The first hole 9 into which the first piston 11 is inserted is opened in the front portion 4a of the housing 4 so that the front portion thereof sags from behind, so that the mold 2 can be clamped from above and the mold 2 ) The allowable range of clamp thickness is large. In addition, since the above-mentioned first hole 9 is only required to be formed straight in the housing 4, the supporting part for the point portion C is machined in advance in the housing 4 or the supporting member of the other part is provided. There is no need to attach, and the manufacturing cost of the clamp device 3 becomes cheap.

The clamping force of the pneumatic clamp device 3 is applied to the pneumatic propulsion force of both pistons 11.12, so that the elastic force of the spring 28 can be used, and thus the clamping ability is large.

In addition, since the wedge 34 is provided as a separate body from the second piston 12, the degree of freedom of choice of the material and surface treatment of the wedge 34 is increased. It becomes easy.

The above first embodiment can be modified as follows.

At the time of switching from the unclamped state to the clamped state, as described above, the process of simultaneously supplying compressed air to both operating chambers 21.22 is replaced with the supply of compressed air to the first operating chamber 21. The compressed air may be discharged from the second operation chamber 22. In this case, in order to retreat the second piston 12 from the first piston 11 at the time of clamping, the throttle valve is connected to the air supply port 24 on the side of the second operation chamber 22. Although it is preferable to slow the discharge rate of the compressed air in the second operation chamber 22, this throttle valve is not essential.

In addition, the clamp state holding spring 28 can be omitted. In this case, at the time of the temporary clamp, the first piston 11 is advanced only by the air pressure of the first operating chamber 21.

It is possible to omit the above shuttle member 41 by selecting an appropriate material or surface treatment between the mold 2 and the clamp portion 7. The zero ring (14.15.16) that seals and closes both pistons (11.12) may be an X ring or a U-packing.

The first swinging interval 37 may be formed in the first hole 9 of the housing 4 so as to have a shaft diameter of the first piston 11. Alternatively, the second swing interval 38 may also be formed in the second piston 12 so as to reduce the diameter of the first piston 11. The first hole 9 may be formed to be straight, and the upper surface and the lower surface may be formed with a concave surface for rocking support in advance.

7 and 8, 9 to 12, and 13 to 15 show the second to seventh embodiments, respectively. In addition, in these Examples, the element example of the structure similar to said 1st Example has attached | subjected the same code | symbol as a rule.

Second Embodiment

7 and 8 show a second embodiment.

A pair of long holes (52.52) is fixed to the rear of the first piston 11 while fixing the clamp and unclamped state detecting rod 26 and the second piston 12 laterally. ), And the pin 51 is inserted into these long holes 52.52 freely in the front-rear direction. An unclamping drive unit D is formed by both sides of the pin 51, and an unclamping manual unit E is formed along the rear wall of the long hole 52. The rod 26 was pressed against the front by the first spring 53 and the first piston 11 was pressed against the rod 26 by the second spring 54.

In the switch box 56 fixed to the rear surface of the housing 4, a clamp state detection limit switch 57 and an unclamp state detection limit switch 58 are provided. Each contact 59.60 of these limit switches 57.58 is operated at the rear of the rod 26.

In this second embodiment, the pressing surface F of the wedge 34 faces the front face via the first spring 53 via the rod 26, the pin 51 and the second piston 12 in order. By suppressing it, the clamping state can be strongly prevented. In addition, it is also possible to omit either or both of the springs 53.54.

Third Embodiment

9 shows a third embodiment.

The shaft diameter portion 61 provided in the rear portion of the first piston 11 was inserted into the small diameter portion 62 of the second piston 12 in an airtight manner with a 0 ring 63 interposed therebetween. The unclamping manual part E was provided in the rear end of the 1st piston shaft diameter part 61, and the drive part D was provided in the 2nd piston small diameter part 62. As shown in FIG. The pressure receiving surface B is provided in the middle portion of the front-rear direction of the first piston 11. In addition, the pressing surface F is provided in front of and below the second piston 12. The rod 26 shown in each of the above embodiments is omitted and the second piston 12 is directly suppressed by the first spring 53 and the second piston 54 is pressed by the second spring 54. 12), the first piston 11 was pressed down.

Fourth Embodiment

FIG. 10 shows the fourth embodiment, and the embodiment of FIG. 19 is modified as follows.

The piston rod 66 protruding toward the front from the second piston 12 was inserted into the airtight shape through the 0 ring 67 in the first hole 9 of the housing 4. The pressure in the first operating chamber 21 acts on the rear surface of the zero ring 69 for the first piston 11 between the piston rod 66 and the first piston shaft diameter portion 68.

[Example 5]

11 shows the fifth embodiment.

The first hole 9 and the second hole 10 are formed in the housing 4 with a gap between them. The first piston 11 is hermetically inserted through the 0 ring 71 in the first hole 9, and the second piston 12 is inserted through the 0 ring 72 in the second hole 10. It is inserted in airtightness. A large diameter first operating chamber 21 is formed behind these pistons 11.12, and a small diameter second operating chamber 22 is formed in front of the second piston 12. As shown in FIG. Each piston 11.12 is pressed forward by the first spring 73 and the second spring 74, respectively. The unclamping manual part E and the pressure receiving surface B are provided in the front and rear of the wedge 75 fixed to the rear lower part of the first piston 11, and the unclamping driving part ( D) and the pressing surface F are provided back and forth.

Sixth Embodiment

12 shows a sixth embodiment.

The first hole 9 and the second hole 10 are formed coaxially horizontally and inserted into the first hole 9 and the working point A of the front portion of the first piston 11 and the mold 2 The clamp tool 81 is provided in between.

In the unclamped state, the clamp tool 81 extends forward with respect to the first piston 11 by the forward spring 82. At the time of clamping, when the sheepskin (11.12) moves out, the lower portion (83) of the clamp tool (81) is picked up by the stopper wall (84), and the clamp tool (81) of the first piston (11). It swings downward according to the working point part A, and sticks to the metal mold | die 2. Subsequently, due to the wedge mechanical force acting on the pressure receiving surface B of the first piston 11 from the pressing surface F of the second piston 12, the pressure receiving surface B is centered on the point C. Rocking upward and the working point A clamps the clamp tool 81 downward.

Therefore, the swing from the advance position of the clamp tool 81 to the temporary clamp position is performed by the driving force of the first piston 11, and the clamp tool 81 is moved from the temporary clamp position to the clamp position seen from the clamp position. The swinging is performed by the driving force of the second piston 12.

[Example 7]

13 to 15 show a seventh embodiment. This seventh embodiment changes the above-described first embodiment (see FIGS. 1 to 6) as follows.

A pair of hydraulic pins 86.86 are rotatably supported on the left and right sides of the rear portion of the first piston 11, and the hydraulic pressure surface B is formed on the lower surface of each pin 86. The two hydraulic pressure surfaces B.B are disposed substantially coaxially with the second piston 12 and the clamp state detecting rod 26. In addition, a support groove 87 is formed in the rear portion of the inner circumferential surface of the second piston 12. The semicircular wedge member 88 inserted into the support groove 87 is restricted by rotation by the stop pin 89. A pair of pressing surfaces (F.F) are formed on the left and right upper surfaces of the wedge member (88).

The unclamping drive part D is provided in the middle part of the front-back direction of the said 2nd piston 12, and the unclamping manual part E is provided in the back part of the 1st piston 11. As shown in FIG.

In addition, a spherical groove 91 is formed in the front portion of the first hole 9 of the housing 4, and a support member 92 having a spherical outer circumferential surface formed on the upper portion of the groove 91 is a pin. (93) is supported. The point portion C of the first piston 11 is supported on the inner circumferential surface of the support member 92.

In addition, two limit switches 57.58 for clamp state detection and unclamp state detection are provided side by side in the switch box 56 side by side.

This embodiment can obtain the following advantages.

Since the fluid pressure applied to the second piston 12 from the compressed air in the first operating chamber 21 during the driving of the clamp acts on the vicinity of the axial center of the first piston 11 via the wedge member 88. The transmission efficiency of 100% is obtained, and clamp force is large. In addition, since the pressure receiving surface B is provided upward on both left and right portions of the first piston 11, the thickness of the annular portion of the first piston 11 cannot be measured. For this reason, a strong large diameter spring is adopted for the clamped state holding spring 28, and the clamp force becomes larger by that much.

Further, since the first piston 11 can be prevented from rotating around the shaft center by a pair of left and right pressing surfaces F. F, the rotational deviation of the first piston 11 is small.

Since the hydraulic pin 86 is made of a round bar, its production is easy. In addition, since the hydraulic pin 86 is rotatably supported by the first piston 11, it has a self-aligning function so that the angle shift when the first piston 11 is clamped can be easily shifted. It can be corrected and prevents wobble or uneven wear. Further, since the hydraulic pin 86 has a self-aligning function, it is only necessary to change the angle of the pressing surface F of the wedge member 88 when changing the angle of the wedge machine sum. For this reason, components can be shared between clamp devices of different models.

In addition, the semicircular wedge member 88 has a large outer circumferential surface, so that the surface pressure during clamping is small. This improves the durability of the clamp device.

In each of the above embodiments, the working fluid of the clamping device may be a gaseous body such as nitrogen gas or a liquid such as oil or water, by changing the compressed air. When high pressure oil is used as the working fluid, a strong clamping force can be secured and the hydraulic clamping device can be made compact by the combination of the wedge force action and the lever piston action action of the first piston.

Although the present invention has been described in detail and clearly by the embodiments as described above, these embodiments are not intended to limit the scope of the present invention, but the description and illustration.

Claims (6)

The housing 4 has a first end and a second end, and the first piston 11 for the temporary clamp and the second piston 12 for the present clamp are moved in the housing 4 in both end directions. The first operating chamber 21 is freely installed, and is formed between the second end of the housing 4 and the pistons 11 and 12, and the second operating chamber 22 is the housing 4. It is formed between the first end of the first piston and the second piston 12, the working point (A) is installed on the first end of the first piston (11), the wedge-type hydraulic pressure surface (B) And the unclamping manual portion E is provided at the second end portion of the first piston 11, and the point portion C is located at the middle portion of both ends of the first piston 11 above. It is installed, the wedge-type pressure surface (F) is installed on the second piston (12) above and facing the above-mentioned tongue pressure surface (B) from below, the unclamping driving unit (D) is the second piston (12) ) In the passive part (E) above the second The first swing interval 37 is installed in a space below the first end portion of the first piston 11, and the second swing interval 38 is the first piston 11. Is installed in the upper space of the second end of the first, the sheepskin stone (11) 12 is advanced to the first end side by the fluid pressure of the first operating chamber (21), after which the first state of the advancement state The second piston 12 is advanced to the first end side with respect to the piston 11, and on the contrary, the second piston 12 is interposed by the second piston 12 by the fluid pressure of the second operation chamber 22. Clamping device characterized in that the first piston (11) is configured to be retracted on the second end side. The clamping device according to claim 1, wherein said first piston (11) and said second piston (12) are provided substantially coaxially in said housing (4). 3. The clamping device according to claim 2, wherein said first piston (11) is inserted into said second piston (12). The clamp device according to claim 1, characterized in that the housing (4) is formed such that the first hole for inserting the first piston (9) descends toward the first end side. The support according to claim 1, wherein the first hole (9) for inserting the first piston is formed straight in the housing (4) and the point portion (C) is directly supported on the upper circumferential surface of the first hole (9). Clamping device characterized in that the installation part. The support member (92) is inserted between the point portion (C) and the housing (4), and the support member (92) swings freely in the vertical direction in the housing (4). Clamp device characterized in that.