CN103350372A - 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 the machine tool accuracy bucking-out system, especially a kind of bucking-out system for compensation 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 be at the mobile pillow functional part of 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 the square ram structure form, finish grindes the formation guide pass on four sides with square ram, forms the sliding friction guideway with the saddle inner surface, and accompanies by hydrodynamic lubrication or oil lubrication.The microgap that sliding friction pair exists, to form lubricating oil film, the precondition of the side's of being beneficial to ram movement, meanwhile, the existence of microgap also is the key factor that affects ram and saddle fit structure, when the microgap is too small, meeting so that borderline oil film break, frictional resistance significantly rises, thereby occurs that Digit Control Machine Tool Z axis feeding positioning accuracy descends, the aggravation of low speed jerking motion phenomenon, the bad phenomenon such as smooth, unstable wear even locking of sliding; And when the microgap is excessive, contact stiffness between ram and the saddle weakens greatly, thereby cause the problems such as processing is trembled, the out-of-flatness of part finished surface, meanwhile, gap width δ itself is the factor of influence of machine finish, and being accompanied by stretching out of ram, gap width δ is amplified at double on the impact of positioning accuracy, thereby causes the positioning accuracy of lathe, repetitive positioning accuracy to reduce.
Based on above-mentioned analysis, the control of the microgap value between square ram and the saddle structure plays an important role for the overall performance that promotes lathe, machining accuracy etc.The concrete analysis of the assembly structure form between side's ram and the saddle, helping to deepen the other side's ram microgap forms the understanding of reason and proposes a kind of rationally effectively compensation method, concrete assembly structure for square ram and saddle, see Figure of description 1 and 2 for details, analysis for concrete structure is further described in detail hereinafter at specification.
Compensation and control for square ram rail plate microgap, belong to microgap compensation or microgap feeding category, little feeding mode commonly used comprises mechanical type, mangneto formula, piezoelectric type, telescopic, the fluid pressure type of heat, wherein, when little feeding mode is used for the compensation of ram microgap, lathe side, the support stiffness of little feeding deflection and the resolution ratio of little distortion have been proposed very high requirement, the synthesise various factor analysis, the hydraulic pressure feeding mode that declines is a kind of comparatively desirable solution.The present invention adopts Circular Thin pressure structure form to realize little feed compensation of fluid pressure type, Circular Thin pressure structure can be arranged on the original gap of lathe and adjust the wedge shape filler rod, when adopting this scheme, minimum to the original structural modification of lathe, but also exist some shortcomings, for example: the separate design of the oil leab that Circular Thin pressurization oil duct and the slip of square ram are required, the sliding friction between Circular Thin pressure structure bending deformation form point and the square ram cause compensation point wearing and tearing aggravation etc.
Summary of the invention
Adopt rail plate to exist the microgap in order to overcome gantry machining center side's ram, support stiffness descended when the side's of causing ram stretched out, degradation problem under machining accuracy decline when causing machine tooling, vibration cutting, the piece surface crudy the present invention proposes a kind of according to square ram Z axis feeding coordinate signal and 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 consist of, it is characterized in that, described compensation drive plate device comprises the compensation drive plate, the flange guide pin bushing, guide pillar consists of, described flange guide pin bushing is fixed on the described compensation drive plate, described guide pillar is fixed on saddle structure or the saddle covering plate structure, described compensation drive plate slidably is installed on the described guide pillar by described flange guide pin bushing, be " ten " word on the described compensation drive plate and be arranged symmetrically with four little gradient wedge shape installed surfaces, the gap is adjusted the wedge shape filler rod and is fixed on the described little gradient wedge shape installed surface by contiguous block; Be provided with M Circular Thin pressure structure on each described little gradient wedge shape installed surface, described Circular Thin pressure structure is made 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 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 is regulated, the pressure oil of constant flow rate is by the adjusting of electromagnetic proportion relief valve realization pressure, and the pressure oil after pressure is regulated is transported to the oiler of described Circular Thin pressure structure by conduit under fluid pressure through the shunt piece; Described electric control module comprises the control amplifier of lathe 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 slidably is installed on the described saddle structure by flange guide pin bushing, guide pillar structure, and another block compensation drive plate slidably is installed on the described saddle covering plate structure by flange guide pin bushing, guide pillar structure.
Further again, be " ten " word on the described compensation drive plate and be arranged symmetrically with four little gradient wedge shape installed surfaces, described little gradient wedge shape installed surface is the installed surface that the wedge shape filler rod is adjusted in the gap, is the lozenges of little gradient, slope is 1:100; On the described little gradient wedge shape installed surface Circular Thin pressure structure is set, the elastic springing thin-walled of described Circular Thin pressure structure is arranged on the back plane of described compensation drive plate, have the sealing ring deep gouge on the described end cap, mounting O-shaped sealing ring in the described sealing ring deep gouge, described end cap is fixed by screws in the counterbore of little gradient wedge shape installed surface, form the pressurization oil pocket, the thickness of described end cap does not exceed little gradient wedge shape installed surface.
As preferred a kind of scheme: on each described little gradient wedge shape installed surface two Circular Thin pressure structures are set.
As preferred another kind of scheme: described control pressurer system can be realized by the overflow voltage-regulating system of constant flow the internal pressurization oil pocket pressure regulation of Circular Thin pressure structure, machine tool hydraulic station power source part is realized the security settings of hydraulic system maximum pressure value by overflow valve, the working connection of machine tool hydraulic station power source part is received the 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 behind the hydraulic valve block oiler, be connected on the flow speed control valve, realized the automatic adjusting of pressure by electromagnetic proportion relief valve through the pressure oil of speed governing, pressure oil after the pressure regulation is connected to the oiler of described Circular Thin pressure structure through pipeline by the hydraulic valve block oil-out, also be provided with the pressure ga(u)ge damper connector on the described hydraulic valve block, overfall, the overfall of described electromagnetic proportion relief valve take back separately fuel tank after connecing a check valve.
As preferred another scheme: described control pressurer system also can be realized by the vacuum regulator system of throttling the internal pressurization oil pocket pressure regulation of Circular Thin pressure structure, an oil circuit of system dynamic source, machine tool hydraulic station part is connected on the 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 the shunt piece, the overfall of described solenoid-operated proportional low-pressure relief valve takes back separately fuel tank after connecing check valve, be connected on the P mouth of bi-bit bi-pass reversal valve on the Long-distance Control X mouth of the proportional pilot valve of described solenoid-operated proportional low-pressure relief valve, the B mouth of described bi-bit bi-pass reversal valve is connected with overflow valve, the A mouth blocks, and the T mouth takes back the draining road.
As preferred another scheme: described electric control module comprises the control amplifier of lathe Z axis feeding coordinate signal unit, D/A converter and proportional pressure valve.Described lathe 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 be processed the Z axis coordinate signal, signal after the processing changes the aanalogvoltage of 0-10V into behind D/A converter, the aanalogvoltage of output changes the analog current that drives proportional pressure valve into behind the control amplifier of proportional pressure valve.
Beneficial effect of the present invention is embodied in:
When being arranged on the gap, the Circular Thin pressure structure of square ram microgap bucking-out system adjusts the wedge shape filler rod, exist following deficiency: first, contact point or the contact-making surface of backlash compensation actuator deflection displacement output are in the dynamic friction state all the time, can aggravate to compensate the material friction wearing and tearing at contact point place; The second, the hydrodynamic lubrication pipeline structure in the filler rod to be changed, this scheme 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 advantage is embodied in: first, deflection displacement output compensation contact point appears on the supporting surface of compensation drive plate and saddle or saddle cover plate, the action that exists only is compensation output and withdrawal, the problem that it not only can overcome fretting wear drives whole filler rod motion simultaneously, does not change the face way of contact of ram and saddle; The second, the pressurization oil duct separates with oil leab, mutually noninterfere, and it is very convenient that oil duct is arranged.
Field adjustable explanation, this system can Effective Raise machine ram support stiffness, improves the piece surface crudy of lathe, simultaneously Machine Tool Positioning Accuracy is had certain compensation effect.
Description of drawings
Fig. 1 is gantry machining center ram saddle assembly structure schematic diagram
Fig. 2 is the structural representation that wedge shape filler rod and saddle are adjusted in gantry machining center ram, gap
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
The specific embodiment
In conjunction with Fig. 1～Fig. 8, before the embodiment that introduces gantry machining center side of the present invention ram support stiffness bucking-out system, paper gantry machining center square ram structure, assembly relation and square ram rail plate clearance adjustment method.
Ram and saddle structure adopt the rail plate fit form, and its concrete structure is as follows: by reference to the accompanying drawings 1,2, and square ram 1 is installed in the saddle 101, and is fixing with saddle cover plate 102, forms the completely encircle structure.Ram sliding friction on the mating surface of saddle has four guide supporting faces, and two face correct grindings are wherein arranged on the saddle, be datum level, and cooperate formation to encircle two other face of shape with these two faces, namely the working face on another side and the saddle cover plate on the saddle is that face is adjusted in the gap.In existing lathe mounting technology, the microgap value δ when adjusting the machine ram slip by gap adjustment wedge shape filler rod 103, this microgap value δ becomes one of restraining factors that affect machine finish.The original gap of ram rail plate is adjusted, and generally adopts at present the artificial method of adjusting, be assembled to ram on the saddle after, the assembling of saddle cover plate is locked.There is certain gap in ram in saddle inside, adjusts wedge shape filler rod 103 with the gap and carries out trace adjustment, and main basis for estimation is the resistance to sliding of ram under hydrodynamic lubrication.Concrete method of adjustment and operation principle are seen accompanying drawing 2, by the adjustment screw on the contiguous block 3, make the gap adjust wedge shape filler rod 103 and slide at the little gradient wedge shape installed surface of saddle, and the adjusting play size, and amount of taper is 1:100.Original gap just can not change in case adjustment is finished.So microgap value δ namely finishes the gap and adjusts the gap that the adjustment of wedge shape filler rod forms afterwards.
Introduced after the assembly structure of traditional gantry machining center ram, introduced by reference to the accompanying drawings side's ram support stiffness bucking-out system of the present invention.
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 consist of, described compensation drive plate device comprises compensation drive plate 2, flange guide pin bushing 2-3, guide pillar consists of, described flange guide pin bushing 2-3 is fixed on the described compensation drive plate 2, described guide pillar is fixed on saddle structure or the saddle covering plate structure, described compensation drive plate slidably is installed on the 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 the flange guide pin bushing, guide pillar structure slidably is installed on the described saddle structure, and another block compensation drive plate is by the flange guide pin bushing, guide pillar structure slidably is installed on the described saddle covering plate structure.Particularly, for traditional gantry machining center, on the gap adjustment face of the described compensation drive plate side of being arranged on ram.
Be " ten " word on the described compensation drive plate and be arranged symmetrically with four little gradient wedge shape installed surface 2-1, the gap is adjusted wedge shape filler rod 103 and is fixed on the described little gradient wedge shape installed surface 2-1 by contiguous block 3; Be provided with two Circular Thin pressure structure 2-2 on each described little gradient wedge shape installed surface, described Circular Thin pressure structure 2-2 is made 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.
Be " ten " word on the described compensation drive plate and be arranged symmetrically with four little gradient wedge shape installed surfaces, described little gradient wedge shape installed surface 2-1 is the installed surface that the wedge shape filler rod is adjusted in the gap, is the lozenges of little gradient, and slope is 1:100; On the described little gradient wedge shape installed surface Circular Thin pressure structure is set, the elastic springing thin-walled 2-6 of described Circular Thin pressure structure is arranged on the back plane of described compensation drive plate, have the sealing ring deep gouge on the described end cap, mounting O-shaped sealing ring 2-8 in the described sealing ring deep gouge, described end cap is fixed by screws in the counterbore of little gradient wedge shape installed surface, form the pressurization oil pocket, described pressurization oil pocket is realized the supply of pressure oil by the pressurization oil duct.The thickness of described end cap does not exceed little gradient wedge shape installed surface, does not affect the gap and adjusts wedge shape filler rod normal mounting at little gradient wedge shape installed surface.
Elastic springing need to could occur in the Circular Thin pressure structure of side's ram support stiffness bucking-out system under the effect of pressure oil, its basic demand to hydraulic control system is: can be according to coordinate figure corresponding to lathe Z axis feeding, provide fast the electrical compensation value by electric control system, hydraulic control system responds required hydraulic fluid pressure output valve fast according to the electrical compensation value, and backlash compensation actuator input pressure oil pressure value responds with Z axis feeding coordinate figure between 0～8Mpa; Control requirement to flow, because the backlash compensation actuator is the sealing pressurised chamber, internal capacity only is 75ml, and the flow value that pressure-responsive is corresponding changes very little, and flow needs the pressure-responsive in the complete earial drainage guarantee actuator, so require very low to flow value, if the Hydraulic Station branch flow is excessive, not only can cause the flow waste, system causes system's temperature rise too high because of excessive overflow, and system may cause because of backflow the local assault of hydraulic pressure, unfavorable system stability when reduction of blood pressure in high-speed.Based on above requirement, proposed to satisfy the control pressurer system of above demand.
Described control pressurer system is made 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 is regulated, the pressure oil of constant flow rate is by the adjusting of electromagnetic proportion relief valve 4-3 realization pressure, and the pressure oil after pressure is regulated is transported to the oiler 2-4 of described Circular Thin pressure structure by conduit under fluid pressure through shunt piece 4-7.
Described control pressurer system can be realized by the overflow voltage-regulating system of constant flow the internal pressurization oil pocket pressure regulation of Circular Thin pressure structure, its structural principle is seen Fig. 7, machine tool hydraulic station power source part 4-1 is realized the security settings of hydraulic system maximum pressure value by overflow valve 4-8, the working connection 4-9 of machine tool hydraulic station power source part receives the 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 behind hydraulic valve block oiler 4-11, be connected on the flow speed control valve 4-2, realized the automatic adjusting of pressure by electromagnetic proportion relief valve 4-3 through the pressure oil of speed governing, pressure oil after the pressure regulation is connected to the oiler of described Circular Thin pressure structure through pipeline by hydraulic valve block oil-out 4-12, also be provided with pressure ga(u)ge damper connector 4-14 on the described hydraulic valve block, overfall 4-13, the overfall of described electromagnetic proportion relief valve takes back separately fuel tank after meeting a check valve 4-4, and the design of hydraulic valve block 4-10 has comprised the along separate routes function of piece.
For the overflow voltage-regulating system of above-mentioned constant flow, flow speed control valve makes the flow that enters electromagnetic proportion relief valve keep constant, and the range of flow of adjusting satisfies the maximum excess flow requirement of electromagnetic proportion relief valve between 0.6～0.7L/min.Electromagnetic proportion relief valve adopts band position sensor feedback type, improves the pressure 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 from that fluid in the electromagnetic proportion relief valve drain mast from letting out fully because of gravity to get back to fuel tank, also be convenient to the dismounting electromagnetic proportion relief valve simultaneously, otherwise siphonage may be with the oily suck-back in the fuel tank.
Described control pressurer system also can be realized by the vacuum regulator system of throttling the internal pressurization oil pocket pressure regulation of Circular Thin pressure structure, its structural principle is seen Fig. 8, an oil circuit of system dynamic source, machine tool hydraulic station part is through being connected to after choke valve 4-15 or the throttle orifice throttling on the solenoid-operated proportional low-pressure relief valve 4-16, hydraulic oil after pressure regulation is connected respectively to the oiler of Circular Thin pressure structure by the shunt piece, the overfall of described solenoid-operated proportional low-pressure relief valve takes back separately fuel tank after connecing check valve, be connected on the P mouth of bi-bit bi-pass reversal valve 4-17 on the Long-distance Control X mouth of the proportional pilot valve of described solenoid-operated proportional low-pressure relief valve, the B mouth of described bi-bit bi-pass reversal valve is connected with overflow valve 4-18, the A mouth blocks, and the T mouth takes back the draining road.
For the control pressurer system shown in accompanying drawing 7, the accompanying drawing 8, the difference of the two and strengths and weaknesses analysis are as follows: first, accompanying drawing 7 control pressurer systems adopt electromagnetic proportion relief valve to carry out pressure control, utilize flow control valve to carry out flow restriction, satisfy the requirement of sealing compression system.This control system is simple in structure, development cost is low, because electromagnetic proportion relief valve is band position-feedback type direct-acting type pressure control valve, the response speed of hydraulic system is faster than accompanying drawing 8 systems, but the override pressure of hydraulic system is relatively large, and accuracy is relatively relatively poor.The main deficiency of another of this control system is that the more important that proportioning valve is different from servo valve is " covering at zero point " problem, minimum adjusting pressure namely arranged and regulates the dead band, and all be to regulate the dead band before the controller electric current 200mA.Because pumping plant meeting continuous firing, when system during without unloading-structure, proportioning valve is minimum to transfer to minimum setting pressure with pressure, that is to say, Circular Thin pressure structure is out of shape under pressure oil always, only has when lathe quits work, and Circular Thin pressure structure could be recovered, so, easier generation fatigue damage.Second, accompanying drawing 8 control pressurer systems adopt the solenoid-operated proportional low-pressure relief valve, dispose the Long-distance Control overflow valve, its cost is higher, with respect to straight type proportion overflow valve, response speed is slow (this system is less demanding to response speed), but the solenoid-operated proportional low-pressure relief valve is the piloted reducer structure, the balancing spring rigidity of main valve is very little, so the open and shut characteristic of this valve is better, override pressure (being the difference between setting and the actual value) is less, and the pressure 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, far control the utilization of mouthful X, can remedy the deficiency of proportioning valve " covering at zero point ".
Described electric control module comprises the control amplifier of lathe Z axis feeding coordinate signal unit, D/A converter and proportional pressure valve.Described lathe Z axis feeding coordinate signal unit comprises Z axis feeding grating scale, the 5-1 of Machine Tools Electric system, the PLC module of Machine Tools Electric system can be processed the Z axis coordinate signal, signal after the processing changes the aanalogvoltage of 0-10V into behind D/A converter 5-2, the aanalogvoltage of output changes the analog current that drives proportional pressure valve into behind the control amplifier 5-3 of proportional pressure valve.
Side's ram support stiffness bucking-out system is carried out adaptive equalization according to Z axis displacement coordinate signal, so this system has proposed the requirement of expansion to the Electrical Control of Machinery Tools system: the Electrical Control of Machinery Tools system can be converted into Z axis displacement coordinate signal the voltage analog signal output of 0～10V, simultaneously, by electrical system PLC processor, can export according to actual condition electrical compensation value or the continuous analog signal of discrete type.
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 that gathers is sinusoidal wave digital signal, this data signal is directly passed to the PLC module of Machine Tools Electric system, after logical process, changed the voltage analog signal of city 0-10V by D/A conversion electron module, voltage analog signal is input on the control amplifier of proportional pressure valve, be output as current analog signal, this current analog signal can be used for driving the electromagnet of proportional pressure valve, thereby the force value of the system of setting, the system pressure value of setting up is used for driving Circular Thin pressure structure generation elastic springing, thereby realizes the backlash compensation that support stiffness strengthens.After field adjustable, set up out after the best relation curve between Z axis displacement coordinate and the backlash compensation value, process the proportionality coefficient of (LED program) and proportional pressure valve control amplifier through the ladder diagram of PLC and set, can satisfy the demand of on-the-spot actual condition.
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 consist of, it is characterized in that, described compensation drive plate device comprises the compensation drive plate, the flange guide pin bushing, guide pillar consists of, described flange guide pin bushing is fixed on the described compensation drive plate, described guide pillar is fixed on saddle structure or the saddle covering plate structure, described compensation drive plate slidably is installed on the described guide pillar by described flange guide pin bushing, be " ten " word on the described compensation drive plate and be arranged symmetrically with four little gradient wedge shape installed surfaces, the gap is adjusted the wedge shape filler rod and is fixed on the described little gradient wedge shape installed surface by contiguous block; Be provided with M Circular Thin pressure structure on each described little gradient wedge shape installed surface, described Circular Thin pressure structure is made 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 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 is regulated, the pressure oil of constant flow rate is by the adjusting of electromagnetic proportion relief valve realization pressure, and the pressure oil after pressure is regulated is transported to the oiler of described Circular Thin pressure structure by conduit under fluid pressure through the shunt piece; Described electric control module comprises the control amplifier of lathe 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 slidably is installed on the described saddle structure by flange guide pin bushing, guide pillar structure, and another block compensation drive plate slidably is installed on the 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: be " ten " word on the described compensation drive plate and be arranged symmetrically with four little gradient wedge shape installed surfaces, described little gradient wedge shape installed surface is the installed surface that the wedge shape filler rod is adjusted in the gap, be the lozenges of little gradient, slope is 1:100; On the described little gradient wedge shape installed surface Circular Thin pressure structure is set, the elastic springing thin-walled of described Circular Thin pressure structure is arranged on the back plane of described compensation drive plate, have the sealing ring deep gouge on the described end cap, mounting O-shaped sealing ring in the described sealing ring deep gouge, described end cap is fixed by screws in the counterbore of little gradient wedge shape installed surface, form the pressurization oil pocket, the thickness of described end cap does not exceed little gradient wedge shape installed surface.
4. such as claim 1 or 2 or 3 described side's ram support stiffness bucking-out systems, it is characterized in that: on each described little gradient wedge shape installed surface two Circular Thin pressure structures are set.
5. such as claim 1 or 2 or 3 described side's ram support stiffness bucking-out systems, it is characterized in that: described control pressurer system can be realized by the overflow voltage-regulating system of constant flow the internal pressurization oil pocket pressure regulation of Circular Thin pressure structure, machine tool hydraulic station power source part is realized the security settings of hydraulic system maximum pressure value by overflow valve, the working connection of machine tool hydraulic station power source part is received the 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 behind the hydraulic valve block oiler, be connected on the flow speed control valve, realized the automatic adjusting of pressure by electromagnetic proportion relief valve through the pressure oil of speed governing, pressure oil after the pressure regulation is connected to the oiler of described Circular Thin pressure structure through pipeline by the hydraulic valve block oil-out, also be provided with the pressure ga(u)ge damper connector on the described hydraulic valve block, overfall, the overfall of described electromagnetic proportion relief valve take back separately fuel tank after connecing a check valve.
6. such as claim 1 or 2 or 3 described side's ram support stiffness bucking-out systems, it is characterized in that: described control pressurer system also can be realized by the vacuum regulator system of throttling the internal pressurization oil pocket pressure regulation of Circular Thin pressure structure, an oil circuit of system dynamic source, machine tool hydraulic station part is connected on the 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 the shunt piece, the overfall of described solenoid-operated proportional low-pressure relief valve takes back separately fuel tank after connecing check valve, be connected on the P mouth of bi-bit bi-pass reversal valve on the Long-distance Control X mouth of the proportional pilot valve of described solenoid-operated proportional low-pressure relief valve, the B mouth of described bi-bit bi-pass reversal valve is connected with overflow valve, the A mouth blocks, and the T mouth takes back the draining road.
7. such as claim 1 or 2 or 3 described side's ram support stiffness bucking-out systems, it is characterized in that: described electric control module comprises the control amplifier of lathe Z axis feeding coordinate signal unit, D/A converter and proportional pressure valve.Described lathe 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 be processed the Z axis coordinate signal, signal after the processing changes the aanalogvoltage of 0-10V into behind D/A converter, the aanalogvoltage of output changes the analog current that drives proportional pressure valve into behind the control amplifier of proportional pressure valve.
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106050778A (en) * | 2016-07-11 | 2016-10-26 | 润琛液压机械南通有限公司 | Manifold valve block for static pile pressing machine |
| 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 |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| 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 |
-
2013
- 2013-06-14 CN CN201310238360.0A patent/CN103350372B/en not_active Expired - Fee Related
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| 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 |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106050778A (en) * | 2016-07-11 | 2016-10-26 | 润琛液压机械南通有限公司 | Manifold valve block for static pile pressing machine |
| 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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| CN103350372B (en) | 2015-07-08 |
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