US3918856A - Gerotor fluid controller with twistable blade energy storing means - Google Patents

Gerotor fluid controller with twistable blade energy storing means Download PDF

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Publication number
US3918856A
US3918856A US443463A US44346374A US3918856A US 3918856 A US3918856 A US 3918856A US 443463 A US443463 A US 443463A US 44346374 A US44346374 A US 44346374A US 3918856 A US3918856 A US 3918856A
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United States
Prior art keywords
fluid
valve
blades
end portion
blade
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
US443463A
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English (en)
Inventor
Laurence L Miller
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Northrop Grumman Space and Mission Systems Corp
Original Assignee
TRW Inc
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by TRW Inc filed Critical TRW Inc
Priority to US443463A priority Critical patent/US3918856A/en
Priority to DK29175AA priority patent/DK135224B/da
Priority to AU77924/75A priority patent/AU486487B2/en
Priority to CA219,398A priority patent/CA1017224A/en
Priority to GB562475A priority patent/GB1475206A/en
Priority to DE2505569A priority patent/DE2505569C2/de
Priority to IE259/75A priority patent/IE40801B1/xx
Priority to FR7504520A priority patent/FR2261435B1/fr
Priority to BE153321A priority patent/BE825487A/xx
Priority to LU71870A priority patent/LU71870A1/xx
Priority to BR986/75A priority patent/BR7500986A/pt
Priority to JP2030875A priority patent/JPS5443253B2/ja
Priority to AT124575A priority patent/AT339745B/de
Priority to NLAANVRAGE7501980,A priority patent/NL175048C/xx
Priority to SU752110470A priority patent/SU791264A3/ru
Priority to IT20420/75A priority patent/IT1031858B/it
Application granted granted Critical
Publication of US3918856A publication Critical patent/US3918856A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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    • 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
    • G—PHYSICS
    • G05—CONTROLLING; REGULATING
    • G05G—CONTROL DEVICES OR SYSTEMS INSOFAR AS CHARACTERISED BY MECHANICAL FEATURES ONLY
    • G05G25/00—Other details or appurtenances of control mechanisms, e.g. supporting intermediate members elastically
    • G—PHYSICS
    • G05—CONTROLLING; REGULATING
    • G05G—CONTROL DEVICES OR SYSTEMS INSOFAR AS CHARACTERISED BY MECHANICAL FEATURES ONLY
    • G05G2700/00—Control mechanisms or elements therefor applying a mechanical movement
    • G05G2700/12—Control mechanisms with one controlling member and one controlled member
    • G05G2700/14—Control mechanisms with one controlling member and one controlled member with one elastic element as essential part, e.g. elastic components as a part of an actuating mechanism

Definitions

  • An improved fluid controller includes a gerotor gear assembly having an internally toothed stator and an externally toothed rotor which are operable to provide a metered flow of fluid.
  • a valve sleeve is movable axially between a closed position blocking fluid flow to and from the gerotor gear assembly and an open position in which fluid is ported to the gerotor gear assembly.
  • the valve sleeve Upon initial rotation of an input member, the valve sleeve is moved axially from the closed position to the open position. During axial movement of the valve sleeve, the input member resiliently twists a plurality of torsion blades which extend between the input member and a wobble shaft connected with the rotor of the gerotor gear assembly. When the rotation of the input member is stopped, the resiliently twisted torsion blades are effective to rotate the valve sleeve relative to the input member to effect movement of the valve sleeve to its closed position.
  • the torsion blades are connected with the input shaft and wobble shaft in such a manner as to prevent the inducing of stresses at the connections between the blades and the two shafts.
  • the torsion blades cooperate with the two shafts in such a manner as to minimize lost motion at the connections between the blades and the shafts.
  • the blades have major sides with relatively large surface areas to facilitate the dissipating of heat resulting from flexing of the blades.
  • This invention relates generally to an improved fluid controller and more specifically to a fluid controller which has a rotary input memberassociated with a valve member to effect movement of the valve member upon rotation of the input member relative thereto.
  • Steering controllers of the type to which this invention relates are used to effect powered hydrostatic steering of a vehicle.
  • Fluid controllers for use in hydrostatic steering of a vehicle are known. Such controllers include a gerotor mechanism for metering fluid flow to a power steering cylinder and a valve mechanism for porting fluid to the gerotor mechanism and to the steering-cylinder.
  • An operator-controlled input shaft is connected with the valve member to effect movement of the valve member upon rotation of the input member relative thereto.
  • a torsion coupling Upon initial rotation of the input shaft and movement of the valve member from an initial position a torsion coupling stores energy to return the valve member to its initial position.
  • the torsion coupling is connected between the gerotor mechanism and the input shaft.
  • This known torsion coupling includes a torsion rod which has a relatively long axial length and is twisted about its central axis upon movement of the valve member.
  • the torsion rod Due to the fact that the torsion rod is sized so as to have a desired spring rate, it has a limited outer surface area for-dissipating heat which results during flexing of the rod.
  • the torsion rod and its connections with the input shaft and valve member are relatively expensive to fabricate.
  • Two known fluid controllers having torsion coupling arrangements are disclosed in US. Pat. Nos. 3,443,378 and 3,452,543.
  • the present invention provides an improved fluid controller having at least one torsion blade which is resiliently twisted about its central axis upon rotation of an input member relative to a valve member.
  • a pair of torsion blades are utilized to minimize the width and axial extent of the blades and provide a desired spring rate.
  • the opposite end portions of the torsion blades are disposed in mounting slots formed in the input member and in a member connected with the gerotor mechanism.
  • the torsion blades are advantageously bowed or curved so that they press firmly against the sides of the mounting slots.
  • the blades are formed with protuberances which prevent engagement of the blades with the corners of the slots as the blades are twisted.
  • the new and improved fluid controller of the present invention has a simple torsion coupling which is inexpensive to fabricate, is relatively free of stress concentrations, and has a minimum of lost motion.
  • the torsion blade construction which is resiliently twisted about its central axis upon movement of an input member relative to the valve member.
  • the valve member is movable from an initial position to port fluid to the gerotor gear assembly and the resiliently deflectable'torsion blade construction is twisted about its central axis by the input force applied to the input shaft and thereby stores energy to effect movement of the valve member back to its initial position when the input force is removed.
  • FIG. 1 is an axial sectional view of a fluid controller constructed in accordance with the present invention
  • FIG. 2 is a fragmentary view, taken generally along the line 2-2 of FIG. I;
  • FIG. 3 is an enlarged plan view of thetorsion blades
  • FIG. 4 is a view taken along the line 44 of FIG. 3, further illustrating the curved construction of the torsion blades;
  • FIG. 5 is an enlarged sectional view, taken generally along the line 55 of FIG. 3 and illustrating the relationship between inner end portions of the torsion blades;
  • FIG. 6 is an enlarged section view, taken generally along the line 6-6 of FIG. 3, illustrating the relationship between outer end portions of the torsion blades;
  • FIG. 7 is an enlarged sectional view, taken generally along the line 7-7 of FIG. 3, further illustrating the relationship between the inner end portions of the torsion blades when they are in an unrestrained condition;
  • FIG. 8 is a sectional view of a portion of the controller shown in FIG. 1 and taken along the line 8-8 thereof,
  • FIG. 9 is a schematic view of a portion of the fluid controller illustrating the gear assembly therein.
  • a fluid controller 10 constructed iniaccordance with the present invention is illustrated in FIG. 1 and includes a gerotor gear assembly 12.
  • the gerotor gear assembly 12 is operable to provide a metered flow of fluid upon actuation of a control valve 14 in response to rotation of an input shaft 16.
  • the fluid controller 10 has an improved torsion coupling assembly l8 which is effective to return the valve 14 back to its initial or unactuated condition, as will be described below.
  • the fluid controller 10 includes a generally cylindrical casing or housing 22 which is connected 'with a pump or other source of fluid (not shown) by a conduit 24.
  • the housing 22 is connected to a reservoir or drain through a second conduit 28.
  • a ball 34 cooperates with a generally helical groove 36 to axially shift a valve sleeve 32. This axial shifting of the valve sleeve 32 enables high pressure fluid to flow from an annular pressure groove to the gerotor gear assembly 12.
  • a measured fluid output from the gerotor gear assembly 12 is ported by the valve to either a conduit 44 connected with one end of a piston and cylinder type hydraulic motor (not shown) or to a conduit 46 connected with the opposite end of the motor.
  • the gerotor gear assembly 12 includes an internally toothed stator 50 which circumscribes an externally toothed rotor 54.
  • the rotor 54 has one less tooth than the stator 50 and cooperates with the stator, a spacer plate 56, and a bearing plate 58 to form a plurality of fluid receiving pockets which provide a metered fluid output upon rotational and orbital movement of the rotor relative to the stator.
  • a commutator valve 62 cooperates with the gerotor gear assembly 12 to port fluid to and from the pockets formed between the stator 50 and rotor 54.
  • the construction of the gerotor gear assembly 12 and the manner in which it cooperates with the valve assembly 14 and commutator valve 62 is the same as is disclosed in U.S. Pat. No. 3,452,543 which is incorporated herein in its entirety by this reference thereto. In order to avoid prolixity of description, the known relationships between these components will not be further described herein.
  • the torsion coupling 18 includes a pair of torsion blades 66 and 68 (see FIGS. 1-4).
  • the torsion blades 66 and 68 extend between the input shaft 16 and a wobble shaft 74 having an externally toothed head portion 76 disposed in meshing engagement with internal teeth on the rotor 50.
  • the torsion blades 66 and 68 are resiliently twisted as the valve sleeve 32 is shifted axially to an actuated position. Twisting of the torsion blades 66 and 68 stores potential energy to effect a shifting of the valve sleeve 32 back to its initial or closed position upon interruption of rotation of the input member 16.
  • the torsion blades 66 and 68 are resiliently twisted in a clockwise direction about their longitudinal axes. As the torsion blades 66 and 68 are twisted, the valve sleeve 32 is shifted toward the left by the interaction between the ball 34 and helical groove 36. Once the valve sleeve 32 has been moved to an actuated position, a stop element (not shown) on the input shaft 16 rotates the valve sleeve 32 with the input shaft.
  • valve sleeve 32 When the input force on the input shaft 16 is interrupted, the potential energy stored in the resiliently twisted torsion blades 66 and 68 is sufficient to cause the valve sleeve 32 to rotate in a counterclockwise direction and to be shifted axially toward the right to the position of FIG. 1 by the interaction between the ball 34 and helical groove 36. This return of the valve sleeve is effected by the torsion blades turning the shaft 16 relative to the valve sleeve 32.
  • the torsion blades 66 and 68 are resiliently twisted in a counterclockwise direction during initial rotation of the input shaft 16.
  • the valve sleeve 32 is shifted toward the right from the position of FIG. 1 to port fluid to the gerotor gear assembly 12 and to the steering cylinder.
  • the potential energy stored in the resiliently twisted torsion blades 66 and 68 is effective to cause the valve sleeve 32 to rotate and be shifted toward the left under the influence of the ball 34 and helical groove 36.
  • the blade 68 has a pair of relatively large major sides 82 and 84 (see FIGS. 3 and 4) which are exposed to hydraulic fluid within a valve chamber 88 (FIG 1). As the hydraulic fluid flows through the valve chamber 88, it passes along the major side surfaces 82 and 84 of the blade 68. Such flow cools the blade and dissipates heat generated due to twisting thereof.
  • the blade 68 has a pair of minor sides 92 and 94 which extend parallel to each other in such a manner that the blade 68 has a generally rectangular cross sectional configuration. Although the configuration of only the blade 68 is shown in FIG. 3, it should be understood that the blade 66 has the same configuration as the blade 68.
  • connection 98 with the input shaft 16 is formed by a slot 104 which extends diametrically across the inner end of the shaft 16 and is sized to receive the outer end portions 108 and 110 of the torsion blades 66 and 68.
  • a central locating hole 112 is formed in the end of the input shaft 16 and receives axially projecting tongues 118 and 120 formed on the torsion blades 66 and 68.
  • a connection 100 with the wobble shaft 74 is of a construction which is generally similar to the connection 98 and includes a slot 122 formed in an externally toothed head end portion 124 of the wobble shaft 74.
  • the slot 122 extends diametrically across the wobble shaft 74 and receives inner end portions 126 and 128 of the torsion blades 66 and 68.
  • the externally toothed head end 124 of the wobble shaft 74 is disposed in meshing engagement with axially extending internal splines or teeth 132 formed on the valve sleeve 32. Therefore during rotation of the input shaft 16, the torsion blades 66 and 68 apply torque to the valve sleeve 32 through the head end portion 124 of the wobble shaft 74.
  • the wobble shaft 74 is drivingly connected to the valve sleeve 32 and this connection is provided by splines 132 on the valve spool which mesh with a cooperating gear on the wobble shaft 74. Since the connection 100 is formed in the head end portion 124 of the wobble shaft 74, the torsion blades 66 and 68 are rotated with the wobble shaft and valve sleeve 32 as the wobble shaft is rotated about its central axis during rotational movement of the rotor 54 relative to the stator 50. ()f course, the rotor 54 and wobble shaft 74 rotate about their central axes in the same direction as the input shaft 16.
  • the rotor 54 is also subjected to orbital movement relative to the stator 50.
  • the direction of orbital movement of the rotor is opposite from the direction in which it rotates about its central axis.
  • the orbital movement of the rotor 50 results in oscillatory movement of the head end 124 of the wobble shaft 74 relative to the valve spool splines 132 and the torsion blades 66 and 68.
  • the inner end portions 126 and 128 of the blades 66 and 68 are cut away to clear the diametrically extending bottom surface 136 of the slot 124.
  • the blade 68 has sloping end surfaces 138 and 140 (see FIG. 3) which are spaced from the bottom surface 136 of the slot 124. If the end portion 128 of the blade 68 was cut square, that is if it was cut along a line extending perpendicular to the minor sides 92 and 94 of the blade, the end portion 128 of the blade to be engaged by the bottom 136 of the slot 122 and would interfere with the movement of the wobble shaft 74. Although the configuration of the inner end portion 128 of only the blade 68 has been shown in FIG. 3, it should be understood that the inner end portion 126 of the blade 66 has the same configuration.
  • the major sides of the torsion blades are twisted relative to the sides of the slots 104 and 122. If the major sides of the torsion blades 66 and 68 engage the extending corner portions of the slots 104 and 122, severe localized stress conditions would be induced in the torsion blades 66 and 68. Of course, these severe localized stress conditions would be detrimental to the operating life of the torsion blades.
  • the blades 66 and 68 are formed with rounded protuberances which hold the blades 66 and 68 away from the corner edge portions of the slots.
  • the outer end portion 110 of the blade 68 is formed with a pair of protuberances or bumps 144 and 146 (see FIGS. 3 and 6).
  • the protuberances 144 and 146 engage a side surface 150 of the slot 104 (see FIG. 2) at a location axially inwardly from the outer corner edge portion of the slot 104.
  • the arcuate radius of the protuberances 144 and 146 is sufficient to hold the major side 82 of the blade 68 away from the corner edge portion of the slot 104 as the blade 68 is twisted or flexed.
  • the inner end of the blade 68 is also formed with a pair of protuberances 154 and 156 (see FIG. 3) which engage a side surface 158 (see FIG. 2) of the slot 122 to hold the major side surface 82 of the blade 68 away from the corners of the slot during twisting of the blades 66 and 68.
  • the curved configuration of the protuberances 144, 146, 154, and 156 formed in the blade 68 enable the protuberances 144, 146 to rock and slide freely relative to the input shaft 16 and wobble shaft 64 as the blade is twisted or flexed.
  • the blade 66 is provided with protuberances similar to the protuberances formed on the blade 68.
  • the outer end portion 108 of the blade 66 is formed with a pair of protuberances 162 and 164 (FIG. 6) which have the same configuration as the protuberances 144 and 146 formed in the blade 68.
  • the inner end portion 126 of the blade 66 is formed of a pair of protuberances 166 and 168 (FIG. 5) which have the same configuration as the protuberances 154 and 156 on the blade 68.
  • the protuberances 162, 164, 166, and 168 engage side surfaces of the slots 104 and 122 which are opposite from the side surfaces engaged by the protuberances on the blade 68.
  • the inner end portions 126, 128 of the blades 66, 68 are also held against movement radially toward the valve spool 32. This is accomplished by the splines 132.
  • the inner end portions of the blades 66, 68 are held in a centered relationship with the valve spool 32 by the splines 132 (FIG. 8).
  • a pair of oppositely projecting dimples are formed on the inner end portions 126 and 128 of each of the blades 66 and 68.
  • the blade 68 is formed with a dimple 172 which projects outwardly from the major side 82 of the blade.
  • a second dimple 174 projects outwardly from the opposite side 84 of the blade 68.
  • the two dimples 172 and 174 cooperate with a pair of dimples 178 and 180 formed in the blade 66 in the manner illustrated in FIG. 5 to hold the two blades 66 and 68 against endwise or axial movement relative to each other.
  • the torsion blades are designed in such a manner that they press firmly against the side walls of the slots 104 and 122 even though the manufacturing tolerances with which the slots are formed may be such that they are not the exact size desired.
  • the torsion blades are formed with a longitudinally extending arcuate curvature.
  • the torsion blade 68 is bowed so that the major side surface 82 has a convex curvature while the major side surface 84 has a concave curvature (see FIG. 4).
  • the torsion blade 66 is formed with the same curved or bowed configuration as the torsion blade 68.
  • the two torsion blades 66 and 68 When the two torsion blades 66 and 68 are placed in the fluid controller 10, they are positioned with their concavely bowed or curved major sides in a side-byside or facing relationship as shown in FIG. 4. This results in an angular separation of the blades at their end portions in the manner illustrated in FIGS. 2 and 7. As the blades are inserted into the slots 104 and 122, the various protuberances on the end portions of the blades engage the side surfaces of the slots and press the adjacent major sides together. Thus, the blades in effect act as springs and try to return to their free state.
  • the fluid controller 10 includes a valve assembly 14 which is actuated upon rotation of input shaft 16 to activate a gerotor gear assembly 12.
  • a valve assembly 14 which is actuated upon rotation of input shaft 16 to activate a gerotor gear assembly 12.
  • the input shaft H When the input shaft H) is initially rotated in u clockwise direction with the valve assembly 14 in the position of HO. 1, the blades 66, 68 twist. This twisting results because of the resistance of the rotor 54 to rotation. As this occurs, the input shaft 16 rotates relative to the wobble shaft 74. This clockwise rotation of the input shaft 16 relative to the wobble shaft 74 flexes or twists the torsion blades 66 and 68.
  • the ball 34 cooperates with the helical groove 36 to shift the valve sleeve 32 axially toward the left (as viewed in FIG. 1).
  • the splines 132 on the inside of the valve spool 32 slide relative to the external teeth on the head portion 124 of the wobble shaft 74.
  • valve assembly 14 This leftward movement of the valve spool 32 operates the valve assembly 14 from the closed condition to an actuated condition in which fluid under pressure is ported from the pressure supply to the gerotor gear assembly 12.
  • the rotor 54 is also rotated in a clockwise direction and a metered flow of fluid is returned to the valve and ported to the steering cylinder through conduit 46.
  • the other motor conduit 44 is connected withdrain through the valve assembly 14.
  • the valve spool 32 Upon rotation of the input shaft 16 in a counterclockwise direction, the valve spool 32 is shifted toward the right and the rotor 54 is rotated in a counterclockwise direction to provide a metered flow of fluid to the motor conduit 44. As the valve spool 32 is shifted toward the right, the torsion blades 66 and 68 are flexed. During continued counterclockwise rotation of the input member 16 and counterclockwise rotation of the rotor 54 and wobble shaft 74 about their central axes, the torsion blades 66 and 68 are maintained in a flexed or twisted condition. However, upon interruption of counterclockwise rotation of the input shaft 16, the stored energy in the torsion blades acts as described above.
  • torsion coupling 18 has been formed by a pair of torsion blades 66 and 68 in the illustrated embodiment of the invention, it is contemplated that either a greater or lesser number of torsion blades could be utilized. However, it should be noted that the utilization of a plurality of torsion blades 66 and 68 enables the desired spring rate to be obtained with torsion blades of a relatively short axial length.
  • An apparatus for use in controlling a flow of fluid comprising a housing having first and second outlet ports, gerotor gear means connected with said housing and operable in one direction to provide a metered flow of fluid to said first outlet port and operable in another direction to provide a metered flow of fluid to said second outlet port, commutator valve means associated with said gerotor gear means for dirccting fluid to and from said gerotor gear means.
  • directional control valve means for porting fluid to said commutator valve means and for porting fluid received from said commutator valve means to one of said outlets, said directional control valve means including a valve member movable in a first direction from an initial position to a first actuated position to port a flow of fluid to said commutator valve means and to port fluid from said commutator valve means to said first outlet and movable in a second direction from the initial position to a second actuated position to port a flow of fluid to said commutator valve means and to port fluit from said commutator valve means to said second outlet, an input member operatively connected with said valve member, said input member being rotatable in a first direction to effect movement of said valve member from said initial position to said first actuated position and being rotatable in a second direction to effect movement of said valve member from said initial position to said second actuating position, resiliently twistable blade means operatively connected with said input member and said directional central valve means for storing energy to effect movement
  • gerotor gear means includes an internally toothed stator member and an externally toothed rotor member circumscribed by said stator member, said rotor member having one less tooth than said stator member and being rotatable about its own central axis and orbital about the central axis of said stator member during operation of gerotor gear means.
  • said blade means includes a blade member having major sides of a first area and minor sides of a second area which is substantially less than said first area.
  • said blade means includes a pair of blade members each of which has one end portion connected with said input member and another end portion connected with said gerotor gear.
  • An apparatus for use in controlling a flow of fluid comprising a housing having first and second outlet ports, gerotor gear means connected with said housing and operable in one direction to provide a metered flow of fluid to said first outlet port and operable in another direction to provide a metered flow of fluid to said second outlet port, commutator valve means associated with said gerotor gear means for directing fluid to and from said gerotor gear means, directional control valve means for porting fluid to said commutator valve means and for porting fluid received from said commutator valve means to one of said outlets, said directional valve means including a valve member movable in a first direction from an initial position to a first actuated position to port a flow of fluid to said commutator valve means and to port fluid from said commutator valve means to said first outlet and movable in a second direction from the initial position to a second actuated position to port a flowv offluid to said commutator valve means and to port fluid from said commutator valve means to said
  • said second head end portion of said wobble shaft includes surface means for defining a slot in the second head end portion of said wobble shaft, said end portion of said blade means being disposed in said slot.
  • An apparatus for use in controlling a flow of fluid comprising a housing, gerotor gear means connected with said housing and operable in one direction to provide a metered flow of fluid to a first port and operable in another direction to provide a metered flow of fluid to a second port, valve means for porting fluid to said gerotor gear means, said valve means including a valve member movable in a first direction from an initial position to a first actuated position to port a flow of fluid to said gerotor gear means during operation of said gerotor gear means in the one direction and movable in a second direction from the initial position to a second actuated position to port a flow of fluid to said gerotor gear means during operation of said gerotor gear means in the other direction, an input member connected with said valve member, said input member being rotatable in a first direction in response to one input force to effect movement of said valve member from said initial position to said first actuated position and being rotatable in a second direction in response to another input force to effect movement
  • An apparatus as set forth in claim 7 further including first surface means fixedly connected with said input member for engaging'said convexly curved major sides of each of said blade members and pressing said blade members toward each other to provide a tight connection between said blade members and said input member, and second surface means connected with said valve member for engaging said convexly curved major sides of each of said blade members and pressing said blade members toward each other to provide a tight connection between said blade member and said valve member.
  • said apparatus comprising a housing having an inlet port and a pair of outlet ports, metering means located in said housing and operable to provide a metered flow of fluid, said metering means including an internally toothed member and an externally toothed member disposed in meshing engagement and supported for relative orbital and rotational movements, valve means located in said housing and operable from an initial condition to an actuated condition to port fluid to said metering means and to port fluid from said metering means to a selected one of said outlet ports, a shaft having a first head end portion connected with said externally toothed member for movement therewith and a second head end portion connected with said valve means, a rotatable input member, and means for enabling operation of said valve means from the initial condition to an actuated condition in response to rotation of said input member and for storing energy to effect operation of said valve means from an actuated condition to said initial condition, and means including a pair of resiliently twistable blade having a first end portion connected with said input member and a second end portion connected directly to
  • An apparatus for use in controlling a flow of fluid comprising a housing having an inlet port and a pair of outlet ports, metering means located in said housing and operable to provide a metered flow of fluid, said metering means including an internally toothed member and an externally toothed member disposed in meshing engagement and supported for relative orbital and rotational movements, valve means located in said housing and operable from an initial condition to an actuated condition to port fluid to said metering means and to port fluid from said metering means to a selected one of said outlet ports, a shaft having a first head end portion connected with said externally toothed member for movement therwith and a second head end portion connected with said valve means, a rotatable input member, and means for enabling operation of said valve means from the initial condition to an actuated condition in response to rotation of said input member and for storing energy to effect operation of said valve means from an actuated condition to said initial condition, said means including a pair of resiliently twistable blade having a first end portion connected

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Automation & Control Theory (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Power Steering Mechanism (AREA)
US443463A 1974-02-19 1974-02-19 Gerotor fluid controller with twistable blade energy storing means Expired - Lifetime US3918856A (en)

Priority Applications (16)

Application Number Priority Date Filing Date Title
US443463A US3918856A (en) 1974-02-19 1974-02-19 Gerotor fluid controller with twistable blade energy storing means
DK29175AA DK135224B (da) 1974-02-19 1975-01-29 Apparat til styring af en fluidumstrøm, især til hydrostatisk servostyring af et køretøj.
AU77924/75A AU486487B2 (en) 1974-02-19 1975-02-05 Gerotor fluid controller with twistable blade energy storing means
CA219,398A CA1017224A (en) 1974-02-19 1975-02-05 Fluid controller
DE2505569A DE2505569C2 (de) 1974-02-19 1975-02-10 Druckmittelsteuerung für Servolenkungen oder dgl.
IE259/75A IE40801B1 (en) 1974-02-19 1975-02-10 Fluid controller
GB562475A GB1475206A (en) 1974-02-19 1975-02-10 Fluid controller
BE153321A BE825487A (fr) 1974-02-19 1975-02-13 Regulateur pour circuit fluidique
FR7504520A FR2261435B1 (en, 2012) 1974-02-19 1975-02-13
LU71870A LU71870A1 (en, 2012) 1974-02-19 1975-02-18
BR986/75A BR7500986A (pt) 1974-02-19 1975-02-18 Aparelho aperfeicoado para utilizacao no controle do fluxo de fluido
JP2030875A JPS5443253B2 (en, 2012) 1974-02-19 1975-02-18
AT124575A AT339745B (de) 1974-02-19 1975-02-19 Vorrichtung zur verwendung bei der regelung eines fluidstromes, insbesondere bei servolenkungen in kraftfahrzeugen
NLAANVRAGE7501980,A NL175048C (nl) 1974-02-19 1975-02-19 Inrichting voor vloeistofstroomregeling.
SU752110470A SU791264A3 (ru) 1974-02-19 1975-02-19 Устройство дл управлени потоком текучей среды
IT20420/75A IT1031858B (it) 1974-02-19 1975-02-19 Apparecchio regolatore di fluido

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US443463A US3918856A (en) 1974-02-19 1974-02-19 Gerotor fluid controller with twistable blade energy storing means

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US3918856A true US3918856A (en) 1975-11-11

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US443463A Expired - Lifetime US3918856A (en) 1974-02-19 1974-02-19 Gerotor fluid controller with twistable blade energy storing means

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US (1) US3918856A (en, 2012)
JP (1) JPS5443253B2 (en, 2012)
AT (1) AT339745B (en, 2012)
BE (1) BE825487A (en, 2012)
BR (1) BR7500986A (en, 2012)
CA (1) CA1017224A (en, 2012)
DE (1) DE2505569C2 (en, 2012)
DK (1) DK135224B (en, 2012)
FR (1) FR2261435B1 (en, 2012)
GB (1) GB1475206A (en, 2012)
IE (1) IE40801B1 (en, 2012)
IT (1) IT1031858B (en, 2012)
LU (1) LU71870A1 (en, 2012)
NL (1) NL175048C (en, 2012)
SU (1) SU791264A3 (en, 2012)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0061005A1 (en) * 1981-03-13 1982-09-29 Trw Inc. Fluid control system
EP0092637B1 (en) * 1982-04-23 1986-03-05 Trw Inc. Apparatus with staged pressure differential for controlling fluid flow
CN115735074A (zh) * 2020-06-23 2023-03-03 米兰综合工科大学 具有用于控制管道中的流体流动的侧向流动阀的能量回收阀系统

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2919051C2 (de) * 1979-05-11 1986-09-18 Zahnradfabrik Friedrichshafen Ag, 7990 Friedrichshafen Hydrostatische Hilfskraftlenkung
DE2919050A1 (de) 1979-05-11 1980-11-13 Zahnradfabrik Friedrichshafen Hydrostatische hilfskraftlenkung, insbesondere fuer kraftfahrzeuge
DE3037660C2 (de) * 1980-10-04 1982-12-02 Zahnradfabrik Friedrichshafen Ag, 7990 Friedrichshafen Hydrostatische Hilfskraftlenkung
US4457132A (en) * 1981-11-05 1984-07-03 Trw Inc. Control apparatus
EP0107829B2 (en) * 1982-10-29 1993-03-24 Trw Inc. Hybrid load sense vehicle hydrostatic steering system
GB2134054B (en) * 1983-01-31 1986-05-29 Mo N Proizv Ob Str Dorozh Mash Hydraulic power steering assembly

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2243900A (en) * 1938-10-12 1941-06-03 Fulcher Frank Christian Flexible driving coupling
US3360932A (en) * 1966-05-05 1968-01-02 Int Harvester Co Rotary emittance valve
US3385057A (en) * 1964-08-25 1968-05-28 Trw Inc Hydraulic controller
US3597128A (en) * 1969-04-10 1971-08-03 Trw Inc Hydraulic device having hydraulically balanced commutation

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3443378A (en) * 1967-04-04 1969-05-13 Trw Inc Hydrostatic single unit steering system
US3528521A (en) * 1968-06-13 1970-09-15 Allis Chalmers Mfg Co Hydraulic steering system

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2243900A (en) * 1938-10-12 1941-06-03 Fulcher Frank Christian Flexible driving coupling
US3385057A (en) * 1964-08-25 1968-05-28 Trw Inc Hydraulic controller
US3360932A (en) * 1966-05-05 1968-01-02 Int Harvester Co Rotary emittance valve
US3597128A (en) * 1969-04-10 1971-08-03 Trw Inc Hydraulic device having hydraulically balanced commutation

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0061005A1 (en) * 1981-03-13 1982-09-29 Trw Inc. Fluid control system
EP0183279A3 (en) * 1981-03-13 1986-07-30 Trw Inc. Hydrostatic load-sense steering system
EP0187682A3 (en) * 1981-03-13 1986-07-30 Trw Inc. Hydrostatic load-sense steering system
EP0092637B1 (en) * 1982-04-23 1986-03-05 Trw Inc. Apparatus with staged pressure differential for controlling fluid flow
CN115735074A (zh) * 2020-06-23 2023-03-03 米兰综合工科大学 具有用于控制管道中的流体流动的侧向流动阀的能量回收阀系统

Also Published As

Publication number Publication date
GB1475206A (en) 1977-06-01
IE40801B1 (en) 1979-08-15
CA1017224A (en) 1977-09-13
AT339745B (de) 1977-11-10
DK135224C (en, 2012) 1977-08-29
FR2261435A1 (en, 2012) 1975-09-12
IE40801L (en) 1975-08-19
DE2505569A1 (de) 1975-08-21
BR7500986A (pt) 1975-12-02
FR2261435B1 (en, 2012) 1980-08-08
DE2505569C2 (de) 1983-09-08
JPS5443253B2 (en, 2012) 1979-12-19
NL175048B (nl) 1984-04-16
BE825487A (fr) 1975-05-29
DK29175A (en, 2012) 1975-10-20
NL175048C (nl) 1984-09-17
NL7501980A (nl) 1975-08-21
IT1031858B (it) 1979-05-10
AU7792475A (en) 1976-08-05
SU791264A3 (ru) 1980-12-23
LU71870A1 (en, 2012) 1975-06-24
JPS50117135A (en, 2012) 1975-09-12
ATA124575A (de) 1977-02-15
DK135224B (da) 1977-03-21

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