US3561488A - Fluid flow control valve - Google Patents

Fluid flow control valve Download PDF

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Publication number
US3561488A
US3561488A US3561488DA US3561488A US 3561488 A US3561488 A US 3561488A US 3561488D A US3561488D A US 3561488DA US 3561488 A US3561488 A US 3561488A
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Prior art keywords
spool
pressure
fluid
valve
stage
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James Otto Byers
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Lockheed Corp
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Sanders Associates Inc
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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
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • 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
    • 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
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/042—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure
    • F15B13/043—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure with electrically-controlled pilot valves
    • F15B13/0438—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure with electrically-controlled pilot valves the pilot valves being of the nozzle-flapper 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20538—Type of pump constant capacity
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/255—Flow control functions
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/26—Power control functions
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/3056—Assemblies of multiple valves
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/329—Directional control characterised by the type of actuation actuated by fluid 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/515—Pressure control characterised by the connections of the pressure control means in the circuit
    • F15B2211/5151—Pressure control characterised by the connections of the pressure control means in the circuit being connected to a pressure source and a directional control valve
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/52—Pressure control characterised by the type of actuation
    • F15B2211/528—Pressure control characterised by the type of actuation actuated by fluid 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/635—Circuits providing pilot pressure to pilot pressure-controlled fluid circuit elements
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7051—Linear output members
    • F15B2211/7053—Double-acting output members
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/75—Control of speed of the output member
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/76—Control of force or torque of the output member
    • 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
    • Y10T137/86582—Pilot-actuated
    • Y10T137/8659—Variable orifice-type modulator
    • Y10T137/86598—Opposed orifices; interposed modulator
    • 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
    • Y10T137/86582—Pilot-actuated
    • Y10T137/86606—Common to plural valve motor chambers
    • 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
    • Y10T137/86582—Pilot-actuated
    • Y10T137/86614—Electric

Definitions

  • a subsidiary object is to provide such a valve in which feedback from the load is not required.
  • Another object is to provide a two stage valve in which the rate of flow of fluid to the load is directly proportional to the rate of flow of fluid through the first stage.
  • Another object is to provide a two-stage valve in which exact spacing of the second stage metering lands is not required.
  • Another object is to provide a valve which is not unduly sensitive to wear of the metering lands.
  • the second-stage housing and spool are formed so that, when this spool is displaced from a reference position by a control pressure from the first stage, a first passageway is opened which allows fluid to flow from the first stage to the load port. This flow tends to reduce the control pressure.
  • An opposing bias pressure which may be obtained from the first stage or from the fluid supply for the second stage, cooperates with the control pressure to position the spool so that for any input signal to the first stage, there is a corresponding rate of flow of fluid from the first stage to the load port.
  • the spool and housing are also formed so that a second passageway is opened simultaneously with the first which allows fluid to flow from the second-stage supply to the same load port.
  • the two passageways have a predetermined, fixed ration of cross-sectional areas and the control pressure and the second-stage supply pressure are made equal with the result that the flow through the second passageway is proportional to that through the first. Accordingly, the rate of flow of fluid to the load depends solely on the input signal and is independent of load pressure.
  • FIG. 1 is a schematic cross-sectional view of a flow control valve incorporating the invention
  • FIG. 2 is a cross-sectional view taken on the line 2-2 of FIG. 1;
  • FIG. 3 is a pictorial view of one of the elements of the valve of FIG. 1 before its assembly with the remaining elements;
  • FIG. 4 is a schematic cross-sectional. view of another flow control valve incorporating the invention.
  • FIG. 5 is a fragmentary cross-sectional view of a modification of the valve shown in FIG. 4;
  • FIG. 6 is a schematic cross-sectional view of another valve incorporating the invention.
  • FIG. 7 is a cross-sectional view taken on the line 7-7 of FIG. 6;
  • FIG. 8 is a cross-sectional view taken on the line 8-8 of FIG. 7;
  • FIG. 9 is a pictorial view of one of the elements of the valve of FIG. 6 before its assembly to the remaining elements.
  • FIG. 10 is a cross-sectional view of an alternative form of pressure-reducing valve which may be used with the invention.
  • a housing Ill is formed with a hollow cylinder which, in turn, is formed with a centrally located port 12 and with ports 13 and I4 on either side thereof.
  • a spool 15 formed with a central land 16 which, when in the neutral position, is line on line" with the port 12.
  • the spool 15 also includes lands l7 and 18 on either end thereof.
  • Ports 13 and 14, which are positioned on either side of land 16, are connected by conduits 21 and 22 respectively to the second stage of the valve.
  • the central port 16 is connected by means of a conduit 23 to a source central port 16 is connected by means of a conduit 23 to a source of fluid under pressure, 24, having a pressure designated as PI.
  • Centering springs 25 and 26 bear against opposite ends of the cylinder and against lands 17 and 18 respectively, and normally hold the spool in the central position shown.
  • the end spaces containing these springs are connected to the fluid return, or sump.
  • a force motor 27 is mechanically connected to the spool 15 and acts in the usual manner to accept an input signal, and in response thereto, to displace the spool 15 from the reference position shown.
  • the housing 11 is also formed with a second cylinder including ports 31 and 32 connected by means of conduits 33 and 34 respectively to an actuator 35 which is the useful load device.
  • the second cylinder also includes a port 36 connected to the return and a port 37 connected by means of a conduit 38 to the low-pressure side of a pressure-reducing valve 39, the high-pressure side of which is connected to the source 24.
  • the pressure of the fluid applied to the: port 37 is designated P2.
  • the second cylinder contains a spool 41 formed with lands 42, 43, and 44. To the left of the spool 41, as shown in FIG. I, is a second spool which is a mirror image of the spool 41 and whose various portions are designated by similar but primed reference characters.
  • the conduits 21 and 22 are connected to the left and right ends respectively of the cylinder so that the fluid pressures therein bear against lands 42' and 42 respectively.
  • the space between lands 44 and 44 is connected to the conduit 38 so as to be subjected to the pressure P2.
  • Port 32' is connected to the port 31 and port 31' is connected to the port 32.
  • the spool 41 is formed with a central bore which extends from the right end thereof as far as the land 44.
  • the spool 41' is formed with a bore which extends from the left end thereof as far as the land 44.
  • An important part of the present invention is the portion of the spool between lands 43 and 44. As best shown in FIGS. 2 and 3, a generally flat central portion 45Lextends from the land 43. At the extreme left end, it is formed with a slot 46 which divides this portion into two tongue members 47 and 48. The slot 46 communicates with the bore in the spool.
  • This portion of the spool is first made as a component separate from the land 44, as shown in FIG. 3. It is then placed against the flat right-hand face of he land 44 and brazed or welded thereto. When placed within the cylindrical chamber in the housing 11, there are defined a chamber 49 between the tongue mem- 5 FIG.
  • the right-hand edge of the land 44 is approximately on line with the right-hand edge of the port 31 and just occludes it. It can be seen that if the spool 41 be moved to the left, a first passageway will be opened between the chamber 49 and the port 32 and at exactly the same time a second passageway will be opened between the chambers 51 and 52 and the port 31.
  • the pressure in the conduit 22, designated P3 will be equal to the pressure P2 in the chamber 53 between the lands 44 and 44'. This must necessarily be so because if the pressure P3 should tend to increase above P2, the spool 43 would move slightly to the left thereby opening the passageway between the chamber 49 and the port 31 and allowing fluid to flow. This flow would then reduce the pressure P3 until it equalled the pressure P2. On the other hand, if P3 should drop below P2, then the spool 41 would be moved to the right and flow would be shut off and the leakage through the first stage would tendto raise the pressure P3 until it equalled P2.
  • a certain amount of fluid will be flowing from the conduit 22 to the port '31. Let us designate this flow as 0,. As best shown in FIG. 2, it is seen that this flow occurs through a passageway whose cross-sectional area is proportional to the distance A between the tongue members 47 and 48. At the same time, fluid will also flow from the chambers 51 and 52 to the port 31. This flow will be through a passageway whose cross-sectional area is proportional to the distance B. Since the pressure in chambers 51 and 52 is also equal to P2, the flow of fluid from the second-stage supply will be in the ratio of these areas or will be equal to Q B/A. The total flow to the load conduit 33 will be equal to plus Q B/A regardless of the load pressure. For any input signal to the force motor 27 there is a definite corresponding flow of fluid through the first stage and therefore there is also a corresponding proportional flow through the second stage.
  • the secondstage spools are automatically adjusted at the neutral position so that the leakage rate of the first stage is passed. Therefore, exact spacing of the various lands is unnecessary. Similarly, wear of the metering lands has little or no effect. Likewise, it is not necessary that the lands 44 and 43 open the ports 31 and 32 respectively at exactly the same time because nothing can flow until both are open.
  • the gain of the valve can be varied by varying the setting of the pressure reducing valve 39. Reduction of the pressure P2 with respect to P1 makes for greater sensitivitybecause the pressure drop across the first stage is Pl minus'P2. However, P2 must be great enough to provide adequate flow of the fluid to the load.
  • FIG. 4 Another embodiment of the invention is shown in FIG. 4.
  • the first stage is a flapper valve instead of a spool valve.
  • a source 61 of fluid under pressure is connected through two restrictors 62 and 63 to nozzles 64 and 65 respectively positioned within a chamber 66 and the flow from which nozzles is directed to opposite side of a flapper or vane 67.
  • the chamber 66 is connected to the return or sump.
  • a motor 69 which may be either a force motor or a torque motor. controls the position of the vane 67.
  • the second stage includes a spool 71 which operates in a hollow cylinder formed in a housing 72 formed with ports 73 and 74 connected to the return and with ports 75 and 76 connected to opposite sides of a load device 77.
  • a port 78 is connected to the low-pressure side of a pressure reducingvalve 79, the high-pressure side of which is connected to the source 61.
  • the pressure of the source will be denoted as P1 and that at the port 78 as P2.
  • the spool 71 is formed with lands 81, 82, 83 and 84. Conduits 85 and 86' lead from the nozzles 64 and 65 respectively to the left and right ends respectively of the spool 71.
  • the spool 71 is formed with a bore which extends from the left hand end, as viewed in FIG. 4 as far as the land 82.
  • the section designated A-A is identical to that designated 2-2 in FIG. 1 and is as illustrated in FIG. 2.
  • a stop ring 88 is placed to the left of the spool 71 to limit its leftward travel.
  • a second spool 71 is substantially identical to the spool 71 except that it is turned end for end with respect thereto.
  • the various parts are designated by the same reference characters as those for spool 71 except that they are primed.
  • the spool 71 operates in a similar cylinder formed with similar ports.
  • Conduits 85 and 86 are connected to the left and right ends of the spool 71 respectively.
  • the section designated B-B is identical to that designated A-A.
  • Tl-le neutral position of the first stage is defined as the position of the flapper 67 at which the pressure in the conduits leading to the orifices is thesame, provided there is no flow, or are equal rates of flow, in the conduits 85 and 86.
  • the spools 71 and 71 will be in' their neutral positions substantially as shown. For example, if the spool 71 were displaced slightly to the right, then fluid would flow from the conduit 85 through the central bore to the port 76 thereby reducing the pressure on the left end of the spool 71 and allowing the pressure in the conduit 86 to return the spool 71 to its neutral position. The stop 88 prevents the spool from going too far to theleft. Similarly, if the spool 71 were unbalanced, a similar sequence of events would return it to the neutral position. At this position there is no flow of fluid to the load 77.
  • the opposing pressures which position the spool are both taken from the first stage of the valve rather than taking one from the first stage and the other from the supply to the second stage. It is also to be noted that there is no dead space in this embodiment either and that as soon as there is an input signal, fluid starts to flow to the load. It is also to be noted that since the spools position themselves in accordance with flow rates and pressure drops, there is automatic compensation for wear.
  • FIG. 4 When operating certain types of load devices, it is desirable that there be a dead space, that is that there be no movement of the load device until the input signal has reached a predetermined amount, positive or negative.
  • the embodiment of FIG. 4 can readily be modified to achieve such a condition. As shown in FIG. 5, a spring 89 is placed in the space between the left end of the land 81' and the end of the cylinder and a similar spring would be placed to the right of the land 81 of the spool 71. Then there would be no flow of fluid to the load until the input signal were sufficient to raise the pressure in one of the conduits 85 or 86 sufficiently to overcome the spring pressure.
  • the pilot stage is also a flapper valve.
  • a source of fluid 91 is connected to restrictors 92 and 93 which in turn are connected to nozzles 94 and 95 respectively, which act on opposite sides of a vane or flapper 96 which is positioned by a force motor 97.
  • Conduits 98 and 99 lead from the nozzles 94 and 95 to the second stage.
  • the second stage includes a housing 101 in which is formed a hollow cylinder and which is also formed with ports 102 and 103 leading to the return; with ports 104 and 105 communicating with the load device 106; and with a port 107 to which is connected a conduit 108 leading to the low-pressure side of a pressure-reducing valve 109, the high-pressure side of which is connected to the source 91.
  • a single piston 111 formed with a land 112 on the right-hand end, a land 113 on the left end, and with a central land 114. Both ends of the cylinder are stepped as shown. defining end spaces, in which washers 115 and 116 are placed.
  • a pair of springs 117 and 118 are placed in the right and left end spaced respectively and bear. against the washers 115 and 116 which in turn bear against the lands 112 and 113 so as to center the spool 111.
  • the conduits 98 and 99 communicate with ports 119 and 120 respectively which in turn communicate, by means of internal passageways, with the end spaces containing the springs 117 and 118 respectively.
  • the flow control cham bers and passageways are formed in the housing instead of in the spool.
  • a segment 121 is formed as a separate piece and later joined to the remaining parts. As shown in FIG. 7, 8 and 9 the segment 121 is generally cylindrical in shape and has a central cylindrical bore. Each end face has formed therein two diametrically opposite holes 122 and 123 which extend inward a short distance. Slots 124 and 125 communicate with these holes and with the central bore. These holes and slots together with the land 114 of the spool 111 define chambers. As shown schematically in FIG. 6 by dotted lines the holes 122 and 123 communicate with the part 120 and the holes 126 and 127 on the other side communicate with the port 119.
  • Each end of the segment 121 is also formed with four recesses 131, 132, 133 and 134, each of which extends completely through the segment from the outside to the central bore. These recesses cooperate with the land 114 to define chambers. All of these chambers communicate with the port 107 and the conduit 108.
  • the segment 121 is made as a separate piece and then welded or brazed to the flat faces of the housing 101. It is apparent that, as the spool 111 is displaced one way or the other, the chambers defined by the holes 122, etc., and the chambers defined by the recesses 131, etc., are all opened simultaneously.
  • the total flow to the load will be directly proportional to the flow from the first stage through the conduit 98 in an amount determined by the flow through conduit 98 and by the ration of the lengths of he recesses 131-134 to the lengths of the slots 124-127, all as measured along the circumference of the cylindrical bore. More particularly, if the length of each recess by denoted by R, the length of each slot be denoted by S, and the flow through conduit 98 (and the slots) be denote d by 0,, then, since there are four recesses and two slots, the total flow will be equal to Q plus Q, X ZR/S. As in the previously described embodiments, this flow likewise will be independent of load pressure.
  • FIG. 10 An alternative form of pressure reducing valve is indicated generally by the reference character 14l1 in FIG. 10.
  • the valve comprises a piston 142, moveable in a cylinder, and formed with lands 143 and 144.
  • the end space to the right of the land 143 communicates with a conduit 145 intended for connection to a source of control pressure
  • the end space to the left of the land 144 communicates, by means of internal passageways 146 in the piston 142, with the space between the lands 143 and 155.
  • a conduit 147 is connected to this space.
  • a port 148 is connected to a source of fluid pressure.
  • the conduit 147 is connected to the device the pressure of which is to be controlled, that is, to port 78 of FIG. 4 or to conduit 108 of FIG. 6.
  • the conduit 145 si connected to the reference pressure, that is, to conduit 86 of FIG. 4 or to conduit 98 of FIG. 6.
  • Fluid from source Pl starts to flow to conduit 147 but also shifts the piston 142 to the right, thereby shutting off the flow.
  • the piston 142 is shifted to the left, opening port 148.
  • An equilibrium position is soon reached with the pressure in conduit 147 equal to that in conduit 145, without requiring any flow of fluid from the conduit 145.
  • valve 141 instead of the valve 79 or the valve 109 makes the pressure P2 precisely equal to that in the conduits 86 or 98, thereby increasing the accuracy of the independence of flow rate from load pressure.
  • FIG. 6 is preferred in some cases, especially if a dead space in the neutral position is desired, because it contains but one spool and is therefore somewhat simpler.
  • FIGS. 1 or 4 may be preferred in some cases, because these embodiments may be made to have no dead space whatsoever and are much less affected by wear of the metering lands. in any case, however, the all important flow control passageways can be formed either in the spools or in the surrounding sleeves or housings.
  • a valve for controlling the flow of fluid to a load comprising:
  • a first stage for generating a fluid control pressure in a conduit in response to an input signal
  • a second stage including a housing formed with a hollow cylinder and a spool moveable therein, said housing and spool being formed to define a passageway from said conduit to said load which passageway is closed when said spool is in its reference position and which opens as said spool is displaced therefrom;
  • a valve for controlling the flow of fluid to a load comprising:
  • a first stage including a first source of fluid under pressure for generating a control pressure in response to an input signal
  • a second stage including a housing formed with a hollow cylinder and a spool moveable therein to and from a reference position in response to said control pressure for controlling the flow of fluid to said load;
  • said housing and spool being formed so that, with said spool displaced from said reference position, they define first and second passageways communicating with said control pressure and with said second source respectively and both communicating with said load.
  • a valve in accordance with claim 2 in which said housing and spool are formed so that upon displacement of said spool from said reference position said first and second passageways open simultaneously.
  • a valve for controlling the flow of fluid to a load comprising:
  • a second stage including a housing formed with a hollow cylinder and a spool moveable therein, means for applying a force derived from said control pressure and an opposing biasing force to said spool, whereby said spool is moved when said forces are unequal;
  • said said housing and spool being formed to define a first passageway from said conduit to said load which passageway is closed when said spool is in its reference position and which opens when said spool is displaced therefrom, whereby when said control pressure increases, said spool is displaced from said reference position and said passageway opens until the flow of fluid therethrough chambers and reduces said control pressure and the force derived therefrom to again equal said biasing force;
  • said housing and spool also being formed to define a second passageway from said source to said load which passageway is opened and closed simultaneously with said first passageway.
  • a valve in accordance with claim 5 including means for substantially equalizing the pressure in said conduit and the pressure of said source.
  • a valve for controlling the flow of fluid to a load comprising:
  • a second stage including a housing formed with a hollow cylinder and a spool therein, said housing and spool being formed to define and open a first passageway from said conduit to said load upon displacement of said spool from a reference position, said second stage including an operative connection to said conduit for displacing said spool until the flow through the aforesaid passageway is sufiicient to reduce said control fluid pressure to equal a reference pressure applied to said spool;
  • said housing and spool also being formed to define and open a second passageway from a source of fluid under pressure to said load simultaneously with the opening of said first passageway.
  • a valve in accordance with claim 9 win which said reference pressure is said source.
  • a valve in accordance with claim 9 win which said reference pressure is derived from said first stage.
  • a valve in accordance with claim 9 in which said first stage includes an additional conduit and in which said control pressure comprises a differential pressure generated between said conduits in a sense determined by the sense of said input signal.
  • a valve in accordance with claim 14 including an additional spool operating in said hollow cylinder coaxially with the aforesaid spool and in which said conduits are operatively connected to opposite remote ends of said spools and in which said source is operatively connected to the space between said spools.
  • a valve in accordance with claim 14 including an additional hollow cylinder formed in said housing and an additional spool both substantially identical to the aforesaid cylinder and spool and in which said conduits are connected to opposite ends of both of said cylinders in such a sense as to render said spools and cylinders operative alternatively depending upon the sense of said input signal.
  • a valve for controlling the flow of fluid to a load comprising:
  • a first stage for generating a control pressure in a conduit in response to an input signal
  • a second stage including a housing having a hollow cylinder and a spool moveable therein to and from a reference position in response to said control pressure;
  • a source of fluid under pressure connected to said second stage; and said cylinder and spool being formed to define first and second chambers communicating with said conduit and with said source, respectively, and which, upon movement of said spool away from said reference position, open simultaneously into a third chamber communicating with said load.
  • a valve in accordance with claim 17 in which said first and second chambers are defined by portions of said spool and the inner surface of said cylinder.
  • a two-stage valve for controlling the flow of fluid to a load comprising:
  • first stage including a first source of fluid under pressure for generating a fluid pressure differential in first and second conduits in response to an input signal;
  • second stage including a second source of fluid under a pressure less than that of said first source; said second stage including a housing having a bore and a spool moveable therein to and from a reference position;
  • said housing and spool being formed to define first and second chambers communicating with said first conduit and with said second source respectively and which, upon movement of said spool away from said reference position, open simultaneously into a third chamber through first and second passageways respectively, said third chamber communicating with said load, whereby when the pressure in said first conduit exceeds that in said second conduit, said spool is displaced from said reference position and opens said first passageway until the flow of fluid therethrough reduces the pressure in said first conduit to equal that in said second conduit.
  • a valve in accordance with claim 20 in which said housing and spool are also formed to define fourth, fifth and sixth chambers similar to said first, second and third chambers respectively, said fourth and fifth chambers communicating with said second conduit and with said second source respectively, said third and sixth chambers communicating with said load through different connections, whereby when the pressure in said second conduit exceeds that in said first conduit, fluid flows from said fourth and fifth chambers through said sixth chamber to said load.
  • a valve according to claim 20 in which said spool includes a central land and first and second lands on opposite sides thereof and in which said first and second chambers are defined by openings in said housing and the outer surface of said central land.
  • a valve in accordance with claim 24 including first and second centering springs bearing against said first and'second lands respectively.
  • a two-stage fluid flow control valve for controlling the flow of fluid to a load comprising:
  • a first stage including a first source of fluid under pressure for generating a fluid pressure differential in first and second conduits in response to an input signal;
  • a second stage including a second! source of fluid under a pressure less than that of said first source
  • said second stage including a housing having an axial bore and a spool moveable therein and fluid connections from said first and second conduits to said bore at opposite ends of said spool;
  • said housing including a centrally positioned segment formed with first and second chambers communicating with said first and second conduits respectively and both communicating with said boreysaid segment also being formed with a recess communicating with said second source and with said bore;
  • said spool including a central land cooperating with said segment to close said chambers and said recess from communication with said bore when in a reference position and to open said first and second chambers to said bore on opposite sides of said land upon'displacement of said spool from said reference position in first and second directions respectively and to open said recess to said bore, simultaneously with the opening of either of said chambers;
  • said housing including first and second ports communicating with said bore on opposite sides of said reference position of said land and communicating with firs and second load conduits respectively, whereby, upon receipt of a signal said first stage generates a pressure differential which displaces said spool causing fluid to flow from one of said conduits to said load and also from said second source to said load.
  • a valve in accordance with claim 26 in which first and second centering springs bear against opposite ends of said spool to maintain in a reference position in the absence of a signal having a predetermined threshold magnitude.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Servomotors (AREA)
  • Multiple-Way Valves (AREA)
  • Fluid-Pressure Circuits (AREA)
US3561488D 1969-07-01 1969-07-01 Fluid flow control valve Expired - Lifetime US3561488A (en)

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US83806269A 1969-07-01 1969-07-01

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US (1) US3561488A (ja)
JP (1) JPS5012558B1 (ja)
BE (1) BE752583A (ja)
CA (1) CA931855A (ja)
CH (1) CH538054A (ja)
DE (1) DE2032395C3 (ja)
FR (1) FR2056329A5 (ja)
GB (1) GB1273297A (ja)
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SE (1) SE350574B (ja)

Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3742981A (en) * 1972-02-24 1973-07-03 Sanders Associates Inc Flow control valve with single spool second stage
US3805674A (en) * 1971-11-24 1974-04-23 Westinghouse Bremsen Apparate Hydraulic pressure control valve
JPS517528A (ja) * 1974-07-08 1976-01-21 Fujikoshi Kk Atsuryokuhoshotsukiryuryoseigyoben
US4006663A (en) * 1973-02-07 1977-02-08 Danfoss A/S Hydraulic control means, especially a steering means
US4052929A (en) * 1973-02-07 1977-10-11 Danfoss A/S Hydraulic control means, especially a steering means
US4094229A (en) * 1974-11-05 1978-06-13 Leonard Willie B Fluidic repeater
US4215623A (en) * 1978-04-12 1980-08-05 Sanders Associates, Inc. Hydraulic velocity and acceleration control system
DE2932847A1 (de) * 1979-08-14 1981-02-26 Danfoss As Hydraulische steuervorrichtung fuer einen servomotor, insbesondere fuer fahrzeuglenkungen
DE2941938A1 (de) * 1979-10-17 1981-04-30 Danfoss A/S, 6430 Nordborg Hydraulischer verstaerker fuer einen servomotor
DE3411261A1 (de) * 1983-04-27 1984-10-31 Závody těžkého strojírenství Výzkumný ústav stavebních a zemních stroju, Brünn/Brno Hydraulische, zweistufige betaetigungseinrichtung fuer einen servomotor
DE3428403A1 (de) * 1983-08-01 1985-04-11 Závody těžkého strojírenství Výzkumný ústav stavebních a zemních stroju, Brünn/Brno Zweistufige, druckkompensierte hydraulische steuereinrichtung fuer mindestens zwei verbraucher
US4664135A (en) * 1984-05-07 1987-05-12 Sanders Associates, Inc. Pilot valve
WO1993005303A1 (en) * 1991-09-03 1993-03-18 Caterpillar Inc. Pressure compensated flow amplifying poppet valve
WO1999063232A1 (en) 1998-06-05 1999-12-09 J. Otto Byers & Associates Servo positioning system
US20160161013A1 (en) * 2013-08-01 2016-06-09 Moog Controls Limited Improvements in hydraulic servovalves
US9458905B2 (en) 2012-09-20 2016-10-04 Steelcase Inc. Spring assembly and method
CN109058206A (zh) * 2018-09-29 2018-12-21 吕伟健 一种液压流量控制器

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2534984B1 (fr) * 1982-10-21 1987-04-17 Bennes Marrel Dispositif de commande a distance amplifiee pour un circuit hydraulique

Citations (5)

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US3054388A (en) * 1961-07-03 1962-09-18 Bell Aerospace Corp Servo valve with flow rate feedback
US3228423A (en) * 1956-01-23 1966-01-11 Moog Servocontrols Inc Fluid control valve in which a mechanical motion is transmitted from a dry region to a pressurized fluid filled region
US3357444A (en) * 1965-01-21 1967-12-12 Weston Instruments Inc Fluid flow control
US3363366A (en) * 1965-06-30 1968-01-16 Barnes Drill Co Abrading machine
US3464318A (en) * 1966-06-03 1969-09-02 Moog Inc Servomechanism providing static load error washout

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3228423A (en) * 1956-01-23 1966-01-11 Moog Servocontrols Inc Fluid control valve in which a mechanical motion is transmitted from a dry region to a pressurized fluid filled region
US3054388A (en) * 1961-07-03 1962-09-18 Bell Aerospace Corp Servo valve with flow rate feedback
US3357444A (en) * 1965-01-21 1967-12-12 Weston Instruments Inc Fluid flow control
US3363366A (en) * 1965-06-30 1968-01-16 Barnes Drill Co Abrading machine
US3464318A (en) * 1966-06-03 1969-09-02 Moog Inc Servomechanism providing static load error washout

Cited By (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3805674A (en) * 1971-11-24 1974-04-23 Westinghouse Bremsen Apparate Hydraulic pressure control valve
US3742981A (en) * 1972-02-24 1973-07-03 Sanders Associates Inc Flow control valve with single spool second stage
US4006663A (en) * 1973-02-07 1977-02-08 Danfoss A/S Hydraulic control means, especially a steering means
US4052929A (en) * 1973-02-07 1977-10-11 Danfoss A/S Hydraulic control means, especially a steering means
JPS5838669B2 (ja) * 1974-07-08 1983-08-24 株式会社不二越 アツリヨクホシヨウツキリユウリヨウセイギヨベン
JPS517528A (ja) * 1974-07-08 1976-01-21 Fujikoshi Kk Atsuryokuhoshotsukiryuryoseigyoben
US4094229A (en) * 1974-11-05 1978-06-13 Leonard Willie B Fluidic repeater
US4215623A (en) * 1978-04-12 1980-08-05 Sanders Associates, Inc. Hydraulic velocity and acceleration control system
DE2932847A1 (de) * 1979-08-14 1981-02-26 Danfoss As Hydraulische steuervorrichtung fuer einen servomotor, insbesondere fuer fahrzeuglenkungen
US4364302A (en) * 1979-08-14 1982-12-21 Danfoss A/S Hydraulic control apparatus for a servo-motor, particularly for vehicle steering
DE2941938A1 (de) * 1979-10-17 1981-04-30 Danfoss A/S, 6430 Nordborg Hydraulischer verstaerker fuer einen servomotor
DE3411261A1 (de) * 1983-04-27 1984-10-31 Závody těžkého strojírenství Výzkumný ústav stavebních a zemních stroju, Brünn/Brno Hydraulische, zweistufige betaetigungseinrichtung fuer einen servomotor
DE3428403A1 (de) * 1983-08-01 1985-04-11 Závody těžkého strojírenství Výzkumný ústav stavebních a zemních stroju, Brünn/Brno Zweistufige, druckkompensierte hydraulische steuereinrichtung fuer mindestens zwei verbraucher
US4664135A (en) * 1984-05-07 1987-05-12 Sanders Associates, Inc. Pilot valve
WO1993005303A1 (en) * 1991-09-03 1993-03-18 Caterpillar Inc. Pressure compensated flow amplifying poppet valve
WO1999063232A1 (en) 1998-06-05 1999-12-09 J. Otto Byers & Associates Servo positioning system
US9458905B2 (en) 2012-09-20 2016-10-04 Steelcase Inc. Spring assembly and method
US20160161013A1 (en) * 2013-08-01 2016-06-09 Moog Controls Limited Improvements in hydraulic servovalves
US10344885B2 (en) * 2013-08-01 2019-07-09 Moog Controls Limited Hydraulic servovalves
CN109058206A (zh) * 2018-09-29 2018-12-21 吕伟健 一种液压流量控制器

Also Published As

Publication number Publication date
CA931855A (en) 1973-08-14
NL7008883A (ja) 1971-01-05
GB1273297A (en) 1972-05-03
BE752583A (fr) 1970-12-01
JPS5012558B1 (ja) 1975-05-13
CH538054A (it) 1973-06-15
IL34445A (en) 1973-02-28
IL34445A0 (en) 1970-07-19
SE350574B (ja) 1972-10-30
DE2032395C3 (de) 1978-08-31
DE2032395A1 (de) 1971-01-14
FR2056329A5 (ja) 1971-05-14
DE2032395B2 (de) 1978-01-05

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