US3145023A - Card-feeder mechanism - Google Patents

Card-feeder mechanism Download PDF

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Publication number
US3145023A
US3145023A US203259A US20325962A US3145023A US 3145023 A US3145023 A US 3145023A US 203259 A US203259 A US 203259A US 20325962 A US20325962 A US 20325962A US 3145023 A US3145023 A US 3145023A
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United States
Prior art keywords
card
leaf
picker knife
stack
cards
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Expired - Lifetime
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US203259A
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English (en)
Inventor
Gustave D Cerf
Krakinowski Morris
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Unisys Corp
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Sperry Rand Corp
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Priority to NL294207D priority Critical patent/NL294207A/xx
Application filed by Sperry Rand Corp filed Critical Sperry Rand Corp
Priority to US203259A priority patent/US3145023A/en
Priority to FR935871A priority patent/FR1366839A/fr
Priority to GB23320/63A priority patent/GB986961A/en
Priority to CH741163A priority patent/CH403363A/de
Application granted granted Critical
Publication of US3145023A publication Critical patent/US3145023A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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    • G—PHYSICS
    • G06—COMPUTING OR CALCULATING; COUNTING
    • G06K—GRAPHICAL DATA READING; PRESENTATION OF DATA; RECORD CARRIERS; HANDLING RECORD CARRIERS
    • G06K13/00—Conveying record carriers from one station to another, e.g. from stack to punching mechanism
    • G06K13/02—Conveying record carriers from one station to another, e.g. from stack to punching mechanism the record carrier having longitudinal dimension comparable with transverse dimension, e.g. punched card
    • G06K13/08—Feeding or discharging cards
    • G06K13/10—Feeding or discharging cards from magazine to conveying arrangement
    • G06K13/103—Feeding or discharging cards from magazine to conveying arrangement using mechanical means

Definitions

  • a card-feeder incorporating a picker knife suspension which is free of sliding friction, avoids critical tolerances, is simple and inexpensive to make and maintain, requires no lubrication or adjustment, is resistant to failure, and alleviates backlash.
  • the card-feeder must not only operate at high speeds; it must do so while simultaneously providing a reliable card feed which does not skip or damage the cards. Accordingly, it is a further object of this invention to provide a card-feeder which is reliable at high speeds, and is not subject to misfeed or card-mutilation.
  • Still further objects of this invention are to provide a card-feeder picker knife mechanism which is of low mass, and which provides accurate control of the card-feeding trajectory.
  • a material-advancing mechanism comprising a support, at least one flexible mounting member secured to the support and projecting in a selected direction therefrom, and a material-advancing device mounted on the projecting part of the mounting memher, the latter being sufliciently bendable to permit the material-advancing device to move relative to the support through a material-advancing motion in a direction trans verse to the selected direction.
  • FIG. 1 is a side elevational view, with parts in section, of a card-feeder and picker knife mechanism in accordance with this invention
  • FIG. 2 is a rear elevational view of the aforesaid mechanism
  • FIGS. 3 to 6 are a sequence of fragmentary side elevational views, similar to that of FIG. 1, illustrating the aforesaid mechanism in various consecutive positions of its operating cycle;
  • FIG. 7 is a geometric diagram illustrating certain features of the aforesaid mechanism
  • FIG. 8 is a rectangular coordinate graph illustrating further features of the aforesaid mechanism.
  • FIGS. 1 and 2 show a portion of a card-handling machine including a gravity feed card hopper 10 having a front wall 12 and a pair of side walls 14.
  • This hopper is designed to hold a stack of up to some maximum number of data-tabulating cards C, the individual cards each lying substantially horizontally and the stack rising substantially vertically within the hopper 10.
  • the bottom of the hopper is substantially open, thus exposing the lowermost card C
  • the hopper 10 includes a throat plate 16 upon which the forward part of the stack rests, and the rearward part rests upon a picker knife 18, which is bifurcated as seen in FIG. 2.
  • a pair of counter-rotating feed rollers 20 which cooperate to deliver the cards C one-by-one to another location (e.g. the operating station, not shown, of the card-handling machine). Such delivery occurs after a card is initially moved out of the stack and into the grip of the rollers 20.
  • each half of the latter has a blade in the form of a slight step 18a formed in its upper surface 18b, 0.
  • the vertically rising wall of the step 18a faces forwardly and constitutes a card-edge-engaging surface which, upon forward motion of the picker knife 18, abuts against the rear edge of the lowermost card C as seen in FIG. 3, and drives that card forwardly through an appropriately positioned exit space 22 between the lower edge of the hopper front wall 12 and the throat plate 16, and on out of the hopper 10, as seen in FIG. 4, until it eventually meets both the feed rollers 20, as seen in FIG.
  • This stroke of the picker knife is continuously re peated, and on each cycle thereof the card which is then in the lowermost position C is moved out of the stack of cards C, after which the remainder of the stack in the gravity feed hopper 10 drops down and the process is repeated in this manner for each following card.
  • a weight 24 may be placed on top of the card stack to assure that there is always enough pressure to keep the cards C moving down through the hopper 10, and also to press the individual cards flat so that they mate properly with the blade 18a and with the exit opening 22.
  • the height of the blade 18a is slightly less than the thickness of a standard data card, while the height of the exit opening 22 is between one and two such thicknesses.
  • the structure for mounting the picker knife 18 and driving it through its card-moving stroke includes a sup port 30, which may be part of the frame of the larger card-handling machine.
  • This support is formed with a flat clamping surface 30a, to which the lower end of a member 32 is clamped by means of a clamping bar 34 and several bolts 36.
  • the member 32 is a flexure spring consisting of a flat, flexible metal leaf, the elongated upper portion of which rises free of the support 30 and carries the picker knife 18, which is secured to the upper tip thereof by several bolts 38.
  • the broader dimensions of the leaf 32 define a relatively flat plane which is substantially vertically oriented, and thus is practically perpendicular to the forward, substantially horizontal direction of the picker knife stroke.
  • the free upper portion of the leaf 32 can be bent elastically in either direction, essentially perpendicular to the plane defined thereby, i.e. forwardly and backwardly, to allow the picker knife 18 a latitude of movement in those directions, while acting as a kind of guide in that it limits motion parallel to the plane defined thereby, i.e. Vertically and also sidewardly (with respect to the view of FIG. 2).
  • the leaf 32 thus provides a dynamic suspension and guide for the moving picker knife 18, yet the strictly fiexural movement of this suspension is entirely free of sliding friction, and it makes unnecessary any linkages, pivots, rails, or other types of guides inherently subject to sliding friction.
  • the picker knife suspension of this invention is better able to Withstand high speed picker knife operation, Without any lubrication or adjustment of the leaf 32.
  • this leaf has a simpler shape than most linkages, rails, guides, etc. and does not require as close tolerances as such structures generally do, so that it is easier and less expensive to manufacture; simply stamping the required leaf shape from a sheet of suitable thickness and composition suffices.
  • the fact that the mounting leaf 32 is firmly bolted both to the support 30 and the picker knife 18 means that there can be little looseness and backlash in this suspension, as compared to structures employing various kinds of movable joints.
  • cam-follower assembly including a double-ended stub shaft 40 secured to the leaf 32 just below the picker knife 18 by several bolts 42, and a pair of cam-follower rollers 44 rotatably mounted at either end of the stub shaft 40. Acting against these cam-follower rollers 44 to cycle the picker knife 18 through its card-moving stroke are a pair of cams 46 fastened to a cam drive shaft 48 powered by the conventional main drive (not shown) of the card-handling machine. Under the influence of this cam drive, the picker knife 18 and its mounting leaf 32 are repeatedly reciprocated forwardly and rearwardly through the successive operating positions illustrated by FIGS. 1 and 3 to 6, in that order.
  • the leaf 32 is sufiiciently springy and resilient so that it inherently provides the restoring spring force which forces the camfollower rollers 44 against their drive cams 46 and thereby returns the driven cam-follower, picker knife, mounting member assembly forwardly after each rearward driving stroke of the cams.
  • the leaf 32 is sufiiciently springy and resilient so that it inherently provides the restoring spring force which forces the camfollower rollers 44 against their drive cams 46 and thereby returns the driven cam-follower, picker knife, mounting member assembly forwardly after each rearward driving stroke of the cams.
  • the leaf In order for the leaf to provide adequate spring restoring force through all phases of its cycle of reciprocation, including the phase of minimum flexure, it is maintained in a flexed condition over the entire range of its operating stroke.
  • the clamping surface 30a is slanted forwardly so that the part of the leaf 32 immediately adjacent the support is aimed too far forward.
  • cam drive 46, 48 is positioned in front of the leaf 32, but located far enough back to keep the latter flexed rearwardly (and thus exerting a restoring force) even at the forward limit of the card-moving stroke (FIG. 6).
  • the leaf is made substantially in the form of an isoceles triangle having its base at the lower end and its apex 50 at the upper end, as shown by the dashed lines superimposed on FIG. 2.
  • the only variations from the triangular shape are the tabs 32a added where necessary for fastening to the support 30, picker knife 18, and cam-follower shaft 40.
  • the purpose of this shape is to concentrate the mass of the leaf 32 as much as possible toward the immobilized lower end thereof. This more evenly distributes the flexing stresses over the length of the leaf 32, and reduces the amount of mass which must be moved back and forth over the greater distances traveled by the free upper end of the leaf.
  • the effective mass of the leaf 32 may be considered the approximate equivalent of a mass one-fifteenth the actual mass of the leaf, but concentrated at the apex 5th of the triangle.
  • the masses of the picker knife 18, cam-follower assembly 40, 44, and their respective fasteners 38 and 42 are so placed as to center about a horizontal line passing through the triangle apex 5%.
  • the cam-follower shaft 40 is formed with a flat surface 40a abutting against the front surface of the leaf 32 such that the axis of rotation of the rollers 44 coincides with that surface, further simplifying the design considerations. These factors are also helpful in minimizing any tendency toward harmonic vibration.
  • the first requirement, illustrated by FIG. 1, is that the rearward limit of the picker knife trajectory be far enough back so that the blade 18a moves behind the rear edge of the card C and will then be in position to catch such edge as the earns 48 rotate past the position of FIG. 1 and the spring action of the leaf 32 drives the picker knife 18 forwardly to the position of FIG. 3. As this forward stroke continues to the position illustrated by FIG. 4, it is necessary that the blade 18a remain in engagement with the rear edge of the card C in order to prevent misfeed.
  • FIG. 5 depicts the moment when the card C has just been moved into contact with the feed rollers 20. From this moment on, the feed rollers will take over the job of moving the card C therefore it is highly desirable that at such time the picker knife 18 drop below the level of the card C in order to disengage the blade 18a from the rear edge thereof.
  • the diagram of FIG. 7 illustrates these design requirements geometrically.
  • the straight line 60 represents the plane of the clamping surface 3t note that it is slanted at an angle 62 to the vertical line 64.
  • Point 66 represents the point at which the leaf 32 emerges from between the clamping surface 30 and the clamping bar 34 and begins to curve.
  • the curved lines L and L represent the curvatures of the leaf at the key operating positions of the respective correspondingly numbered FIGS. 1 and 3-6.
  • line L represents the rearward limit position of FIG. 1
  • lines L represents the intermediate positions of FIGS. 3 to 5 respectively
  • line L represents the forward limit position of FIG. 6.
  • the curve 70 represents the trajectory of the blade 18a, and the points P and P therealong represent the location of the blade at the phases of operation illustrated by the respective correspondingly numbered FIGS. 1 and 3 to 6.
  • the straight line 72 represents the orientation of the lowermost card C This line intersects the blade trajectory curve 70 at point P where the blade first engages the rear card edge (the position of FIG. 3). Be tween that point P and the point P (the initial position of FIG. 1) the blade trajectory curve 70 rises up to meet the card line '72. The blade trajectory curve 70 then continues to rise after passing the initial engagement point P and thus goes above the card line 72 to achieve the slight lift which improves the firmness of card-engagement and thus the reliability of the feed. At point P (the position of FIG.
  • the blade trajectory curve 70 again intersects the card line 72, heading downward, and the blade thus desirably disengages from the card edge to prevent card damage, subsequently continuing forward to point P (the position of FIG. 6).
  • point P the position of FIG. 6
  • a line 74 which is tangent to the blade trajectory curve 70 is also parallel to the card line 72.
  • the card C is fed along the line 72 until it meets the feed rollers 20 at point 76.
  • a card orientation 72 which is tilted down toward the feed rollers 20 at an angle 78 to the horizontal 80.
  • Such a card orientation is achieved by mounting the throat plate 16 an appropriate distance below the level of the front upper surface 18b of the picker knife 18.
  • Prior picker knife mechanisms were generally designed so that the various linkages, pivots, rails, and other guides thereof imparted a linear trajectory to the picker knife.
  • the present flexure spring suspension structure in contrast, inherently involves a curved picker knife trajectory 70 because of the vertical displacement which the free upper end of the leaf 32 undergoes when the leaf flexes during the horizontal reciprocation of the picker knife 18. This fact presents an opportunity to select the curved path 70 which will provide the superior trajectory described above, including the advantageous rise and fall features discussed.
  • a standard engineering text on small deflection theory such as Elements of Strength of Materials, by Timoshenko and Young, 4th edition, 1962, D. Van Nostrand Company, Inc., pp.
  • M is the bending moment experienced by the beam at the point P; E is the modulus of elasticity of the beam material; and I is the moment of inertia of the beam at point P.
  • the expression is Equation 5.4, Timoshenko and Young, p. 114-, which is there derived from a general definition of moment of inertia that is true for all cases, whether or not there is pure bending.
  • the next step is to show that the curvature M/EI is constant.
  • B the modulus of elasticity, is constant for a given material.
  • M and I are both variable, depending on the location of the point P.
  • the ratio M/I remains nearly constant over the length of the leaf 32. It then follows that the leaf curvature M/El is nearly constant over the length of the leaf; i.e. the curve assumed by the bent leaf 32 approximates a circular arc. Further, in order to avoid consideration of any minute variations in the length of the leaf 32 during bending, we may make the simplifying assumption, (true for pure bending and approximately so in other cases; see Timoshenko and Young, p. 112) that the length of the central portion of the beam, the neutral fiber, remains approximately constant and equal to the length of the beam before bending. Using this information, a way has been devised to calculate the approximate trajectory 70 of the free end of the beam or leaf 32 and thus of the picker knife 18 mounted thereon.
  • FIG. 8 represents a rectangular coordinate graph in which the origin 0 represents the point (66 in FIG. 7) at which the fixed end of the curved leaf 32 is anchored against the support 39, the remainder of the leaf below that point being clamped and therefore unable to bend.
  • point 0 is the lower end of the curved leaf 32.
  • the upper end of the curved leaf is at point P, having the coordinates x, y.
  • the circular arc L drawn between points 0 and P represents the approximately circular curve of the leaf 32. This circular arc is drawn tangent to the y axis at the origin 0; therefore the x axis coincides with a radius of the circular are.
  • the leaf length L then sets certain limitations on the minimum thickness of the leaf 32. In choosing this thickness it is first necessary to select a shape for the cams 46 which, if followed by the rollers 44, would give the desired card-acceleration. Then the leaf 32 should be chosen of suflicient thickness, in view of its length, to meet certain operating requirements.
  • the motion of the picker knife 18 is necessarily rapid in both directions over its entire stroke, so as to be compatible with high-speed card-handling and other data-processing procedures.
  • the cams 46 are shaped so as to vary the picker knife velocity according to the phase of the card-feeding cycle in a manner to provide superior results.
  • the cams 46 are designed so that the velocity of the picker knife 18 is comparatively low as it initially engages the card C (FIG. 3), so as to avoid violent hammering of the card and to provide for a more even engagement of the card edge by the blade 18a. After this initial engagement the cams 46 accelerate the picker knife 18 and card C rapidly through the phase of the cycle represented by FIG.
  • the picker knife acceleration is calculated for the various phases of the operating cycle thereof. Then, from the basic equation relating force, mass, and acceleration, it is possible to calculate the force necessary to impart the required acceleration at each phase of the operating cycle to the known combined mass of the card C and the driven assembly of the picker knife 18, shaft 4%, rollers 44, and fasteners 38 and 42, plus the effective mass of the leaf 32 itself.
  • the accelerating force exerted by the deflected leaf 32 at each such phase of the cycle depends upon the extent of the leaf deflection at that phase, which is a known quantity determined by the geometry of the structure, and by the ratio of the leafs thickness to its length L. Since the length L is determined by the required picker knife trajectory, the only remaining variable to be chosen is the thickness of the leaf 32. This dimension is then made large enough so that the degree of leaf deflection occurring along each part of the operating stroke produces the cam-following force necessary to cause the required acceleration and keep the cam-follower rollers 44 pressed into engagement with the drive cams 46. In particular, this driving engagement is maintained in the least deflected position of FIG. 6 because of the fact that even in this position the leaf 32 is deflected owing to the static pre-load, as indicated by the curved line L6 in FIG. 7.
  • the earns 46 be shaped so that on the backstroke they drive the picker knife assembly rapidly rearwardly from the position of FIG. 6 to that of FIG. 1.
  • the cam-following force developed by the leaf 32 at this rearward limit position of FIG. 1 must then be great enough so that at the end of the backstroke the driven assembly does not whip backwardly to bring the cam-follower rollers 44 momentarily out of contact with the drive cams 46.
  • the thickness and thus the stiffness of the leaf 32 must be sufiicient to provide a force great enough to produce the powerful deceleration required by the shape of the cams 46 when the driven assembly reaches the end of its backstroke.
  • the stiffness of the leaf 32 must be sufl'icient to keep the natural frequency of flexural oscillation of the leaf 32, with its attached masses, well above the cycling rate encountered at the maximum operating speed for which the card-handling machine is designed, so as to discourage harmonic vibrations which would similarly affect both operation and longevity.
  • the leaf thickness should be chosen large enough so that the static and dynamic loads to which the leaf 32 is subjected are well Within the static and dynamic stress and fatigue limits of the material used, which, in view of the rapid and prolonged flexing to which the leaf 32 is subjected, should be an elastic and resilient metal such as high quality heat-treated spring steel, beryllium copper, or Phosphor bronze.
  • the dynamic loads imposed on the leaf 32 are determined by the maximum forward and backward deflections to which it is driven by the cams 46. In order to avoid concentration of these bending stresses at the place where the leaf 32 emerges from between the clamping surface 30 and clamping bar 34, locations 3tla and 34a are provided with the gentle curvatures seen in FIG. 1.
  • the static forces include the flexural static pre-load to which the leaf is subjected by virtue of its being maintained in a flexed condition to act as a cam-following return spring.
  • the static stresses include the downward buckling or compressive force, which is determined by the force of the combined weight of the leaf 32 itself, picker knife 18, shaft 40, rollers 44, and bolts 38 and 42, plus whatever portion of the weight of the cards C and weight 24 is borne by the picker knife 18.
  • the thickness of the leaf 32 must also be great enough so that its stiffness is suflicient to support the buckling load associated with the maximum card stack size, and to do so without suffering, at any of the flexed positions to which it is driven, a buckling deflection great enough to significantly alter the picker knife trajectory 70 or to disrupt the driving contact between the cams 46 and their follower rollers 44.
  • the forward and rear ward surfaces 18b and 13c are curved downwardly for wardly and rearwardly of the blade 18a respectively.
  • the level at which the rear portion of the cards C is supported is not altered solely due to the forward and backward tilting of the picker knife 18 (compare FIGS. 1 and 6) induced by the flexing of the leaf 32, since the described curvatures provide clearance for the cards C even at the rearward (FIG. 1) and forward (FIG. 6) limits of the picker knife travel.
  • the proper curvatures may be calculated from the picker knife trajectory and the degree of flexing to which the leaf 32 is subjected at these limit positions, since the latter determines the degree of tilting of the picker knife 18.
  • the forward and rearward curved surfaces 18b and 180 respectively are displaced from each other in such a manner that, if we imagine the curvature of the forward surface 18b to be extended rearwardly past the step 18a, the curve of the rearward surface 180 would be substantially parallel to, but not congruent with, such extension curve.
  • the curve of 1180 is spaced upwardly from the extension of the curve of 1811 (as meas ured along any common radius of the curves) by substantially the thickness of a conventional data card. This has the advantage that as the lowermost card C leaves the stack of cards C, the remaining cards do not drop suddenly down upon the picker knife 18 but instead, as seen in FIG. 1, they are supported at a constant level by the rear surface 136.
  • a card-feeder and picker knife mechanism so constructed not only avoids the manifold disadvantages of other suspensions and spring return mechanisms, but also affords reliable and non-damaging card feed over a long operating life.
  • a card-feeding mechanism comprising:
  • a card-feeding mechanism comprising:
  • the support and the drive means being arranged to maintain the flexible member in a flexed condition whereby to exert a static pre-load on the picker knife.
  • a card-feeding mechanism comprising:
  • the flexible member being in the form of a leaf arranged with the plane thereof substantially perpendicular to the direction of movement of the picker knife and being sufliciently bendable to permit such movement thereof.
  • a card-feeding mechanism comprising:
  • the clamping surface being so angled in relation to the picker knife positioning means as to maintain the flexible member in a flexed condition for exerting a static pre-load on the picker knife.
  • Card-handling machinery comprising:
  • a container adapted to hold a stack of cards, and arranged to permit extraction of the endmost card at one end of the container, and for feeding the stack toward the said end of the container when the said endmost card is removed therefrom;
  • Card-handling machinery comprising:
  • a gravity feed hopper adapted to contain a substantially vertical stack of substantially horizontal cards, and arranged to permit removal of and to at least partly expose the lower surface of the lowermost card to provide access thereto;
  • the card-moving device is formed with a forward upper surface, a forwardly directed card-edge-engaging blade behind the forward upper surface, and a rearward upper surface behind the card-edge-engaging blade elevated by substantially one card-thickness above the forward upper surface whereby to prevent dropping down of the remaining cards upon the card-moving device as the forward stroke thereof moves the lowermost card.
  • Card-handling machinery comprising:
  • a gravity feed hopper adapted to contain a substantially vertical stack of up to a selected maximum number of substantially horizontal cards, and arranged to permit removal of and to at least partly expose the lower surface of the lowermost card to provide access thereto;
  • (12) means adjacent the lower end of the hopper and arranged to feed the said lowermost card from the stack to another location when such card is initially moved theretoward;
  • a support spaced below the lower end of the hop (d) a flexure spring having a lower end secured to the support and an upper portion rising generally toward the hopper;
  • a device for performing such initial card-movement mounted on the upper portion of the flexure spring in position to exert an upward force on the exposed part of such lowermost card for at least partially supporting the weight of the stack, and constructed to make card-moving engagement with such lowermost card when moved in a substantially horizontal direction;
  • the fiexure spring being suificiently stiff to support the Weight of the card-moving device and cam-follower assembly plus the required portion of the weight of the selected maximum number of cards, without undergoing a sufficiently large buckling deflection to disrupt operative engagement between the cam drive and cam-follower or disrupt operative engagement between the lowermost card and the card-moving device.
  • Card-handling machinery comprising:
  • a gravity feed hopper adapted to contain a substantially vertical stack of substantially horizontal cards, and arranged to permit removal of the lowermost therefrom;
  • the flexure spring being sufficiently bendableto permit the card-moving device to perform such movement, and tilting and guiding such device along a curved trajectory;
  • the card-moving device having card-edge-engaging means thereon and being formed with a top surface adjacent the card-edge-engaging means curved downwardly away from the card-edge-engaging means whereby to provide clearance for the tilting of the card-moving device relative to the card stack.
  • Card-handling machinery comprising:
  • the stack-supporting means being arranged to orient such endmost card substantially parallel to a line which is tangent to the curved card-moving trajectory at a point between the end points of the cardengaging portion of such trajectory.
  • Card-handling machinery comprising:
  • the stack-supporting means being arranged to orient such endmost card substantially parallel to a line which is tangent to the curved card-moving trajectory at a point between the end points of the card-engaging portion of such trajectory, wherein the line of orientation of such endmost card is aligned with a chord of the curved trajectory, whereby in traversing the card-engaging portion of such trajectory the card-engaging means extends beyond such line of card orientation in the direction toward the stack, to exert an increased force against the said endmost card.
  • Card-handling machinery comprising:
  • the stack-supporting means being arranged to orient such endmost card along a line so selected that the curved card-rnoving trajectory extends beyond such line in the direction away from the stack to disengage the card-edge-engaging means from the endmost card near the terminal end of the cardmoving stroke thereof.
  • Card-handling machinery comprising:
  • a hopper adapted to contain a substantially vertical stack of substantially horizontal cards and to orient the lowermost of such cards along a selected line;
  • the flexure spring being bendable to guide the picker knife through a card-moving stroke such that the blade describes a curved trajectory wherein it is eifective to move the lowermost card from the stack;
  • such card-handling machinery being so arranged that the blade trajectory includes an initial cardi4. engagement point, followed by a rise above the selected card-orientation line, thereafter followed by a drop below such cardorientation line for disengagement of the blade from the lowermost card near the terminal end of the card-moving stroke.
  • Card-handling machinery comprising:
  • the flexure spring being bendable to guide the picker knife through a card-moving stroke such that the blade describes a curved trajectory wherein it is effective to move the lowermost card from the stack;
  • the throat plate being so positioned in relation to the picker knife to orient the lowermost card along a line which tilts downwardly from the picker knife to the throat plate and is aligned with a chord of the curved blade trajectory;
  • such card-handling machinery being arranged so that the terminal portion of the card-moving stroke carries the blade below the card-orientation line.

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US203259A 1962-06-18 1962-06-18 Card-feeder mechanism Expired - Lifetime US3145023A (en)

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Application Number Priority Date Filing Date Title
NL294207D NL294207A (de) 1962-06-18
US203259A US3145023A (en) 1962-06-18 1962-06-18 Card-feeder mechanism
FR935871A FR1366839A (fr) 1962-06-18 1963-05-24 Mécanisme d'alimentation de cartes
GB23320/63A GB986961A (en) 1962-06-18 1963-06-12 Card feeder mechanism
CH741163A CH403363A (de) 1962-06-18 1963-06-14 Karten-Fördervorrichtung

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Cited By (9)

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US3341193A (en) * 1965-05-07 1967-09-12 Honeywell Inc Document picker
US3380732A (en) * 1966-05-18 1968-04-30 Continental Can Co Sheet feeding apparatus
US3383106A (en) * 1966-11-17 1968-05-14 Ibm Record card feeding control apparatus
US3391927A (en) * 1966-12-02 1968-07-09 Gen Electric Card feeding mechanism
US3414258A (en) * 1966-12-12 1968-12-03 Ibm Record card feeding apparatus
US3693967A (en) * 1970-09-29 1972-09-26 Honeywell Inc Card reader
US3701524A (en) * 1970-09-29 1972-10-31 Honeywell Inc Modularized card reader
US4078788A (en) * 1975-12-03 1978-03-14 Ing. C. Olivetti & C., S.P.A. Sheet feeder
CN107423781A (zh) * 2017-05-22 2017-12-01 山东启能云计算网络技术有限公司 一种射频卡自动发卡装置

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US1625157A (en) * 1927-04-19 And the like

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Cited By (9)

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US3341193A (en) * 1965-05-07 1967-09-12 Honeywell Inc Document picker
US3380732A (en) * 1966-05-18 1968-04-30 Continental Can Co Sheet feeding apparatus
US3383106A (en) * 1966-11-17 1968-05-14 Ibm Record card feeding control apparatus
US3391927A (en) * 1966-12-02 1968-07-09 Gen Electric Card feeding mechanism
US3414258A (en) * 1966-12-12 1968-12-03 Ibm Record card feeding apparatus
US3693967A (en) * 1970-09-29 1972-09-26 Honeywell Inc Card reader
US3701524A (en) * 1970-09-29 1972-10-31 Honeywell Inc Modularized card reader
US4078788A (en) * 1975-12-03 1978-03-14 Ing. C. Olivetti & C., S.P.A. Sheet feeder
CN107423781A (zh) * 2017-05-22 2017-12-01 山东启能云计算网络技术有限公司 一种射频卡自动发卡装置

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Publication number Publication date
NL294207A (de)
GB986961A (en) 1965-03-24
CH403363A (de) 1965-11-30

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