CN101695764B - Clamping force multi-stage regulating device of hydraulic power chuck with hydraulic lock - Google Patents
Clamping force multi-stage regulating device of hydraulic power chuck with hydraulic lock Download PDFInfo
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- CN101695764B CN101695764B CN2009101532298A CN200910153229A CN101695764B CN 101695764 B CN101695764 B CN 101695764B CN 2009101532298 A CN2009101532298 A CN 2009101532298A CN 200910153229 A CN200910153229 A CN 200910153229A CN 101695764 B CN101695764 B CN 101695764B
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- 230000001105 regulatory effect Effects 0.000 title claims abstract description 15
- 238000012806 monitoring device Methods 0.000 claims abstract description 8
- 239000003638 chemical reducing agent Substances 0.000 claims description 42
- 239000002828 fuel tank Substances 0.000 claims description 29
- 230000009467 reduction Effects 0.000 claims description 17
- 230000001133 acceleration Effects 0.000 abstract description 2
- 239000003921 oil Substances 0.000 description 40
- 210000000078 claw Anatomy 0.000 description 6
- 238000000034 method Methods 0.000 description 5
- 230000000630 rising effect Effects 0.000 description 4
- 238000004880 explosion Methods 0.000 description 3
- 239000010720 hydraulic oil Substances 0.000 description 3
- 238000010586 diagram Methods 0.000 description 2
- RYGMFSIKBFXOCR-UHFFFAOYSA-N Copper Chemical compound [Cu] RYGMFSIKBFXOCR-UHFFFAOYSA-N 0.000 description 1
- 239000004411 aluminium Substances 0.000 description 1
- XAGFODPZIPBFFR-UHFFFAOYSA-N aluminium Chemical compound [Al] XAGFODPZIPBFFR-UHFFFAOYSA-N 0.000 description 1
- 229910052782 aluminium Inorganic materials 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 239000010949 copper Substances 0.000 description 1
- 229910052802 copper Inorganic materials 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 229920006351 engineering plastic Polymers 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 238000003754 machining Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 230000006641 stabilisation Effects 0.000 description 1
- 238000011105 stabilization Methods 0.000 description 1
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Abstract
The invention discloses a clamping force multi-stage regulating device of a hydraulic power chuck with a hydraulic lock, which comprises the hydraulic power chuck with the hydraulic lock, a hydraulic pump station and a signal acquisition control system, wherein the hydraulic pump station comprises an oil supply device and an oil pressure adjusting and monitoring device, the oil pressure adjusting and monitoring device comprises two pilot-operated reducing valves, two energy accumulators, two safety valves, two two-position three-way electromagnetic directional valves, two pressure difference relays and two pressure regulating valve groups, wherein each set of pressure multi-stage regulating valves all comprise 2-5 sets of pressure valve groups; the signal acquisition control system comprises a controller, a rotating speed transducer and three sets of relay groups, wherein the rotating speed transducer is arranged at the rear end part of a lathe spindle. During the acceleration and the moderation of the spindle, the output oil pressure of the hydraulic pump station and the oil supply pressure of a rotating hydraulic cylinder can be adjusted in a step way, the clamping force of the hydraulic power chuck can be kept to change a little; when a workpiece is clamped, the invention can not only realize reliable clamping, but also can realize high rotating speed and meet the requirement of high-speed cutting; in addition, the clamping force multi-stage regulating device has low hardware cost.
Description
Technical field
The present invention relates to the clamping device of lathe, specifically relate to a kind of clamping force multi-stage regulating device of the hydraulic power chuck with hydraulic lock.
Background technology
The hydraulic power chuck of band hydraulic lock is the work piece holder of numerically controlled lathe, is made up of the rotating hydraulic cylinder and the power chuck of band hydraulic lock.The rotating hydraulic cylinder inside of band hydraulic lock carries the hydraulic lock of being made up of two hydraulic control one-way valves, and when the output oil feed line explosion of hydraulic power unit, hydraulic lock is to the rotating hydraulic cylinder pressurize of band hydraulic lock.The charge oil pressure of the rotating hydraulic cylinder of band hydraulic lock 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.
Improving the initial charge oil pressure of the rotating hydraulic cylinder of band hydraulic lock, 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 of band hydraulic lock.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.When being with the hydraulic power chuck holding workpiece endoporus of hydraulic lock, 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 of band hydraulic lock, can reach high rotating speed again, be a difficult problem.The clamping force of the hydraulic power chuck of the band hydraulic lock of employing electric-hydraulic proportion pressure valve control keeps constant when the lathe spindle speed change, but the hardware cost height.
Summary of the invention
Therefore the objective of the invention is to propose a kind of clamping force multi-stage regulating device of the hydraulic power chuck with hydraulic lock, less variation only takes place in the clamping force of the hydraulic power chuck of band hydraulic lock when lathe spindle rotates.
The technical solution adopted for the present invention to solve the technical problems is:
Comprise the hydraulic power chuck of being with hydraulic lock, regulate the hydraulic power unit that monitoring device is formed, signal acquisition control system by fueller, oil pressure; Wherein:
1) described oil pressure is regulated monitoring device: comprise two piloted reducers, two accumulators, two safety valves, two two-position three way solenoid directional control valves, two multistage control valve groups of pressure that the pressure reduction relay is identical with two nested structures, the multistage control valve group of every cover pressure includes 2～5 cover pressure valve groups, and every cover pressure valve group includes overflow valve, bi-bit bi-pass solenoid directional control valve and fixer resistance.
The oil-in of first 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 first two-position three way solenoid directional control valve and the oil-in of first accumulator, its oil return opening is connected with fuel tank, its Long-distance Control mouth links to each other with the oil-in of the multistage control valve group of the first cover pressure, the oil-in of first safety valve links to each other with the oil-out of first piloted reducer, the oil-out of first safety valve links to each other with fuel tank, the oil return opening of first two-position three way solenoid directional control valve links to each other with fuel tank, and the output oil port of first two-position three way solenoid directional control valve links to each other with first oil inlet and outlet of the rotating hydraulic cylinder of band hydraulic lock;
The oil-in of second 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 second two-position three way solenoid directional control valve and the oil-in of second accumulator, its oil return opening is connected with fuel tank, its Long-distance Control mouth links to each other with the oil-in of the multistage control valve group of the second cover pressure, the oil-in of second safety valve links to each other with the oil-out of second piloted reducer, the oil-out of second safety valve links to each other with fuel tank, the oil return opening of second two-position three way solenoid directional control valve links to each other with fuel tank, and the output oil port of second two-position three way solenoid directional control valve links to each other with second oil inlet and outlet of the rotating hydraulic cylinder of band hydraulic lock.
The oil-in of the multistage control valve group of two cover pressure links to each other with first oil-in that overlaps the pressure valve group separately, the oil-in of first overflow valve of the first cover pressure valve group links to each other with the oil-in of first fixer resistance separately, 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 separately, and the oil-out of first bi-bit bi-pass solenoid directional control valve is with the oil-out and first oil-out that overlaps the pressure valve group of first overflow valve link to each other separately; The oil-in of last cover pressure valve group links to each other with the oil-out of going up a cover pressure valve group separately, the oil-in of last overflow valve of last cover pressure valve group links to each other with the oil-in of the oil-in of last fixer resistance separately with last cover pressure 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 separately, the oil-out of last bi-bit bi-pass solenoid directional control valve is with the oil-out of last overflow valve and the oil-out of last cover pressure valve group link to each other separately, the oil-out of last cover pressure valve group links to each other with the oil-out of the multistage control valve group of pressure separately, and two oil-outs that overlap the multistage control valve group of pressure link to each other with fuel tank;
The high pressure oil-in of the first pressure reduction relay links to each other with the oil-out of first two-position three way solenoid directional control valve, and its low pressure oil-in links to each other with the oil-out of second two-position three way solenoid directional control valve; The high pressure oil-in of the second pressure reduction relay links to each other with the oil-out of second two-position three way solenoid directional control valve, and its low pressure oil-in links to each other with the oil-out of first two-position three way solenoid directional control valve.
2) described signal acquisition control system: comprise controller, rotating speed transmitter and three cover relay groups, first cover and the second cover relay group include 2～5 relays, and the 3rd cover relay group comprises two 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 each relay of first cover and the second cover relay group, overlap the signal of telecommunication end electrical connection of bi-bit bi-pass solenoid directional control valve corresponding in the multistage control valve group of pressure respectively with first cover and second, the output signal of telecommunication end of first relay of the 3rd cover relay group is electrically connected with the signal of telecommunication end of first two-position three way solenoid directional control valve, the output signal of telecommunication end of second relay of the 3rd cover relay group is electrically connected with the signal of telecommunication end of second two-position three way solenoid directional control valve, and the input electrical signal end of each relay is electrically connected with controller respectively.
First pressure transmitter is installed on the oil-out of described first piloted reducer, second pressure transmitter is installed on the oil-out of second piloted reducer, the signal of telecommunication end of first pressure transmitter and second pressure transmitter is electrically connected with controller respectively.
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 hardware cost simultaneously.
Description of drawings
Fig. 1 is the structural principle schematic diagram of first embodiment of the invention.
Fig. 2 is the structural principle schematic diagram of second embodiment of the invention.
Fig. 3 is clamping force, charge oil pressure and the lathe spindle rotation speed relation figure of first embodiment of the invention.
Among the figure: 1. bar-shaped workpieces, 2. claw, 3. power chuck, 4. lathe spindle, 5. trombone slide, 6. counter flange, 7. rotating hydraulic cylinder, 8. hydraulic lock, 9. oil return cover, 10. support, 11. fuel tanks, 12. filters, 13. variable pump, 14. motors, 15. Pressure gauges, 16. check valve, 17. accurate filters, 18,19. piloted reducer, 20,21. accumulator, 22,23. Pressure gauge, 24,25. safety valve, 26,27. the two-position three way solenoid directional control valve, 28,29. the pressure reduction relay, 30,31. relay, 32,33,34,53,54,55. overflow valve, 35,36,37,50,51,52. the fixer resistance, 38,39,40,47,48,49. the bi-bit bi-pass solenoid directional control valve, 41,42,43,44,45,46. relay, 56. controller, 57. the rotating speed transmitter, 58,59. pressure transmitter, 1 '. disk type work.
The specific embodiment
The invention will be further described by drawings and Examples.
First embodiment of the present invention the present invention includes the hydraulic power chuck of band hydraulic lock as shown in Figure 1, regulates the hydraulic power unit that monitoring device is formed, signal acquisition control system by fueller, oil pressure.
The hydraulic power chuck of band hydraulic lock is made up of the rotating hydraulic cylinder 7 of power chuck 3 and band hydraulic lock, the inside of the rotating hydraulic cylinder 7 of band hydraulic lock carries the hydraulic lock of being made up of two hydraulic control one-way valves 8, power chuck 3 links to each other with the front end of lathe spindle 4, the rotating hydraulic cylinder 7 of band hydraulic lock 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 the rotating hydraulic cylinder 7 of being with hydraulic lock and the wedge-catch system of power chuck 3 respectively, the rotating hydraulic cylinder 7 of band hydraulic lock drives power chuck 3 clampings or unclamps bar-shaped workpieces 1 by trombone slide 5, the cylinder body of the rotating hydraulic cylinder 7 of band hydraulic lock and piston rod are with lathe spindle 3 rotations, and the oil return cover 9 of the rotating hydraulic cylinder 7 of band hydraulic lock is fixed on the body of lathe bed by support 10.
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 oil pressure of hydraulic power unit is regulated monitoring device and is comprised the multistage control valve group of pressure that two piloted reducers 18 are identical with 29, two nested structures with 25, two two-position three way solenoid directional control valves 26 and 27, two pressure reduction relays 28 with 19, two accumulators 20 and 21, two safety valves 24, the multistage control valve group of every cover pressure includes 3 cover pressure valve groups, and every cover pressure valve group includes overflow valve, bi-bit bi-pass solenoid directional control valve and fixer resistance;
The oil-in of first 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 first two-position three way solenoid directional control valve 26 and the oil-in of first accumulator 20, its oil return opening is connected with fuel tank 11, its Long-distance Control mouth links to each other with the oil-in of the multistage control valve group of the first cover pressure, the oil-in of first safety valve 24 links to each other with the oil-out of first piloted reducer 18, the oil-out of first safety valve 24 links to each other with fuel tank 11, the oil return opening of first two-position three way solenoid directional control valve 26 links to each other with fuel tank 11, and the output oil port of first two-position three way solenoid directional control valve 26 links to each other with first oil inlet and outlet of the rotating hydraulic cylinder 7 of band hydraulic lock.
The oil-in of the multistage control valve group of the first cover pressure links to each other with the oil-in of its first cover pressure valve group, the oil-in of first overflow valve 32 of the first cover pressure valve group links to each other with the oil-in of first fixer resistance 35, the oil-out of first fixer resistance 35 links to each other with the oil-in of first bi-bit bi-pass solenoid directional control valve 38, and the oil-out of first bi-bit bi-pass solenoid directional control valve 38 links to each other with the oil-out of first overflow valve 32 and the oil-out of the first cover pressure valve group.
The oil-in of the second cover pressure valve group of the multistage control valve group of the first cover pressure links to each other with the oil-out of the first cover pressure valve group, the oil-in of second overflow valve 33 of the second cover pressure valve group links to each other with the oil-in of the oil-in of second fixer resistance 36 with the second cover pressure valve group, the oil-out of second fixer resistance 36 links to each other with the oil-in of second bi-bit bi-pass solenoid directional control valve 39, and the oil-out of second bi-bit bi-pass solenoid directional control valve 39 links to each other with the oil-out of second overflow valve 33 and the oil-out of the second cover pressure valve group.
The oil-in of the 3rd cover pressure valve group of the multistage control valve group of the first cover pressure links to each other with the oil-out of the second cover pressure valve group, the oil-in of the 3rd overflow valve 34 of the 3rd cover pressure valve group links to each other with the oil-in of the oil-in of the 3rd fixer resistance 37 with the 3rd cover pressure valve group, the oil-out of the 3rd fixer resistance 37 links to each other with the oil-in of the 3rd bi-bit bi-pass solenoid directional control valve 40, the oil-out of the 3rd bi-bit bi-pass solenoid directional control valve 40 links to each other with the oil-out of the 3rd overflow valve 34 and the oil-out of the 3rd cover pressure valve group, the oil-out of the 3rd cover pressure valve group links to each other with the oil-out of the multistage control valve group of the first cover pressure, and the oil-out of the multistage control valve group of the first cover pressure links to each other with fuel tank.
The oil-in of second piloted reducer 19 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 second two-position three way solenoid directional control valve 27 and the oil-in of second accumulator 21, its oil return opening is connected with fuel tank 11, its Long-distance Control mouth links to each other with the oil-in of the multistage control valve group of the second cover pressure, the oil-in of second safety valve 25 links to each other with the oil-out of second piloted reducer 19, the oil-out of second safety valve 25 links to each other with fuel tank 11, the oil return opening of second two-position three way solenoid directional control valve 27 links to each other with fuel tank 11, and the output oil port of second two-position three way solenoid directional control valve 27 links to each other with second oil inlet and outlet of the rotating hydraulic cylinder 7 of band hydraulic lock.
The oil-in of the multistage control valve group of the second cover pressure links to each other with the oil-in of quadruplet pressure valve group, the oil-in of the 4th overflow valve 53 of quadruplet pressure valve group links to each other with the oil-in of the 4th fixer resistance 50, the oil-out of the 4th fixer resistance 50 links to each other with the oil-in of the 4th bi-bit bi-pass solenoid directional control valve 47, and the oil-out of the 4th bi-bit bi-pass solenoid directional control valve 47 links to each other with the oil-out of the oil-out of the 4th overflow valve 53 and quadruplet pressure valve group.
The oil-in of the 5th cover pressure valve group of the multistage control valve group of the second cover pressure links to each other with the oil-out of quadruplet pressure valve group, the oil-in of the 5th overflow valve 54 of the 5th cover pressure valve group links to each other with the oil-in of the oil-in of the 5th fixer resistance 51 with the 5th cover pressure valve group, the oil-out of the 5th fixer resistance 51 links to each other with the oil-in of the 5th bi-bit bi-pass solenoid directional control valve 48, and the oil-out of the 5th bi-bit bi-pass solenoid directional control valve 48 links to each other with the oil-out of the oil-out of the 5th overflow valve 54 with the 5th cover pressure valve group.
The oil-in of the 6th cover pressure valve group of the multistage control valve group of the second cover pressure links to each other with the oil-out of the 5th cover pressure valve group, the oil-in of the 6th overflow valve 55 of the 6th cover pressure valve group links to each other with the oil-in of the oil-in of the 6th fixer resistance 52 with the 6th cover pressure valve group, the oil-out of the 6th fixer resistance 52 links to each other with the oil-in of the 6th bi-bit bi-pass solenoid directional control valve 49, the oil-out of the 6th bi-bit bi-pass solenoid directional control valve 49 links to each other with the oil-out of the 6th overflow valve 55 and the oil-out of the 6th cover pressure valve group, the oil-out of the 6th cover pressure valve group links to each other with the oil-out of the multistage control valve group of the second cover pressure, and the oil-out of the multistage control valve group of the second cover pressure links to each other with fuel tank.
The high pressure oil-in of the first pressure reduction relay 28 links to each other with the oil-out of first two-position three way solenoid directional control valve 26, and its low pressure oil-in links to each other with the oil-out of second two-position three way solenoid directional control valve 27; The high pressure oil-in of the second pressure reduction relay 29 links to each other with the oil-out of second two-position three way solenoid directional control valve 29, and its low pressure oil-in links to each other with the oil-out of first two-position three way solenoid directional control valve 27.
Signal acquisition control system comprises controller 56 (controller can adopt single-chip microcomputer, DSP, PLC controller or industrial computer), rotating speed transmitter 57, two pressure transmitters 58 and 59, three cover relay groups, the first cover relay group comprises three relays 41,42 and 43, the second cover relay group comprises that three relays 44,45 and 46, the three cover relay groups comprise two relays 30 and 31; Rotating speed transmitter 57 is installed in the rearward end of lathe spindle 4, and its signal of telecommunication end is electrically connected with controller 56; First pressure transmitter 58 is installed on the oil-out of first piloted reducer 18, second pressure transmitter 59 is installed on the oil-out of second piloted reducer 19, and the signal of telecommunication end of first pressure transmitter 58 and second pressure transmitter 59 is electrically connected with controller 56 respectively.
The output signal of telecommunication end of each relay of first cover and the second cover relay group, overlap corresponding bi-bit bi-pass solenoid directional control valve 38 in the multistage control valve group of pressure with first cover and second respectively, 39,40,47,48 and 49 signal of telecommunication end is electrically connected, the output signal of telecommunication end of first relay 30 of the 3rd cover relay group is electrically connected with the signal of telecommunication end of first two-position three way solenoid directional control valve 26, the output signal of telecommunication end of second relay 31 of the 3rd cover relay group is electrically connected with the signal of telecommunication end of second two-position three way solenoid directional control valve 27, and the input electrical signal end of each relay of three cover relay groups is electrically connected with controller 10 respectively.
As shown in figures 1 and 3, the periphery of power chuck 3 clamping rod workpiece 1.Six overflow valves of the multistage control valve group of initial adjustment two cover pressure make first overflow valve 32, second overflow valve 33, the 3rd overflow valve 34, the 4th overflow valve 47, the 5th overflow valve 48, the 6th overflow valve 49 oil inlet and outlet pressure reduction be respectively 2MPa, 1MPa, 0.5MPa, 2MPa, 1MPa, 0.5MPa.
When hydraulic power unit was not opened, two two-position three way solenoid directional control valves 26 and 27 control coil were not switched on, and two two-position three way solenoid directional control valves 27 and 28 all are operated in position, a left side, and two pressure chambers of the rotating hydraulic cylinder 7 of band hydraulic lock communicate with fuel tank 11.After hydraulic pump 13 was opened, three bi-bit bi-pass solenoid directional control valves 38,39 and 40 initially all were operated in position, a left side, and three bi-bit bi-pass solenoid directional control valves 47,48 and 49 initially all are operated in right position, and two piloted reducers 18 and 19 outputs are near zero minimum pressures.
After lathe spindle 4 began rotation, the speed of mainshaft that rotating speed transmitter 57 records fed back to controller 56, along with the rising of lathe spindle 4 rotating speeds, because of claw 2 suffered centrifugal force increase, the clamping force of power chuck 3 reduces, and when the rotating speed of lathe spindle 4 was elevated to 2000rpm, clamping force was reduced to F
1, controller 56 output control signals are operated in right position through 40 commutations of the 3rd bi-bit bi-pass solenoid directional control valve of the 5th relay 43 controls, first piloted reducer, 18 output pressure 2.5MPa, and the clamping force of power chuck 3 returns to initial clamping force F
0When the rotating speed of lathe spindle 4 was elevated to 3500rpm, clamping force was reduced to F
2Controller 56 output control signals are operated in right position through 39 commutations of second bi-bit bi-pass solenoid directional control valve of the 4th relay 42 controls, when first pressure transmitter 58 detects first piloted reducer, 18 output pressures and rises to 3MPa, controller 56 output control signals are operated in right position through 40 commutations of the 3rd bi-bit bi-pass solenoid directional control valve of the 5th relay 43 controls, first piloted reducer, 18 stable state 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 was elevated to 4500rpm, clamping force was reduced to F
3, controller 56 output control signals are operated in right position through 40 commutations of the 3rd bi-bit bi-pass solenoid directional control valve of the 5th relay 43 controls, and first piloted reducer, 18 output pressures rise to 3.5MPa, and 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 35,36,37 and accumulator 20 play pressure stabilization function when pressure switches.
After bar-shaped workpieces 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 raises.The speed drop of lathe spindle 4 is during to 4500rpm, and the clamping force of power chuck 3 rises to F
0Controller 56 output control signals are operated in position, a left side through 49 commutations of the 6th bi-bit bi-pass solenoid directional control valve of the 8th relay 46 controls, the left cavity pressure of the rotating hydraulic cylinder 7 of second piloted reducer, 19 output pressures and band hydraulic lock rises to 0.5MPa, and the clamping force of power chuck 3 is reduced to F
3The speed drop of lathe spindle 4 is during to 3500rpm, and the clamping force of power chuck 3 increases to F again
0Controller 56 output control signals are operated in position, a left side through 48 commutations of the 5th bi-bit bi-pass solenoid directional control valve of the 7th relay 45 controls, when second pressure transmitter 59 detects second piloted reducer, 19 output pressures and rises to 1MPa, controller 56 output control signals are operated in right position through 49 commutations of the 6th bi-bit bi-pass solenoid directional control valve of the 8th relay 46 controls, second piloted reducer, 19 stable state output pressures rise to 1MPa, and the clamping force of power chuck 3 is reduced to F
2The speed drop of lathe spindle 4 is during to 2000rpm, and the clamping force of power chuck 3 is increased to F once more
0, controller 56 output control signals are operated in position, a left side through 49 commutations of the 6th bi-bit bi-pass solenoid directional control valve of the 8th relay 46 controls, and second piloted reducer, 19 output pressures rise to 1.5MPa, and the clamping force of power chuck 3 is reduced to F
1In 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 operating, controller 56 output control signals are operated in position, a left side through first two-position three way solenoid directional control valve 26 commutations of first relay, 30 controls, and the piston rod of the rotating hydraulic cylinder 7 of band hydraulic lock drives power chuck 3 and unclamps clavate bar-shaped workpieces 1.
Rotated 4 o'clock at lathe spindle, if the output oil pressure of first three-way solenoid valve 26 reduces to zero suddenly because of reasons such as oil pipe explosions, the first pressure reduction relay 28 outputs signal to controller 56, controller 56 output control signals are operated in position, a left side through 27 commutations of second two-position three way solenoid directional control valve of second relay, 31 controls, the output oil port of second two-position three way solenoid directional control valve 27 communicates with fuel tank, guarantees hydraulic lock 8 operate as normal.The output fluid of two safety valves 24 and 25 restriction hydraulic power units are not higher than the maximum charge oil pressure that the rotating hydraulic cylinder 7 of be with hydraulic lock is permitted usefulness.
As shown in Figure 2, the inner hole surface of power chuck 3 clamping disk type works 1 '.Six overflow valves of the multistage control valve group of initial adjustment two cover pressure make first overflow valve 32, second overflow valve 33, the 3rd overflow valve 34, the 4th overflow valve 47, the 5th overflow valve 48, the 6th overflow valve 49 oil inlet and outlet pressure reduction be respectively 2MPa, 1MPa, 0.5MPa, 2MPa, 1MPa, 0.5MPa.When hydraulic power unit was not opened, two two-position three way solenoid directional control valves 26 and 27 all were operated in position, a left side, and two pressure chambers of the rotating hydraulic cylinder 7 of band hydraulic lock communicate with fuel tank 11.
After hydraulic pump 13 was opened, three bi-bit bi-pass solenoid directional control valves 38,39 and 40 initially all were operated in position, a left side, and three bi-bit bi-pass solenoid directional control valves 47,48 and 49 initially all are operated in right position, and two piloted reducers 18 and 19 outputs are near zero minimum pressures.Controller 56 output control signals are operated in position, a left side through 47 commutations of the 4th bi-bit bi-pass solenoid directional control valve of the 6th relay 44 controls, second piloted reducer, 19 output pressure 2MPa, controller 56 output control signals are controlled two two-position three way solenoid directional control valves commutations respectively through first relay 30 and first relay 31 and are operated in right position, hydraulic oil enters the left chamber of the rotating hydraulic cylinder 7 of band hydraulic lock, and piston rod drives the inner hole surface of power chuck 3 stretching disk type works 1 ' to the right.
After lathe spindle 4 begins rotation, the speed of mainshaft that rotating speed transmitter 57 records feeds back to controller 56, rising along with lathe spindle 4 rotating speeds, controller 35 output signals are controlled the multistage control valve group of first pressure, make first piloted reducer, 18 output pressures be increased to 1.5MPa step by step from 0, reduce piston rod thrust to the right, offsetting power chuck 3 increases the clamping force that improves because of claw centrifugal force, and less variation only takes place the clamping force of power chuck 3.The workpiece cutting finishes, along with the rotating speed of lathe spindle 4 constantly reduces, controller 56 output signals are controlled the multistage control valve group of first pressure, make first piloted reducer, 18 output pressures reduce to minimum pressure step by step from 1.5MPa, the thrust output of the rotating hydraulic cylinder 7 of band hydraulic lock improves gradually, remedy power chuck 3 because of claw centrifugal force reduce to reduce clamping force, less variation only takes place in the clamping force of power chuck 3.
After lathe spindle 4 stops operating, controller 56 output control signals are operated in position, a left side through 27 commutations of second two-position three way solenoid directional control valve of second relay, 31 controls, and improving the output pressure of first piloted reducer 18, the piston rod of the rotating hydraulic cylinder 7 of band hydraulic lock drives power chuck 3 left and unclamps disk type work 1 '.Controller 56 output signals are controlled the multistage control valve group of first pressure, make first piloted reducer, 18 output pressures be reduced to minimum pressure, and first two-position three way solenoid directional control valve 27 commutations are operated in position, a left side, begin the next workpiece of clamping again.Rotated 4 o'clock at lathe spindle, if the output oil pressure of second two-position three way solenoid directional control valve 27 reduces to zero suddenly because of reasons such as oil pipe explosions, the second pressure reduction relay 29 outputs signal to controller 56, controller 56 output signals are operated in position, a left side through first two-position three way solenoid directional control valve 26 commutations of first relay, 30 controls, the output oil port of first two-position three way solenoid directional control valve 26 communicates with fuel tank, guarantees hydraulic lock 8 operate as normal.
The tricks of the pressure valve group that the multistage control valve group of two cover pressure comprises pressure adjustable range and pressure controlled progression is as requested determined, the tricks of the pressure valve group that the tricks of the pressure valve group that the first cover pressure multistage control valve group comprises can comprise with the multistage control valve group of the second cover pressure equates, also can be unequal.
Claims (3)
1. the clamping force multi-stage regulating device with the hydraulic power chuck of hydraulic lock comprises the hydraulic power chuck of being with hydraulic lock, regulates the hydraulic power unit that monitoring device is formed, signal acquisition control system by fueller, oil pressure; It is characterized in that:
1) described oil pressure is regulated monitoring device: comprise two piloted reducers (18,19), two accumulators (20,21), two safety valves (24,25), two two-position three way solenoid directional control valves (26,27), the multistage control valve group of pressure that two pressure reduction relays (28,29) are identical with two nested structures, the multistage control valve group of every cover pressure includes 2～5 cover pressure valve groups, and every cover pressure valve group includes overflow valve, bi-bit bi-pass solenoid directional control valve and fixer resistance;
The oil-in of first 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 first two-position three way solenoid directional control valve (26) and the oil-in of first accumulator (20), its oil return opening is connected with fuel tank (11), its Long-distance Control mouth links to each other with the oil-in of the multistage control valve group of the first cover pressure, the oil-in of first safety valve (24) links to each other with the oil-out of first piloted reducer (18), the oil-out of first safety valve (24) links to each other with fuel tank (11), the oil return opening of first two-position three way solenoid directional control valve (26) links to each other with fuel tank (11), and the output oil port of first two-position three way solenoid directional control valve (26) links to each other with first oil inlet and outlet of the rotating hydraulic cylinder (7) of band hydraulic lock;
The oil-in of second piloted reducer (19) 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 second two-position three way solenoid directional control valve (27) and the oil-in of second accumulator (21), its oil return opening is connected with fuel tank (11), its Long-distance Control mouth links to each other with the oil-in of the multistage control valve group of the second cover pressure, the oil-in of second safety valve (25) links to each other with the oil-out of second piloted reducer (19), the oil-out of second safety valve (25) links to each other with fuel tank (11), the oil return opening of second two-position three way solenoid directional control valve (27) links to each other with fuel tank (11), and the output oil port of second two-position three way solenoid directional control valve (27) links to each other with second oil inlet and outlet of the rotating hydraulic cylinder (7) of band hydraulic lock;
The oil-in of the multistage control valve group of two cover pressure links to each other with first oil-in that overlaps the pressure valve group separately, the oil-in of first overflow valve of the first cover pressure valve group links to each other with the oil-in of first fixer resistance separately, 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 separately, and the oil-out of first bi-bit bi-pass solenoid directional control valve is with the oil-out and first oil-out that overlaps the pressure valve group of first overflow valve link to each other separately; The oil-in of last cover pressure valve group links to each other with the oil-out of going up a cover pressure valve group separately, the oil-in of last overflow valve of last cover pressure valve group links to each other with the oil-in of the oil-in of last fixer resistance separately with last cover pressure 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 separately, the oil-out of last bi-bit bi-pass solenoid directional control valve is with the oil-out of last overflow valve and the oil-out of last cover pressure valve group link to each other separately, the oil-out of last cover pressure valve group links to each other with the oil-out of the multistage control valve group of pressure separately, and two oil-outs that overlap the multistage control valve group of pressure link to each other with fuel tank;
The high pressure oil-in of the first pressure reduction relay (28) links to each other with the oil-out of first two-position three way solenoid directional control valve (26), and its low pressure oil-in links to each other with the oil-out of second two-position three way solenoid directional control valve (27); The high pressure oil-in of the second pressure reduction relay (29) links to each other with the oil-out of second two-position three way solenoid directional control valve (27), and its low pressure oil-in links to each other with the oil-out of first two-position three way solenoid directional control valve (26);
2) described signal acquisition control system: comprise controller (56), rotating speed transmitter (57) and three cover relay groups, first cover and the second cover relay group include 2～5 relays, and the 3rd cover relay group comprises two relays (30,31); Rotating speed transmitter (57) is installed in the rearward end of lathe spindle (4), and its signal of telecommunication end is electrically connected with controller (56); The output signal of telecommunication end of each relay of first cover and the second cover relay group, overlap the signal of telecommunication end electrical connection of bi-bit bi-pass solenoid directional control valve corresponding in the multistage control valve group of pressure respectively with first cover and second, the output signal of telecommunication end of first relay (30) of the 3rd cover relay group is electrically connected with the signal of telecommunication end of first two-position three way solenoid directional control valve (26), the output signal of telecommunication end of second relay (31) of the 3rd cover relay group is electrically connected with the signal of telecommunication end of second two-position three way solenoid directional control valve (27), and the input electrical signal end of each relay is electrically connected with controller (56) respectively.
2. the clamping force multi-stage regulating device of a kind of hydraulic power chuck with hydraulic lock according to claim 1, it is characterized in that: first pressure transmitter (58) is installed on the oil-out of described first piloted reducer (18), second pressure transmitter (59) is installed on the oil-out of second piloted reducer (19), and the signal of telecommunication end of first pressure transmitter (58) and second pressure transmitter (59) is electrically connected with controller (56) respectively.
3. the clamping force multi-stage regulating device of a kind of hydraulic power chuck with hydraulic lock according to claim 1 and 2, it is characterized in that: described piloted reducer (18,19) is pilot-type two-port pressure-reducing valve or pilot-operated type three-way pressure reducing valve.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2009101532298A CN101695764B (en) | 2009-10-26 | 2009-10-26 | Clamping force multi-stage regulating device of hydraulic power chuck with hydraulic lock |
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| Application Number | Priority Date | Filing Date | Title |
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| CN2009101532298A CN101695764B (en) | 2009-10-26 | 2009-10-26 | Clamping force multi-stage regulating device of hydraulic power chuck with hydraulic lock |
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| CN101695764A CN101695764A (en) | 2010-04-21 |
| CN101695764B true CN101695764B (en) | 2011-01-05 |
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| CN2009101532298A Expired - Fee Related CN101695764B (en) | 2009-10-26 | 2009-10-26 | Clamping force multi-stage regulating device of hydraulic power chuck with hydraulic lock |
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| CN102635584A (en) * | 2012-03-28 | 2012-08-15 | 济南东测试验机技术有限公司 | Multi-channel electro-hydraulic servo low and high-pressure oil distributing device |
| CN107882778A (en) * | 2017-11-16 | 2018-04-06 | 中国航空工业集团公司北京航空精密机械研究所 | A kind of ultra-precision machine tool oil supply system with emergent supply capability |
| CN114233708B (en) * | 2021-12-15 | 2023-11-24 | 中国航发动力股份有限公司 | Hydraulic control system and method for indexing plate positioning |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4723778A (en) * | 1985-11-06 | 1988-02-09 | Howa Machinery, Ltd. | Automatic lubricating system of power chuck |
| CN2569951Y (en) * | 2002-09-20 | 2003-09-03 | 济南一机床集团有限公司 | Pressure control device of lathe hydraulic chuck |
| CN101216052A (en) * | 2008-01-09 | 2008-07-09 | 浙江大学 | Rotating speed variable driving shield cutterhead energy-saving hydraulic control system |
| CN101272878A (en) * | 2005-09-23 | 2008-09-24 | 株式会社三千里机械 | Synchronized clamping chuck for machine tool |
-
2009
- 2009-10-26 CN CN2009101532298A patent/CN101695764B/en not_active Expired - Fee Related
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4723778A (en) * | 1985-11-06 | 1988-02-09 | Howa Machinery, Ltd. | Automatic lubricating system of power chuck |
| CN2569951Y (en) * | 2002-09-20 | 2003-09-03 | 济南一机床集团有限公司 | Pressure control device of lathe hydraulic chuck |
| CN101272878A (en) * | 2005-09-23 | 2008-09-24 | 株式会社三千里机械 | Synchronized clamping chuck for machine tool |
| CN101216052A (en) * | 2008-01-09 | 2008-07-09 | 浙江大学 | Rotating speed variable driving shield cutterhead energy-saving hydraulic control system |
Non-Patent Citations (1)
| Title |
|---|
| JP平3-121707A 1991.05.23 |
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