Patent Abstract:
A spindle capable of operation at 200,000 revolutions per minute (RPM) with a reciprocating shaft design to minimize the moving mass. The spindle has a ceramic spindle shaft to decrease the moving mass and increase the shaft stiffness for better dynamic stability. The spindle employs a built-in linear motor to provide direct drilling motion to move the shaft along the axis, and a permanent magnet DC brushless motor to rotate the spindle shaft. The linear motor is coupled to the shaft by a combination of an air bearing and a magnetic thrust bearing to reduce the size of the thrust area for better dynamic stability and reduction in stresses of material. A double gripping centrifugal chuck is mounted in the hollow ceramic shaft, and reduces drill bit runout.

Full Description:
CROSS-REFERENCE TO RELATED APPLICATION 
     This application is a continuation of application Ser. No. 09/158,385, filed Sep. 22, 1998, now U.S. Pat. No. 5,997,223. 
    
    
     TECHNICAL FIELD OF THE INVENTION 
     This invention relates to high speed drilling systems for precision drilling of work pieces such as printed circuit boards and the like, and more particularly to systems for drilling very small diameter holes in such work pieces at high speed. 
     BACKGROUND OF THE INVENTION 
     Printed circuit boards are typically populated with many surface-mounted circuit devices. Many small holes are formed in the boards to interconnect the layers of the circuit board. Printed circuit boards are also populated with other types of devices which also need holes formed in the boards. 
     Drilling machines are typically used to drill the holes in the printed circuit boards. One exemplary type of system is described in U.S. Pat. No. 4,761,876, the entire contents of which are incorporated herein by this reference. 
     There has been a dramatic increase in the hole count on printed circuit boards, which makes the cost of drilling the holes a significant part of the total production cost. In addition, hole sizes are getting smaller. Small drills are more expensive and can not be fed with the same velocity as larger drills. Due to this fact, drilling time and cost are further increased. 
     To increase the throughput, higher drill bit rotation rates can be employed. However, there is a limit on the spindle rotation rate, which is due to the effect of the large centrifugal forces acting on the spindle rotors at very high rotation rates. Typically, the spindle is fabricated as a solid rod of steel, which will have a growth in the rotor diameter due to centrifugal force at very high rotation rates. Because the rotor typically is supported on air bearings with relatively small gaps between the bearing structure and the rotor, the growth in the rotor diameter will close or significantly narrow these bearing gaps, leading to seizure of the rotor in the bearings. 
     Drilling spindles typically use a chuck such as a centrifugal chuck to grip the drilling tool while it is being rotated. Centrifugal chucks are advantageous since the tool can be changed without mechanically operating a release mechanism, as there is no gripping centrifugal force when the chuck is not rotated. Small drill applications can have very small drill bit runout tolerances, which can be difficult to achieve with centrifugal chucks in a single grip configuration. 
     It would therefore represent an advance in the art to provide a spindle capable of extremely high drilling speeds. 
     It would also be an advantage to provide a centrifugal chuck capable of gripping tools with significantly reduced run-out. 
     SUMMARY OF THE INVENTION 
     This invention provides many advantages and features. One aspect of the invention is a spindle capable of operation at 200,000 revolutions per minute (RPM) with a reciprocating shaft design to minimize the moving mass. Another aspect of the invention is a double gripping centrifugal chuck for a drilling spindle to reduce drill bit run-outs. 
     In accordance with a further aspect of the invention, a combination of an air bearing and a magnetic thrust bearing is employed to reduce the size of the thrust area for better dynamic stability and reduction in stresses of material. 
     A drilling spindle in accordance with another aspect of the invention includes a ceramic spindle shaft to decrease the moving mass and increase the shaft stiffness for better dynamic stability. The spindle employs a built-in linear motor to provide direct drilling motion, and a permanent magnet DC brushless motor to rotate the spindle shaft. 
     In one exemplary embodiment, a high speed drilling spindle in accordance with the invention includes a spindle body, a rotatable rotor shaft supported within the spindle body for high speed rotation about a rotor axis. The rotor shaft is fabricated of a ceramic material capable of withstanding centrifugal forces exerted during high rotation rates without significant diametrical growth of the rotor shaft. A rotary air bearing supports the rotor shaft for high speed rotation with low frictional drag within the spindle body. A rotary drive system imparts rotational drive forces to the rotor shaft so as to rotate the shaft on the rotary bearing at high speeds. A linear drive system imparts an axially directed drive force to the rotor shaft to perform drilling movements. A thrust bearing couples the linear drive system to the rotor shaft, and includes an air bearing and a magnetic thrust bearing. 
     The rotary drive system includes a DC brushless permanent magnet motor, with a permanent magnet mounted within an opening formed in the rotor shaft. 
     The spindle includes a centrifugal chuck mounted in the rotor shaft, holding a tool having a tool shank in place during high speed rotation to perform tool operations. 
    
    
     BRIEF DESCRIPTION OF THE DRAWING 
     These and other features and advantages of the present invention will become more apparent from the following detailed description of an exemplary embodiment thereof, as illustrated in the accompanying drawings, in which: 
     FIG. 1A is a side cross-sectional view of a drilling spindle in accordance with aspects of this invention. 
     FIG. 1B is a partial cross-sectional view of the spindle of FIG. 1A, rotated with respect to FIG.  1 A and showing elements of the linear motor in further detail. 
     FIG. 2 is a schematic view illustrative of general magnetic elements of the motor providing the rotary drive for the drilling spindle of FIG.  1 . 
     FIG. 3 is a functional block diagram of the spindle and the ancillary system elements for operating the spindle. 
     FIG. 4 is an isometric view of a centrifugal chuck comprising the spindle of FIG. 1 showing the forward end of the chuck. 
     FIG. 5 is an isometric, partially broken away view of the centrifugal chuck of FIG.  4 . 
     FIG. 6 is an isometric view of the centrifugal chuck, showing the inward end of the chuck. 
     FIG. 7 is a partially broken-away isometric view of the front end of the centrifugal chuck. 
    
    
     DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS 
     The Spindle 
     FIG. 1 is a side cross-sectional view of an exemplary drilling spindle  50  embodying aspects of the present invention. The spindle includes a spindle housing  52 , which in an exemplary embodiment is stationary in a rotational sense. The spindle  50  is typically mounted on an overhead beam or gantry, in the manner illustrated in U.S. Pat. No. 4,761,876. A work piece is positioned on a work table below the gantry, which is moved relative to the spindle by an X-Y positioning system. In this embodiment, the spindle is fixed in the X-Y sense, although in other applications, it can be moved in the X-Y as well as Z directions to provide relative motion to position the spindle and the work piece and for other functions such as tool changing. 
     A reciprocating spindle shaft  60  is mounted within the spindle body  52 , and is rotatable, by a rotary drive system, and axially movable, by a linear drive system, to advance/retract the shaft along the spindle axis  54 . The shaft is shown in the advanced, down position in FIG.  1 . Instead of being fabricated of a steel, the shaft is fabricated of a material which is very stiff and which has significantly less diametric growth than a steel shaft at high shaft revolution rates. In this exemplary embodiment, the reciprocating shaft  60  is fabricated of a ceramic material to obtain a shaft of high stiffness (high Young&#39;s modulus), relatively low weight, and low diametric growth at high revolution rates. An exemplary ceramic material is the product UL 600 of Coors Ceramic Company, 600 Ninth Street, Golden, Colo. 80401, which is believed to be 96% alumina, with a Young&#39;s modulus value of 44 million, and which is fabricated to produce a sintered alumina ceramic tube. In contrast, tool steel has a typical Young&#39;s modulus value on the order of 30 million, and so the ceramic tube is much stiffer. Ceramic tubes suitable for the purpose can be fabricated by those skilled in the industrial ceramics art. 
     In one exemplary embodiment, the shaft is a hollow tube having an outer diameter of 0.7 inch, an inner diameter of 0.5 inch, and a length of 6 inches. This tube has a typical weight of 0.3 pound, in contrast to an all metal shaft which could weigh 0.75 pounds or more. The shaft is reciprocated along the shaft axis in the spindle through a range of 0.4 inch. A conventional spindle with a non-reciprocating shaft, requiring the entire spindle to be moved up/down, can weight 12-20 pounds. 
     The shaft  60  is captured in two radial air bearings  70 ,  72 . The first air bearing  70  is at the front (distal) end  62  of the shaft. The second air bearing  72  is at the back (interior) end  64  of the shaft. Air bearing  70  is supplied with pressurized air from an air supply connected at port  74 , through passageway  70 A and transverse openings including openings  70 B,  70 C formed in the body and extending radially about the shaft opening. Air bearing  72  is supplied with pressurized air from an air supply connected at port  122 , through passageway  72 A and transverse openings including openings  72 B,  72 C formed in the body and extending radially about the shaft opening. The radial air bearings support the shaft  60  during rotation and also allow it to move up and down along the rotating axis  54 . 
     The ceramic shaft  60  is a hollow tubular shaft, with a hole  62  running through its center. A centrifugal chuck  150  is mounted in a steel sleeve  148  attached in the front end of the shaft within the hole  62 . The function of the sleeve is to distribute local stresses and prevent fracturing of the ceramic shaft  60 . The sleeve can be very lightly pressed into place within the hole  62 , or preferably secured in place by epoxy. 
     In accordance with an aspect of the invention, the shaft  60  is supported for rotation at rates which can exceed 200,000 revolutions per minute. The shaft is driven by a rotary drive system comprising a DC permanent magnet brushless motor  80 . In accordance with another aspect of the invention, the motor includes a rare earth permanent magnet  82  mounted in the middle of the shaft  60  within the hole  62 , and preferably secured in place by epoxy. The permanent magnet DC motor  80  further includes a stator circuit  84  mounted in the bore of the spindle housing  52  between the radial air bearings  70 ,  72 . The stator circuit  84  includes a plurality of stator structures  84 A each having a stator winding  84 B wound thereon. The magnet  82  has formed therein axially aligned north and south poles. A DC motor driver provides excitation signals to the stator windings  84 B, setting up electromagnetic fields which act on the magnet  82 , imparting a rotational force to the magnet and thus to the shaft. 
     FIG. 2 is a schematic view illustrative of general magnetic elements of the rotary drive motor  80 . In this schematic end view, the north and south poles of the magnet  82  are represented as N and S, respectively. The stator lamination structures  84 A and the windings  84 B are depicted schematically. As shown therein, the magnet  82  is disposed within the opening in the hollow shaft tube. A metal sleeve (not shown) could be used to line the inside of the shaft tube in the region in which the magnet is positioned. This exemplary form of motor is a 2-pole, 3-phase motor, although other types of electrical motors could alternatively be employed. 
     It is noted that rare earth magnet DC brushless motors are generally known in the art, as well as techniques for driving the motors. The placement of the magnet within a hollow spindle shaft is not known. At high rotation rates, the magnet will tend to have diametrical growth due to the high centrifugal forces exerted on the magnet during rotation. If the magnet were to be placed on the external periphery of the shaft, this diametrical growth could lead to magnet damage or seizure of the rotor. However, the ceramic shaft  60  is stiff enough to withstand the centrifugal force without a significant diametrical expansion, and to hold the magnet within the shaft opening. 
     Again referring to FIG. 1A, a steel thrust plate  88  is attached at the back end of the shaft  60 , e.g. by epoxy. The plate  88  defines a flange  88 A having a diameter larger than the outer diameter of the shaft  60 . The purpose of the flange is to prevent the shaft  60  from sliding out of the spindle body. The flange  88 A will contact the air bearing structure to provide a lower travel stop on the axial movement of the shaft. 
     The spindle  50  thus comprises a shaft assembly  90  with several components, including the hollow ceramic shaft  60 , the centrifugal chuck  150  for holding the drill bit, the permanent magnet  82  to provide rotation to the shaft, and the thrust plate  88 . The thrust plate  88  accepts the Z-axis driving motion applied to the shaft  60  through a thrust bearing  100  from the linear drive system  110 . The thrust bearing  100  includes a thrust bearing slider  104 . 
     The thrust bearing  100  provides the combination of a magnetically-attracted and an air-pressure-repelled thrust bearing in this embodiment to reduce the area required for the thrust bearing. This reduction in the thrust bearing area decreases the stress level in the thrust bearing flange  88 A. The thrust plate  88  is attracted toward a magnet plate  102  installed in the forward end of the thrust bearing slider  104 , and repelled at the same time by an air thrust bearing  106  built into the magnet plate  102 . Air pressure between the magnet plate  102  and the thrust plate  88  creates a gap at interface  108  between these two components and allows the shaft  62  to rotate in respect to the thrust bearing slider  104  which does not rotate. The magnet plate  102  is a permanent magnet structure. The air bearing  106  is supplied by pressurized air at port  122 . 
     The thrust bearing slider  104  is captured in two radial air bearings  104 B,  104 C which keep it in position and allow up and down reciprocating motion to drive the spindle shaft  60  and the drill bit into the work piece. This motion is generated by the linear motor  110  attached to the back of the spindle. 
     The drive system  110  includes a linear motor comprising a motor coil structure  112  formed in a cup-like configuration, with coil windings  112 A and  112 B wound about the periphery of the cup-like structure, as shown in FIGS. 1A and 1B. In an exemplary embodiment, the coil structure  112  is fabricated of aluminum, and is cooled by air. The thrust bearing slider  104  is attached to the coil structure  112  by fasteners  104 A, and is provided with an anti-rotation device which is attached to the linear motor coil  112 , and interacts with the wall of linear motor adapter  114 . The anti-rotation device is a pin  115  which slides in a slot  117  formed in the linear motor housing. A pair of TEFLON (TM) dowels is disposed on either side of the pin within the slot to guide the pin in the slot. The pin  115  extends from the coil structure which rides up/down within a slot formed in the adaptor housing. 
     A linear motor magnet assembly  116  is attached by a clamping device  118  into the linear motor adapter  114 , which is secured at the upper end of the spindle housing structure  52 . The magnet assembly  116  includes an iron cylinder  116 A, and iron core elements  116 B,  116 C supported inside the cylinder  116 A, which sandwich permanent magnets  116 D and  116 E. The magnet assembly  116  is stationary, while the coil structure  112  moves axially along axis  54  within a gap between the cylinder  116 A and the sandwiched iron core elements  115  and magnets  116 C in response to linear motor drive signals applied to the coil windings. In this exemplary embodiment, the linear motor provides an axial range of movement to the shaft of 0.4 inch, although other applications may require different movement ranges. The excitation drive signals to the linear motor are provided on a set of leads  119  which are coupled to the linear motor driver. 
     Air to all air bearings is distributed to fittings at port  122 . Cooling water is also distributed through input fitting  124 , into the spindle body and output through output fitting  126 , and is routed within passageways  128  within the spindle body around the air bearings end to the DC permanent magnet brushless motor  80  to keep the spindle at constant temperature. 
     FIG. 3 is a functional block diagram of the spindle  50  and the ancillary system elements for operating the spindle. These ancillary elements include a controller/motor driver system  30  which generates the motor drive signals for the rotary drive motor  80  and for the linear drive motor  110 . A pressurized air supply  32  is connected to the spindle housing to supply the air bearings. A recirculating coolant supply is also connected to the spindle housing to circulate a liquid coolant through the spindle housing. 
     The Centrifugal Chuck 
     The centrifugal chuck  150  is illustrated in further detail in FIGS. 4-7. The centrifugal chuck  150  holds the drill bit  10  in place during drilling operations, and is designed to provide the capability to grip the drill shank  12  at two points  152 ,  154  which are separated along the axis of rotation of the tool shank. Engaging the shank at two points guarantees parallelism of the shank to the axis of rotation. 
     The chuck  150  is designed in the form of a uni-body flexure which has two gripping segments  160  and  170 , the first  160  at the front and the second  170  at the back of the chuck  150 . Each gripping segment includes four weights which are joined by flexures to form a uni-body construction. Thus, the first gripping segment  160  includes four weights  162 A,  162 B,  162 C and  162 D which are joined adjacent a gripping end by flexures  164 A,  164 B,  164 C and  164 D. The second gripping segment  170  includes four weights  172 A,  172 B,  172 C and  172 D which are joined by flexures  174 A,  174 B,  174 C and  174 D. The joining flexures are disposed well away from the longitudinal center of mass of the respective weights, permitting movement of the weights in a pivoting action in response to centrifugal forces. 
     The front and back gripping segments are connected with each other by four thin wall flexures  180 A,  180 B,  180 C and  180 D. Each weight, when exposed to the spindle rotation, is subjected to centrifugal force which moves it outward. It then rotates around a pivot point defined by a ring of metal protruding from the flexures joining the four weights of each gripping segment, and rests against the interior sleeve  148  fitted into the bore in the spindle shaft. During this motion the gripping end of the weight is closing on the shank  12  of the drill bit  10  to apply force on the drill shaft to provide the drilling torque for the drill bit and to overcome drill bit resistance when entering the material. Thus, for example, weight  162 A has a weighted end  162 A 1  and a gripping end  162 A 2 . The weighted end  162 A 1  moves outwardly in response to centrifugal force, pivoting about the ring  165  at flexures  164 A,  164 B to apply leverage force to move gripping end  162 A 2  inwardly against the shank  12 . The ring surface protrudes slightly, by a few thousandths of an inch, from the exterior surface of the chuck. Similarly, exemplary weight  172 C (FIG. 6) has a weighted end  172 C 1  and a gripping end  172 C 2 . The weighted end  172 C 1  moves outwardly in response to centrifugal force, pivoting about the ring  175  flexures  174 C,  174 D to apply leverage force to move gripping end  172 C 2  inwardly against the shank  12 . The other weights operate in a similar fashion. 
     The chuck is fabricated from a block of tool steel, which is machined to produce the uni-body chuck structure. 
     A rubber O-ring  192  is installed into a groove  194  of the front segment of the chuck to frictionally engage the shank  12 , which keeps the drill bit in the centrifugal chuck when it is not rotating. The front ring  165  has a slightly larger outer diameter (by, e.g., 0.1 inch) than the outer diameter of the ring  175 , and is pressed into the sleeve  148 . The back segment of the chuck, at ring  175 , has a slip fit into the sleeve  148  to allow it to float in the bore when actuated. Behind the chuck  150  is a disk  200  with a threaded hole in the center which allows chuck removal without damage. 
     The front segment  160  of the chuck  150  is pressed into the sleeve in the spindle shaft and the bore of the chuck is ground on the assembly to guarantee concentricity of the drill shank with the axis of rotation. The front of the chuck is secured by a wire ring  196  (FIG. 1) located in a groove  198 , which prevents the chuck from being forced out of the spindle nose. 
     The chuck can be removed from the rotor shaft by inserting a threaded shaft into the chuck and threading it into the chuck removal disk and then applying force outwardly to the shaft. The disk in that condition is applying force to the chuck and forces it out of the bore of the spindle shaft. 
     The grip on the drill shank is increasing with the increase of the rpm and it is strongest on the highest rpm. The grip on the drill shank is adequate to be able to rout with 0.062 diameter router in a three high stack of boards each 0.062 thick. 
     It is understood that the above-described embodiments are merely illustrative of the possible specific embodiments which may represent principles of the present invention. Other arrangements may readily be devised in accordance with these principles by those skilled in the art without departing from the scope and spirit of the invention.

Technology Classification (CPC): 1