WO2011080820A1 - ラムの撓み補正装置 - Google Patents
ラムの撓み補正装置 Download PDFInfo
- Publication number
- WO2011080820A1 WO2011080820A1 PCT/JP2009/071754 JP2009071754W WO2011080820A1 WO 2011080820 A1 WO2011080820 A1 WO 2011080820A1 JP 2009071754 W JP2009071754 W JP 2009071754W WO 2011080820 A1 WO2011080820 A1 WO 2011080820A1
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- WIPO (PCT)
- Prior art keywords
- ram
- saddle
- hydrostatic bearing
- hydraulic pressure
- spindle unit
- Prior art date
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Classifications
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
- B23B—TURNING; BORING
- B23B35/00—Methods for boring or drilling, or for working essentially requiring the use of boring or drilling machines; Use of auxiliary equipment in connection with such methods
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
- B23Q—DETAILS, COMPONENTS, OR ACCESSORIES FOR MACHINE TOOLS, e.g. ARRANGEMENTS FOR COPYING OR CONTROLLING; MACHINE TOOLS IN GENERAL CHARACTERISED BY THE CONSTRUCTION OF PARTICULAR DETAILS OR COMPONENTS; COMBINATIONS OR ASSOCIATIONS OF METAL-WORKING MACHINES, NOT DIRECTED TO A PARTICULAR RESULT
- B23Q1/00—Members which are comprised in the general build-up of a form of machine, particularly relatively large fixed members
- B23Q1/25—Movable or adjustable work or tool supports
- B23Q1/26—Movable or adjustable work or tool supports characterised by constructional features relating to the co-operation of relatively movable members; Means for preventing relative movement of such members
- B23Q1/38—Movable or adjustable work or tool supports characterised by constructional features relating to the co-operation of relatively movable members; Means for preventing relative movement of such members using fluid bearings or fluid cushion supports
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
- B23Q—DETAILS, COMPONENTS, OR ACCESSORIES FOR MACHINE TOOLS, e.g. ARRANGEMENTS FOR COPYING OR CONTROLLING; MACHINE TOOLS IN GENERAL CHARACTERISED BY THE CONSTRUCTION OF PARTICULAR DETAILS OR COMPONENTS; COMBINATIONS OR ASSOCIATIONS OF METAL-WORKING MACHINES, NOT DIRECTED TO A PARTICULAR RESULT
- B23Q1/00—Members which are comprised in the general build-up of a form of machine, particularly relatively large fixed members
- B23Q1/25—Movable or adjustable work or tool supports
- B23Q1/26—Movable or adjustable work or tool supports characterised by constructional features relating to the co-operation of relatively movable members; Means for preventing relative movement of such members
- B23Q1/38—Movable or adjustable work or tool supports characterised by constructional features relating to the co-operation of relatively movable members; Means for preventing relative movement of such members using fluid bearings or fluid cushion supports
- B23Q1/385—Movable or adjustable work or tool supports characterised by constructional features relating to the co-operation of relatively movable members; Means for preventing relative movement of such members using fluid bearings or fluid cushion supports in which the thickness of the fluid-layer is adjustable
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
- B23Q—DETAILS, COMPONENTS, OR ACCESSORIES FOR MACHINE TOOLS, e.g. ARRANGEMENTS FOR COPYING OR CONTROLLING; MACHINE TOOLS IN GENERAL CHARACTERISED BY THE CONSTRUCTION OF PARTICULAR DETAILS OR COMPONENTS; COMBINATIONS OR ASSOCIATIONS OF METAL-WORKING MACHINES, NOT DIRECTED TO A PARTICULAR RESULT
- B23Q1/00—Members which are comprised in the general build-up of a form of machine, particularly relatively large fixed members
- B23Q1/70—Stationary or movable members for carrying working-spindles for attachment of tools or work
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
- B23Q—DETAILS, COMPONENTS, OR ACCESSORIES FOR MACHINE TOOLS, e.g. ARRANGEMENTS FOR COPYING OR CONTROLLING; MACHINE TOOLS IN GENERAL CHARACTERISED BY THE CONSTRUCTION OF PARTICULAR DETAILS OR COMPONENTS; COMBINATIONS OR ASSOCIATIONS OF METAL-WORKING MACHINES, NOT DIRECTED TO A PARTICULAR RESULT
- B23Q11/00—Accessories fitted to machine tools for keeping tools or parts of the machine in good working condition or for cooling work; Safety devices specially combined with or arranged in, or specially adapted for use in connection with, machine tools
- B23Q11/001—Arrangements compensating weight or flexion on parts of the machine
- B23Q11/0028—Arrangements compensating weight or flexion on parts of the machine by actively reacting to a change of the configuration of the machine
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
- B23Q—DETAILS, COMPONENTS, OR ACCESSORIES FOR MACHINE TOOLS, e.g. ARRANGEMENTS FOR COPYING OR CONTROLLING; MACHINE TOOLS IN GENERAL CHARACTERISED BY THE CONSTRUCTION OF PARTICULAR DETAILS OR COMPONENTS; COMBINATIONS OR ASSOCIATIONS OF METAL-WORKING MACHINES, NOT DIRECTED TO A PARTICULAR RESULT
- B23Q15/00—Automatic control or regulation of feed movement, cutting velocity or position of tool or work
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T408/00—Cutting by use of rotating axially moving tool
- Y10T408/16—Cutting by use of rotating axially moving tool with control means energized in response to activator stimulated by condition sensor
- Y10T408/17—Cutting by use of rotating axially moving tool with control means energized in response to activator stimulated by condition sensor to control infeed
- Y10T408/172—Responsive to Tool
Definitions
- the ram of the horizontal boring machine incorporates the spindle unit 15 and is fitted to the saddle 13 so as to be slidable in the horizontal direction.
- the ram 1 moves up and down along the guide of the column 14. Since the saddle 13 is cantilevered, as shown schematically in FIG. 12, when the ram 1 is retracted, the ram 1 is hardly bent as shown in FIG.
- the ram 1 is moved in the direction of the arrow W in a cantilever state, which causes a problem that the center 1a in FIG. 12B bends as 1b.
- Patent Document 2 Japanese Patent Laid-Open No. 2003-103434
- Patent Document 2 Japanese Patent Laid-Open No. 2003-103434
- a spindle head (saddle) that supports a ram so as to be slidable in the left-right direction is configured to move up and down with two ball screws on the left and right sides.
- the ball screw is driven by the first servo motor, the ball screw on the root side is driven by the second servo motor, and when the ram is discharged to the tip side, the ball screw is rotated more than the spindle movement command before correction, The spindle head is lifted, and the second servo motor rotates the ball screw less than the correction spindle movement command before the correction so as to lower the spindle head, and maintains the attitude of the spindle head as a whole as a whole. Therefore, since the guide surface of the ram is kept horizontal, it is possible to prevent an error from occurring in the position of the spindle head at the tip of the ram.
- the present invention includes a ram that eliminates the need for a balance weight for weight balance, and that can correct the positional deviation of the tip of the spindle unit caused by the ram feeding with a simple structure and low device cost.
- the purpose is to provide a machine tool.
- the first invention includes a saddle that moves up and down along a column guide, and a ram that has a built-in spindle unit and is slidably fitted in the saddle in the horizontal direction.
- the saddle is supported on the column by using a plurality of hydrostatic bearings in the longitudinal direction of the column, and the hydraulic pressure of the hydrostatic bearing is changed to increase the straightness of the ram in the main axis direction.
- the control means includes a hydraulic pressure of a hydrostatic bearing installed in the ram feeding direction and below the main shaft of the main spindle unit among a plurality of hydrostatic bearings that support the saddle in the longitudinal direction of the column. It is configured to control and maintain the straightness of the ram in the main axis direction.
- the second invention of the present invention can be configured as follows. That is, in a machine tool including a saddle that moves up and down along a column guide and a ram that incorporates a spindle unit and is slidably fitted in the saddle in the horizontal direction, the ram is moved in the longitudinal direction of the ram.
- the hydrostatic bearing is supported by the saddle using a plurality of hydrostatic bearings, and the hydraulic pressure of the hydrostatic bearing is changed to maintain the straightness of the ram in the main shaft direction.
- control means controls the hydraulic pressure of a hydrostatic bearing installed in the ram feeding direction and below the main shaft of the main spindle unit among a plurality of hydrostatic bearings that support the ram on the saddle. The straightness of the ram in the main axis direction is maintained.
- the control means in addition to the hydrostatic bearing installed in the ram feeding direction and below the main spindle of the main spindle unit, the control means includes a main axis of the main spindle unit and a direction perpendicular to the main spindle.
- the hydraulic pressure is also controlled for the hydrostatic bearing installed at a symmetrical position with respect to the intersection with the center line of the saddle so that the straightness in the main shaft direction of the ram is maintained.
- the specific means in the control means includes a throttle device that restricts the amount of oil to the hydrostatic bearing, and a hydraulic sensor that measures the hydraulic pressure to each of the hydrostatic bearings, and the control means includes a hydraulic pressure from the hydraulic sensor. Based on the detected value, the throttle amount of the throttle device is controlled so as to be the target hydraulic pressure of the hydrostatic bearing.
- a throttle device that throttles the amount of oil to the hydrostatic bearing is provided, and the control means reduces the throttle amount so that the throttle amount of the throttle device becomes a throttle flow rate calculated to become the target hydraulic pressure of the hydrostatic bearing. To control.
- the hydraulic pressure of the hydrostatic bearing in accordance with the displacement of the ram in the vertical direction, it is possible to correct the deviation of the main spindle unit position by the inclination of the ram according to the hydraulic pressure control. Therefore, according to the present invention, the straightness of the ram in the main axis direction can be maintained with high accuracy by the correction method, and high machining accuracy can be obtained. In addition, since it can be corrected by adjusting the hydraulic pressure of the plurality of hydrostatic bearings, a conventional balance weight is not required, and high processing accuracy as described above can be obtained with a simple structure and low equipment cost. Can do.
- the main shaft is in the ram feeding direction. Since the hydraulic pressure of the hydrostatic bearing installed below the main shaft of the unit is controlled, the straightness of the ram in the main shaft direction can be maintained with a simple configuration by the inclination of the saddle according to the control of the hydraulic pressure. In addition, among the plurality of hydrostatic bearings that support the ram on the saddle, the hydraulic pressure of the hydrostatic bearing installed in the ram feeding direction and below the main spindle of the main spindle unit is controlled. The straightness of the ram in the main axis direction can be maintained with a simple configuration by the inclination of the ram according to the above.
- the hydrostatic bearing controls the hydraulic pressure of the hydrostatic bearing installed at a symmetrical position with respect to the intersection of the main shaft of the main shaft unit and the center line of the column perpendicular to the main shaft, and the ram Can be corrected by, for example, the inclination of the saddle according to the control of the hydraulic pressure of the two hydrostatic bearings of the hydrostatic bearing 2a and the hydrostatic bearing 3a shown in FIG.
- the ram is extended and below the main shaft of the main spindle unit.
- the hydrostatic bearing is a hydrostatic bearing installed at a symmetrical position with respect to the intersection of the main shaft of the main spindle unit and the center line of the saddle perpendicular to the main shaft. Since the hydraulic pressure is controlled to maintain the straightness of the ram in the main shaft direction, that is, it can be corrected by the inclination of the ram according to the control of the hydraulic pressure of the two hydrostatic bearings.
- a throttle device for reducing the amount of oil to the static pressure bearing, and a hydraulic sensor for measuring the hydraulic pressure to each of the static pressure bearings the control means is based on a hydraulic pressure detection value from the hydraulic sensor Since the throttle amount of the throttle device is controlled so as to be the target hydraulic pressure of the bearing, the displacement of the spindle unit position due to the inclination angle of the ram and the deflection of the ram according to the hydraulic pressure control is determined by each hydrostatic sensor. Since the result of detecting the hydraulic pressure of the bearing is fed back, the pressure of the hydrostatic bearing can be maintained at an appropriate value with high accuracy.
- a throttle device that throttles the amount of oil to the hydrostatic bearing is provided, and the control means reduces the throttle amount so that the throttle amount of the throttle device becomes a throttle flow rate calculated to become the target hydraulic pressure of the hydrostatic bearing. Therefore, a control configuration that does not use a hydraulic sensor can be achieved.
- (A), (B) is a block diagram of the combination body of the column, saddle, and ram concerning 1st Example of this invention. It is a block diagram of the combination body of the column, saddle, and ram concerning 2nd Example of this invention. It is a block diagram of the combination body of the column concerning the 3rd Example of this invention, a saddle, and a ram. It is a block diagram of the combination body of the column concerning the 4th Example of this invention, a saddle, and a ram. It is a block diagram of the combination body of the column concerning the 5th Example of this invention, a saddle, and a ram.
- FIG. 1 is a configuration diagram of a combination of a column, a saddle, and a ram according to a first embodiment of the present invention. 1 to 5, the other configuration is the same as the portion excluding the balance weights 21 and 22 in FIG. 11 (except for the portion 19 surrounded by the broken line in FIG. 11).
- reference numeral 14 denotes a column
- a saddle 13 that moves up and down along the guide of the column 14 and a spindle unit 15 are built in and slidably fitted in the saddle 13 in the horizontal direction.
- the ram 1 is provided.
- the saddle 13 is supported at four places on the left and right sides by the hydrostatic bearings 2a and 2b on the moving end side of the ram 1 and by the hydrostatic bearings 3a and 3b on the base side.
- the hydrostatic bearing 2 a is a hydrostatic bearing 2 a, 2 b, 3 a, 3 b that supports the saddle 13 in the longitudinal direction of the column 14, and is in the feeding direction of the ram 1 and below the spindle of the spindle unit 15.
- the hydrostatic bearing is installed in the hydrostatic bearing, and the hydraulic pressure of the hydrostatic bearing 2a is controlled.
- the controller 10 increases the hydraulic pressure Pr 2a of the hydrostatic bearing 2a in accordance with the vertical displacement of the ram 1, that is, the deflection ⁇ , so as to maintain the straightness of the ram 1 in the main shaft direction 1s.
- FIG. 6 shows a method of correcting the deflection ⁇ by the inclination of the saddle 13 according to the increase of 2a .
- the flow coefficient Ki of the hydrostatic bearing i is estimated (step S4).
- Hydrostatic bearing i when the tilt angle theta (control for hydrostatic bearing 2a, except the hydrostatic bearing 2b, 3a, 3b) determine the pressure Pr i in (step S5).
- Pr i (1 / (1 + K i / Kc i )) ⁇ Ps i (3)
- Kc i Flow coefficient of variable throttle i
- Ps i Supply pressure of hydrostatic bearing i
- the throttle flow coefficient of the variable throttle is obtained and the throttle amount is controlled by the throttle flow coefficient, so that the control configuration can be simplified without using a hydraulic sensor.
- the straightness of the ram 1 in the main shaft direction 1 s can be maintained with high accuracy by the above correction method, and high machining accuracy can be obtained. Further, by adjusting the state of the hydraulic pressures and variable throttles of the plurality of hydrostatic bearings, the conventional balance weight is unnecessary (the broken line portion 19 is not required in FIG. 11), and the structure is simple and the apparatus cost is low. With such a device, high processing accuracy as described above can be obtained.
- the basic configuration is the same as that of the first embodiment, and the saddle 13 is supported at four places on the left and right sides by the hydrostatic bearings 2a and 2b on the moving end side of the ram 1 and supported by the hydrostatic bearings 3a and 3b on the root side. Has been.
- the oil discharged from the hydraulic pump 8 is connected to the hydrostatic bearing 2a through the variable throttle 6, and is connected to the hydrostatic bearing 3a through the variable throttle 7.
- the controller 10 controls the aperture amount of the variable aperture 6 and the aperture amount of the variable aperture 7.
- the hydrostatic bearing 2 a is a hydrostatic bearing 2 a, 2 b, 3 a, 3 b that supports the saddle 13 in the longitudinal direction of the column 14, and is in the feeding direction of the ram 1 and below the spindle of the spindle unit 15.
- the hydrostatic bearing 3a is located symmetrically with respect to the intersection C1 of the main shaft unit 15 and the center line of the column perpendicular to the main shaft with respect to the hydrostatic bearing 2a. It is an installed hydrostatic bearing and controls the hydraulic pressure for the hydrostatic bearings 2a and 3a.
- the controller 10 adjusts the throttle amount of the variable throttle 6 to increase the pressure of the static pressure bearing 2a, and adjusts the throttle amount of the variable throttle 7 to increase the pressure of the static pressure bearing 3a.
- FIG. 3 is a configuration diagram of a combination of a column, a saddle and a ram according to a third embodiment of the present invention.
- a saddle 13 that moves up and down along the guide of a column 14 (see FIG. 11)
- a ram 1 that incorporates a spindle unit 15 and that is slidably fitted in the saddle 13 in the horizontal direction are provided.
- the ram 1 is supported at two upper and lower positions in the longitudinal direction of the ram 1, that is, the lower side is supported by hydrostatic bearings 20a and 20b, and the upper side is supported by hydrostatic bearings 30a and 30b.
- Reference numeral 8 denotes a hydraulic pump, and oil discharged from the hydraulic pump 8 is connected to the hydrostatic bearing 20 a through a variable throttle 61.
- Reference numeral 10 denotes a controller which controls the aperture amount of the variable aperture 61.
- the hydrostatic bearing 20 a is a static hydrostatic bearing 20 a, 20 b, 30 a, 30 b that supports the ram 1 on the saddle 13.
- the hydrostatic bearing 20 a is installed in the extending direction of the ram 1 and below the spindle of the spindle unit 15. This is a pressure bearing, and the hydraulic pressure of the hydrostatic bearing 20a is controlled.
- the ram 1 moves as indicated by the arrow Y in FIG. It is displaced to the left and the center A bends like the center B.
- the controller 10 adjusts the throttle amount of the variable throttle 61, thereby increasing the pressure of the hydrostatic bearing 20a. Therefore, as shown by the arrow F in FIG. 3, the spindle unit 15 side of the ram 1 is lifted by the hydrostatic bearing 20a. As a result, the tip position of the ram 1 moves onto the center axis of the ram 1 when there is no deflection as indicated by the arrow S in FIG. 2, and the straightness in the direction of the spindle unit 15 is maintained.
- the controller 10 increases the hydraulic pressure Pr 20a of the hydrostatic bearing 20a in accordance with the vertical displacement of the ram 1, that is, the deflection ⁇ , so as to maintain the straightness of the ram 1 in the main shaft direction 1s.
- FIG. 8 shows a method of correcting the displacement of the spindle unit 15 position by the inclination angle ⁇ of the ram 1 according to the increase of 20a .
- W 20a W + W 30b + W 30a ⁇ W 20b (5)
- W Weight of ram 1 and attachment Refer to FIG. 3 for symbols other than those described above. Otherwise, it is the same as the first embodiment.
- FIG. 4 is a configuration diagram of a combination of a column, a saddle and a ram according to a fourth embodiment of the present invention.
- a saddle 13 that moves up and down along the guide of a column 14 (see FIG. 11) and a ram 1 that incorporates a spindle unit 15 and that is slidably fitted in the saddle 13 in the horizontal direction are provided.
- the ram 1 is supported at two upper and lower positions in the longitudinal direction of the ram 1, that is, the lower side is supported by hydrostatic bearings 20a and 20b, and the upper side is supported by hydrostatic bearings 30a and 30b.
- the hydrostatic bearing 30a is statically installed at a symmetrical position with respect to the intersection C2 of the main shaft unit 15 and the center line of the saddle 13 perpendicular to the main shaft with respect to the hydrostatic bearing 20a. This is a pressure bearing, and the hydraulic pressure is controlled with respect to the static pressure bearings 20a and 30a.
- the controller 10 adjusts the throttle amount of the variable throttle 32 to increase the pressure of the static pressure bearing 20a, and adjusts the throttle amount of the variable throttle 33 to increase the pressure of the static pressure bearing 30a.
- FIG. 9 shows a method of correcting the displacement of the spindle unit 15 position by the inclination angle ⁇ of the ram 1 according to the increase of the hydraulic pressures Pr 20a and Pr 30a .
- FIG. 9 is a flowchart of the control means for correcting the positional deviation of the spindle unit according to the fourth embodiment.
- the flow coefficient Kc 30a of the variable throttle 33 of the hydrostatic bearing 30a corresponding to the deflection amount ⁇ of the ram 1 tip obtained in step S52 is obtained.
- the flow coefficient Kc 30a of the variable throttle 33 in the formula of the Pri step S55 used to calculate the aperture adjustment amount S 33 in step S60.
- the third embodiment is the same as the third embodiment.
- the oil discharged from the hydraulic pump 8 is connected to the hydrostatic bearing 20a through the variable throttle 32, and is connected to the hydrostatic bearing 30a through the variable throttle 33.
- the oil discharged from the hydraulic pump 8 is connected to the hydrostatic bearing 20b through the variable throttle 34, and is connected to the hydrostatic bearing 30b through the variable throttle 35.
- a controller 10 controls the aperture amount of the variable aperture 32 and the aperture amount of the variable aperture 33.
- the aperture amount of the variable aperture 34 and the aperture amount of the variable aperture 35 are also controlled by the controller 10.
- Oil pressure sensors 37, 38, 39, 40 for measuring the oil pressure of the oil passages are provided in the oil passages to the hydrostatic bearings 20a, 20b and the hydrostatic bearings 30a, 30b.
- the hydraulic pressure detection values 39 and 40 are input to the controller 10.
- FIG. 10 shows a method of correcting the deviation of the position of the spindle unit 15 due to the inclination angle ⁇ of the ram 1 according to the increase of the hydraulic pressures Pr 20a and Pr 30a .
- FIG. 10 is a flowchart of the control means for correcting the deviation of the spindle unit position according to the fifth embodiment.
- the displacement of the main spindle unit 15 is detected by the hydraulic sensors 37, 38, 39, 40 so that the straightness of the ram 1 in the main shaft direction 1s is maintained. Since the detection result of the hydraulic pressure is fed back, it can be corrected with high accuracy.
- the inclination correction of the saddle 13 with respect to the column 14 of the first and second embodiments and the inclination correction of the ram 1 with respect to the saddle 13 of the third and fifth embodiments are combined to provide the saddle 13 with respect to the column 14 and the ram 1 with respect to the saddle 13.
- the tilt correction may be controlled as a whole.
- a machine tool equipped with a ram that eliminates the need for a balance weight for weight balance, can correct the misalignment of the tip of the spindle unit caused by the ram feeding, with a simple structure and low device cost. Can provide.
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Abstract
Description
前記サドル13には、主軸ユニット15を内蔵したラム1が水平方向に摺動可能に嵌合されている。
該サドル13、ラム1等は吊り金具18によってバランスウェイト20,21に連結され、該バランスウェイト20,21と前記サドル13、ラム1等の機材とが重量バランスを行っている。
かかる問題の解決案として、特許文献2(特開2003-103434号公報)が、提案されている。
従って、ラムの案内面は水平に保たれるため、ラム先端の主軸頭の位置に誤差が生じるのを防止できる。
即ち、前記制御手段は、前記サドルを前記コラムの長手方向に支持する複数の静圧軸受のうち、前記ラムの繰り出し方向であって前記主軸ユニットの主軸より下方に設置した静圧軸受の油圧を制御して、前記ラムの主軸方向の真直度を保持するように構成する。
即ち、前記制御手段は、前記ラムの繰り出し方向であって前記主軸ユニットの主軸より下方に設置した前記静圧軸受に加えて、該静圧軸受とは前記主軸ユニットの主軸と該主軸に直角方向の前記コラムの中心線との交点に対して対称位置に設置した静圧軸受に対しても油圧を制御して、前記ラムの主軸方向の真直度を保持するように構成する。
即ち、コラムの案内に沿って上下動するサドルと、主軸ユニットを内蔵し該サドルに水平方向に摺動可能に嵌合されたラムとを備えた工作機械において、前記ラムを該ラムの長手方向に複数の静圧軸受を用いて前記サドルに支持するとともに、該静圧軸受の油圧を変化させて、前記ラムの主軸方向への真直度を保持するように、前記静圧軸受の油圧をラムの垂直方向変位に従い制御することで、かかる油圧の制御に従うラムの傾斜により前記主軸ユニット位置のずれを補正する制御手段を備えたことを特徴とする。
即ち、前記制御手段は、前記ラムを前記サドルに支持する複数の静圧軸受のうち、前記ラムの繰り出し方向であって前記主軸ユニットの主軸より下方に設置した静圧軸受の油圧を制御して、前記ラムの主軸方向の真直度を保持するに構成する。
即ち、前記制御手段は、前記ラムの繰り出し方向であって前記主軸ユニットの主軸より下方に設置した前記静圧軸受に加えて、該静圧軸受とは前記主軸ユニットの主軸と該主軸に直角方向の前記サドルの中心線との交点に対して対称位置に設置した静圧軸受に対しても油圧を制御して、前記ラムの主軸方向の真直度を保持するように構成する。
また、前記静圧軸受への油量を絞る絞り装置を備え、前記制御手段は、該絞り装置の絞り量を前記静圧軸受の目標油圧になるために算出した絞り流量となるように絞り量を制御する。
また、前記ラムを該ラムの長手方向に複数の静圧軸受を用いて前記サドルに支持するとともに、該静圧軸受の油圧を変化させて、前記ラムの主軸方向への真直度を保持するように、前記静圧軸受の油圧をラムの垂直方向変位に従い制御することで、かかる油圧の制御に従うラムの傾斜により前記主軸ユニット位置のずれを補正できる。
従って、本発明によれば、前記の補正方法によってラムの主軸方向への真直度を高精度で保持することができ、高い加工精度を得ることができる。
また、前記複数の静圧軸受の油圧の調整によって補正できるので、従来のようなバランスウェイトは不要となり、簡単な構造で且つ装置コストが低廉な装置で、前記のような高い加工精度を得ることができる。
また、前記ラムを前記サドルに支持する複数の静圧軸受のうち、前記ラムの繰り出し方向であって前記主軸ユニットの主軸より下方に設置した静圧軸受の油圧を制御するので、かかる油圧の制御に従うラムの傾斜によって簡単な構成で前記ラムの主軸方向への真直度を保持できる。
また、ラムの先端を持ち上げる静圧軸受の負荷能力が上昇し、アタッチメントの追加等によるラムの重量増加に対応できる。
また、ラムの先端を持ち上げる静圧軸受の負荷能力が上昇し、アタッチメントの追加等によるラムの重量増加に対応できる。
図1(A)、(B)において、14はコラムで、該コラム14の案内に沿って上下動するサドル13と、主軸ユニット15を内蔵し該サドル13に水平方向に摺動可能に嵌合されたラム1とを備えている。
前記サドル13は、左右4箇所を、ラム1の移動端部側を静圧軸受2a、2bで支持され、根本側を静圧軸受3a、3bで支持されている。
このとき、コントローラ10は、前記可変絞り6の絞り量を調整し静圧軸受2の圧力を上昇させて、図1(A)に矢印Fのように静圧軸受2aによってサドル13を持ち上げる。
これにより、図1(B)のZ矢印ように、サドル13が傾斜してラム1の主軸ユニット15側を持ち上げる。尚、図1(B)において1uは水平線である。
これにより、ラム1の主軸ユニット15方向への真直度が保持される
図6において、ラム1の繰り出し量Xを検出して(ステップS1)、この検出値を用いて次の補正を行う。
ラム1先端の撓み量δを、次式により推定する(ステップS2)。
δ=(WaX3/3EI)+(wX4/8EI) (1)
ここで、Wa:アタッチメントの重量
w:ラム1の等分布荷重(自重)
E:ラム1の縦弾性係数
I:ラム1の断面2次モーメント
ラム1の撓み量δを補正するために、ラム1を上方に傾斜させる角度θは次式により推定する。(ステップS3)。
θ=tan-1(y/x) (2)
y,x は傾斜度
傾斜角θのときの静圧軸受i(制御する静圧軸受2a、以外の静圧軸受2b、3a、3b)の圧力Priを求める(ステップS5)。
Pri=(1/(1+Ki/Kci))・Psi (3)
ここで、Kci:可変絞りiの流量係数
Psi:静圧軸受iの供給圧力
Wi=Ai・Pri (4)
ここで、Ai:静圧軸受iの有効面積
静圧軸受2aの負荷荷重W2aを算出する。記載以外の符号は図1(B)を参照(ステップS7)。
M+W3bL3b+W2bL2b=W2aL2a+W3aL3a (5)
ここで、M:ラム、アタッチメント、サドルの自重によりサドルを回転させようと
する回転モーメント
静圧軸受圧力2aの圧力Pr2aを算出する(ステップS8)。
Pr2a=W2a/A2a (6)
前記圧力Pr2aを得るための可変絞り6の絞り流量係数Kc2aを求め、この絞り流量係数Kc2aになるように可変絞り6の絞り量を絞り長さS6に調節する(ステップS9、S10)。この絞り長さとは、可変絞りの絞り調整量である。
また、前記複数の静圧軸受の油圧および可変絞りの状態調整によって、従来のようなバランスウェイトは不要となり(図11において、破線部分19が不要となる)、簡単な構造で且つ装置コストが低廉な装置で、前記のような高い加工精度を得ることができる。
基本構成は第1実施例と同じであり、サドル13は、左右4箇所を、ラム1の移動端部側を静圧軸受2a、2bで支持され、根本側を静圧軸受3a、3bで支持されている。
この静圧軸受2aは、前記サドル13を前記コラム14の長手方向に支持する静圧軸受2a、2b、3a、3bのうち、前記ラム1の繰り出し方向であって前記主軸ユニット15の主軸より下方に設置した静圧軸受であり、さらに、静圧軸受3aは、静圧軸受2aとは主軸ユニット15の主軸と該主軸に直角方向の前記コラムの中心線との交点C1に対して対称位置に設置した静圧軸受であり、静圧軸受2a、3aに対して油圧を制御するようになっている。
このとき、コントローラ10は、前記可変絞り6の絞り量を調整し前記静圧軸受2aの圧力を上昇させ、また前記可変絞り7の絞り量を調整し前記静圧軸受3aの圧力を上昇させる。
これにより、ラム1の先端位置が、図2のS矢印のように、撓みが無い場合のラム1の中心軸上に移り、主軸ユニット15方向への真直度が保持される。
図7はかかる第2実施例により主軸ユニットの位置のずれを補正する制御手段のフローチャートである。
図7において、ステップS12で求めたサドル13先端の撓み量δに応じて、事前に求めたデータベースにより静圧軸受3aの可変絞り7の流量係数Kc3aを求める。
この可変絞り7の流量係数Kc3aをステップS15のPriの算式に用いるとともに、ステップS20で絞り調整量の絞り長さS7の算出に用いる。
これ以外は、前記実施例1と同様である。
また、ラム1の先端を持ち上げる静圧軸受の負荷能力が上昇し、アタッチメントの追加等によるラム1の重量増加に対応できる。
図3において、コラム14(図11参照)の案内に沿って上下動するサドル13と、主軸ユニット15を内蔵し該サドル13に水平方向に摺動可能に嵌合されたラム1とを備えている。
前記ラム1は、該ラム1の長手方向に上下各2箇所、つまり下部側を静圧軸受20a、20bで支持され、上部側を静圧軸受30a、30bで支持されている。
この静圧軸受20aは、ラム1をサドル13に支持する複数の静圧軸受20a、20b、30a、30bのうち、前記ラム1の繰り出し方向であって主軸ユニット15の主軸より下方に設置した静圧軸受であり、この静圧軸受20aの油圧を制御するようになっている。
このとき、コントローラ10は、前記可変絞り61の絞り量を調整し、これにより静圧軸受20aの圧力が上昇する。従って、図3のF矢印ように、静圧軸受20aによりラム1の主軸ユニット15側を持ち上げる。
これにより、ラム1の先端位置が、図2のS矢印のように、撓みが無い場合のラム1中心軸上に移り、主軸ユニット15方向への真直度が保持される。
尚、図8において、
静圧軸受20aの負荷荷重W20aを算出する(ステップS37)。
W20a=W+W30b+W30a-W20b (5)
ここで、W:ラム1及びアタッチメントの重量
上記記載以外の符号は図3を参照
これ以外は、前記実施例1と同様である。
図4において、コラム14(図11参照)の案内に沿って上下動するサドル13と、主軸ユニット15を内蔵し該サドル13に水平方向に摺動可能に嵌合されたラム1とを備えている。
前記ラム1は、該ラム1の長手方向に上下各2箇所、つまり下部側を静圧軸受20a、20bで支持され、上部側を静圧軸受30a、30bで支持されている。
10はコントローラで、可変絞り32の絞り量、及び可変絞り33の絞り量を制御する。
この静圧軸受20aは、ラム1をサドル13に支持する複数の静圧軸受20a、20b、30a、30bのうち、前記ラム1の繰り出し方向であって主軸ユニット15の主軸より下方に設置した静圧軸受であり、さらに、静圧軸受30aは、静圧軸受20aとは主軸ユニット15の主軸と該主軸に直角方向の前記サドル13の中心線との交点C2に対して対称位置に設置した静圧軸受であり、静圧軸受20a、30aに対して油圧を制御するようになっている。
このとき、コントローラ10は、前記可変絞り32の絞り量を調整し前記静圧軸受20aの圧力を上昇させ、また前記可変絞り33の絞り量を調整し前記静圧軸受30aの圧力を上昇させる。
これにより、ラム1の先端位置が、図3のS矢印のように、撓みが無い場合のラム1中心軸上に移り、主軸ユニット15方向への真直度が保持される。
図9はかかる第4実施例により主軸ユニットの位置のずれを補正する制御手段のフローチャートである。
図9において、ステップS52で求めたラム1先端の撓み量δに応じた静圧軸受30aの可変絞り33の流量係数Kc30aを求める。
この可変絞り33の流量係数Kc30aをステップS55のPriの算式に用いるとともに、ステップS60の絞り調整量S33の算出に用いる。
これ以外は、前記実施例3と同様である。
また、ラム1の先端を持ち上げる静圧軸受の負荷能力が上昇し、アタッチメントの追加等によるラム1の重量増加に対応できる。
図5において、コラム14(図11参照)の案内に沿って上下動するサドル13と、主軸ユニット15を内蔵し該サドル13に水平方向に摺動可能に嵌合されたラム1とを備えている。
前記ラム1は、該ラム1の長手方向に上下各2箇所、つまり下部側を静圧軸受20a、20bで支持され、上部側を静圧軸受30a、30bで支持されている。
前記各静圧軸受20a、20b及び静圧軸受30a、30bへの油路には、各油路の油圧を計測する油圧センサ37、38、39、40が設けられ、これら油圧センサ37、38、39、40の油圧検出値はコントローラ10に入力される。
このとき、コントローラ10は、前記可変絞り32の絞り量を調整し前記静圧軸受20aの圧力を上昇させ、また前記可変絞り33の絞り量を調整し前記静圧軸受30aの圧力を上昇させる。
また、可変絞り34の絞り量を調整して静圧軸受20bの圧力を調整するとともに、可変絞り35の絞り量を調整して静圧軸受30bの圧力を調整する。
即ち、上記の制御により、図5のF1矢印に示すように、静圧軸受20aによりラム1の主軸ユニット15側を持ち上げ、同時に静圧軸受30aにより、ラム1の繰り出し側とは反対側をF2矢印のように押し下げる。
これにより、ラム1の先端位置が、図5のS矢印のように、撓みが無い場合のラム1中心軸上に移り、主軸ユニット15方向への真直度が保持される。
図10は、かかる第5実施例により主軸ユニット位置のずれを補正する制御手段のフローチャートである。
図10において、ステップS72で求めたラム1先端の撓み量δに応じて事前に求めたデータベースより、静圧軸受30aの可変絞り33の流量係数Kc30aを求める。
この可変絞り33の流量係数Kc30aをステップS75のPriの算式に用いるとともに、ステップS80の絞り長さS33の算出に用いる。
そして、この油圧Priが目標油圧になっているか判定し(ステップS82)、なっていなければ各可変絞りを調整する。
これ以外は、前記実施例4と同様である。
Claims (8)
- コラムの案内に沿って上下動するサドルと、主軸ユニットを内蔵し該サドルに水平方向に摺動可能に嵌合されたラムとを備えた工作機械において、
前記サドルを前記コラムの長手方向に複数の静圧軸受を用いて前記コラムに支持するとともに、該静圧軸受の油圧を変化させて、前記ラムの主軸方向の真直度を保持するように、前記静圧軸受の油圧をラムの垂直方向変位に従い制御することで、かかる油圧の制御に従うサドルの傾斜により前記主軸ユニット位置のずれを補正する制御手段を備えたことを特徴とするラムの撓み補正装置。 - 前記制御手段は、前記サドルを前記コラムの長手方向に支持する複数の静圧軸受のうち、前記ラムの繰り出し方向であって前記主軸ユニットの主軸より下方に設置した静圧軸受の油圧を制御して、前記ラムの主軸方向の真直度を保持することを特徴とする請求項1記載のラムの撓み補正装置。
- 前記制御手段は、前記ラムの繰り出し方向であって前記主軸ユニットの主軸より下方に設置した前記静圧軸受に加えて、該静圧軸受とは前記主軸ユニットの主軸と該主軸に直角方向の前記コラムの中心線との交点に対して対称位置に設置した静圧軸受に対しても油圧を制御して、前記ラムの主軸方向の真直度を保持することを特徴とする請求項2記載のラムの撓み補正装置。
- コラムの案内に沿って上下動するサドルと、主軸ユニットを内蔵し該サドルに水平方向に摺動可能に嵌合されたラムとを備えた工作機械において、
前記ラムを該ラムの長手方向に複数の静圧軸受を用いて前記サドルに支持するとともに、該静圧軸受の油圧を変化させて、前記ラムの主軸方向への真直度を保持するように、前記静圧軸受の油圧をラムの垂直方向変位に従い制御することで、かかる油圧の制御に従うラムの傾斜により前記主軸ユニット位置のずれを補正する制御手段を備えたことを特徴とするラムの撓み補正装置。 - 前記制御手段は、前記ラムを前記サドルに支持する複数の静圧軸受のうち、前記ラムの繰り出し方向であって前記主軸ユニットの主軸より下方に設置した静圧軸受の油圧を制御して、前記ラムの主軸方向の真直度を保持することを特徴とする請求項4記載のラムの撓み補正装置。
- 前記制御手段は、前記ラムの繰り出し方向であって前記主軸ユニットの主軸より下方に設置した前記静圧軸受に加えて、該静圧軸受とは前記主軸ユニットの主軸と該主軸に直角方向の前記サドルの中心線との交点に対して対称位置に設置した静圧軸受に対しても油圧を制御して、前記ラムの主軸方向の真直度を保持することを特徴とする請求項5記載のラムの撓み補正装置。
- 前記静圧軸受への油量を絞る絞り装置、前記各静圧軸受への油圧を計測する油圧センサを備え、前記制御手段は、該油圧センサからの油圧検出値に基づいて前記静圧軸受の目標油圧になるように前記絞り装置の絞り量を制御するように構成したことを特徴とする請求項1~6記載のラムの撓み補正装置。
- 前記静圧軸受への油量を絞る絞り装置を備え、前記制御手段は、該絞り装置の絞り量を前記静圧軸受の目標油圧になるために算出した絞り流量となるように絞り量を制御するように構成したことを特徴とする請求項1~6記載のラムの撓み補正装置。
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---|---|---|---|---|
CN102896330A (zh) * | 2011-07-26 | 2013-01-30 | 发得科技工业股份有限公司 | 镗铣床主轴辅助支撑滑轨装置 |
CN102896330B (zh) * | 2011-07-26 | 2014-12-10 | 发得科技工业股份有限公司 | 镗铣床主轴辅助支撑滑轨装置 |
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KR101348861B1 (ko) | 2014-01-07 |
CN102470498A (zh) | 2012-05-23 |
IN2012DN00295A (ja) | 2015-05-08 |
KR20120016665A (ko) | 2012-02-24 |
CN102470498B (zh) | 2014-04-30 |
RU2012103175A (ru) | 2013-08-10 |
US20130202373A1 (en) | 2013-08-08 |
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