CN101693301B - Hydraulic power chuck with multi-level adjustable clamping force - Google Patents
Hydraulic power chuck with multi-level adjustable clamping force Download PDFInfo
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- CN101693301B CN101693301B CN2009101533996A CN200910153399A CN101693301B CN 101693301 B CN101693301 B CN 101693301B CN 2009101533996 A CN2009101533996 A CN 2009101533996A CN 200910153399 A CN200910153399 A CN 200910153399A CN 101693301 B CN101693301 B CN 101693301B
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Abstract
The invention discloses a hydraulic power chuck with multi-level adjustable clamping force, which comprises a hydraulic power chuck, a hydraulic power unit and a signal acquisition control system, wherein the hydraulic power unit comprises an oil supply device, an oil-pressure adjusting device, an oil supply direction control device and an oil supply pressure monitoring device; the oil-pressure adjusting device comprises a pilot reducing valve or a pilot overflow valve, an energy accumulator and a plurality of pressure adjusting valve groups; a rotation speed transducer of the signal acquisition control system is installed at a back end part of a lathe main shaft and electrically connected with a controller; and the input electrical signal terminal of a control relay of each pressure adjusting valve group is electrically connected with the controller. In the accelerating and decelerating process of the lathe main shaft, the output oil pressure of the hydraulic power unit and the oil supply pressure of a rotary hydraulic cylinder can be adjusted at levels, the clamping force for keeping the hydraulic power chuck can only change slightly, and when the hydraulic power chuck is used for retaining a finish machining workpiece or a proteiform workpiece, the hydraulic power chuck can realize reliable retaining and high rotary speed, thereby meeting the requirement for high speed cutting and simultaneously having the advantage of low cost.
Description
Technical field
The present invention relates to the clamping device of lathe, specifically relate to the adjustable hydraulic power chuck of a kind of clamping force multi-stage.
Background technology
Hydraulic power chuck is the work piece holder of numerically controlled lathe, is made up of rotating hydraulic cylinder and power chuck.The charge oil pressure of conventional hydraulic power chuck is regulated by manually adjustable pressure-reducing valve or overflow valve, after the initial setting of charge oil pressure, in the process of main axis rotation, keep invariable, rising along with rotating speed, the centrifugal force of claw increases, the clamping force of the outer bowlder of power chuck holding workpiece reduces, and the clamping force loss has limited the raising of hydraulic power chuck rotating speed.
Heightening initial charge oil pressure, increase the initial clamping force of power chuck, allow power chuck still have enough clamping forces under high rotating speed, is a kind of effective ways that improve the hydraulic power chuck rotating speed.But in fine finishining, excessive initial clamping force can be destroyed workpiece surface quality, and the material of easy deformation such as copper, aluminium, engineering plastics can be bad by folder under very big initial clamping force effect.
During hydraulic power chuck holding workpiece endoporus, clamping force increases along with the rising of rotating speed, excessive clamping force can be destroyed the workpiece of fine finishining and easy deformation equally, and low excessively initial charge oil pressure can cause the initial clamping force of power chuck low excessively again, and clamping is unreliable.
In the high-speed turning processing of high speed and precision turning processing and yielding workpiece, how to make the both reliable holding workpiece of hydraulic power chuck, can reach high rotating speed again, be a difficult problem, traditional technical scheme can not solve this difficult problem.Adopt the electric-hydraulic proportion pressure valve can keep clamping force constant to the technology of clamping force step-less adjustment, but the cost height.
Summary of the invention
Therefore the objective of the invention is to propose the adjustable hydraulic power chuck of a kind of clamping force multi-stage, realize that less variation only takes place the clamping force of hydraulic power chuck when lathe spindle rotates.
The technical solution adopted for the present invention to solve the technical problems is:
The present invention includes hydraulic power chuck, by the hydraulic power unit that fueller, hydraulic adjustment device, fuel feeding direction-control apparatus and charge oil pressure monitoring device are formed, signal acquisition control system; Wherein:
1) described hydraulic adjustment device: comprise piloted reducer, accumulator, 2～5 cover pressure-regulating valve groups, every cover pressure-regulating valve group includes overflow valve, bi-bit bi-pass solenoid directional control valve and fixer resistance; The oil-in of piloted reducer links to each other with the high pressure oil-out of fueller, its oil-out links to each other with the high pressure oil-in of the solenoid directional control valve of fuel feeding direction-control apparatus, its oil return opening links to each other with fuel tank, its Long-distance Control mouth links to each other with the oil-in of the first cover pressure-regulating valve group, and the oil-in of accumulator links to each other with the oil-out of piloted reducer;
Or described hydraulic adjustment device: comprise pilot operated compound relief valve, accumulator, 2～5 cover pressure-regulating valve groups, every cover pressure-regulating valve group includes overflow valve, bi-bit bi-pass solenoid directional control valve and fixer resistance; The oil-in of pilot operated compound relief valve links to each other with the high pressure oil-out of fueller and the high pressure oil-in of the solenoid directional control valve of fuel feeding direction-control apparatus, its oil return opening links to each other with fuel tank, its Long-distance Control mouth links to each other with the oil-in of the first cover pressure-regulating valve group, and the oil-in of accumulator links to each other with the oil-in of pilot operated compound relief valve;
The oil-in of first overflow valve of the first cover pressure-regulating valve group links to each other with the oil-in of the oil-in of first fixer resistance with the first cover pressure-regulating valve group, the oil-out of first fixer resistance links to each other with the oil-in of first bi-bit bi-pass solenoid directional control valve, and the oil-out of first bi-bit bi-pass solenoid directional control valve links to each other with the oil-out of first overflow valve and the oil-out of the first cover pressure-regulating valve group; The oil-in of last cover pressure-regulating valve group links to each other with the oil-out of a last cover pressure-regulating valve group, the oil-in of last overflow valve of last cover pressure-regulating valve group links to each other with the oil-in of last fixer resistance and the oil-in of last condom pressure-regulating valve group, the oil-out of last fixer resistance links to each other with the oil-in of last bi-bit bi-pass solenoid directional control valve, the oil-out of last bi-bit bi-pass solenoid directional control valve links to each other with the oil-out of the oil-out of last overflow valve with last cover pressure-regulating valve group, and the oil-out of last cover pressure-regulating valve group links to each other with fuel tank;
2) described signal acquisition control system: comprise controller, rotating speed transmitter and 2～5 cover relays; The rotating speed transmitter is installed in the rearward end of lathe spindle, and its signal of telecommunication end is electrically connected with controller; The output signal of telecommunication end of every cover relay is electrically connected with the signal of telecommunication end of bi-bit bi-pass solenoid directional control valve separately, and the input electrical signal end of every cover relay is electrically connected with controller respectively.
Setting pressure transmitter on the high pressure oil-in of the solenoid directional control valve of described fuel feeding direction-control apparatus, the signal of telecommunication end of pressure transmitter is electrically connected with controller.
Described piloted reducer is pilot-type two-port pressure-reducing valve or pilot-operated type three-way pressure reducing valve.
The beneficial effect that the present invention has is:
In the process of lathe spindle acceleration and deceleration, the charge oil pressure that grade output oil pressure of adjusting hydraulic power unit and rotating hydraulic cylinder can be arranged, keep the clamping force of hydraulic power chuck that less variation only takes place, when clamping finishing workpiece or yielding workpiece, can realize reliable clamping, can realize high rotating speed again, satisfy the requirement of high-speed cutting; Has the low advantage of cost simultaneously.
Description of drawings
Fig. 1 is a kind of structural principle schematic diagram of the present invention;
Fig. 2 is an another kind of structural principle schematic diagram of the present invention;
Fig. 3 is the comparison diagram of clamping force of the present invention and lathe spindle rotation speed relation and background technology;
Among the figure: 1. workpiece, 2. claw, 3. power chuck, 4. lathe spindle, 5. trombone slide, 6. counter flange, 7. rotating hydraulic cylinder, 8. oil return cover, 9. support, 10. controller, 11. fuel tanks, 12. filters, 13. variable pump, 14. motors, 15. Pressure gauges, 16. check valve, 17. accurate filters, 18. piloted reducers, 19. accumulator, 20. Pressure gauges, 21. two-position four-way solenoid directional control valves, 21a, 21b. coil, 22,23. pressure switch, 24,25,26. overflow valve, 27,28,29. the fixer resistance, 30,31,32. the bi-bit bi-pass solenoid directional control valve, 33,34,35. relay, 36, the rotating speed transmitter, 37. pressure transmitters, 18 '. pilot operated compound relief valve.
The specific embodiment
By the invention will be further described by drawings and Examples.
First embodiment of the present invention the present invention includes hydraulic power chuck as shown in Figure 1, by the hydraulic power unit that fueller, hydraulic adjustment device, fuel feeding direction-control apparatus, charge oil pressure monitoring device are formed, signal acquisition control system.
Hydraulic power chuck is made up of power chuck 3 and rotating hydraulic cylinder 7, power chuck 3 links to each other with the front end of lathe spindle 4, rotating hydraulic cylinder 7 links to each other with the tail end of lathe spindle 4 by counter flange 6, the two ends of trombone slide 5 link to each other with the piston rod of rotating hydraulic cylinder 7 and the wedge-catch system of power chuck 3 respectively, rotating hydraulic cylinder 7 drives power chuck 3 clampings or unclamps workpiece 1 by trombone slide 5, the cylinder body of rotating hydraulic cylinder 7 and piston rod are with lathe spindle 3 rotations, and the oil return cover 8 of rotating hydraulic cylinder 7 is fixed on the body of lathe bed by support 9.
The fueller of hydraulic power unit comprises fuel tank 11, filter 12, hydraulic pump 13, motor 14, Pressure gauge 15, includes the accurate filter 17 of check valve 16, the hydraulic pump 13 of hydraulic power unit is under the driving of motor 14, from 12 oil suctions of fuel tank 11 process filters, the hydraulic oil of hydraulic pump 13 outputs outputs to the high pressure oil-out of fueller after accurate filter 17 filters, Pressure gauge 15 is measured the outlet pressure of hydraulic pump.
The hydraulic adjustment device of hydraulic power unit comprises piloted reducer 18, accumulator 19,3 cover pressure-regulating valve groups, and every cover pressure-regulating valve group comprises overflow valve, bi-bit bi-pass solenoid directional control valve and fixer resistance; The oil-in of piloted reducer 18 links to each other with the high pressure oil-out of fueller, its oil-out links to each other with the high pressure oil-in of the solenoid directional control valve 21 of fuel feeding direction-control apparatus, its oil return opening links to each other with fuel tank 11, its Long-distance Control mouth links to each other with the oil-in of the first cover pressure-regulating valve group, and the oil-in of accumulator 19 links to each other with the oil-out of piloted reducer 18.
The oil-in of first overflow valve 24 of the first cover pressure-regulating valve group links to each other with the oil-in of the oil-in of first fixer resistance 27 with the first cover pressure-regulating valve group, the oil-out of first fixer resistance 27 links to each other with the oil-in of first bi-bit bi-pass solenoid directional control valve 30, and the oil-out of first bi-bit bi-pass solenoid directional control valve 30 links to each other with the oil-out of first overflow valve 24 and the oil-out of the first cover pressure-regulating valve group.
The oil-in of the second cover pressure-regulating valve group links to each other with the oil-out of the first cover pressure-regulating valve group, the oil-in of second overflow valve 25 of the second cover pressure-regulating valve group links to each other with the oil-in of the oil-in of second fixer resistance 28 with the second cover pressure-regulating valve group, the oil-out of second fixer resistance 28 links to each other with the oil-in of second bi-bit bi-pass solenoid directional control valve 31, and the oil-out of second bi-bit bi-pass solenoid directional control valve 31 links to each other with the oil-out of second overflow valve 25 and the oil-out of the second cover pressure-regulating valve group.
The oil-in of the 3rd cover pressure-regulating valve group links to each other with the oil-out of the second cover pressure-regulating valve group, the oil-in of the 3rd overflow valve 26 of the 3rd cover pressure-regulating valve group links to each other with the oil-in of the oil-in of the 3rd fixer resistance 29 with the 3rd cover pressure-regulating valve group, the oil-out of the 3rd fixer resistance 29 links to each other with the oil-in of the 3rd bi-bit bi-pass solenoid directional control valve 32, the oil-out of the 3rd bi-bit bi-pass solenoid directional control valve 32 links to each other with the oil-out of the 3rd overflow valve 26 and the oil-out of the 3rd cover pressure-regulating valve group, and the oil-out of the 3rd cover pressure-regulating valve group links to each other with fuel tank.
The fuel feeding direction-control apparatus of hydraulic power unit is a solenoid directional control valve 21, its high pressure oil-in links to each other with the oil-in of piloted reducer 18, its oil return opening links to each other with fuel tank 11, two output oil ports of solenoid directional control valve 21 link to each other with two oil inlet and outlets of rotating hydraulic cylinder respectively, solenoid directional control valve 21 changes the piston direction of motion that fluid flows to control rotating hydraulic cylinder 7 by control coil 21a, 21b, and Pressure gauge 20 is measured the high pressure oil-in pressure of solenoid directional control valve 21; The charge oil pressure monitoring device of hydraulic power unit is pressure switch 22 and 23, and they link to each other with two output oil ports of solenoid directional control valve 21 respectively, and whether the output oil pressure of monitoring hydraulic power unit is higher than the minimum charge oil pressure that rotating hydraulic cylinder 7 requires.
Signal acquisition control system comprises controller 10 (controller can adopt single-chip microcomputer, DSP, PLC controller or industrial computer), rotating speed transmitter 26, pressure transmitter 25 and three cover relays 33,34 and 35; Rotating speed transmitter 26 is installed in the rearward end of lathe spindle 4, its signal of telecommunication end is electrically connected with controller 10, pressure transmitter 25 is installed on the high pressure oil-in of solenoid directional control valve 21 of fuel feeding direction-control apparatus, the signal of telecommunication end of pressure transmitter 25 is electrically connected with controller 10, first relay 33, the output signal of telecommunication end of second relay 34 and the 3rd relay 35 respectively with first bi-bit bi-pass solenoid directional control valve 30, the signal of telecommunication end of second bi-bit bi-pass solenoid directional control valve 31 and the 3rd bi-bit bi-pass solenoid directional control valve 32 is electrically connected, three cover relays 33,34 and 35 input electrical signal end is electrically connected with controller (10) respectively.
As Fig. 1, shown in Figure 3, three overflow valves of initial adjustment 24,25,26 make the oil inlet and outlet pressure reduction of first overflow valve 24, second overflow valve 25, the 3rd overflow valve 26 be respectively 2MPa, 1MPa and 0.5MPa.After hydraulic pump 13 work, three bi-bit bi-pass solenoid directional control valves 30,31,32 all are operated in position, a left side, piloted reducer 18 outputs are near zero minimum pressure, controller 10 output control signals are operated in right position through first bi-bit bi-pass solenoid directional control valve 30 commutations of relay 33 controls, piloted reducer 18 output pressure 2MPa, the coil 21b energising of two-position four-way solenoid directional control valve 21, coil 21a dead electricity, 21 commutations of two-position four-way solenoid directional control valve are operated in right position, hydraulic oil enters the right chamber of rotating hydraulic cylinder 7, piston rod drives the periphery of power chuck 3 clamping work pieces 1 left, and clamping force is F
0After lathe spindle 4 begins rotation, the speed of mainshaft that rotating speed transmitter 26 records feeds back to controller 10, rising along with lathe spindle 4 rotating speeds, because of claw 2 suffered centrifugal force increase, the clamping force of power chuck 3 reduces, when the rotating speed of lathe spindle 4 is elevated to 2000rpm, controller 10 output control signals are operated in right position through 32 commutations of the 3rd bi-bit bi-pass solenoid directional control valve of the 3rd relay 35 controls, piloted reducer 18 output pressure 2.5MPa, the clamping force of power chuck 3 returns to initial clamping force F
0When the rotating speed of lathe spindle 4 is elevated to 3500rpm, controller 10 output control signals are operated in right position through 31 commutations of second bi-bit bi-pass solenoid directional control valve of second relay, 34 controls, export control signal simultaneously and be operated in position, a left side through 32 commutations of the 3rd bi-bit bi-pass solenoid directional control valve of the 3rd relay 35 controls, piloted reducer 18 output pressure 3MPa, the clamping force of power chuck 3 returns to initial clamping force F again
0When the rotating speed of lathe spindle 4 is elevated to 4500rpm, controller 10 output control signals are operated in right position through 32 commutations of the 3rd bi-bit bi-pass solenoid directional control valve of the 3rd relay 35 controls, piloted reducer 18 output pressure 3.5MPa, the clamping force of power chuck 3 returns to initial clamping force F once more
0In whole boosting velocity procedure, the clamping force of power chuck 3 only changes in small range.Fixer resistance 27,28,29 and accumulator 19 play pressure stabilization function when pressure switches.The signal of telecommunication end of pressure transmitter 25 feeds back to controller 10, when the pressure switching needs two bi-bit bi-pass solenoid directional control valves of control to commutate simultaneously, utilize switching time poor of two solenoid directional control valves of the accurate control of signal of pressure transmitter 25, make the variation of oil-out pressure of piloted reducer 18 more steady, pressure switches more reliable.
After workpiece 1 machining finishes, lathe spindle 4 beginning reductions of speed, along with the reduction of lathe spindle 4 rotating speeds, because of claw 2 suffered centrifugal force reduce, the clamping force of power chuck 3 increases.The speed drop of lathe spindle 4 is during to 4500rpm, and the clamping force of power chuck 3 increases to F
0, controller 10 output control signals are operated in position, a left side through 32 commutations of the 3rd bi-bit bi-pass solenoid directional control valve of the 3rd relay 35 controls, and piloted reducer 18 output pressures are reduced to 3MPa; The speed drop of lathe spindle 4 is during to 3500rpm, and the clamping force of power chuck 3 increases to F again
0Controller 10 output control signals are operated in position, a left side through 31 commutations of second bi-bit bi-pass solenoid directional control valve of second relay, 34 controls, export control signal simultaneously and be operated in right position through 32 commutations of the 3rd bi-bit bi-pass solenoid directional control valve of the 3rd relay 35 controls, piloted reducer 18 output pressures are reduced to 2.5MPa; The speed drop of lathe spindle 4 is during to 2000rpm, and the clamping force of power chuck 3 increases once more likes F
0, controller 10 output control signals are operated in position, a left side through 32 commutations of the 3rd bi-bit bi-pass solenoid directional control valve of the 3rd relay 35 controls, and piloted reducer 18 output pressures are reduced to 2MPa; In whole reduction of speed process, the variation of the clamping force of power chuck 3 is limited in the small range; After lathe spindle 4 stops the rotation, the coil 21a energising of two-position four-way solenoid directional control valve 21, coil 21b dead electricity, 21 commutations of two-position four-way solenoid directional control valve, the high-voltage oil liquid of hydraulic power unit output enters the left chamber of rotating hydraulic cylinder 7, and rotating hydraulic cylinder 7 drives power chuck 3 and unclamps bar-shaped workpieces 1.
During the endoporus of power chuck 3 clamp circle disk shape workpiece, the coil 21a energising of solenoid directional control valve 21, coil 21b dead electricity, the high-voltage oil liquid of hydraulic power unit output enters the left chamber of rotating hydraulic cylinder 7, and rotating hydraulic cylinder 7 drives the endoporus that power chuck 3 clamps round-disk shape workpiece.When the rotating speed of lathe spindle 4 raises, because of claw 2 suffered centrifugal force increase, the clamping force of power chuck 3 increases, and three bi-bit bi-pass solenoid directional control valves of controller 10 output signals control make the output pressure of piloted reducer turn down successively from 2MPa and are 1.5MPa, 1MPa, 0.5MPa; When the rotating speed of lathe spindle 4 reduces, three bi-bit bi-pass solenoid directional control valves of controller 10 output signals control, the output pressure of piloted reducer is raise successively from 0.5MPa be 1MPa, 1.5MPa, 2MPa, in the process of the raising speed of lathe spindle 4 and reduction of speed, the variation of the clamping force of power chuck 3 is limited in the small range all the time.After lathe spindle 4 stops the rotation, the coil 21b of solenoid directional control valve 21 energising, coil 21a dead electricity, solenoid directional control valve 21 commutations, the high-voltage oil liquid of hydraulic power unit output enters the right chamber of rotating hydraulic cylinder 7, and rotating hydraulic cylinder 7 drives power chuck 3 and unclamps disk type work.
Second embodiment of the present invention as shown in Figure 2, the hydraulic adjustment device of hydraulic power unit comprises pilot operated compound relief valve 18 ', accumulator 19,2～5 cover pressure-regulating valve groups, and every cover pressure-regulating valve group includes overflow valve, bi-bit bi-pass solenoid directional control valve and fixer resistance; The high pressure oil-in of the high pressure oil-out of the oil-in of pilot operated compound relief valve 18 ' and fueller and the solenoid directional control valve 21 of fuel feeding direction-control apparatus links to each other, its oil return opening links to each other with fuel tank 11, its Long-distance Control mouth links to each other with the oil-in of the first cover pressure-regulating valve group, and the oil-in of accumulator 19 links to each other with the oil-in of pilot operated compound relief valve 18 '.Controller 10 output control signals are through three bi-bit bi-pass solenoid directional control valves 24,25,26 of three cover relays, 33,34,35 controls, regulate the oil-in pressure of pilot operated compound relief valve 18 ' and the oil liquid pressure in rotating hydraulic cylinder 7 chambeies, keep the clamping force of power chuck 3 only in small range, to change.
Claims (3)
1. the hydraulic power chuck that clamping force multi-stage is adjustable comprises hydraulic power chuck, by the hydraulic power unit that fueller, hydraulic adjustment device, fuel feeding direction-control apparatus and charge oil pressure monitoring device are formed, signal acquisition control system; It is characterized in that:
1) described hydraulic adjustment device: comprise piloted reducer (18), accumulator (19), 2～5 cover pressure-regulating valve groups, every cover pressure-regulating valve group includes overflow valve, bi-bit bi-pass solenoid directional control valve and fixer resistance; The oil-in of piloted reducer (18) links to each other with the high pressure oil-out of fueller, the oil-out of described piloted reducer (18) links to each other with the high pressure oil-in of the solenoid directional control valve (21) of fuel feeding direction-control apparatus, the oil return opening of described piloted reducer (18) links to each other with fuel tank (11), the Long-distance Control mouth of described piloted reducer (18) links to each other with the oil-in of the first cover pressure-regulating valve group, and the oil-in of described accumulator (19) links to each other with the oil-out of described piloted reducer (18);
Or described hydraulic adjustment device: comprise pilot operated compound relief valve (18 '), accumulator (19), 2～5 cover pressure-regulating valve groups, every cover pressure-regulating valve group includes overflow valve, bi-bit bi-pass solenoid directional control valve and fixer resistance; The high pressure oil-in of the high pressure oil-out of the oil-in of pilot operated compound relief valve (18 ') and fueller and the solenoid directional control valve (21) of fuel feeding direction-control apparatus links to each other, the oil return opening of described pilot operated compound relief valve (18 ') links to each other with fuel tank (11), the Long-distance Control mouth of described pilot operated compound relief valve (18 ') links to each other with the oil-in of the first cover pressure-regulating valve group, and the oil-in of described accumulator (19) links to each other with the oil-in of described pilot operated compound relief valve (18 ');
The oil-in of the overflow valve in every suit pressure-regulating valve group all links to each other with the oil-in of this cover pressure-regulating valve group with the oil-in of fixer resistance, the oil-out of the fixer resistance of every suit pressure-regulating valve group links to each other with the oil-in of the bi-bit bi-pass solenoid directional control valve of this cover pressure-regulating valve group, and the oil-out of the bi-bit bi-pass solenoid directional control valve in every suit pressure-regulating valve group all links to each other with the oil-out of this cover pressure-regulating valve group with the oil-out of overflow valve; Except that the first cover pressure-regulating valve group, all the other oil-ins that respectively overlap the pressure-regulating valve group link to each other with an oil-out that overlaps the pressure-regulating valve group on it, and oil-out of last cover pressure-regulating valve group links to each other with fuel tank;
2) described signal acquisition control system: comprise controller (10), rotating speed transmitter (36) and 2～5 cover relays; Rotating speed transmitter (36) is installed in the rearward end of lathe spindle (4), and the signal of telecommunication end of described rotating speed transmitter (36) is electrically connected with controller (10); The output signal of telecommunication end of every cover relay is electrically connected with the signal of telecommunication end of the bi-bit bi-pass solenoid directional control valve of corresponding pressure-regulating valve group, and the input electrical signal end of every cover relay is electrically connected with described controller (10) respectively.
2. the adjustable hydraulic power chuck of a kind of clamping force multi-stage according to claim 1, it is characterized in that: setting pressure transmitter (37) on the high pressure oil-in of the solenoid directional control valve of described fuel feeding direction-control apparatus (21), the signal of telecommunication end of pressure transmitter (37) is electrically connected with controller (10).
3. the adjustable hydraulic power chuck of a kind of clamping force multi-stage according to claim 1 and 2 is characterized in that: described piloted reducer (18) is pilot-type two-port pressure-reducing valve or pilot-operated type three-way pressure reducing valve.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2009101533996A CN101693301B (en) | 2009-10-22 | 2009-10-22 | Hydraulic power chuck with multi-level adjustable clamping force |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2009101533996A CN101693301B (en) | 2009-10-22 | 2009-10-22 | Hydraulic power chuck with multi-level adjustable clamping force |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101693301A CN101693301A (en) | 2010-04-14 |
| CN101693301B true CN101693301B (en) | 2011-01-05 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN2009101533996A Expired - Fee Related CN101693301B (en) | 2009-10-22 | 2009-10-22 | Hydraulic power chuck with multi-level adjustable clamping force |
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| CN (1) | CN101693301B (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN106392114B (en) * | 2016-12-12 | 2018-01-30 | 山东交通职业学院 | A kind of lathe chuck with velocity modulation section clamping force |
| CN107457578A (en) * | 2017-08-21 | 2017-12-12 | 哈尔滨理工大学 | A kind of heart pump processes automatic clamping device |
| CN111120456B (en) * | 2019-12-30 | 2020-12-08 | 浙江大学 | Material increase manufacturing hydraulic flow channel on-way pressure loss testing device |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN86210593U (en) * | 1986-12-30 | 1987-10-07 | 首都钢铁公司 | Drawing and releasing device for steel cable control |
| CN2040414U (en) * | 1988-11-08 | 1989-07-05 | 张国 | Dual purpose means of hydraulic scroll chuck and vice |
| EP0995527A1 (en) * | 1998-10-23 | 2000-04-26 | Gamet Precision | Process to control the clamping and unclamping of an hydraulicly controlled chuck |
| CN2778442Y (en) * | 2004-12-29 | 2006-05-10 | 大连机床集团有限责任公司 | Fastening force control device for NC lathe chuck |
| DE202006015097U1 (en) * | 2006-10-02 | 2006-11-23 | Deckel Maho Pfronten Gmbh | Clamping device for machine tools includes hydraulic tensioning cylinder for clamping jaws associated with pressure sensors to monitor and ultimately identify tensioning state of jaws |
-
2009
- 2009-10-22 CN CN2009101533996A patent/CN101693301B/en not_active Expired - Fee Related
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN86210593U (en) * | 1986-12-30 | 1987-10-07 | 首都钢铁公司 | Drawing and releasing device for steel cable control |
| CN2040414U (en) * | 1988-11-08 | 1989-07-05 | 张国 | Dual purpose means of hydraulic scroll chuck and vice |
| EP0995527A1 (en) * | 1998-10-23 | 2000-04-26 | Gamet Precision | Process to control the clamping and unclamping of an hydraulicly controlled chuck |
| CN2778442Y (en) * | 2004-12-29 | 2006-05-10 | 大连机床集团有限责任公司 | Fastening force control device for NC lathe chuck |
| DE202006015097U1 (en) * | 2006-10-02 | 2006-11-23 | Deckel Maho Pfronten Gmbh | Clamping device for machine tools includes hydraulic tensioning cylinder for clamping jaws associated with pressure sensors to monitor and ultimately identify tensioning state of jaws |
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| Publication number | Publication date |
|---|---|
| CN101693301A (en) | 2010-04-14 |
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