US3759292A - Hydraulic control valve assembly - Google Patents

Hydraulic control valve assembly Download PDF

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Publication number
US3759292A
US3759292A US00207028A US3759292DA US3759292A US 3759292 A US3759292 A US 3759292A US 00207028 A US00207028 A US 00207028A US 3759292D A US3759292D A US 3759292DA US 3759292 A US3759292 A US 3759292A
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United States
Prior art keywords
bore
spool
inlet
fluid
control
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Expired - Lifetime
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US00207028A
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English (en)
Inventor
D Bianchetta
K Lohbauer
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Caterpillar Inc
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Caterpillar Tractor Co
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Assigned to CATERPILLAR INC., A CORP. OF DE. reassignment CATERPILLAR INC., A CORP. OF DE. ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: CATERPILLAR TRACTOR CO., A CORP. OF CALIF.
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    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2278—Hydraulic circuits
    • E02F9/2296—Systems with a variable displacement pump
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2221—Control of flow rate; Load sensing arrangements
    • E02F9/2239—Control of flow rate; Load sensing arrangements using two or more pumps with cross-assistance
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2278—Hydraulic circuits
    • E02F9/2292—Systems with two or more pumps
    • 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
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/17—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors using two or more pumps
    • 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
    • F15B13/06—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with two or more servomotors
    • F15B13/08—Assemblies of units, each for the control of a single servomotor only
    • 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
    • F15B2211/20546—Type of pump variable capacity
    • F15B2211/20553—Type of pump variable capacity with pilot circuit, e.g. for controlling a swash plate
    • 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
    • F15B2211/20576—Systems with pumps with multiple pumps
    • 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
    • F15B2211/3059—Assemblies of multiple valves having multiple valves for multiple output members
    • F15B2211/30595—Assemblies of multiple valves having multiple valves for multiple output members with additional valves between the groups of valves for multiple 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
    • F15B2211/30—Directional control
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3105—Neutral or centre positions
    • F15B2211/3116—Neutral or centre positions the pump port being open in the centre position, e.g. so-called open centre
    • 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
    • F15B2211/355—Pilot pressure control
    • 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
    • F15B2211/763—Control of torque of the output member by means of a variable capacity motor, i.e. by a secondary control on the motor
    • 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
    • Y10T137/87169—Supply and exhaust

Definitions

  • This invention relates to valves, and pertains, more particularly, to a plurality of cooperating distributor valves.
  • Backhoes and hydraulic excavators have come into widespread use because of their versatility. They can, for example, serve the function of loaders, ditchers, and small cranes.
  • Still others have proposed a combining of the pumps after the track drive motors with the remaining motors series connected. This results in a system where no fluid is available to downstream motors when the first motor in the series is being operated. That is, the system can supply only the priority upstream demand.
  • Another object of the present invention is to provide a control valve assembly that is operative to maintain a plurality of fluid sources separate for separate operation of a plurality of fluid motors and to automatically combine the flow from the plurality of sources for actuation of selected motors.
  • a further object of the present invention is to provide a hydraulic control valve assembly for combining the output from multiple fluid pumps in order to supply one or more implements with the combined output from the multiple pumps.
  • Another object of the present invention is to provide a valve system having the operative advantages of a series connected system and the combining advantages of a parallel system.
  • a major advantage of the present system is that a plurality of sources can be used independently or can be selectively combined for use.
  • FIG. 1 is a schematic layout of a control system for a hydraulic excavator incorporating the valve assembly of the present invention
  • FIG. 2 is a schematic illustration in section, of an embodiment of the present invention.
  • FIG. 3 is a schematic illustration of a modified form of the present invention.
  • FIG. 4 is a sectional view of a valve assembly constructed in accordance with the present invention.
  • FIG. 5 is a section taken along lines V--V of FIG. 4;
  • FIG. 6 is a section taken along lines VIVI of the valve assembly of FIG. 4;
  • FIG. 7 is a schematic illustration of a further embodiment of the present invention.
  • FIG. 1 there is illustrated a circuit for a hydraulic excavator which is self-propelled and in which all the operations are performed by hydraulic power.
  • the power for the hydraulic system is supplied by two main identical variable displacement pumps 10 and 12, a smaller pump 14 and an auxiliary pump 16, all drawing fluid from a sump or tank 18, and driven by a suitable engine, not shown.
  • the pump 14 may be fixed or variable displacement to suit the needs of the system.
  • the main variable displacement pumps 10 and 12 are suitably connected together by means of a regulator 20 which is responsive to the needs of the system to regulate the pumps 10 and 12 to supply optimum pressure and/or flow as required by the system.
  • the regulator 20 and the unique valve assembly arrangement of the present system cooperate to provide a system having maximum efficiency.
  • the two main pumps 10 and 12 will each supply one half of the working components of the excavator, however, in the interest of safety, the preferred embodiment provides for a separate platform swing circuit, as will be explained later.
  • the valving system provides for combining of the fluid flow from pumps 10 and 12 for selected operation of certain components at a higher rate of movement.
  • the regulator or horsepower limiting means 20 allows the engine output to be distributed to the pumps according to the requirements of each pump. Although both pumps 10 and 12 may'deliver the same quantity of oil, the operating pressure of each will vary according to the function that the excavator is performing. Therefore, the available engine power can be unevenly distributed to the various machine elements in accordance with the power needed at the time.
  • the pump 10 supplies fluid by way of a conduit 22 to a bank of distributor valves comprising distributor spools or valve stems 24, 26 and 28 which are operatively connected to distribute fluid respectively to track drive motor 30, a bucket motor 32, and the boom motors 34.
  • the pump 12 supplies fluid along the conduit 36 to a bank of valves comprising distributor valves 40 and 42 and cross-over valve 44, which are operative to distribute fluid to a track drive motor 48, and a dipper or stick motor 50.
  • Pump 14 supplies fluid to a distributor 38 for operation of a slew motor 46.
  • This fluid if not used, may either go to exhaust, as illustrated, or may be available for combining downstream with fluid from pump 12 for operation of other implements as will be hereinafter explained.
  • the auxiliary pump 16 supplies fluid for pilot operation of the main control valves as well as for operating brakes for the track drive motors and the slew motors.
  • FIG. 2 A schematic layout of a valve assembly is illustrated in FIG. 2 with all the passageways and elements revolved about an axis to the same plane to facilitate comprehension.
  • the valve assembly comprises a housing 52 having a plurality of bores 54, 56, 58 and 60, in which are slidably mounted the control spools 38, 40, 42, and crossover spool 44.
  • the axes of the spools are intersected by a common plane and the bores are intersected by a through passage 62 and two branches 64 and 66 of a low pressure exhaust passageway.
  • a plurality of inlet passages comprising a first passage 68 for supplying fluid to the first spool 38, a second inlet passage 70 for supplying fluid to the spool 40 and a third inlet passage 72 are provided for supplying fluid to the control spools of the valve assembly.
  • Each of the valve spools are double acting, which means they are operative to direct fluid to a double acting or reversible hydraulic motor.
  • the inlets 68 and 70 can be supplied by separate fluid sources or supplied by a single source using flow dividing means.
  • the three spools 38, 40, and 42 are also open-centered with the center intersecting through passage 62 such that fluid not used by the first valve in the series flows past the center through passage 62 and is made available for the downstream spool, and so on, for the series.
  • the through passage comprises a series of Y-shaped passages 74, 76, 78, and 80 overlapping at the bores and interconnected thereby.
  • valve spool 38 we see that if the spool is moved to the left, such that lands 90 and 92 block the flow of fluid from inlet 68 into the passageway 74, the fluid pressure will open check valve 94 permitting the fluid to flow into branch passage 96. It will then be seen that communication will be established between the branch supply passage 96 and a high pressure motor port 98 by means of a groove 100 formed between lands 92 and 102 on valve spool 38. At the same time, groove 184 formed on spool 38 between lands 106 and 108 will have established communication between another high pressure motor port 110 and branch 64 of the exhaust passageway.
  • Both sides of the motor circuit are protected against excess pressures by means of a high pressure relief valve 112 provided between motor port 110 and exhaust branch 64 and a high pressure relief valve 114 provided between high pressure motor port 98 and exhaust branch 66.
  • each side of the motor is protected against cavitation by means of an anticavitation valve 116 between motor ports 110 and exhaust passage 64 and an anti-cavitation valve 118 provided in the passageway between motor port 98 and the exhaust passage 66.
  • These valves operate in the usual manner independently of the valve spool 38. When excess pressures are reached in the motor port 110 the valve 112 will open and relieve pressure into the exhaust passageway 64.
  • the anticavitation valve 116 will open and permit fluid to pass from the exhaust passageway 64 into the motor passageway 110 to supplement fluid being supplied thereto by means of the pump.
  • the fluid passageway arrangement for spool 40 is similar to that of spool 38 wherein fluid blocked in the through passage flows past a check valve 119 to branched supply passage 120 wherein communication may then be established with a high pressure motor port 121 or 122 by means of grooves 124 and 126 formed in the spool 40.
  • a pair of high pressure relief valves 128 and 130 are provided between the high pressure motor ports 121 and 122 and the respective branches 66 and 64 of the exhaust passageway.
  • a pair of anti-cavitation valves 132 and 134 are also provided between the motor ports 121 and 122 and the respective branches 66 and 64 of the exhaust passageway.
  • the spool 40 controls the flow of fluid to and from the track motors and for this reason is provided with a pair of retarding or antioverspeed valves 136 and 138 which are operative to retard the flow of exhaust fluid from the motors to prevent the motors from over-running or running away such as to cause loss of control of the vehicle.
  • These valves comprise spools 140 and 142 slidably mounted in bores 144 and 146 and biased by means of springs 148 and 150 to a position to permit communications by way of passages 152 and 154 and grooves 156 and 158 with the exhaust passages 66 and 64.
  • Passages 159 and 160 provide communication between the motor ports 121 and 122 and chambers 161 and 162 at the ends of the spools 140 and 142. If, for example, motor port 121 is being exhausted to exhaust passageways 66 by way of passageway 152 and groove 156 the pressure buildup in port 121 resulting from over-running of the motor such as when the vehicle may be descending a grade,
  • the spool 140 operates automatically in response to over-running of a motor connected with passageway 121, and thus provides an automatic retarding on the motor itself.
  • the spool 142 operates in an identical manner to control the flow of fluid through the motor port 122.
  • the spool 38 can operate a suitable motor from a supply of fluid through inlet 68 while at the same time fluid flowing through inlet 70 may be diverted by means of spool 40 for operation of a motor connected to ports 121 and 122 completely independent of the supply fluid through inlet 68.
  • the control spool 38 is returned to its neutral position, the fluid supplied to inlet 68 then flows into passageway 74 and becomes available together with the fluid through inlet 70 to be directed by means of spool 40 for control of the motors connected to passages 121 and 122.
  • first spool 38 is operative to control the flow of fluid from the first inlet opening 68 while at the same time spool 40 may be operative to control the flow of fluid from inlet 70 independent of the inlet 68 and, in addition, is operative to control the combined flow from 'the two inlets 68 and 70.
  • the control spool or distributor 42 has inlet and control passages arranged similarly to the previous control spools. Movement of spool 42 in either direction blocks the flow of fluid from passage 76 to passage 78 and directs the fluid past check valve 164 into branch passage 166 where it may then be directed by means of grooves 168 and 170 to the motor ports 172 and 174.
  • a pair of high pressure relief valves 176 and 178 provide communication between the motor ports 172 and 174 in case of excess pressure therein to exhaust ports 64 and 66.
  • a pair of anti-cavitation valves 180 and 182 provide communication between the exhaust passageways in the motor ports in the event of a drop of pressure in the motor line which is likely to cause cavitation.
  • a cross-over spool 44 which is operatively coupled to move with the control spool 42 and facilitate combining of fluid from inlet 72 with that from passageway 76 for distribution by means of spool 42 to a suitable motor connected with motor passages 172 and 174.
  • movement of spool 42 causes spool 44 to move in the same direction, thus blocking flow of fluid from the inlet 72 to passageway 86 causing it to open check valve I84 and permit flow into passageway 166 where it combines with fluid from passageway 76 for operation of motors controlled by the stem 42.
  • valve stem 42 and 44 are capable of supplying fluid from a source 72 for operation of motor at the same time that valves 40 and 38 are being operated for control of. their respective motors.
  • the motor operated by valve stem 42 may be operated from a number of sources of fluid either independently or combined.
  • the unique valve arrangement and cooperating relationship of the valve assembly of the present invention is capable of providing for extremely versatile operation of a plurality of hydraulic implements such as a backhoe or hydraulic excavator.
  • FIG. 3 The embodiment showing FIG. 3 is identical to that of FIG. 2, with the exception that the stems 42 and 44 of FIG. 2 have been replaced by stems 188 and 190 with the stem 188 having a completely open center and the through passage blocking function performed by means of the central land 192 rather than by land on valve 42 as shown in FIG. 2.
  • This arrangement has the advantage of distributing the functions of spools such that the crossover spool 190 performs more of the function than in the previous embodiment.
  • FIG. 4 is a sectional view through an actual valve body and illustrates, among other things, that each of the valve elements or distributor spools are held in place by compression spring arrangement.
  • Spool 38 for example, has a compression spring 193, positioned between washers 194 and 196 which are slidably mounted on the spool 38 and bear against shoulders thereon for maintaining the spool in the central posi' tion.
  • the washer 196 biases against a cap member 198 to maintain it in its fixed position with respect to housing 52.
  • the spool or distributor 40 is similarly provided with a similar spring 200 for maintaining it in the neutral position.
  • each end of the spool 40 is chambers 202 and 204 into which fluid is introduced by means of conduits 206 and 208 for pilot operation of the valve.
  • the spools I88 and 190 are coupled together by a coupling member 210 for movement together and are provided with suitable centering means such as springs 212 and 214 arranged as described above.
  • suitable centering means such as springs 212 and 214 arranged as described above.
  • FIG. 4 Another feature of interest as shown in FIG. 4 is that the outlet from spool 38 and the inlet to spool 40 are actually coupled together in the actual embodiment by means of an external conduit 216 although the passageway could conveniently be placed within the valve body itself. This arrangement permits a complete separation of the circuit controlled by distributor spool 38, and of distributor spool 40.
  • An additional feature of the valve assembly is a further inlet opening 218 which may be provided for directing fluid to the spool 188.
  • a further inlet opening 218 which may be provided for directing fluid to the spool 188.
  • an additional source of fluid may be provided such that fluid is always available to the valve 188 despite upstream operation by the other valves.
  • FIG. 6 illustrates the actual construction arrangement at cross-over valve 190 and the relationship of the inlet 72 and outlet 80.
  • FIG. 7 illustrates an alternate embodiment having two cross-over or combining spools.
  • One spool provides for combining a new source of fluid with the supply at the control spool.
  • the other spool provides for diverting fluid downstream of that spool to provide a source to be used by another spool.
  • valve system comprising a housing 220 having a plurality of control spools 222, 224, and 226 constructed and arranged substantially as disclosed in the previous embodiments.
  • the porting and passage arrangement is such that three different supplies are available selectively, individually or combined at certain control spools.
  • an inlet 228 supplies fluid from a first pump or source solely to control spool 222, where it is either used or returned via outlet 230 to reservoir.
  • a second inlet 232 supplies fluid from a second pump or source to control spool 224.
  • This fluid if not used, passes along through passage 234 and becomes available to be used by control spool 226.
  • the fluid continues past spool 226 if not used there, along passage 236 where it crosses a combining spool 238 and into a return or exhaust passage 240 for return to reservoir.
  • the spool 238 is operative upon movement to the right to block the flow of fluid to exhaust 240 and cause it to flow past a check valve 242 to an outlet passage 244 to become available to another circuit.
  • the fluid from one bank of valves would become selectively available to the other bank when not used in the first.
  • a third inlet 246 supplies fluid to a combining or cross-over spool 248 disposed in a bore 250.
  • the fluid is permitted to flow along the spool and out to exhaust passage 240 when the spool 248 is in neutral.
  • spool 248 Upon actuation of spool 248, the fluid is forced to flow along passage 252 through check valve 254 to combine at spool 226 with fluid from passage 234.
  • the valve 248 may be coupled to spool 226 either mechanically or hydraulically to move therewith for automatic combining when fluid is available. Alternately, the spool 248 may be independently operable for selective combining when fluid is available at inlet 246.
  • the selective combining feature is important in situations such as in operation of a hydraulic excavator wherein at one minute the operator is carrying out rapid excavation and at the next minute he may be trimming the excavation at a point adjacent underground utility lines or the like. In the second instance, it is necessary that he have full and precise control of the movement of the tool. Such precise control is best achieved with lower volume of fluid modulated by the main control spool.
  • control valve arrangements having a plurality of main control spools, and means operative to combine fluid from a plurality of sources at selected main control spools.
  • a control valve said valve comprising:
  • a housing having a cylindrical bore formed therein;
  • a combining passageway for providing communication between said second inlet passage and said first inlet
  • a second control spool disposed in said second bore and operative to direct fluid from said second inlet to combine with fluid from said first inlet for control by said first spool;
  • said first and second spools are operatively coupled together.
  • a control valve said valve comprising:
  • a housing having a cylindrical bore formed therein;
  • a second control spool disposed in said second bore and operative to direct fluid from said second inlet to combine with fluid from said first inlet for control by said first spool;
  • said third spool being operative to divert fluid from said through passage downstream of said first control spool for use by another control spool.
  • a hydraulic valve assembly for controlling bidirectional motion of a plurality of fluid motors, said valve assembly comprising:
  • valve body having a plurality of parallel bores
  • valve elements operatively coupled to move together
  • a first stem mounted for movement in a first bore
  • an intake passageway connectable with a first source of pressurized fluid and communicating with said first bore for admitting pressurized fluid thereto;
  • an intake connectable with a second source of pressurized fluid and communicating with a passageway between said first bore and a second bore;
  • said pair of valve elements being responsive to combine the fluid from said inputs and direct it to a selected one of said outputs.
  • a bank of control valves comprising a housing having a plurality of parallel bores and a slidable spool in each of said bores;
  • a first slidable spool operative to control the flow of fluid from a first inlet opening
  • a second slidable spool operative to control fluid from a second inlet and from said first inlet;
  • a third slidable spool operative to control fluid from a third inlet and from said first and second inlets.
  • each of said bores are intersected by a pair of high pressure motor ports and a branched exhaust passage.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mining & Mineral Resources (AREA)
  • Civil Engineering (AREA)
  • Structural Engineering (AREA)
  • Mechanical Engineering (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Operation Control Of Excavators (AREA)
  • Multiple-Way Valves (AREA)
US00207028A 1971-12-13 1971-12-13 Hydraulic control valve assembly Expired - Lifetime US3759292A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US20702871A 1971-12-13 1971-12-13

Publications (1)

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US3759292A true US3759292A (en) 1973-09-18

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Application Number Title Priority Date Filing Date
US00207028A Expired - Lifetime US3759292A (en) 1971-12-13 1971-12-13 Hydraulic control valve assembly

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US (1) US3759292A (enrdf_load_stackoverflow)
JP (2) JPS4865382A (enrdf_load_stackoverflow)
BE (1) BE792618A (enrdf_load_stackoverflow)
CA (1) CA976839A (enrdf_load_stackoverflow)
DE (1) DE2261626C2 (enrdf_load_stackoverflow)
FR (1) FR2163536B1 (enrdf_load_stackoverflow)
GB (1) GB1413689A (enrdf_load_stackoverflow)
SE (1) SE390199B (enrdf_load_stackoverflow)

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1980001940A1 (en) * 1979-03-05 1980-09-18 Mcwilliams O Balanced spool valve
US6397890B1 (en) * 1999-02-15 2002-06-04 Case Corp. Variable metering fluid control valve
EP1178222A3 (en) * 2000-07-31 2003-01-02 Hydrocontrol S.p.A. Hydraulic distribution unit for controlling the actuation of a bush cutter
US20130125539A1 (en) * 2010-06-22 2013-05-23 Hitachi Construction Machinery Co., Ltd. Hydraulic control device for working vehicle
US20150377370A1 (en) * 2014-06-25 2015-12-31 Parker-Hannifin Corporation Reverse flow check valve in hydraulic valve with series circuit
US9387759B2 (en) 2014-09-22 2016-07-12 Caterpillar Inc. Flow divider free wheeling valve
US20170234336A1 (en) * 2016-02-16 2017-08-17 Kubota Corporation Hydraulic Block
CN111051707A (zh) * 2017-08-15 2020-04-21 伊顿智能动力有限公司 滑阀
US11460053B2 (en) * 2020-03-16 2022-10-04 Parker-Hannifin Corporation Open center control valve configured to combine fluid flow received from multiple sources
US20240384733A1 (en) * 2021-09-17 2024-11-21 Parker Hannifin Emea S.À.R.L. A redundant hydraulic system

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US4078681A (en) * 1976-08-24 1978-03-14 Caterpillar Tractor Co. Dual pump hydraulic control system with predetermined flow crossover provision
US4280397A (en) * 1978-04-27 1981-07-28 Joy Manufacturing Company Hydraulic fluid control apparatus
DE3044144A1 (de) 1980-11-24 1982-09-09 Linde Ag, 6200 Wiesbaden Hydrostatisches antriebssystem mit einer einstellbaren pumpe und mehreren verbrauchern
DE3044171A1 (de) * 1980-11-24 1982-06-16 Linde Ag, 6200 Wiesbaden Antriebssystem mit mindestens zwei teilsystemen
JPS57120704A (en) * 1981-01-19 1982-07-27 Toshiba Mach Co Ltd Confluent composite control valve
JPS5880033A (ja) * 1981-11-02 1983-05-14 Kobe Steel Ltd 油圧シヨベルの油圧回路
JPS59186502U (ja) * 1983-05-31 1984-12-11 株式会社小松製作所 方向切換弁
DE3415621C3 (de) * 1983-06-13 1997-07-17 Husco Int Inc Hydraulisches Mehrwege-Steuerventil
JPH0349286Y2 (enrdf_load_stackoverflow) * 1986-09-01 1991-10-22
JP5087047B2 (ja) * 2009-06-18 2012-11-28 日立建機株式会社 油圧作業機械

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US2879612A (en) * 1956-05-02 1959-03-31 Gar Wood Ind Inc Hydraulic drive for ditcher conveyor
US2979908A (en) * 1960-01-04 1961-04-18 Warner Swasey Co Hydraulic control systems
DE1159764B (de) * 1960-06-07 1963-12-19 Fritz Spierig Fa Hydraulische Steuereinrichtung zum Betrieb von hydraulisch betaetigten Arbeitsgeraeten
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Cited By (15)

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WO1980001940A1 (en) * 1979-03-05 1980-09-18 Mcwilliams O Balanced spool valve
US6397890B1 (en) * 1999-02-15 2002-06-04 Case Corp. Variable metering fluid control valve
EP1178222A3 (en) * 2000-07-31 2003-01-02 Hydrocontrol S.p.A. Hydraulic distribution unit for controlling the actuation of a bush cutter
US20130125539A1 (en) * 2010-06-22 2013-05-23 Hitachi Construction Machinery Co., Ltd. Hydraulic control device for working vehicle
US9175456B2 (en) * 2010-06-22 2015-11-03 Hitachi Construction Machinery Co., Ltd. Hydraulic control device for working vehicle
US10619750B2 (en) 2014-06-25 2020-04-14 Parker-Hannifin Corporation Reverse flow check valve in hydraulic valve with series circuit
US10024445B2 (en) * 2014-06-25 2018-07-17 Parker-Hannifin Corporation Reverse flow check valve in hydraulic valve with series circuit
US20150377370A1 (en) * 2014-06-25 2015-12-31 Parker-Hannifin Corporation Reverse flow check valve in hydraulic valve with series circuit
US9387759B2 (en) 2014-09-22 2016-07-12 Caterpillar Inc. Flow divider free wheeling valve
US20170234336A1 (en) * 2016-02-16 2017-08-17 Kubota Corporation Hydraulic Block
US10626891B2 (en) * 2016-02-16 2020-04-21 Kubota Corporation Hydraulic block
CN111051707A (zh) * 2017-08-15 2020-04-21 伊顿智能动力有限公司 滑阀
CN111051707B (zh) * 2017-08-15 2023-02-28 丹佛斯动力系统Ii技术有限公司 滑阀
US11460053B2 (en) * 2020-03-16 2022-10-04 Parker-Hannifin Corporation Open center control valve configured to combine fluid flow received from multiple sources
US20240384733A1 (en) * 2021-09-17 2024-11-21 Parker Hannifin Emea S.À.R.L. A redundant hydraulic system

Also Published As

Publication number Publication date
JPS4865382A (enrdf_load_stackoverflow) 1973-09-08
DE2261626A1 (de) 1973-06-14
FR2163536B1 (enrdf_load_stackoverflow) 1978-08-04
CA976839A (en) 1975-10-28
BE792618A (fr) 1973-06-12
FR2163536A1 (enrdf_load_stackoverflow) 1973-07-27
SE390199B (sv) 1976-12-06
DE2261626C2 (de) 1985-08-29
JPS55134505U (enrdf_load_stackoverflow) 1980-09-24
GB1413689A (en) 1975-11-12

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