CA1305859C - Centerless grinder construction - Google Patents
Centerless grinder constructionInfo
- Publication number
- CA1305859C CA1305859C CA000581150A CA581150A CA1305859C CA 1305859 C CA1305859 C CA 1305859C CA 000581150 A CA000581150 A CA 000581150A CA 581150 A CA581150 A CA 581150A CA 1305859 C CA1305859 C CA 1305859C
- Authority
- CA
- Canada
- Prior art keywords
- regulating wheel
- wheel
- axis
- rotation
- regulating
- 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
Links
Landscapes
- Grinding Of Cylindrical And Plane Surfaces (AREA)
Abstract
CENTERLESS GRINDER CONSTRUCTION
ABSTRACT OF THE DISCLOSURE
A centerless grinder having a rotary grinding wheel and a rotary regulating wheel wherein the regulating wheel is adjustable toward and away from the grinding wheel and has its axis of rotation rockable in a substantially horizontal plane.
An infinitely variable speed mechanism is coupled to the regulating wheel in such manner as to enable the drive mechanism and the drive coupling to move conjointly with the regulating wheel. The coupling mechanism resists unwanted changes in the speed of rotation of the regulating wheel and absorbs shocks that result from the replacement of finished workpieces with unfinished workpieces.
ABSTRACT OF THE DISCLOSURE
A centerless grinder having a rotary grinding wheel and a rotary regulating wheel wherein the regulating wheel is adjustable toward and away from the grinding wheel and has its axis of rotation rockable in a substantially horizontal plane.
An infinitely variable speed mechanism is coupled to the regulating wheel in such manner as to enable the drive mechanism and the drive coupling to move conjointly with the regulating wheel. The coupling mechanism resists unwanted changes in the speed of rotation of the regulating wheel and absorbs shocks that result from the replacement of finished workpieces with unfinished workpieces.
Description
~3~5~59 I
CENTERLESS GRINDER CONST~ UCTION
1 ¦ This inven~ion relates to a centerless grinder of the 2 ¦ kind having a rotary grinding wheel and a rotary regulating 3 ~ wheel with a gap therebetween in which a workpiece may be 4 ¦ accommodated for grinding.
~ ¦ Centerless grinders are well known and conventionally 7 ¦ comprise a base on which a rotary grinding wheel is mounted for 8 ¦ rotation in one direction about a substantially horizontal axis ~ ¦ and a regulating wheel which confronts, but is spaced from, the ¦ grinding wheel and which is mounted on the base for rotation in 11 ¦ the same direction about an axis. The axis of rotation of the 12 ¦ regulating wheel frequently is inclined somewhat to the ¦ horizontal so as to enable a workpiece accommodated in the gap 14 ¦ between the grinding and regulating wheels to be fed ¦ automatically through such gap as the workpiece is ground.
1~ ¦ It i8 conventional to mount the grinding wheel, the 17 ¦ regulating wheel, or both, for adjustment toward and away from 18 ¦ one another and thereby vary the gap between such wheel~.
1~ Adjustability of the gap is necessary so a~ to enable the ¦ grinding machine to accommodate workpieces of different 21 ¦ diameters and also to compensate for wear of the grinding wheel 22 ¦ due to attrition and dressing. Although conventional centerless ¦ grinders include adjusting mechanisms for these purposes, 24 ¦ adjusting means should be provided to compensate for changes in the peripheral speed of the grinding wheel because of the reduc-¦ tion in its diameter due to such attrition and dressing. It is ~7 ¦ believed that some centerless grinders provide one, or possibly a8 ¦ two, input driving speeds for the grinding wheel or regulating a~ ¦ wheel, but in those instances in which the grinder is used to ~0 ¦ grind workpieces to extremely small tolerences, such limited ~3~ 359 1 sE ed adju~tments are inadequate.
2 Apparatus constructed in accordance with the invention overcomes the prior art inadequacy by providing an infinitely 4 adjustable drive mechanism for the regulating wheel.
It is not uncommon for the coupling between the ~ regulating wheel and its driving means to comprise a complex, 7 geared transmission. Since the grinding wheel and the 8 regulating wheel are driven in the same direction, and since 8 the workpiece is positioned in the gap between the two wheels, and since the grinding wheel conventionally is the larger wheel 11 and has a greater peripheral speed, the workpiece transmits a 12 force from the grinding wheel to the regulating wheel that attempts to accelerate the latter. This phenomenon often i5 14 referred to as "back driving" and subjects the conventional 1~ geared transmission to severe strain and consequent wear. The 1~ adverse effect of the grinding wheel's tending to drive the 17 regulating wheel via the workpiece is particùlarly noticeable 18 in those instances in which workpieces are presen~ed to the 19 grinder in spaced intervals. Thus, when a ground workpiece is removed from the gap between the wheels, the speed of the 21 regulating wheel may decrease, but when a fresh workpiece is 2Z introduced to the gap there is an immediate shock imposed on the regulating wheel drive mechanism due to the grinding ~4 wheel's attempting to accelerate the regulating wheel. As a consequence the speed of rotation of the regulating wheel 2~ varies, with adverse results on the finish of the workpiece, a7 and the drive mechanism is subjected to wear.
a~ Apparatus constructed in accordance with the invention 2~ overcomes these disadvantages of the known grinders by ~0 utilizing a regulating wheel drive mechanism which positively ~3~
1 resists any tendency to the regulating wheel.
2 The invertion as claimed provides a centerless 3 grinder construction comprising a base, a rotatable 4 grinding wheel mounted on the base Eor rotation about an axis, and a body member mounted on the base for linear 6 movements toward and away from the grinding wheel. There 7 is a rotatable regulating wheel and carrier means mounting 8 the regulating wheel for rotation about an axis spaced from 9 the axis of the grinding wheel. Adjustable mounting means mounts the carrier means on the body member for linear 11 movements with the body member and for rocking movements 12 relative to the body member about an axis normal to the 13 axis of rotation of the regulating wheel. Support means is 14 secured directly to the carrier means for movements therewith. Driving means is rotatable about an axis spaced 16 from and parallel to the axis of rotation of the regulating 17 wheel. Drive transmission means is rotatable about an axis 18 spaced from and parallel to the axis of rotation of the 19 regulating wheel, the transmiæsion means including a hydrostatic pump-motor assembly coupling the driving means 21 and the regulating wheel for rotating the latter. The 22 transmission means has an infinitely variable speed output 23 and is operable to maintain substantially constant any 24 selected output speed. Means secures the driving means and the transmission means directly to the support means 26 whereby the driving means, the transmission means, and the 27 regulating wheel are conjointly and bodily movable relative 28 to the body member about the normal axis.
29 More particularly, a centerless grinder A
~3~
1 constructed in accordance with the invention includes a 2 base on which is mounted a rotary grinding wheel and a body 3 member on which is mounted a rotary regulating wheel. The 4 body and, consequently, the regulating wheel are adjustable toward and away from the grinding wheel so as to vary the 6 workpiece-accommodating gap therebetween. The regulating 7 wheel is carried by a carrier which is mounted on the body 8 for rocking movements about a substantially horizontal 9 axis, thereby enabling the axis of rotation of the regulating wheel to be adjusted in a substantially vertical 11 plane.
12 The regulating wheel is coupled by drive 13 transmission means to rotary driving means. The regulating 14 wheel carrier and the driving means are rigidly secured to one another for conjoint movement not only toward and away 16 from the grinding wheel, but also for conjoint rocking 17 movements. Securing the regulating wheel carrier and the 18 driving means to one another ensures that the drive 19 transmitting means which couples the driving means and the regulating wheel will be maintained in a fixed position 21 relative to the driving means and to the regulating wheel, 22 thereby positively avoiding the imposition of undesirable 23 forces on the drive transmitting means due to rocking of 24 the axis of rotation oE the regulating wheel.
The regulating wheel driving means associated with 26 apparatus constructed in accoxdance with the invention is 27 infinitely variable in speed, thereby enabling optimum 28 relative peripheral speeds of the regulating wheel and the 29 grinding wheel to be maintained for the most efficient grinding of a workpiece.
- 3a -13~5~5g 1 The driving mechanism for the regulating wheel 2 incorporates self-actuating means which resi~t forces tending to rotate the regulating wheel backwards and which also absorb 4 shocks caused by substituting a fresh workpiece for a finished one.
7 A preferred embodiment of the invention is illustrated 8 in the accompanying drawings, wherein:
~ Figure 1 is a side elevational view of a centerless grinding machine incorporating apparatus constructed in 11 accordance with the inventiont 12 Figure 2 is a fragmentary, greatly enlarged, sectional 13 view taken generally on the line 2-2 of Figure ls 14 Figure 3 is a sectional view taken generally on the 1~ line 3-3 of Figure 2, appearing with Figure l; and 1~ Figure 4 is a somewhat diagramatic view, on a reduced 17 scale, illustrating the opposite side of the apparatus shown in 18 Figure 3.
~20 A centerless grlnder 1 according to the invention has 21 a base 2 on which is mounted a housing 3 in which is journaled 2Z a rotary grinding wheel GW driven in the direction of the arrow Z5 a by a suitable motor (not shown). The housing 3 is adjustable ~4 longitudinally of the base 1 by conventional adjusting means 4.
26 The machine 1 includes a body or housing 5 mounted on 2B the base 2 for adjustments longitudinally of the latter toward ~7 and away from the grinding wheel GW by means of conventional a8 adjusting means 6. At that end of the housing 5 which a~ confronts the grinding wheel GW is a carrier 7 in which is ~0 journaled a regulating wheel shaft 8 on which is fixed a ~3C~ i9 1 r gulating wheel RW. The car~ier 7 abuts a mounting plate 9 2 ¦ carried by the housing 5 and is provided with mounting bolts 10 at its opposite ends which extend through slots 11 formed in 4 the mounting plate 9. The bolts 10 may be loosened, when desired, to enable the support 7 and consequently the regulating ~ wheel RW, to be rocked about a substantially horizontal axis 7 that is perpendicular to the axis of rotation of the grinding 8 wheel GW. The bolts 10 then may be tightened to maintain the ~ carrier 7 in any selected position of angular adjustment. The carrier 7 also is adjuGtable vertically by means of a conven-11 tional adju~ting mechanism 12 so as to position the axis of the 12 shaft 8 at a desired level.
Between the grinding wheel GW and the regulating wheel 14 RW is a support 14 on which a cylindrical workpiece WP may be supported. The gap between the grinding wheel GW and the 1~ regulating wheel RW may be adjusted by either or both of the 17 respective adjusting means 4 and 6 to enable the workpiece WP
18 to be engaged by the peripheries of both of the whee~s.
19 The housing 5 has a bottom 16 provided with guideways or the like ~not shown) to facilitate its adjustment longitudin-21 ally of the base 2 i.e. toward and away from the grinding wheel 2Z GW. The housing 5 also has a rear wall 17, a front wall 18, Z5 and side walls 19. The housing also has an upper wall 20 a4 provided with an opening 21. Accommodated in the opening 21 is a support or mounting plate 22 of less area than that of the opening 21. Fixed to and depending from the lower surface of 27 the plate 22 is a mounting plate 23 at the forward end of which 28 is fixed an extension 24 that is welded or otherwise suitably fixed to a generally rectangular frame 25 having an opening 26 ~0 thereinO The front wall 18 of the housing 5 has an opening 27 _5_ ~
1 t rein thlough which the exten~ion 24 and the mounting frame 2 25 freely extend. The mounting frame 25 is secured by bolts or the like to the rear wall 28 of the carrier 7 r and such wall 4 has an ~pening 29 therein.
Means is provided for effecting rotation of the ~ regulating wheel RW and comprises an infinitely variable speed, 7 integrated, hydrostatic pump-motor coupling unit 30 of known 8 construction, such as that produced and sold by Dana Corporation ~ under the trademark HSV and described in its bulletin No.
MTP-003-85. In essence, the coupling unit 30 has a variable 11 displacement radial piston pump that drives a fixed displacement 12 radial piston mQtOr. The coupling unit is driven by a suitable 13 constant speed electric motor 31 having its output shaft 14 connected to the drive unit 30 in a conventional manner. The drive motor 31 and the coupling unit 30 are mounted by supports 1~ 32 on the common support plate 22 and the unit 30 has its 17 output shaft fixed to a driving pulley or sprocket wheel 33 18 around which is trained a driving belt or chain 34 which also 19 is trained around a pulley or sprocket wheel 35 fixed on the input shaft 36 of a geared speed reducer 37 of known kind. The 21 speed reducer 37 has a mounting flange 38 that is bolted or 22 otherwise fixed to the mounting plate 23, and such plate has an opening 39 through which the output shaft 40 of the reducer 37 a4 extends. Fixed to the shaft 40 is a pulley or sprocket wheel 41 around which is trained a drive transmitting belt or chain aB 42 which extends through the opening 2g in the rear wall 28 of a7 the carrier 7 and is trained around a sprocket wheel or pulley a8 43 that is fixed to the shaft 8 of the regulating wheel RW.
The construction and arrangement of the regulating wheel driving mechanism and its support are such that the l mo ting plate 22 is secured rigidly t~ the rear ~all 28 of the 2 regulating wheel carrier 7, but is not secured to the base 2 or S the housing 5. Accordingly, the driving means, the regulating 4 wheel RW, and the drive coupling means are movable as a unit and the axes of rotation of the coupling unit 30, the drive ~ motor 31, the reducer 37, and the regulating wheel shaft 8 are 7 maintained fixed at all times in parallel relationship. Thus, 8 whenever the regulating wheel housing carrier 7 is rocked to ~ tilt the axis of the shaft 8, the mounting plate 22 and the drive components 30, 31, and 37, together with drive ll transmitting chains or belts 34 and 42, also are rocked to the 12 same extent.
13 Since the drive motor, the drive coupling unit, and 14 the regulating wheel RW are fixed to the regulating wheel 1~ carrier 7, movement of the latter by the housing 5 longitudin-l~ ally of the base 2 also will be imparted to the drive and drive 17 transmitting units. Such movements of the regulating wheel 18 carrier 7 and the regulating wheel are possible because of the l9 securing of the carrier 7 to the mounting plate 9 of the housing 5.
21 Conventionally, and as is shown in Figure 1, the 22 grinding wheel GW is of considerably larger diameter than the 23 rgulating wheel RW. The grinding wheel thus has greater mass a4 and more inertia than the regulating wheel.
2~ In the operation of the apparatus, the grinding wheel a~ GW is caused to rotate in the direction of the arrow a in a a7 conventional manner by a suitable motor ~not shown3 and the a~ regulating wheel RW is caused to rotate in the direction of the 2~ arrow b by means of the drive motor 31 and the coupling unit ~0 30. Either or both of the driving and regulating wheels is ~3;~8~
1 ad usted to provide a suf~icient gap tùerebetween as to accomm~-2 date the workpiece WP for grinding. The regulating wheel also is adjusted by the adjusting means 12 so that its axis of rota-4 tion is at a level somewhat below the central axis of the work-piece WP, as is conventional.
~ The regulating wheel support 7 is adjusted, by manipu-7 ¦ lation of the bolts 10, so as to tilt the axis of rotation of 8 ¦ the regulating wheel an amount sufficient to effect feeding of ~ ¦ the workpiece in one direction or the other through the gap ¦ between the grinding and regulating wheels. The speed of 11 ¦ rotation of the regulating wheel 11 is set by manipulation of a 12 ¦ valve adjusting wheel 44 on the coupling unit 30 which lS ¦ regulates the rate of rotation of its output shaft. A
14 ¦ workpiece WP then may be introduced to the gap between the ¦ grinding and regulating wheels for grinding.
1~ ¦ As the grinding operations progress, the grinding 17 wheel becomes worn due to attrition and dressing. The diameter 18 of the grinding wheel, therefore, gradually decreases. As a 19 consequence, the peripheral speed of the grinding wheel decreases and the size of the gap between the grinding wheel 21 and the regulating wheel increases.
22 The size of the gap between the grindiny and regulat-23 ing wheels may be maintained substantially constant by operation a4 of the adjusting means 6 to effect movement of the body 5, including the carrier 7, toward the grinding wheel. The speed a~ of rotation of the workpiece may be maintained substantially a7 constant by varying the speed of rotation of the regulating a8 wheel RW by adjustment of the valve regulator 44 of the coupling a~ unit 30. The adjustments of the position and speed of the ~ regulating wheel may be effected by automatic means, rather ~3~
1 t n manua1ly, if desired.
2 Whenever a workpiece is being ground the greater mass and inertia of the grinding wheel GW causes the latter to exert 4 a force on the regulating wheel RW, via the workpiece, tending to accelerate the speed of rotation of the regulating whee1.
In the disclosed construction these tendencies are positively 7 overcome by the hydrostatic pump-motor coupling unit 30. This 8 is possible because, when a retarding force is imposed on the ~ motor of the pump-motor assembly, the motor converts itself into a pump which opposes the pump of the pump~motor assembly.
ll As a consequence, retardation of the speed of rotation of the 12 regulating wheel is virtually non-existent and shocks caused by 13 replacement of ground workpieces with fresh workpieces are 14 absorbed by the pump-motor assembly.
1~ The disclosed embodiment is representative of a lB presently preferred form of the invention, but is intended to 17 be illustrative rather than definitive thereof. The invention 19 i~ fined in the claims.
~8
CENTERLESS GRINDER CONST~ UCTION
1 ¦ This inven~ion relates to a centerless grinder of the 2 ¦ kind having a rotary grinding wheel and a rotary regulating 3 ~ wheel with a gap therebetween in which a workpiece may be 4 ¦ accommodated for grinding.
~ ¦ Centerless grinders are well known and conventionally 7 ¦ comprise a base on which a rotary grinding wheel is mounted for 8 ¦ rotation in one direction about a substantially horizontal axis ~ ¦ and a regulating wheel which confronts, but is spaced from, the ¦ grinding wheel and which is mounted on the base for rotation in 11 ¦ the same direction about an axis. The axis of rotation of the 12 ¦ regulating wheel frequently is inclined somewhat to the ¦ horizontal so as to enable a workpiece accommodated in the gap 14 ¦ between the grinding and regulating wheels to be fed ¦ automatically through such gap as the workpiece is ground.
1~ ¦ It i8 conventional to mount the grinding wheel, the 17 ¦ regulating wheel, or both, for adjustment toward and away from 18 ¦ one another and thereby vary the gap between such wheel~.
1~ Adjustability of the gap is necessary so a~ to enable the ¦ grinding machine to accommodate workpieces of different 21 ¦ diameters and also to compensate for wear of the grinding wheel 22 ¦ due to attrition and dressing. Although conventional centerless ¦ grinders include adjusting mechanisms for these purposes, 24 ¦ adjusting means should be provided to compensate for changes in the peripheral speed of the grinding wheel because of the reduc-¦ tion in its diameter due to such attrition and dressing. It is ~7 ¦ believed that some centerless grinders provide one, or possibly a8 ¦ two, input driving speeds for the grinding wheel or regulating a~ ¦ wheel, but in those instances in which the grinder is used to ~0 ¦ grind workpieces to extremely small tolerences, such limited ~3~ 359 1 sE ed adju~tments are inadequate.
2 Apparatus constructed in accordance with the invention overcomes the prior art inadequacy by providing an infinitely 4 adjustable drive mechanism for the regulating wheel.
It is not uncommon for the coupling between the ~ regulating wheel and its driving means to comprise a complex, 7 geared transmission. Since the grinding wheel and the 8 regulating wheel are driven in the same direction, and since 8 the workpiece is positioned in the gap between the two wheels, and since the grinding wheel conventionally is the larger wheel 11 and has a greater peripheral speed, the workpiece transmits a 12 force from the grinding wheel to the regulating wheel that attempts to accelerate the latter. This phenomenon often i5 14 referred to as "back driving" and subjects the conventional 1~ geared transmission to severe strain and consequent wear. The 1~ adverse effect of the grinding wheel's tending to drive the 17 regulating wheel via the workpiece is particùlarly noticeable 18 in those instances in which workpieces are presen~ed to the 19 grinder in spaced intervals. Thus, when a ground workpiece is removed from the gap between the wheels, the speed of the 21 regulating wheel may decrease, but when a fresh workpiece is 2Z introduced to the gap there is an immediate shock imposed on the regulating wheel drive mechanism due to the grinding ~4 wheel's attempting to accelerate the regulating wheel. As a consequence the speed of rotation of the regulating wheel 2~ varies, with adverse results on the finish of the workpiece, a7 and the drive mechanism is subjected to wear.
a~ Apparatus constructed in accordance with the invention 2~ overcomes these disadvantages of the known grinders by ~0 utilizing a regulating wheel drive mechanism which positively ~3~
1 resists any tendency to the regulating wheel.
2 The invertion as claimed provides a centerless 3 grinder construction comprising a base, a rotatable 4 grinding wheel mounted on the base Eor rotation about an axis, and a body member mounted on the base for linear 6 movements toward and away from the grinding wheel. There 7 is a rotatable regulating wheel and carrier means mounting 8 the regulating wheel for rotation about an axis spaced from 9 the axis of the grinding wheel. Adjustable mounting means mounts the carrier means on the body member for linear 11 movements with the body member and for rocking movements 12 relative to the body member about an axis normal to the 13 axis of rotation of the regulating wheel. Support means is 14 secured directly to the carrier means for movements therewith. Driving means is rotatable about an axis spaced 16 from and parallel to the axis of rotation of the regulating 17 wheel. Drive transmission means is rotatable about an axis 18 spaced from and parallel to the axis of rotation of the 19 regulating wheel, the transmiæsion means including a hydrostatic pump-motor assembly coupling the driving means 21 and the regulating wheel for rotating the latter. The 22 transmission means has an infinitely variable speed output 23 and is operable to maintain substantially constant any 24 selected output speed. Means secures the driving means and the transmission means directly to the support means 26 whereby the driving means, the transmission means, and the 27 regulating wheel are conjointly and bodily movable relative 28 to the body member about the normal axis.
29 More particularly, a centerless grinder A
~3~
1 constructed in accordance with the invention includes a 2 base on which is mounted a rotary grinding wheel and a body 3 member on which is mounted a rotary regulating wheel. The 4 body and, consequently, the regulating wheel are adjustable toward and away from the grinding wheel so as to vary the 6 workpiece-accommodating gap therebetween. The regulating 7 wheel is carried by a carrier which is mounted on the body 8 for rocking movements about a substantially horizontal 9 axis, thereby enabling the axis of rotation of the regulating wheel to be adjusted in a substantially vertical 11 plane.
12 The regulating wheel is coupled by drive 13 transmission means to rotary driving means. The regulating 14 wheel carrier and the driving means are rigidly secured to one another for conjoint movement not only toward and away 16 from the grinding wheel, but also for conjoint rocking 17 movements. Securing the regulating wheel carrier and the 18 driving means to one another ensures that the drive 19 transmitting means which couples the driving means and the regulating wheel will be maintained in a fixed position 21 relative to the driving means and to the regulating wheel, 22 thereby positively avoiding the imposition of undesirable 23 forces on the drive transmitting means due to rocking of 24 the axis of rotation oE the regulating wheel.
The regulating wheel driving means associated with 26 apparatus constructed in accoxdance with the invention is 27 infinitely variable in speed, thereby enabling optimum 28 relative peripheral speeds of the regulating wheel and the 29 grinding wheel to be maintained for the most efficient grinding of a workpiece.
- 3a -13~5~5g 1 The driving mechanism for the regulating wheel 2 incorporates self-actuating means which resi~t forces tending to rotate the regulating wheel backwards and which also absorb 4 shocks caused by substituting a fresh workpiece for a finished one.
7 A preferred embodiment of the invention is illustrated 8 in the accompanying drawings, wherein:
~ Figure 1 is a side elevational view of a centerless grinding machine incorporating apparatus constructed in 11 accordance with the inventiont 12 Figure 2 is a fragmentary, greatly enlarged, sectional 13 view taken generally on the line 2-2 of Figure ls 14 Figure 3 is a sectional view taken generally on the 1~ line 3-3 of Figure 2, appearing with Figure l; and 1~ Figure 4 is a somewhat diagramatic view, on a reduced 17 scale, illustrating the opposite side of the apparatus shown in 18 Figure 3.
~20 A centerless grlnder 1 according to the invention has 21 a base 2 on which is mounted a housing 3 in which is journaled 2Z a rotary grinding wheel GW driven in the direction of the arrow Z5 a by a suitable motor (not shown). The housing 3 is adjustable ~4 longitudinally of the base 1 by conventional adjusting means 4.
26 The machine 1 includes a body or housing 5 mounted on 2B the base 2 for adjustments longitudinally of the latter toward ~7 and away from the grinding wheel GW by means of conventional a8 adjusting means 6. At that end of the housing 5 which a~ confronts the grinding wheel GW is a carrier 7 in which is ~0 journaled a regulating wheel shaft 8 on which is fixed a ~3C~ i9 1 r gulating wheel RW. The car~ier 7 abuts a mounting plate 9 2 ¦ carried by the housing 5 and is provided with mounting bolts 10 at its opposite ends which extend through slots 11 formed in 4 the mounting plate 9. The bolts 10 may be loosened, when desired, to enable the support 7 and consequently the regulating ~ wheel RW, to be rocked about a substantially horizontal axis 7 that is perpendicular to the axis of rotation of the grinding 8 wheel GW. The bolts 10 then may be tightened to maintain the ~ carrier 7 in any selected position of angular adjustment. The carrier 7 also is adjuGtable vertically by means of a conven-11 tional adju~ting mechanism 12 so as to position the axis of the 12 shaft 8 at a desired level.
Between the grinding wheel GW and the regulating wheel 14 RW is a support 14 on which a cylindrical workpiece WP may be supported. The gap between the grinding wheel GW and the 1~ regulating wheel RW may be adjusted by either or both of the 17 respective adjusting means 4 and 6 to enable the workpiece WP
18 to be engaged by the peripheries of both of the whee~s.
19 The housing 5 has a bottom 16 provided with guideways or the like ~not shown) to facilitate its adjustment longitudin-21 ally of the base 2 i.e. toward and away from the grinding wheel 2Z GW. The housing 5 also has a rear wall 17, a front wall 18, Z5 and side walls 19. The housing also has an upper wall 20 a4 provided with an opening 21. Accommodated in the opening 21 is a support or mounting plate 22 of less area than that of the opening 21. Fixed to and depending from the lower surface of 27 the plate 22 is a mounting plate 23 at the forward end of which 28 is fixed an extension 24 that is welded or otherwise suitably fixed to a generally rectangular frame 25 having an opening 26 ~0 thereinO The front wall 18 of the housing 5 has an opening 27 _5_ ~
1 t rein thlough which the exten~ion 24 and the mounting frame 2 25 freely extend. The mounting frame 25 is secured by bolts or the like to the rear wall 28 of the carrier 7 r and such wall 4 has an ~pening 29 therein.
Means is provided for effecting rotation of the ~ regulating wheel RW and comprises an infinitely variable speed, 7 integrated, hydrostatic pump-motor coupling unit 30 of known 8 construction, such as that produced and sold by Dana Corporation ~ under the trademark HSV and described in its bulletin No.
MTP-003-85. In essence, the coupling unit 30 has a variable 11 displacement radial piston pump that drives a fixed displacement 12 radial piston mQtOr. The coupling unit is driven by a suitable 13 constant speed electric motor 31 having its output shaft 14 connected to the drive unit 30 in a conventional manner. The drive motor 31 and the coupling unit 30 are mounted by supports 1~ 32 on the common support plate 22 and the unit 30 has its 17 output shaft fixed to a driving pulley or sprocket wheel 33 18 around which is trained a driving belt or chain 34 which also 19 is trained around a pulley or sprocket wheel 35 fixed on the input shaft 36 of a geared speed reducer 37 of known kind. The 21 speed reducer 37 has a mounting flange 38 that is bolted or 22 otherwise fixed to the mounting plate 23, and such plate has an opening 39 through which the output shaft 40 of the reducer 37 a4 extends. Fixed to the shaft 40 is a pulley or sprocket wheel 41 around which is trained a drive transmitting belt or chain aB 42 which extends through the opening 2g in the rear wall 28 of a7 the carrier 7 and is trained around a sprocket wheel or pulley a8 43 that is fixed to the shaft 8 of the regulating wheel RW.
The construction and arrangement of the regulating wheel driving mechanism and its support are such that the l mo ting plate 22 is secured rigidly t~ the rear ~all 28 of the 2 regulating wheel carrier 7, but is not secured to the base 2 or S the housing 5. Accordingly, the driving means, the regulating 4 wheel RW, and the drive coupling means are movable as a unit and the axes of rotation of the coupling unit 30, the drive ~ motor 31, the reducer 37, and the regulating wheel shaft 8 are 7 maintained fixed at all times in parallel relationship. Thus, 8 whenever the regulating wheel housing carrier 7 is rocked to ~ tilt the axis of the shaft 8, the mounting plate 22 and the drive components 30, 31, and 37, together with drive ll transmitting chains or belts 34 and 42, also are rocked to the 12 same extent.
13 Since the drive motor, the drive coupling unit, and 14 the regulating wheel RW are fixed to the regulating wheel 1~ carrier 7, movement of the latter by the housing 5 longitudin-l~ ally of the base 2 also will be imparted to the drive and drive 17 transmitting units. Such movements of the regulating wheel 18 carrier 7 and the regulating wheel are possible because of the l9 securing of the carrier 7 to the mounting plate 9 of the housing 5.
21 Conventionally, and as is shown in Figure 1, the 22 grinding wheel GW is of considerably larger diameter than the 23 rgulating wheel RW. The grinding wheel thus has greater mass a4 and more inertia than the regulating wheel.
2~ In the operation of the apparatus, the grinding wheel a~ GW is caused to rotate in the direction of the arrow a in a a7 conventional manner by a suitable motor ~not shown3 and the a~ regulating wheel RW is caused to rotate in the direction of the 2~ arrow b by means of the drive motor 31 and the coupling unit ~0 30. Either or both of the driving and regulating wheels is ~3;~8~
1 ad usted to provide a suf~icient gap tùerebetween as to accomm~-2 date the workpiece WP for grinding. The regulating wheel also is adjusted by the adjusting means 12 so that its axis of rota-4 tion is at a level somewhat below the central axis of the work-piece WP, as is conventional.
~ The regulating wheel support 7 is adjusted, by manipu-7 ¦ lation of the bolts 10, so as to tilt the axis of rotation of 8 ¦ the regulating wheel an amount sufficient to effect feeding of ~ ¦ the workpiece in one direction or the other through the gap ¦ between the grinding and regulating wheels. The speed of 11 ¦ rotation of the regulating wheel 11 is set by manipulation of a 12 ¦ valve adjusting wheel 44 on the coupling unit 30 which lS ¦ regulates the rate of rotation of its output shaft. A
14 ¦ workpiece WP then may be introduced to the gap between the ¦ grinding and regulating wheels for grinding.
1~ ¦ As the grinding operations progress, the grinding 17 wheel becomes worn due to attrition and dressing. The diameter 18 of the grinding wheel, therefore, gradually decreases. As a 19 consequence, the peripheral speed of the grinding wheel decreases and the size of the gap between the grinding wheel 21 and the regulating wheel increases.
22 The size of the gap between the grindiny and regulat-23 ing wheels may be maintained substantially constant by operation a4 of the adjusting means 6 to effect movement of the body 5, including the carrier 7, toward the grinding wheel. The speed a~ of rotation of the workpiece may be maintained substantially a7 constant by varying the speed of rotation of the regulating a8 wheel RW by adjustment of the valve regulator 44 of the coupling a~ unit 30. The adjustments of the position and speed of the ~ regulating wheel may be effected by automatic means, rather ~3~
1 t n manua1ly, if desired.
2 Whenever a workpiece is being ground the greater mass and inertia of the grinding wheel GW causes the latter to exert 4 a force on the regulating wheel RW, via the workpiece, tending to accelerate the speed of rotation of the regulating whee1.
In the disclosed construction these tendencies are positively 7 overcome by the hydrostatic pump-motor coupling unit 30. This 8 is possible because, when a retarding force is imposed on the ~ motor of the pump-motor assembly, the motor converts itself into a pump which opposes the pump of the pump~motor assembly.
ll As a consequence, retardation of the speed of rotation of the 12 regulating wheel is virtually non-existent and shocks caused by 13 replacement of ground workpieces with fresh workpieces are 14 absorbed by the pump-motor assembly.
1~ The disclosed embodiment is representative of a lB presently preferred form of the invention, but is intended to 17 be illustrative rather than definitive thereof. The invention 19 i~ fined in the claims.
~8
Claims (4)
1. A centerless grinder construction comprising a base; a rotatable grinding wheel mounted on said base for rotation about an axis; a body member mounted on said base for linear movements toward and away from said grinding wheel; a rotatable regulating wheel; carrier means mounting said regulating wheel for rotation about an axis spaced from the axis of said grinding wheel; adjustable mounting means mounting said carrier means on said body member for linear movements with said body member and for rocking movements relative to said body member about an axis normal to the axis of rotation of said regulating wheel; support means secured directly to said carrier means for movements therewith; driving means rotatable about an axis spaced from and parallel to the axis of rotation of said regulating wheel; drive transmission means rotatable about an axis spaced from and parallel to the axis of rotation of said regulating wheel; said transmission means including a hydrostatic pump-motor assembly coupling said driving means and said regulating wheel for rotating the latter, said transmission means having an infinitely variable speed output and being operable to maintain substantially constant any selected output speed; and means securing said driving means and said transmission means directly to said support means whereby said driving means, said transmission means, and said regulating wheel are conjointly and bodily movable relative to said body member about said normal axis.
2. The construction according to Claim 1 wherein the axes of said regulating wheel and said driving means are at vertically spaced levels.
3. The construction according to claim 1 wherein said driving means comprises a constant speed motor connected to said transmission means.
4. The construction according to Claim 1 wherein said transmission means includes a speed reduction unit between said assembly and said regulating wheel.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CA000581150A CA1305859C (en) | 1988-10-25 | 1988-10-25 | Centerless grinder construction |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CA000581150A CA1305859C (en) | 1988-10-25 | 1988-10-25 | Centerless grinder construction |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA1305859C true CA1305859C (en) | 1992-08-04 |
Family
ID=4138975
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA000581150A Expired - Lifetime CA1305859C (en) | 1988-10-25 | 1988-10-25 | Centerless grinder construction |
Country Status (1)
| Country | Link |
|---|---|
| CA (1) | CA1305859C (en) |
-
1988
- 1988-10-25 CA CA000581150A patent/CA1305859C/en not_active Expired - Lifetime
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US4783932A (en) | Centerless grinder construction | |
| US2070944A (en) | Method and apparatus for finishing surfaces | |
| CA1305859C (en) | Centerless grinder construction | |
| US4441280A (en) | Device for centerless grinding of rotation-symmetrical surfaces on work pieces | |
| US5613899A (en) | Centerless ceramic ferrule grinder | |
| US2466478A (en) | Grinding machine | |
| US5012617A (en) | Dual purpose grinding machine | |
| KR20030051133A (en) | A machine for polishing pipes | |
| US2073079A (en) | Lapping machine | |
| WO2022071190A1 (en) | Roller grinding device and carrier | |
| US5384983A (en) | Method and grinding machine for the internal grinding of bores | |
| CN219053930U (en) | Abrasive belt grinding machine capable of changing abrasive belt angle through adjusting shaft | |
| US2922258A (en) | Grinder with oscillating head | |
| US2487949A (en) | Drive mechanism for grinding wheels | |
| US3029374A (en) | Method and apparatus for automatically adjusting the torque demand on a rotary motor | |
| US4384433A (en) | Abrading device | |
| US1421205A (en) | Work holding and feeding device for grinding or polishing machines | |
| US4184293A (en) | Roll neckrest support | |
| JP4570923B2 (en) | Method for polishing blades of a rotary cutting device and rotary cutting device for carrying out this method | |
| CN219521735U (en) | Installation mechanism of grinder roller | |
| US3783561A (en) | Constant surface speed grinder | |
| JP4511255B2 (en) | Centerless grinding machine | |
| US3924359A (en) | Centerless grinder with hydraulic drive | |
| EP0265953A2 (en) | Apparatus for grinding a workpiece | |
| US1976035A (en) | Grinding machine |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| MKLA | Lapsed |