US3690072A - R adjusting the angular relation between a workpiece to be ground and a tool - Google Patents

R adjusting the angular relation between a workpiece to be ground and a tool Download PDF

Info

Publication number
US3690072A
US3690072A US98807*7A US3690072DA US3690072A US 3690072 A US3690072 A US 3690072A US 3690072D A US3690072D A US 3690072DA US 3690072 A US3690072 A US 3690072A
Authority
US
United States
Prior art keywords
grinding
workpiece
spindle
support
signal
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
Application number
US98807*7A
Other languages
English (en)
Inventor
Ralph E Price
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Landis Tool Co
Original Assignee
Landis Tool Co
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Landis Tool Co filed Critical Landis Tool Co
Application granted granted Critical
Publication of US3690072A publication Critical patent/US3690072A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

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
    • B23Q15/00—Automatic control or regulation of feed movement, cutting velocity or position of tool or work
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B24—GRINDING; POLISHING
    • B24B—MACHINES, DEVICES, OR PROCESSES FOR GRINDING OR POLISHING; DRESSING OR CONDITIONING OF ABRADING SURFACES; FEEDING OF GRINDING, POLISHING, OR LAPPING AGENTS
    • B24B49/00—Measuring or gauging equipment for controlling the feed movement of the grinding tool or work; Arrangements of indicating or measuring equipment, e.g. for indicating the start of the grinding operation
    • B24B49/02—Measuring or gauging equipment for controlling the feed movement of the grinding tool or work; Arrangements of indicating or measuring equipment, e.g. for indicating the start of the grinding operation according to the instantaneous size and required size of the workpiece acted upon, the measuring or gauging being continuous or intermittent
    • B24B49/04—Measuring or gauging equipment for controlling the feed movement of the grinding tool or work; Arrangements of indicating or measuring equipment, e.g. for indicating the start of the grinding operation according to the instantaneous size and required size of the workpiece acted upon, the measuring or gauging being continuous or intermittent involving measurement of the workpiece at the place of grinding during grinding operation
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B24—GRINDING; POLISHING
    • B24B—MACHINES, DEVICES, OR PROCESSES FOR GRINDING OR POLISHING; DRESSING OR CONDITIONING OF ABRADING SURFACES; FEEDING OF GRINDING, POLISHING, OR LAPPING AGENTS
    • B24B5/00—Machines or devices designed for grinding surfaces of revolution on work, including those which also grind adjacent plane surfaces; Accessories therefor
    • B24B5/36—Single-purpose machines or devices
    • B24B5/42—Single-purpose machines or devices for grinding crankshafts or crankpins

Definitions

  • a differential circuit (48) directly compares the voltage output of the right hand (R.l-l.) and the left hand (Ll-i.) gage heads (43, 44) and generates a signal when the difference varies by more than a predetermined amount. Compensation is effected by deflecting the appropriate wheel spindle bearing support (41 or 41') in a forward direction, as separate force applying means (49, 49') are provided at each end of the wheel spindle (18) for that purpose.
  • This invention relates to an improved method and apparatus for preventing a taper from being formed on a workpiece, which is being ground on a multiple grinding wheel machine.
  • the invention also has application on wide wheel grinding machines. In multiple or wide wheel cylindrical grinding machines, it is very important to maintain a parallel relationship between the axis of the workpiece and the axis of the grinding wheel(s). Otherwise, the workpiece can be ground with a taper, i.e., one end of the workpiece is ground oversize in relation to the other.
  • gaging means were provided for measuring spaced diameters on a workpiece. Facilities were provided to stop the grinding operation if one of the diameters was ground to a low limit before the other diameter had been ground to a high limit. The taper was then corrected by adjusting a swivel table a slight amount to compensate for the measured taper.
  • An example of this method was covered in the Pheil U.S. Pat. No. 3,097,454, granted July I6, 1963. This method is used on manual machines and would not be satisfactory for automatically-operated machines.
  • a multiple or wide wheel grinding machine for grinding axially spaced portions of a workpiece.
  • the machine includes a work support for supporting the workpiece and the grinding wheel support including a spindle for supporting one or more rotatably mounted grinding wheels.
  • Means are provided to effect a relative transverse feeding movement between the wheel spindle and the workpiece support to perform a grinding operation.
  • At least two electrical size signals are generated from spaced portions on the workpiece during the grinding cycle.
  • the two signals are compared directly and a third signal is generated when the difference between the signals exceeds a predetermined value.
  • the third signal actuates means for deflecting the wheel support to move the corresponding grinding wheel toward the workpiece.
  • separate and independent means are provided at spaced portions of the grinding wheel, to displace one or the other of the spindle supports in a transverse direction.
  • the supports are in the form of cantilever arms which can be deformed in a forward direction toward the workpiece.
  • an object of the present invention to control a parallel relationship between the axis of the wheel spindle and the axis of the workpiece automatically.
  • Another object is to provide a control device which directly compares the voltage output from two gages to each other and generates a taper compensating signal in response thereto.
  • Another object is to remove all compensation from the workpiece, which enables the original setting of the headstock, tailstock, work rests, and the gage heads to be undisturbed during the complete grinding cycle.
  • Another object is to maintain a parallel relationship between the axis of the wheel spindle and the axis of the workpiece, without interfering with the support of pressure from a work rest.
  • Another object is to provide a means for compensating for any taper automatically, without losing contact between the grinding wheel and the surface of the workpiece.
  • Another object is to enable any over-compensation to be corrected by effecting movement of the opposite taper compensating mechanism, without losing contact between the grinding wheel and the surface of the workpiece.
  • Another object is to provide means to reset the position of the grinding wheel spindle to its original parallel position at completion of each grinding cycle autom atically.
  • FIG. I is a plan view of a multiple wheel grinding machine, embodying the present invention, and showing taper compensation mechanisms for advancing either end of the grinding wheel spindle, the visual readout dials from the gage system, and the schematic diagram showing the hydraulic controls, and
  • FIG. 2 is a partial R.H. end view showing the RH. taper compensation mechanism mounted on the wheel support, and the differential circuit of the gage system, and
  • FIGS. 3A and 3B are a diagram showing the circuit logic for the taper compensation mechanisms.
  • FIG. I there is illustrated the plan view of a grinding machine, generally designated by the numeral 10, having a bed 11, which supports a wheel support 12 and a work support 13.
  • the wheel support 12 carries the spindle bearings 16 and I7, which support the rotatable spindle 18.
  • spindle bearings are retained in a spaced relation by means of R.H. and Lil. clamps, l9 and 20, which are pivotably mounted, but secured to the front of the wheel support 12. through fasteners 21.
  • Grinding wheels 22, 23, 24, 2S, and 26 are carried in a spaced relation to correspond to the portions of the workpiece W to be ground, by means of spacers 27, 28, 29, 30,31 and 32, which are locked in position by wheel center rings 33 and 34.
  • the workpiece W is rotatably supported by the headstock and tailstock work centers 36 and 37 in a conventional manner.
  • the headstock 38 and the tailstock 39 are longitudinally positioned and locked to the work support 13, and the work support 13 is manually positioned to align the workpiece portions with the spaced grinding wheels 22-26.
  • the front portion of the wheel support 12 includes wheel spindle supports 41 and 41' which are longitudinally spaced to form the rear support for the spindle bearings 16 and 17 at the respective locations.
  • the wheel spindle support 41 is connected to the wheel support 12 at its lower end, but is unsupported at its upper end, the wheel support 41 is formed in a similar manner.
  • the supports 41 and 41' act as cantilever arms which can be deflected to change the angular position of the wheel spindle 18 with respect to the workpiece W.
  • the appropriate support 41 or 41' is deflected automatically during a dwell in the grinding cycle to insure a parallel relationship between the axis of the wheel spindle l8 and the axis of the workpiece W prior to reaching size.
  • An electronic grinding gage system 42 consists of two gage heads 43 and 44 having readout dials 46 and 47 which receive signals from conventional probe members or transducers 45 and 45' and also directs a signal to a differential comparator circuit 48, which compares all readings directly through a continuous plus or minus reading from a normal zero setting as indicated by a differential dial 50, described more fully hereinafter.
  • the gage system 42 is similar to the electronic gage Model l35B-79 R-l shown in a catalogue of Federal Products Corporation, 1144 Eddy Street, Buffalo, Rhode Island 02901.
  • the differential comparator circuit 48 includes two oscillators (not shown) which transmit signals through linear variable differential transformers to the transducers 45 and 45'.
  • the transducers 45 and 45' send voltage signals back to the differential comparator circuit 48, the voltages of which are a function of the position of the transducers.
  • the signals are directly compared in the differential comparator circuit 48, and if there is a differential between the voltages which exceeds a predetermined amount, one of two relays (not shown) within the differential comparator circuit 48, is energized.
  • a first of the relays has a contact CR1 and a second of the relays has a contact CR2 (see FIG. 2).
  • This circuit 48 is used to make taper corrections by advancing the respective end of the wheel spindle l8 automatically to compensate for any undesired taper between the ends of the workpiece W, when the tolerance limits are exceeded.
  • Each end of the spindle 18 is advanced by the movement of a taper compensator assembly 49 and 49', to compensate for the oversize diameter portion.
  • the taper compensation assemblies 49 and 49 are secured to each side of the wheel support 12, as shown in FIG. 1.
  • the RH. and L.l-l. taper compensating mechanisms are identical, therefore, only the R.H. assembly 49 will be described.
  • the right hand end of the wheel spindle 18 is advanced when the diameter of the right hand end of the workpiece W exceeds the tolerance over the left hand diameter.
  • the forward movement is effected by movement of a piston 51, within a hydraulic cylinder 52, which s secured to a R.l-l. housing 53, through an adaptor plate 54.
  • the RJ-l. housing 53 houses a busing 56, which supports a slidable plunger 57.
  • the plunger 57 is in threaded engagement with a pinion nut 58.
  • the outer teeth 59 of the pinion nut 58 are in mesh with the teeth of a rack member 61 which is secured to a piston rod 62 of the piston 51.
  • a threaded portion 60 of the pinion nut 58 is in threaded engagement with the internal threads of the bushing 56, to provide a fine advance movement of the plunger 57, by means of differential threads.
  • the bushing 56 includes a vertical slot 63, as shown in FIG. 2, which enables a key 64 to be secured to the plunger 57, to prevent the plunger 57 from rotating when the pinion nut 58 is rotated.
  • the sides of the slot 63 also provide means to limit the total amount of movement of the plunger 57 in either direction.
  • Movement of the piston rod 62 effects movement of the rack member 61, and the pinion nut 58 is rotated, which advances the pinion nut 58 to the left, as shown in FIG. 2.
  • the plunger 57 is retracted to the right rela tive to the pinion nut 58.
  • the nut 58 may have 8 threads per inch, and the plunger 10 threads per inch.
  • the plunger 57 is advanced against a pressure post 66, that is secured to the wheel spindle support 41. Movement of the plunger 57 deflects the wheel spindle support 41 a slight amount, and the RH. bearing 16 and the RH. end of the spindle 18 are advanced until the signals from the gage heads 43 and 44 come within the allowed tolerance as determined by the differential comparator circuit 48. The normal fine feed rate is then initiated and continues until size is reached.
  • control means which effects the operation of the taper compensating mechanisms 49 and 49' are not actuated until after the wheel support 12 has been advanced by any of the conventional means.
  • the gage heads 43 and 44 are not advanced to engage the workpiece diameters until the diameter of the workpiece W has been rough ground. This method is conventional and prevents the gage heads 43 and 44 from being damaged by the rough surface of an unground workpiece.
  • the grinding wheels 22-26 or a single wide wheel are advanced by a digital feed system which effects movement of the wheel support 12 for predetermined distances and at predetermined rates, after the workpiece W has been properly positioned in alignment with the grinding wheels 22-26, and after the headstock 38 has started the rotation of the workpiece W.
  • a feed system of this type is disclosed in co-pending application of Price et al., Ser. No. 45,829, filed on June 12, 1970, entitled “Feed Rate And Positioning Control System For A Machine Tool,” assigned to Landis Tool Co., which is expressly incorporated herein.
  • a sequence control counter disclosed in the above patent application determines the rate of infeed, the end points, and the dwell periods during the grinding operation, by controlling the rate and the number of pulses directed to the electro-hydraulic pulse motor.
  • the pulse motor advances the grinding wheels 22-26 transversely at preselected distances, until a size signal is obtained by means of the gage heads 43 and 44.
  • the grinding wheels are advanced at a rapid infeed rate, until a load control relay (not shown) is deenergized by contact between the grinding wheels 22-26 and the workpiece W. This reduces the infeed rate of the grinding wheels 22-26 to a first grinding feed rate.
  • the work rests 67 and 68 are advanced to compensate for the resultant forces from the grinding wheels 22-26, to prevent deflection of the workpiece W in a conventional manner.
  • the grinding feed rate continues until a dwell period is effected.
  • gage heads 43 and 44 are then advanced to a position as shown in FIG. 1 in the following manner.
  • a gage advance solenoid 1P SOL is energized which shifts a control valve 79 to the left, and fluid pressure is directed through a line 80 to the valve 79 and to the head end of the hydraulic motors or cylinders 81 and 82 through lines 83, 83a and 83b.
  • Flow control valves 86 and 87 are included in the lines 83a and 83b, respectively, to control the operating speed of pistons 88 and 89, by throttling the pressure and by allowing free flow of the returning fluid.
  • Fluid pressure from the lines 83, 83A, and 83B advances the pistons 88 and 89, which advance the gage heads 43 and 44, respectively, against the end portions of the workpiece W.
  • the lines 90 and 90A direct the fluid being exhausted from the rod end of the cylinders 81 and 82 through the valve 79 and to a drain 85.
  • the wheel support 12 is retracted a small amount at the end of a first dwell period, until the counter is equal to the number set on the reset switches (not shown).
  • the grinding wheels 22-26 are advanced after a second dwell period and a second feed rate is effected which continues until either of the No. 2 gage contacts on the dial 46 or 47 are tripped, to effect the third dwell period.
  • Taper compensation will be effected automatically during the third dwell period, by the energization of the RH. or L.H. taper compensation solenoids HA SOL or 11HA SOL, respectively, if the comparator circuit 48 indicates a predetermined difference between the RH. and the LR. portions of the workpiece W.
  • taper compensation switch S510 When the taper compensation switch S510 is in the ON position, taper compensation will be effected to advance the RH. end of the wheel spindle 18. This occurs when the signal from the comparator circuit 48 determines that the diameter of the RH. portion of the workpiece W as measured by the transducer 45 of the R.I-I. gage head 43, exceeds the allowable tolerance over the diameter being measured by the transducer 45 of the L.H. gage head 44.
  • the solenoid IOHA SOL is energized when a signal from an expander 91 is directed to an AND gate 92 through a line 93 and the AND gate 92 directs a signal to an AND gate 97 through a line 94.
  • a signal is directed from the AND gate 97 to an output converter 98 through a line 99.
  • the output converter 98 converts the d-c voltage signal to an a-c voltage signal and energizes the solenoid 10I-IA SOL, which is protected by conventional fuses (unnumbered).
  • the energization of the solenoid 10HA SOL shifts a control valve 100 to the right (FIG. 1).
  • Main pressure from a hydraulic source directs hydraulic fluid from a line 101 through the valve 100, and through a line 102, which connects the valve 100 to the head end of the hydraulic cylinder 52.
  • a flow control valve 103 is included in the line 102 to control the operating speed of the piston 51 within the cylinder 52 by throttling the fluid pressure and by allowing free flow of the returning fluid when the piston 51 is reset.
  • the piston 51, the piston rod 62, and the rack member 61 which are in mesh with the outer teeth 59 of the pinion nut 58, are advanced. This movement effects rotation of the nut 58 which advances to the left (FIG.
  • the line 104 directs the fluid being exhausted from the rod end of the cylinder 52 through the valve 100, and to a line 105 which is connected to a drain 106.
  • the fine feed rate is started at completion of the third dwell period.
  • the grinding wheels 22-26 are advanced at a slow rate until either of the No. 3 gage contacts, as shown on the readout dials 46 and 47 (FIG. 1) are tripped.
  • the fourth dwell period is effected and a sparkout operation is effected which continues until size is obtained.
  • the wheel support 12 is retracted in a conventional manner when size is reached and the RH. taper compensating assembly 49 is reset.
  • the reset movement is effected by the energization of the solenoid 10I-IB SOL, which occurs when the RH. compensation flip-flop 107 (FIG. 3A) is reset. This occurs when the line 108 directs a signal to the a-c converter 109, which converts the d-c voltage signal to an a-c voltage signal, and energizes the RH. compensation reset solenoid 10HB SOL.
  • compensation flip-flop 107 is reset when a signal from the expanders 76 and 77 are directed to the AND gate 78 which directs a signal to the flip-flop 107 through a line 84, following a delay after the grinding cycle is completed.
  • the flip-flop 107 is also reset should the footstock 39 be retracted, as an expander 95 will provide a signal to the AND gate 78 which is connected to the flip-flop 107 through the line 84.
  • the energization of the solenoid HB SOL shifts the control valve 100 (H0. 1) to the left, and hydraulic fluid is directed from the line 101 through the valve 100, and through the line 104, to the rod end of the cylinder 52.
  • the piston 51 and the piston rod 62 are reset and the rack member 61 rotates the pinion nut 58 to retract the plunger 57 to the reset or original position.
  • the axis of the wheel spindle 18 is returned to its normal free position which is parallel to the axis of the workpiece W.
  • the operation of the L.H. taper compensation assembly 49 as shown in FIG. 1, is effected in a similar manner, should the comparator circuit 48 determine that the diameter of the L.H. portion of the workpiece W, as measured by the transducer 45' of the L.H. gage head 43, exceeds the allowable tolerance over the diameter being measured by the transducer 45 of the RH. gage head 43.
  • the L.H. compensation advance solenoid Ill-IA SOL is energized, and the control valve 111 is shifted to-the right. Fluid pressure is directed through the lines 101 and 101A, through the valve 111 to a line 112, which is connected to the head end of the cylinder 52'.
  • a flow control valve 113 is included in the line 112 to control the operating speed of the piston 51' within the cylinder 52' by throttling the fluid pressure and by allowing free flow of the returning fluid when the piston 51' is reset.
  • the line 114 directs the fluid being exhausted from the rod end of the cylinder 52' through the valve 111, to a line 116 which is connected to the line 105 and drain 106.
  • the wheel support 12 is retracted in a conventional manner following a delay after size is reached, and the L.H. compensating reset solenoid llHB SOL is energized.
  • the control valve 111 is shifted to the left, and hydraulic fluid from the lines 101 and 101A is directed through the valve 111 and to the rod end of the cylinder 52, through the line 114.
  • the piston 51 is reset, and the plunger 57' is retracted to its reset position in preparation for grinding the next workpiece W.
  • FIG. 3B for L.H. taper compensation is similar to FIG. 3A for RH. taper compensation, and like elements have been given like numerals with a prime designation.
  • a signal is directed from the AND gate 92 to an AND gate 118 through a line 119 when a signal for RH.
  • a signal from an AND gate 92' directs a signal through a line 121 to the expander 122 and to the AND gate 118 when a signal for L.H. compensation is generated.
  • the R.H. or L.H. compensation is otherwise effected as previously stated.
  • a grinding machine for grinding axially spaced portions of a workpiece, including a work support for supporting said workpiece, a grinding wheel support including a spindle for supporting a grinding apparatus including at least one rotatably mounted grinding wheel, axially spaced spindle bearings for supporting opposite ends of said grinding wheel spindle, means for effecting a relative transverse feeding movement between said wheel spindle and said work support to perform a grinding operation, the improvement comprising:
  • said grinding wheel support includes a cantilever arm at each end for supporting said spindle;
  • said deflecting means includes two separate force applying mechanisms, one of each end of the wheel support, for moving the grinding wheel spindle toward the workpiece.
  • a hydraulic motor having a piston rod with a rack member formed in the end thereof, said motor being operable in response to said third signal
  • a pinion nut having internal threads for receiving said one end of said plunger and having external teeth in mesh with said rack member, and further having external threads adjacent the external teeth;
  • a grinding machine for grinding axially spaced portions of a workpiece, including a work support for supporting said workpiece, a spindle for supporting a grinding apparatus including at least one rotatably mounted grinding wheel, axially spaced spindle bearings for supporting opposite ends of said grinding wheel spindle, feeding means for effecting a relative transverse feeding movement between said wheel spindle and said work support to perform a grinding operation, means for controlling said feeding means, the improvement comprising:
  • a grinding wheel spindle support including a pair of cantilever mounted arms for supporting opposite ends of said spindle;
  • a grinding machine as recited in claim 4, wherein said displacing means comprises:
  • a hydraulic motor having a piston rod with a rack member formed in the end thereof, said motor being operable in response to said signal;
  • a plunger having one end associated with said grinding wheel support and being threaded on the other end;
  • a pinion nut having internal threads for receiving the threaded end of said plunger and having external teeth in mesh with said rack member, and further having external threads adjacent the external teeth;
  • said displacing means further comprises,
  • means including a hydraulic motor, for advancing one of said plungers in response to said other signal.
  • said force applying mechanisms include plungers for deflecting one of said arms upon generation of said signal.
  • a grinding machine for grinding axially spaced portions of a workpiece including a work support for supporting said workpiece, a grinding wheel support including a spindle for supporting a grinding apparatus including at least one rotatably mounted grinding wheel, feeding means for effecting a relative transverse feeding movement between said wheel spindle and said work support to perform a grinding operation, means for controlling said feeding means, the improvement comprising:
  • said grinding wheel support having axially spaced cantilevered portions extending therefrom to support said spindle

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Constituent Portions Of Griding Lathes, Driving, Sensing And Control (AREA)
  • Grinding Of Cylindrical And Plane Surfaces (AREA)
US98807*7A 1970-12-16 1970-07-01 R adjusting the angular relation between a workpiece to be ground and a tool Expired - Lifetime US3690072A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US9880770A 1970-12-16 1970-12-16

Publications (1)

Publication Number Publication Date
US3690072A true US3690072A (en) 1972-09-12

Family

ID=22270985

Family Applications (1)

Application Number Title Priority Date Filing Date
US98807*7A Expired - Lifetime US3690072A (en) 1970-12-16 1970-07-01 R adjusting the angular relation between a workpiece to be ground and a tool

Country Status (4)

Country Link
US (1) US3690072A (show.php)
JP (1) JPS5119635B1 (show.php)
DE (1) DE2159721C3 (show.php)
GB (1) GB1366498A (show.php)

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3877179A (en) * 1973-02-13 1975-04-15 Cincinnati Milacron Inc Work locating device for grinding machines
US3916576A (en) * 1973-06-11 1975-11-04 Cincinnati Milacron Heald Grinding machine
US3998010A (en) * 1975-12-24 1976-12-21 Landis Tool Company Cylindrical grinder
US4116111A (en) * 1976-04-24 1978-09-26 Gebrueder Heller Maschinenfabrik Gmbh Milling apparatus
FR2456583A1 (fr) * 1979-03-30 1980-12-12 Komatsu Mfg Co Ltd Machine a fraiser des vilebrequins
US5484327A (en) * 1993-06-21 1996-01-16 Eaton Corporation Method and apparatus for simultaneously grinding a workpiece with first and second grinding wheels
US6077146A (en) * 1997-10-01 2000-06-20 Nippei Toyama Corporation Method of correcting a taper in a grinding machine, and apparatus for the same
WO2000064632A1 (en) * 1999-04-23 2000-11-02 Unova U.K. Limited Method and apparatus for controlling a workrest
JP3373408B2 (ja) 1997-10-01 2003-02-04 株式会社日平トヤマ 研削盤のテーパ補正装置
WO2003008148A3 (en) * 2001-07-17 2003-04-10 Sarcos L C Micromachining system
EP1193028A3 (en) * 2000-09-29 2004-03-31 Toyoda Koki Kabushiki Kaisha Method for measuring work portion and machining method
US20070082585A1 (en) * 2004-12-02 2007-04-12 Mitsubishi-Hitachi Metals Machinery, Inc. On-line grinding method for work roll
US20100035517A1 (en) * 2007-05-21 2010-02-11 Hall David R O.D. Centerless Grinding Machine
US20130045665A1 (en) * 2011-08-15 2013-02-21 Roland Schmitz Simultaneous grinding machine

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3064395A (en) * 1959-04-17 1962-11-20 Landis Tool Co Device for effecting axial alignment between a tool and workpiece
US3097454A (en) * 1960-12-16 1963-07-16 pheil
US3145508A (en) * 1963-02-21 1964-08-25 Landis Tool Co Apparatus for grinding intersecting annular and cylindrical surfaces
US3271910A (en) * 1961-04-12 1966-09-13 Haisch Rudolf Method of and apparatus for correcting the size and angular relation between a workpiece to be ground and a tool

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1143833A (show.php) *

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3064395A (en) * 1959-04-17 1962-11-20 Landis Tool Co Device for effecting axial alignment between a tool and workpiece
US3097454A (en) * 1960-12-16 1963-07-16 pheil
US3271910A (en) * 1961-04-12 1966-09-13 Haisch Rudolf Method of and apparatus for correcting the size and angular relation between a workpiece to be ground and a tool
US3145508A (en) * 1963-02-21 1964-08-25 Landis Tool Co Apparatus for grinding intersecting annular and cylindrical surfaces

Cited By (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3877179A (en) * 1973-02-13 1975-04-15 Cincinnati Milacron Inc Work locating device for grinding machines
US3916576A (en) * 1973-06-11 1975-11-04 Cincinnati Milacron Heald Grinding machine
US3998010A (en) * 1975-12-24 1976-12-21 Landis Tool Company Cylindrical grinder
US4116111A (en) * 1976-04-24 1978-09-26 Gebrueder Heller Maschinenfabrik Gmbh Milling apparatus
FR2456583A1 (fr) * 1979-03-30 1980-12-12 Komatsu Mfg Co Ltd Machine a fraiser des vilebrequins
US5484327A (en) * 1993-06-21 1996-01-16 Eaton Corporation Method and apparatus for simultaneously grinding a workpiece with first and second grinding wheels
US6553880B2 (en) * 1996-09-16 2003-04-29 Sarcos, Lc Micromachining system
US6077146A (en) * 1997-10-01 2000-06-20 Nippei Toyama Corporation Method of correcting a taper in a grinding machine, and apparatus for the same
JP3373408B2 (ja) 1997-10-01 2003-02-04 株式会社日平トヤマ 研削盤のテーパ補正装置
DE19845284B4 (de) * 1997-10-01 2006-01-26 Nippei Toyama Corp. Konizitätskorrektur-Vorrichtung für eine Schleifmaschine
GB2351685A (en) * 1999-04-23 2001-01-10 Unova Uk Ltd Workrest control in a multi-wheel grinding machine
WO2000064632A1 (en) * 1999-04-23 2000-11-02 Unova U.K. Limited Method and apparatus for controlling a workrest
EP1193028A3 (en) * 2000-09-29 2004-03-31 Toyoda Koki Kabushiki Kaisha Method for measuring work portion and machining method
WO2003008148A3 (en) * 2001-07-17 2003-04-10 Sarcos L C Micromachining system
US20070082585A1 (en) * 2004-12-02 2007-04-12 Mitsubishi-Hitachi Metals Machinery, Inc. On-line grinding method for work roll
US7364492B2 (en) * 2004-12-02 2008-04-29 Mitsubishi-Hitachi Metals Machinery, Inc. On-line grinding method for work roll
CN100427232C (zh) * 2004-12-02 2008-10-22 三菱日立制铁机械株式会社 用于工作轧辊的在线研磨方法
US20100035517A1 (en) * 2007-05-21 2010-02-11 Hall David R O.D. Centerless Grinding Machine
US7677954B2 (en) 2007-05-21 2010-03-16 Hall David R O.D. centerless grinding machine
US7828627B2 (en) 2007-05-21 2010-11-09 Hall David R O.D. centerless grinding machine
US20130045665A1 (en) * 2011-08-15 2013-02-21 Roland Schmitz Simultaneous grinding machine

Also Published As

Publication number Publication date
DE2159721B2 (de) 1978-04-13
GB1366498A (en) 1974-09-11
JPS5119635B1 (show.php) 1976-06-18
DE2159721C3 (de) 1978-12-07
DE2159721A1 (de) 1972-06-22

Similar Documents

Publication Publication Date Title
US3690072A (en) R adjusting the angular relation between a workpiece to be ground and a tool
US3878651A (en) Machine tool with rest apparatus
US3118258A (en) Machine machine
US3627490A (en) Grinding machine with automatic wheel exchange device
US3157971A (en) Size control device adaptable to different diameters
US3603044A (en) Gauge mechanism for grinding machines
US3247619A (en) Machine for grinding pistons automatically
US2049611A (en) Automatic sizing mechanism
US3653854A (en) Digitally controlled grinding machines
US4443977A (en) Machine for producing parts having skew surfaces of predetermined configuration
GB1440851A (en) Apparatus for operating on a workpiece having a reference surface
USRE28082E (en) Means for adjusting the angular relation between a workpiece to be ground and a tool
US3487588A (en) Machine tool control apparatus
US3153884A (en) Apparatus for grinding flexible workpieces
US3717962A (en) Machine tool with time control device
US3663189A (en) Automatic end surface positioning apparatus for use with digitally controlled machine tools
US3192675A (en) Feed indicator for machine tools
US3097454A (en) pheil
CN203210166U (zh) 一种立式四工位旋转工作台数控珩磨机床
US3651605A (en) Grinding machines
US3590534A (en) Wheel wear compensation
US2882651A (en) Positioning abrasive discs for dressing
US2943425A (en) Feed correction mechanism
US3247620A (en) Multiple position feed mechanism
GB1251089A (show.php)