CN103350372B - Support stiffness compensation system for square ram of gantry machining center - Google Patents
Support stiffness compensation system for square ram of gantry machining center Download PDFInfo
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Abstract
A support stiffness compensation system for a square ram of a gantry machining center consists of a compensation driver board device, a pressure control system and an electric control module, wherein the compensation driver board device comprises a compensation driver board, a flange guide sleeve and a guide post, four small-inclination wedge-shaped mounting surfaces are symmetrically arranged on the compensation driver board in a crossed manner, two circular thin-walled pressurizing structures are arranged on each small-inclination wedge-shaped mounting surface, and each circular thin-walled pressurizing structure consists of an elastic bent and deformed thin wall, a pressurizing oil chamber, an end cover and a sealing device; the pressure control system consists of a machine tool hydraulic station power source part, a hydraulic valve block, a speed control valve, an electromagnetic proportional overflow valve, a pressure gauge bumper, a pressure gauge and the like; the electric control module comprises a machine tool Z-axis feed coordinate signal unit, a D/A (Digital/Analog) converter and a control amplifier of a proportional pressure valve. The microgap compensation system provided by the invention can achieve self-adaptive microgap compensation according to a Z-axis feed coordinate signal of the square ram.
Description
Technical field
The present invention relates to machine tool accuracy bucking-out system, especially a kind of bucking-out system for compensating gantry machining center side's ram rail plate support stiffness and machine finish.
Background technology
In the heavy process equipments such as large-sized gantry numerical control machining center, vertical turning center, numerical control floor type boring and milling machine, square ram and saddle structure are one of important composition structures.Ram (Ram) is that the parts such as knife rest or main spindle box are housed, and having guide rail can the pillow functional part of movement on lathe bed or miscellaneous part, and the guide rail of square ram is exactly himself substantially.The ram of existing heavy process equipment generally adopts square ram structure form, forms guide pass, form sliding friction guideway, and accompany by hydrodynamic lubrication or oil lubrication with saddle inner surface with square ram four sides fine grinding.The microgap that sliding friction pair also exists, form lubricating oil film, the precondition of the side's of being beneficial to ram movement, meanwhile, the existence of microgap is also the key factor affecting ram and saddle fit structure, when microgap is too small, borderline oil film can be made to break, frictional resistance significantly rises, thus number controlled machine Z axis feeding positioning precision declines, the aggravation of low speed jerking motion phenomenon, smooth, the unstable wear even bad phenomenon such as locking of sliding; And when microgap is excessive, contact stiffness between ram and saddle weakens greatly, thus cause processing to tremble, the problem such as part finished surface out-of-flatness, meanwhile, gap width δ itself is the factor of influence of machine finish, and stretching out along with ram, gap width δ is amplified at double on the impact of positioning precision, thus causes positioning precision, the repetitive positioning accuracy reduction of lathe.
Based on above-mentioned analysis, the control that the microgap between square ram and saddle structure is worth, plays an important role for the overall performance, machining accuracy etc. promoting lathe.The concrete analysis of the assembly structure form between side's ram and saddle, contribute to the understanding of intensification the other side's ram microgap Crack cause and propose a kind of rationally effective compensation method, for the concrete assembly structure of square ram and saddle, refer to Figure of description 1 and 2, for the analysis of concrete structure, be further described in detail hereinafter at description.
For the Compensation andcontrol of square ram rail plate microgap, belong to microgap to compensate or microgap feeding category, conventional Fine Feed mode comprises mechanical type, mangneto formula, piezoelectric type, thermal expansion formula, fluid pressure type, wherein, when Fine Feed mode is used for the compensation of ram microgap, lathe side, propose very high requirement to the support stiffness of Fine Feed deflection and the resolution ratio of Light deformation, synthesise various factor analysis, fluid pressure type Fine Feed mode is a kind of ideal solution.The Fine Feed that the present invention adopts Circular Thin pressure structure form to realize fluid pressure type compensates, Circular Thin pressure structure can be arranged on lathe original gap adjustment wedge shape filler rod, when adopting the program, minimum to the original structural modification of lathe, but also there are some shortcomings, such as: the separate design of oil leab needed for Circular Thin pressurization oil duct and square ram slide, the sliding friction between Circular Thin pressure structure bending deformation form point and square ram causes compensation point to wear and tear to aggravate.
Summary of the invention
Rail plate is adopted to there is microgap in order to overcome gantry machining center side's ram, when the side's of causing ram stretches out, support stiffness declines, degradation problem under machining accuracy decline, vibration cutting, piece surface crudy when causing machine tooling, the present invention proposes a kind of according to square ram Z axis feeding coordinate signal the square ram support stiffness bucking-out system of adaptive equalization microgap.
The technical solution adopted for the present invention to solve the technical problems is:
A kind of gantry machining center side ram support stiffness bucking-out system, by compensation drive plate device, control pressurer system and electric control module are formed, it is characterized in that, described compensation drive plate device comprises compensation drive plate, flange guide pin bushing, guide pillar is formed, described flange guide pin bushing is fixed on described compensation drive plate, described guide pillar is fixed on saddle structure or saddle covering plate structure, described compensation drive plate is slidably arranged on described guide pillar by described flange guide pin bushing, described compensation drive plate four little gradient wedge shape installed surfaces have been arranged symmetrically with in " ten " word, gap adjustment wedge shape filler rod is fixed on described little gradient wedge shape installed surface by contiguous block, each described little gradient wedge shape installed surface is provided with M Circular Thin pressure structure, described Circular Thin pressure structure is made up of elastic springing thin-walled, pressurization oil pocket, end cap and sealing device, described elastic springing thin-walled is arranged on the back plane of described compensation drive plate, and described elastic springing thin-walled contacts with described saddle structure or saddle covering plate structure, described control pressurer system is made up of machine tool hydraulic station power source part, hydraulic valve block, flow speed control valve, electromagnetic proportion relief valve, pressure ga(u)ge damper and Pressure gauge etc., power source part branch's oil circuit in described machine tool hydraulic station is after flow speed control valve regulates, the pressure oil of constant flow rate is realized the adjustment of pressure by electromagnetic proportion relief valve, the pressure oil after pressure regulates is transported to the oiler of described Circular Thin pressure structure by conduit under fluid pressure through shunt block, described electric control module comprises the control amplifier of machine Z-axis feeding coordinate signal unit, D/A converter and proportional pressure valve.
Further, described compensation drive plate device comprises two block compensation drive plates, one block compensation drive plate is slidably arranged in described saddle structure by flange guide pin bushing, guide pillar structure, and another block compensation drive plate is slidably arranged on described saddle covering plate structure by flange guide pin bushing, guide pillar structure.
Further again, described compensation drive plate has been arranged symmetrically with four little gradient wedge shape installed surfaces in " ten " word, and described little gradient wedge shape installed surface is the installed surface of gap adjustment wedge shape filler rod, and be the lozenges of little gradient, slope is 1:100; Described little gradient wedge shape installed surface arranges Circular Thin pressure structure, the elastic springing thin-walled of described Circular Thin pressure structure is arranged on the back plane of described compensation drive plate, described end cap has sealing ring deep gouge, mounting O-shaped sealing ring in described sealing ring deep gouge, described end cap is fixed by screws in the counterbore of little gradient wedge shape installed surface, form pressurization oil pocket, the thickness of described end cap does not exceed little gradient wedge shape installed surface.
As preferred a kind of scheme: each described little gradient wedge shape installed surface arranges two Circular Thin pressure structures.
As preferred another kind of scheme: described control pressurer system can be realized the internal pressurization oil pocket pressure regulation of Circular Thin pressure structure by the overflow voltage-regulating system of constant flow, machine tool hydraulic station power source part is realized the security settings of hydraulic system maximal pressure force value by overflow valve, the working connection of machine tool hydraulic station power source part receives ram balancing cylinder, on the actuators such as broaching tool oil cylinder and tool magazine tool changing hydraulic motor, wherein, a branch road of machine tool hydraulic station power source part is after hydraulic valve block oiler, be connected on flow speed control valve, realized the automatic adjustment of pressure by electromagnetic proportion relief valve through the pressure oil of speed governing, pressure oil after pressure regulation is connected to the oiler of described Circular Thin pressure structure through pipeline by hydraulic valve block oil-out, described hydraulic valve block is also provided with pressure ga(u)ge damper connector, overfall, fuel tank is taken back separately after the overfall of described electromagnetic proportion relief valve connects a check valve.
As another scheme preferred: described control pressurer system also can be realized the internal pressurization oil pocket pressure regulation of Circular Thin pressure structure by the vacuum regulator system of throttling, an oil circuit of system dynamic source, machine tool hydraulic station part is connected on solenoid-operated proportional low-pressure relief valve after choke valve or throttle orifice throttling, hydraulic oil after pressure regulation is connected respectively to the oiler of Circular Thin pressure structure by shunt block, fuel tank is taken back separately after the overfall of described solenoid-operated proportional low-pressure relief valve connects check valve, the Long-distance Control X mouth of the proportional pilot valve of described solenoid-operated proportional low-pressure relief valve is connected on the P mouth of bi-bit bi-pass reversal valve, the B mouth of described bi-bit bi-pass reversal valve is connected with overflow valve, A mouth blocks, T mouth takes back draining road.
As another scheme preferred: described electric control module comprises the control amplifier of machine Z-axis feeding coordinate signal unit, D/A converter and proportional pressure valve.Described machine Z-axis feeding coordinate signal unit comprises Z axis feeding grating scale, Machine Tools Electric system, the PLC module of Machine Tools Electric system can process Z axis coordinate signal, signal after process changes the analog voltage of 0-10V into after D/A converter, and the analog voltage of output changes the analog current driving proportional pressure valve into after the control amplifier of proportional pressure valve.
Beneficial effect of the present invention is embodied in:
When the Circular Thin pressure structure of square ram microgap bucking-out system is arranged on gap adjustment wedge shape filler rod, there is following deficiency: first, the contact point that backlash compensation actuator flexing displacement exports or contact surface are in dynamic friction state all the time, can aggravate the material friction wearing and tearing compensating contact point place; The second, change the hydrodynamic lubrication pipeline structure in filler rod, the program is unfavorable for capstan and the design of hydrodynamic lubrication oil duct.Based on above 2 considerations, the present invention proposes above square ram support stiffness bucking-out system, its Advantages found exists: first, flexing displacement exports compensation contact point and appears on the supporting surface of compensation drive plate and saddle or saddle cover plate, the action also existed is only to compensate and exports and regain, it not only can overcome the problem of fretting wear, drives whole filler rod to move simultaneously, does not change the face way of contact of ram and saddle; The second, pressurization oil duct is separated with oil leab, non-interference, and it is very convenient that oil duct is arranged.
Field adjustable illustrates, this system can effectively improve machine ram support stiffness, improves the piece surface crudy of lathe, has certain compensation effect simultaneously to Machine Tool Positioning Accuracy.
Accompanying drawing explanation
Fig. 1 is gantry machining center ram saddle assembly structure schematic diagram
Fig. 2 is the structural representation of gantry machining center ram, gap adjustment wedge shape filler rod and saddle
Fig. 3 is the compensation drive plate structure drawing of device of side's ram support stiffness bucking-out system of the present invention
Fig. 4 is the compensation drive plate device partial structurtes enlarged drawing of side's ram support stiffness bucking-out system of the present invention
Fig. 5 is the Circular Thin pressure structure figure of side's ram support stiffness bucking-out system of the present invention
Fig. 6 is hydraulic valve block structural representation of the present invention
Fig. 7 is constant flow overflow voltage-regulating system fundamental diagram of the present invention
Fig. 8 is expenditure and pressure voltage-regulating system fundamental diagram of the present invention
Detailed description of the invention
Composition graphs 1 ~ Fig. 8, before the embodiment introducing gantry machining center side of the present invention ram support stiffness bucking-out system, first introduces gantry machining center square ram structure, assembly relation and square ram rail plate clearance adjustment method.
Ram and saddle structure adopt rail plate fit form, and its concrete structure is as follows: by reference to the accompanying drawings 1,2, and square ram 1 is arranged in saddle 101, fix, form completely encircle structure with saddle cover plate 102.Ram sliding friction on the mating surface of saddle, has four guide supporting faces, wherein saddle has two face fine grindings, for datum level, and two other face being formed and encircle shape is coordinated with these two faces, the working face namely on saddle on another side and saddle cover plate is adjustment face, gap.In existing lathe mounting technology, adjust microgap value δ when machine ram slides by gap adjustment wedge shape filler rod 103, this microgap value δ becomes one of restraining factors affecting machine finish.The original gap adjustment of ram rail plate, generally adopts the method for artificial adjustment at present, after being assembled to by ram on saddle, by locked for the assembling of saddle cover plate.There is certain gap in saddle inside in ram, carry out trace adjustment with gap adjustment wedge shape filler rod 103, main basis for estimation is the resistance to sliding of ram under hydrodynamic lubrication.Concrete method of adjustment and operation principle are shown in accompanying drawing 2, by the adjustment screw on contiguous block 3, make gap adjust wedge shape filler rod 103 and slide on the little gradient wedge shape installed surface of saddle, adjusting play size, and amount of taper is 1:100.Original gap, once adjust, would not change.Therefore, the gap that microgap value δ is formed after namely completing the adjustment of gap adjustment wedge shape filler rod.
After describing the assembly structure of traditional gantry machining center ram, introduce side's ram support stiffness bucking-out system of the present invention by reference to the accompanying drawings.
A kind of gantry machining center side ram support stiffness bucking-out system, by compensation drive plate device, control pressurer system and electric control module are formed, described compensation drive plate device comprises compensation drive plate 2, flange guide pin bushing 2-3, guide pillar is formed, described flange guide pin bushing 2-3 is fixed on described compensation drive plate 2, described guide pillar is fixed on saddle structure or saddle covering plate structure, described compensation drive plate is slidably arranged on described guide pillar by described flange guide pin bushing, described compensation drive plate device comprises two block compensation drive plates, one block compensation drive plate is by flange guide pin bushing, guide pillar structure is slidably arranged in described saddle structure, another block compensation drive plate is by flange guide pin bushing, guide pillar structure is slidably arranged on described saddle covering plate structure.Specifically, for traditional gantry machining center, on the adjustment face, gap of the described compensation drive plate side of being arranged on ram.
Described compensation drive plate has been arranged symmetrically with four little gradient wedge shape installed surface 2-1 in " ten " word, and gap adjustment wedge shape filler rod 103 is fixed on described little gradient wedge shape installed surface 2-1 by contiguous block 3; Each described little gradient wedge shape installed surface is provided with two Circular Thin pressure structure 2-2, described Circular Thin pressure structure 2-2 is made up of elastic springing thin-walled 2-6, pressurization oil pocket 2-7, end cap 2-5 and sealing device, described elastic springing thin-walled is arranged on the back plane of described compensation drive plate, and described elastic springing thin-walled contacts with described saddle structure or saddle covering plate structure.
Described compensation drive plate has been arranged symmetrically with four little gradient wedge shape installed surfaces in " ten " word, and described little gradient wedge shape installed surface 2-1 is the installed surface of gap adjustment wedge shape filler rod, and be the lozenges of little gradient, slope is 1:100; Described little gradient wedge shape installed surface arranges Circular Thin pressure structure, the elastic springing thin-walled 2-6 of described Circular Thin pressure structure is arranged on the back plane of described compensation drive plate, described end cap has sealing ring deep gouge, mounting O-shaped sealing ring 2-8 in described sealing ring deep gouge, described end cap is fixed by screws in the counterbore of little gradient wedge shape installed surface, form pressurization oil pocket, described pressurization oil pocket is realized the supply of pressure oil by the oil duct that pressurizes.The thickness of described end cap does not exceed little gradient wedge shape installed surface, does not affect gap adjustment wedge shape filler rod normal mounting at little gradient wedge shape installed surface.
The Circular Thin pressure structure of side's ram support stiffness bucking-out system needs elastic springing to occur under the effect of pressure oil, it to the basic demand of hydraulic control system is: coordinate value that can be corresponding according to machine Z-axis feeding, electrical compensation value is provided fast by electric control system, hydraulic control system responds required hydraulic fluid pressure output valve fast according to electrical compensation value, and backlash compensation actuator input pressure oil pressure force value responds with Z axis feeding coordinate value between 0 ~ 8Mpa; To the control overflow of flow, because backlash compensation actuator is closed pressurised chamber, internal capacity is only 75ml, and the flow value change that pressure-responsive is corresponding is very little, and flow needs the pressure-responsive in complete earial drainage guarantee actuator, therefore require very low to flow value, if Hydraulic Station branch flow is excessive, flow not only can be caused to waste, system causes system temperature rise too high because of excessive overflow, and system may because of the local assault causing hydraulic pressure that refluxes when reduction of blood pressure in high-speed, unfavorable system stability.Based on above requirement, propose the control pressurer system meeting above demand.
Described control pressurer system is made up of machine tool hydraulic station power source part 4-1, hydraulic valve block 4-10, flow speed control valve 4-2, electromagnetic proportion relief valve 4-3, pressure ga(u)ge damper 4-6 and Pressure gauge 4-5 etc., power source part branch's oil circuit in described machine tool hydraulic station is after flow speed control valve regulates, the pressure oil of constant flow rate is realized the adjustment of pressure by electromagnetic proportion relief valve 4-3, the pressure oil after pressure regulates is transported to the oiler 2-4 of described Circular Thin pressure structure by conduit under fluid pressure through shunt block 4-7.
Described control pressurer system can be realized the internal pressurization oil pocket pressure regulation of Circular Thin pressure structure by the overflow voltage-regulating system of constant flow, its structural principle is shown in Fig. 7, machine tool hydraulic station power source part 4-1 is realized the security settings of hydraulic system maximal pressure force value by overflow valve 4-8, the working connection 4-9 of machine tool hydraulic station power source part receives ram balancing cylinder, on the actuators such as broaching tool oil cylinder and tool magazine tool changing hydraulic motor, wherein, a branch road of machine tool hydraulic station power source part is after hydraulic valve block oiler 4-11, be connected on flow speed control valve 4-2, realized the automatic adjustment of pressure by electromagnetic proportion relief valve 4-3 through the pressure oil of speed governing, pressure oil after pressure regulation is connected to the oiler of described Circular Thin pressure structure through pipeline by hydraulic valve block oil-out 4-12, described hydraulic valve block is also provided with pressure ga(u)ge damper connector 4-14, overfall 4-13, fuel tank is taken back separately after the overfall of described electromagnetic proportion relief valve meets a check valve 4-4, the design of hydraulic valve block 4-10 has comprised the function of block along separate routes.
For the overflow voltage-regulating system of above-mentioned constant flow, flow speed control valve makes the flow constant entering electromagnetic proportion relief valve, and the range of flow of adjustment, between 0.6 ~ 0.7L/min, meets the maximum excess flow requirement of electromagnetic proportion relief valve.Electromagnetic proportion relief valve adopts band position sensor feedback type, improves regulation precision.The drain tap of electromagnetic proportion relief valve connects check valve, takes back fuel tank by independent drain mast.The setting of check valve, forms certain back pressure, prevents the fluid in electromagnetic proportion relief valve drain mast from letting out completely because of gravity and gets back to fuel tank, be also convenient to dismounting electromagnetic proportion relief valve, otherwise siphonage may by the oily suck-back in fuel tank simultaneously.
Described control pressurer system also can be realized the internal pressurization oil pocket pressure regulation of Circular Thin pressure structure by the vacuum regulator system of throttling, its structural principle is shown in Fig. 8, an oil circuit of system dynamic source, machine tool hydraulic station part is connected on solenoid-operated proportional low-pressure relief valve 4-16 after choke valve 4-15 or throttle orifice throttling, hydraulic oil after pressure regulation is connected respectively to the oiler of Circular Thin pressure structure by shunt block, fuel tank is taken back separately after the overfall of described solenoid-operated proportional low-pressure relief valve connects check valve, the Long-distance Control X mouth of the proportional pilot valve of described solenoid-operated proportional low-pressure relief valve is connected on the P mouth of bi-bit bi-pass reversal valve 4-17, the B mouth of described bi-bit bi-pass reversal valve is connected with overflow valve 4-18, A mouth blocks, T mouth takes back draining road.
For the control pressurer system shown in accompanying drawing 7, accompanying drawing 8, the difference of the two and strengths and weaknesses analysis as follows: first, accompanying drawing 7 control pressurer system adopts electromagnetic proportion relief valve to carry out Stress control, utilizes flow control valve to carry out flow restriction, meets and closes compression system requirement.This Control system architecture is simple, development cost is low, and because electromagnetic proportion relief valve is band position-feedback type direct-acting type pressure control valve, the response speed of hydraulic system is faster compared to accompanying drawing 8 system, but the override pressure of hydraulic system is relatively large, accuracy is relatively poor.Another main deficiency of this control system is, the more important that proportioning valve is different from servo valve is " covering at zero point " problem, namely has minimum adjustment pressure and regulates dead band, is all regulate dead band before controller electric current 200mA.Because pumping plant meeting continuous firing, when system is without unloading-structure, proportioning valve is minimum is adjusted to minimum setting pressure by pressure, that is, Circular Thin pressure structure is out of shape always under pressure oil, and only have when lathe quits work, Circular Thin pressure structure could be recovered, therefore, more easily there is fatigue damage.Second, accompanying drawing 8 control pressurer system adopts solenoid-operated proportional low-pressure relief valve, be configured with Long-distance Control overflow valve, its cost is higher, relative to straight type proportion overflow valve, response speed comparatively slow (this system is less demanding to response speed), but solenoid-operated proportional low-pressure relief valve is piloted reducer structure, the balancing spring rigidity of main valve is very little, therefore the open and shut characteristic of this valve is better, override pressure (difference namely between setting and actual value) is less, regulation precision is higher, opening feature is much better than closing characteristics, and the dynamic property of pressure regulation is better than direct-acting overflow valve.Meanwhile, the utilization of control mouth X far away, can make up the deficiency of proportioning valve " covering at zero point ".
Described electric control module comprises the control amplifier of machine Z-axis feeding coordinate signal unit, D/A converter and proportional pressure valve.Described machine Z-axis feeding coordinate signal unit comprises Z axis feeding grating scale, Machine Tools Electric system 5-1, the PLC module of Machine Tools Electric system can process Z axis coordinate signal, signal after process changes the analog voltage of 0-10V into after D/A converter 5-2, and the analog voltage of output changes the analog current driving proportional pressure valve into after the control amplifier 5-3 of proportional pressure valve.
Side's ram support stiffness bucking-out system carries out adaptive equalization according to Z axis displacement coordinate signal, therefore this system proposes the requirement of expansion to Electrical Control of Machinery Tools system: the voltage analog signal that Z axis displacement coordinate signal can be converted into 0 ~ 10V by Electrical Control of Machinery Tools system exports, simultaneously, by electrical system PLC processor, electrical compensation value or the continuous analog signal of discrete type can be exported according to actual condition.
The control signal transitive relation of electric control module is as follows: Z axis coordinate displacement signal is by grating scale or encoder collection, the signal gathered is sinusoidal wave data signal, this data signal is directly passed to the PLC module of Machine Tools Electric system, by the voltage analog signal of D/A conversion electron module transitions city 0-10V after logical process, voltage analog signal is input on the control amplifier of proportional pressure valve, export as current analog signal, this current analog signal can be used for driving the electromagnet of proportional pressure valve, thus the force value of the system of setting, the system pressure value set up is for driving Circular Thin pressure structure generation elastic springing, thus realize the backlash compensation of support stiffness enhancing.After field adjustable, after setting up out the best relation curve between Z axis displacement coordinate and backlash compensation value, through the ladder diagram process (LED program) of PLC and the proportionality coefficient setting of proportional pressure valve control amplifier, the demand of on-the-spot actual condition can be met.
Claims (7)
1. gantry machining center side's ram support stiffness bucking-out system, by compensation drive plate device, control pressurer system and electric control module are formed, it is characterized in that, described compensation drive plate device comprises compensation drive plate, flange guide pin bushing, guide pillar is formed, described flange guide pin bushing is fixed on described compensation drive plate, described guide pillar is fixed on saddle structure or saddle covering plate structure, described compensation drive plate is slidably arranged on described guide pillar by described flange guide pin bushing, described compensation drive plate four little gradient wedge shape installed surfaces have been arranged symmetrically with in " ten " word, gap adjustment wedge shape filler rod is fixed on described little gradient wedge shape installed surface by contiguous block, each described little gradient wedge shape installed surface is provided with Circular Thin pressure structure, described Circular Thin pressure structure is made up of elastic springing thin-walled, pressurization oil pocket, end cap and sealing device, described elastic springing thin-walled is arranged on the back plane of described compensation drive plate, and described elastic springing thin-walled contacts with described saddle structure or saddle covering plate structure, described control pressurer system is made up of machine tool hydraulic station power source part, hydraulic valve block, flow speed control valve, electromagnetic proportion relief valve, pressure ga(u)ge damper and Pressure gauge, power source part branch's oil circuit in described machine tool hydraulic station is after flow speed control valve regulates, the pressure oil of constant flow rate is realized the adjustment of pressure by electromagnetic proportion relief valve, the pressure oil after pressure regulates is transported to the oiler of described Circular Thin pressure structure by conduit under fluid pressure through shunt block, described electric control module comprises the control amplifier of machine Z-axis feeding coordinate signal unit, D/A converter and proportional pressure valve.
2. side's ram support stiffness bucking-out system as claimed in claim 1, it is characterized in that: described compensation drive plate device comprises two block compensation drive plates, one block compensation drive plate is slidably arranged in described saddle structure by flange guide pin bushing, guide pillar structure, and another block compensation drive plate is slidably arranged on described saddle covering plate structure by flange guide pin bushing, guide pillar structure.
3. side's ram support stiffness bucking-out system as claimed in claim 1, it is characterized in that: described compensation drive plate has been arranged symmetrically with four little gradient wedge shape installed surfaces in " ten " word, described little gradient wedge shape installed surface is the installed surface of gap adjustment wedge shape filler rod, for the lozenges of little gradient, slope is 1:100; Described little gradient wedge shape installed surface arranges Circular Thin pressure structure, the elastic springing thin-walled of described Circular Thin pressure structure is arranged on the back plane of described compensation drive plate, described end cap has sealing ring deep gouge, mounting O-shaped sealing ring in described sealing ring deep gouge, described end cap is fixed by screws in the counterbore of little gradient wedge shape installed surface, form pressurization oil pocket, the thickness of described end cap does not exceed little gradient wedge shape installed surface.
4. the square ram support stiffness bucking-out system as described in claim 1 or 2 or 3, is characterized in that: each described little gradient wedge shape installed surface arranges two Circular Thin pressure structures.
5. the square ram support stiffness bucking-out system as described in claim 1 or 2 or 3, it is characterized in that: described control pressurer system can be realized the internal pressurization oil pocket pressure regulation of Circular Thin pressure structure by the overflow voltage-regulating system of constant flow, machine tool hydraulic station power source part is realized the security settings of hydraulic system maximal pressure force value by overflow valve, the working connection of machine tool hydraulic station power source part receives ram balancing cylinder, on broaching tool oil cylinder and tool magazine tool changing hydraulic motor, wherein, a branch road of machine tool hydraulic station power source part is after hydraulic valve block oiler, be connected on flow speed control valve, realized the automatic adjustment of pressure by electromagnetic proportion relief valve through the pressure oil of speed governing, pressure oil after pressure regulation is connected to the oiler of described Circular Thin pressure structure through pipeline by hydraulic valve block oil-out, described hydraulic valve block is also provided with pressure ga(u)ge damper connector, overfall, fuel tank is taken back separately after the overfall of described electromagnetic proportion relief valve connects a check valve.
6. the square ram support stiffness bucking-out system as described in claim 1 or 2 or 3, it is characterized in that: described control pressurer system also can be realized the internal pressurization oil pocket pressure regulation of Circular Thin pressure structure by the vacuum regulator system of throttling, an oil circuit of system dynamic source, machine tool hydraulic station part is connected on solenoid-operated proportional low-pressure relief valve after choke valve or throttle orifice throttling, hydraulic oil after pressure regulation is connected respectively to the oiler of Circular Thin pressure structure by shunt block, fuel tank is taken back separately after the overfall of described solenoid-operated proportional low-pressure relief valve connects check valve, the Long-distance Control X mouth of the proportional pilot valve of described solenoid-operated proportional low-pressure relief valve is connected on the P mouth of bi-bit bi-pass reversal valve, the B mouth of described bi-bit bi-pass reversal valve is connected with overflow valve, A mouth blocks, T mouth takes back draining road.
7. the square ram support stiffness bucking-out system as described in claim 1 or 2 or 3, is characterized in that: described electric control module comprises the control amplifier of machine Z-axis feeding coordinate signal unit, D/A converter and proportional pressure valve; Described machine Z-axis feeding coordinate signal unit comprises Z axis feeding grating scale, Machine Tools Electric system, the PLC module of Machine Tools Electric system can process Z axis coordinate signal, signal after process changes the analog voltage of 0-10V into after D/A converter, and the analog voltage of output changes the analog current driving proportional pressure valve into after the control amplifier of proportional pressure valve.
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| CN106239152A (en) * | 2016-08-29 | 2016-12-21 | 泊头巨人重工机械有限公司 | A kind of numerical control gantry moves turnning and milling and bores boring combined machine system |
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| CN101417400A (en) * | 2008-12-22 | 2009-04-29 | 齐齐哈尔二机床(集团)有限责任公司 | Large-size CNC horizontal milling and boring machine ram movable inclined guide-rail compensation method and device |
| DE102009020383A1 (en) * | 2009-05-08 | 2010-11-11 | Schaeffler Technologies Gmbh & Co. Kg | Bearing arrangement e.g. radial axial-thrust bearing arrangement, for machine table, has cooling channels forming circuit by gap and hydraulic unit, where hydraulic fluid is conveyable through circuit |
| CN201900515U (en) * | 2010-12-13 | 2011-07-20 | 宁波海天精工机械有限公司 | Fine compensation device of ram of floor-type boring machine |
| CN102380802A (en) * | 2011-11-03 | 2012-03-21 | 芜湖恒升重型机床股份有限公司 | Ram deflection deformation compensation device |
| CN203304994U (en) * | 2013-06-14 | 2013-11-27 | 严松法 | Square ram support stiffness compensation system of gantry machining center |
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| JPH04101753A (en) * | 1990-08-15 | 1992-04-03 | Hitachi Ltd | Correction method for straightness of table |
| CN101417400A (en) * | 2008-12-22 | 2009-04-29 | 齐齐哈尔二机床(集团)有限责任公司 | Large-size CNC horizontal milling and boring machine ram movable inclined guide-rail compensation method and device |
| DE102009020383A1 (en) * | 2009-05-08 | 2010-11-11 | Schaeffler Technologies Gmbh & Co. Kg | Bearing arrangement e.g. radial axial-thrust bearing arrangement, for machine table, has cooling channels forming circuit by gap and hydraulic unit, where hydraulic fluid is conveyable through circuit |
| CN201900515U (en) * | 2010-12-13 | 2011-07-20 | 宁波海天精工机械有限公司 | Fine compensation device of ram of floor-type boring machine |
| CN102380802A (en) * | 2011-11-03 | 2012-03-21 | 芜湖恒升重型机床股份有限公司 | Ram deflection deformation compensation device |
| CN203304994U (en) * | 2013-06-14 | 2013-11-27 | 严松法 | Square ram support stiffness compensation system of gantry machining center |
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