US3484064A - Plumb control for horizontal boring drilling and milling machine - Google Patents
Plumb control for horizontal boring drilling and milling machine Download PDFInfo
- Publication number
- US3484064A US3484064A US652800A US3484064DA US3484064A US 3484064 A US3484064 A US 3484064A US 652800 A US652800 A US 652800A US 3484064D A US3484064D A US 3484064DA US 3484064 A US3484064 A US 3484064A
- Authority
- US
- United States
- Prior art keywords
- column
- hydrostatic
- saddle
- bearing
- flow control
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Lifetime
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Classifications
-
- 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
- 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
-
- 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
- Y10T409/00—Gear cutting, milling, or planing
- Y10T409/30—Milling
- Y10T409/309576—Machine frame
- Y10T409/309744—Machine frame including means to compensate for deformation
Definitions
- a machine tool has a vertical tool carrying column with a base which is slidable carried on a saddle which is also slidable carried on ways on the machine tool support.
- Hydrostatic bearing shims are provided on one side of the column between the column and column base, or the column base and saddle, or the saddle and the ways and are controlled by a sensor, carried on the column, which senses minor deviations of the column from the vertical in order to cause lifting of one side of the column to return it to true vertical.
- a pair of sensor and hydrostatic lifting bearing arrangements may be used arranged perpendicular to each other to position the column in two directions.
- This invention has great and particular utility in connection with large horizontal boring, drilling, and milling machines.
- the cutting tool, spindle, and driving head are carried on a very large vertical column.
- This vertical column will generally be secured to a column base.
- the column base is slidably carried by a saddle, which is in turn slidably carried by a runway which supports the entire machine and rests on a reinforced concrete foundation.
- Each axis of motion involves one member sliding on another with possible inaccuracies at sliding joints.
- Temperature gradients in various elements of the machine may be created by sunlight, local drafts, and even by continued operation of the machine. These gradients cause unequal expansions of components and relative motion between them.
- this invention contemplates the provision of level sensing means associated with the vertical column and arranged to detect level error, and column tilting means operative in response to a level error detected by the sensing means to tilt the column into true vertical alignment.
- the tilting of the column into true vertical alignment will be accomplished hydrostatically. That is, means are provided wherein the quantity of fluid supplied to certain hydrostatic pads can be varied so as to effect a very slight tilting of the column sufiicient to bring it into true vertical alignment.
- the tilt correction is accomplished by means of a hydrostatic shim, disposed between one edge of the columnand the column base, while in a second embodiment of the invention, the tilt correction is accomplished by providing hydrostatic bearings between for example the saddle and column base, and varying the quantity of hydraulic fluid supplied to certain of those bearing pads in order to accomplish the tilt correction.
- FIGURE 1 is a perspective view showing a horizontal boring, drilling and milling machine to which this invention can advantageously be applied.
- FIGURE 2 is a partial cross-sectional view through one edge of the column flange and showing a hydrostatic shim.
- FIGURE 3 is a horizontal plan view showing a plurality of hydrostatic shim pads under one column flange.
- FIGURE 4 is a partial cross-sectional view similar to FIGURE 2 but showing a modification of the hydrostatic shim.
- FIGURE 4a is a fragmentary view on an enlarged scale of a portion of FIGURE 4.
- FIGURE 5 is a crosssectional view similar to FIG- URE 4 showing still another modification of the invention.
- FIGURE 6 is a plan view showing the arrangement of a plurality of hydrostatic bearings.
- FIGURE 7 is a partial cross-sectional view showing a single adjustable hydrostatic bearing.
- FIGURE 8 is a partial cross-sectional view similar to FIGURE 7 showing a modification of a single hydrostatic bearing.
- FIGURE 9 is a partial cross-sectional view showing a further modification of a single hydrostatic bearing.
- FIGURE 10 is a plan view showing another arrangement of hydrostatic bearings for accomplishing the adjustment of this invention.
- FIGURE 11 is a schematic diagram showing a control circuit for the hydrostatic shim.
- FIGURE 12 is a schematic diagram showing the fluid control circuit for the modified hydrostatic shim illustrated in FIGURE 5.
- FIGURE 13 is a schematic diagram illustrating the fluid control circuit for a plurality of hydrostatic bearings such as contemplated in FIGURE 6.
- FIGURE 14 is a schematic view of the fluid control circuit for the hydrostatic bearings illustrated in plan View in FIGURE 10.
- FIGURE 1 is a perspective view of a typical large horizontal boring, drilling, and milling machine.
- a cutting tool will be mounted on the end of a cylindrical spindle 12 which is carried by the driving head 14.
- the head 14 is mounted on vertical ways 16 on the large column 18, and is moved up and down these ways by the vertical screw 20.
- the column 18 is mounted on the column base 22, which may be moved in a direction parallel to the spindle axis on ways 24 which support the column base 22 on a saddle 26.
- the saddle 26 may be moved along the ways 28 in a direction perpendicular to the spindle axis on a runway 30, which supports the whole machine and rests on a reinforced concrete foundation.
- the cross travel of the column 18 on the ways 24 may vary from 24 inches to 72 inches, and the column travel along the ways 28 may vary from 6 feet to 40 feet Or more. It is in part the large size of these dimensions which led to the instant invention. That is, it is impossible to design a tool of this magnitude with suflicient rigidity to prevent small deflections permitting the column to get out of true vertical alignment. Therefore, it is necessary to provide means for continuously sensing and compensating for vertical misalignment due to any cause during operation.
- transverse column tilting will be defined as tilting in a plane parallel to the spindle axis, and longitudinal column tilting as tilting in a plane perpendicular to the spindle axis. It will also be noted that the standard observer orientation (right, left, front, rear) used in describing this machine is illustrated in FIGURE 1.
- One way to correct the vertical misalignment of the column is to provide a lifting device between one edge of the column 18 and the column base 22.
- this adjustment is accomplished by a hydrostatic shim, as illustrated in cross-section in FIGURE 2.
- the column 18 includes an outwardly extending column flange 18a which overlies a portion 22a of the column base.
- a shim plate 32 will be suitably secured to the column base 22a in a position underlying the flange 18a.
- a suitable block 34 Secured to the upper surface of the shim plate 32 will be a suitable block 34 which is provided on its upper surface with a plurality of recesses 36.
- FIGURE 13 shows in plan view the arrangement of a plurality of recesses 36 in the block 34. It will be noted that each recess is provided with the passages 38 and 40 which communicate with a supply of high pressure oil to be described hereinafter.
- a drain groove 42 Surrounding all of the recesses 36 will be a drain groove 42 which communicates through conventional passages with a reservoir in the oil supply system. 2
- dirt seal 44 surrounding the drain grooves 42 is the dirt seal 44.
- These seals can be of any suitable material, and simply serve to keep dirt and the like out of the hydrostatic shim system.
- FIGURE 11 The control for this hydrostatic shim is schematically shown in FIGURE 11.
- 46 is an electronic level sensor of conventional design which is associated with the column 18 as shown in FIGURE 1 so as to produce a signal indicating the presence of level error.
- This signal may be amplified as at 48 and sent to an electro-hydraulic controller 50 which actuates a variable flow control valve 52.
- Hydraulic oil for the hydrostatic system is contained in a reservoir 54.
- the pump 56 draws oil from the reservoir 54, pumps it through the cooler 58 and filter 60 to the flow control valve 52 previously menti Jll t-i.
- the relief valve 62 is disposed a short distance up stream or the flow control valve 52, and serves to limit the pressure in the system.
- the hydraulic oil passing the flow control valve 52 goes directly to the passages 40 and 38, and into the recesses 36 previously described.
- the drain grooves 42 will be connected to the reservoir 54 by suitable passages.
- any tilt in the column which increases the distance between the column flange and the column base also increases the leakage area between the recesses and the drain groove, and thereby lower the pressure and lifting forces across the flange.
- the column tilt decreases the distance between the column flange and the column base, the leakage area decreases with a consequent increase in pressure and lifting force.
- the block 64 is provided with a recess 66 having a shoulder 66a. This shoulder is provided with the annular wedge groove 68.
- the seal ring 70 includes a wedge 72 designed to mate with the wedge groove 68, and carries on its opposite surface the sealing member 74.
- the sealing ring 70 is generally biased toward the under surface of the column flange by means of the calibrated springs 76.
- the rigidity of the overall machining system must be extremely high and a more positive anchoring force is required on the flange of the column than the weight of the column alone.
- an opposed pair of hydrostatic shims such as illustrated in FIGURE 5 is used.
- this arrangement provides hydrostatic pressure pads both above and below the column flange so that large forces are exerted in both directions whenever the oil pressure is appleid.
- the areas of the two pads are proportioned so that the column flange floats between the two pads with approximately equal clearance on each side.
- the oil flow is simultaneously adjusted to both the upper and lower pads so that the neutral position of the column flange is raised or lowered the desired amount.
- the hydrostatic shim block 80 is arranged to have a portion under the flange 18b, as Well as a second portion over the flange 18b. It
- the shim block 80 carries a number of recesses 82 which will be under the flange 18b, and a plurality of somewhat smaller recesses 84 which will be on top of the flange 18b. These recesses are supplied with oil through the passages 86 and 38 respectively. Leakage from the recesses 82 and 34 will be collected in the drain grooves 90, 92 and 94.
- the control system for this arrangement is illustrated schematically in FIGURE 12, and again includes the electronic level sensor 46 and amplifier 48 which detect level error and via the electro-hydraulic controller 59 control the flow of hydraulic oil to the system.
- the electro-hydraulic controller 50 controls both the variable fiow control valve 52 as well as the reverse-acting variable flow control valve 52a. It will be observed that the other components of the system are substantially the same as that described in connection with FIGURE 11.
- FIGURE 6 shows in plan view an arrangement of hydrostatic bearings between the column base 22 and the saddle 26. Bearings A, B, and C on each of the three ways would be conventional hydrostatic bearings supplied with high pressure oil through a constant flow controller. Bearings D and E for each way would be supplied with oil through variable flow control valves which are actuated by a level error signal as described earlier. The elevation of the column base may be changed by changing the flow to these hearings.
- FIGURE 6 shows that there is some space between bearing E and the right end of the ways to allow for column cross travel. A normal non-metallic bearing is used in this area.
- bearing E on way III is shown in cross-section in FIGURE 7. It will be apparent that the operation of this hearing is substantially identical to that of the single hydrostatic shim shown in FIGURE 2 and described earlier. Accordingly, similar reference numerals have been used.
- FIGURE 9 illustrates in cross-section the details of an opposed hydrostatic bearing.
- This opposed bearing is substantially the same as the opposed hydrostatic shim shown in FIGURE 5 and described earlier. And, again, similar reference numerals have been used.
- the control system for the hydrostatic bearing system of FIGURE 6 is schematically shown in FIGURE 13.
- the level sensor 46, the amplifier 48, and the electrohydraulic controller 5b are the same as described previously.
- the oil supply system consisting of the reservoir 54, pump 56, cooler 58, filters 60 and relief valves 62 is the same as described earlier.
- Flow control valves 96 are self contained devices which maintain a constant fiow rate under all conditions.
- Variable fiow control valves 52 supplying bearings D and E are actuated by the level sensor to increase or decrease the quantity of fiow to these hearings, and hence, to raise or lower the column base as desired.
- FIGURE 10 shows in plan view the arrangement of hydrostatic bearings as used between the saddle 26 and the runway 3%.
- the bearings on ways 1 and 2 are conventional hydrostatic bearings, supplied with a constant flow of oil to each bearing.
- the hearings on ways 3 and 4 are supplied with a variable flow of oil which is changed to raise or lower the saddle as well as the column base and column, as required to maintain the true vertical alignment of the column.
- FIGURE 14 The control system for this arrangement is schematically shown in FIGURE 14. It is substantially the same as that shown in FIGURE 13, and similar reference numerals have been used to designate the components.
- the bearings between the column base and the saddle illustrated in FIGURE 6 may be controlled to correct tilt in a longitudinal direction rather than in a transverse direction.
- all of the bearings on way III could be controlled to raise or lower the rear edge or the column and thus provide longitudinal tilting correction.
- all of the bearings N could be controlled to provide longitudinal tilting correction.
- a machine tool having a vertical column, a column base carrying said column, a saddle having a plurality of transverse ways slidably carrying said column base, and a runway having a plurality of longitudinal ways slidably carrying said saddle; the improvement comprising means to maintain true vertical alignment of said column during movement along said ways, said means including,
- variable flow control means to actuate said hydrostatic bearing means in response to level error detected by said level sensing means whereby to tilt said column into true vertical alignment to eliminate said level error.
- said lifting means comprises a hydrostatic shim including (a) a shim block disposed between said edge of said column and said column base, said shim block having (i) a plurality of recesses therein, and (ii) drain means surrounding said recesses.
- said one edge of said column includes a flange
- said lifting means includes opposed hydrostatic pads bearing on the top and bottom of said flange
- said means to actuate said lifting means includes a variable flow control valve controlling the flow of fluid to one of said hydrostatic pads and a reverse acting variable flow control valve controlling the flow of fluid to the other of said hydrostatic pads.
- the arrangement claimed in claim 1 including two level sensing means arranged to detect level error in perpendicular planes, second lifting means disposed between an edge of said column perpendicular to said first mentioned edge and said column base, and means to raise and lower said second lifting means in response to level error detected by one of said level sensing means, said first mentioned means to raise and lower said lifting means being operative in response to level error detected by the other level sensing means, whereby to tilt said column into true vertical alignment,
- tilt correcting means comprising:
- sealing ring having an annular Wedge adapted to fit within said V groove, and means normally biasing said ring away from said V groove;
- said supporting surface includes a portion overlying an edge of said supported surface, said portion of said supporting surface having at least one recess, means for supplying fluid from said supply to said last mentioned recess, said means including flow control means acting oppositely to said first mentioned flow control means, said last mentioned flow control means being operative in response to said level sensing means, and drain means for returning said fluid from said second recess to said supply.
- the tilt correcting means claimed in claim 7 including at least one additional recess in said one of said surfaces, independent means for supplying said fluid to said additional recess, said means including pump means and flow control means, and a second level sensing means operative in a plane perpendicular to said first mentioned level sensing means and operative to actuate said control means, and drain means for returning fluid from said second recess to said supply.
- a machine tool having a vertical column, a column base carrying said column, a saddle having a plurality of transverse ways slidably carrying said column base, and a runway having a plurality of longitudinal ways slidable carrying said saddle; the improvement comprising means to maintain true vertical alignment of said column during movement along said ways, said means including,
- said hydrostatic bearing having the variable flow control means includes an annular V groove near the periphery of the bearing recess, and including a sealing ring having an annular wedge adapted to fit within said V groove, and means normally biasing said ring away from said V groove.
- a machine tool having a vertical column, a column base carrying said column, a saddle having a plurality of transverse ways slidably carrying said column base, and a runway having a plurality of longitudinal ways slidably carrying said saddle: the improvement comprising means to maintain true vertical alignment of said column during movement along said ways, said means including,
- flow control means for each said hydrostatic hearing pad, at least one of said flow control means being variable, the remainder of said flow control means being adapted to provide a constant flow to the respective bearings,
- said hydrostatic bearing having the variable flow control means includes an annular V groove near the periphery of the bearing recess, and including a sealing ring having an annular wedge adapted to fit within said V groove, and means normally biasing said ring away from said V groove.
- tilt correcting means comprising:
- variable flow control valve means operative in response to level error detected by said level sensing means to control the flow of fluid to some of said hydrostatic bearing pads;
- tilt correcting means comprising:
Description
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US65280067A | 1967-07-12 | 1967-07-12 |
Publications (1)
Publication Number | Publication Date |
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US3484064A true US3484064A (en) | 1969-12-16 |
Family
ID=24618214
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US652800A Expired - Lifetime US3484064A (en) | 1967-07-12 | 1967-07-12 | Plumb control for horizontal boring drilling and milling machine |
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US (1) | US3484064A (en) |
Cited By (22)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3583774A (en) * | 1968-05-31 | 1971-06-08 | Philips Corp | Hydrostatically journalled slide and slide guide |
US3597021A (en) * | 1968-03-30 | 1971-08-03 | Ferranti Ltd | Slide bearing systems for variable loads |
US3635532A (en) * | 1969-02-08 | 1972-01-18 | Riv Officine Di Villar Perosa | Hydrostatically supported machine tool slide |
US3711167A (en) * | 1970-07-10 | 1973-01-16 | Asquith Ltd William | Hydrostatic bearings |
US3744858A (en) * | 1971-06-15 | 1973-07-10 | Apex Bearings Co | Gas bearings |
US3754799A (en) * | 1971-11-18 | 1973-08-28 | Lidkoepings Mekaniska Verkstad | Movable machine element supported with the aid of a gas or fluid bearing |
US3818736A (en) * | 1972-10-10 | 1974-06-25 | Caterpillar Tractor Co | Tooth forming machine |
US3890017A (en) * | 1972-10-10 | 1975-06-17 | Caterpillar Tractor Co | Machine slide assembly |
US3903993A (en) * | 1973-03-26 | 1975-09-09 | Minster Machine Co | Hydrostatic bearing arrangement for press slide |
US4286359A (en) * | 1975-09-27 | 1981-09-01 | Daimler-Benz Aktiengesellschaft | Push button, especially for locks of safety belts |
US4553792A (en) * | 1982-10-01 | 1985-11-19 | Dixon International Limited | Structural slide bearing |
US4632615A (en) * | 1984-02-09 | 1986-12-30 | Teijin Seiki Company Limited | Machine tools |
US4643590A (en) * | 1985-03-15 | 1987-02-17 | Federal Products Corporation | Guide system |
US4648723A (en) * | 1984-07-23 | 1987-03-10 | Omron Tateisi Electronics Co. | Static pressure air surface stage |
US5310146A (en) * | 1993-10-01 | 1994-05-10 | Maguire Edward J | Dual axis leveling system |
US5330270A (en) * | 1992-02-24 | 1994-07-19 | Nippon Thompson Co., Ltd. | Statically pressure balanced slide unit |
US5829932A (en) * | 1995-05-05 | 1998-11-03 | Giddings & Lewis, Inc. | Machine alignment compensation actuator system |
US6434922B2 (en) * | 1999-12-22 | 2002-08-20 | Angelo Dalerba | Track sliding facilitating method and device for a wire stranding machine |
US6695159B2 (en) * | 2002-04-22 | 2004-02-24 | Mi-Jack Products, Inc. | Shock absorbing bumper for gantry cranes |
EP1413388A1 (en) * | 2002-10-25 | 2004-04-28 | Mori Seiki Co., Ltd. | Machine tool with hydrostatic slideways with variable pressure |
JP2010082795A (en) * | 2008-10-03 | 2010-04-15 | Toshiba Mach Co Ltd | Precision feeder of machine tool |
CN102029522A (en) * | 2010-12-16 | 2011-04-27 | 北京科技大学 | Four-axis four-linkage inverted turning and milling combined machining device |
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US2648999A (en) * | 1949-01-13 | 1953-08-18 | New Britain Machine Co | Horizontal boring, drilling, and milling machine |
US2869933A (en) * | 1955-05-02 | 1959-01-20 | Gould & Eberhardt Inc | Weight-compensating means for precision-shifted members |
US3008381A (en) * | 1958-01-02 | 1961-11-14 | Method and means of machine support | |
US3097568A (en) * | 1961-10-09 | 1963-07-16 | Ingersoll Milling Machine Co | Machine tool |
US3260162A (en) * | 1963-03-16 | 1966-07-12 | Asquith Ltd William | Slide bearings for machine tools |
US3269685A (en) * | 1965-05-28 | 1966-08-30 | Frank Hamachek Machine Company | Leveling control for electrically operating hydraulic leveling means |
US3310263A (en) * | 1965-03-04 | 1967-03-21 | Wright Barry Corp | Gravity-sensitive levelling |
US3355990A (en) * | 1964-08-26 | 1967-12-05 | Henschef Werke A G | Hydrostatic positioning of worktables of machine tools |
US3395947A (en) * | 1964-06-03 | 1968-08-06 | Charles Churchill And Company | Slideway system |
US3397915A (en) * | 1965-10-06 | 1968-08-20 | Gullick Ltd | Longwall mining machine having automatic means to maintain angular setting |
-
1967
- 1967-07-12 US US652800A patent/US3484064A/en not_active Expired - Lifetime
Patent Citations (10)
Publication number | Priority date | Publication date | Assignee | Title |
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US2648999A (en) * | 1949-01-13 | 1953-08-18 | New Britain Machine Co | Horizontal boring, drilling, and milling machine |
US2869933A (en) * | 1955-05-02 | 1959-01-20 | Gould & Eberhardt Inc | Weight-compensating means for precision-shifted members |
US3008381A (en) * | 1958-01-02 | 1961-11-14 | Method and means of machine support | |
US3097568A (en) * | 1961-10-09 | 1963-07-16 | Ingersoll Milling Machine Co | Machine tool |
US3260162A (en) * | 1963-03-16 | 1966-07-12 | Asquith Ltd William | Slide bearings for machine tools |
US3395947A (en) * | 1964-06-03 | 1968-08-06 | Charles Churchill And Company | Slideway system |
US3355990A (en) * | 1964-08-26 | 1967-12-05 | Henschef Werke A G | Hydrostatic positioning of worktables of machine tools |
US3310263A (en) * | 1965-03-04 | 1967-03-21 | Wright Barry Corp | Gravity-sensitive levelling |
US3269685A (en) * | 1965-05-28 | 1966-08-30 | Frank Hamachek Machine Company | Leveling control for electrically operating hydraulic leveling means |
US3397915A (en) * | 1965-10-06 | 1968-08-20 | Gullick Ltd | Longwall mining machine having automatic means to maintain angular setting |
Cited By (25)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3597021A (en) * | 1968-03-30 | 1971-08-03 | Ferranti Ltd | Slide bearing systems for variable loads |
US3583774A (en) * | 1968-05-31 | 1971-06-08 | Philips Corp | Hydrostatically journalled slide and slide guide |
US3635532A (en) * | 1969-02-08 | 1972-01-18 | Riv Officine Di Villar Perosa | Hydrostatically supported machine tool slide |
US3711167A (en) * | 1970-07-10 | 1973-01-16 | Asquith Ltd William | Hydrostatic bearings |
US3744858A (en) * | 1971-06-15 | 1973-07-10 | Apex Bearings Co | Gas bearings |
US3754799A (en) * | 1971-11-18 | 1973-08-28 | Lidkoepings Mekaniska Verkstad | Movable machine element supported with the aid of a gas or fluid bearing |
US3818736A (en) * | 1972-10-10 | 1974-06-25 | Caterpillar Tractor Co | Tooth forming machine |
JPS4973355A (en) * | 1972-10-10 | 1974-07-16 | ||
US3890017A (en) * | 1972-10-10 | 1975-06-17 | Caterpillar Tractor Co | Machine slide assembly |
JPS579893B2 (en) * | 1972-10-10 | 1982-02-24 | ||
US3903993A (en) * | 1973-03-26 | 1975-09-09 | Minster Machine Co | Hydrostatic bearing arrangement for press slide |
US4286359A (en) * | 1975-09-27 | 1981-09-01 | Daimler-Benz Aktiengesellschaft | Push button, especially for locks of safety belts |
US4553792A (en) * | 1982-10-01 | 1985-11-19 | Dixon International Limited | Structural slide bearing |
US4632615A (en) * | 1984-02-09 | 1986-12-30 | Teijin Seiki Company Limited | Machine tools |
US4648723A (en) * | 1984-07-23 | 1987-03-10 | Omron Tateisi Electronics Co. | Static pressure air surface stage |
US4643590A (en) * | 1985-03-15 | 1987-02-17 | Federal Products Corporation | Guide system |
US5330270A (en) * | 1992-02-24 | 1994-07-19 | Nippon Thompson Co., Ltd. | Statically pressure balanced slide unit |
US5310146A (en) * | 1993-10-01 | 1994-05-10 | Maguire Edward J | Dual axis leveling system |
US5829932A (en) * | 1995-05-05 | 1998-11-03 | Giddings & Lewis, Inc. | Machine alignment compensation actuator system |
US6434922B2 (en) * | 1999-12-22 | 2002-08-20 | Angelo Dalerba | Track sliding facilitating method and device for a wire stranding machine |
US6695159B2 (en) * | 2002-04-22 | 2004-02-24 | Mi-Jack Products, Inc. | Shock absorbing bumper for gantry cranes |
EP1413388A1 (en) * | 2002-10-25 | 2004-04-28 | Mori Seiki Co., Ltd. | Machine tool with hydrostatic slideways with variable pressure |
JP2010082795A (en) * | 2008-10-03 | 2010-04-15 | Toshiba Mach Co Ltd | Precision feeder of machine tool |
CN102029522A (en) * | 2010-12-16 | 2011-04-27 | 北京科技大学 | Four-axis four-linkage inverted turning and milling combined machining device |
CN102029522B (en) * | 2010-12-16 | 2012-07-18 | 北京科技大学 | Four-axis four-linkage inverted turning and milling combined machining device |
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