US3799200A - Flow and pressure regulating control for hydraulic motors - Google Patents

Flow and pressure regulating control for hydraulic motors Download PDF

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Publication number
US3799200A
US3799200A US00261885A US26188572A US3799200A US 3799200 A US3799200 A US 3799200A US 00261885 A US00261885 A US 00261885A US 26188572 A US26188572 A US 26188572A US 3799200 A US3799200 A US 3799200A
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United States
Prior art keywords
valve
fluid
pressure
port
opposed
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Expired - Lifetime
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US00261885A
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English (en)
Inventor
J Tipton
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Gardner Denver Inc
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Gardner Denver Inc
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Filing date
Publication date
Application filed by Gardner Denver Inc filed Critical Gardner Denver Inc
Priority to US00261885A priority Critical patent/US3799200A/en
Priority to GB503573A priority patent/GB1422431A/en
Priority to GB2901775A priority patent/GB1422432A/en
Priority to CA162,847A priority patent/CA970252A/en
Priority to AU51923/73A priority patent/AU471273B2/en
Priority to ZA730897A priority patent/ZA73897B/xx
Priority to FR7307734A priority patent/FR2188076B3/fr
Priority to JP48031745A priority patent/JPS4932220A/ja
Priority to DE2319030A priority patent/DE2319030A1/de
Priority to SE7308156A priority patent/SE404415B/xx
Priority to IT7260/73A priority patent/IT992165B/it
Priority to US42451273 priority patent/US3897719A/en
Application granted granted Critical
Publication of US3799200A publication Critical patent/US3799200A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • 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
    • F15B13/0401—Valve members; Fluid interconnections therefor
    • F15B13/0402—Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool valves
    • F15B13/0403—Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool valves a secondary valve member sliding within the main spool, e.g. for regeneration flow
    • E—FIXED CONSTRUCTIONS
    • E21—EARTH OR ROCK DRILLING; MINING
    • E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
    • E21B19/00—Handling rods, casings, tubes or the like outside the borehole, e.g. in the derrick; Apparatus for feeding the rods or cables
    • E21B19/08—Apparatus for feeding the rods or cables; Apparatus for increasing or decreasing the pressure on the drilling tool; Apparatus for counterbalancing the weight of the rods
    • E21B19/084—Apparatus for feeding the rods or cables; Apparatus for increasing or decreasing the pressure on the drilling tool; Apparatus for counterbalancing the weight of the rods with flexible drawing means, e.g. cables
    • E—FIXED CONSTRUCTIONS
    • E21—EARTH OR ROCK DRILLING; MINING
    • E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
    • E21B19/00—Handling rods, casings, tubes or the like outside the borehole, e.g. in the derrick; Apparatus for feeding the rods or cables
    • E21B19/08—Apparatus for feeding the rods or cables; Apparatus for increasing or decreasing the pressure on the drilling tool; Apparatus for counterbalancing the weight of the rods
    • E21B19/086—Apparatus for feeding the rods or cables; Apparatus for increasing or decreasing the pressure on the drilling tool; Apparatus for counterbalancing the weight of the rods with a fluid-actuated cylinder
    • E—FIXED CONSTRUCTIONS
    • E21—EARTH OR ROCK DRILLING; MINING
    • E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
    • E21B44/00—Automatic control systems specially adapted for drilling operations, i.e. self-operating systems which function to carry out or modify a drilling operation without intervention of a human operator, e.g. computer-controlled drilling systems; Systems specially adapted for monitoring a plurality of drilling variables or conditions
    • E21B44/02—Automatic control of the tool feed
    • E21B44/06—Automatic control of the tool feed in response to the flow or pressure of the motive fluid of the drive
    • 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
    • F15B13/0401—Valve members; Fluid interconnections therefor
    • F15B13/0402—Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool 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
    • 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
    • F15B13/0422—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 manually-operated pilot valves, e.g. joysticks
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
    • F16H3/20—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially using gears that can be moved out of gear
    • F16H3/38—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially using gears that can be moved out of gear with synchro-meshing
    • F16H3/385—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially using gears that can be moved out of gear with synchro-meshing with braking means
    • 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

Definitions

  • Shuttle valves of Search disposed in the spool and the opposed chambers prol37/625.63, 625-69 vide for reversible operation of the spool valve.
  • the pressure regulator spool valve is operated to control [56] R f n Cit flow, direction of flow, and pressure by a pressure dif- UNITED STATES PATENTS ferential control valve which can be manually oper- 2,536,965 1/1951 Taylor l37/625.66 med Supply fluid at Variable Pressure to either of 2,910,971 11/1959 MacDuff l37/625.63 x the pp 'chambers-
  • the flow and Pressure regula- 2;93l,389 4/ 1960 Moog, Jr. et al. 137/62562 tor control is particularly adaptable for control of hy- 2,964,059 12/1960 Geyer l37/625.62 draulic feed or pull-down mechanisms for rock drills. 3,015,317 l/l962 Buchanan et a]. l37/625.62
  • the present invention provides an improved pressure fluid flow and pressure regulating control which is operable to regulate the pressure of fluid supplied to a fluid motor or similar fluid power device to a pressure valve corresponding to the pressure of a pilot fluid used to actuate the control.
  • the present invention also provides a pressure regulating control which is operable to provide directional control of pressure fluid at a regulated pressure for reversible operation of a fluidmotor or the like.
  • the pressure regulating control of the present invention comprises a control valve for supplying fluid directly to a reversible fluid motor or the like at a regulated pressure corresponding substantially to a pilot fluid pressure used to actuate the control valve.
  • a pressure fluid flow and pressure regulating control which comprises a so-called four-way directional control valve combined with a fluid pressure regulator in a single valve which is also operable as a flow control valve capable of controlling a substantial range of fluid flow rates for operating reversible fluid motors and the like.
  • the flow and pressure regulating control of the present invention further includes a differential pressure control valve which is operable to supply pressure fluid at different pressures to pilot actuators or the like such as opposed pilot actuator chambers of the reversible flow control and pressure regulating valve of the present invention.
  • the present invention also provides an improved flow and pressure regulating control for fluid operated rock drill feed mechanisms whereby a simplified control circuit provides for reversible movement of a drill along a feed support at a desired speed and feed force for drilling, and at a desired speed for removal of the drill rod and bit from a drill hole.
  • a pressure fluid control circuit in combination with a fluid operated rock drill feed mechanism according to the present invention a simple and reliable control circuit is provided which controls drill feed force and drill position with great accuracy.
  • FIG. 1 is a longitudinal section view of a fluid flow and pressure regulating control valve in accordance with the present invention
  • FIG. 2 is a section view of a differential pressure control valve in accordance with the present invention.
  • FIG. 3 is a schematic view of a control system for a rock drill feed mechanism in accordance with the present invention.
  • FIG. 4 is a section view taken along the line 4-4 of FIG. 3.
  • a flow and pressure regulating control valve in accordance with the present invention is generally designated by the numeral 10.
  • the valve 10 includes a housing 12 having a bore 14 in which is disposed, closely fitted, a cylindrical sleeve 16.
  • the sleeve 16 is provided with a cylindrical bore 18, and with spaced apart circumferential grooves 20, 22, 24, 26, and 28, each groove having radially extending passages 30 opening into the bore 18.
  • the grooves 20, 22, 24, 26, and 28 are respectively in communication with ports 32, 34, 36, 38, and 40 in the housing 12.
  • the sleeve 16 is retained in the housing 12 by opposed flanged cover members 42 and 43 suitably fastened to the housing and having, respectively, chambers formed by recess 44 and 45 opening toward the bore 18 of the sleeve.
  • the cover members 42 and 43 are also provided with bores 46 and 48 which open from the recesses 44 and 45 to suitablethreaded passages or ports 50 and 52.
  • the valve 10 also includes a cylindrical closure member or spool 54 movably disposed in close fitting relationship within the bore 18.
  • the spool 54 is provided with circumferential recesses 56 and 58 and a portion 60 interposed between the recesses.
  • the portion 60 is dimensioned to provide for blocking the flow of fluid from the supply port 36 to either of the recesses 56 or 58, in the position of the spool shown in FIG. 1.
  • the recesses 56 and 58 are also proportioned such that the spool 54 blocks the ports 32 and 40 from communication with the recesses 56 and 58, respectively, in the position of the valve shown in FIG. 1.
  • the spool 54 may be moved to connect port 32 with port 34 by way of recess 56, and port 36 with port 38 by way of recess 58.
  • the spool 54 may also be moved in the opposite direction to connect port 34 with port 36 by way of recess 56 and at the same time connect port 38 with port. 40 by way of recess 58.
  • the spool 54 is also provided with longitudinal chambers 62 and 64 which respectively open to opposed end faces 66 and 68.
  • a passageway 70 connects chamber 62 with recess 58 and a passageway 72 connects chamber 64 with recess 56.
  • the chambers 62 and 64 each include a cylindrical shuttle valve element 74 slidably disposed therein.
  • the valve elements 74 are each characterized by an end face 76 and a flanged portion 78 which abut against the respective end faces of the spool 54.
  • Passages 80 in the valve elements open into the respective chambers 62 and 64 and are operable to be in communication with the recesses 44 and 45 in the cover members 42 and 43 when suitably displaced within the chambers.
  • the chambers formed by the recesses 44 and 45 together with the surfaces 66 and 68 on the spool 54 comprise means for moving the spool 54 to place the fluid supply port 36 in communication with either first port 34 or second port 38.
  • pilot pressure fluid is introduced through port 50 and passage 84 in the valve element 82 into the recess 44 it will act on end face 66 to move spool 54 to connect port 34 with port 36 by way of recess 56 assuming, of course, that the pressure force exerted on end face 66 is great enough to overcome the bias force of the opposing spring 88.
  • the spool 54 may be moved against the bias force of the spring 86 disposed in the recess 44. Any more than slight movement of the spool to connect port 36 with port 38 will prevent communication of the recess 44 with port 50 in the cover member 42 by moving the valve element 82 disposed in bore 46 to cause the passage 84 to be blocked by the wall of the bore 46.
  • the valve elements 82 are closely fitted in the bores 46 and 48 to substantially block the passages 84 in certain positions of the spool, leakage of pressure fluid out of the recesses 44 or 45 between the bores 46 and 48 and the valve elements 82 can occur to permit movement of the spool 54 when the passages 84 are blocked.
  • valve 10 provides for directional control of pressure fluid flow as well as control of the amount or rate of flow of fluid by precisely controlling the reversible movement of the spool (54) to uncover the port 36.
  • the valve 10 is also operable to regulate the pressure of fluid flowing to either port 34 or 38 from port 36. For example, if pressure fluid is supplied to port 50 to cause the pool to move to connect port 34 with port 36 the passage 72 will conduct fluid from the recess 56 to the chamber 64 to act on the end face 76 of the valve element 74. A pressure force due to fluid acting on the valve element 74 will shift the valve elements 74 and 82 to place the passage 80 in communication with the recess 45 and chamber 64.
  • the spool 54 will move to control the flow of pressure fluid from the port 36 to regulate the pres sure of fluid flowing to the port 34 to correspond substantially to the pressure of the pilot control fluid supplied to the recess 44 through port 50.
  • the springs 86 and 88 may be provided with a spring rate or stiffness which will not have a significant effect on the pressure regulating operation of the valve 10 for the range of pressures normally encountered with hydraulic fluid systems.
  • the valve 10 therefore operates as a pressure regulating valve as well as a directional flow control and flow metering type of valve.
  • valve 10 When the valve 10 is operated to control flow to either port 34 or port 38 metering or flow control alone without pressure regulation will be provided as long as the passages in the valve elements 74 are blocked from communication with the recesses 44 or 45. Therefore, by controlling the fluid pressure to port 52 to provide a pressure force acting against surface 83 which will hold the valve element 74 in the position shown in FIG. 1 with respect to the spool 54, pressure fluid from recess 56 will be prevented from entering recess 45.
  • valve elements 74 comprise means responsive to a predetermined fluid pressure in either the first port 34 or the second port 38 acting on the surfaces 76 for moving the valve elements to place the recesses 56 or 58 in communication with the respective recesses 45 or 44 to cause the spool 54 to operate in the pressure regulating mode.
  • a cylindrical valve closure member 100 Disposed within the bore 96 is a cylindrical valve closure member 100 having radially inwardly sloping surfaces 102 and 104' which form a chamber 106 in the bore 96.
  • the member 100 includes a threaded portion 108 disposed in a cover member 110 suitably fastened to the housing 94 and having a complementary threaded portion 112.
  • the valve closure member 110 also includes an end portion 115 to which an operating handle 114 is detachably connected. In response to rotation of the valve member 100 by the handle 114 the valve member is moved longitudinally in the bore 96 by means comprising the cooperating threaded portions 108 and 112.
  • the valve 92 also includes passages 116 and 118 in the housing 94 which intersect the bore 96.
  • the valve 92 is operable to raise the fluid pressure in the passage 116 and simultaneously lower the fluid pressure in passage 118 by rotation of the handle 114 to provide for movement of the member 100 longitudinally in the bore 96 away from the cover member 98. Such movement will decrease the flow area of an orifice formed between the sloping surface 102 and the intersection opening of the passage 116 with the bore 96. Simultaneously, an orifice formed by the sloping surface 104 and the intersection of passage 118 with the bore 96 will increase in area to provide for comparatively unrestricted flow of fluid from passage 118 through chamber 106 to the passage 126.
  • valve 92 may be advantageously used in conjunction with the control valve 10 as a means of controlling the fluid pressure in the ports 50 and 52 to thereby operate the valve 10 for control of fluid flow and pressure to a reversible fluid motor or the like.
  • the aforedescribed control valves 10 and 92 provide for particularly superior control of rock drill feed mechanisms using reversible fluid motors for advancing and retracting a rock drill along an elongated feed support.
  • the valves 10 and 92 are shown in a hydraulic control circuit for a rock drill feed mechanism generally designated by the numeral 134.
  • the rock drill feed mechanism 134 is characterized by an elongated support 136 upon which is slidably mounted rock drill means 138 including a mounting plate 139.
  • the drill 138 is operable to actuate an extension drill string 140 comprising extension drill rod members 141 and 143 coupled end to end in a manner well known.
  • the feed mechanism 134 is exemplary of one type which may be used with the below described control circuit. Feed mechanisms using reversible rotary motors in combination with cables, chains, or elongated feed screws may also enjoy the benefits of the present invention.
  • a control circuit for the feed mechanism 134 includes a hydraulic pump 170 which may be suitably driven by a fluid motor 172.
  • the pump 170 is connected by way of conduits 174 and 176 to the passage 120 of valve 92 and the port 36 of valve 10, respectively, for supplying hydraulic fluid thereto at substantially constant pressure.
  • the passages 116 and 118 of valve 92 are respectively connected to ports 50 and 52 of valve 10 by way of conduits 178 and 180.
  • the ports 34 and 38 of valve 10 are connected to opposite ends of the hydraulic cylinder 146 by the respective conduits 182 and 184.
  • the passage 126 in valve 92 is connected to a low pressure reservoir or tank 186 by the conduit 188 and the ports 32 and 40 of valve 10 are also connected to drain fluid to the tank 186 through conduit 190.
  • valve 92 by operation of the valve 92 to supply pressure fluid to the port 50 of valve 10 at a higher pressure than supplied to port 52, may cause the valve 10 to meter fluid to the cylinder 146 to retract the rod 150 to posi-' tion the drill for adding a drill rod member to the drill string 140.
  • the valve 92 will be operated to increase the pressure at either port 50 or 52 only enough to shift the spool 54 against the bias force of the opposing spring and the opposing pressure force acting on surface 83 of the respective valve element 82.
  • Movement of the drill 138 along the support 136 for positioning purposes will normally not require substantial pressure in the cylinder 146 and the pressure of the pilot control fluid acting on the surfaces 83 maybe predetermined to be sufficient to prevent movement of the valve elements 74 with respect to the spool 54. Moreover, if the drill should unexpectedly strike an obstruction or the feeding mechanism become jammed during positioning movement, the pressure of fluid supplied to the cylinder 146 would only increase to substantially the pressure of the fluid supplied to the ports 50 or 52 as the valve 10 would commence to function as a pressure regulator.
  • the pressure of fluid supplied to port 52 of valve 10 is increased by movement of the valve member 100 to further restrict the orifice formed by the passage 118 and sloping surface 104 and at the same time the pressure in port 50 is reduced to assure that the valve element 74 is free to move to connect recess 58 with recess 44. Accordingly, the fluid pressure in the cylinder 146 and at the port 38 of the valve 10 will usually be sufficient, due to resistance to penetration of a rock formation by the drill string 140, to immediately move the valve element 74 to admit pressure fluid to recess 44 thereby commencing operation of the valve 10 in the pressure regulating mode to maintain a desired feed force on the drill 138.
  • valve closure member disposed in said housing and movable to alternately place said supply port in communication with said first or second ports;
  • pressure fluid operated means including opposed chambers in said valve housing and actuating means disposed in each of said chambers and responsive to pilot pressure fluid from a source admitted to one of said chambers to move said closure member to place said supply port in communication with one of said first and second ports; and,
  • said means comprising shiftable valve means including opposed first and second pressure surfaces in communication with said one port and with pressure fluid from a pilot pressure fluid source, respectively.
  • said shiftable valve means comprises a pair of valve elements engaged with said closure member for movement with said closure member and with respect to said closure member.
  • said closure member comprises a cylindrical spool reciprocably disposed in said valve housing.
  • one of said valve elements operates to block the communication of pilot pressure fluid to said other opposed chamber in said valve in response to movement of said spool and to block the communication of pressure fluid from said one port to said other chamber as long as a pressure fluid force acting on said first surface of said one valve element is less than a pressure fluid force acting on said second surface of said one valve element.
  • a fluid flow and pressure regulating control valve comprising:
  • valve closure member disposed in said housing and movable to alternately place said supply port in communication with said first or second ports;
  • pressure fluid operated means including opposed chambers in said valve housing and actuating means disposed in each of said chambers and responsive to pilot pressure fluid from a source admitted to one of said chambers to move said clo-' sure member to place said supply port in communication with one of said first and second ports; and,
  • said closure member includes a passage for communicating said first port with one of said opposed chambers and a passage for communicating said second port with the other of said opposed chambers
  • said movable valve means comprises a pair of valve elements disposed in said respective passages and cooperable with said closure member for movement between open and closed positions.

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  • Engineering & Computer Science (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Mining & Mineral Resources (AREA)
  • Geology (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Environmental & Geological Engineering (AREA)
  • General Life Sciences & Earth Sciences (AREA)
  • Geochemistry & Mineralogy (AREA)
  • Earth Drilling (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Multiple-Way Valves (AREA)
US00261885A 1972-06-12 1972-06-12 Flow and pressure regulating control for hydraulic motors Expired - Lifetime US3799200A (en)

Priority Applications (12)

Application Number Priority Date Filing Date Title
US00261885A US3799200A (en) 1972-06-12 1972-06-12 Flow and pressure regulating control for hydraulic motors
GB503573A GB1422431A (en) 1972-06-12 1973-02-01 Flow and pressure regulating control valve for hydraulic motors
GB2901775A GB1422432A (en) 1972-06-12 1973-02-01 Rock drill feed mechanism
CA162,847A CA970252A (en) 1972-06-12 1973-02-02 Flow and pressure regulating control for hydraulic motors
AU51923/73A AU471273B2 (en) 1972-06-12 1973-02-07 Flow and pressure regulating control for hydraulic motors
ZA730897A ZA73897B (en) 1972-06-12 1973-02-08 Flow and pressure regulating control for hydraulic motors
FR7307734A FR2188076B3 (fr) 1972-06-12 1973-03-05
JP48031745A JPS4932220A (fr) 1972-06-12 1973-03-19
DE2319030A DE2319030A1 (de) 1972-06-12 1973-04-14 Mediumdurchfluss- und druckregelventil fuer hydraulikmotoren
SE7308156A SE404415B (sv) 1972-06-12 1973-06-08 Reglerventil for fluiddrivna motorer
IT7260/73A IT992165B (it) 1972-06-12 1973-06-12 Comando di regolazione della portata e della pressione per motori idraulici
US42451273 US3897719A (en) 1972-06-12 1973-12-13 Flow and pressure regulating control for hydraulic motors

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US00261885A US3799200A (en) 1972-06-12 1972-06-12 Flow and pressure regulating control for hydraulic motors

Publications (1)

Publication Number Publication Date
US3799200A true US3799200A (en) 1974-03-26

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Family Applications (1)

Application Number Title Priority Date Filing Date
US00261885A Expired - Lifetime US3799200A (en) 1972-06-12 1972-06-12 Flow and pressure regulating control for hydraulic motors

Country Status (10)

Country Link
US (1) US3799200A (fr)
JP (1) JPS4932220A (fr)
AU (1) AU471273B2 (fr)
CA (1) CA970252A (fr)
DE (1) DE2319030A1 (fr)
FR (1) FR2188076B3 (fr)
GB (2) GB1422432A (fr)
IT (1) IT992165B (fr)
SE (1) SE404415B (fr)
ZA (1) ZA73897B (fr)

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3949645A (en) * 1973-07-03 1976-04-13 Messier Hispano Distributing unit for a dual action hydraulic electro-distributor
US4052929A (en) * 1973-02-07 1977-10-11 Danfoss A/S Hydraulic control means, especially a steering means
US4066006A (en) * 1974-12-21 1978-01-03 Robert Bosch G.M.B.H. Flow regulating system
US4280397A (en) * 1978-04-27 1981-07-28 Joy Manufacturing Company Hydraulic fluid control apparatus
WO1982002230A1 (fr) * 1980-12-24 1982-07-08 Hall Lowell R Systeme avec dispositif d'actionnement a force constante
US4372193A (en) * 1980-12-24 1983-02-08 Caterpillar Tractor Co. System with constant force actuator
US4478250A (en) * 1981-04-09 1984-10-23 Mannesmann Rexroth Gmbh Pressure control valve
US5005467A (en) * 1987-05-18 1991-04-09 Atlas Copco Aktiebolag Pilot-operated flow controlling directional control valve with copying spool
US5996627A (en) * 1998-10-15 1999-12-07 Warren Rupp, Inc. Adjustable fluid valve for diaphragm pumps
US20060150623A1 (en) * 2005-01-12 2006-07-13 Holder Robert E Fluid powered control system with a load pressure feedback
US20150128826A1 (en) * 2012-06-04 2015-05-14 Firestone Industrial Products Company, Llc Valve assembly for rail vehicles and pneumatic system including same
CN108518377A (zh) * 2018-05-18 2018-09-11 宁波真格液压科技有限公司 一种用于垃圾压缩站的自动换向阀

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2557218B1 (fr) * 1983-12-21 1988-01-15 Bennes Marrel Emetteur hydraulique de commande a distance avec amplificateurs de debit
US4883091A (en) * 1988-12-27 1989-11-28 Ross Operating Valve Company Multi-port self-regulating proportional pressure control valve
CN1055514C (zh) * 1995-07-07 2000-08-16 中南工业大学 一种液压钻车的推进系统

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US2536965A (en) * 1946-08-23 1951-01-02 Cincinnati Milling Machines Lt Hydraulic valve operated by differential pressures
US2910971A (en) * 1958-06-27 1959-11-03 Bendix Aviat Corp Power steering valve
US2931389A (en) * 1956-04-18 1960-04-05 Moog Servocontrols Inc Servo valve producing output differential pressure independent of flow rate
US2964059A (en) * 1959-03-05 1960-12-13 Moog Valve Co Inc Pressure-flow servo valve
US3015317A (en) * 1958-02-11 1962-01-02 Hydraulic Res And Mfg Company Pressure control servo valve

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US3566749A (en) * 1968-03-13 1971-03-02 Caterpillar Tractor Co Hydraulic flow amplifier valve

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US2536965A (en) * 1946-08-23 1951-01-02 Cincinnati Milling Machines Lt Hydraulic valve operated by differential pressures
US2931389A (en) * 1956-04-18 1960-04-05 Moog Servocontrols Inc Servo valve producing output differential pressure independent of flow rate
US3015317A (en) * 1958-02-11 1962-01-02 Hydraulic Res And Mfg Company Pressure control servo valve
US2910971A (en) * 1958-06-27 1959-11-03 Bendix Aviat Corp Power steering valve
US2964059A (en) * 1959-03-05 1960-12-13 Moog Valve Co Inc Pressure-flow servo valve

Cited By (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4052929A (en) * 1973-02-07 1977-10-11 Danfoss A/S Hydraulic control means, especially a steering means
US3949645A (en) * 1973-07-03 1976-04-13 Messier Hispano Distributing unit for a dual action hydraulic electro-distributor
US4066006A (en) * 1974-12-21 1978-01-03 Robert Bosch G.M.B.H. Flow regulating system
US4280397A (en) * 1978-04-27 1981-07-28 Joy Manufacturing Company Hydraulic fluid control apparatus
WO1982002230A1 (fr) * 1980-12-24 1982-07-08 Hall Lowell R Systeme avec dispositif d'actionnement a force constante
US4372193A (en) * 1980-12-24 1983-02-08 Caterpillar Tractor Co. System with constant force actuator
US4478250A (en) * 1981-04-09 1984-10-23 Mannesmann Rexroth Gmbh Pressure control valve
US5005467A (en) * 1987-05-18 1991-04-09 Atlas Copco Aktiebolag Pilot-operated flow controlling directional control valve with copying spool
US5095806A (en) * 1987-05-18 1992-03-17 Atlas Copco Aktiebolag Device in a hydraulic power system connected to a load driving hydraulic motor
US5996627A (en) * 1998-10-15 1999-12-07 Warren Rupp, Inc. Adjustable fluid valve for diaphragm pumps
US20060150623A1 (en) * 2005-01-12 2006-07-13 Holder Robert E Fluid powered control system with a load pressure feedback
US7121187B2 (en) * 2005-01-12 2006-10-17 Eaton Corporation Fluid powered control system with a load pressure feedback
US20150128826A1 (en) * 2012-06-04 2015-05-14 Firestone Industrial Products Company, Llc Valve assembly for rail vehicles and pneumatic system including same
US9592814B2 (en) * 2012-06-04 2017-03-14 Firestone Industrial Products Company, Llc Valve assembly for rail vehicles and pneumatic system including same
CN108518377A (zh) * 2018-05-18 2018-09-11 宁波真格液压科技有限公司 一种用于垃圾压缩站的自动换向阀

Also Published As

Publication number Publication date
IT992165B (it) 1975-09-10
JPS4932220A (fr) 1974-03-23
DE2319030A1 (de) 1974-01-03
AU5192373A (en) 1974-08-08
FR2188076B3 (fr) 1976-03-05
CA970252A (en) 1975-07-01
FR2188076A1 (fr) 1974-01-18
GB1422431A (en) 1976-01-28
AU471273B2 (en) 1976-04-15
SE404415B (sv) 1978-10-02
GB1422432A (en) 1976-01-28
ZA73897B (en) 1973-11-28

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