US3020057A - Rotary fluid supply system - Google Patents

Rotary fluid supply system Download PDF

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Publication number
US3020057A
US3020057A US5735A US573560A US3020057A US 3020057 A US3020057 A US 3020057A US 5735 A US5735 A US 5735A US 573560 A US573560 A US 573560A US 3020057 A US3020057 A US 3020057A
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Prior art keywords
spindle
pressure
ring
groove
motor
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US5735A
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English (en)
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Louis J-M Gamet
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LA PRECISION INDUSTRIELLE
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LA PRECISION INDUSTRIELLE
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/66—Special parts or details in view of lubrication
    • F16C33/6637—Special parts or details in view of lubrication with liquid lubricant
    • F16C33/6659—Details of supply of the liquid to the bearing, e.g. passages or nozzles
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23B—TURNING; BORING
    • B23B31/00—Chucks; Expansion mandrels; Adaptations thereof for remote control
    • B23B31/02—Chucks
    • B23B31/10—Chucks characterised by the retaining or gripping devices or their immediate operating means
    • B23B31/12—Chucks with simultaneously-acting jaws, whether or not also individually adjustable
    • B23B31/16—Chucks with simultaneously-acting jaws, whether or not also individually adjustable moving radially
    • B23B31/16195—Jaws movement actuated by levers moved by a coaxial control rod
    • B23B31/16216—Jaws movement actuated by levers moved by a coaxial control rod using fluid-pressure means to actuate the gripping means
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23B—TURNING; BORING
    • B23B31/00—Chucks; Expansion mandrels; Adaptations thereof for remote control
    • B23B31/02—Chucks
    • B23B31/24—Chucks characterised by features relating primarily to remote control of the gripping means
    • B23B31/30—Chucks characterised by features relating primarily to remote control of the gripping means using fluid-pressure means in the chuck
    • B23B31/302—Hydraulic equipment, e.g. pistons, valves, rotary joints
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
    • F16C19/34—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load
    • F16C19/38—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers
    • F16C19/383—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone
    • F16C19/385—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone with two rows, i.e. double-row tapered roller bearings
    • F16C19/386—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone with two rows, i.e. double-row tapered roller bearings in O-arrangement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/58—Raceways; Race rings
    • F16C33/60—Raceways; Race rings divided or split, e.g. comprising two juxtaposed rings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C41/00—Other accessories, e.g. devices integrated in the bearing not relating to the bearing function as such
    • F16C41/005—Fluid passages not relating to lubrication or cooling
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16L—PIPES; JOINTS OR FITTINGS FOR PIPES; SUPPORTS FOR PIPES, CABLES OR PROTECTIVE TUBING; MEANS FOR THERMAL INSULATION IN GENERAL
    • F16L39/00—Joints or fittings for double-walled or multi-channel pipes or pipe assemblies
    • F16L39/04—Joints or fittings for double-walled or multi-channel pipes or pipe assemblies allowing adjustment or movement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2322/00—Apparatus used in shaping articles
    • F16C2322/39—General buildup of machine tools, e.g. spindles, slides, actuators
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T279/00—Chucks or sockets
    • Y10T279/12—Chucks or sockets with fluid-pressure actuator
    • Y10T279/1274—Radially reciprocating jaws
    • Y10T279/1291—Fluid pressure moves jaws via mechanical connection

Definitions

  • the invention relates to such a fluid distributing system for use in machine-tool headstocks of the type incorporating a hydraulic motor rotatable with the spindle of the headstock, and serving to actuate a work-carrying chuck, or other power-actuated mechanism, during rotation of the spindle.
  • a liuid motor for example of the cylinder and piston type, incorporated in the headstock and rotatable with the spindle of the machine-tool.
  • Such incorporated tluid motor may serve for Various purposes including the actuation of a work-clamping chuck between its work engaging and disengaging conditions, the selective clamping and feeding of continuous bar stock through the machine, the machining of work in a jig carried by the spindle, or the like.
  • the motor has to be supplied with uid from a stationary source of pressure fluid outside the machine ⁇ and a rotary distributor assembly has to be provided for permitting the flow of lluid from the stationary source to the revolving motor and back.
  • Objects of the invention are to provide a uid distributor system of the specified type which will be of considerably more compact construction than was heretofore possible; to provide such a system wherein no additional bearings will be required for the distributor, beyond those supporting the spindle in the headstock, or other frame'in which the system ofthe invention may be used; to provide such a distributor system for a machine-tool headstock wherein the distributor and motor may be mounted in directly adjacent relation to the chuck or other mechanism to be actuated thereby, thus doing away with undesirable mechanical drive transmissions such as tubes extending through the spindle.
  • Another important object is to facilitate the construction of the distributor assembly for a given, extremely narrow width of the annular clearance space between its stationary and rotatable parts.
  • An object is to apply such a distributor system to various machine-tool headstock coniigurations.
  • FIG. 1 is an laxial section of a machine-tool headstock incorporating a pressure fluid distributor, huid motor andv
  • FIG. 5 is a simplified outline view, to a reduced scale
  • FIG. 6 is a similar view of a machine-tool for machining both ends of elongated stock, e.g. lengths of tubing;
  • FIG. 7 is a similar view of a lathe embodying bar feedv mechanism; the last three figures being all illustrative of types of machine-tools to which the invention is supplied,.-
  • FIG. 8 is a partial end view of the outer ring member of a distributor system according to another embodiment of the invention.
  • FIG. 9 is a plan view of the embodiment of FIG. 8 as seen in the direction shown by the arrow IX in the latter figure;
  • FIG. l0 is a sectional view on the broken line X-X of FIG. 9 illustrating the last-mentioned embodiment; and FIG. 1l is a partial View on line Xl-XI of FIG. l0.
  • the invention contemplates providing a pair of spaced roller bearings having a common stationary outer race ring member formed with a cylindrical internal surface intermediate its length with at least one pressure fiuid delivery orifice opening radially into said surface, said bearings having separate, axially spaced inner race ring members. Between such inner race rings is mounted a spacer ring member having an outer cylindrical surface defining an extremely narrow radial clearance space with an inner cylindrical surface of the stationary common outer ring.
  • the said rotatable inner race ring members and the intermediate spacer ring member are mounted in a close fit on a cylindrical section of the spindle, and means are provided for exerting an axial clamping pressure on the three juxtaposed members for bodily rotation thereof with the spindle.
  • a pair of interconnected circumferential grooves are defined respectively by the outer and inner cylindrical surfaces of the intermediate spacer ring member, respectively with the inner cylindrical surface of the stationary outer ring member, and with the cylindrical surface of the spindle, which grooves are both formed in a common axial plane corresponding with that in which said fluid delivery inlet orifice delivers, and both grooves being interconnected by at least one generally radial duct formed through the rotatable inner ring member.
  • the inner one of said grooves communicates with at least one generally axial passage formed through the spindle and leading t the fluid motor carried by the spindle.
  • both bearings embody a common outer stationary ball race
  • an accurate coaxial and concentric relationship can easily be provided between the outer circumferential roller race surfaces and the cylindrical intermediate surface constituting the stationary part of the distributor, by simply boring the inner surface of said common stationary Outer ring.
  • an accurate coaxial and concentric relationship is readily had between the inner circumferential roller race surfaces and the cylindrical surface of the intermediate ring member constituting the rotatable part of the distributor, by simply grinding the surface of the cylindrical spindle section.
  • This accurately centered relationship will in turn ensure that the intermediate spacer ring can revolve in very closely spaced relationship with the outer ring surface, a radial clearance distance on the order of one or two hundredths of one millimeter being readily achievable.
  • the pressure liuid can thus be led from the inlet through the outer groove and through the inner groove and thence into the spindle passage leading to the motor at the cost of low controlled laminar leakage through the gap between the outer and inner ring members, the leakage flow as being collected and used for lubricating the roller bearings supporting the spindle.
  • the spacing selected between the bearings would be just sufficient to ensure a firm support of the spindle without the provision of auxiliary bearings.
  • the spindle may be provided comparatively very short, whereby machining of its inner bore from either end of the spindle as far as4 its central distributorforming portion can very simply and conveniently be performed.
  • FIGS, l and 2 of the accompanying diagrammatic drawings -a spindle 1 of a headstock 2 of a machine-tool, such as a lathe, is supported lin two axially spaced taper roller bearings, the bearing assemblage advantageously being constructed in accordance with the prior Patent No. 2,499,640 and comprising a common external ring 3 having two internal rolling surfaces 3a, 3b of truncated conical form, and a central cylindrical surface 3c.
  • Internal rings 4, 5 of the two roller bearings and an intermediate or central spacer ring 6, are fixedly positioned on the spindle 1.
  • the rollers 7, 8 of the bearings are respectively enclosed in cages 9, 10 which may be retained on the internal rings 4, 5 by steel wire rings 11 during mounting of the spindle I in the headstock 2.
  • the three internal rings 4, 5 and 6, with the cages 9, 10 of the rollers 7, 8 carried by the rings 4, 5 are inserted in the external ring 3 and the whole assembly is placed on the spindle 1.
  • the assemblage is then inserted into the headstocl: 2, the angular position of the external ring 3 being defined by a spigot 42 the head of which engages in a rounded recess in an external tiange 3d of the ring 3.
  • the external ring 3 is provided with two circumferential grooves 12 and 13 for receiving oil under pressure from channels 14, 15 respectively.
  • Each of the grooves 12, 13 communicates with the inernal cylindrical surface 3c through a series of radial holes 16.
  • These holes 16 are opposite grooves 17 and 18 respectively, which are provided in the central ring 6.
  • the external grooves 17 and 18 of the central ring 6 are connected to internal grooves 20 and 21 of the latter.
  • two channels 23 (see FIG. 2) in the spindle 1 extend to the front face of a back plate la on the nose of the spindle 1.
  • two opposite channels 24 extend in the spindle 1 and are offset so as to terminate at orifices 25 in the front face of the back plate 1a.
  • a chuck 26 is xed by means of three pairs of screws 2'! (see FIG. 2) which traverse the chuck from front to back.
  • Peripheral packing 28 ensures oil-tightness of the joint.
  • the face of the chuck turned towards the spindle is provided with a cavity 29 which, with the front face of the back plate 1a, forms an annular ram cylinder in which an annular piston 3f) of a hydraulic jack is slidable.
  • Packings 31 and 32 hermetically seal an extending central part of this piston in the interior of the spindle 1 and an oppositely extending part in the interior of the chuck 26.
  • a packing 33 forms a seal at the periphery of the piston 30 in the cavity 29.
  • the piston 30 is prevented from turning in its housing by a pin 36 which engages in a recess in the rear face of the cavity 29.
  • the front part of the piston 30 comprises three cavities 37 spaced at 120 from one another and in which there are housed cylindrically faced ends 38a of bellcrank levers 38 movable around pivots 39 and carried by the chuck 26.
  • the other ends 38h of these levers 38 also are cylindrically faced and are engaged in the housings 49a of jaw-holders 40 which, by means of screws 41, support the chuck jaws.
  • annular connecting part 43 Between the periphery of the back plate 1a and the headstock 2.
  • This part 43 is fixed to the headstock 2, with the interposition of joint packing 44, by screws (not shown) suitably spaced.
  • It is provided with an oil-retaining groove 45 around the spindle 1 opposite a peripheral ⁇ slot therein.
  • An oriiice 45a arranged at the lowest point of this groove 45, permits return of oil received by the groove 45 to a collecting reservoir through a cavity in the annular part 43 and a channel 47 connecting therewith.
  • a similar groove 46 surrounds the back plate la to prevent infiltration of the cutting or coolant liquid towards the interior of the headstock, any infiltration being passed to the exterior through a channel 46a.
  • the spindle l carries, on the left-hand in FIG. l, a gearwheel Sii which is prevented from turning by a key 51.
  • a threaded ring 52 with grub screw 52a presses against a shoulder 1b of the spindle 1, the assembly of the rings 4, 5 and 6 and the gearwheel 5l), so as to prevent any longitudinal displacement of the assembled units and rotation of the rings 4, 5 and 6 on the spindle 1.
  • the gearwheel Sil (and the gearw-heels which drive it) may be enclosed in an oil-tight gearcase.
  • the internal ⁇ diameter of the cylindrical surface 3c, and the external diameter of the ring 6 can -be selected so that the annular space which separates them is very small, for example, of the order of one to two hundreths of a millimeter.
  • peripheral grooves 12 and 13 By the peripheral grooves 12 and 13 the oil is distributed to all the radial channels 16 and an effect of concentric pressure on the periphery of the ring 3 is secured which prevents any distortion of the latter capable of causing seizing on contact with the ring'6 owing to the very small distance which separates the internal face of the ring 3 from the said ring 6. ln the same way, the similar internal and external grooves of the ring 6 play a similar role in the uniform distribution of the ow of liquid and maintaining equilibrium of forces and, moreover, they render it possible to obtain without special precautions at the time of mounting, registering of the orifices in the wall of the spindle (ends of the channels 23 and 24) with the oil feed passages.
  • the right-hand bearing (rollers 8) is lubricated by leakage of oil only when the groove 12 is under pressure, and the left-hand bearing (rollers 7) only when the groove 13 is under pressure because, in both cases, the leakage of oil which escapes from one groove 17 or 18 towards the other is collected by the latter and evacuated. There is therefore a risk 6 of inadequate lubrication of the roller bearings which support the entire load of the machine.
  • the external ring 3 may be provided with oil feed orifices 54 and 55 which emerge adjacent the small diameter end of each of the conical bearings. ⁇ Oil fed through these channels traverses the said conical bearings, and especially the internal holes of the rollers 7 and 8, to be expelled, after its lubricatingk and cooling elect. to the outside of the roller bearings'.
  • the orilices 54 and 55 can be fed with oil om any source but preferably are fed withthe same oil which is utilised in the hydraulic circuits, since the two oils are mixed in the collecting sump.
  • a pump 57 feeds oil under pressure through the channels 14 and 15 along the path shown by the dotted lines 58, and including a distributor which is not shown.
  • the pressure of oil supplied by the pump must be regulated to a predetermined value.
  • a pressure-regulating or relief valve 59 comprising a flap 6l) closed by a spring 61, the thrust of which is adjustable.
  • a bleed passage 65 communicates with the groove 17 and extends to the inner end of the right-hand roller bearing.
  • a bleed passage 66 communicates with the groove 18' and extends to the inner end of the left-hand roller bearing.
  • the leakage paths and the bleed passages 65, 66 can be calibrated in such a way that, for normal working of the machine, lubrication of the twov bearings is tially equal and adequate.
  • bearing assembly to provide a rotary distributor for oil under pressure is particularly4 appropriate in a lathe having a central or double-ended headstock, that is, a headstock provided with a chuck at each end of the spindle for engaging parts which traverse the spindle.
  • the two jacks of the chucks can be connected by suitable holes in the spindle extending in opposite directions, as is shown in FIG. 3.
  • the ring 3 yhas three Series of holes I671, 672 and 673, which feed grooves 681, 682 and 633 of the ring 6.
  • the grooves 681 and 663 correspond to grooves 691 and 693 provided in the spindle 1, which communicate with the holes 70 and i1 for feeding oil under pressure for operation of jacks at the ends of the spindle 1 in the direction of the tightenf ing of the corresponding chuck.
  • the central groove 6924 of the spindle, which communicates with the groove 6824 of the ring 6, also communicates with a channel 72 common to the two jacks which permits loosening.
  • FIGS. 5 to 7 illustrate other possible modifications.
  • a central headstock 74 incorporates a driving motor which, through a transmission 75 by belt, chain or gearwheel, drives the internal spindle 1 which is provided, at its two ends, with chucks 26a and 26h.
  • a part 76, which traverses the headstoclr, can thus be machined at both ends by tools mounted in tool-holders 77a and 77b.
  • stocks 78 and 79 carries a spindle provided at its ends with a chuck 26a and 26h respectively.
  • the two spindles are connected by a tube 80 which ensures their being driven simultaneously.
  • this tube 80 a length S1 of bar or tube may be accommodated while being machined at both ends which are held in the chucks 26a and 251).
  • a tubular spindle S2 is carried by two bearing assemblies S3 and 04, such as described with regard to FIGS. l, 3 and 4.
  • the rotary distributor of the bearing assembly 84 feeds oil under pressure for operating the chuck S5, while the rotary distributor of the bearing assembly 83 feeds oil under pressure for operating a bar-feed device 86 of known type comprising automatic tightening clamps for a bar or tube 37 and hydraulic jacks for me longitudinal displacement of these clamps.
  • a bar-feed device 86 of known type comprising automatic tightening clamps for a bar or tube 37 and hydraulic jacks for me longitudinal displacement of these clamps.
  • the chuck When the part after machining is cut from the tube of bar 87, the chuck is loosened and the bar-feed device comes into action to move the bar forward by the length of a new part to be machined.
  • the combination of the operation of a hydraulic motor of a chuck and of a barfeed device can be obtained by means of end-of-stroke limit switches actuating electro-vales or by manual con tacts or by a combination of these two methods.
  • this possibility is averted by providing means for blocking the pressure fluid in the motor in an engaged condition of the mechanism operated thereby.
  • valve means for selectively controlling the communication between an outer and an inner annular groove of the intermediate ring member.
  • the valve may assume the form of an axially displaceable plunger spring-biassed in a direction to seal such communication, and exposed to the pressure of the fluid in the outer groove to move in the opposite direction for opening said communication.
  • a further plunger member may be provided for similarly controlling a communication between the grooves for blocking the return fiow of fluid from the motor to exhaust.
  • FIGS. 8 to l1 illustrating a lform of the invention in which the last described features are embodied will new be described.
  • FIG. i0 the stationary common outer ring member 3 is provided with two threaded fiuid connections 14 and 15 to the fluid supply line.
  • a spigot 42 cooperating with an arcuate recess formed in the peripheral end fiangc 3d of said ring member is a spigot 42 serving to locate the angular position of the ring 3 in the headstock frame.
  • lubricating orifices 54 and 55 are formed through the ring member 3 which discharge into proximity with the taper rollers of the bearings.
  • connection 14 and 15 respectively open into the two axially spaced grooves 17 and 18 formed in the inner periphery of ring member 3.
  • the spacer' member 6 interposed between the inner race ring members 4 and 5 of the bearings and rotatable with the spindle is formed with internal annular grooves 20 and I1 which respectively register in axial position with the grooves 17 and 18.
  • the inner grooves 20 and 21 respectively communicate with the axial passages 23 and 24 formed in the spindle and leading to the opposite ends of an hydraulic motor carried by the spindle, such as a cylinder and piston motor similar to that shown in FIG. l.
  • the groove 17 is connected with groove 20 through a first radial duct 90, which is intcrsected by an axial bore 96 formed through the member 6, and is further connected with said groove 20 through a zigzag passageway comprising the oblique passages 91a and 9Ib and the intersecting axial bore 92 (see FIG. 11) yformed in the ring member 6.
  • the groove 18 is connected with the groove 21 through a first radial duct 93 intersected by axial bore 97 (see FIG. 1l), and by a second zigzag passageway comprising the oblique passages 94a and 94b intersected by axial bore 95 formed in ring member 6 (FIG, l0).
  • valve plungers 9S and 99 Slidably positioned in the axial bores 92 and 95 forming part of the zigzag passageways are valve plungers 9S and 99 respectively.
  • the plungers 98 and 99 are biassed in opposite directions by compression springs 100. These .bias springs are seated at one end against perforated plugging members 101, and at their opposite ends against imperforate plugging members 102.
  • the plungers 98 and 99 are formed with stop pins 98a and 99a respectively, preventing the plunger end faces directed towards the imperforate plugs from engaging the latter.
  • valve plungers 103 and 104 mounted between an imperforate and perforate plugging members 102 and 101 and urged by bias springs 100 towards the imperforate plugs 102.
  • Each of these plungers 103 and 104 includes a reduced diameter intermediate section, 103a and 104a respectively, and an end stop member, 103i: and 104i respectively, serving to provide pressure chambers betwen the imperforate plugging members and the corresponding end faces of the plungers.
  • the pressure chambers are pressurized through the bores 105 and 106 with fluid from the respective outer grooves 1.7 and 18.
  • plungers 98 and 104 associated with groove 17 are both oriented in one common direction while the plungers 99 and 103 associated with groove 13 are both oriented in a common direction reverse from the first.
  • the bias springs lili) may be calibrated so as to determine some suitable intermediate pressure in the range between the inlet pressure and the exhaust pressure.
  • the pair of plungers associated with that connection are both moved to sealing position; since the other pair of plungers (asociated with the other fluid connection) were both moved to sealing positions due to the effect of the return or exhaust pressure, it is seen that all the connections between the motor and the external supply circuit are eiectively blocked, and the motor is thus positively locked in its present condition.
  • the arrangement just described provides for a fully positive and irreversible operation of the motor.
  • the bias springs may be calibrated so as to move the plungers to their sealing positions only for a pressure lower than the return or exhaust pressure.
  • the motor is rendered irreversible (or self-locking) only as concerns such faults in the supply system as may involve the part of the system between the pump and the distributor.
  • the plungers will at all times assume their open positions during normal operation and will only be moved to sealing condition in the event of a pressure drop simultaneously occuring in both sides of the pressure system connected to the respective lines 14 and l5.
  • the plungers are arranged for displacement in axial directions so that their displacements are not affected by centrifugal forces which might otherwise undesirably modify the biassing forces applied to the plungers.
  • ya machine-tool including a stationary frame, a rotatable spindle 4having a cylindrical portion and at least one axially directed bore, and a yiiuid motor bodily rotatable with said spindle and operatively connected with the opening of said bore, the combination of a pair of axially spaced roller cages, each including a set of regularly distributed taper lroliers, said cages having their smaller diameter ends facing one another; a stationary outer-ring fitted in said frame, secured against rotation therein and surrounding said cages and rollers, and having spaced outer-race ways for said sets of rollers and a cylindrical inner surface therebetween; ⁇ a set of' three coaxially juxtaposed annular members having cylindrical inner faces iitted about said cylindrical portion of said spindle, both outer members being each provided with an inner-race way respectively for said sets of rollers and the middle member having a cylindrical outer surface defining with said cylindrical inner surface an annular gap of narrow radial width; axial tightening means carried by said
  • said fluid motor comprises a coaxial ram motor carried by the spindle, and further comprising a chuck assembly carried by the spindle yadjacent to said ram motor and connected thereto for operation thereby between an engaging and a disengaging condition.
  • a machine-tool including a rotatable spindle having a fiuid ram bodily rotatable therewith, the combination of a pair of axially spaced roller bearings supporting the spindle; a common stationary outer ring surrounding the rollers of said bearings and defining outer-race surfaces therefor; an inner ring between the bearings and rotatable with the spindle, and having an annular cylindrical outer surface defining with an annular inner surface of said outer ring a narrow annular clearance gap; an external pressure fluid system; first orifice means in said outer ring connectable with said system to operate said ram to a selected condition; second orifice means in the spindle connected with said ram; groove means defined between said annular surfaces and registering with said first orifice means; radial duct means in the inner ring connecting said groove means with said second orifice means; and valve means interposed in said duct means and movable in response to pressure in said orifice means in a direction to permit fiow through said duct
  • a machine-tool including a rotatable spindle having a fluid ram bodily rotatable therewith, the combination of a pair of axially spaced roller bearings supporting the spindle; a common stationary outer ring surrounding the rollers of said bearings and defining outer race surfaces therefor; a recessed inner ring between the bearings and rotatable with the spindle and having ⁇ an annular outer surface defining with an annular inner surface of said outer ring a narrow annular clearance; an external pressure fluid system; a pair of first orifices in said outer ring selectively connectabie with a highand a low-pressure side of said system to operate said ram to a selected condition; a pair of second orifices in the spindle connected with opposite sides of said ram; a pair of grooves defined between said ⁇ annular surfaces ⁇ and registering with said first orifices; ducts in the inner ring connecting said groovm with the respective secondêts; and valve means mov
  • valve members comprise plungers movable in bores formed in said inner ring in directions parallel to the spindle axis.
  • a head-stock assembly for a machine-tool comprising a head-stock frame; -a stationary outer-ring fitted into said frame and secured against rotation therein, said outer-ring having two outwardly flaring outer-race ways for taper rollers and a cylindrical inner surface therebetween in the middle part of said outer-ring and further having a pair of axially spaced apart first recessed duct means in said middle part; ⁇ a pair of roller bearing cages, each including a set of taper rollers respectively cooperating with said outer-race ways; an axially bored rotatable spindle having a cylindrical outer portion and a pair of axially directed blind hores starting from one end of said spindle; a set of three coaxially juxtaposed annular members having cylindrical inner faces fitted about said cylindrical portion of said spindle, both outer iembers having each ⁇ an inner-race way respectively for said sets of rollers and the middle member having a cylindrical outer surface defining with said cylindrical inner surface of the said outer-ring an annular gap of narrow
  • a head-stock assembly for a machine-tool comprising a head-stock frame; a stationary outer-ring fitted into said frame and secured against rotation therein, said outer-ring having two outwardly aring outer-race ways for taper rollers and a cylindrical inner surface therebetween in the middle part of said outer-ring; a pair of roller bearing cages, each including a set of taper rollers respectively cooperating with said outerrace ways; an axially bored rotatable spindle having a cylindrical outer portion and .two pairs of axially directed bores, each pair issuing at one end of said spindle; a set of three coaxially juxtaposed annular members having cylindrical inner faces 'fitted ⁇ about said cylindrical portion of said spindle, both outer members having each an inner-race way respectively for said sets of rollers and the middle member having ⁇ a cylindrical outer surface defining with said cylindrical inner surface of the said outer-ring an annular gap of narrow radial width; axial tightening means carried by said spindle for securing said

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Gripping On Spindles (AREA)
  • Sliding-Contact Bearings (AREA)
US5735A 1959-02-12 1960-02-01 Rotary fluid supply system Expired - Lifetime US3020057A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR786568A FR1230498A (fr) 1959-02-12 1959-02-12 Broche de machine-outil à moteur hydraulique incorporé
FR814680A FR76893E (fr) 1959-02-12 1959-12-31 Broche de machine-outil à moteur hydraulique incorporé

Publications (1)

Publication Number Publication Date
US3020057A true US3020057A (en) 1962-02-06

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ID=26183803

Family Applications (1)

Application Number Title Priority Date Filing Date
US5735A Expired - Lifetime US3020057A (en) 1959-02-12 1960-02-01 Rotary fluid supply system

Country Status (4)

Country Link
US (1) US3020057A (de)
DE (1) DE1301195B (de)
FR (2) FR1230498A (de)
GB (1) GB912538A (de)

Cited By (24)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3097857A (en) * 1962-02-26 1963-07-16 Nat Acme Co Chucking cylinder valve
US3364823A (en) * 1965-07-09 1968-01-23 Erickson Tool Co Fluid motor and control valve assembly therefor
US3369464A (en) * 1964-01-24 1968-02-20 Forkardt Paul Kg Method of and apparatus for actuating double-acting rotatable clamping means, especially for working spindles
US3685397A (en) * 1970-12-21 1972-08-22 Parker Hannifin Corp Swivel fitting
US3988969A (en) * 1973-04-13 1976-11-02 La Precision Industrielle Rotary hydraulic jack
US4040338A (en) * 1976-06-14 1977-08-09 Logansport Machine Co., Inc. Fluid supply distributor
US4168654A (en) * 1976-06-14 1979-09-25 Logansport Machine Co., Inc. Fluid supply distributor
FR2511116A1 (fr) * 1981-08-10 1983-02-11 Fives Cail Babcock Dispositif pour amener un fluide a un appareil rotatif et/ou pour l'evacuer
US4549822A (en) * 1983-08-15 1985-10-29 Sms Schloemann-Siemag, Inc. Apparatus to distribute a highly-pressurized fluid medium
US4621568A (en) * 1984-11-30 1986-11-11 The S-P Manufacturing Corporation Rotary hydraulic cylinder
US4700924A (en) * 1986-10-06 1987-10-20 Vetco Gray, Inc. Pressure energized rotary hydraulic seal
US4795128A (en) * 1988-03-01 1989-01-03 Vetco Gray Inc. Gate type kelly cock valve
EP0363328A1 (de) * 1988-10-06 1990-04-11 Schäublin S.A. Werkzeugmaschinenspindel
US4945819A (en) * 1988-08-02 1990-08-07 Roehm Guenter H Clamping apparatus for the rotary spindle of a machine tool
ES2158762A1 (es) * 1998-08-17 2001-09-01 Campos Jose Luis Galvez Mejoras introducidas en la patente de invencion n- 9801770, por "perfeccionamientos en los giratorios hidraulicos.
US6668859B1 (en) * 2002-10-21 2003-12-30 Hsuan-Lung Wu Hydraulic collet assembly with a valve unit
WO2008045245A3 (en) * 2006-10-05 2008-07-31 Wayne Dalton Corp Pressurized bearing assembly
WO2014029393A2 (de) * 2012-08-23 2014-02-27 Schaeffler Technologies AG & Co. KG Wälzlager mit radialer druckmittelübertragung
FR3003617A1 (fr) * 2013-03-22 2014-09-26 Ntn Snr Roulements Bague pour roulement, roulement, systeme comprenant des elements de roulement, et procede de fabrication et d'utilisation de roulements.
CN106523532A (zh) * 2016-12-26 2017-03-22 河南科技大学 一种双向喷嘴的油气润滑轴承座及其使用方法
CN108421995A (zh) * 2018-04-11 2018-08-21 宁波迈途机械科技有限公司 一种液压分度卡盘
US20210061640A1 (en) * 2017-12-28 2021-03-04 Kawasaki Jukogyo Kabushiki Kaisha Fluid loading joint and fluid loading equipment
US20210071795A1 (en) * 2017-12-28 2021-03-11 Kawasaki Jukogyo Kabushiki Kaisha Fluid loading joint
US11953126B1 (en) * 2023-04-21 2024-04-09 Princetel, Inc. Fluid rotary joint assembly suitable for high rotational speed

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2919180C2 (de) * 1979-05-12 1983-10-27 Paul Forkardt GmbH & Co KG, 4000 Düsseldorf Vorrichtung zur Zufuhr von Drucköl von einer stationären Druckölquelle in das Innere einer umlaufenden Welle
FR2509393A2 (fr) * 1981-07-10 1983-01-14 Precision Industrielle Dispositif de verin hydraulique, annulaire, notamment pour la commande d'un mandrin de serrage de piece sur une machine-outil

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2674461A (en) * 1950-11-28 1954-04-06 Prec Ind Control jack for work-carrying members of machine tools
US2835227A (en) * 1953-03-09 1958-05-20 Prec Ind Hydraulic rotary distributor and its application to operating jacks for work-holdersof machine-tools
US2880009A (en) * 1955-06-07 1959-03-31 Prec Ind Lever actuated machine-tool chuck

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2157892A (en) * 1937-03-12 1939-05-09 Gisholt Machine Co Transmission and control
US2423244A (en) * 1944-01-28 1947-07-01 Jones & Lamson Mach Co Power-operated chuck
US2768830A (en) * 1954-09-15 1956-10-30 Sprague & Henwood Inc Fluid operated chuck

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2674461A (en) * 1950-11-28 1954-04-06 Prec Ind Control jack for work-carrying members of machine tools
US2835227A (en) * 1953-03-09 1958-05-20 Prec Ind Hydraulic rotary distributor and its application to operating jacks for work-holdersof machine-tools
US2880009A (en) * 1955-06-07 1959-03-31 Prec Ind Lever actuated machine-tool chuck

Cited By (32)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3097857A (en) * 1962-02-26 1963-07-16 Nat Acme Co Chucking cylinder valve
US3369464A (en) * 1964-01-24 1968-02-20 Forkardt Paul Kg Method of and apparatus for actuating double-acting rotatable clamping means, especially for working spindles
US3364823A (en) * 1965-07-09 1968-01-23 Erickson Tool Co Fluid motor and control valve assembly therefor
US3685397A (en) * 1970-12-21 1972-08-22 Parker Hannifin Corp Swivel fitting
US3988969A (en) * 1973-04-13 1976-11-02 La Precision Industrielle Rotary hydraulic jack
US4168654A (en) * 1976-06-14 1979-09-25 Logansport Machine Co., Inc. Fluid supply distributor
US4040338A (en) * 1976-06-14 1977-08-09 Logansport Machine Co., Inc. Fluid supply distributor
FR2511116A1 (fr) * 1981-08-10 1983-02-11 Fives Cail Babcock Dispositif pour amener un fluide a un appareil rotatif et/ou pour l'evacuer
EP0072326A1 (de) * 1981-08-10 1983-02-16 FIVES-CAIL BABCOCK, Société anonyme Vorrichtung zum Zuführen einer Flüssigkeit in ein rotierendes Gerät und/oder zu dessen Entleerung
US4549822A (en) * 1983-08-15 1985-10-29 Sms Schloemann-Siemag, Inc. Apparatus to distribute a highly-pressurized fluid medium
US4621568A (en) * 1984-11-30 1986-11-11 The S-P Manufacturing Corporation Rotary hydraulic cylinder
US4700924A (en) * 1986-10-06 1987-10-20 Vetco Gray, Inc. Pressure energized rotary hydraulic seal
US4795128A (en) * 1988-03-01 1989-01-03 Vetco Gray Inc. Gate type kelly cock valve
US4945819A (en) * 1988-08-02 1990-08-07 Roehm Guenter H Clamping apparatus for the rotary spindle of a machine tool
EP0363328A1 (de) * 1988-10-06 1990-04-11 Schäublin S.A. Werkzeugmaschinenspindel
ES2158754A1 (es) * 1998-08-17 2001-09-01 Campos Jose Luis Galvez Perfeccionamientos en los cilindros giratorios hidraulicos.
ES2158762A1 (es) * 1998-08-17 2001-09-01 Campos Jose Luis Galvez Mejoras introducidas en la patente de invencion n- 9801770, por "perfeccionamientos en los giratorios hidraulicos.
US6668859B1 (en) * 2002-10-21 2003-12-30 Hsuan-Lung Wu Hydraulic collet assembly with a valve unit
WO2008045245A3 (en) * 2006-10-05 2008-07-31 Wayne Dalton Corp Pressurized bearing assembly
CN104685245B (zh) * 2012-08-23 2017-09-05 舍弗勒技术股份两合公司 具有液压的压力介质的径向传递装置的滚动轴承
WO2014029393A3 (de) * 2012-08-23 2014-05-30 Schaeffler Technologies AG & Co. KG Wälzlager mit radialer übertragung eines hydraulischen druckmittels
CN104685245A (zh) * 2012-08-23 2015-06-03 舍弗勒技术股份两合公司 具有液压的压力介质的径向传递装置的滚动轴承
WO2014029393A2 (de) * 2012-08-23 2014-02-27 Schaeffler Technologies AG & Co. KG Wälzlager mit radialer druckmittelübertragung
FR3003617A1 (fr) * 2013-03-22 2014-09-26 Ntn Snr Roulements Bague pour roulement, roulement, systeme comprenant des elements de roulement, et procede de fabrication et d'utilisation de roulements.
CN106523532A (zh) * 2016-12-26 2017-03-22 河南科技大学 一种双向喷嘴的油气润滑轴承座及其使用方法
US20210061640A1 (en) * 2017-12-28 2021-03-04 Kawasaki Jukogyo Kabushiki Kaisha Fluid loading joint and fluid loading equipment
US20210071795A1 (en) * 2017-12-28 2021-03-11 Kawasaki Jukogyo Kabushiki Kaisha Fluid loading joint
US11608263B2 (en) * 2017-12-28 2023-03-21 Kawasaki Jukogyo Kabushiki Kaisha Fluid loading joint and fluid loading equipment
US11608923B2 (en) * 2017-12-28 2023-03-21 Kawasaki Jukogyo Kabushiki Kaisha Fluid loading joint
CN108421995A (zh) * 2018-04-11 2018-08-21 宁波迈途机械科技有限公司 一种液压分度卡盘
CN108421995B (zh) * 2018-04-11 2023-11-14 宁波迈途机械科技有限公司 一种液压分度卡盘
US11953126B1 (en) * 2023-04-21 2024-04-09 Princetel, Inc. Fluid rotary joint assembly suitable for high rotational speed

Also Published As

Publication number Publication date
GB912538A (en) 1962-12-12
DE1301195B (de) 1969-08-14
FR1230498A (fr) 1960-09-16
FR76893E (fr) 1961-12-15

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