High speed drilling spindle

A high speed drilling system is disclosed for high speed drilling of very small holes in workpieces such as printed circuit boards. The X-Y positioning system includes air bearings to provide lift between the stationary guide beams, the crossbeam and the top table, and further includes a vacuum preloading apparatus for providing a preloading force between the table and the guide beam. The preload force dampens Z axis oscillations which can result in drill bit breakage. The top table is a lightweight honeycomb structure, whose effective rigidity is virtually that of the guide beam due to the vacuum preloading. The system includes pairs of spindles, one a conventional spindle for drilling holes larger than about 0.125 inches, and the other a high speed spindle for drilling holes in the range of about 0.003 to 0.125 inches. The high speed spindle includes a stationary spindle body carrying the stator of the rotary drive motor. Only the spindle rotor is translated along the Z axis to perform the drilling movements. The rotor is supported within the spindle body by rotary and linear air bearings, and is axially driven by a linear motor. A toolchanger loaded by clips carrying the drilling bits is mounted on the top work table, and minimizes the time required to change drilling tools. The clips minimize the manual handling of the fragile drill bits. A vacuum hold-down appratus is employed to secure the workpieces to a drilling station.

BACKGROUND OF THE INVENTION 
The present invention relates to high speed drilling systems for precision 
drilling of workpieces such as printed circuit boards and the like, and 
more particularly to systems for drilling very small diameter holes in 
such workpieces at high speed. 
Printed circuit boards are in universal use today to mount and interconnect 
electrical components forming electrical circuits. Typically, the leads of 
the components are inserted through holes drilled in the boards to form 
predetermined hole patterns. Various systems are known in the art for 
automated drilling of the holes in printed circuit boards. Examples of 
such systems and components thereof are described in U.S. Pat. Nos. 
4,088,417; 3,578,827 and 3,973,863. Such systems typically employ multiple 
spindles, and are numerically controlled to drill the workpieces in 
accordance with a predetermined drilling sequence. The systems typically 
employ automatic tool-changing devices to allow the drill tool to be 
rapidly changed during the drilling sequence. The workpiece is mounted on 
a table supported for X-Y translational movement to accurately position 
the workpiece in relation to the drill spindles. Typically, the work table 
is supported by a plurality of air bearings on a granite beam, and a lead 
screw mechanism is provided to allow the capability of translation along 
one of the X-Y axes. The granite beam is in turn typically supported above 
a granite base by a plurality of air bearings and another lead screw 
mechanism provides the capability of translation along the other of the 
X-Y axes. 
Printed circuit boards used today may employ holes of very small diameters, 
e.g., as small as four thousandths of an inch, with as many as forty 
thousand holes per board, to accommodate high component densities on the 
board. There are a number of problems in drilling such small holes with 
high speed and the required precision. 
One of the most detrimental problems for small hole drilling is the Z axis 
vibration during drilling, which results in drilling tool breakage. 
Printed circuit board drilling machines are typically multi-station 
devices to increase the throughput, and relatively large moving tables are 
required to accommodate all work stations. To meet high speed operating 
requirements, the work table supporting the workpieces are made as 
lightweight as possible. Because the conventional work table is 
constructed from cast iron, the table is generally quite thin to reduce 
the weight. In conventional systems, these tables are usually supported by 
the air bearings at four or six points. This configuration results in a 
"drum" effect when the pressure feet for the respective tool spindles hit 
the table supported workpiece to hold the workpiece down as the spindles 
are lowered for drilling operation. The impact of each pressure foot 
causes vibrations in the table creating motion in the direction of the 
advancing bit, consequently dramatically increasing the chip load on the 
drill bit. This condition is one of the main causes of small drill bit 
breakage. Work table oscillations also result from the acceleration and 
deceleration of the work table to rapidly position the workpieces. 
Conventional spindles presently used in P.C.B. drilling systems rotate the 
drill as it is gripped by one of many types of chucking devices. One type 
of chuck is the centrifugal chuck which apply gripping forces on the drill 
bit caused by the centrifugal forces set up by the high speed rotation of 
the spindle and bit. There are some disadvantages to these conventional 
chuck types, including insufficient bit clamping force at lower speeds, 
lack of concentricity of the bit and the spindle axis, control of the 
runout of the bit, and control of the depth of insertion of the bit. 
Moreover, in conventional systems, the entire spindle, including the heavy 
spindle body, is lowered and raised to accomplish the drilling, thereby 
tending to set up relatively high reaction forces and vibration during the 
rapid acceleration and deceleration of the spindle required for high speed 
drilling operations. 
It would therefore represent an advance in the art to provide a drilling 
system capable of high speed drilling of small diameter (on the order of 
0.003 to 0.06 inches in diameter) holes in workpieces such as printed 
circuit boards and substrates. 
SUMMARY OF THE INVENTION 
A new high speed drilling system is disclosed. One aspect of the invention 
is the X-Y positioning system employed to position the workpiece beneath 
the stationary (relative to X-Y coordinates) drilling spindle. The 
workpiece is supported by a work table, suspended by air bearings above a 
floating crossbeam, which is in turn suspended above stationary guide 
beams by air bearings. X-axis translation is accomplished by a 
servo-motor-driven leadscrew coupling the work table and the floating 
crossbeam. Y-axis translation is accomplished by a servo-motor-driven 
leadscrew coupling the floating crossbeam to the stationary guide beams. 
In accordance with one aspect of the invention, the respective air bearings 
between the respective work table the floating crossbeam and the guide 
beams support substantial areas between the translating surfaces. This 
novel air bearing configuration operates cooperatively with a plurality of 
distributed vacuum chambers to provide a vacuum preloading force tending 
to draw together the adjacent surfaces of the work table and the 
crossbeam, and the adjacent surfaces of the crossbeam and the guide beams. 
The vacuum preloading forces are opposed by the air bearings acting on the 
adjacent respective surfaces surrounding the vacuum chambers. The vacuum 
preload forces is significantly larger than the forces developed by the 
spindle pressure foot in clamping a workpiece, thereby substantially 
eliminating the work table vibration caused by the impact of the pressure 
foot on the workpiece. The vacuum preloading coupled with the distribution 
of the air bearing over large translating areas contributes to outstanding 
work table rigidity unobtainable by conventional table designs wherein the 
table is suspended on four to six bearing points or feet. With the vacuum 
preloading, the stiffness of the work table is virtually equal to the 
machine base table. 
Due to the novel air bearing and vacuum pre-load arrangement described 
above, the work table need not be inherently very stiff, and can therefore 
be very light. In accordance with another aspect of the invention, the 
work table is fabricated by sandwiching a metal honeycomb structure 
between two thin plates of stainless steel. The mass of such a structure 
is reduced by as much as 80% over conventional solid tables, and can 
therefore be accelerated faster by the lead screws while using smaller 
servo motors. This results in reduced wear on the translation system 
components, and increased productivity resulting from the increased speed. 
Another aspect of the invention is the type of high speed spindle which is 
employed as part of the drilling system. The spindle employs a novel 
centrifugal chuck for gripping the drill bit, resulting in improved grip 
and concentricity of the bit with the spindle axis. The chuck is designed 
in such a fashion that the centrifugal forces on the bit are multiplied 
through pairs of opposing lever arms. The chuck is designed as a unitary 
element to prevent relative motion of the rotating components during 
operation and to eliminate potential balance problems. Due to its 
balanced, unitary design, the chuck does not produce axial displacement 
resulting from the process of gripping the bit, in contrast to the tapered 
chucks in common use today. 
Runout of the drill is minimized by separate alignment bushings mounted 
concentrically to the rotational axis of the spindle for centering the 
chuck. The initial bit gripping force, when the spindle is not rotating, 
is generated by the spring action of an O ring held under compression 
forcing the lever arms of the chuck outward, and a circular spring 
providing a static frictional engagement of the drill shank. 
Another aspect of the invention is the spindle arrangement allowing 
simultaneous rotary and linear motion of the rotor, making it possible to 
move the rotor up and down to perform the drilling strokes while the rotor 
is rotating. To carry out this function, the spindle rotor is rotated by 
an AC brushless motor stator fixed in the spindle housing. The rotor is 
longer than the extent of the stator windings to allow axial movement 
without disturbing the rotary operation. The rotor is supported for axial 
and rotary motion relative to the spindle housing by circular and linear 
air bearings. 
The top of the spindle rotor is coupled by a thrust air bearing to a 
non-rotating plunger element mounted for axial movement within the spindle 
housing. The plunger is in turn coupled to the moving coil of a linear 
motor which is moved up and down in reaction to the electromotive forces 
created by the electric current applied to the linear motor coil. Thus, 
the linear motor arrangement provides the capability of raising or 
lowering the spindle rotor simultaneously as the rotor is being rotated at 
high speed. 
The weight of the rotor represents only a fraction of the total spindle 
weight. Because only the rotor, plunger and moving coil is translated up 
and down, while the spindle body remains stationary, the relatively 
lightweight rotor can be linearly accelerated and decelerated without 
generating high reaction forces and high vibration levels. The arrangement 
eliminates the compliance of conventional spindle drives, and provides the 
smooth, vibration-free spindle feed necessary for successful drilling of 
small holes. 
A further aspect of the invention resides in the tool changers. The tool 
changer is carried by the work table and supplies the various tools, i.e., 
the various sizes of drill bits utilized during the workpiece drilling 
operation of the disclosed embodiment. In accordance with the invention, 
the bits are supplied in clips, each carrying six bits. The clips are 
provided with clip covers which protect the bits against damage or loss 
during clip shipment or storage. The covers are removed prior to inserting 
the clips into the magazines of the tool changer. 
A novel tool clip is employed to ship and store the drill bits and to load 
the magazines of the toolchanger. The small size of the drill bits renders 
them subject to breakage or damage from handling as well as from actual 
operating breakages. The clips further provide a means for virtual 
elimination of manual handling of the drill bits. The clip comprises a 
elongated housing member which includes six bores formed therein for 
receiving the drill bits. Each bore is countersunk to provide a shoulder 
surface. A clip cover is provided to protect against bit loss or damage 
during shipment or storage. The cover is removed prior to loading the clip 
into the toolchanger magazine. 
Special bit configurations are employed for the bits to be loaded into the 
clip. In one embodiment a collar is fitted around the shank of each bit, 
and has an outer circumferential groove to be engaged by portions of the 
clip cover to lock the bit into position within the clip. The collar mates 
against a counterbored shoulder in the clip housing to control the depth 
of insertion of the bit into the clip housing. 
In another embodiment, a shoulder and a groove are formed in the bit shank. 
The shoulder mates against the counterbored shoulder in the clip housing 
to control the depth of bit insertion into the bore, and portions of the 
clip cover engage the groove in the bit shank to secure the bit in the 
clip while the clip cover is installed on the clip housing. 
Each toolchanger is carried along a front edge of the work table, and 
comprises a magazine into which a plurality of tool clips (e.g, six) may 
be loaded. The magazine comprises a top locking plate. A plurality of 
elongated slots are formed in the top plate. The thickness of the top 
plate and the slot width is such that the slot edges engage into the 
groove formed in the bit shank or alternatively the bit collar as the clip 
is loaded into the magazine. The elongated slots have a plurality of 
enlarged clearance openings spaced along the slot. The toolchanger 
includes a pneumatic mechanism for translating the locking plate 
horizontally along the slot axis between locked and unlocked positions. 
With the locking plate in the locked position, the bits are locked in 
place by the engagement of the slot edges into the respective grooves 
formed in the bit (or bit collar), and may not be removed. With the 
locking plate in the unlocked position, the enlarged openings in the slots 
are aligned with the bit axes, providing clearance between the slot edge 
and the bit (or bit collar), thereby allowing the bits to be removed from 
or inserted in the toolchanger. 
The toolchangers are supported by pneumatic mechanisms for movement along 
the Z-axis, to raise or lower the toolchanger in relation to its 
associated spindle(s). To load a tool into the spindle, the work table is 
positioned such that the desired bit in the magazine is disposed directly 
beneath the spindle. With the spindle rotor in the zero or home position, 
the toolchanger is raised to place the bit shank within the centrifugal 
chuck so that the bit is gripped by the chuck. The toolchanger then is 
lowered beneath the level of the work surface and the drilling operation 
commences. This cycle is reversed to replace the bit in the clip. 
Utilization of the integrated toolchanger eliminates the need for a 
separate bit transfer system for transporting the bits between the spindle 
and a tool storage location, and results in faster toolchanging than 
conventional systems. 
Conventional drilling systems employ spindle pressure feet to secure the 
workpiece while the drilling operation takes place. The pressure feet 
strike the workpiece with considerable force, causing vibrations which 
tend to cause bit breakage. To solve this problem, a vacuum frame fixture 
is employed in the system to secure the workpiece in the appropriate 
location. An opening is provided in the top surface of the work table; 
this opening communicates with a source of vacuum. A tool plate, also with 
a large vacuum opening formed therein, is disposed on the work table with 
the opening in the tool plate in alignment with the opening in the work 
table. A vacuum chuck member is placed on the flat plate, and comprises a 
flat top surface and a bottom surface having a plurality of transverse 
elongated relieved areas defined therein. 
A backup board and a stack of the thin workpieces to be drilled are laid on 
the flat surface of the vacuum chuck member. A frame is then placed around 
the periphery of the board stack, and comprises a rectilinear side fixture 
region with a flexible vacuum seal which contacts the flat plate, and a 
top fixture region with a flexible vacuum seal which contacts the top 
periphery of the top workpiece in the stack. The fixture and vacuum chuck 
member serves to define a sealed chamber around the periphery of the 
workpiece stack. As a source of vacuum is applied to the opening in the 
flat plate, air is drawn along the transverse relieved areas of the vacuum 
chuck to evacuate the seal chamber. The atmospheric pressure on the 
exposed surface of the topmost board firmly depresses the boards to a 
flattened state, and the seals compress so that the frame clamps the 
periphery of the board stack to the work table. During the drilling 
sequence, the depth of the drill insertion is controlled such that the bit 
does not penetrate the backup board. Thus, drilling holes in the workpiece 
does not break the vacuum seal securing the workpieces.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT 
A preferred embodiment of a precision high speed drilling system embodying 
the invention is depicted in the front plan view of FIG. 1. The system 50 
comprises a horizontal lower granite base table 55 supported by granite 
pedestals 57 and 59. A pair of granite guide beams 60 and 62 are attached 
to the base table 55. Granite crossbeam 65 is disposed on the two guide 
beams 60 and 62. During system operation, the crossbeam is supported above 
the guide beams by air bearings, to be described in further detail below. 
The system 50 includes means for translating the crossbeam 65 along the Y 
axis in relation to the guide beams 60 and 62 in dependence on control 
signals provided by the system control unit (FIG. 25). The translating 
means comprises a precision lead screw arrangement, visible in FIG. 2, 
driven by a servo motor which is controlled by the system control unit in 
the conventional manner. Such translating means are well known to those 
skilled in the art. 
A work table 70 is supported above the crossbeam 65 by air bearing means. 
The system 50 further comprises means for translating the work table 70 
along the X axis in relation to the crossbeam 65. This translating means 
also comprises a precision leadscrew arrangement driven by a servo motor 
controlled by the system control unit, in a manner similar to that 
described above with respect to the translating means for the crossbeam 
65. 
A granite top support beam 80 is permanently supported above the work table 
70 by a pair of C-shaped uprights 75 and 77. The top beam 80 in turn 
supports a plurality of drilling spindles. In accordance with one aspect 
of the invention, the system comprises a plurality of pairs of drilling 
spindles; one spindle of each pair is adapted for drilling of medium to 
large diameter holes in workpieces, and the second spindle is adapted for 
high speed drilling of small diameter holes. Thus, the high speed spindles 
81-84 are respectively paired with the conventional spindles 85-88. Each 
pair of spindles are mounted in a side-by-side relationship above 
corresponding tooling plates 91-94 which are in turn mounted on the work 
table 70. The respective translating means for the crossbeam 65 and the 
top work table 70 provide a means for precisely positioning the work table 
70 in relation to the X-Y location of the spindles. 
The system 50 depicted in FIG. 1 comprises four drilling work stations 
comprising the respective tooling plates 91-94 and the pairs of drilling 
spindles. The control unit is programmed to select the appropriate 
drilling spindle of the respective spindle pairs for drilling a particular 
hole in a workpiece secured to a tooling plate, and to automatically carry 
out a sequence of drilling movements to drill a predetermined pattern of 
holes of varying predetermined sizes in the workpiece. 
A plurality of toolchangers 95-98 are also depicted in FIG. 1, one for each 
of the drilling stations of the system. The toolchangers are adapted to 
cooperate with the spindles and translating means to provide a means for 
supplying the appropriate spindles with the appropriate drilling tools 
under control of the system control unit. As will be described in further 
detail below, the toolchangers are adapted to perform their functions with 
a minimum of required movements, thereby minimizing the time required for 
toolchanging. 
X-Y Positioning System with Vacuum Pre-loading 
Referring now to FIG. 2, a top cross-sectional view of the system 50 is 
shown, taken along line 2-2 of FIG. 1. The translating means for 
positioning the crossbeam 65 in relation to the guide beams 60 and 62 
comprises the precision leadscrew 100 and a drive mechanism including the 
servo motor 102 and a coupling device for coupling the motor shaft to the 
leadscrew. The leadscrew 100 is substantially aligned with the Y axis and 
attached by ballnut 104 to the cradle 66, in turn secured to the bottom 
surface of the crossbeam 65 so as to fit between the two guide beams 60 
and 62. Cradle 66 houses four air bearings whose locations are indicated 
generally by reference numerals 66a-d in FIG. 2, providing guiding for the 
cross beam 65 along the edges of the guide beams 60 and 62, to constrain 
the movement of the crossbeam 65 relative to the guide beams to the Y 
direction. Rotational energy of the leadscrew 100 (driven by the motor 
102) is transferred into a translating force tending to translate the 
crossbeam along the axis of the leadscrew 100, with the direction of the 
imparted force being determined by the direction of rotation of the 
leadscrew, i.e., clockwise or counter-clockwise. The means for translating 
the work table 70 similarly comprises leadscrew 110, substantially aligned 
with the X-axis, servo motor 112 and ballnut 114, which is secured to the 
underside of table 70. By appropriate rotation of the leadscrew 110 by the 
motor 112, a force is imparted to the table 70 tending to translate the 
table along the axis of the leadscrew 110. X and Y linear scales 66 and 67 
provide electrical signals to the system control unit indicative of the 
respective X and Y position of the crossbeam 65 and table 70. 
The crossbeam 65 is preferably constructed of granite. The system is 
provided with air bearings to allow virtually friction-less movement 
between the respective guide beams 60 and 62, the crossbeam 65, and the 
work table 70. The air bearings comprise a supply of pressurized air (not 
shown). A plurality of orifices 120a and 120b are provided in the upper 
and lower surfaces of the crossbeam 65 in communication with the air 
source by vertical air channels 130 and horizontal channels 134 bored in 
the crossbeam 65, air fittings 131, and air supply lines 132 (FIG. 4). In 
this embodiment, the air bearing is distributed over the area of the 
sliding surfaces of the respective guide beams 60 an 62, the crossbeam 65 
and the work table 70, instead of operating only on localized supporting 
feet. Thus, while the use of air bearings in drilling systems is itself 
not new, one aspect of the invention resides in the distribution of the 
air bearing to support large areas of the sliding surfaces of the X-Y 
positioning system. 
Another aspect of the invention is the provision of means for exerting a 
preloading force (in addition to gravity) tending to oppose the air 
bearing lift pressure separating the respective guide beams 60 and 62, the 
crossbeam 65 and the work table 70. The preloading means comprises a 
plurality of vacuum chambers 128 which are formed in the crossbeam 65 as 
shown in FIG. 2. The chambers 128 comprise relative large diameter 
openings, for example, about 3.0 inches, formed through the crossbeam 65. 
In this embodiment, a total of twelve vacuum chambers 128 are formed in 
the crossbeam 65, six chambers above the guide beam 60, and six additional 
chambers above the second guide 62. The width dimension of the crossbeam 
is selected in cooperation with the maximum allowable excursions of the 
crossbeam 65 so that all six chambers are always between the upper 
surfaces of the respective beams 60 and 62 and the lower surface of the 
top work table 70. In this embodiment, the crossbeam 65 is about 20 inches 
wide, 70 inches long, and 3.5 inches in thickness. This distribution of 
the chambers 128 serves to ensure that the preload force is substantially 
constant over the entire range of movement of the respective guide beams 
60 and 62, the crossbeam 65, and the top table 70. 
The vacuum chambers 128 are respectively coupled to a source of vacuum (not 
shown) via bores 122 which are formed in the crossbeam 65, fittings 124 
and vacuum lines 125. Slots 129 are formed between the six chambers 
forming each group of six chambers to couple all the chambers of that 
group to the source of vacuum. The second group of six chambers 128 is 
coupled by a similar arrangement to the source of vacuum. In this 
embodiment, the source of vacuum is preferably a vacuum pump developing 
2-3 psi. 
The vacuum chambers provide a means for damping the magnitude of any 
movements of the crossbeam 65 and the top work table 70 in the Z axis 
direction resulting from forces applied during the operating of the 
system. Such forces arise from the reaction forces resulting from the 
acceleration and deceleration of the respective beam 65 and the work table 
70 during X-Y translation, and from the impact of the drilling tools in 
the Z direction. In conventional systems, these forces result in 
substantial Z axis oscillations of the work table 70, impairing the 
accuracy of the drilling operations and exerting Z axis forces on the 
drilling tools, which for drills of relatively small diameter would result 
in tool breakage. The present system is adapted to minimize such 
oscillations, allowing high speed drilling of very small diameter holes in 
the workpieces. The preloading force applied by the vacuum preload system 
is selected to be greater than the impact forces in the work table 70 
resulting from the impact of the drilling tool and the spindle pressure 
feet. For the disclosed embodiment, the preload force resulting from the 
twelve vacuum chambers, each three inches in diameter is about 260 pounds. 
With the vacuum preloading, the rigidity of the top work table 70 is 
virtually that of the stationary guide beams 60 and 62, and consequently 
that of the base table 55. 
Another advantage of the vacuum preloading means is that, because the 
rigidity of the table 70 is now virtually that of the granite base table 
55, the top table 70 need not be inherently massive to achieve the 
rigidity necessary for the operation of the system. Instead, in the 
disclosed embodiment, the work table 70 is fabricated from a honeycomb 
core 71, sandwiched between respective upper and lower sheets 72 and 73, 
fabricated from stainless steel. The resulting structure 70 has a weight 
of 80 to 100 pounds, in contrast to the typical weights of 700 to 800 
pounds for the cast iron work tables used in conventional drilling 
systems. 
FIG. 3 shows a cross-section of the work table 70. Several advantages flow 
from the use of the relatively lightweight table 70. These include lower 
cost of the table, and use of lighter elements to comprise the respective 
translating means for achieving the lateral positioning of the table in 
relation to the spindles during operation. Because the mass of the table 
has been dramatically reduced, the table may be moved much more rapidly 
and with less driving energy than required for conventional systems. As a 
result, the system uses less energy, may be fabricated at a lower cost, 
and operated at substantially higher speed. The higher speed results in 
increased throughout and higher productivity of the system. 
FIG. 3 further illustrates the respective arrangement of the air bearings 
and the preloading means in relation to the guide beam 60, the crossbeam 
65 and the top work table 70. The air bearings provide a lifting force, so 
that the table 70 floats on a cushion of air over the top surface of the 
crossbeam 65 (as depicted in FIG. 7), and the crossbeam 65 in turn floats 
on a cushion of air above the top surface of the guide beams 60 and 62. 
The vacuum preloading means provides vacuum preloading forces tending to 
draw the top table 70 and the guide beams 60 and 62 toward each other. 
FIG. 4 further illustrates the preloading means and the air bearings 
between the beams and the work table. It is to be noted that the orifices 
for the air bearing and the vacuum chambers are carried by the same 
member, i.e., the crossbeam 65, to ensure a proper relation between the 
air bearing and the vacuum preloading means assuring that a vacuum chamber 
will never come into direct communication with an air bearing orifice. As 
illustrated in FIG. 4, pairs of orifices 120a and 120b are disposed in the 
upper and lower surfaces of the crossbeam 65, connected by bores 130 
extending in the vertical (Z) direction. Horizontal bores 134 extend in 
the crossbeam 65 in communication with respective ones of the vertical 
bores 130 and with fittings 131 inserted in the exposed end of the bore 
134 to provide a connection with the air supply hoses 132. The exposed 
ends of the vertical bores 130 are sealed with orifice fittings 135, best 
shown in FIG. 5, in which are formed the calibrated orifices 120a (top 
surface) and 120b (bottom surface). An exemplary fitting 135 is shown in 
the cross-sectional view of FIG. 6. The fitting 135 comprises a 
cylindrical insert member 135a having a counterbored opening 135b formed 
therein. A threaded plug 135c is threadingly received within the 
counterbore of insert 135a, with orifice 120a formed in the plug in 
communication with the opening 130. The air flow rate out of orifice 120a 
is dependent on the orifice size and the air pressure. In the disclosed 
embodiment, 0.006 inch diameter orifices and an air supply at 80 psi are 
employed. 
FIG. 7 further illustrates the interface between the adjacent surfaces of 
the top table 70 crossbeam 65 and guide beam 60, with the arrows 
indicating the flow of air through the air bearing passages and out the 
orifices to lift the respective crossbeam 65 and table 70. The flow of air 
into a vacuum chamber is also depicted, and the resulting preload force 
indicated by the downwardly extending arrows against the upper surface of 
table 70. 
Workpiece Hold-Down Apparatus 
Referring now to FIGS. 8-10, a further aspect of the invention is 
illustrated. FIG. 9 is a cross-sectional view illustrating the workpiece 
hold-down apparatus 140 employed to secure the workpiece in a registered 
position at a typical workstation. The apparatus comprises a plenum 74 
formed in work table 70, and the tooling plate 91, which is preferably 
fabricated from a relatively lightweight metal such as aluminum or a 
honeycomb structure, and which is disposed over the work table 70. A duct 
141 is formed in the tooling plate 91 which is disposed on the table 70 
with the duct 141 in communication with plenum 74. The plenum 74 is 
coupled to a source of vacuum (not shown). 
Pins 142 and 143 are fitted in bores in the plate 95, and serve to register 
the position of other elements of the hold-down apparatus 140. These 
elements include a rectangular frame 145, a corrugated vacuum chuck 
fixture 49 and a workpiece backup board 136. One or more workpieces 
comprising the workpiece stack 137 are disposed on the backup board 136 
for drilling by one of the spindle of the system. 
The frame 145 is fabricated with the cross-sectional configuration 
illustrated in FIG. 9, with an upwardly extending side member 145a joined 
with the horizontal top member 145b. Resilient seals 147 and 148 are 
fitted respectively along the bottom surfaces of the side member 145a and 
the top member 145b. The seals are fabricated from a resilient material 
such as neophrene, and serve to seal against the vacuum which is drawn 
down within the sealed chamber 144 defined by the tooling plate 91, the 
board stack 137 and the frame 145. The vacuum chuck 149 comprises a 
plurality of channels 149a (best shown in FIG. 10) for distributing the 
vacuum over the chamber 144. To increase the system throughput, normally 
several printed circuits boards are stacked together to form the stack 37. 
The seals 147 and 148 have substantial compressible thicknesses, so as to 
accommodate varying thicknesses of the board stack 137, depending on the 
number of boards and their particular thickness. 
The hold-down apparatus 140 operates in the following manner. With the 
tooling plate 91 installed on the table 70 and its position determined 
relative to the drilling spindles by conventional techniques, the vacuum 
chuck fixture 149 is disposed on the plate 91, with the pins 142 and 143 
being received through bores formed in the fixture 149. The backup board 
136 and the workpieces comprising the stack 137 are then placed on the 
fixture 149, with the pins 142 and 143 also fitting through corresponding 
openings formed therein to register the position of the workpieces on the 
work station. Next, the frame 145 is disposed over and surrounding the 
respective elements 149, 136 and 137 to define the vacuum chamber 144. It 
will be appreciated that the top surface of the stack 137 is subjected to 
the force of the atmospheric pressure, indicated by the arrows impinging 
on the exposed surface of the board stack 137 in FIG. 9. As the frame 145 
settles in the position shown in FIG. 9, the air within the chamber 144 
will be drawn down to a relative vacuum. The atmospheric pressure on the 
top of stack 137 will force the stack down, as well as drawing the frame 
145 downwardly against the resiliency of the seals 147 and 148. The boards 
comprising the board stack are securely held in position by the 
atmospheric pressure. The drilling spindle carries out its sequence of 
drilling strokes to drill a predetermined hole pattern. The drill 
penetrates through the stack 137 into the backup board 136, but does not 
enter the vacuum chuck fixture 149, which would penetrate the vacuum 
chamber and permit air to enter the chamber. Thus, the vacuum in the 
chamber 144 is not relieved during the drilling strokes so that the boards 
remain securely fixed throughout the entire drilling sequence. This 
represents an improvement over known vacuum fixtures which employ the 
workpiece itself to define the vacuum chamber so that as holes are drilled 
in the workpiece the chamber is breached and air is admitted. 
High Speed Drilling Spindle 
One aspect of the invention is the provision of drilling spindles which are 
capable of very high sustained drilling speeds (80,000 to 120,000 
revolutions per minute) and drilling rates or "hits" (on the order of 300 
holes drilled per minute) using small diameter bits, e.g., 0.006 inches in 
diameter. FIG. 11 is an enlarged view of the spindle 81, an exemplary one 
of the high speed spindles 81-84 comprising the system 50 of FIG. 1. In 
accordance with the invention, the spindle comprises a stationary spindle 
body 156 mounted in the spindle housing 155 fastened to the upper support 
beam 80, and a spindle rotor 160 which is supported by air bearings within 
the spindle body 156 for very high rotational speeds and simultaneous 
rapid linear movements in the Z axis (along the rotor axis 161) to achieve 
the drilling strokes. 
This arrangement contrasts with that of conventional drilling spindles, 
wherein the entire spindle is mounted for linear movement along the Z 
axis, and is driven by an external translating mechanism such as a 
leadscrew or a cam/rocker arm arrangement, and where linear motion is 
performed through guide bearings which are external to the spindle. The 
conventional spindle weighs on the order of 15 to 30 pounds, requiring a 
translating mechanism with suitable power capabilities to drive the weight 
of the entire spindle through the drilling strokes at the desired hit 
rates. The acceleration and deceleration of the entire spindle to achieve 
the drilling strokes results in substantial reaction forces on the entire 
drilling system, which tends to cause vibration in the system structure. 
Moreover, with the entire spindle translated through the drilling stroke, 
larger impact forces on the machine structure result, which in turn 
results in substantial Z axis vibration of the drill and workpiece. The Z 
axis vibration causes undesirable variations in the chip load on the 
fragile drill bits, introducing torsional stress and causing drill bit 
breakage. 
By achieving the capability of translating only the spindle rotor, which 
may weigh only one pound, to achieve the drilling strokes, less power is 
required to drive the rotor through a drilling stroke, and the resultant 
impact force is substantially reduced, thereby also substantially reducing 
the z axis vibration. The acceleration/deceleration reaction forces on the 
system are also dramatically reduced. The reduction of such vibrations 
allows the use of the very small diameter drill bits and the high drilling 
rates and stroke rates described above. 
The weight of the rotor 160 is supported by the counter-balancing springs 
165 and 166, which attach to respective ends of rod member 168 and to 
respective ends of T-shaped support fixture 164, which is in turn mounted 
to the top of the spindle body cap 157. As will be described more fully 
below, the member 168 is coupled to the rotor 160, and translates up and 
down along the axis 161 with the rotor 160. Thus, the movement of member 
168 along the axis 161 tracks the movement of the rotor 160. 
The spindle 81 is provided with position and velocity feedback sensors 151 
and 153 which provide respectively Z axis position and Z axis velocity 
information to the spindle control unit (FIG. 25). The position and 
velocity sensors 151 and 153 actually measure the relative position and 
the position rate of change of the member 168, which is directly related 
to the corresponding parameters for the rotor 160. 
The position sensor 151, in the form of a potentiometer, comprises a wiper 
152a, the upper end of which is secured to the member 168 and the lower 
end of which moves upwardly and downwardly within corresponding bore 152b 
formed in potentiometer body 152c containing a resistive element. 
Similarly, the velocity sensor 153 is in the form of a velocity transducer 
comprising a magnetic slider 154a, the upper end of which is secured to 
rod 168 and the lower end of which moves upwardly and downwardly within 
the bore 154b formed in the coil 154b. Such sensors are available 
commercially. For example, the position sensor may comprise the T50A502 
model sensor marketed by Sieb & Meyer GMBH, West Germany, and the velocity 
sensor may 
comprise the 0111-0000 model sensor marketed by Trans Tek. 
The construction of the spindle 81 is shown in further detail in the 
cross-sectional view of FIG. 12. The spindle comprises elongated 
cylindrical rotor shaft 160, which includes a thrust flange 170 at the 
upper end 160a of the rotor 160. A thrust bearing 172 captures the flange 
170 and couples the rotor to sliding plunger 174. 
The plunger 174 comprises a cylindrical hollow member having a 
substantially closed lower end 174a. The plunger 174 slides within the 
hollow cylindrical opening defined by the tubular insert member 175 with 
its liner 177, comprising an anti-seize surface, for example, 
Teflon-impregnated bronze, which in turn is fitted within the spindle body 
156. The insert member 175 includes the air bearing passage 175a, which 
communicates with bore 157 formed through the spindle body 156. An air 
fitting 158 is secured in the bore 157, and an air line 159 attached 
thereto is connected to a pressurized air source (not shown). A groove is 
formed in the outer periphery of the insert member 175 to define a 
circumferential input air plenum 179a. Passages 179b are formed in the 
insert member 175 and liner 177 between the plenum 179a and the inner 
periphery of the liner 177, thereby allowing air to flow between the 
plenum 179a and the annular opening between the rotor and the liner 177. A 
plurality of the passages 179b are distributed radially about the axis 161 
to provide a distributed air supply into the annular opening. 
The plunger 174 has formed therein an air passage 176 which extends from 
the region adjacent the air plenum 175b defined by the insert member 175 
liner 177 down into the lower end 174a, where the passage communicates 
with corresponding passages formed in the thrust bearing 172. 
The thrust bearing 172 is shown in further detail in the enlarged partially 
broken-away, cross-sectional view of FIG. 21. The bearing 172 comprises 
three circular elements 172a, 172b, and 172c secured to each other and to 
the plunger 174 by six conventional fasteners 172f. The multi-element 
construction of the thrust bearing 172 allows the assembly of the bearing 
about the flange 170 of the rotor 160. Element 172a is first assembled to 
the end 174a of the plunger 174. Next, the center element 172b, comprising 
a ring-like structure, is assembled to the element 172a. With the flange 
170 inserted into the recess defined by the upper element 172a and the 
center ring-like element 172b, the lower element 172, also a ring-like 
structure may be slipped around the rotor shaft 160 and assembled to the 
exposed lower annular surface of the center element 172b. The entire 
thrust bearing assembly may then be secured by the fastener 172f to the 
plunger 174. 
Each of the elements comprising the thrust bearing 172 includes air 
passages which communicate with the air passage 174a formed in the plunger 
174 to form an air passage network supplying the pressurized air 
supporting the flange 170 within the thrust bearing. Thus, the upper 
element 172a includes six passage orifices 172d (two of which are visible 
in FIG. 21) which distribute pressurized air about the top peripheral 
surface of the flange 170. Lower element 172c includes six passage 
orifices 172e (one is visible in FIG. 21.) which distribute pressurized 
air about the lower peripheral surface of the flange 170. The center 
element 172b includes connecting passages to connect corresponding aligned 
passages formed in the upper and lower elements 172a and 172c. The 
direction of the air flow is indicated by the arrows shown in FIG. 21. 
The purpose of the air line 159 and the various air passages formed in the 
body 156, the insert 175, the plunger 174 and the thrust bearing 172 is to 
provide an air bearing facilitating the sliding of the plunger 174 within 
the insert member 175, and the rotation of the flange 170 and rotor 160 
relative to the (rotationally stationary) thrust bearing member 172. As 
will be described more fully below, the rotor and plunger translate 
axially during operation along the extent of a range of movement, while 
the rotor 160 is simultaneously rotating at high .speeds relative to the 
plunger 174. The pressurized air is admitted through bore 157 into passage 
175a, and provides a separating air cushion or bearing in the narrow 
annular region between the liner 177 and the plunger 174, substantially 
reducing any sliding friction between the two members. Additionally, the 
pressurized air flows through the plenum 175b into passage 176 in the 
plunger 174, and is conducted through the passages in the thrust bearing 
elements and out the orifices 172d and 172e. Thus, an air bearing is 
formed to separate the adjacent surfaces of the rotor flange 170 and the 
thrust bearing member 172. 
The upper end of the plunger 174 is secured to member 168. Cylindrical rod 
members 168a and 168b comprising member 168 extend through slots 180 and 
181 formed in the upper end of the spindle body 156 and extend parallel to 
the vertical axis 161 of the spindle. Ball bearing race 182 is fitted to 
the rod member 168a to substantially reduce any frictional drag on member 
168a caused by contact with a wall of slot 180. Thus, the rod member 
168a, race 182 and slot 180 cooperatively form an anti-rotation bearing 
preventing rotation of the plunger 174 while permitting linear travel of 
the plunger along axis 161. 
The upper and lower ends 160a and 160b of the rotor 160 are also supported 
by rotary air bearings within spindle body 156 to allow virtually 
frictionless rotation about the axis 161. The lower spindle housing 155 
comprises a bore formed therein for receiving the spindle body 156. Upper 
tubular insert member 185a having an inner liner 183a is fitted within the 
body 156. The insert member 185a with its liner 183a encircles the rotor 
at its upper end 160a, and is adapted to support the rotor end within a 
relatively small tolerance between the outer rotor periphery and the inner 
periphery of the liner 183a. The liner 183a comprises the anti-seize 
compound lining its inner surface which surrounds the rotor. The purpose 
of the liner is to prevent damage to the rotor and the insert member 185a 
in the event the air bearing supply is terminated while the rotor is still 
rotating at high speed. Without an anti-seize lining, the heat resulting 
from the friction between the rotor and the adjacent liner or insert 
surfaces could result in welding of the rotor to those surfaces. 
A groove is formed in the outer periphery of the insert member 185a to 
define a circumferential input air plenum 186a. Passages 187a are formed 
in the insert member 185a and liner 183a between the plenum 186a and the 
inner periphery of the insert member, thereby allowing air to flow from 
the plenum 186a into the annular opening between the rotor and the insert. 
A plurality of the passage 187a are radially distributed about the axis 
161 to provide a distributed air supply into the annular opening. A bore 
188a is formed through the body 156 and the spindle housing 155. Air line 
190a is connected to the fitting 189a inserted in the bore 188a, and to a 
pressurized air source (not shown). O ring pairs 191a and 192a provide an 
air seal between the housing 155 and the body 156, and between the body 
156 and the insert member 185a. 
In a similar fashion, the lower end 160b of the rotor 160 is supported 
within the spindle body 156 for rotation on a circular air bearing. Lower 
tubular insert member 185b with liner 183b is fitted within the lower end 
156a of the spindle body 156, and is secured in position by a threaded 
fastener 193. A plurality of passages 187b are formed in the insert member 
185b and liner 183b between the circumferential plenum 186b and the inner 
periphery of the liner 183b. A bore 188b is formed through the spindle 
housing 155 and the body 156. Air line 190b is connected between the 
fitting 189b mounted in the bore 188b and the source of pressurized air. 
The spindle rotor 160 is driven by a rotary drive motor. The stator of the 
drive motor is disposed within the spindle body 156 intermediate to the 
upper and lower insert members 185a and 185b. The stator comprises a 
laminated iron core 195 and a plurality of copper wire windings 196 which 
are wound around a corresponding number of axial slots formed in the core 
195. Wires 197 couple the respective stator windings 196 to a frequency 
converter for driving the motor. 
The rotor 160 of the disclosed embodiment comprises a solid cylinder shaft 
of tool steel, 0.625 inches in diameter and 5.3 inches in length, with a 
weight of about one pound. The rotor 160 further comprises a plurality of 
elongated copper bars 198 which are inlaid in axial slots at the outer 
periphery and which are all connected at each end by copper rings embedded 
in the shaft outer periphery, to conduct the rotor electrical currents and 
thereby permit the electromotive force to be exerted on the rotor by the 
stator during drive motor operation. In accordance with another aspect of 
the invention, the bars 198 are disposed along the rotor shaft so as to 
overlap the extent of the stator by a length at least equal to the maximum 
axial travel of the rotor. The overlap is split between the upper and 
lower ends of the stator elements. For example, in the disclosed 
embodiment the windings 196 have a lengthwise extent of 1.08 inches, and 
the bars have a corresponding lengthwise extent of 1.71 inches allowing a 
total travel of 0.62 inches. The actual dimensions may, of course, be 
varied to provide a travel length necessary for the particular 
application. With the added length of the bars, the rotor may be axially 
translated along the allowed range of movement without the loss of any 
magnetic flux by the motor magnetic circuit, so that a substantially 
constant electromotive force is applied to the rotor by the drive motor 
throughout its range of axial movement. This results in a substantially 
constant rotation speed irrespective of the rotor axial position within 
its range of movement. 
The drive motor comprising the rotor 161, the stator windings 196 and the 
core 195 is an ac variable frequency brushless motor. Drive signals are 
applied to the stator windings via wires 197 from a frequency converter. 
In this embodiment, the frequency of the drive signal is variably selected 
to provide the desired rotational speed. For example, using a 21.35.1 
model frequency converter marketed by Sieb & Meyer GMBH, West Germany to 
drive the windings 196, a drive signal frequency of 1000 cycles per second 
results in a rotor speed of 60,000 rpm, while a drive signal of 2,000 
cycles per second results in a rotor speed of 120,000 rpms. For the 
disclosed embodiment, the motor is power rated at 120 watts. The design of 
ac brushless motors is well known, and the precise details of the stator 
windings, the core layout and the motor driver need not be described in 
further detail, as it is well within the purview of one of ordinary skill 
in the art to provide a motor for achieving the motor requirements for a 
particular application. 
The spindle 81 further comprises an active coolant system for cooling the 
spindle in the region of the ac brushless motor. The coolant system 
comprises an inlet passage 200 and the circumferential inlet plenum 202 
formed in the housing 155 around the body 156 adjacent an upper portion of 
the windings 196. The inlet plenum 202 is in communication with the 
passage 200, and also with the outlet plenum 203 though openings (not 
shown) formed in the common dividing wall 202a. Plenum 203 is formed in 
the housing 155 around the body 156 in the region adjacent a lower portion 
of the stator windings 196. 
Outlet passage 204 is formed in the housing 155 in communication with the 
outlet plenum 203 to exhaust the coolant out of the outlet plenum. An 
inlet line 206 is coupled to inlet passage 200 by fitting 205, and is 
connected to a coolant pump 706 (FIG. 26). Water is suitable for use as 
the coolant fluid. 
A coolant outlet line 208 is coupled to passage 206 by fitting 207, and is 
connected to a heat exchanger 702 (FIG. 26) and then to a coolant 
reservoir 704. The cooling system is preferably a closed system, wherein 
the coolant is recirculated from the reservoir 704 back to the pump, to be 
pumped back into the spindle housing 155. Thus, in operation the coolant 
flows into the passage 200 and then into the inlet plenum 202 and the 
outlet plenum 203, where heat is absorbed from the spindle body. The 
heated coolant fluid is then exhausted from the outlet plenum through the 
passage 204. The flow of coolant through the system is preferably 
continuous to maintain a steady state operating temperature. 
The spindle 81 further comprises a linear motor which drives the rotor 160 
along its axis to perform the drilling motions. The motor is adapted to 
provide axially directed forces on the rotor about five pounds in 
magnitude, tending to drive the plunger 174 and the rotor 160 downwardly 
in the Z axis direction to feed the drill tool into the workpiece 
positioned below the drilling spindle, or upwardly to lift the rotor and 
drill tool away from the workpiece. The counterbalancing springs bias the 
rotor to the centered rest position depicted in FIG. 12, and serve to 
counteract the force of gravity so that the rotor weight is transparent to 
the linear motor operation. Thus, the motor is not required to exert more 
force to raise the rotor than to lower it. 
The linear motor comprises a moving coil assembly 210 acting in cooperation 
with a permanent magnet and flux connector assembly 220. The moving coil 
assembly 210 comprises a bottom flange member 211 which is fastened by a 
fastener 211a screw to the top of member 168, and a thin hollow metal 
spool 212 connected to the flange. Insulated copper wire is wound around 
the outside of the spool from the bottom to the top of the spool and then 
back down to the spool bottom to form the coil 213. The ends 214 of the 
wire forming the coil are brought down and secured to the top of rod 168b 
and connected to a linear motor driver to provide the motor drive signals. 
The drive signal is a pulse width modulated, four quadrant closed loop 
signal whose voltage is proportional to the load. The motor is adapted for 
a 70% duty cycle and to provide maximum stroke excursions of .+-.0.375 
inches, with feed rates ranging from one inch per minute up to 1000 inches 
per minute. 
The permanent magnet and flux connector assembly 220 comprises the annular 
permanent magnet assembly 222 which fits around the inner periphery of the 
flux connector 224. The connector 224 is preferably fabricated from high 
permeability steel and comprises a hollow outer cylinder 224a and a solid 
inner cylinder 224b. The outer cylinder fits around the outer periphery of 
the moving coil assembly 210, and the inner cylinder 224b is adapted to be 
inserted within the hollow metal cylinder 212 comprising the coil assembly 
210. The outer and inner cylinder members of the flux connector are 
connected by the top plate 224c to complete the magnetic path. 
The spindle cap member 157 fits over the flux connector 224, and is secured 
to the spindle body 156 by engagement of mating threads. 
The spindle 81 further comprises a sensor 178 mounted to the plunger 174 
for sensing the rotations of the rotor 160 and providing a signal on line 
179 indicative of its rotational speed (rpms) of the rotor 160. The sensor 
may comprise a magnetic sensor such as the model 3080 magnetic sensor, 
marketed by Electro Corporation, Newport Beach, California. 
The spindle control unit receives the rpm indication signals, the Z axis 
position signals and the Z axis velocity signals from the respective 
sensors 178, 152 and 154. The rpm signals are employed to control the ac 
brushless motor excitation signals to provide the desired rotation speed. 
The position and velocity signals are processed by the spindle control 
unit to control the linear motor to provide the desired rotor axial 
position and velocity. 
High Leverage Centrifugal Chuck 
The spindle 81 comprises a novel centrifugal chuck assembly 250, disclosed 
in detail in FIGS. 13 and 14. The assembly elements are disposed within 
the axial bore 162 formed in the lower end 160b of the rotor shaft. The 
elements include a tool alignment bushing 251 fitted into the end of the 
bore 162 in alignment with the rotor shaft axis 161, unitary high leverage 
centrifugal chuck 255, chuck alignment bushing 265, and chuck retainer 
270. As depicted in FIGS. 12 and 13, the shank of the drill bit 400 is 
inserted into the chuck, and its upper end received within the hollow 
alignment bushing 251. The shank is gripped securely by the chuck 255 
during high speed rotation of the rotor, as will be described in further 
detail. 
The chuck 255 is shown in perspective in FIG. 14, and comprises four 
elongated lever arm members 256a-d, all connected to the upper portion of 
fulcrum region 257 (see FIG. 13). The lever arms are arranged in two pairs 
of diametrically opposed levers, 256a, 256c and 256b, 256d. Four 
corresponding gripping jaws 258a-d are connected to the lower portion of 
region 257. The jaws are also arranged in corresponding diametrically 
arranged pairs, 258a, 285c and 258b, 258d. 
The chuck 255 may be machined from a block of tool steel or other high 
tensile strength, springy material. The exterior shaping of the chuck, 
with its larger diameter upper end tapering to a central region of 
intermediate diameter, the central region in turn tapering to a relatively 
small diameter at its lower end, may be provided by turning the block 
workpiece on a lathe. The counterbored shank opening 259 may then be bored 
into the chuck. The four respective lever arm and jaw members may then be 
defined by performing a cutting or sawing operation along four lines 
running parallel to the chuck axis and disposed at 90.degree. spacings to 
form the open regions between the respective arms and the respective jaws. 
After the cutting operation, the only connection between the jaws and 
lever arms is provided by the connective fulcrum ring region 257 (FIG. 
13). 
It will be appreciated that the chuck 255 need not be fabricated as a 
unitary element, but could instead comprise separate lever arm elements 
joined in a pivoted assembly, for example. 
In FIG. 13, the diametrically opposed pair of lever arm members 256b and 
256d are shown. The corresponding jaw members 258b and 258d are connected 
to the respective lever arm members by fulcrum region 257. The region 257 
forms a solid ring region surrounding the shank opening formed in the 
chuck, providing a means for connecting the respective jaw and lever arm 
members to form the chuck 255. 
It will be appreciated that the lever arm 256b, viewed as extending 
substantially parallel to the rotor axis from the center connective region 
257 by a distance L, has a center of mass depicted at point A and located 
a distance L.sub.a from the center of region 257. Similarly, the exemplary 
jaw member 258b has a center of mass, again in relation to the center of 
region 257, depicted at point B. The chuck 255 in the disclosed embodiment 
is dimensioned such that the relative distances L.sub.a is about five 
times the length of L.sub.b. 
The chuck 255 is disposed into the bore 162 in rotor 160 and secured in 
place by the bushing 265. A chuck retainer 270 is threaded into the end of 
the rotor to secure the chuck assembly in place. 
The bushing 265 comprises a protruding rim member 265a which seats against 
the shoulder 163 defined at the lower end of the rotor, thereby 
registering the bushing position. The bushing 265 includes a central bore 
267 formed therethrough to receive the shank of the drill bit 300. The 
upper end of the bushing 265 has formed therein a larger bore 268 which 
accepts the intermediate region of the chuck 255. The upper end of the 
bushing 265 is chamfered to provide a tapered surface 269 so as to clear 
the tapered region 261 of the chuck 255. A shoulder 266 is formed in the 
bushing, providing a stop surface for the shoulder 263 of the chuck 255. 
The chuck bushing 265 is seated within bore 162 in axial alignment with the 
rotor shaft. The bit 400 is therefore aligned with the axis of the rotor 
by the cooperative engagement of the bit shank in the bushing 251, with 
the chuck jaws 258a-d and the inner periphery of the bore 267 formed in 
the chuck bushing 265. This cooperative engagement serves to minimize the 
bit runout during operation. 
The centrifugal chuck 255 acts as a passive chuck, with chuck gripping 
forces being derived primarily by the centrifugal forces created during 
high speed rotation of the rotor shaft 160. O-ring 263a is disposed around 
the alignment bushing 251 at the upper ends of the chuck lever arms 
256a-d, urging them outwardly away from the rotor shaft. The lever arms 
256a-d rotate around the fulcrum region 257 of the chuck 255, causing the 
respective jaws 258a-d to pivot inwardly to grip the shank of the bit. 
Since the four jaws comprise diametrically opposed jaw pairs which are 
uniformly spaced around the bit periphery, the bit will be gripped by all 
four jaws 258a-d in a circularly symmetrical manner. A split ring 263b is 
disposed in a circular recess formed in the chuck 255, and frictionally 
engages the periphery of the inserted bit shank, with enough force to 
retain the bit shank with the chuck in the static (non-rotating) 
condition. The O-ring 263a and spring 263b provide a slight gripping force 
sufficient to retain the bit shank in the inserted position shown in FIG. 
13 while the rotor is not spinning at high speed. 
The lever arms 256a-b serve to magnify the centrifugal forces resulting 
from high rotor speeds to provide very substantial jaw gripping forces. 
The relative dimensions of the jaws and lever arms are cooperatively 
selected so that as the rotor spins, the weight of lever arms results in 
an outwardly directed force, as indicated by the arrows shown in FIG. 13. 
In the disclosed embodiment, with the center of mass of the lever arms 
located at a distance from the fulcrum region which is five times the 
distance of the center of mass of the jaws from the fulcrum, the 
centrifugal forces are magnified by a factor of five and exerted against 
the bit shank. In this embodiment, the gripping force exerted by the 
centrifugal chuck action through a single jaw on the drill shank is equal 
to 900 pounds with the chuck rotating at 120,000 rpm. The tremendous 
gripping forces ensures that the drill bit will be securely and 
concentrically gripped during operation. With the passive chuck 
arrangement described above, the bit is very securely held while the rotor 
is at high rpms, when high gripping forces are needed, and is only loosely 
held while the rotor is not rotating. Other advantages of the chuck 
assembly are the automatic alignment of the bit with the axis of the 
rotor, thereby minimizing the bit runout, and the ready removal of the bit 
to change drilling tools. 
The Tool Changer 
Referring now to FIG. 15, a top view of exemplary tool changer 95 is shown. 
The device 95 includes a top plate 305 mounted for sliding movement along 
an axis parallel to the Y axis (FIG. 2). The device 95 further includes 
left and right side members 307 and 310, and end member 312 (more clearly 
shown in FIG. 16). The position of the plate 305 in the Z axis direction 
is maintained by screws 315 extending from above the plate 305 through the 
elongated slots 317 formed in the top plate to a structural member 321 
comprising the tool changer 95 (see FIG. 17). Thus, the screws 315 allow 
sliding movement of the plate 305 along the extents of the slots 317. 
A piston 325 driven by a pneumatic cylinder (not shown) actuates slider 328 
having a rectangular cross-section and fitted within a slot 330 having a 
corresponding rectangular cross-section beneath the top plate 305. A pair 
of upwardly extending pins 332 and 334 are attached to the slider 328, and 
extend through slots 336 and 338, respectively, formed in the top plate 
305. These slots 336 and 338 are angularly offset from the X axis 
direction, so that as the slider 328 is translated back and forth along an 
axis parallel to the Y axis indicated by arrow 340, the pins 332 and 334 
impart a force to the top plate 305 tending to move the plate 305 along an 
axis parallel to the Y axis. In the disclosed embodiment, the slots are 
arranged at an angle of about 30 degrees with respect to the X axis, 
although the exact angular offset is a matter of design choice. 
The tool changer 95 includes a plurality of magazines for accepting clips 
carrying the drilling tools or bits. By utilizing clips which have been 
preloaded with the bits, operator handling of individual bits is 
eliminated, thereby eliminating one primary cause of bit breakage. 
The respective clips are inserted into each magazine along a respective one 
of the elongated slots 347 defined in the top plate 305. An exemplary clip 
350 is depicted in the fully inserted position in the cross-sectional view 
of FIG. 16. The clip 350 comprises an elongated body having a plurality of 
openings 352 formed therein in an aligned relationship for receiving the 
bits 400. The respective magazine is defined by the upper surface of the 
bottom member 320 of the device 95, the structural members 321, the end 
member 312 and the top plate 305. The clip is fed into the magazine from 
the end 251 until the inserted end of the clip abuts the spring-loaded 
plunger 342. The clip is retained against the spring 344 bias by the key 
345, which is in turn spring-loaded by spring 346 against the bottom 
surface of the clip 350. A notch 354 is provided in the clip bottom 
surface to provide a stop shoulder against which the end of the key 
lodges. To remove the clip 350, the system operator manually lifts the 
outer key end thereby releasing the clip to move out of the magazine as a 
result of the bias of the spring 344. 
An important feature of the tool changer 95 is the provision of a means for 
locking and unlocking the bits in the tool changer, thereby preventing the 
bits from being removed or dislodged from the clips unless the access 
means is unlocked, while accommodating the loading of clips holding the 
bits. The locking and unlocking means employs the cooperation of the clip 
350, the bit configuration, and the top plate 305. As shown in FIGS. 16 
and 17, a collar 402 is fitted around each bit and comprises a groove 403 
formed in the outer periphery of the collar. The clip 350 comprises a body 
having an upper surface 356, in which a plurality of aligned apertures 352 
are formed. Each aperture is counterbored to partially receive the collar 
402 of a drill tool or bit 400. The bit is disposed in a clip aperture 
with the collar 403 partially inserted into the counterbored aperture. The 
remaining portion of the collar, including the groove, extends above the 
top of the surface 357. As the clip is inserted into the magazine, the 
groove 403 in each bit collar 402 receives the edge of the elongated slot 
347 formed in the top of the plate 305. The width of each slot is selected 
such that the slot is just wider than the diameter of the collar 402 at 
the groove interior. Thus, with the bits 400 aligned along the 
longitudinal extent of the clip 350, the collars 402 slide along the slot 
347 and are captured by the slot edges 348. 
Each slot 347 comprises six enlarged clearance openings 349 defined 
therein, each opening corresponding to a particular one of the six bits 
400 in the clip 350. In the locked position, the top plate 305 is aligned 
such that the collars 402 of the bits 400 are captured by the slot edges 
348 at the narrowed regions of the slot. The locked position is 
illustrated in FIG. 15. The unlocked position of the plate 305 corresponds 
to the plate position wherein the clearance openings 347 are aligned with 
the axis of the corresponding bit in the clip. In this position, the 
collars 402 are no longer captured by the edges 348 of the slots, and the 
bits are then free to be lifted out of the clip and the tool changer. 
To achieve the unlocked position, the slider 328 is translated to move the 
pins 332 and 334 from the position shown in FIG. 15 to the other end of 
slots 336 and 338 in the direction of arrow 340 in FIG. 15. This 
translating movement results in a force pushing the plate 305 in the 
direction of arrow 341 in FIG. 15. This force slides the plate in the +Y 
direction with the length of the slots 336 and 338 being precisely 
determined to provide the appropriate travel to align the respective axis 
of the enlarged openings 349 with the respective bit axis. 
The tool changers are each mounted for movement along the Z axis, to load 
and unload the bits 400 into the respective drilling spindles. Thus, the 
toolchanger 95 may be raised or lowered along the Z axis by a pneumatic 
cylinder arrangement, comprising cylinder 380 carried by plate 382 secured 
to the top table 70 (not shown in FIG. 16) Piston 384 is actuated by the 
cylinder 380. The end of the piston is secured to mounting plate 385, 
secured to the lower member 320 of the tool changer. By operation of the 
pneumatic cylinder in a manner which is well known to those skilled in the 
art, the tool changer 95 may be raised or lowered to accomplish the tool 
changing functions to be described in further detail hereinbelow. 
Tool Bit and Clip Configuration 
Another aspect of the invention is represented by the tool clip and bit 
configuration shown in the cross-sectional view of FIG. 18. The cover 360 
is adapted to protect the bits 400 in the clip and to secure their 
position during shipment or storage. The clip cover 360 includes a pair of 
inwardly extending ribs 362 which are adapted to capture the bit collar at 
the groove 403 defined in the outer periphery of the collar. The cover 360 
further comprises a pair of downwardly extending ears which engage about a 
corresponding pair of shoulders 358 defined by the grooves 359 in the side 
of the clip body 350. Thus, the cover 360 is secured in position of the 
clip body by the engagement of the ears with the shoulders, nd the ribs of 
the cover engage the collar to capture the bit in the clip. Prior to 
loading the clips 360 into the respective magazines of the tool changer, 
the clip covers 360 are removed. 
Referring now to FIGS. 19 and 20, an alternative embodiment of the tool and 
a corresponding clip configuration are disclosed. The bit 410 comprises a 
groove 415 defined in the shank of the bit. The cutting end of the bit 
transitions to a stop shoulder 417 defined in the bit shank. The clip 420 
is adapted to store drill bits having the configuration of the bit 410. In 
this configuration, the ribs 426 of the clip cover 424 are extended to be 
received within the groove 415 formed in the bit shank so as to capture 
the bit 410. The clip body includes a bore 421 for receiving the cutting 
end of the bit 410, and a stop shoulder 422 formed by counterboring the 
aperture 421 and defining a shoulder surface 422 adapted to provide a stop 
surface for engage the corresponding shoulder 417 of the bit 410. Thus, 
the depth of insertion of the bit 410 into the body of the clip is 
controlled by the depth of the counterbore of opening 421 and the relative 
location of the shoulder 417. 
The tool configuration shown in FIG. 19 may be employed in tool changers of 
the type shown in FIG. 15. To accommodate the alternate clip and bit 
embodiment, the width of each slot 347 is narrowed so that the grooves 415 
in the bit shanks are captured by the edges 348 of the slots 347. To 
operate with the tool configuration of FIG. 19, the chuck assembly 250 is 
provided with an adjustable set screw 430, fitted into the alignment 
bushing 251, to prevent drill slippage into the chuck assembly during tool 
change operations when only static forces are gripping the tool shank. 
System Operation 
Referring now to FIG. 25, a system level block diagram of the control 
system is disclosed. The system comprises a system control unit 505 for 
providing overall control of the various components of the system. In this 
embodiment, the controller 505 comprises a commercially available unit, 
the model 35 controller marketed by Sieb & Meyer, GMBH, West Germany. The 
controller 505 comprises in this embodiment a display, operator controls, 
a keyboard for receiving operator instructions, paper tape reader for 
inputting a program, a spindle select control for direct manual selection 
and control over the drilling spindles, and a paper punch for providing a 
hard copy of a program, in addition to a computer. The particular 
requirements of a given application will dictate to some extent the 
necessary elements of the controller 505. 
The system control unit 505 is coupled to the remaining elements of the 
system by the interface unit 510. Thus, the interface unit 510 is 
connected to the X and Y linear scales 66 and 67, to the X axis and Y axis 
servo motor amplifiers 512 and 516, and to the respective toolchangers 
95-98. This provides the capability of the controller 505 controlling the 
operation of the servo motors 102 and 112 to position the crossbeam 65 and 
work table 70 precisely. Servo motor tachometer units 514 and 518 provide 
feedback of the respective shaft positions of the motors 102 and 112, and 
the linear scales 66 and 67 provide signals indicative of the positions of 
the crossbeam 65 and table 70. 
The spindle control unit 525 is also coupled to the system control unit 
through the interface unit 510. The spindle control unit comprises the 
frequency converters needed to drive the rotary motors of the spindles, 
and the amplifiers needed to drive the linear motors. The spindle control 
unit 525 is coupled to the spindles 81-84 and 85-89 to control the various 
functions carried out by the drilling spindles. 
The spindle position and velocity sensors are indicated by FIG. 25 by the 
reference letters "P" and "V." The rotary drive motors are indicated 
generally by the reference letters "SM," and the Z axis translating means 
(such as the linear motor for the high speed spindles 82-84) are indicated 
generally by the reference "M." The sensor for indicating the rotational 
speed of the spindle rotor is indicated generally by the reference "R." 
As indicated schematically in FIG. 25, the spindle control unit 525 
provides the drive signals to the various spindle motors, and receives 
position, velocity and rotational speed information from the various 
sensors to control the high speed spindles 81-84 in the desired manner. 
The conventional spindles 85-89 are also controlled by the spindle control 
unit 525, and position and velocity information is also fed back to the 
unit 525 for these spindles as well. 
The operation of the high speed drilling system described above is 
controlled by the system control unit. The particular drilling sequence to 
be performed on a particular workpiece is predetermined and the particular 
sequences to be carried out are embodied in instructions which are 
programmed for implementation during operation. Thus, the controller 
instructs the translating means to position the respective workpieces 
under the respective spindles to commence the first drilling bit. The 
control unit 505 is programmed with appropriate instructions to direct the 
spindle control unit to operate the rotary motor driver and the linear 
motor driver to rotate the rotor shaft and the shaft to be translated 
downwardly to drill the hole in the workpieces. To increase the system 
throughput, a plurality of workpieces will be stacked under each drilling 
station to be drilled simultaneously. The various elements of the system 
cooperate to allow the system to sustain hit rates of 300 per minute when 
drilling very small diameter holes for the high speed spindles described 
above. 
The system (shown in FIG. 25) that controls the motion of the drilling 
spindle is an interrelated series of electrical circuits that control the 
velocity and the excursion positions of the mechanism. The linear 
potentiometer or position transducer (P) associated with the spindle 
movement provides the feedback to the electrical circuits and thereby is 
capable of being controlled to computer-generated position requirements. 
The linear velocity transducer (V) provides a feedback signal that is 
indicative of the instantaneous velocity of the mechanism. The spindle 
control unit compares the feedback velocity actual to the 
computer-requested velocity. The result of this comparison is to produce a 
velocity that is equal to the requested velocity. Should any disturbance 
occur in which either the position or velocity is not equal to the 
requested values, the spindle control unit responds with corrective 
amounts of drive to the spindle actuator (motor) to bring the error to 
null. 
The system is prepared for operation by placing the workpieces on the tool 
plates and securing their position by the vacuum hold-down apparatus 
described above. The appropriate tool clips having the drill bits which 
will be used during the drilling operation on the particular workpieces 
are loaded into the tool changer magazines. The mix of bit sizes will 
typically include the small diameter bits for the high speed spindles as 
well as larger diameter bits for conventional drill spindles. 
To load the spindles with a desired tool, the X and Y translating motors 
are operated to position the desired one of the spindles for a drilling 
station over the tool changer for the station. The spindle is positioned 
directly over the particular drill bit to be loaded. With the top plate of 
the tool changer in the locked position, the Z axis pneumatic cylinder for 
the tool changer is actuated to raise the tool changer upwardly, inserting 
the shank of the bit into the chuck of the spindle. The top plate of the 
tool changer is then moved to the unlocked position, releasing the bits in 
the tool changer. The Z axis cylinder is then actuated to lower the 
changer with the bit held in the spindle chuck. With the tool changer 
lowered to a level beneath the work table, the drilling sequence employing 
the loaded bit is then carried out. 
The tool changer may be repeatedly accessed to change tools as required to 
complete the drilling sequence on the workpiece. To unload a bit, the 
loading sequence is simply reversed. 
The invention is not limited to the use of only two spindles per work 
station. As indicated in FIG. 1, a number of spindles may be employed at 
each work station and may even be operated simultaneously if the 
particular drilling sequence permits, i.e., with repetitive sequences. 
In some applications which result in substantial quantities of debris from 
the drilling operations, it may be advantageous to employ the alternate 
embodiment of the crossbeam depicted in FIG. 22-24. It is difficult to 
grind and maintain a sharp edge on the granite crossbeam due to the 
brittleness of granite, and grit or other debris on the guide beams can be 
swedged between the granite surfaces of the guide beams and the crossbeam, 
thereby contaminating the air bearing. The alternative embodiment of of 
the crossbeam solves this problem. In this embodiment, the one piece 
granite crossbeam 65 of FIG. 1 is replaced by a crossbeam assembly 600, 
comprising two pairs of aluminum lower transverse beams 605, 610 and 615, 
620, and a pair of granite crossbeam members 625 and 630. The use of the 
aluminum transverse beams provides a means of readily providing a 
structure having very sharp corners, thereby tending to prevent debris 
particles from becoming swedged between the upper granite surface of the 
guide beams and the bottom surfaces of the aluminum beams. 
One pair of the aluminum transverse beams 605, 610 is shown in the 
cross-sectional view of FIG. 23. Each transverse beam includes two vacuum 
chamber openings extending through the beam thickness, and a plurality of 
air bearing orifices opening from the lower surface thereof. Communicating 
passages are formed within the transverse beams to supply pressurized air 
to the orifices. Only vacuum chambers 605 and 611 and orifices 607 are 
visible in FIG. 23. One pair of transverse beams 605, 610 is situated for 
translation above the guide beam 60, and the second pair of transverse 
beams 615, 620 is situated for translation above the second guide beam 62. 
FIG. 24 is a side cross-sectional view showing the manner in which the 
transverse beams fit together with the granite crossbeam members 625 and 
630. As shown in this view, the transverse beam 620 comprises lower planar 
regions 621a, 621b which are supported above the guide beam 62 by the air 
bearing created by the air supplied from orifices 624. The sharp corners 
623a and 623b serve to prevent debris from being swedged between the upper 
surfaces of the granite guide beam 60 and 62 and the planar regions 621a 
and 621b of the transverse beams. The upper surface of the transverse beam 
620 includes relieved areas into which the granite crossbeam members 625 
and 630 are fitted. The transverse beam 620 comprises two vacuum chambers 
622a and 622b, air passages 624a and orifices 624b fitted into the 
passages. The air passages are coupled to a source of pressurized air (not 
shown). 
The crossbeam members 625 and 630 each comprise two pairs of vacuum 
chambers, one pair situated above and communication with the corresponding 
vacuum chambers formed in the respective transverse beams. Each chamber 
extends through the thickness of the crossbeam. A slot is formed in the 
upper surface of the crossbeam to extend between the vacuum chambers of 
each pair to form an elongated vacuum chuck. The respective pairs of 
vacuum chambers and elongated slots provide a powerful preload force 
tending to draw the top table 70 and the guide beams 60 and 62 together. 
Each of the crossbeams 625 and 630 are also provided with air bearing 
orifices and connecting passages to supply pressurized air to support the 
table 70 above the beams 625 and 630 in the same manner as described above 
for crossbeam 65. 
Thus, the beam member 625 shown in FIG. 23 comprises vacuum chambers 626 
and 627 respectively aligned with chamber 606 in transverse beam 605 and 
chamber 611 formed in transverse beam 610. Orifices 628b are fitted in 
passages 628a to provide an upper air bearing supporting the work table 
70. 
The alternate crossbeam assembly depicted in FIGS. 22-24 provides several 
advantages. The assembly comprising the two pairs of aluminum transverse 
beams and the two crossbeam members is substantially lighter in weight 
than the one-piece granite crossbeam 65 of FIG. 1. Sharp corners may be 
readily formed at the lower sliding surfaces of the aluminum transverse 
beams, tending to prevent debris particles from being swedged between the 
guide beams and crossbeam sliding surfaces and thereby contaminating the 
air bearing between the two surfaces. 
For example, the preloading of the wok table in opposition to the air 
bearing lift forces may be employed in split-axis machine tool systems, in 
which the work table is translated along one axis (e.g., the X axis) and 
the tool head such as a drilling spindle is mounted for translation along 
a second axis (e.g., the Y axis). In a split axis drilling system the 
drilling head is also conventionally mounted for translation along the Z 
axis to feed the drill tool into and out of the workpiece. Thus, in such a 
split axis system a preloading force may be applied between the work table 
and its guide beam. A second preload force could be applied to oppose the 
bearing allowing spindle or tool head translation along the Y axis. While 
the invention has been described in the context of a high speed drilling 
system, it will be apparent that many aspects of the invention are not 
limited to drilling systems per se, but may be employed in other machine 
tool applications. These aspects include, by way of example only, the 
positioning system and the vacuum hold-down apparatus. 
It is understood that the above-described embodiment is merely illustrative 
of the many possible specific embodiments which can represent principles 
of the present invention. Numerous and varied other arrangements can 
readily be devised in accordance with these principles by those skilled in 
the art without departing from the spirit and scope of the invention.