US3541738A

US3541738A - Orbital finishing machine

Info

Publication number: US3541738A
Application number: US721433A
Authority: US
Inventors: John F Rampe
Original assignee: JOHN F RAMPE
Current assignee: JEPMAR RESEARCH; JOHN F RAMPE
Priority date: 1968-04-15
Filing date: 1968-04-15
Publication date: 1970-11-24
Anticipated expiration: 1987-11-24
Also published as: FR2006229A1; GB1212307A; DE1919151A1

Description

Nov.24, 1970 J.. 3,541,738

ORBITAL FINISHING MACHINE Filed April 15, 1968 6 Sheets-Sheet l 1 -r m (\r 4 TTOIZNE Y5 Nov. 24, 1970 J. F. RAM PE ORBITAL FINISHING MACHINE Filed April 15, 1968 6 Sheets-Sheet 5 INVENTOR. JOHN F- PAM/ E BY Nov. 24, 1970 .1. F. RAMPE ORBITAL FINISHING MACHINE I 6 Sheets-Sheet 4 Filed April 15, 1968 N, m t Kw I 1 L w.

ATTORNEYS.

Nov. 24, 1970 J. F. RAMPE 3,541,738

ORBITAL FINISHING MACHINE V Filed April 15, 1968 6 Sheets-:Sheet 5 INVENTOR.

l-IN F. PAM/ E Nov. 24, 1970 J. F. RAMPE ORBITAL FINISHING MACHINE 6 Sheets-Sheet 6 Filed April 15, 1968 Fig. 9

. 1 L J'UPI'U W I .5 M WW /M A, v. H 1 Y rB M v m A 7'TOZNE Y5.

United States Patent O 3,541,738 ORBITAL FINISHING MACHINE John F. Rampe, 3417 Fairfax Road, Cleveland Heights, Ohio 44118 Filed Apr. 15, 1968, Ser. No. 721,433 Int. Cl. B241) 31/00 US. Cl. 51-163 11 Claims ABSTRACT OF THE DISCLOSURE A precision finishing machine of the orbital type making use of a multiplicity of vibration-inducing units wherein there is a plurality of units on each of the two long sides of the machine. On each side, the units are arranged in overlying or superimposed relationship. At each level, there may be one, two or more units. By mounting the units in tandem at the same level, the length of the machine and its capacity may be increased without exceeding the bearing load limits. The vibration-inducing units on both sides of the machine are preferably driven in timed relation.

RELATED CASES This invention deals with a precision finishing machine of the orbital type characterized by generally circular movement of the finishing media. It constitutes an improvement on precision finishing machines of kinds heretofore known. Such are described, for example, in pending application Ser. No. 534,710, new Pat. No. 3,449,869, and in prior Pats. Nos. 3,191,347, 3,191,348, 3,230,671, 3,300,908, 3,337,997 and 3,339,316, all in the name of John F. Rampe.

BACKGROUND OF THE INVENTION The various types of orbital finishing machines heretofore employed in the precision finishing of workpieces of metal, plastic or the like have been used mainly (largely because they are relatively expensive) in instances in which the goods do not lend themselves to finishing by the more conventional methods of grinding, bui'fing and polishing. A major object of the present invention is the provision of a precision finishing machine that will accomplish to even better advantage the purposes and objectives for which the orbital finishing machines of the prior art have commonly been used.

To that end, the invention provides a heavy-duty precision finishing machine of the orbital type which is so designed, constructed and arranged that it is not limited to the precision finishing of goods not readily finished by the commonly employed methods of grinding, bufling and polishing. On the contrary, it is one which lends itself to use in the large scale finishing of goods that heretofore have normally been finished by just such methods. What the invention provides, therefore, is a heavy-duty machine of a kind for which there is a broad market, broader than that for orbital finishing machines of the types commercially available up to the present time.

By providing a plurality of vibration-inducing units (vibratory units) on each of the two long sides of the machine, preferably at different levels, the number of such units and therefore the potential capacity of the machine may be increased without exceeding the load capacities of the bearings. Heretofore, the latter has been a limiting factor tending to hold down the size of heavyduty finishing machines of the orbital type. In general, such machines have used but a single vibratory unit, two at the most. In eflect, machine capacity has been restricted by the capacity of the bearings. By using a 3,541,738 Patented Nov. 24, 1970 multiplicity of vibratory units operating in timed relation to each other, the way has been opened to enlargement of the size and therefore of the potential capacities of such machines.

BRIEF DESCRIPTION OF DRAWINGS Objects, advantages and features of the invention will be apparent from the description which follows and from the accompanying drawings, in which:

FIG. 1 is a side elevation of a precision finishing machine of the orbital type incorporating the features of the present invention;

FIG. 2 is an end elevation of the same machine;

FIG. 3 is a section on line 33 of FIG. 1;

FIG. 4 is a partial section on line 4--4 of FIG. 2 showing details of parts seen in elevation at the righthand end of FIG. 1;

FIGS. 5, 6 and 7 correspond to FIGS. 1,2 and 3, respectively, but deal with a modification of the machine shown therein;

FIG. 8 is a side elevation, with parts broken away, of a further modification; and

FIGS. 9 and 10 are sections on lines 99 and 10-10 of FIG. 8.

PREFERRED EMBODIMENTS OF THE INVENTION In the embodiment of the invention illustrated in FIGS. 1 to 4, the finishing machine as a whole is designated 1. The supporting structure consists, along with other structural elements, of a horizontal base 2; a vertical end plate 3, seen in FIG. 2; a pair of vertically disposed plates 4 each of which is cut away to the extent indicated by the dotted lines in FIG. 3; and, at the opposite end of the machine, a like pair of vertically disposed cut-away plates 5 held to each other by transverse channels 6. Longitudinally extending channels 7, seen in FIG. 1, connect cut-away plates 4 and 5 a short distance below their mid-portions.

At the top of the machine, channels 8 connect

corresponding plates

4 and 5 on the near and far sides of the machine.

Plates

3 and 4 are connected at the top of the machine by short channels 9 and, at the level of channel 6, by short channels 10. See FIGS. 1 and 3. Diagonal braces are used for stiffening as indicated in FIG. 1. Also forming part of the framework of the machine are tie rods 11, of which there are two, one on each side of the machine.

Rubber-in-shear mounts 12, of which there are eight in all, are supported at their inboard ends by

plates

4 and 5. At the right-hand end of the machine, seen in FIG. 1, the outboard ends of mounts 12 are carried by a square supporting plate 13. At the lefthand end of the machine, the outboard ends of the mounts are carried by a U-shaped plate 14.

Plates

13 and 14 serve as end pieces for receptacle 15, commonly referred to as a tub.

For the most part, tub 15 is generally cylindrical in transverse cross section; however, at the top the generally cylindrical contour of the tub is interrupted by vertical flanges 16 that define an elongated opening extending lengthwise of the tub from one end to the other. Media and workpieces are introduced into the tub through this opening and are discharged at the left-hand end of the tub through a bottom opening leading into a dis charge chute 17. During the operating cycle, a vertical door 18 slideably mounted in a frame 19 keeps the contents of the tub from discharging prematurely.

For convenience in describing the manner of operation of the machine of FIGS. 1 to 4, the vibratory units will be dealt with first, after which the drive trains will be described in a sequence opposite to that by which power flows from the prime mover to the vibrators.

Whereas orbital finishing machines of the kinds known to the prior art have commonly had a single vibratory unit operating directly or indirectly on the tub and whereas the finishing machine disclosed in prior application Ser. No. 534,710 has two such units, each at the level of the center of mass, the finishing machine of FIGS. 1 to 4 has a total of six vibratory units, three of which appear in FIG. 1. This use of a multiplicity of vibratory units, each attached directly to the tub, makes it possible to increase the length of the tub in relation to the cross-section and therefore to increase the number of workpieces being finished at any given time. In installations characteristic of the prior art, tub capacities have been sharply limited by the load-bearing capacities of the bearings used in or with the vibratory units. What is shown in FIG. 1 is a machine wherein the provision and conjoint use of a multiplicity of vibratory units gives rise to a structure in which each unit contributes to the end result of producing a large volume of finished workpieces of high quality.

In a machine equipped with a multiplicity of vibratory units, such as that shown in FIGS. 1 to 4, the vibratory effect is multiplied and the capacity of the machine is greatly increased, yet the load on any given pair of bearings is never excessive. As in the orbital finishing machine of the abovementioned prior application, there are two assemblies at the level of the center line of the tub, one on each side. Designated 20 in FIGS. 1 and 3, each includes an inverted channel 21, best seen in FIG. 3, that is securely welded to the cylindrical portion of tub 15. Mounted on inverted channels 21 are elongated bearing yokes 22, usually one on each channel, but, as will appear hereinafter, sometimes more than one.

At the opposite ends of the two bearing yokes 22, of which there is one on each side of the tub, are bushings 23 equipped with antifriction bearings. Disposed therein are longitudinal shafts 24 terminating in flexible couplings 25. Each of the two shafts carries an eccentrically mounted weight 26. If the weights are properly paired; i.e., so disposed as to augment and not oppose each other, rotation of shafts 24 tends to produce a smooth, rhythmic vibration in tub and its contents.

Mounted above and below assemblies in the generally superposed relationship illustrated in FIG. 3 are assemblies similar to assemblies 20.

Eccentrics

27 and 28 are mounted therein on shafts similar to shaft 24 that are themselves supported in bearings similar to those in bushings 23. Bearing yokes on inverted channels are employed to mount

eccentrics

27 and 28. Each eccentric coacts and cooperates with a paired eccentric on the opposite side of the machine. See FIG. 3.

Turning now to the power trains, openings 29 in plates 4 and cut-away portions 13a in end piece 13 enable extension shafts 30 to connect

flexible couplings

25 and 31 to the end of transmitting power from the latter to the former and thus to the shafts in the vibratory units. To the right of the several flexible couplings 31, seen as in FIG. 1, short shafts 32 extend into gearboxes 33 mounted on end plate 3 by means of laterally etxending flanges 33a. Gearboxes 33 and flanges 33a are to be seen in FIGS. 1 and 2, from which it will be evident that shafts 32 are reduced in diameter mid-way of their lengths. Reduced portions 34 project into and terminate in bosses 35 on the outboard ends of gearboxes 33. Beveled gears 36 and 37, the former seated on the shoulders formed on shafts 32, occupy the central portions of the gearboxes.

Radially extending shafts 38, seen in FIG. 2, emerge from gearboxes 33 through bosses 39 and extend thence into flexible couplings 40 wherein they are joined to other radially directed shafts 41. The latter continue inward toward the central axis of tub 15, passing through bosses 42 into a central gearbox 42, best seen in FIG. 4. Gearbox 43 has arcuate flanges 44 (FIG. 2) by which bolts 45 passing through supporting element 46 (FIG. 4) hold the gearbox in place on plate 3. Within gearbox 43 are the bevel gears 47 and 48, of which the former are mounted on radial shafts 41 and the latter is mounted on a horizontal shaft 49 of which one end extends into a bearing assembly 51 in a sleeve 52 forming part of supporting element 46. A cover plate 53 provides access to bearing assembly 51.

The opposite end of horizontal shaft 49 emerges from gearbox 43 as shown in FIG. 4, passing through a hearing assembly 54 and a shaft seal 55. Respectively, the latter are mounted on, the inside and outside faces of the exposed end of gearbox 43. Shaft 49 terminates in a flexible coupling 56, wherein it is joined to a second horizontal shaft 57 entering coupling '56 from the opposite side. Shaft 57 is supported between its ends in a pillar bearing block 58 mounted on a platform 59 carried by structural elements 60 and 61. The outboard end of the shaft terminates in a boss 63 forming part of a driven gear 62 the teeth of which mesh with the cleats 65 on an endless timing belt 64. Belt 64 is driven from a drive gear 66 on shaft 67 of motor 68, see FIG. 1.

Motor 68 is the prime mover from which power is transmitted, in turn, to central gearbox 43, satellite gearboxes 33, and the six vibratory units on tub 15 typified by assembly 20. Motor 68 is carried by a base 69 mounted for adjustment, by means of rack 70, on a raised table 71 bolted at 72 to a support 73 that is itself bolted to the foundation of the machine as a whole. By rotating handwheel 74 in the proper direction, base 69 of motor 68 may be moved to the left or right, seen as in FIG. 2, thereby tightening or loosening belt 64 as needed.

The finishing machine of FIGS. 1 to 4 is one in which the inclusion of

flexible couplings

25, 31, 40 and 56 gives a system in which the drive system components, which in general are those at the right-hand end of the machine as seen in FIG. 1, are substantially free from the effects of vibration. It is evident that without such safeguards, a multiplicity of vibratory units, six in the machine of FIGS. 1 to 4, would have unacceptable effects on shafts and gears. Nevertheless, by using individual gearboxes and providing flexible couplings as described, it is entirely feasible to operate all six of the vibratory units simultaneously in accurately timed relation to each other.

FIGS. 5, 6 and 7 have to do with a modification of the previously described machine in which the machine embraces a total of twelve vibratory units, six on each side. In the interests of simplicity, reference numerals below 18 designate parts that are identical with similarly numbered parts in FIGS. 1 to 4. From FIGS. 6 and 7 it will be evident that, on each side of the machine shown in elevation in FIG. 5, there are vibratory units which are in generally superposed relation. As will appear and as shown in FIG. 5 itself, each assembly includes two vibratory units disposed in tandem.

On and at approximately the level of the center line of tub 15, viewed as in FIG. 5, is an assembly 75 that includes an elongated inverted channel 76 capable of accommodating two individual units in end-to-end relation. Each such unit consists, among other things, of an elongated bearing yoke (77 and 78) the ends of which take the form of bearing blocks (79 and 82) housing bushings provided with suitable antifriction bearings. The shafting, which term is used to embrace aligned shafts and 83, is substantially co-extensive with inverted channel 76.

In assembly 75,

shafts

80 and 83 carry eccentrically mounted weights 81 and 84 of the type already described in connection with the embodiment of the invention shown in FIGS. 1 to 4. Above assembly 75 a similar assembly is mounted on tub 15. Below it is another such assembly, likewise mounted on tub 15. See FIGS. 6 and 7 as illustrating the superposed relation of the three assemblies on each side of the machine.

Flexible couplings '85 are employed as shown in FIG. 5 between the two units on each yoke. Three similar couplings '86 are located adjacent plates 4. Three other flexible couplings, designated 88, are located immediately to the left of plate 3. Shafts 87 connect couplings 86 and '88, passing through cut-away areas 89' in end plate 13 of tub 15. By this arrangement, vibrations produced by the vibratory units are prevented from disrupting the drive system.

To the right of plate 3, seen as in FIG. 5, is supporting structure that is not present in the machine of FIGS. 1 to 4. The additional supporting structure consists of an end plate 90, two upper channels 91 and two lower channels 92.

Channels

91 and 92 serve to connect plate 90 with plate 3. In the space between the two plates is most of the mechanism required for driving the dual vibratory assemblies on each of the two long sides of the machine. As will appear below, near-side components 109 to 124 (all of which will be described hereinafter) figure in downward transmission of power from the top level to the middle level and from the middle level to the bottom level.

In general, it can be said that the physical disposition of the components employed between

plates

3 and 90 is the same on both sides of the machine; however, the direction of power transmittal is opposite on the near and after sides.

Referring now to the view showing the machine in end elevation, FIG. 6, it will be noted that electric motor 93, which serves as the prime mover, is on the far side of the machine, viewed as in FIG. 5. Motor shaft 94 carries a gear 95 through which, with the aid of a cleated belt 96, power is communicated to a like gear 97 on outwardly projecting shaft 98. Like motor 93, gears 95 and 97, belt 96 and horizontal shaft 98 are all on the far side of a central vertical plane passing lengthwise through the machine. In order to simplify the explanation of the manner of operation of the drive system, FIG. 7 includes a series of letters A, B, C, D, E and F each of which designates what may be described as a station in the power transmission system.

Referring first to station A, power from belt 96 and gears 95 and 97 turns shaft 98, which is supported by spaced outer and inner bearing housings similar to those appearing in section in FIG. 5. In FIG. 6, gear 97 obscures the outer bearing housing: In FIG. 7, only the flange of the inner bearing housing, designated 99, appears. Mounted on shaft 98 between the two bearing housings is a gear 100 from which a cleated belt 101 transmits power to a simlar gear 102 at station B.

Gear 102 is mounted on a shaft 103 which likewise is supported by spaced outer and inner bearing housings as at 104. Power is transmitted between stations B and C by a cleated belt 105 and two gears similar to those just referred to, both of which are obscured by other parts appearing in FIG. 7. At station C, shaft 106, which likewise is supported by spaced bearing housings, carries a second gear, shown in FIG. 7, designated 107. Gear 107 serves to transmit power from one side of the machine to the other through the intervention of a transversely extending cleated belt 125.

On the near side of the machine, at station D, gear 109 receives power from belt 125, transmitting it in turn to shaft 110: see FIG. 5. Shaft 110 is supported in spaced bearing housings 111 and 112. A second gear 113 on shaft 110, through the intervention of a cleated belt 114, transmits power to a like gear 115 on shaft 116 (station E). Shaft 116, supported in bearing housings 117 and 118, is provided with a gear 119 which, acting through cleated belt 120, transmits power to gear 121 (station F).

Bearing housings

123 and 124 at station F support the end portions of shaft 122, on which gear 121 is mounted.

From the foregoing, it will be understood that power developed by motor 93 is transmitted counterclockwise from station to station, first upward on the right-hand side of the machine as seen in FIGS. 6 and 7 and then downward on the opposite side. All of the belts employed in the machine are cleated belts cooperating with cleated gears. Thus all of the rotating parts of the mechanism from shaft 94 on motor 93 to gear 121 on shaft 122 are enabled to operate in timed relation to each other. As a result of the use of flexible couplings elsewhere in the machine, this relationship is not disrupted, notwithstanding the use of twelve vibratory units on the tub itself.

In FIGS. 8 to 10, which. deal with a finishing machine characterized by a cylindrical tub 126 that is capable of being continuously charged at one end and continuously discharged at the other, components bearing'reference characters up to 92 are substantially the same as similarly designated components in previously described embodiments of the invention. To show the construction of the tub, FIG. 8 is broken away at one end and again near the middle of the figure. It will be noted that the cylindrical interior of the tub is protected by a thick layer 127 of rubber or a rubber-like material. Such protection is particularly advantageous in a heavy-duty finishing machine.

When first readied for use, tub 126 is loaded through hopper 128 the lower portion of which is open and in registry with vertical opening 129 in plate 13. After the machine has been put in operation, media and workpieces are introduced more or less continuously through hopper 128. They follow a generally helical course from the zone wherein they enter the tub to the zone wherein they leave it. At the discharge end of the tub, door 18, illustrated in closed position, is of course raised while the machine is in continuous operation.

As can be seen in FIG. 8, inner bearing housings 130 are used to support shafts 131 that extend from couplings 88 on one hand to couplings 132 on the other. Couplings 132 serve to join shafts 131 to shafts 133, each of which mounts an independently operating electric motor 134. On each side of the machine, there are three such motors, one for each two-unit vibratory assembly. By virtue of the use of gears 135 and a cleated belt 136, all six operate in synchronism.

The use of physically independent motors makes for a simpler power transmission system than either of those previously described. Apart from the fact that the use of flexible coupling prevents interference from vibrations induced by the vibratory units, a system of individual drive motors has a further advantage; namely, that after continuity of flow'through the tub has been established, it will not always be necessary to use all of them at any one time. Once the pattern has been established, paired motors may be disconnected from the source of power and allowed to idle. The remainder, still connected to the power source, continue to supply sufiicient energy to vibrate the tub and its contents. This conserves power and reduces the cost.

As a result of the increased length of the tub in relation to its cross-section, the productive capacity of the finishing machine of FIGS. 8 to 10 is enhanced for reasons mentioned in connection with the previously described embodiments of the invention. As there brought out, the use of vibratory units in superposed relation to each other, preferably in tandem, permits of greater through-put and makes for improved eificiency. Because of the fact that the machine of FIGS. 8 to 10 can be operated on a continuous basis, its productive capacity is greatly enhanced over what would otherwise be the case.

In the practice of the invention, whether it be in the form of the first, second or third of the three embodiments, it is not necessary to use eccentrics of the type shown; that is to say, shaft-supported weights. Other vibration-inducing components may be used instead, including magnetic and pneumatic vibration-inducing units. In each case, the forces exerted by the vibration-inducing units should not be so directed as to oppose each other. Synchronization is decidedly helpful in making sure that vibratory units in opposite parts of the machine act in harmony.

It is intended that the patent shall cover, by summarization in appended claims, all features of patentable novelty residing in the invention.

What is claimed is:

1. A precision finishing machine characterized by orbital movement of the finishing media comprising supporting structure; a receptacle resiliently carried by the supporting structure; a plurality of superposed vibratory units in juxtaposition to the receptacle on each of two opposite sides thereof; and means for driving the vibratory units in timed relation to each other.

2. A precision finishing machine according to claim 1 wherein there are at least three vibratory units on each of the two opposite sides of the receptacle.

3. A precision finishing machine according to claim 1 wherein, on each of said opposite sides, the several vibratory units are mounted on the side walls of the receptacle itself.

4. A precision finishing machine according to claim 1 wherein the driving means take the form of a motor and a series of belts driven seriatim in timed relation to each other.

5. A precision finishing machine according to claim 4 wherein the driving means take the form of a central gearbox and a plurality of satellite gearboxes connected to said central gearbox.

6. A precision finishing machine according to claim 1 wherein the driving means include a plurality of physically independent prime movers operating in synchronism.

7. A precision finishing machine according to claim 6 wherein said physically independent prime movers are 8 paired on opposite sides of a vertical plane passing through the central axis of the receptacle.

8. A precision finishing machine characterized by orbital movement of the finishing media comprising supporting structure; a receptacle resiliently carried by the supporting structure; a plurality of superposed shaftsupported eccentrics mounted on each two opposite sides of the receptacle with the longitudinal axes of the shafts disposed in parallelism to the longitudinal axis of the receptacle; flexible couplings connected to the shafts at the driven ends thereof; and a drive system connected to said couplings.

9. A precision finishing machine according to claim 8 wherein the drive system takes the form of a motor and a series of belts driven seriatim in timed relation to each other.

10. A precision finishing machine according to claim 8 wherein the poWer system includes a central gearbox and a plurality of satellite gearboxes connected to said central gearbox.

11. A precision finishing machine according to claim 8 wherein the drive system takes the form of a plurality of electric motors operating in synchronism with each other.

References Cited UNITED STATES PATENTS 3,021,082 2/1962 Sullivan 241 FOREIGN PATENTS 899,573 12/1953 Germany.

HAROLD D. WHITEHEAD, Primary Examiner