US3717961A - Multi-wheel grinding machine - Google Patents

Multi-wheel grinding machine Download PDF

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Publication number
US3717961A
US3717961A US00123215A US3717961DA US3717961A US 3717961 A US3717961 A US 3717961A US 00123215 A US00123215 A US 00123215A US 3717961D A US3717961D A US 3717961DA US 3717961 A US3717961 A US 3717961A
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Prior art keywords
wheel
slide
dressing
grinding wheels
grinding
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US00123215A
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English (en)
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I Suzuki
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Toyoda Koki KK
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Toyoda Koki KK
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    • 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
    • B24B49/18—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 taking regard of the presence of dressing tools

Definitions

  • a multi-wheel grinding machine having a [21] AppL NO: 123,215 plurality of grinding wheels for simultaneously perfon'ning a grinding operation on a plurality of portions of a workpiece.
  • a separate dressing head correspond- [30] Apphcauon Pnomy Data ing to each grinding wheel is provided for respectively March 11,1970 Japan ..45/20716 dressing the Several grinding Wheels in a Controlled manner.
  • the present invention relates to a grinding machine, and more particularly concerns an improved multiwheel grinding machine which enables a plurality of portions on a workpiece to be simultaneously ground by multiple grinding wheels.
  • Multi-wheel grinding machines are known in the art, but when a grinding operation is carried out on a workpiece by such machines heretofore available, the several portions of the workpiece being ground by the several grinding wheels are provided with finished diameters which due to various causes are not the same.
  • every diameter is measured after the grinding operation on the plural portions of the workpiece is completed.
  • the measuring apparatus produces a signal.
  • the rejected workpiece should be abandoned according to the past practice, which of course is economically unfavorable although necessary for maintaining recognized quality standards.
  • a preferable practice would be to measure the diameters of the portions which are being ground before the grinding operation has been completed and to keep the difference being produced therebetween within the required value during the completion of the grinding operation.
  • an object of the present invention to provide an improved multi-wheel grinding machine which is operative to substantially eliminate any difference in diameters of the several portions of a workpiece being ground thereby during the grinding operation.
  • Another object of the present invention is to provide an improved grinding machine having a plurality of grinding wheels for simultaneously grinding a corresponding plurality of portions of a workpiece and being automatically operable during a grinding operation to provide each of the finished ground portions of the workpiece with the same diameter within a predetermined range of accuracy.
  • a still further object of this invention is to provide a multi-wheel grinding machine wherein a wheel slide carrying the grinding wheels is advanced to compensate for wear of the grinding wheels after the grinding operation is completed so that safety in operation and high machining accuracy are obtained.
  • a grinding machine having a plurality of grinding wheels for simultaneously grinding a plurality of portions on a workpiece, a dressing head for each grinding wheel, and an automatic sizing apparatus for measuring the diameters of the workpiece portions being ground by the grinding wheels and responsive to detecting a dif ference in the diameters of the workpiece portions beyond a predetermined limit for stopping the feeding movement of a wheel slide carrying the grinding wheels and advancing the dressing heads in a controlled manner for dressing the grinding wheels unevenly so that the difference in the diameters is substantially BRIEF DESCRIPTION OF THE DRAWINGS
  • Various other objects, features and attendant advantages of the present invention will be more fully appreciated as the same becomes better understood from the following detailed description of a preferred em bodiment, when considered in connection with the ac companying drawings, in which like reference numerals designate like or corresponding parts throughout the several figures, and wherein:
  • FIG. 1 is a plan view of a multi-wheel grinding machine formed according to the invention
  • FIG. 2 is a cross-sectional view taken along the line Il-Il in FIG. 1;
  • FIG. 3 is a schematic illustration of a hydraulic circuit for actuating the multi-wheel grinding machine of FIGS. 1 and 2 to effect the various movements thereof;
  • FIGS. 4 and 5 taken together, constitute a schematic illustration of an electric control circuit for controlling the hydraulic circuit shown in FIG. 3 for causing a grinding operation to be performed on a workpiece with the multi-wheel grinding machine of the invention.
  • a tailstock 2 and a headstock 3 for supporting a workpiece 5 therebetween are carried by a table 24 which is pivotally mounted on a base 1 about a pivot pin 25 secured thereto.
  • a motor 4 for rotating the workpiece 5 is mounted on the headstock 3.
  • Automatic sizing devices 6a and 6b also carried by the table 24 are arranged to engage the workpiece 5 at spaced portions 5a and 5b thereon which are to be ground by a pair of grinding wheels 9a and 9b.
  • a wheel slide 7 is slidably mounted on parallel slide ways 47 formed on the base 1 and carries a rotatable wheel spindle 8 which is rotated about a horizontal axis perpendicularly oriented relative to the path of movement of the wheel slide by a suitable motor, not shown, through a V-grooved pulley 10 and a plurality of V- belts coupled thereto.
  • a plurality of grinding wheels being shown in this embodiment as two in number, namely, the grinding wheels 90 and 9b, are fixedly mounted on the wheel spindle 8 at positions corresponding to the workpiece portions 511 and 5b.
  • a slide base 19 is mounted on a sloping surface of a pedestal 79 which is secured to the wheel slide 7 on the side of the grinding wheels 9n and 9b oppositely disposed from the workpiece 5.
  • a slide 22 which carries a plurality of dressing heads corresponding in number to the grinding wheels, in this embodiment two dressing heads 12a and 12b.
  • rotary dressers 16a and 16b are rotatably mounted and connected with each other by means of a spline shaft 90 and universal joints 91.
  • a drive pulley 15 for the rotary dressers 16a and 16b is connected to the drive shaft of an electric motor 13 mounted on the dressing head 12a by a belt 14.
  • the dressing heads 12a and 12b are slidably mounted through rams 23 on the slide 22 and are individually movable toward and away from the grinding wheels 90 and 9 b by respective ratchet mechanisms 20a and 20b through feed screws 21a and 21b and the rams 23 which are interengaged therewith.
  • another ratchet mechanism 17 is provided for moving the slide 22 back and forth on the slide base 19 through the operation of a feed screw 18 which is threadably engaged with the slide 22. Therefore, the dressing heads 12a and 1217 may be moved together by operating feed screw 18 to move the slide 22 and also individually through the operation of feed screws 21a and 21b.
  • a feed mechanism for the wheel slide 7 will now be described, still referring to FIGS. 1 and 2.
  • the shaft 34 is supported by a bushing 35 fixedly mounted on the base 1.
  • the gear 26 is further provided with a cylindrical hollow, or chamber, 28 in one end thereof which contains a slidable piston 28a and a spring 27 compressed between the piston end remote from the shaft 34 and a closure member secured to the open end of the chamber 28 for normally urging the clutch elements 29 and 30 away from each other and thereby maintaining the same in a disengaged state.
  • the shaft 34 When the clutch elements 29 and 30 are disengaged from each other, the shaft 34 may be rotated by the operator through the hand wheel 11, the gear 26 keyed thereto and intermediate connecting gears, not shown.
  • the shaft 34 when the clutch elements 29 and 30 are engaged with each other, the shaft 34 may be automatically rotated by a feeding actuator device 71, that is, the movement of a rack 31 formed on the piston rod of the feeding actuator 71 is transferred to the shaft 34 through a pinion 30a and the clutch elements 29 and 30.
  • the rotation of the shaft 34 is further transferred to a transmission shaft 37 through gears 32 and 33 being respectively secured to the shaft 34 intermediate its ends and the front end of the transmission shaft 37.
  • Engagement of the clutch 29 with the clutch element 30 may be effected by supplying pressurized fluid through an end radial port 36 and an axial bore 34a in the shaft 34 to the chamber 28 between the piston 28a and the clutch element 29 for urging the piston to further compress the spring 27 and the clutch 29 to be shifted toward the clutch element 30.
  • a gear 38 which meshingly engages an idler gear 39 which further engages an axially elongate gear member 40.
  • the elongate gear 40 is rotatably supported in the base 1 and engages another gear 41 secured to the rear end of a feeding shaft 44 so that the shaft 44 may be rotated either manually through operation of hand wheel 11 or by the feeding actuator 71.
  • a hydraulic actuator 42 is provided which comprises a cylindrical chamber 420, a piston 43 slidably disposed therein and the feeding shaft 44.
  • the piston 43 is rotatably mounted. on the shaft 44 but is retained by conventional shoulders from any axial movement with respect to the shaft.
  • a screw 45 is formed on the front end of the feeding shaft 44 where it engages a nut 46 secured to the underside of the wheel slide 7 for causing the same to be moved along the longitudinal axis of the shaft 44. Therefore, the wheel slide 7 may be moved at a rapid speed toward and from the workpiece 5 by the hydraulic actuator 42 and at a slower speed either manually through operation of the hand wheel 1 1 or by the feeding actuator 71 through the transmission shaft 37 and its associated mechanism.
  • a rocking piece 48 which is rotatably mounted on the end of the transmission shaft 37 but is prevented from axial movement thereon, has a pinion 480 formed thereon which is engaged with a rack 52.
  • a ratchet pawl 51 is pivotally mounted on the rocking piece 48 and is engageable with a ratchet wheel 49 which is keyed to the shaft 37. lnterposed between the ratchet pawl 51 and the ratchet wheel 49 is an arc-shaped plate member 50 which is secured to a housing 50a for the compensating mechanism.
  • the compensating actuator 64 for the compensating mechanism is actuated by pressurized fluid for turning the rocking piece 48 to thereby make the ratchet pawl 51 engage with the ratchet wheel 49.
  • the transmission shaft 37 may be turned through a predetermined angle so that the wheel slide 7 may be shifted according to the reduction of the grinding wheel radius caused by normal wear thereof and any dressing operations performed thereon.
  • the amount of compensation may be controlled by the arc-shaped plate 50. That is, the ratchet pawl 51 is positioned on the plate 50 at the start and therefore is not initially engaged with the ratchet wheel 49.
  • the ratchet pawl 51 slides on the plate 50 through a predetermined distance, and thereafter the pawl 51 becomes disengaged from the plate 50 so that it engages the ratchet wheel 49, whereby it is operative to rotate the ratchet wheel 49 therewith. Accordingly, by controlling the angular position of the plate 50, the distance through which the pawl 51 slides on the plate 50 may be changed and thus, the amount of rotation of the ratchet wheel 49 is changed, since the total amount of rotation of the rocking piece 48 is always the same.
  • the clutch elements 29 and 30 are disengaged from each other and the wheel slide 7 is located in a retracted or an original position.
  • FIG. 3 in conjunction with the grinding machine shown in FIGS. 1 and 2, the ratchet feeding mechanism 17 positioned at the rear of the pedestal 79 for moving the dressing head-supporting slide 22 thereon will now be described in detail.
  • a rocking piece 77 which is rotatably mounted on one end of the feed screw shaft 18, meshingly engages a rack 78a formed on a piston 78'slidably disposed in a hydraulic actuator 80.
  • a pair of ratchet pawls 73 and 75 are pivotally carried by the rocking piece 77, the ratchet pawl 73 being used for advancing the slide 22 and the ratchet pawl 75 being used for retracting the slide 22.
  • a pair of ratchet wheels 72a and 72b are secured in side-by-side relation to the feed screw 18.
  • a pair of arc-shaped plates 74 and 76 are respectively adjustably mounted on the interior of the feed mechanism housing between the ratchet wheel 72a and the ratchet pawl 73 and between the ratchet wheel 72b and the ratchet pawl 75.
  • the rocking piece 77 is turned in a clockwise direction so that the ratchet pawl 73 slides over the arc-shaped plate 74 during a predetermined amount of such movement of the rocking piece 77, and thereafter becomes engaged with the ratchet wheel 72a, whereby the feeding screw connected therewith is turned so that the slide 22 and the dressing heads 12a and 12b disposed thereon are advanced toward the grinding wheels 9a and 9b.
  • the pawl 75 rides onto the sur face of the plate 76.
  • the piston 78 is moved to the right for retracting the ratchet pawl 73 onto the plate 74, the pawl 73 at first freely riding over the wheel 72a during this counterclockwise rotation of the rocking piece 77.
  • the ratchet pawl 75 slides on the plate 76 for a predetermined distance and thereafter becomes engaged with the ratchet wheel 72b, so that the dressing heads 12a and 12b are retracted. Since the feed screw 18 is not rotated while the ratchet pawl 75 slides on the plate 76, the dressing heads 12a and 12b are disposed at an advanced position by a calibrated distance.
  • a changeover valve 55 is provided for the hydraulic actuator 42, having an associated solenoid SOL l which is operative upon energization or de-energization to cause the wheel slide 7 to be moved toward or from the workpiece at a high rate of speed.
  • Another changeover valve 56 controls the supply of pressurized fluid to the hydraulic actuator 71 for providing automatic relatively slower feeding movement of the wheel slide 7.
  • a solenoid SOL 2 associated with the change over valve 56 is energized, fluid pressure moves a piston 71a of the hydraulic actuator 71 to the right, as viewed in FIG.
  • a throttling circuit which comprises a rough feed throttle valve 58, a fine feed throttle valve 59 and a shut-off valve 57.
  • the throttle valves 58 and 59 are provided in series with each other between the forward chamber 71b of the hydraulic actuator 71 and the changeover valve 56.
  • the shut-off valve 57 and the throttle valve 59 are connected in parallel relation.
  • Numeral 61 indicates a changeover valve which is provided for causing engagement and disengagement of the automatic sizing devices 60 and 6b with workpiece 5.
  • Another changeover valve 62 controls the operation of the compensating actuator 64.
  • a solenoid SOL 8 associated with the changeover valve 62 is energized, a piston in the compensating actuator 64 is advanced in order to compensate for any diametric reduction of the grinding wheels 9a and 9b.
  • a manual changeover valve 63 which controls the hydraulic actuator 28.
  • the manual changeover valve 63 is changed to AUTO, that is, to a position indicated by I, the pressurized fluid is directed to the actuator 28 so as to engage the clutch elements 29 and 30 by moving the piston against the force of the compressed spring 27.
  • a changeover valve 65 is provided for controlling the operation of the hydraulic actuator 80.
  • a solenoid SOL 7 When a solenoid SOL 7 is energized, the piston 78 is moved to the left as viewed in FIG. 3, and thus, the dressing heads 12a and 12b are advanced by means of the ratchet mechanism 17. Until engagement between a shut-off valve 66 and a dog 83 mounted on the piston rod 78b occurs, the dressing heads 12a and 12b are advanced at a rapid speed toward the grinding wheels 9a and 9b.
  • the dog 83 engages the shutoff valve 66, whereby a by-pass conduit through shutoff valve 66 is closed and thus, the fluid being evacuated from the actuator 80 is throttled by a throttle valve 81 so that the rotary dressers 16a and 16b are advanced at a slow dressing speed into the grinding wheels 9a and 9b to perform the desired dressing operation thereon.
  • a limit switch LS3 is actuated by a dog 84 secured thereto for de-energizing the solenoid SOL 7 so that the pressurized fluid will be supplied to the opposite chamber of the hydraulic actuator 80 through a check valve 82 which is interposed in parallel relation with the throttle valve 81, and thus, the dressing heads 12a and 12b are retracted at a rapid speed.
  • LS2 indicates another limit switch in line with LS3 which is provided to confirm the fact that the piston 78 has been fully retracted to the right end, or in other words, that the dressing heads 12a and 12b have been retracted to their original positions.
  • Changeover valves 67 and 68 are provided for hydraulic actuators 69 and 70, respectively, comprising the ratchet mechanisms 20a and 20b for individually advancing the dressing heads 12a and 12b.
  • solenoids SOL 9 and SOL 10 which are controlled by the signals supplied by the automatic sizing devices 6a and 6b, respectively, are energized, the dressing heads 12a and 12b are advanced toward the grinding wheels 9a and 9b by a predetermined short distance.
  • the signals supplied by the automatic sizing devices 6a and 6b are passed through an amplifier 101 to a Schmitt trigger circuit 102 which, in turn, provides signals S1, S2, S3 and S4 from each of the sizing devices.
  • the signals S1, S2, S3 and S4 are respectively produced when the diameters of portions a and 5b on the workpiece 5 are ground to predetermined levels.
  • the signals S1 and S2 are produced for each of the workpiece portions at preselected diameter values thereon, and the difference between the signals S1 and S2 is equal to an established permissible tolerance between the finished diameters of the portions 5a and 5b.
  • the fact that the signal S2 is produced by either one of the automatic sizing devices 60 and 6b when the signal S1 has not yet been produced by the other of the sizing devices means that the differencein the diameters of workpiece portions 5a and 5b at that point exceeds the allowed tolerance.
  • the signal S3 is produced when the depth of the workpiece portion yet to be removed reaches a point that requires the feed speed of the wheel slide 7 to be changed from a rough grinding speed to a fine grinding speed
  • the signal S4 is produced when the respective diameters of the portions 5a and 5b are ground to a finished diameter.
  • the signals produced by the automatic sizing device 6a are indicated hereinafter by the reference characters 181, 182, 183 and 184, and the signals produced by the automatic sizing device 6b are indicated by 281, 282, 283 and 284.
  • each pair of signals for example, the signals 182 and 282
  • the signal 281 has not been produced in spite of the fact that the signal 182 has already been produced, as indicated hereinbefore, the workpiece portions 5a and 5b are being unevenly ground such that the diameter of the portion 5b is larger than that of the portion 5a.
  • Symbols CR, SOL and TR are used to designate relay coils, solenoids and timer coils, respectively.
  • Symbols cr indicate contacts in the control circuit associated with the relay coils having the same number.
  • Numerals 1 and 2 which appear at the head of the symbol as indicate the contacts operated by the signals which are supplied from the automatic sizing devices 6a and 6b respectively.
  • the symbol as or cr, with the symbol x thereafter, represents a normally closed contact, while without the symbol x, a normally open contact is represented.
  • the relay coil CR5 and solenoid SOLS are energized by normally closed coils crlx and cr2x, and furthermore, the relay coils CRIS and CR13 are energized, since the limit switches LS1 and LS2 are actuated.
  • an operator of the machine herein disclosed pushes a button PB2 to permit energization of the relay coil CR1 and the solenoid SOLl to thereby close contacts crl, whereby the relay coil CR1 is self held by means of the now closed associated contact crl disposed parallel to PB2.
  • the period determined by the timer coil TRl elapses, causing contact trl to close to thereby energize the relay coil CR3 and the solenoid SOL3, whereby the automatic sizing devices 6a and 6b are advanced to engage the workpiece 5.
  • the signals 181 and 281 are supplied by the automatic sizing devices 6a and 6b to open normally closed contacts laslx and 2aslx.
  • the signals 182 and 282 are supplied to thereby close the normally open contacts 11152 and 2as2.
  • the automatic sizing devices 6a and 6b supply the signals 183 and 283, whereby normally closed contacts 1as3x and 2as3x are opened to thereby de-energize the relay coil CR4 and solenoid SOL4. Accordingly, the by-pass through the shut-off valve 57 is closed so that a fine grinding speed is rendered to the wheel slide 7.
  • the automatic sizing devices 6a and 6b supply the sizing signals 184 and 284 which respectively are effective to close the contacts las4 and 2as4.
  • the. automatic sizing devices 6:: and 6b are retracted to the original positions thereof, since the relay coil CR3 and the solenoid SOL 3 are now deenergized, the timer coil TR 1 being de-energized when the relay coil TRl is dc-energized.
  • the limit switch LS1 is actuated, whereby the spindle motor 4 is stopped.
  • a button P133 is pushed by an operator resulting in the energization of the relay coil CR14, since the relay coil CR13 has been energized by means of the limit switch LS2 to close contacts crl3.
  • the relay coil CR14 is energized, all of its associated contacts cr14 are closed to thereby energize a relay coil CR7 and the solenoid SOL 7, whereby the dressing heads 12a and 12b are advanced toward the grinding wheels 9a and 9b for the dressing operation by the rotary dressers 16a and 16b being rotated by the motor 13.
  • the compensating actuator 64 is actuated to advance the wheel slide 7 to compensate for the reduced radius of g the grinding wheels 9a and 9b due to wear thereof and the dressing operation performed thereon. It will be appreciated that, at this time the clutch elements 29 and 30 are disengaged from each other under the forceof spring 27.
  • a limit switch LS3 is actuated by the dog 84 to thereby energize relay coil CRIS and timer coil TR3.
  • tr3 closes sothat the relay coil CR16 is energized, whereby contacts cr16x are opened and the relay coil CR14 is de-energized.
  • the relay coil CR7 and the solenoid SOL Tare also de-energized, contacts cr14 now being open again, so that the dressing apparatus is retracted at a rapid speed, and the limit switch LS3 is disengaged from the dog 84 to thereby tie-energize the relay coils CR15, CR8 and solenoid SOL 8.
  • the relay coil CRll is energized, such that all the normally open and closed contacts all and crllx, respectively, associated therewith are reversed, whereby the relay coil CR2 and the solenoid SOL 2 are de-energized to stop the movement of the wheel slide 7 and at the same time, the relay coil CR7 and the solenoid SOL 7 are energized so that the slide 22 is advanced by means of the ratchet mechanism 17. Furthermore, the relay coil CR9 and the solenoid SOL 9 are now energized to advance the dressing head 12a with respect to the slide 22 so that the grinding wheel 9a may be dressed off by a larger amount than that of the grinding wheel 9b.
  • the limit switch LS3 is disengaged from the dog 84 to thereby de-energize the relay coil CRIS.
  • the relay coil CR17 is energized to thereby de-energize the relay coil CR1 1 and energize the relay coil CR2 and the solenoid SOL 2.
  • solenoid SOL 2 pressurized fluid is supplied to the actuator 71 in a direction to advance the wheel slide 7 toward the workpiece 5 again.
  • the automatic sizing device 6b produces the signals 251 and 282.
  • the signals 183 and 283 are simultaneously produced by the automatic sizing devices 6a and 6b, since the grinding wheels 9a and 9b are dressed up to grind the workpiece 5 into the same size.
  • the signals 183 and 283 effect the de-energization of the relay coil CR4 and SOL 4 so that the infeed speed of the wheel slide 7 is changed from a rough grinding speed to a fine grinding speed.
  • the sizing signals 184 and 284 are produced by the automatic sizing devices and 6b,
  • the relay coil CR6 is energized and thus, relay coil CR2 and solenoid SOL 2 are de-energized to stop the movement of the wheel slide 7 and the timer coil TR2 is energized to make the wheel slide 7 stay at the same position to perform a spark-out operation. After the predetermined time, the wheel slide 7 is retracted in the usual manner according to an ordinary grinding operation.
  • the relay coil CRIS is energized to thereby energize the relay coil CR8, solenoid SOL 8 and timer coil TR4 through the now closed contacts cr17 and crl8.
  • the compensating actuator 64 is actuated to compensate for the diameter reduction of the grinding wheels 9a and 9b, that is to advance the wheel slide 7 by the amount which the radius of the grinding wheels has been reduced.
  • the relay coils CR17 and CR8 and solenoid SOL 8 are de-energized after a time determined by the timer coil TR4.
  • the difference is automatically detected and the grinding operation is automatically instantly halted.
  • the grinding wheels are then unevenly dressed so that the difference is eliminated. Accordingly, the workpieces are not ruined and are machined with high machining accuracy, since the compensating operation is done during the grinding operation.
  • a multi-wheel grinding machine comprising:
  • supporting means mounted on said base and adapted to rotatably support a workpiece having a plurality of portions thereon to be ground;
  • first feeding means for moving said wheel slide toward and away from said workpiece to perform a grinding operation thereon with said grinding wheels
  • second feeding means mounted on said wheel slide and connected to said dresser slide for moving said dresser slide toward and away from said grinding wheels to perform dressing operations thereon;
  • a plurality of third feeding means mounted on said dresser slide for moving said plurality of dressing means toward and away from said grinding wheels;
  • a multi-wheel grinding machine comprising:
  • head stock and foot stock means mounted on said table for supporting a workpiece therebetween having at least two portions to be ground;
  • a pair of automatic sizing devices mounted on said table and operable to measure the diameters of said two portions
  • a wheel slide slidably mounted on said base and supporting at least a pair of rotatable grinding wheels
  • first feeding means for moving said wheel slide toward and from said workpiece to perform a grinding operation thereon with said grinding wheels
  • second feeding means mounted on said wheel slide and connected to said dresser slide for moving said dresser slide toward and from said at least a pair of grinding wheels to perform dressing operations thereon;
  • a control system operably connected to said first, second and third feeding means for halting the movement of said first feeding means and actuating said second and third feeding means to dress said grinding wheels unevenly when a difference between output values of said sizing devices corresponding to diameters of said workpiece portions being ground is detected to be beyond a predetermined value, and for advancing said wheel slide again following a dressing operation, whereby said workpiece portions are ground to substantially predetermined dimensions.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Grinding Of Cylindrical And Plane Surfaces (AREA)
  • Constituent Portions Of Griding Lathes, Driving, Sensing And Control (AREA)
  • Grinding-Machine Dressing And Accessory Apparatuses (AREA)
US00123215A 1970-03-11 1971-03-11 Multi-wheel grinding machine Expired - Lifetime US3717961A (en)

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JP45020716A JPS496277B1 (enrdf_load_stackoverflow) 1970-03-11 1970-03-11

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US3717961A true US3717961A (en) 1973-02-27

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US (1) US3717961A (enrdf_load_stackoverflow)
JP (1) JPS496277B1 (enrdf_load_stackoverflow)
DE (1) DE2111770C3 (enrdf_load_stackoverflow)
FR (1) FR2081852B1 (enrdf_load_stackoverflow)
GB (1) GB1285852A (enrdf_load_stackoverflow)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3885353A (en) * 1972-10-28 1975-05-27 Toyoda Machine Works Ltd Grinding machine
US4376357A (en) * 1980-05-21 1983-03-15 Keighley Grinders (Machine Tools) Ltd. Machine tools
CN101590619B (zh) * 2008-05-30 2013-06-26 无锡上机数控股份有限公司 一种数控曲轴曲拐外圆磨床
CN112264846A (zh) * 2020-10-23 2021-01-26 江西国丰电子科技有限公司 一种电子产品圆形外壳打磨装置

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112091782B (zh) * 2020-10-10 2024-08-06 江苏准信精密技术有限公司 一种修磨总装

Citations (5)

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Publication number Priority date Publication date Assignee Title
US2851827A (en) * 1957-11-08 1958-09-16 Norton Co Multiple wheel grinding machine
US2931145A (en) * 1957-02-28 1960-04-05 Norton Co Grinding machine
US2946162A (en) * 1958-05-19 1960-07-26 Norton Co Multiple wheel grinding machine
US2950581A (en) * 1959-03-30 1960-08-30 Cincinnati Milling Machine Co Gaging device
US3006332A (en) * 1958-10-10 1961-10-31 Norton Co Powered rotary truing device

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2931145A (en) * 1957-02-28 1960-04-05 Norton Co Grinding machine
US2851827A (en) * 1957-11-08 1958-09-16 Norton Co Multiple wheel grinding machine
US2946162A (en) * 1958-05-19 1960-07-26 Norton Co Multiple wheel grinding machine
US3006332A (en) * 1958-10-10 1961-10-31 Norton Co Powered rotary truing device
US2950581A (en) * 1959-03-30 1960-08-30 Cincinnati Milling Machine Co Gaging device

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3885353A (en) * 1972-10-28 1975-05-27 Toyoda Machine Works Ltd Grinding machine
US4376357A (en) * 1980-05-21 1983-03-15 Keighley Grinders (Machine Tools) Ltd. Machine tools
CN101590619B (zh) * 2008-05-30 2013-06-26 无锡上机数控股份有限公司 一种数控曲轴曲拐外圆磨床
CN112264846A (zh) * 2020-10-23 2021-01-26 江西国丰电子科技有限公司 一种电子产品圆形外壳打磨装置
CN112264846B (zh) * 2020-10-23 2021-12-10 江苏柒捌玖电子科技有限公司 一种电子产品圆形外壳打磨装置

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DE2111770B2 (de) 1978-08-17
DE2111770C3 (de) 1979-03-29
GB1285852A (en) 1972-08-16
FR2081852B1 (enrdf_load_stackoverflow) 1973-06-08
DE2111770A1 (de) 1971-09-30
FR2081852A1 (enrdf_load_stackoverflow) 1971-12-10
JPS496277B1 (enrdf_load_stackoverflow) 1974-02-13

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