US3699993A - Control valve for the flow to and from a variable pressure chamber - Google Patents

Control valve for the flow to and from a variable pressure chamber Download PDF

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Publication number
US3699993A
US3699993A US3699993DA US3699993A US 3699993 A US3699993 A US 3699993A US 3699993D A US3699993D A US 3699993DA US 3699993 A US3699993 A US 3699993A
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United States
Prior art keywords
valve
control
pistons
straight passage
control valve
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Expired - Lifetime
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English (en)
Inventor
Erich Hemon
Erich Ruchser
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Technomatic AG
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Technomatic AG
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Publication date
Priority claimed from CH693570A external-priority patent/CH501860A/de
Application filed by Technomatic AG filed Critical Technomatic AG
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    • 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
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/12—Actuating devices; Operating means; Releasing devices actuated by fluid
    • F16K31/42—Actuating devices; Operating means; Releasing devices actuated by fluid by means of electrically-actuated members in the supply or discharge conduits of the fluid motor
    • F16K31/423—Actuating devices; Operating means; Releasing devices actuated by fluid by means of electrically-actuated members in the supply or discharge conduits of the fluid motor the actuated members consisting of multiple way valves
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B30B15/14—Control arrangements for mechanically-driven presses
    • B30B15/142—Control arrangements for mechanically-driven presses controlling the brake or the clutch
    • 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
    • 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
    • F15B20/00—Safety arrangements for fluid actuator systems; Applications of safety devices in fluid actuator systems; Emergency measures for fluid actuator systems
    • F15B20/001—Double valve requiring the use of both hands simultaneously
    • 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
    • Y10T137/2496—Self-proportioning or correlating systems
    • Y10T137/2544—Supply and exhaust type

Definitions

  • ABSTRACT A control valve has two valve pistons disposed on op- May 6, 1970 Switzerland"; .26935/ I June 30 1970 Switzerland .9953/70 Passage whch at one end wlth an expandmg and contracting pressure chamber of a hydraulic press or brake system, and has U.S. Cl.
  • valve Int Cl Gosd 7/00 Flsb 11/08 pistons have a first position in which fluid from the Fie'ld H07 102 51/424 442 contracting pressure chamber can flow with minimal g 1 resistance through the straight passage and out of the discharge opening.
  • valve pistons have closure pieces provided with longitudinal and transverse bores, through which a pressure fluid is supplied to'a consumer apparatus after several deflections If this known control valve is shifted from the operative position to the inoperative position, the pres.- sure fluid flows from the pressure chamber in the consumer apparatus through the control valve along a tortuous path on which it is several times deflected.
  • valve piston means are provided which close the discharge opening of the straight passage while fluid is supplied into the passage and through the same to the pressure chamber of the consumer apparatus.
  • valve pistons are moved by pressure fluid in the supply conduit means and in the working cylinders to the second control position so that the discharge opening is closed, and pressure fluid flows through the channel means into the straight passage and out of the same into the pressure chamber of the consumer apparatus for expanding the same.
  • two oppositelyv arranged valve pistons have confronting inner frustoconical end portions cooperating with corresponding frustoconical valve seats.
  • Each of the valve seats has a slot, and the slots are respectively closed by the two valve pistons in the second control position.
  • valve pistons It is preferred to provide a channel in the valve pistons through which pressure fluid is guided into the straight passage.
  • a spring between the valve pistons urges the same apart to the first control position. It is advantageous to provide check valves in the channels of the valve pistons, so that the valve pistons close the discharge opening of the straight passage, before the check valves open and the pressure fluid can flow through the straight passage into the pressure chamber of the consumer apparatus.
  • each valve piston has its outer peripheral surface, at least one channel recess which is directly connected with the inlet conduit for the pressure fluid, and through which the pressure fluid can flow into the straight passage when the valve pistons are placed in the second control position closing-the discharge opening.
  • Channel means connect'the supplyconduit means with the passage portions of the passage.
  • Valve pistons are located in the working cylinders for movement toward and away from the straight passage between a first constraight passage. v It is advantageous to make the diameters of the piston parts outwardly of the channel recesses greater than the diameter of the piston parts located inward of the channel recesses, so that the pistons are urged outwardly to the first control position opening the discharge opening.
  • a further feature of the invention is to provide a double piston in a pressure cylinder forming balancing chambers at the ends of the pressure cylinder which are connected by first ducts with supply conduits for the fluid, and by second ducts with the straight passage.
  • the double piston is operated to move to one of its end positions and to actuate a stop motion switch for the consumer apparatus, if one of the control valves for controlling the flow of pressure fluid to the channels of the valve pistons does notproperly function, or if one of the valve pistons is blocked.
  • FIG. 1 is a schematic sectional view illustrating a first embodiment of the invention in a first control position
  • FIG. 2 is a fragmentary schematic sectional view taken on line Il-II in FIG. 1;
  • FIG. 3 is a schematic sectional view illustrating the embodiment of FIG. 1 in a second control position
  • FIG. 4 is a fragmentary schematic sectional view taken on line IV-IV in FIG. 3;
  • FIG. 5 is a schematic section illustrating the embodiment of FIG. 1 in undesired condition caused by a malfunction
  • FIG. 6 is a fragmentary cross section taken on line VI-VI in FIG. 5;
  • FIG. 7 is a schematic section illustrating a modification of the embodiment of FIG. 6 in a first control positron
  • FIG. 8 is a schematic sectional view of he embodiment of FIG. 7 in a second control position
  • FIG. 9 is a schematic sectional view illustrating another embodiment of the invention in a first control position
  • FIG. 10 is a fragmentary cross sectional view taken on line X-X inFIG. 9;
  • FIG. 11 is a schematic sectional view of the embodiment of- FIG. 9 is a second control position.
  • FIG. 12 is a fragmentary sectional view taken on line XII-XII in FIG. 11.
  • a control valve 10 has a housing 12 in which two valve pistons 14 and 16 are movably mounted in working cylinders 15 and 17.
  • the two pistons 14 and 16 are coaxial, and movable toward and away from each other.
  • the confronting inner end portions 18 and 20 of the two pistons 14 and 16 are frustoconical, and cooperate with corresponding frustoconical valve seats 22 and 24.
  • the working cylinders l5 and 17 are connected at the inner ends thereof by a passage portion.25.
  • Valve pistons 14 and 16 are sealed in working cylinders 15 and 17 by sealing rings 14a and 160.
  • Each of the pistons 14 and 16 has a cen-.
  • a compression spring 30 is mounted in the aligned bores 26 and 28, and has outer ends abuting shoulders 32 and 34 provided in bores 26 and 28. Spring 30 urges the two valve pistons 14 and 16 apart.
  • a check valve 36 and 38, respectively, is provided in each bore 26 and 28.
  • a passage 44 has an opening 40 at one end which is connected with the expanding and contracting pressure chamber of a hydraulic press, not shown, and has a discharge opening 42 at the other end thereof so that a pressure fluid discharged by the contracting pressure chamber of the hydraulic press can flow through passage 44 and out of discharge opening 42'without pressure loss.
  • the passage 44 between the openings 40 and 42 is straight so that fluid flowing into opening 40,
  • the straight passage .44 has two portions 45 and 47,
  • portion 45 is connected with the pressure chamber of the hydraulic press
  • portion 47 is connected with the return conduit.
  • the portion 45 is connected by a single opening 46 with the central space 49 from which a pressure fluid supplied through channels 26 and 28 can flow through portion 45 of passage 44 to the consumer apparatus, or through the discharge opening in portion 47 to the return conduit.
  • the portion 47 of the straight passage 40 communicates with the central space 49 through two discharge slots 48 and 50 which are separated by a partition body 52, as best seen in FIGS. 2 and 4.
  • the dischargeslots 48 and 50 have openings in the valveseats 22 and 24 of the valves 76 and 78, each of which includes one of the valve pistons 14 and 16, and the respective valve seats 22 and 24.
  • the working chambers 77 and 79 of valves 76 and 78 are connected by supply conduits 72 and 74 with control valves 54 and 56 which have valve seats 58,68, and 60,70, respectively.
  • the valve seats 58 and 60 of the, two control valves 54 and 56 are connected by supply conduits 64 and 66 with the inlet conduit 62 to which pressure fluid is supplied in the direction of the arrow P.
  • a pump may be connected with the inlet conduit 62.
  • the valve pistons 68 and 70 of the control valves 54 and 56 are, for example, electromagnetically operated.
  • Control valve 56 controls valve 78
  • control valve 54 controls valve 76.
  • the control valve device 10 is provided with a stop motion arrangement for stopping the consumer apparatus, such as a hydraulic press, when a malfunction takes place.
  • a pressure balancing device is provided for this purpose, and includes a double piston 82 movable in a pressure cylinder 83 in housing 12.
  • the end faces 84 and 86 of the double piston 82 form balancing chambers and 87 which-are connected by ducts 92 and 94 with the supply conduits 72 and 74 which connect the control valves 56,54 with the working chambers 77 and 79, and also connected by ducts 96 and 98 with the spaces 97 and99 in front of valve pistons 14' and 16. As shown in FIGS. 1 and 3, ducts 96 and 98 open at the valve seats 22 and 24.
  • Check valves 100 and 102 are provided in the ducts 92 and 94, together with throttles 103 and 105.
  • Double piston 82 has slanted actuating faces 104 and 106 which control the actuator ofa stop motion switch 110.
  • the control valve device 10 shown in FIGS. 1 to 4 operates as follows:
  • valves 54 and 56 are closed, and pressure fluid cannot flow through conduits 62, 64, 66 and valve seats 58 and 60. Neither valves 76 and 78, nor the stop motion device 80 are subjected to fluid pressure. Double piston 82 is in a central position due to the action of springs 88 and 90. Stop motion switch 110 is open. Valve pistons 14 and 16 are in the retracted outer positions and the pressure chamber of the consumer apparatus, not shown, is
  • the double piston 82 remains in the central position. so that stop motion switch 110 is not actuated.
  • FIGS. 5 and 6 illustrate a malfunction of. the device. It is assumed that upon shifting of control valves 54 and 56 by electromagnetic means, only the controlvalve 54 opens, as control valve 56, perhaps due to failure of the electromagnetic means, has remained in the inoperative position closing opening 60.
  • Piston 14 is subjected to pressure and moves towards its valve seat, while piston 16 remains in the outer inoperative position.
  • Discharge slot 50 is closed by piston 14, while discharge slot 48'remains open.
  • the pressure fluid flows through control valve 54 and opening 58 into the working chamber 77 and through the respective check valve 38 and the corresponding channel 26 and the open discharge slot 48 directly tothe return conduit.
  • the ratio between the flow across sections of the control valves 54 and 56 and the channel 26 is about 1:10 so that in the interior of the valve, only a small pressure remains which is below the pressure required by the pressure chamber of the .consumer apparatus, such as a coupling or a brake of a press. Consequently, no pressure fluid is supplied to the consumer apparatus.
  • the position of the control valve device shown in FIGS. 5 and 6 also results in the event that both control valves .54 and 56 are correctly operated, but valve piston16 is blocked in this outer position.
  • the pressure fluid flows through the channels in the valve pistons 14 and 16, and then flows through the open discharge slot 48 into thexreturn conduit.
  • the pressure fluid further flowsthrough duct 92 and duct 94 towards the balancing chambers 87 and 85.
  • duct 96 is closed by valve piston 14- so that pressure can develop in the balancing chamber 85
  • 1duct98 is open since valve piston 16 has not moved-forward to the inner control position.
  • the fluid flowing through duct 94 con ⁇ sequently flows through duct 98 into the space97' in front of valve piston'16, and out of discharge slot 48. No pressure can develop in balancing chamber 87 so that the double piston 82 moves to the left and operates the stop motion switch 10.
  • valve pistons 54 and 56 are shifted out of the position shown in FIG. 3 to the position of FIG. 1, while valve piston. 14 is blocked in the inner control position shown in FIG. 5.
  • Valve piston 16 is moved to the outer control position by the action of spring 30, so that discharge slot 48 leading to the return conduit, and also the opening of the duct 98 which is connected with balancing chamber 87 is uncovered.
  • the pressure chamber of the consumer apparatus is relieved since the straight passage 44 to the discharge opening 42 is opened.
  • the balancing chamber 87 is relievedsince the pressure fluid flows away through duct 98.
  • throttles 103 and 105 are provided .in ducts 92 and 94 in order to equalize small motion and shifting tolerances of the valves, and also for obtaining a uniform pressure built up in the safety device 80.
  • double piston 82 may be provided with a throttle connecting the two end faces.
  • FIGS. 7 and 8 corresponds to the embodiments of FIGS. 1 to 6, but has a different channel arrangement for connecting the inlet conduit 82 with the straight passage 44.
  • valve 120 is connected by a channel 122 with the inlet conduit 62.
  • the auxiliary piston 124 is connected by a piston rod 125 with valve 120, and is controlled by control valve 54 through a channel 126.
  • pressure fluid from inlet conduit 62 flows through valve seat 128 and a connecting chan- .nel 130 directly into the portion 45 of the straight passage 44 which is connected with the consumer apparatus, as explained with reference to FIG. 2.
  • valve 120 In the event that the valve 120 malfunctions and, for example, remains in the closed position as shown in FIG. 7, no fluid is supplied to the consumer apparatus. In the event that the valve 120 remains in its open position after the control valves 54 and 56 have been shifted, perhaps due to jamming of piston 124, the supplied pressure fluid flows through the discharge slots 48 and 50 which are opened by the retracted pistons 14 and 16. Consequently, a single valve 120 is sufficient.
  • each of the two valve pistons 14'.and 16 has four channel recesses 140 and 142, respectively, which extend parallel to the axis of symmetry of the respective piston and over a part of its axial length.
  • the channel recesses 140 and 142, respectively, are spaced 90 in circumferential direction, and the bottom of the channel recesses 140,142 is preferably part-circular so that the channel recesses 140,142 are substantially segment shaped, as shown in the drawing.
  • the channel recesses form part of the channel means by which the inlet conduit 62 is connected with the straight passage 44 when the valve piston 14' and 16 are in the inner control position shown in FIG. 12.
  • the channel recesses, and associated channels replace the channel bores 26 and 28 of the embodiment of FIGS. 1 to 4
  • the control valves 54 and 56 are closed.
  • the channel recesses 140 and 142 register with openings 160 and 162 and annular channels 161,163 in housing 12, and are further connected by supply conduits64 and 66 with an inlet conduit 62 through which the pressure fluid is supplied. Sealing means 156 and 158 in housing 12 prevent in the position of FIG. 9, the flow of pressure fluid from channel recesses 140,142 into the straight passage 44.
  • Sealing means 156 and 158 cooperate with portions 148 and 150 of the valve pistons 14' and 16'. Sealing means 152,154 seal the channel recesses 140,142 from the separate conduits 72 and 74 which are supplied with fluid when the control valves 54 and 56 are operated. Sealing rings 152,154 are mounted in annular portions 144 and 146 of the valve pistons 14' and 16'.
  • valve seats 60 and 58 When the control valves 54 and 56 are moved to the position of FIG. 11, pressure fluid flows through valve seats 60 and 58 into the supply conduits 72 and 74 and exerts pressure on the outer end faces of valve pistons 14' and 16' so that the valve pistons move to the inner control position closing the discharge slots 48 and 50 which communicate with the discharge opening 42.
  • the channel recesses 140,142 are in this control position not any more sealed from the straight passage 44.
  • the pressure fluid flows through inlet conduit 62, supply conduit 64 and 66, openings 160 and 162, and annular channels 161 and 163 into the channel recess 140.142 and out of the same through annular gaps 164,166, see FIG. 12, so that the fluid enters the straight passage 44 and flows to the consumer ap'- paratus.
  • Annularchannels 168,170, see FIG. 12, are provided in housing 12 through which the pressure fluid flowing out of annular gaps 164 and 166 is guided to the opening 40 communicating with consumer apparatus.
  • the diameter of the piston portions 154,156 which are located outwardly of the channel recesses 140,142 is greater than the diameter of the portions 148,150 which are located inwardly of the channel recesses 140,142.
  • a pressure differential is obtained which urges the. valve pistons14' and 16' outof the control position shown in FIG. 9.
  • the embodiments of FIGS. 9 to 12 is particularly advantageous since it. is suitable for very high volumes of the pressure chamber'of theconsumer apparatus without requiring valve 120 of the embodiment of FIGS. 7 and 8.
  • the spring by which the fluid is pressed out of the working chambers of valve pistons 14 and 16' in the embodiments of FIGS. 1 to 8, can be so designed that it permits a closing of the straight passage 40 by the valve pistons only at a predetermined pressure, for example more than 3 k/cm. Such an arrangement eliminates the necessity of providing a pressure operated switch responsive to the pressure of the fluid.
  • More than one safety device may be provided for operating other switches when a malfunction takes place. It is advantageous to make the valve pistons of a synthetic plastic material so that the mass is small, permitting a further reduction of the time periods for acceleration of the pistons so that the time required for shifting the control valve device is further reduced.
  • Control valve for controlling the flow to and from a variable pressure chamber of a consumer apparatus, comprising housing means including a substantially straight passage means connected at one end with said pressure chamber, and having at the other end thereof a discharge opening, said housing means having working cylinder means laterally of said straight passage means, and supplyconduit means including an inlet conduit for supplying a pressure fluid into said working cylinder means; channel means connecting said supply conduit means with apassage portion of said passage means; and valve piston means located in said working cylinder means for movement toward and away from said straight passage means between a first control position retracted from said straight passage means so that fluid from said pressure chamber flows through said straight passage means and directly out of said discharge opening, and a second control position located in said straight passage means and closing said discharge opening, said valve piston means being moved by pressure fluid in said supply conduit means and in said working cylinder means to said second control position so that said discharge opening is closed, and pressure fluid flows through said channel means into said passage portion and out of said one end into said pressure chamber for expanding the same.
  • Control valve as claimed in claim 1,;wherein said working cylinder means includes two working cylinders located on opposite sides of said straight passage means; wherein said valve piston means include two valve pistons located in said working cylinders; wherein said supply conduit means includes two supply conduits respectively connecting said inlet conduit with said working cylinder; wherein said channel means includes two channels formed by said valve pistons, respectively, and communicating with said working cylinders, respectively; and wherein fluid pressure in said supply conduits and working cylinders-simultaneously urges said valve pistons to said second control position for together closing said discharge opening while pressure fluid flows through said channels and straight passage means into said pressure chamber.
  • said straight passage means includes a partition body divide ing said discharge opening into two discharge slots; wherein said frustoconical end portions of said valve piston in said second control position abut said partition body and close said discharge slots.
  • Control valve as claimed in claim 4 wherein said work-ing cylinders are located outward of said valve pistons and receive the end portions of said valve pistons remote from said frustoconical end portions.
  • Control valve as claimed in claim 2 wherein said channel means include axially extending bores in said valve pistons having partly closed outer ends; and a pressure spring located in said bores between said partly closed ends, and urging said valve pistons apart to said first control position.
  • Control valve as claimed in claim 2 wherein said channels'extend between the outer and inner ends of said valve pistons, respectively; and comprising biassed check valves located in said channels, respectively, and adapted to close said channels so that said valve pistons are moved to said second controlposition by the pressure in said working cylinders whereupon the pressure increases in said working chambers and opens said check valves to permit flow through said channels into said passage means and out of 'said one end of the same.
  • Control valve as claimed in claim 2 comprising two control valves mounted in said housing means operable between an operative position opening said supply conduits, respectively, and an inoperative position closing the same so that the movements of said valve pistons are controlled by said control valves; and wherein the ratio between the effective flow cross sections of said supply conduits controlled by said control pistons and said channels in said valve pistons is about 1:10.
  • Control valve as claimed in claim 1 comprising a valve means located in said channel means and having a closed position, and an open position for connecting said inlet conduit directly with said straight passage means.
  • Control valve as claimed in claim 10 comprising control valve means mounted on said housing means operable between an operative position connecting said inlet conduit with said working cylinder means, and .an inoperative position disconnecting the same; and comprising actuating piston and cylinder means for operating said valve means under the control of said control valve means.
  • Control valve means as claimed in claim 1, wherein said working cylinder means include two working cylinders located on opposite sides of said straight passage means; wherein said valve piston means include two valve pistons located in said working cylinders, respectively; wherein said supply conduit means include two supply conduits connecting said inlet conduit with said working cylinders, respectively; and wherein said channel means include channel recesses in said valve pistons communicating with said inlet conduit and being closed in said first control position,and communicating also with said straight passage means in said second control position.
  • valvepistons comprise sealing rings engaging said working cylinders in said first control position for sealing said channel recesses against communication with said straight passage means.
  • channel recesses include a plurality of channel recesses spaced circumferentially about each of said valve pistons.
  • Control valve as claimed in .claim 14 wherein said channel recesses extend in the respective valve piston parallel to the axis of symmetry of the same and over a part of the length of the same.
  • each of said channel recesses has a part-circular bottorn and is segment shaped.
  • each valve piston has a greater diameter at the outer end portion remote from said straight passage means than at the inner end portion thereof; and wherein said channel recesses are located between said inner and outerend portions.
  • said working cylinder means include two working cylinders located on opposite sides of said straight passage means; wherein said valve piston means include two valve pistons located in said working cylinders, respectively; wherein said supply conduit means include two supply conduits connecting said inlet conduit with said working cylinders, respectively; wherein said housing means forms a pressure cylinder having ends; comprising a double piston in said pressure cylinder forming balancing chambers at said ends of said pressure cylinder and being movable between a central inoperative position, and two end positions; a stop motion switch actuated by said double piston in said end positions; wherein said housing means has first ducts connecting said supply conduits with said balancing chambers, respectively, and second ducts connected with said balancing chambers, respectively, and communicating with said straight passage means in said first control positions of said valve pistons, and being closed, respectively, by the respective valve piston in said second control position of the same whereby malfunctions of any valve piston causes movement of said double piston to one end position and actuation of said stop
  • Control valve as claimed in claim 18, comprising check valves in said first ducts for blocking flow from said balancing chambers into said supply conduits, respectively.
  • Control valve as claimed in claim 18, comprising throttle means in said first ducts, respectively.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Multiple-Way Valves (AREA)
  • Fluid-Driven Valves (AREA)
  • Regulating Braking Force (AREA)
  • Valves And Accessory Devices For Braking Systems (AREA)
  • Control Of Presses (AREA)
US3699993D 1970-05-06 1970-12-31 Control valve for the flow to and from a variable pressure chamber Expired - Lifetime US3699993A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH693570A CH501860A (de) 1970-05-06 1970-05-06 Sicherheitsventil für druckmittelbetriebene Vorrichtungen
CH995370A CH509535A (de) 1970-05-06 1970-06-30 Sicherheitsventil für druckmittelbetriebene Vorrichtungen

Publications (1)

Publication Number Publication Date
US3699993A true US3699993A (en) 1972-10-24

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US3699993D Expired - Lifetime US3699993A (en) 1970-05-06 1970-12-31 Control valve for the flow to and from a variable pressure chamber

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US (1) US3699993A (es)
JP (1) JPS4919293B1 (es)
CH (1) CH509535A (es)
ES (1) ES195163Y (es)
FR (1) FR2066747A5 (es)
GB (1) GB1291507A (es)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3870073A (en) * 1973-02-14 1975-03-11 Technomatic A G Valve assembly for controlling fluid pressure operated apparatus particularly presses
DE4032877A1 (de) * 1990-10-17 1992-04-23 Teves Gmbh Alfred Durchflussregelventil
US6382076B1 (en) * 1998-08-24 2002-05-07 Industria De Turbo Propulsores, S.A. Piston servo-actuation main system with hydromechanically self-contained detection
US20040182234A1 (en) * 2002-12-20 2004-09-23 Dorma Gmbh + Co. Kg Electrohydraulic servo door drive for operating a door, a window, etc.
US20050045234A1 (en) * 2003-09-03 2005-03-03 Bento Jose Carlos Double valve constructed from unitary single valves

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS49135792U (es) * 1973-03-24 1974-11-21
JPS5222194U (es) * 1975-07-11 1977-02-16
CN111577695A (zh) * 2020-06-15 2020-08-25 裕泰液压科技(上海)有限公司 一种导向溢流阀用整体插装式阀芯组件

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3870073A (en) * 1973-02-14 1975-03-11 Technomatic A G Valve assembly for controlling fluid pressure operated apparatus particularly presses
DE4032877A1 (de) * 1990-10-17 1992-04-23 Teves Gmbh Alfred Durchflussregelventil
US6382076B1 (en) * 1998-08-24 2002-05-07 Industria De Turbo Propulsores, S.A. Piston servo-actuation main system with hydromechanically self-contained detection
US20040182234A1 (en) * 2002-12-20 2004-09-23 Dorma Gmbh + Co. Kg Electrohydraulic servo door drive for operating a door, a window, etc.
US6978609B2 (en) * 2002-12-20 2005-12-27 Dorma Gmbh + Co. Kg Electrohydraulic servo door drive for operating a door, a window, etc.
US20050045234A1 (en) * 2003-09-03 2005-03-03 Bento Jose Carlos Double valve constructed from unitary single valves
US7114521B2 (en) * 2003-09-03 2006-10-03 Ross Operating Valve Company Double valve constructed from unitary single valves
CN100378347C (zh) * 2003-09-03 2008-04-02 罗斯控制阀公司 由单式阀构成的双联阀

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Publication number Publication date
JPS4919293B1 (es) 1974-05-16
CH509535A (de) 1971-06-30
GB1291507A (en) 1972-10-04
FR2066747A5 (es) 1971-08-06
ES195163U (es) 1975-01-16
ES195163Y (es) 1975-07-01

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