Machine Element Alignment Positioner

Abstract

A compact portable positioner includes a movable table on a main body with ball bearing means between the table and the body for allowing precise transverse and/or longitudinal movement in the horizontal plane. Lifting means support the main body to provide the third dimensional adjustment so that movement of the table in either plane does not upset previous adjustment. The ball bearing means comprises a plurality of balls held captive by an apertured plate means held in a frame of suitable resilient material, such as polyethylene foam. The frame is attached to the table and the body to provide biasing means for urging the table to the home position. Adjusting and fixing means in the horizontal plane preferably includes opposed jackscrews and may include nonparallel vertical cam surfaces and jackscrews having frusto-conical terminal ends. The lifting means may be mechanical screws resting on indented bearing plates, or alternatively hydraulic lift cylinders with a control circuit having check valves and bypasses to effect operation.

Description

The present invention relates to an alignment positioner for machine elements or the like, and more particularly, to a positioner that is portable and provides horizontal and vertical adjustments without affecting previous vertical and horizontal adjustments, respectively.

BACKGROUND OF THE INVENTION

The alignment of machinery and machine elements is a critical and highly complex procedure. Particularly with large electric motors or similar drivers that must be positioned to drive machines, such as large rotary or centrifugal pumps, fans or the like, the output shaft of the motor must be closely aligned (that is, within a few thousandths of an inch) with the input shaft of the driven machine. With such alignment, the conventional flexible coupling is operative to take care of the remaining difference and provide an acceptable driving connection. In the past, the alignment of the machine elements, such as the driver and driven shafts, has been carried out by either using built-in jacking devices or an array of common hand tools and devices in a very inefficient manner.

As to the built-in arrangement, transverse and longitudinal jackscrews are mounted on the driver baseplate or soleplates, to exert force against driver feet and thereby permit precise movement in the desired direction in the horizontal plane. Built-in vertical jackscrews are also sometimes employed, arranged to lift the driver for insertion or removal of shims between the driver feet and supporting surfaces. Such jackscrews work reasonably well, but require that a certain procedural order be followed, i.e., vertical adjustments first, then horizontal adjustments, repeated until desired alignment accuracy is achieved. This is because vertical adjustments can and usually do cause some horizontal movement, but horizontal adjustments do not affect vertical positioning, which is controlled by the shims. The main disadvantage of built-in jackscrews is their cost, since they must be welded or otherwise attached to the machine feet or supporting baseplate and become integral with one machine only, thus requiring a separate set for every machine. A further disadvantage is the difficulty in their field installation. If not equipped with jackscrews before field installation, limited access or hot-work restrictions may preclude their later addition in the field.

Where permanent jackscrews are not installed, the common tools that are used include portable clamp-on jackscrews, portable hydraulic jacks, wedges, pry bars, cranes, hoists, and sledge hammers. Usually a combination of several such tools is required to move a large driver vertically and horizontally for alignment adjustment. Lack of precision, excessive time required, and danger to machinery and personnel, are common disadvantages of such adjustment means.

One requirement for providing precise adjustment in any precision machine element positioner is the provision of a low friction bearing between the main body of the positioner and the movable table. Heretofore, one type of low friction bearing in such an apparatus required the provision of a quantity of grease between the main body and movable table. The grease in such an apparatus is confined to the area between the main body and movable table with an O-ring. The grease must be injected via an external high pressure gun, and allowed to exhaust at the completion of each usage. Although satisfactory as a bearing the grease injection and removal requirement is somewhat inconvenient and messy. Such a system is disclosed in U.S. Pat. No. 3,578,281.

I have previously devised a plotting system that is useful in drastically cutting the time of the trial and error operations using the common hand tools of the past, as described above. This system allows the installer to take a few simple measurements, plot them on a board and then read from the board the movements necessary to bring the two shafts or elements into alignment. This invention entitled "Machine Element Alignment System" is disclosed and claimed in my previous U.S. patent application, Ser. No. 227,525, filed Feb. 17, 1972, now U.S. Pat. No. 3,789,507. Thus, this plotting system has greatly alleviated the difficulty with aligning machine elements and has reduced the cost and time involved. But prior to the present invention, the non-specialized hand tools still had to be used in order to move the motor or other machine element into position. Thus, even after developing the plotting system of my previous invention, there was a need for a portable mechanical device that could be easily positioned in the small vertical space under the machine element with jacking devices to be actuated to lift the element in the vertical direction to provide the Y axis adjustment of the output shaft, and with separate adjusting means to be actuated to provide the necessary X and Z adjustment in the horizontal plane. Once the aligned position is reached, the permanent supports, including shims, if necessary, could be placed under the feet of the machine, the machine bolted down and then the positioners removed for use at another time.

OBJECTIVES OF THE INVENTION

Thus, it is one object of the present invention to provide a new, specialized tool for positioning a machine element or the like in the vertical, as well as the horizontal planes.

It is still another object of the present invention to provide an alignment positioner of the type described wherein the vertical positioning step does not affect the horizontal positioning step so that previous adjustments are not upset.

It is still another object of the present invention to provide a machinery alignment positioner that is substantially universal in use, is safe and easy to use, is compact and portable, and has a low initial cost factor since its cost may be prorated over a great number of machines which it will be used to align.

It is still another object of the present invention to provide a combined vertical and horizontal positioner utilizing vertical screws resting on indented bearing plates for the Y-axis adjustment, or alternatively hydraulic lift cylinders, and a ball bearing supported table for precise adjustment along the X and Z axes.

BRIEF DESCRIPTION OF THE INVENTION

The positioner of the present invention includes a main body, a movable table providing the support for the machine to be aligned, high strength ball bearing means for allowing precise movement of the table on the body in the horizontal plane and mechanical or hydraulic jacking means attached to the body for the vertical alignment. The positioners are preferably used in pairs beneath the machine and preferably two mechanical or hydraulic jacking devices are attached to each body. The positioners are placed under the machine at any location spaced from the area of the machine feet so that the machine is safely balanced during the alignment procedure. Lifting means can be either mechanical, such as jackscrews resting on indented bearing plates, or hydraulic, such as cylinder rams actuated by external hydraulic pressure means. The choice will be determined by factors such as weight to be raised, available space, and number of machines to be aligned. The various lifting methods cited are equally applicable without departing from the broad aspects of the present invention.

In both embodiments illustrated, jackscrews threadedly engage the main body in opposed relationship across the table and are operated to adjust and fix the table in any horizontal position, when the full weight of the machine to be aligned is being carried by the positioners. Care should be taken to see that the machine being aligned is completely picked up so as to satisfy this full weight supporting requirement, since a dragging foot of the machine makes horizontal movement difficult, if not impossible. That is, two opposing screws on the sides of the positioner are operative to move the machine so that the extending shaft to be aligned is moved along the X axis. The Z axis alignment, that is the movement of the shaft toward and away from the desired point, i.e., the end of the shaft to which it is to be aligned, is accomplished by opposed jackscrews at the front and the rear of the positioner device. Alternatively, or in supplement to these positioners, at least two non-parallel vertical cam surfaces can be used for the horizontal positioning step, especially where access at the sides of the positioner is restricted.

The movable table is positioned for precise directional movement in the X and Z senses, on a bed of bearing balls. These bearings are held by an apertured horizontal spaced plate means and a frame of polyethylene foam or other suitable resilient material extends around the same. The frame not only serves to seal the space that houses the bearing balls, but is fixedly attached to the table as well as the main body so that as the table is moved in one direction or the other a bias is provided to allow return of the table to the home position when the vertical loading force is released. The resilient frame also serves to lift the table free of the bearing balls when no load is applied, thus facilitating return of the ball bearing assembly to the home or center position.

The mechanical screw lift system of one embodiment is preferably made from stationary vertically threaded apertures in outboard projections or blocks attached to the main body at each of its two sides, into which are screwed vertically extending jackscrews having convex bottom ends. The ends mate with indentations on flat horizontal bearing plates which rest on the baseplate or foundation beneath the machine element to be adjusted for alignment. Gradual adjustment of the two screws causes the positioner to raise and lower said machine element for Y-axis adjustment.

As stated above, the positioners are normally used in pairs and the second positioner of the pair, situated at the other end of said machine element, is adjusted equally and at the same time. The two positioners can be adjusted in successive small steps to avoid significant inequality, thus raising or lowering said machine element while maintaining it level. Support via the aforementioned indented bearing plates, assures absence of undesired horizontal movement or "walking" as the jackscrews are adjusted. Other mechanical lifting or jacking systems, such as ratcheting rack-and-pawl devices, or rack-and-pinion devices, could be used without departing from the broad aspects of the present invention.

The hydraulic lifting system which can be used as an alternative to the mechanical system hereinbefore described, is preferably made with hydraulic lifting cylinders or rams attached to the main body in place of the jackscrews described previously, and with the bearing plates omitted. The ram pistons are caused to move vertically through the open lower ends of their respective cylinders formed in the mounting blocks, thus raising and lowering the positioners as desired, in order to effect the Y-axis positioning. Hydraulic pressure is imposed by means of a pump or pumps working through a control circuit, such pumps being conventional piston types; or alternatively the pumps may be hydraulic rams with external force applied mechanically through a linkage mechanism, oppositely acting rams with force applied by screw mechanisms and a single pump, or other suitable means, to effect the necessary equalized raising and lowering movements at all four support positions.

Still other objects and advantages of the present invention will become readily apparent to those skilled in this art from the following detailed description, wherein I have shown and described only the preferred embodiments of the invention, simply by way of illustration of the best modes contemplated by me of carrying out my invention. As will be realized, the invention is capable of other and different embodiments, and its several details are capable of modification in various obvious respects, all without departing from the invention. Accordingly, the drawings and description are to be regarded as illustrative in nature, and not restrictive.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a perspective view of a motor lifted and aligned by a pair of positioners constructed in accordance with the present invention;

FIG. 2 is a top view of a positioner constructed in accordance with the present invention with a portion of the support table cut away for clarity;

FIG. 3 is a cross-sectional view taken through FIG. 2 and following lines 3--3;

FIG. 4 is a schematic showing of the hydraulic system for operating the tandem positioners of the invention as shown in operation in FIG. 1;

FIG. 5 is a detailed schematic of one of the control circuits that is used in the hydraulic system of FIG. 4 in accordance with the teachings of the invention;

FIG. 6 shows a schematic diagram of an alternative hydraulic circuit utilizing oppositely-acting rams and screws; and

FIG. 7 is a cross-sectional view of an alternative screw lift system that may be substituted for the hydraulic means shown in the foregoing figures.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT

In FIG. 1, there is shown a motor M that represents the type of machine element that may be readily aligned by preferably using a pair of alignment positioners 10. A single positioner (not shown), utilizing three or four lifting points rather than the normal two, could be used in special cases where shortness of the machine element to be aligned provides insufficient space for the preferred arrangement of a pair of positioners. In such case, said single positioner must be placed beneath said machine at or near its center of gravity. In the specific instance as illustrated, the pair of positioners 10 is arranged in tandem on the mounting surface 11. Cradling wedges W on the positioners support the housing of the motor M spaced from the permanent mounting stand or feet 12. The motor M has an output shaft 13 with connecting collar 13a that is to be aligned with the corresponding input shaft 14 and connecting collar 14a for the driven machine. As shown in this Figure, the positioners 10 have been raised for vertical positioning of the motor M and the support for the wedges W directly supporting the motor has also been shifted to determine the proper horizontal location. The illustrated space between the collars 13a, 14a is the orientation when flexible members are included between the collars to make a flexible coupling. Thus, and as will be seen in further detail later, the shaft and coupling 13, 13 a may typically be lifted for alignment along the Y axis (up and down); then it may be shifted horizontally along the Z-axis (in and out); and then finally along the X-axis (from side to side) in order to provide the alignment desired between the coupling collars 13a, 14a. In performing the Y-axis alignment the positioners actually first lift the motor slightly higher than necessary for reaching the Y-axis alignment position, whereupon shims are inserted or removed beneath the motor feet in designated area A (FIG. 1). The positioners are thus in the Y-axis, primarily a jacking means to allow the required shim insertion under the feet of the machine element; the shims themselves thereby providing the precision. Although the use of the apparatus of the present invention for alignment of the shaft 13 of large electrical motors, such as the motor M, with any input shaft 14 is particularly advantageous, it is to be understood that use with other types of machines or devices is contemplated. Furthermore, other uses, such as where precise positioning of a workpiece with respect to a machine tool is necessary, will readily occur to those skilled in the art.

Thus, it will be readily apparent that once the position desired is reached, as shown in FIG. 1 and just described, the permanent support shims or plates (not shown) are placed under the machine feet 12 in the designated area A. After bolting down the motor M, it is then permanently attached to the surface 11.

A top view of the alignment positioner 10 of the present invention is shown in FIG. 2. This figure considered in conjunction with the cross-sectional view of FIG. 3, now allows a more detailed description of the specific mechanical structure to be given. Thus, a main body 15 is generally bowlshaped and may be machined from a steel block or forging, or fabricated in any other conventional manner, such as by welding individual parts together. On the sides of the body 15, there are provided shoulders 16, 16a that cooperate with lift blocks 17, 17a; it being understood that the blocks are identical and thus only one need be discussed. A strap 18 holds the block 17 in position under the shoulder 16 for support of the body 15; the strap being fixed on the main body 15 through a suitable number of anchoring bolts (not numbered). Within the lift block 17 is a hydraulic pressure chamber 19 that is fed with pressurized fluid through the channel 20 (see FIG. 2) extending from the coupling 21. Positioned within the chamber 19 is the movable piston P resting on spacers 22 (see FIG. 3). It should thus be realized that when the chambers 19, 19a are provided with hydraulic fluid under pressure the lift blocks 17, 17a are lifted, which in turn, lifts the main body 15, thereby raising the motor M for alignment along the Y axis, and transferring motor weight to the positioners so that horizontal Z and X axis alignment adjustments can be made.

Situated within the enclosure of the main body 15 is the supporting table 25, as best shown in FIGS. 2 and 3. The base for the table is made up of an upper plate 26 and a lower plate 27. These plates 26 and 27 are premanently attached by epoxy, for example, to the table 25 and the bottom of the body 15, respectively. The opposed faces, which are hardened and ground flat, serve as engaging surfaces for the ball bearing means that accommodates the horizontal movement; i.e., the movement in the directions of the X and Z axes. This ball bearing means is preferably made up of a plurality of balls 29 that are spaced over substantially the full expanse of the opposed faces. The balls 29 are held in their spaced positions by apertured plate means, preferably a pair of juxtaposed plates 30, 31 (see FIG. 3). The plates 30, 31 have the apertures formed therein to receive the balls shaped on a taper so that the interface of said plates is maintained along the horizontal center axis of the balls 29. As will be evident, when a load, such as the motor M is placed on the table 25, the upper plate 26 is lowered and rests on the top of the balls 29, whereby the motor M is supported for movement along the X or Z axes, or in any direction in the horizontal plane in between.

Surrounding the ball bearing means including the balls 29, there is provided a resilient frame 35. This frame is preferably made of polyethylene foam so as to be resilient and capable of distortion for purposes that will be presently evident. The top and bottom surfaces of the frame are attached by adhesive strips 36 so that relative shifting movement of the upper and lower plates 26, 27 is in fact restrained.

As shown in FIG. 3, the frame 35 has sufficient memory and resilient strength to raise the plate 26 and the attached table 25 up free from the balls 29 when the load or motor M is not in position. This feature improves joint adhesion, and also allows the ball-and-spacer assembly to return to the center or neutral position when the load is removed. Positioned on top of the table 25 can be any number of extra shims 37 so that the vertical gap between table 25 and motor M can be occupied sufficiently to allow necessary vertical movement without exceeding the limit of the vertical lifting means, in this case the stroke length of the pistons P.

On top of these shims may be positioned the pair of wedges W that provide a cradle for holding the motor M and further occupy the aforementioned gap. Such wedges W would be used on a cylindrical motor, as shown, to provide necessary stability. They would be omitted on a motor having a flat horizontal bottom support surface.

The full periphery of the table 25 and the support assembly therefor, including plates 26, 27 and frame 35, are sealed in by an impervious layer of coated rubber compound, shown in FIG. 3, as coating 40. This coating 40 thus prevents corrosive material and other foreign matter from interfering with the precision movement of the table 25 and also seals in the resilient frame 35 to prevent deterioration due to sunlight and other ambient conditions. It is noted that the contact points for the adjustment screws, presently to be considered, are left free of the compound so as to provide the precision adjustment surfaces that are needed.

There are jackscrews 43, 44 threadedly mounted in the body 15 so as to have their free ends engage the opposite sides of the table 25. This adjustment means allows the table 25 to be controllably moved from side to side or along the X axis, as shown in FIG. 1, so as to provide the alignment, as previously discussed, with great ease. Similar jackscrews 45, 46 are positioned opposite each other on the two opposite sides (front and rear) of the table 25. These jackscrews 45, 46 provide for the travel of the motor M, and thus the shaft 13 toward and away from the mating part or along the Z axis, as shown in FIG. 1.

Because the configurations of some machines that are to be aligned make it difficult to reach the side screws 43, 44, there may also be provided a pair of camming action screws 47, 48 on the same side as the screw 46. The screws 47, 48 have truncated cone-shaped ends that engage respective alignment blocks 49, 50 on the rear of the table 25. Each of the abutment blocks 49, 50 have vertical cam surfaces 49', 50' to cooperate with the truncated cone ends. It will be noted that these cam surfaces 49', 50' are non-parallel and vertical so that the table 25 is provided with components of movement to the side and to the front. Thus, in an instance where the side jackscrews 43, 44 cannot be reached, they are merely backed off, as shown in FIG. 2. The position along the Z axis can then be set by the opposed jackscrews 45, 46 and the side movement may be accomplished by driving one cam screw 48 forward and the other cam screw 47, for example, backward. The desired positioning along the X axis can thus be achieved where access is a problem with little additional effort. Of course, many variations of combinations of the screws 43-48 and the sequence of actuation can be used to get just the exact positioning desired with the least amount of time and effort.

The use of jackscrews 43-48 opposing each other is desirable since not only can the adjustment be made with precision, but also when the precise position is reached, the table 25 can be securely locked in position by oppositely torquing the opposed jackscrews sufficiently to prevent any movement. The camming jackscrews 47, 48 are particularly useful in this regard since they effectively lock in the X direction, and also in the Z direction with the combined use of the screw 45.

The resilient frame 35 is, as explained earlier, effectively coupled to both the upper plate 26 and the lower plate 27, such as by adhesive 36. Thus, upon shifting of the table 25 by selective activation of one or more of the jackscrews 43-48, said frame 35 is distorted or deformed in order to permit the movement. This intentional deformation of the resilient material is advantageous since there is thus in effect a biasing means for urging the table to the centered home position at all times. Thus, if the table 25 is to be moved along the Z axis, and say the direction of movement is to be toward the front side having the jackscrew 45, the jackscrew 45 can be backed off and the jackscrew 46 operated forward with the distortion of the frame 35 assuring that constant pressure is maintained between the tip of the jackscrew 46 and the screw contact point on the perimeter of the table 25. When the adjusted position has been reached, the screw 45 can then be brought back into locking position. Alternatively, of course, the screws 45, 46 can be operated in exact conjunction (opposite rotation) with one another.

After the alignment has taken place and the positioner lowered and the motor M has been permanently mounted, the table 25 may be automatically brought to the home centered position in readiness for the next centering operation by merely backing off all of the screws 43-48, and then bringing them back in until they just touch the table 25. If an overtravel (up to double) adjustment in one direction is needed, this can be provided by pre-setting the appropriate screws all the way to one side. Cotter pins 51 (FIG. 2) may be provided to limit the retraction movement of the screws 43-48 to prevent excessive movement which could rupture resilient frame 35, as well as to prevent inadvertent removal leading to possible loss of the screws. The rubber coating 40 flexes as the alignments are being made and will assist in the repositioning action.

Each chamber 19, 19a in the respective lift blocks 17, 17a is filled with pressurized hydraulic fluid through transfer lines 55, 56, as shown in FIG. 4. Preferably, each of these lines is provided from separate pumps P.sub.1, P.sub.2 with the fluid being transferred through the lines by a control circuit 57 that is identical for each subsystem. Where the additional positioner 11 is utilized, additional pumps P.sub.3, P.sub.4, control circuits and transfer lines are used, as shown in FIG. 4. Since the motor M is preferably raised or lowered uniformly along the full length thereof, operating levers 58 may be moved individually in small increments, or connected with gang link 59 and moved in unison, to attain equal movement at the four lifting points.

The control circuit 57 is shown in more detail in FIG. 5. The pump P.sub.1 receives fluid from intake line 60 from pump reservoir 61 and through inlet check valve 62. A movement of piston 63 for suction (to the right as shown in FIG. 5) brings hydraulic fluid into the pump chamber through the inlet line 60. When the piston 63 is moved in the opposite or power direction, that is in the left hand direction as shown in FIG. 5, the fluid will be checked by the valve 62 and thus forced through line 64 and check valve 65 (valves 66 and 67 remain closed during this operation). The fluid thus flows through line 55, entering chamber 19 and forcing piston P down (see FIG. 3), thus serving to lift the block 17, and in turn, the body 15 and the motor M. The piston 63 of pump P.sub.1 can be operated so that the motor M thus rises as desired for alignment. When ready to lower the motor, bypass valve 66 is opened, and piston 63 is moved to the right to allow precise reverse flow of the fluid out of chamber 19, thus causing precise lowering of the motor M. If lowering has not been completed by the end of piston 63 stroke limit, bypass valve 66 is closed, and bypass valve 67 is opened, allowing piston 63 to return to the left extremity of its stroke, pushing excess fluid into the reservoir 61. Valve 67 is then closed, valve 66 reopened, and the lowering procedure is repeated by moving piston 63 to the right again. Whe the motor M is lowered fully, so that the positioners 10 are unloaded fully, any remaining extension of piston P may be quickly removed by opening both bypass valves 66 and 67, thus returning all excess fluid to the pump reservoir 61.

FIG. 6 shows an alternate hydraulic schematic diagram, employing only a single pump P.sub.5, utilized with four screw frames which actuate oppositely-acting hydraulic rams. In FIG. 6, the same reference numerals are used for equivalent elements as those discussed above. Sequence of action is as follows: Valve 67 is closed, and distributing valves 68, 72, 73, and 74 are opened. Screws 70, 75, 76, and 77 are loosened fully, and the pump P.sub.5 is stroked to the left to raise pilot pistons 78, 79, 80, and 81 equally to about 2/3 of their stroke limit. Valves 68, 72, 73, and 74 are then closed, and valve 67 is opened. The pump is thus de-activated and takes no further part in the proceeding. Screws 70, 75, 76, and 77 are then tightened in rigid C-frames 71, 82, 83, and 84 against the pistons 78, 79, 80, and 81, respectively, using small and equal successive movements to depress said pistons. These piston movements cause the respective pistons P (see FIG. 3) in chambers 19, 19a in lift blocks 17, 17a to be forced down, lifting their respective positioners 10 by amounts equal to the respective depressions of corresponding pistons 78, 79, 80 and 81. When alignment movement is complete, and letdown is desired, the screws are loosened in small equal movements, thus allowing the lifting procedure to be reversed, until letdown is complete.

FIG. 7 shows an alternative mechanical jackscrew arrangement which can be used instead of the hydraulic arrangements described previously. Threaded lift lug 85 is analogous to the lift block 17 and is bolted directly to the body for support cooperation with shoulder 16. Lifting screw 86 threadedly engages the vertical, threaded aperature in lug 85, and its convex lower tip rests in the oiled depression or indentation of bearing plate 87 supported by the spacer 22. Wrenching or turning the screw 86 causes frame 15 and thereby the positioner 10, to be raised or lowered as desired, to accomplish Y-axis alignment or positioning of motor M. This mechanical screw system has the advantages of greater simplicity, compactness, and lower cost than the hydraulic systems. The hydraulic versions, on the other hand, have a higher load capacity. As depicted, however, it is possible to convert the basic positioner 10 to either the mechanical or hydraulic mode, by removing one lifting means and installing the other by use of bolts, or bolts plus holding clamps (see FIGS. 2 and 3).

In view of the foregoing, it is believed apparent that a compact, portable positioner has been provided that is capable of highly efficient and safe alignment of machine elements. The table 25 is raised along the Y axis by movement of the entire assembly by hydraulic or mechanical jacks. The vertical jacking systems allow rapid and precise raising and lowering of the machine to be aligned, while maintaining its level attitude. The adjustments in the horizontal plane along the X and Z axes can thus be accomplished and retained without upset, during the lowering of the machine onto its shimmed supports which actually establish final Y-axis alignment. The ball bearing means for the movement of the table 25 allows precise and easy adjustment in the horizontal plane and the resilient frame 35 provides for resilient centering and release of pressure from the balls 29 during the inoperative periods.

In this disclosure, there is shown and described only the preferred embodiments of the invention, but, as aforementioned, it is to be understood that the invention is capable of use in various other combinations and environment and is capable of changes or modifications within the scope of the inventive concept as expressed herein.

Claims

I claim:

1. A portable positioner for effecting three-dimensional alignment of one machine element or the like with another comprising a main body, a movable table on said body for support of said one machine element, a plurality of balls positioned between said table and said main body for allowing precise movement in the horizontal plane to provide for two-dimensional X and Z adjustment and means for vertically lifting said main body to provide for the third dimensional Y adjustment, whereby movement of said table in either plane does not upset previous adjustment in the other.

2. The positioner of claim 1 wherein is further provided means coupled to said body to adjust and fix said table in the desired horizontal position.

3. The positioner of claim 2 wherein is further provided biasing means for urging said table to the centered home position when said adjusting and fixing means is released.

4. The positioner of claim 3 wherein said adjusting and fixing means includes at least two non-parallel vertical cam surfaces on said table, corresponding cam actuating elements on said body to press against said surfaces to adjust said table over the infinite range of positions within the movement limits of said table.

5. The positioner of claim 4 wherein said cam actuating elements comprise at least two jackscrews, each screw having a frusto-conical terminal end mating with said cam surfaces.

6. The positioner of claim 3 wherein said adjusting and fixing means include at least two pairs of substantially opposed jackscrews to provide positive horizontal adjustment in the directions parallel and perpendicular to the shaft axis of the machine to be adjusted for alignment.

7. The positioner of claim 1 further including horizontal spacer plate means having apertures holding said balls in position.

8. The positioner of claim 7 wherein is further provided means coupled to said body to adjust and fix said table in the desired horizontal position, and biasing means for urging said table to the centered home position when said adjusting and fixing means is released, said biasing means including a resilient frame extending around said bearing means, coupling means to connect said frame to said table and said main body, whereby upon planar relative movement between said table and said main body said frame is deformed to generate the biasing action.

9. The positioner of claim 8 wherein said frame has sufficient effective thickness to lift said table from said balls upon removal of a load, whereby return of the bearing balls and spacer plate to centered home position is facilitated.

10. The positioner of claim 8 wherein said frame is fabricated of resilient foam sheet material, and an impervious coating forming a flexible perimeter seal around said frame.

11. The positioner of claim 9 wherein said frame includes inwardly directed projections engaging the edges of said plate means to hold the same in position.

12. The positioner of claim 1 wherein said lifting means includes hydraulic jack means attached to said main body.

13. The positioner of claim 12 wherein said jack means includes a lift block having a closed end cylinder, a lifting piston mating with said cylinder through the open end and a hydraulic control circuit connected to said cylinder to supply the same with pressure liquid to lift said block and said body.

14. The positioner of claim 13 wherein said control circuit includes pump means, a connecting line between said pump and said cylinder and check valve means to allow normal flow of liquid only to said cylinder, and valved bypass means to allow reverse flow to allow pump controlled lowering movement of said body.

15. The positioner of claim 14 wherein said body is supported by at least two lift blocks, and a control circuit as described for each.

16. The positioner of claim 15 wherein is provided a link to connect the actuating means for said pumps to assure lifting and lowering action in concert.

17. The positioner of claim 14 wherein said control circuit includes release valve means to directly release the pressure in said cylinder and lower said body.

18. The positioner of claim 13 wherein said control circuit includes a hydraulic ram with an operating cylinder and piston, said cylinder being connected by transfer passage to said closed end cylinder of said jack means, means to move said operating piston to raise and lower by transfering hydraulic fluid to and from said lifting piston as required for alignment.

19. The positioner of claim 18 wherein said moving means includes a rigid frame, and a screw mounted on said frame for engaging said operating piston.

20. The positioner of claim 19 and wherein is provided one additional positioner as described, said positioners being located adjacent opposite ends of said machine element for support of the same, each positioner having two jack means, one on each side of said main body, said control circuit including a single pump and individual lines to each transfer passage, and valve means for each individual line.

21. The positioner of claim 1 wherein said lifting means includes vertical jackscrews attached to said body, indented bearing plates to receive the support ends of said jackscrews, whereby said jackscrews may be turned for vertical adjustment and undesired horizontal movement is obviated.