USRE25126E - Controller for fluid pressure operated devices - Google Patents

Controller for fluid pressure operated devices Download PDF

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USRE25126E
USRE25126E US25126DE USRE25126E US RE25126 E USRE25126 E US RE25126E US 25126D E US25126D E US 25126DE US RE25126 E USRE25126 E US RE25126E
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Prior art keywords
fluid
valve element
follow
passages
servomotor
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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
    • F15B9/00—Servomotors with follow-up action, e.g. obtained by feed-back control, i.e. in which the position of the actuated member conforms with that of the controlling member
    • F15B9/02—Servomotors with follow-up action, e.g. obtained by feed-back control, i.e. in which the position of the actuated member conforms with that of the controlling member with servomotors of the reciprocatable or oscillatable type
    • F15B9/08—Servomotors with follow-up action, e.g. obtained by feed-back control, i.e. in which the position of the actuated member conforms with that of the controlling member with servomotors of the reciprocatable or oscillatable type controlled by valves affecting the fluid feed or the fluid outlet of the servomotor
    • F15B9/10—Servomotors with follow-up action, e.g. obtained by feed-back control, i.e. in which the position of the actuated member conforms with that of the controlling member with servomotors of the reciprocatable or oscillatable type controlled by valves affecting the fluid feed or the fluid outlet of the servomotor in which the controlling element and the servomotor each controls a separate member, these members influencing different fluid passages or the same passage
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62D—MOTOR VEHICLES; TRAILERS
    • B62D5/00—Power-assisted or power-driven steering
    • B62D5/06—Power-assisted or power-driven steering fluid, i.e. using a pressurised fluid for most or all the force required for steering a vehicle
    • B62D5/09—Power-assisted or power-driven steering fluid, i.e. using a pressurised fluid for most or all the force required for steering a vehicle characterised by means for actuating valves
    • B62D5/093—Telemotor driven by steering wheel movement
    • B62D5/097—Telemotor driven by steering wheel movement gerotor type
    • 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
    • F15B9/00—Servomotors with follow-up action, e.g. obtained by feed-back control, i.e. in which the position of the actuated member conforms with that of the controlling member
    • F15B9/02—Servomotors with follow-up action, e.g. obtained by feed-back control, i.e. in which the position of the actuated member conforms with that of the controlling member with servomotors of the reciprocatable or oscillatable type
    • F15B9/08—Servomotors with follow-up action, e.g. obtained by feed-back control, i.e. in which the position of the actuated member conforms with that of the controlling member with servomotors of the reciprocatable or oscillatable type controlled by valves affecting the fluid feed or the fluid outlet of the servomotor
    • 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
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/86493—Multi-way valve unit
    • Y10T137/86574—Supply and exhaust
    • Y10T137/86638—Rotary valve
    • Y10T137/86646—Plug type
    • Y10T137/86662—Axial and radial flow

Definitions

  • My invention relates generally t control apparatus for fluid pressure operated devices and more particularly to fluid valve structures for controlling: actuation of devices which operated by fluid under pressure,
  • An important object of my invention is the provision of a novel valve structure including a movable valve element whereby the amount ofmovement of a movable fluid pressure operated member in a given direction is dependent on the amount of movement of said movable valve element in a given direction.
  • Another object of my invention is the provision of a control valve having novel follow-up mechanism which is responsive only to flow of a given quantity of fluid through said control valve to close the valve, thus eliminating the necessity for mechanical linkage between the valve and the fluidpressur-e operated device controlled thereby.
  • a valve having a primary valve element under control of an operator, a movable follow-up valve element, and a servornotor connected to the follow-up, element, the valve structure having passage means whereby all of the fluid under pressure flowing between a source and said fluid-pressure operated device, through said valve, is conducted through said servomotor .to operate the same to move the follow-up element in a direction to stop the fluid flow to said device.
  • Another important object of my invention is the provision of a novel control apparatus as set forth, having novel means whereby the servomotor can be operated by the operator, in the absence of failure of said source 10 provide. fluid .under pressure, so that the servomotor operates as a pump to deliver the desired quantity of fluid under pressure to said fluid-pressure operated device.
  • Still another object of my invention is the provision of control apparatus of the above type which can be easily installed in fluid pressure systems involving dilferent types of fluid-pressure operated devices. to control operation thereof in opposite directions, and being located at remote points from said devices, if desired.
  • FIG- 2 is. an enl ged v ew partly n e eva n a pa t y i ax a sec ion ta en subst ntially n. h line 2-4 of IG- 1, some pa t being bru en way;
  • IG- 4 is a t ansver e sect on ta en substa t a l 0. 1 th n 4- o L G- ome p rts b ing broken away;
  • FI 6 is a v e in idetelevation of the fo low-up valve element of my invention.
  • my novel controller is indicated in its entirety by the numeral 1, and, for the purpose of thfi Present xamp e, i ust at d in. G- 1 as use in h po steering mechanism for a vehicle.
  • The. controller 1 i o e a es ue r dy ruct e 2 avin a inlet 3 w w u is.
  • wunwte wndu 4 ough h ch flu d der pressure is introduced to the controller 1 from a suitable r su h- 5 Pump 5 t a i co cte n a r es uir or tenkfi hyndu t T e c i g s fur he p vided with anvoutlet 8 f0r return of fluid to the tank or reservoir 6 through a conduit 9 suita'bly connected to he ou l t 8- h a n 2-v s u h r p v de with a pair of ports 10 and 11 to which respective conduits 12 and 13 are connected, these conduits leading to opposite finds.
  • a fluid pressurecylinder 14 having mounted for axial reciprocat ory movement therein a piston-equipped plunger rod 15.
  • Said plunger rod 15 is connected to the s e i g l nka e. 1:6 o h e ic e n S by m ans of the usual bell crank17 and rigid link 18.
  • the steering linkage 16- is connected to the steerable wheels 19 in the usual manner.
  • the casing or body structure 2 comprises a tubular casing section 20 which defines the inlet and outlet 3 and :8 respectively and theports 10 and 11, a mounting flange 21 that-is rigidly secured .to one end of the tubular section 20 by machine screws or the like 22 see FIG. 14, a b a ngp t 2 an i t lly o h d mem e 2 nd an end cap;25.
  • the mounting flange 21 is provided with circurnferentially spaced apertures 26 for the reception of mounting bolts or the like 27, by means of which the controller 1 may be mounted on a suitable wall or mounting bracket 28 of the vehicle, as shown, see FIG. 1.
  • F IG With reference toF IG.
  • bearing plate 23, internally toothed member 24, and end cap 25 are rigidly secured in end to end relationship to the .opposite en o t e tubu ar h u ng s t 20 by me s of chine screws 29.
  • the tubular housing or casing section '20 has an in- .ternal cylindrical Wall 30 which, together with the mounting flange 21 and annular bearing plate 23 defines a cylindrical chamber for the reception of concentric primary and. follow-up valve elements 31 and 32 respectively.v
  • the followaup valve element 32 is in the .113- wtru efof a tubular sleevewhich closely engages the inner ovlindrical wall 30, for rotary movement :with respect to, the casing section 20 and concentric therewith, the opposite ends .of the follow-up --valve element 32 having substantiallyrabutting engagement with an inner surface portion otthe mounting flange 21 and with the bearing plate 23.
  • the primary valve element 3.1 is cylindric' n o m an h llow for the greater part or its lengthh re y t defin an xi l r s or pa sa e 33 which. extends inwardly from the ,endthereof adjacent the bear nen ate the a v e emen 1 being uas ugly r c ve within. e in ow-up va v e ment 32 an concentric therewi h. the end pf the primary, valve eleme t .31 is.
  • an O-ring 40 is contained in a suitable annular groove in the mounting flange 21 and encircles the shaft 35 adjacent the thrust bearing 34 to prevent leakage of fluid from within the housing or body structure 2 adjacent the shaft 35.
  • a second O-ring 41 is mounted in the mountingflange 21 and provides a-seal between the mounting flange 21 and the tubular body section 20.
  • the primary valve element 31 is coupled to the followup valve element 32 for limited rotary movement in opposite directions with respect to the follow-up valve element 32, and for common rotary movement with the follow-up valve element 32.
  • Means for thus coupling the valve elements together comprises a transverse drive pin 42 which extends radially through a pair of diametrically opposed circumferentially extended slots 43 in the primaryvalve element 31, see particularly FIG. 4, the opposite-ends of the drive pin 42 being snugly received in diametrically opposed apertures 44 in the follow-up valve element 32.
  • the drive pin 42 becomes engaged by the opposite ends of the opposed slots 43, after which the continued rotary movement of the primary valve element 31 will cause similar rotary movement to be imparted to the follow-up valve element 32.
  • I provide a plurality of resilient leaf springs 45 which extend radially through aligned diametrically opposed notches 46 and 47 in the primary and follow-up valve elements 31 and 32 respectively, and through a groove or channel 48 in the inner end of the control shaft 35 and aligned with the notches 46 and 47.
  • the primary valve element 31 and control shaft 35 are fabricated separately, the inner grooved end of the shaft 35 being welded or otherwise rigidly secured within the adjacent end portion of the tubular section of the valve element 31.
  • the primary valve element 31 is formed to provide, in axially inwardly spaced relation to its opposite ends, a pair of radially outwardly opening circumferential channels 49 and 50, one side of the former defining axially inwardly extending radially outwardly opening recesses 51 in circumferentially spaced relationship.
  • the several channels 57-60 are disposed in registration with respective ones of the openings'in the tubular casing 20, the channel 57 being in registration with the inlet 3, the channel 58 with the delivery port 10, the channel 59 with the delivery port 11, and the channel 60 with the outlet 8.
  • a pair of axially spaced circumferentially extended rows of apertures or passages 61 extend radially inwardly of the channel 57 to the interior of the follow-up valve element 32, each of the apertures 61 being in register with a dilferent one of the apertures 53 in the primary valve element 31 when the primary valve element 31 is in its neutral position relative to the follow-up valve element 32, wherein the drive pin 42 is centered in the slots 43.
  • a plurality of circumferentially spaced openings 1 or passages 62 that are in constant communication with the channel 49 of the primary valve element 31, whereby fluid under pressure is supplied by the pump 5 to the channel 49-and recesses 51 at all times and irrespective of the relative positions of the valve elements 31 and 32.
  • a plurality'of circumferentially spaced radial passages 63 extend inwardly from the outer surface of the follow-up valve element 32 intermediate the channels 57 and 58 thereof, there being a like number of radial passages 63 as that of recesses 51 and axial grooves 54 combined.
  • the row of radial passages 63 overlies the recesses 51 and adjacent end portions of the grooves 54.
  • the follow-up valve element 32 is formed to provide a plurality of slot-like passages 64 which extend radially inwardly from the channel 58 and which are disposed to register selectively with the openings 55 and grooves 54 of the primary valve element 31 upon relative rotation between the valve elements 31 and 32.
  • the slot-like passages 64 are equal in number to one-half of the radial passages 63, the passages 64 being aligned with alternate ones of the radial passages 63 axially of the valve element nel communicates with the recess or passage 33 by of circumferentially spaced radially outwardly opening I passages in the nature of grooves 54 which extend axially of the primary valve element 31, the grooves 54 terminate at one end between adjacent recesses 51 and'in circumferentially spaced relation thereto, and at their other end terminating in axially spaced relation to the channel 50.
  • valve element 31 is provided with pairs of radial openings 55 and 56 which com municate with the passage or recess 33, the radial open ings 55 being located in closely spaced relation to adjacent recesses 51, and the openings 56 being disposed adjacent the opposite ends of the grooves 54, see particularly FIG. 5. It will be noted that axially aligned pairs of the openings 55 and 56 are also disposed in axial alignment with a different one of the recesses 51, for a purpose which will hereinafter become apparent. I
  • the outer cylindrical surface of the follow-up valve element 32 is formed to provide a plurality of axially 32, as best shown in FIG. 6.
  • Similar slot-like passages 65 extend radially inwardly from the bottom of the channel 59 in circumferentially staggered relationship to the passages 64, the passages 65 being aligned with alternate ones of the radial passages 63 axially of the follow-up valve element 32.
  • the slot-like passages 65 are adapted to register selectively with the openings 56 and the adjacent end portions of the grooves 54, in the primary valve element 31, upon relative rotation between the valve elements 31 and 32.
  • the channel 60 of the follow-up valve element 32 is disposed in overlying relationship to the channel 50 of the primary valve element 31, and communication is had between the channels 60 and 50 by a plurality of circumferentially spaced radial passages 66 extending inwardly from the bottom of the channel 60.
  • the internally toothed member 24 comprises the stator of a fluid pressure operated servomotor which also includes an externally toothed member 67 having a less number of teeth 68 than that of the teeth 69 defined by the stator or internally toothed member 24, said member 67 being adapted to rotate on its own axis and partake of orbital movement about the axis of the member 24.
  • the members 24 and 67 are so arranged that the teeth 68 and 69 thereof respectively move into and out of intermeshing engagement and define expanding and contracting nuia chamber 70,1see are. '7', during said "rotary and orbital movement of the member 67'.
  • the construction of the members 24 and 67 is similar to that shown and described in my prior U .8.
  • Thecasing structure 2 is provided with a plurality of circumferentially spaced axially extending fluid passages 71 that extend through the bearing plate 23 one each into a difierent one of the chambers 7 between the root portions of adjacent internal teeth 69. At theirinner ends, the fluid passages 71 extend radially'inwardly through the inner cylindrical wall 30 of the tubular casing section 20 radially outwardly of the row of radial passagm 63.
  • the externally toothed member or rotor 67 is operatively coupled to the follow-up valve element 32 by means or an angularly disposed drive shaft 72 which at its outer end is provided with a 'splined head 73 that is mounted in a central splined opening -7 4 in the rotor 67.
  • a 'splined head 73 that is mounted in a central splined opening -7 4 in the rotor 67.
  • the drive shaft 72 is bifurcated, as indicated at 75, to receive the central portion of the drive pin 42, whereby rotation of the externally toothed member or rotor 67 is imparted to the followup valve element 32.
  • Axial movement of the drive shaft 72 is limited in one direction by engagement of the splined head 73 with the annular bearing plate 23, and in the other direction by engagement of the outer end of the splined head 73 with a stop plug or'the like 76 contained in the splined opening 74 of the externally toothed member 67 between the head 73 and the endcap-ZS.
  • I provide .a fluid passage 77 in the tubular casing section 20, said pas sage -77 communicating at its opposite ends with the inlet 3 and the outlet 8, see FIG. 3.
  • the passage 77 is enlarged to [receivea coil compres! sion spring 78 which exerts yielding hiaswagainst a ball check valve 79 toward seating engagement with .an annular valve seat 80 that is screw threaded into :a further enlarged threaded portion-of the passage 77 adjacent the outlet ,8.
  • This arrangement provides for flow ofhfiuid from the outlet 8 to the inlet 3 when fluid pressure is greater in-the outlet .8 :than in the inlet 3.
  • This movement of the plunger rod- 15 causes fluid to flow from the opposite end of the cylinder 14 through the conduit 12 to the port 10, inwardiy through the s'lotlike passages .64 and openings 55' in'register therewith to the recess or passage 33, and from thence outwardly through the openings 52 and 66 to the outlet 8 to be discharged through the conduit- 9 into the reservoir 6.
  • follow-up valve element .32 operates in the nature of a-colmnutator to position given ones of the radial passages 63 with given recesses 51, grooves 54 and the passages 71 to direct the fluid. in :a manner :to-eause continued orbital movement of the externally toothed member 6.7 until rotation of e samehas moved .thefollow-up-va-lve element 32 intoits neutral position with respect :to the primary valveelement 31.
  • the primary valve element 31 may continue to; :be manually rotated by means of the steering wheel 37 as tiar as desired, the servomotor comprising the toothed mmt bers 24 and 67 continuing to operate until neutrality is obtained between the primary valve element 31 and follow-up valve-element 32.
  • I'husjit.willbe.seenithatrotation of the control wheel 37 causes the steerable wheels 19 to be swung in one direction, while rotation of the control wheel 37 in the opposite direction causes the steerable wheels 19 to partake of steering movements accordingly.
  • the yielding bias exerted by the leaf springs 45 against rotary movement or the primary valve element 31 with respect to the follow-up valve element 32, is such that a nominal amount of steering etfort by the operator is required to rotate the Wheel 37 in either direction from the neutral position above described. Due' to theyielding bias of the leaf springs 45, release of the control wheel 37 by the operator will cause the primary valve element 31 to be immediately returned to its neutral position by the springs 45 to shut off flow of fluid to either end of the fluid pressure operated device or cylinder 14.
  • the servomotor may be used as a pump, operated by manually rotating the control wheel 37 in either direction, to deliver fluid under pressure to a selected end of the cylinder 14, upon failure of the pump 5 to deliver fluid under pressure to the inlet 3.
  • initial manual rotation of the control wheel 3-7 will cause the primary valve element 31 to be rotated until opposite given ends of the slots 43- engage the drive pin 42 at which point the longitudinal grooves 54 are in registration with the desired slot-like passages 64. or 65 in the follow-up valve element 32.
  • a controller for fluid pressure operated devices comprising; valve structure including a. primary movable valve element and a cooperating movable follow-up valve element; means for connecting said primary valve element to acontrol element for common movement therewith; means coupling said primary valve element to said follow-up valve element for limited movements independently of said follow-up valve element and for common movements therewith; and a fluid servomotor including a movable member coupled to said follow-up valve element for imparting follow-up movements'thereto responsive to movement of said movable member; said valve structure defining, an inlet for connection to a source of fluid under pressure and an outlet for return of fluid to said source, a pair of fluid ports for connection to a fluid pressure operated device, and fluid passages communicating with said servomotor; said'valy'e elements each having valve passages which cooperate to direct flow of fluid from said inlet through said servomotor to one of said ports and to direct flow of fluid from the otherof said ports to said outlet responsive to movement of said primary valve element in one direction away from a
  • valve structure further defines an auxiliary fluid passage between said inlet and said outlet independently of the others of said passages, and in further combination with a valve normally closing said auxiliary passage when the inlet pressure is greater than the outlet pressure and opening said auxiliary passage during reversal of said pressure to permit flow of fluid from said outlet to said inlet.
  • a controller for fluid pressure operated devices comprising; body structure defining a cylindrical chamber; a cylindrical primary valve element journal-led in said body structure and extending axially within said chamber; a tubular follow-up v-alve element concentrically journalled on said primary valve element within said chamber; means for imparting rotation to said primary valve element from a neutral position; means coupling said valve elements together, for independent rotation relative to each other between predetermined limits and for common rotation; said body structure defining, an inlet for connection to a source of fluid under pressure, an outlet for return of fluid to said source, and a pair of fluid ports for connection to a fluid pressure operated device; said body structure including a stationary annular internally toothed member concentric with said chamber; an externally toothed member having a less number of teeth than said internally toothed member and mounted in meshing engagement therewith for orbital and rotary movements within said internally toothed member; said toothed members cooperating to provide a servomotor; means coupling said externally toothed member to said follow
  • said primary valve element defines an axial recess extending firom one end of said primary valve element for the greater part of its length
  • said means coupling the valve elements together comprising a transverse drive pin connected at its opposite end portions to diametrically opposed portions of said follow-up valve element, said primary valve element having-diametrically opposed circumferentially extending slots for free reception of said drive pin, the opposite ends of said slots engaging said drive pin to limit said independent movement of the primary valve element.
  • said means coupling the externally toothed member to said followup valve element comprises a drive shaft connected at one end to said externally toothed member for common rotation therewith. and for angular movements with respect thereto, the other end of said drive shaft being bifurcated for reception of the intermediate portion of said drive pin within said recess in the primary valve element.
  • a controller for fluid pressure operated devices comprising; valve structure including a primary movable valve element and a cooperating movable followup valve element; means for connecting said primary valve element to a control element for common movements therewith; and a fluid servomotor including a rotary member coupled to said follow-up element for imparting follow-up movements thereto responsive to rotation of said rotary member; said valve structure defining, an inlet for connection to a source of fluid under pressure and an outlet for return of fluid to said source, a pair of fluid ports for connection to a fluid pressure operated device, and fluid passages communicating with said servomotor; said valve elements each having valve passages which cooperate to direct flow of fluid from said inlet through said servomotor to one of said ports and to direct flow of fluid from the other of said ports to said voutlet responsive .to movement of said primary valve .element in one direction away from a neutral position relative to said follow-up valve element; movement of said primary valve element in the opposite direction from said neutral position causing said valve element passages to be
  • a controller for fluid pressure operated devices comprising; valve structure including a primary movable valve element and a cooperating movable follow-up valve element; means for connecting said primary valve element to a control element for common movement therewith "11 either direction from .a neutral position; means coupling said primary valve element to said follow-up valve element for limited movements follow-up valve element and for member yieldingly urging said valve elements toward relative neutral positions wherein said primary valve element is disposed centrally between the limits of said independent movement thereof relative to said follow-up valve element; and a fluid servomotor including amovable member coupled to said follow-up element for imparting follow-up movements thereto responsive to movement of said movable member; said valve structure defining-an inlet for connection to a source of fluid under pressure and an outlet for return of fluid to said source, .a pair of fluid ports for connection to a fluid pressure operated device, and fluid passages communicating with said servo motor; said valve elements each having valve passages which cooperate to direct flow of fluid from said inlet through said servo
  • a controller comprising; valve structure including a primary movable valve element and a cooperating movable follow-up valve element; means for connecting said primary valve element to a control element .for common movement therewith; means coupling said primary valve element to said follow-up valve element for limited movements independently of said follow-up valve element and for common movements therewith; and a fluid servomotor including, a movable member coupled to said follow-up valve element for imparting follow-up movements thereto responsive to movement of said movable member; said valve structure defining, an inlet connected to said source of fluid and an outlet connected to said source for return of fluid thereto, a pair of ports connected to said fluid pressure operated device, and fluid passages communicating with said servomotor; said valve elements each having valve passages which cooperate to direct flow of fluid from said inlet through said servomotor to one of .said ports and to direct flow of fluid from the other of movement of said primary valve element in the opposite direction from
  • a controller for fluid pressure operated device s comprising; body structure .defining a cylindrical chamber; a cylindrical primary valve element journalled in said body structure and extending axially within said chamber; a tubular follow-up valve element concentrically journalled on said primary valve element within said chamber; means for imparting rotation to said primary valve element from a neutral position; means coupling said valveelements together for independent rotation relative to each other between pre-detersure operated device; and a servomotor comprising an internally toothed member and an externally toothed member; said externally toothed member having a less number of teeth than said internally toothed member and in meshing engagement therewith; one of said members being stationary and the other thereof being movable in an orbit about the axis of the stationary member and rotatable on its own axis responsive to said orbital movement; said follow-up valve element being coupled to said movable member for common rotation therewith; said body structure defining fluid passages communicating with said servomotor; said valve elements each having valve passages which cooperate
  • a controller for fluid pressure operated devices comprising; body structure defining a cylindrical chamber; a cylindrical primary valve element journalled in said body structure and extending axially within said chamber; a tubular follow-up valve element concentrically journalled on said primary valve element within said chamber; means for imparting rotation to said primary valve element from a neutral position relative to said follow-up v-alve element; means coupling said valve elements together for independent rotation relative to each other between predetermined limits and for common rotation and including a resilient member yieldingly urging said valve elements toward relative neutral positions wherein said primary valve element is disposed centrally between the limits of said independent rotation thereof; said body structure defining, an inlet for connection to a source of fluid under pressure, an outlet for return of fluid to said source and a pair of fluid ports for connection to a fluid pressure operated device; and a servomotor comprising an internally toothed member and an externally toothed member; said externally toothed member having a less number of teeth than said internally toothed member and in meshing engagement therewith;
  • a controller for fluid pressure p rated devices comprising; valve structure including a primary movable valve element and a cooperating mov able follow-up valve element; means for connecting said primary valve element to a control element for common movements therewith; and a fluid servomotor including a rotary member coupl d to said follow-up element for imparting follow-up movements thereto responsive to rotation of said rotary member; said valve structure defining, an inlet for connecti n to a source of flu'id under pressure and an outlet for return of fluid to said source, a pair of fluid ports for connection to a fluid pressure operated device, and fluid passages communicating with said servomot r; said valve elements each having valve passages which cooperate to direct flow of fluid from said inlet through said servomotor to one of said ports and to direct flow of fluid from the other of said ports to said outlet responsive to movement of said primary valve element in one direction away from a neutral position relative to said follow-up valve element; movement of said primary valve element in the opposite direction from said neutral position
  • a controller for fluid pressure operated devices comprising; valve structure including a primary movable valve element and a cooperating movable follow-up valve element; means for connecting said primary valve element to a control element for common movement therewith in either direction from a neutral position; means coupling said primary valve element to said follow-up valve element for limited movements independently of said follow-up valve element and for common movements therewith and including a resilient member yieldingly urging said valve elements toward relative neutral positions wherein said primary valve element is disposed centrally between the limits of said independent movement thereof relative to said follow-up valve element; and a fluid servomotor including it movable mem,
  • valve structure defining, an inlet for connection to a source of fluid under pressure and an outlet for return of fluid to said source, a pair of fluid ports for connection to afluid pressure operated device, and fluid passages c mmunicating with said servomotor; said valve elements each having valve passages which cooperate to direct flow of fluid from said inlet through said servomotor to one of said ports and to direct fluid from the other of said ports to said outlet responsive to movement of said primary valve element in one direction away from said neutral position relative to said follow-up valve element; movement of said primary valve element in the opposite direction from said neutral position causing said valve element passages to be disposed to direct flow of fluid from said inlet through said servomotor to the other of said ports and to direct the flow-of fluid from said one of the ports to said outlet; thearrangement being such that the entire stream of fluid flowing from said inlet to the selected One of said ports is conducted through said valve structure defining, an inlet for connection to a source of fluid under pressure and an outlet for return of fluid to said source,
  • a controller for fluid pressure operated devices comprising; body structure defining a cylindrical chamber; a cylindrical primary valve element journalled in said body structure and extending axially within said chamber; a tubular follow-up valve element concentrically journalled on said primary valve element within said chamber; means for imparting rotation to said primary valve element from a neutral position; means coupling said valve elements together for independent rotation relative to each other between pred termined limits and for common rotation; said body structure defining, an inlet for connection to a source of fluid under pressure, an-outlet for return of fluid to said source, and a pair of fluid ports for connection to a fluid pressure operated device; and a servomotor comprising an internally toothed member and an externally toothed member; said externally toothed member having a less number of teeth than said internally toothed member and in meshing engagement therewith; one of said members being stationary and the other thereof being movable with its axis moving in an orbit about the axis of the stationary member, the movable member being rotatable
US25126D 1958-11-25 Controller for fluid pressure operated devices Expired USRE25126E (en)

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US (2) USRE25126E (de)
DE (1) DE1293029B (de)
FR (1) FR1240487A (de)
GB (1) GB897768A (de)

Cited By (45)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3261235A (en) * 1963-12-03 1966-07-19 Lamina Inc Portable rotary machining appliance and apparatus
US3270681A (en) * 1964-11-18 1966-09-06 Germane Corp Rotary fluid pressure device
US3270682A (en) * 1965-01-22 1966-09-06 Germane Corp Rotary fluid pressure device
US3270683A (en) * 1965-08-04 1966-09-06 Char Lynn Co Porting arrangement for balancing valve of fluid pressure device
US3272142A (en) * 1965-08-13 1966-09-13 Char Lynn Co Porting and passage arrangement for fluid pressure device
US3283723A (en) * 1965-07-09 1966-11-08 Germane Corp Rotary fluid pressure devices
US3286928A (en) * 1964-11-20 1966-11-22 Wald Ind Inc Hydraulic compensation of highway striping equipment
US3286645A (en) * 1965-07-09 1966-11-22 Char Lynn Co Rotary fluid pressure device
US3288078A (en) * 1964-08-25 1966-11-29 Trw Inc Hydraulic device
US3288034A (en) * 1965-02-24 1966-11-29 Jr Hollis N White Rotary motor or pump
US3289542A (en) * 1963-10-29 1966-12-06 Lawrence Machine & Mfg Company Hydraulic motor or pump
US3302584A (en) * 1965-09-01 1967-02-07 Char Lynn Co Valving arrangement for fluid pressure device
US3309999A (en) * 1965-06-21 1967-03-21 Char Lynn Co Drive mechanism for gerotor gear set
US3348493A (en) * 1965-10-21 1967-10-24 Char Lynn Co Fluid pressure remote control devices and systems
US3364907A (en) * 1965-04-27 1968-01-23 Ronald J St Onge Rotary piston mechanism
US3425448A (en) * 1966-07-01 1969-02-04 Char Lynn Co Fluid pressure balanced valve
US3532447A (en) * 1968-12-31 1970-10-06 Germane Corp Fluid operated motor
US3547563A (en) * 1968-12-31 1970-12-15 Germane Corp Fluid operated motor
US3547564A (en) * 1968-12-31 1970-12-15 Germane Corp Fluid operated motor
US3584985A (en) * 1968-05-11 1971-06-15 Danfoss As Hydrostatic control equipment particularly for steering systems
US3589129A (en) * 1969-09-04 1971-06-29 Sundstrand Corp Proportional directional control unit
FR2353427A1 (fr) * 1976-06-04 1977-12-30 Eaton Corp Circuit de servo-direction a detection de la charge
US4096883A (en) 1976-08-24 1978-06-27 Eaton Corporation Closed-center controller and neutral bypass arrangement therefor
FR2416367A1 (fr) * 1978-02-06 1979-08-31 Eaton Corp Distributeur sensible a la charge
USRE31067E (en) 1973-10-19 1982-10-26 Trw Inc. Hydrostatic control unit
EP0096963A2 (de) * 1982-06-14 1983-12-28 Eaton Corporation Ladenachweissystem
US5016672A (en) * 1990-04-23 1991-05-21 Eaton Corporation Steering controller with integral parallel control
US5101860A (en) * 1991-09-30 1992-04-07 Eaton Corporation Fluid controller and improved check valve arrangement therefor
EP0480431A1 (de) * 1990-10-11 1992-04-15 Eaton Corporation Steuergerät mit verringertem Schlupf des Endausschlags
EP0482440A1 (de) * 1990-10-24 1992-04-29 Eaton Corporation Drehschieberlenkventil mit grosser Auslenkung
US5115640A (en) * 1990-04-23 1992-05-26 Eaton Corporation Fluid controller and logic control system for use therewith
EP0498223A1 (de) * 1991-01-28 1992-08-12 Eaton Corporation Lenksteuereinrichtung für mehrere lenkbare Achsen
WO1996037714A1 (en) * 1995-05-22 1996-11-28 Commercial Intertech Corp. Power-assisted hydraulic steering system
US5771692A (en) * 1994-03-28 1998-06-30 Bergmann; Erhard Hydraulic steering unit with load signal
US6213247B1 (en) * 1995-12-12 2001-04-10 Danfoss A/S Hydraulic steering device and method for steering a vehicle
US20030217550A1 (en) * 2002-05-27 2003-11-27 Ognibene S.P.A. Hydrostatic power steering device for fast steering
US20070219689A1 (en) * 2006-03-14 2007-09-20 Gacioch Michael T Work vehicle steering system with flow-metering curve selection and associated method
US20080116001A1 (en) * 2006-10-30 2008-05-22 Deere & Company Steering system with variable flow rate amplification ratio and associated method
US20090095561A1 (en) * 2007-10-05 2009-04-16 Cnh America Llc Hydraulic Steering System for a Vehicle
WO2013036759A1 (en) 2011-09-09 2013-03-14 Eaton Corporation Steered wheel visual feedback system for variable rate steering systems
US20130075642A1 (en) * 2011-09-28 2013-03-28 Goodrich Actuation Systems Sas Rotary Control Valve
US20130220458A1 (en) * 2012-02-28 2013-08-29 Ognibene Power S.P.A. Distributor device for hydraulic power steering
US9435446B1 (en) * 2014-07-24 2016-09-06 Google Inc. Rotary valve with brake mode
US9611946B1 (en) 2015-08-17 2017-04-04 Google Inc. Rotary hydraulic valve
WO2021249614A1 (en) 2020-06-08 2021-12-16 Volvo Construction Equipment Ab A power steering system for a working machine

Families Citing this family (37)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3131602A (en) * 1961-11-16 1964-05-05 Kingston Products Corp Steering torque amplifier
GB1084141A (de) * 1964-01-07
US3385057A (en) * 1964-08-25 1968-05-28 Trw Inc Hydraulic controller
FR1475685A (fr) * 1965-11-30 1967-04-07 Dispositif de commande d'un moteur hydraulique
US3360932A (en) * 1966-05-05 1968-01-02 Int Harvester Co Rotary emittance valve
DE1553004C3 (de) * 1966-07-19 1974-09-12 Danfoss A/S, Nordborg (Daenemark) Steuerdrehschiebereinrichtung an einer Rotationskolbenmaschine
US3443378A (en) * 1967-04-04 1969-05-13 Trw Inc Hydrostatic single unit steering system
US3446021A (en) * 1967-06-14 1969-05-27 Int Harvester Co Power steering unit with poppet directional control valves
US3528521A (en) * 1968-06-13 1970-09-15 Allis Chalmers Mfg Co Hydraulic steering system
BE791144A (fr) * 1971-11-16 1973-03-01 Danfoss As Appareil de commande pour systemes hydrostatiques ou hydrauliques
BE791086A (fr) * 1971-11-16 1973-03-01 Danfoss As Appareil de commande pour systemes hydrostatiques ou hydrauliques
US3810417A (en) * 1972-01-31 1974-05-14 H Sieke Method and apparatus for producing vibratory motion
US3801239A (en) * 1972-04-03 1974-04-02 Eaton Corp Controller for fluid operated device
DE2221183C2 (de) * 1972-04-29 1982-12-30 Zahnradfabrik Friedrichshafen Ag, 7990 Friedrichshafen Steuerdrehschiebereinrichtung in einer Rotationskolbenmaschine
DE2253532C3 (de) * 1972-11-02 1981-07-30 Danfoss A/S, 6430 Nordborg Hydraulische Steuereinrichtung für Lenkungen, insbesondere für Fahrzeuglenkungen
US3895888A (en) * 1973-10-19 1975-07-22 Trw Inc Hydrostatic control unit
US3937601A (en) * 1974-03-22 1976-02-10 Trw Inc. Hydrostatic controller wherein the control valve spool includes the commutator valve
DE2553748C3 (de) * 1975-11-29 1981-05-07 Danfoss A/S, 6430 Nordborg Hydraulische Steuereinrichtung, insbesondere für Fahrzeuglenkungen
DE2637332C3 (de) * 1976-08-19 1981-04-23 Danfoss A/S, 6430 Nordborg Hydraulische Hilfskraft-Lenkeinrichtung
DE2712920C3 (de) * 1977-03-24 1980-08-07 Zahnradfabrik Friedrichshafen Ag, 7990 Friedrichshafen Hydraulische Druckmittelsteuereinrichtung, insbesondere für hydrostatische Lenkeinrichtungen von Kraftfahrzeugen
DE2749352C3 (de) * 1977-11-04 1981-01-15 Zahnradfabrik Friedrichshafen Ag, 7990 Friedrichshafen Druckmittelsteuereinrichtung, insbesondere für hydrostatische Lenkeinrichtungen von Kraftfahrzeugen
FR2418132A1 (fr) * 1978-02-23 1979-09-21 Ferodo Sa Dispositif de direction assistee d'un vehicule
DE2809192C2 (de) * 1978-03-03 1983-01-05 Danfoss A/S, 6430 Nordborg Hydrostatische Lenkeinrichtung
DE2944883C2 (de) * 1979-11-07 1982-08-26 Danfoss A/S, 6430 Nordborg Hydrostatische Lenkeinrichtung
DE3006509C2 (de) * 1980-02-21 1984-10-25 Danfoss A/S, Nordborg Hydrostatische Lenkeinrichtung
DE3024171C2 (de) * 1980-06-27 1984-11-08 Danfoss A/S, Nordborg Hydrostatische Stelleinrichtung, insbesondere Lenkeinrichtung für Fahrzeuge
DE3037660C2 (de) * 1980-10-04 1982-12-02 Zahnradfabrik Friedrichshafen Ag, 7990 Friedrichshafen Hydrostatische Hilfskraftlenkung
DE3320444C1 (de) * 1983-06-06 1987-10-01 Danfoss A/S, Nordborg Kupplung zum Verbinden einer Nabe und einer Welle
DE3504993A1 (de) * 1985-02-14 1986-08-14 Danfoss A/S, Nordborg Steuergeraet fuer hydrostatische hilfskraftlenkeinrichtungen
DE3507901A1 (de) * 1985-03-06 1986-09-18 Danfoss A/S, Nordborg Steuergeraet fuer hydrostatische lenkeinrichtungen
DD247421B5 (de) * 1986-03-31 1995-09-21 Hydraulik Nord Gmbh Parchim Hydrostatische Lenkeinrichtung
DE4204336C2 (de) * 1992-02-14 1995-07-06 Hydraulik Nord Gmbh Hydrostatische Lenkeinrichtung
DE19503890C2 (de) * 1995-02-07 1996-11-28 Danfoss As Steuervorrichtung für ein hydraulisches Lenksystem
DE19830747A1 (de) * 1998-07-09 2000-01-13 Zahnradfabrik Friedrichshafen Hilfskraftbetätigtes Lenkgetriebe
EP3078571B1 (de) * 2015-04-08 2017-06-21 Danfoss Power Solutions Aps Hydraulisches lenksystem
DE102020106438B4 (de) 2020-03-10 2022-03-31 Danfoss Power Solutions Aps Fluidsteuereinrichtung, insbesondere als Teil einer hydraulischen Lenkeinheit
DE102020106440A1 (de) * 2020-03-10 2021-09-16 Danfoss Power Solutions Aps Hydraulische Lenkeinheit

Family Cites Families (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US957499A (en) * 1908-08-06 1910-05-10 William Montagu Coward Distributing and reversing expansion-valve.
US979097A (en) * 1909-05-01 1910-12-20 Joseph Rothchild Engine-valve.
US2105473A (en) * 1934-08-10 1938-01-18 Walter C Dean Hydraulic steering gear
US2261444A (en) * 1938-12-20 1941-11-04 Jr Oscar Neubert Follow-up valve
US2321377A (en) * 1940-08-01 1943-06-08 Heil Co Hydraulic steering gear
US2334918A (en) * 1942-06-05 1943-11-23 Heil Co Hydraulic steering gear
DE763594C (de) * 1943-04-25 1952-12-22 Erich Herion Elektromagnetisch zu steuerndes Vierwegventil
US2464110A (en) * 1944-11-27 1949-03-08 Galion Iron Works & Mfg Co Hydraulic system for vehicle steering and other apparatus
DE802298C (de) * 1948-10-09 1951-02-08 Elektro Mechanik G M B H Hydraulische Schiebersteuerung mit Vorsteuerung
US2786539A (en) * 1948-11-26 1957-03-26 Harry J Nichols Controllable-pitch propeller system
US2524055A (en) * 1948-12-04 1950-10-03 Int Harvester Co Hydraulic telemeter system with variable-rate valve shutoff unit
DE816332C (de) * 1949-12-06 1951-10-08 Georg Billeter Regelorgan fuer den hydraulischen Antrieb von Werkzeug- und sonstigen Arbeitsmaschinen
US2688258A (en) * 1952-04-17 1954-09-07 Ford Motor Co Power steering mechanism
DE959081C (de) * 1955-03-03 1957-02-28 Sack Gmbh Maschf Hydraulische Fernsteuerung fuer Servomotoren, insbesondere in hydraulischen Pressen
US2821170A (en) * 1955-05-02 1958-01-28 Robin A Jacobus Stapler
US2833253A (en) * 1955-06-13 1958-05-06 Deere Mfg Co Power steering for vehicles
USRE25291E (en) * 1956-06-08 1962-12-04 Fluid pressure device and valve

Cited By (57)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3289542A (en) * 1963-10-29 1966-12-06 Lawrence Machine & Mfg Company Hydraulic motor or pump
US3261235A (en) * 1963-12-03 1966-07-19 Lamina Inc Portable rotary machining appliance and apparatus
US3288078A (en) * 1964-08-25 1966-11-29 Trw Inc Hydraulic device
US3270681A (en) * 1964-11-18 1966-09-06 Germane Corp Rotary fluid pressure device
US3286928A (en) * 1964-11-20 1966-11-22 Wald Ind Inc Hydraulic compensation of highway striping equipment
US3270682A (en) * 1965-01-22 1966-09-06 Germane Corp Rotary fluid pressure device
US3288034A (en) * 1965-02-24 1966-11-29 Jr Hollis N White Rotary motor or pump
US3364907A (en) * 1965-04-27 1968-01-23 Ronald J St Onge Rotary piston mechanism
US3309999A (en) * 1965-06-21 1967-03-21 Char Lynn Co Drive mechanism for gerotor gear set
US3286645A (en) * 1965-07-09 1966-11-22 Char Lynn Co Rotary fluid pressure device
US3283723A (en) * 1965-07-09 1966-11-08 Germane Corp Rotary fluid pressure devices
US3270683A (en) * 1965-08-04 1966-09-06 Char Lynn Co Porting arrangement for balancing valve of fluid pressure device
US3272142A (en) * 1965-08-13 1966-09-13 Char Lynn Co Porting and passage arrangement for fluid pressure device
US3302584A (en) * 1965-09-01 1967-02-07 Char Lynn Co Valving arrangement for fluid pressure device
US3348493A (en) * 1965-10-21 1967-10-24 Char Lynn Co Fluid pressure remote control devices and systems
US3425448A (en) * 1966-07-01 1969-02-04 Char Lynn Co Fluid pressure balanced valve
US3584985A (en) * 1968-05-11 1971-06-15 Danfoss As Hydrostatic control equipment particularly for steering systems
US3547564A (en) * 1968-12-31 1970-12-15 Germane Corp Fluid operated motor
US3547563A (en) * 1968-12-31 1970-12-15 Germane Corp Fluid operated motor
US3532447A (en) * 1968-12-31 1970-10-06 Germane Corp Fluid operated motor
US3589129A (en) * 1969-09-04 1971-06-29 Sundstrand Corp Proportional directional control unit
USRE31067E (en) 1973-10-19 1982-10-26 Trw Inc. Hydrostatic control unit
FR2353427A1 (fr) * 1976-06-04 1977-12-30 Eaton Corp Circuit de servo-direction a detection de la charge
US4096883A (en) 1976-08-24 1978-06-27 Eaton Corporation Closed-center controller and neutral bypass arrangement therefor
FR2416367A1 (fr) * 1978-02-06 1979-08-31 Eaton Corp Distributeur sensible a la charge
EP0096963A2 (de) * 1982-06-14 1983-12-28 Eaton Corporation Ladenachweissystem
EP0096963A3 (en) * 1982-06-14 1985-01-09 Eaton Corporation Load sensing system
US5016672A (en) * 1990-04-23 1991-05-21 Eaton Corporation Steering controller with integral parallel control
US5115640A (en) * 1990-04-23 1992-05-26 Eaton Corporation Fluid controller and logic control system for use therewith
EP0480431A1 (de) * 1990-10-11 1992-04-15 Eaton Corporation Steuergerät mit verringertem Schlupf des Endausschlags
EP0482440A1 (de) * 1990-10-24 1992-04-29 Eaton Corporation Drehschieberlenkventil mit grosser Auslenkung
EP0498223A1 (de) * 1991-01-28 1992-08-12 Eaton Corporation Lenksteuereinrichtung für mehrere lenkbare Achsen
US5101860A (en) * 1991-09-30 1992-04-07 Eaton Corporation Fluid controller and improved check valve arrangement therefor
US5771692A (en) * 1994-03-28 1998-06-30 Bergmann; Erhard Hydraulic steering unit with load signal
WO1996037714A1 (en) * 1995-05-22 1996-11-28 Commercial Intertech Corp. Power-assisted hydraulic steering system
US5775102A (en) * 1995-05-22 1998-07-07 Commercial Intertech Corp. Power-assisted hydraulic steering system
US6213247B1 (en) * 1995-12-12 2001-04-10 Danfoss A/S Hydraulic steering device and method for steering a vehicle
US20030217550A1 (en) * 2002-05-27 2003-11-27 Ognibene S.P.A. Hydrostatic power steering device for fast steering
US6863147B2 (en) * 2002-05-27 2005-03-08 Ognibene S.P.A. Hydrostatic power steering device for fast steering
US20070219689A1 (en) * 2006-03-14 2007-09-20 Gacioch Michael T Work vehicle steering system with flow-metering curve selection and associated method
US7283900B1 (en) 2006-03-14 2007-10-16 Deere & Company Work vehicle steering system with flow-metering curve selection and associated method
US20080116001A1 (en) * 2006-10-30 2008-05-22 Deere & Company Steering system with variable flow rate amplification ratio and associated method
US7913800B2 (en) 2006-10-30 2011-03-29 Deere & Company Steering system with variable flow rate amplification ratio and associated method
US20090095561A1 (en) * 2007-10-05 2009-04-16 Cnh America Llc Hydraulic Steering System for a Vehicle
US7798280B2 (en) * 2007-10-05 2010-09-21 Cnh America Llc Hydraulic steering system for a vehicle
WO2013036759A1 (en) 2011-09-09 2013-03-14 Eaton Corporation Steered wheel visual feedback system for variable rate steering systems
US20130075642A1 (en) * 2011-09-28 2013-03-28 Goodrich Actuation Systems Sas Rotary Control Valve
US8960228B2 (en) * 2011-09-28 2015-02-24 Goodrich Actuation Systems Sas Rotary control valve
US20130220458A1 (en) * 2012-02-28 2013-08-29 Ognibene Power S.P.A. Distributor device for hydraulic power steering
US9032999B2 (en) * 2012-02-28 2015-05-19 Ognibene Power S.P.A. Distributor device for hydraulic power steering
US9435446B1 (en) * 2014-07-24 2016-09-06 Google Inc. Rotary valve with brake mode
US20160348798A1 (en) * 2014-07-24 2016-12-01 Google Inc. Rotary Valve with Brake Mode
US9927037B2 (en) * 2014-07-24 2018-03-27 Boston Dynamics, Inc. Rotary valve with brake mode
US9611946B1 (en) 2015-08-17 2017-04-04 Google Inc. Rotary hydraulic valve
US10227999B2 (en) 2015-08-17 2019-03-12 Boston Dynamics, Inc. Rotary hydraulic valve
US10808736B2 (en) 2015-08-17 2020-10-20 Boston Dynamics, Inc. Rotary hydraulic valve
WO2021249614A1 (en) 2020-06-08 2021-12-16 Volvo Construction Equipment Ab A power steering system for a working machine

Also Published As

Publication number Publication date
GB897768A (en) 1962-05-30
DE1293029B (de) 1969-04-17
FR1240487A (fr) 1960-09-02
US2984215A (en) 1961-05-16

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