US3227049A - Means for axially reciprocating a revolving shaft - Google Patents

Means for axially reciprocating a revolving shaft Download PDF

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Publication number
US3227049A
US3227049A US370275A US37027564A US3227049A US 3227049 A US3227049 A US 3227049A US 370275 A US370275 A US 370275A US 37027564 A US37027564 A US 37027564A US 3227049 A US3227049 A US 3227049A
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Prior art keywords
pressure
chamber
shaft
chambers
section
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US370275A
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English (en)
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Favrot Paul
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LANDIS GENDRON SA
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LANDIS GENDRON SA
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
    • F15B21/12—Fluid oscillators or pulse generators
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B06—GENERATING OR TRANSMITTING MECHANICAL VIBRATIONS IN GENERAL
    • B06B—METHODS OR APPARATUS FOR GENERATING OR TRANSMITTING MECHANICAL VIBRATIONS OF INFRASONIC, SONIC, OR ULTRASONIC FREQUENCY, e.g. FOR PERFORMING MECHANICAL WORK IN GENERAL
    • B06B1/00—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency
    • B06B1/18—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency wherein the vibrator is actuated by pressure fluid
    • B06B1/183—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency wherein the vibrator is actuated by pressure fluid operating with reciprocating masses
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23Q—DETAILS, COMPONENTS, OR ACCESSORIES FOR MACHINE TOOLS, e.g. ARRANGEMENTS FOR COPYING OR CONTROLLING; MACHINE TOOLS IN GENERAL CHARACTERISED BY THE CONSTRUCTION OF PARTICULAR DETAILS OR COMPONENTS; COMBINATIONS OR ASSOCIATIONS OF METAL-WORKING MACHINES, NOT DIRECTED TO A PARTICULAR RESULT
    • B23Q5/00—Driving or feeding mechanisms; Control arrangements therefor
    • B23Q5/22—Feeding members carrying tools or work
    • B23Q5/26—Fluid-pressure drives
    • B23Q5/261—Fluid-pressure drives for spindles
    • B23Q5/263—Fluid-pressure drives for spindles with means to control the feed rate by controlling the fluid flow
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B24—GRINDING; POLISHING
    • B24B—MACHINES, DEVICES, OR PROCESSES FOR GRINDING OR POLISHING; DRESSING OR CONDITIONING OF ABRADING SURFACES; FEEDING OF GRINDING, POLISHING, OR LAPPING AGENTS
    • B24B41/00—Component parts such as frames, beds, carriages, headstocks
    • B24B41/04—Headstocks; Working-spindles; Features relating thereto
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B24—GRINDING; POLISHING
    • B24B—MACHINES, DEVICES, OR PROCESSES FOR GRINDING OR POLISHING; DRESSING OR CONDITIONING OF ABRADING SURFACES; FEEDING OF GRINDING, POLISHING, OR LAPPING AGENTS
    • B24B47/00—Drives or gearings; Equipment therefor
    • B24B47/02—Drives or gearings; Equipment therefor for performing a reciprocating movement of carriages or work- tables
    • B24B47/06—Drives or gearings; Equipment therefor for performing a reciprocating movement of carriages or work- tables by liquid or gas pressure only
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B24—GRINDING; POLISHING
    • B24B—MACHINES, DEVICES, OR PROCESSES FOR GRINDING OR POLISHING; DRESSING OR CONDITIONING OF ABRADING SURFACES; FEEDING OF GRINDING, POLISHING, OR LAPPING AGENTS
    • B24B47/00—Drives or gearings; Equipment therefor
    • B24B47/10—Drives or gearings; Equipment therefor for rotating or reciprocating working-spindles carrying grinding wheels or workpieces
    • B24B47/14—Drives or gearings; Equipment therefor for rotating or reciprocating working-spindles carrying grinding wheels or workpieces by liquid or gas pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/08—Servomotor systems without provision for follow-up action; Circuits therefor with only one servomotor
    • 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
    • F16C31/00—Bearings for parts which both rotate and move linearly
    • F16C31/02—Sliding-contact bearings
    • 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
    • F16C32/00—Bearings not otherwise provided for
    • F16C32/06—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings
    • F16C32/0681—Construction or mounting aspects of hydrostatic bearings, for exclusively rotary movement, related to the direction of load
    • F16C32/0692—Construction or mounting aspects of hydrostatic bearings, for exclusively rotary movement, related to the direction of load for axial load only
    • 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

Definitions

  • the invention is particularly, although not exclusively, useful in the field of machine-tool construction, as for controlling the reciprocatory movement of a rapidly revolving spindle carrying a grinding wheelor other tool in a grinder, rectifier, milling cutter or the like.
  • Objects of the invention are to provide simple and effective fluid-pressure means whereby a rapidly revolving member can be smoothly and regularly reciprocated cyclically in an axial direction during its rotation, and wherein the rate or cycle period and amplitude of the reciprocatory motion can be easily and efficiently controlled over a wide range.
  • the invention is directed to a device for axially reciprocating a revolving shaft, comprising means supporting the shaft for rotation and axial reciprocation; means for rotating the shaft; a pair of pressure chamber means surrounding the shaft; oppositely directed pressure-responsive surfaces formed on the shaft and exposed to the pressure in the respective chamber means; pressure fluid inlets into the respective chamber means; means defining fluid exhaust passages from the respective chamber means, and so formed that the effective exhaust flow section area from at least one of the chamber means is variable with the axial position of the shaft; pressure-fluid flow circuit means connected for continuously circulating pressure fluid from each inlet through the associated chamber means and out through the associated exhaust passage means; and means for cyclically varying the fluid pressure in the circuit means associated with at least one of the chamber means whereby to reciprocate the shaft in synchronism with such cyclic pressure variations.
  • the invention is also directed in another of its aspects to improved means for creating cyclically variable pressure surges in a pressure fluid circuit which will be controllable over a wide range both in cycle period and amplitude.
  • FIG. 1 is a simplified view mainly in axial section of a first embodiment of a reciprocable revolving shaft provided with the reciprocating means of the invention
  • FIG. 2 i a similar view of a modified embodiment
  • FIG. 3 is a cross section on line III-III of FIG. 2;
  • FIG. 4 illustrates, mainly in axial section, a form of cyclic fluid pressure varying device according to the invention which is suitable for use in conjunction with the reciprocating means shown in FIGS. 1-3;
  • FIG. 5 is a cross section on line V-V of FIG. 4.
  • FIG. 1 Illustrated in FIG. 1 is a revolving spindle or shaft 1, e.g., a spindle carrying a grinding wheel (not shown) in a grinder or similar machine-tool.
  • the shaft 1 is supported in a pair of axially spaced bearing blocks 2 and 3 formed with cylindrical bores in which complementary cylindrical journal sections 4 and 5 of the shaft are rotatable, and axially reciprocable. It will be understood ice that the shaft 1 maybe driven in rapid rotation by any suitablemotor means, not shown, and connected to an end of the shaft beyond one of the bearings, or possibly to an intermediatesection of the shaft between the bearings 2 and 3.
  • annular chamber :3 surrounding the journal section 5 and having one of its side walls defined by a transverse wall portion 9 formed by a shoulder or increased-diameter section 11 of the spindle Lwhich section is positioned in a bore 13 of the bearing block 3, providing a coaxial extension of chamber 8.
  • the shaft section 11 has a diameter d2 .whichis greater than the diameter d1 of the journal section 5.
  • the bore 13 in which this large-diameter shaft section 11 is positioned is slightly larger in diameter than the diameter d2 of said section 11, so as to define a narrow annular gap 14 providing an exhaust passage from the pressure chamber 8, as will presently appear.
  • Chamber 8 has a side inlet, as shown, with which conmeets a pressure delivery line connected as at 16 with a suitable source of pressure fluid not shown, said delivery line having interposed in it, as schematically shown a. calibrated orifice nozzle 17.
  • the other bearing bloclc 2 has an annular chamber 18 urrounding the shaft journal 4 and having one of its side walls defined by a transverse wall section 24 of the shaft 1.
  • the transverse wall 24 constitutes the end surface of a conically tapered section 25 of the spindle 1, which cooperates with a complementary conical bore 26 of the bearing block :2.
  • Communicating with the inner end of the conical bore 26 is another annular chamber 21, of larger radius than the chamber 18, and communicating with this latter chamber as shown by way of a radial annular space extending across the transverse wall surface 24-.
  • Chamber 18 has a side inlet which connects with the pressure fluid supply line 16 by way of a branch line including a calibrated orifice nozzle 19, and chamber 21 likewise has a side inlet which connects with the pressure line 16 by way of another branch line in which is interposed a cyclically variable pressure device .22.
  • An exemplary construction suitable for the variable pressure device 22 will be described later with reference to FIGS. 4 and 5.
  • the pressure fluid circuit associated with the chamber 21 extends from pressure line 16 through variable pressure device 22, through chamber 21 and out therefrom by way of the conical annular exhaust passage 27 defined between the complementary conical surfaces 25 and 26.
  • T his exhaust passage 27 has a variable flow section area which depends on the axial position of the spindle 1 in its bearings, the exhaust section area increasing with increasing axial displacements of the spindle 1 in the rightward direction as here shown.
  • the pressure fluid circuit associated with chamber 18 extends from pressure line 16, through fixed orifice 19, through chamber 18, then radially outward across the end surface 24 of the spindle, into chamber 21 and out therefrom through variable exhaust passesge 27.
  • d3 designates the diameter of the shaft journal section 4
  • d4 designates the mean diameter of the effective annular part of the transverse surface 2.4
  • d5 the mean diameter of the conical surface 25.
  • the calibrated orifices 17 and 159 may be so selected and adjusted that the pressure normally obtaining in chamber 18 is about one half the source pressure in pressure line 16, and thep ressure in chamber 8 exerts an opposing axial thrust which substantially balances the pressure in chamber 18.
  • the system operates as follows. Assume first the var.- iable pressure orifice 22 is completely shut off, so that the pressures in both chamber 18 and 21 are equivalent.
  • the fixed calibrated orifices 17 and 19 can be so adjusted in relation to one another that the shaft 1 can be made to be retained floatingly at a stationary axial position as determined by equilibrium between the rightward thrust exerted by the pressure in chambers 18-21 upon an effective surface area determined by the difference between the diameters d3 and d4 on one side, and the leftward thrust exerted by the pressure in chamber 8 upon the eltective surface area determined by the diiference between diameters dl and d2 on the other side.
  • variable-orifice device 22 is progressively opened, the pressure in chamber 21 rises, the rightward thrust predominates over the leftward thrust, and the spindle 1 shifts axially in the rightward direction.
  • FIG. 2 differs 'from the construction just described in two ways, which may be applied separately if desired.
  • a first modification resides in the fact that the variable section orifice 22 instead of being interposed in the inlet leg of the fluid circuit associated with chamber 21, is interposed in the discharge leg of said circuit. That is, the chambers 18 and 21 are here disopsed in series in a common pressure fiuid circuit rather than being disposed in the parallel relation shown in FIG. 1.
  • the common circuit is traced from pressure line 16, through fixedcalibrated orifice 19, through chamber 18, chamber 21 and out to the exhaust or sump by way of the variablesection orifice 22.
  • This flow circuit arrangement may be substituted in the system illustrated in FIG. 1 if desired.
  • the tapered conical shaft section of the first construction is omitted, and the chamber 21 has one side wall defined by a transverse annular wall 32 of a largeradius cylindrical section (diameter d6) of spindle 1 slidable in a complementary cylindrical bore of bearing 2.
  • This annular wall 32 constitutes a shoulder between said large-diameter spindle section (diameter d) and an intermediate-diameter shaft section of diameter d7 providing the transverse wall exposed to the pressure in chamber 18 as in the first embodiment.
  • FIGS. 2-3 operates in a manner similar to that of FIG. 1, except for the fact that closure (not opening) of the variable-orifice nozzle 22 will produce a leftward shift of the shaft l in order to restore pressure equilibrium, while opening of the nozzle 22 will cause a rightward shift of the shaft.
  • closure (not opening) of the variable-orifice nozzle 22 will produce a leftward shift of the shaft l in order to restore pressure equilibrium, while opening of the nozzle 22 will cause a rightward shift of the shaft.
  • the variable orifice 22 in this instance is interposed in the exhaust leg of the flow circuit associated with chamber 21.
  • FIGS. 4 and 5 An exemplary embodiment of a cyclically variable orifice device usable as either of the devices 22 referred to above, will now be described with reference to FIGS. 4 and 5.
  • the device shown in those figures comprises a gener ally cylindrical casing or body 35 formed with a first large-diameter chamber 56 coaxial with the casing near one end of it, and another, smaller chamber 57 near its other end in eccentric relation to chamber 56.
  • Rotatable in the chamber 56 is a disc-like member 36 having a bevelled outer face 37, and formed integral with an axial shaft 38 rotatable in a central bore 39 formed in the end Wall of casing 35.
  • the shaft 38 connects with disc 36 by way of a hub section having a fiat face 41 seated against the inner wall surface of casing 35 to fix the axial position of the disc member in chamber 56.
  • a stop collar 43 Pinned to the outer end of shaft 38 is a stop collar 43 having a flat face 42 seated against the outer wall surface of the casing.
  • the projecting end of shaft 38 is adapted for coupling to any suitable motor means, such as a small electric motor and reducer unit schematically indicated at 45 as being secured to the casing 35 through bolts or spacers 46.
  • the motor unit 45 has provision for adjusting its speed, so as to make it possible to impart a desired angular velocity to the disc member 35 within a range of values, say about a mean value of about 1 revolution per second.
  • a nozzle member including a hub 49 and an excentric nozzle orifice 48 formed through said hub in a direction parallel to its axis and near its periphery, is mounted a tight friction fit in a bore formed in the separating wall between the chambers 56 and 57 as shown.
  • the nozzle passage 48 has a tip projecting into the chamber 56 towards the disc member 36, so as to define with the bevel face 37 of that member a variable gap 22' the width of which is a minimum for one angular position of the disc member 36 about its axis, the position shown in FIG. 4, and is a maximum for the diametrically opposite angular position of the disc member.
  • the nozzle hub 49 has an axial pivot 51 projecting from it through the inlet chamber 57 and through the opposite end wall of casing 35, and an adjusting knob 55 is keyed on to the projecting outer end of said pivot.
  • the axial position of the nozzle hub 49 in the casing is fixed by the seating of a shoulder surface 53 of pivot 51 against a wall of chamber 57 as shown.
  • the flat face 54 of knob 55 is seated against the outer end wall surface of casing 35.
  • Seal rings 61, 62 and 63 are seated in grooves formed in the casing 35 around the shaft 38, nozzle hub 49 and pivot 51 respectively.
  • the nozzle orifice 48 is spaced from the centre axis of nozzle hub 49 by a distance e which is substantially equal to the off-centre displacement of the axis of said nozzle disc 49 from the axis of the revolving disc member 36 and each of said eXcentricity values 2 is substantially equal to one half the radius R of the disc member 36.
  • Outlet chamber 56 and inlet chamber 57 have side openings 58 and 59 respectively, threaded for connection with pressure fluid lines. Referring to FIG. 1, it will be understood that the inlet chamber opening 59 would there be connected with pressure line 16 and outlet chamber opening 58 would be connected with the chamber 21. In the arrangement of FIG. 2, opening 59 would be connected with chamber 21 and outlet opening 58 would be connected to the sump.
  • the device operates as follows. With the angular position of nozzle disc 49 determined by the setting of knob 55 so that nozzle 48 assumes a position of maximum eccentricity with respect to the axis of disc member 36, as shown in FIGS. 4 and 5, it will be understood that each revolution of the disc member 36 produces a maximum amount of variation in the Width 22 of the gap through which the fluid is constrained to pass in flowing to the outlet 58. If on the other hand knob 55 is rotated to the diametrically opposite setting nozzle orifice 48 becomes substantially aligned with the centre of disc member 36 so that there is no variation in the width of gap 22'.
  • knob 55 permits adjusting the amplitude of the cyclic pressure variations produced in the operation of the device, while adjustment of the speed of rotation of disc member 36 varies the frequency of said cyclic variations.
  • the cyclically varying pressure drop to which the fluid is subjected as it is forced through the variable gap 22' creates the pressure variations or surges in chamber 21, referred to in the description of FIGS. 1-3.
  • variable pressure device of FIGS. 4-5 is used as the device designated 22 in either of the embodiments of the invention first described, the reciprocation of the shaft 1 during rotation thereof in the bearings 2 and 3 can be adjusted over a wide range.
  • variable-orifice device may be associated with the chamber having a constant-section exhaust passage, i.e. provided in place of the fixed-orifice nozzle designated 17 in the figures, and in which case the vairable-section exhaust passage 27 or 31 may be arranged to have its effective cross-section increased with leftward rather than rightward displacement of the shaft (as by reversing the taper of the conical surfaces 25, 26 in FIG. 1).
  • the exhaust passages from both side chambers may be made variable with shaft position, and/or the cyclic pressure vairations may be applied to both side chambers in a properly synchronized manner.
  • the constant pressure chamber 18 may be omitted.
  • the opposite pressure chambers may be defined within a common cylindrical capacity surrounding the shaft, on opposite sides of a piston-like flange carried by the shaft and movable in said capacity.
  • Mechanism comprising a shaft; bearing means supporting the shaft for rotation and axial reciprocation; a first and a second pressure chambers surrounding axially spaced sections of the shaft; oppositely-directed first and second pressureresponsive surfaces on the shaft exposed to the pressure in the first and second chambers respectively; a third pressure chamber surrounding the shaft adjacent said first chamber and a third pressure-responsive surface on the shaft directed in the same axial direction as said first pressure responsive surface and exposed to the pressure in said third chamber; pressure fluid inlets into the respective chambers; means defining fluid exhaust passages from the respective chambers with the effective exhaust flow section area through the exhaust passage means from at least one of the chambers being variable with the axial position of the shaft in its bearing means; pressure fluid flow circuit means connected for circulating pressure fluid from each inlet through the associated chamber means and out through the associated exhaust passage means, said circuit means including means for producing substantially equally and oppositely-acting pressure in said first and second chambers to tend to maintain the shaft floatingly in a balanced axial position in its bearing means; and means for cyclically varying the fluid pressure in

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Constituent Portions Of Griding Lathes, Driving, Sensing And Control (AREA)
  • Finish Polishing, Edge Sharpening, And Grinding By Specific Grinding Devices (AREA)
  • Magnetic Bearings And Hydrostatic Bearings (AREA)
  • Turning (AREA)
US370275A 1963-05-27 1964-05-26 Means for axially reciprocating a revolving shaft Expired - Lifetime US3227049A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
FR936045A FR1366093A (fr) 1963-05-27 1963-05-27 Dispositif de commande de déplacements axiaux cycliques d'une broche rotative de machine

Publications (1)

Publication Number Publication Date
US3227049A true US3227049A (en) 1966-01-04

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US370275A Expired - Lifetime US3227049A (en) 1963-05-27 1964-05-26 Means for axially reciprocating a revolving shaft

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US (1) US3227049A (fr)
CH (1) CH401731A (fr)
DE (1) DE1297510B (fr)
ES (1) ES299551A1 (fr)
FR (1) FR1366093A (fr)
GB (1) GB1019190A (fr)
NL (1) NL6405826A (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3589239A (en) * 1967-05-26 1971-06-29 Roulements Soc Nouvelle Hydrodynamic spindle rotating at high speed with axial reciprocation
US4046060A (en) * 1974-08-22 1977-09-06 Gewerkschaft Eisenhutte Westfalia Hydraulic control systems for use with mining apparatus
EP2705927A1 (fr) * 2012-09-10 2014-03-12 Fuji Jukogyo Kabushiki Kaisha Dispositif de contrôle d'air et procédé de contrôle d'air
CN105351360A (zh) * 2015-11-27 2016-02-24 贵州大学 高速精密轧辊磨头的偏心套的改进方法及其偏心套

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2171005A (en) * 1936-05-05 1939-08-29 Eclipse Aviat Corp Speed-responsive device
US2787254A (en) * 1955-09-19 1957-04-02 Gen Electric Hydraulic amplifier
US2835265A (en) * 1955-11-16 1958-05-20 Bendix Aviat Corp Transfer valve
US2841168A (en) * 1952-11-19 1958-07-01 Kleelavite Company Ltd Hydraulic control valve apparatus
US2872934A (en) * 1955-02-21 1959-02-10 Warner Swasey Co Control system for fluid operated power device
US2992633A (en) * 1959-05-26 1961-07-18 Thompson Ramo Wooldridge Inc Fluid pressure operated servo actuator
US3027918A (en) * 1959-11-16 1962-04-03 Schloemann Ag Throttle valves for extrusion presses
US3147770A (en) * 1962-01-26 1964-09-08 David B Perlis Cycling valve

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE465799C (de) * 1925-10-21 1928-09-25 Robert Annen Schleifvorrichtung mit im Arbeitsvorschub axial hin und her bewegter umlaufender Werkzeugspindel
US2661580A (en) * 1950-10-05 1953-12-08 Norton Co Hydraulic thrust bearing and reciprocator for shafts
CH357998A (de) * 1957-08-23 1961-10-31 Zuberbuehler Werner Bearbeitungs-Apparat

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2171005A (en) * 1936-05-05 1939-08-29 Eclipse Aviat Corp Speed-responsive device
US2841168A (en) * 1952-11-19 1958-07-01 Kleelavite Company Ltd Hydraulic control valve apparatus
US2872934A (en) * 1955-02-21 1959-02-10 Warner Swasey Co Control system for fluid operated power device
US2787254A (en) * 1955-09-19 1957-04-02 Gen Electric Hydraulic amplifier
US2835265A (en) * 1955-11-16 1958-05-20 Bendix Aviat Corp Transfer valve
US2992633A (en) * 1959-05-26 1961-07-18 Thompson Ramo Wooldridge Inc Fluid pressure operated servo actuator
US3027918A (en) * 1959-11-16 1962-04-03 Schloemann Ag Throttle valves for extrusion presses
US3147770A (en) * 1962-01-26 1964-09-08 David B Perlis Cycling valve

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3589239A (en) * 1967-05-26 1971-06-29 Roulements Soc Nouvelle Hydrodynamic spindle rotating at high speed with axial reciprocation
US4046060A (en) * 1974-08-22 1977-09-06 Gewerkschaft Eisenhutte Westfalia Hydraulic control systems for use with mining apparatus
EP2705927A1 (fr) * 2012-09-10 2014-03-12 Fuji Jukogyo Kabushiki Kaisha Dispositif de contrôle d'air et procédé de contrôle d'air
US9555482B2 (en) 2012-09-10 2017-01-31 Fuji Jukogyo Kabushiki Kaisha Air control device and air control method
CN105351360A (zh) * 2015-11-27 2016-02-24 贵州大学 高速精密轧辊磨头的偏心套的改进方法及其偏心套
CN105351360B (zh) * 2015-11-27 2017-12-01 贵州大学 高速精密轧辊磨头的偏心套的改进方法及其偏心套

Also Published As

Publication number Publication date
CH401731A (fr) 1965-10-31
NL6405826A (fr) 1964-11-30
DE1297510B (de) 1969-06-12
GB1019190A (en) 1966-02-02
FR1366093A (fr) 1964-07-10
ES299551A1 (es) 1964-07-01

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