US2376519A - Valve control for presses and the like - Google Patents

Valve control for presses and the like Download PDF

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US2376519A
US2376519A US496602A US49660243A US2376519A US 2376519 A US2376519 A US 2376519A US 496602 A US496602 A US 496602A US 49660243 A US49660243 A US 49660243A US 2376519 A US2376519 A US 2376519A
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valve
main
chamber
pressure
press
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US496602A
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Thomas F Stacy
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French Oil Mill Machinery Co
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French Oil Mill Machinery Co
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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/024Systems essentially incorporating special features for controlling the speed or actuating force of an output member by means of differential connection of the servomotor lines, e.g. regenerative circuits
    • BPERFORMING OPERATIONS; TRANSPORTING
    • B30PRESSES
    • B30BPRESSES IN GENERAL
    • B30B15/00Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B30B15/16Control arrangements for fluid-driven presses
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/024Systems essentially incorporating special features for controlling the speed or actuating force of an output member by means of differential connection of the servomotor lines, e.g. regenerative circuits
    • F15B2011/0243Systems essentially incorporating special features for controlling the speed or actuating force of an output member by means of differential connection of the servomotor lines, e.g. regenerative circuits the regenerative circuit being activated or deactivated automatically
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/20Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/21Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge
    • F15B2211/212Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge the pressure sources being accumulators
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/30Directional control
    • F15B2211/305Directional control characterised by the type of valves
    • F15B2211/30525Directional control valves, e.g. 4/3-directional control valve
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/30Directional control
    • F15B2211/305Directional control characterised by the type of valves
    • F15B2211/3056Assemblies of multiple valves
    • F15B2211/30565Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve
    • F15B2211/3058Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve having additional valves for interconnecting the fluid chambers of a double-acting actuator, e.g. for regeneration mode or for floating mode
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/30Directional control
    • F15B2211/315Directional control characterised by the connections of the valve or valves in the circuit
    • F15B2211/3157Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source, an output member and a return line
    • F15B2211/31576Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source, an output member and a return line having a single pressure source and a single output member
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/30Directional control
    • F15B2211/32Directional control characterised by the type of actuation
    • F15B2211/329Directional control characterised by the type of actuation actuated by fluid pressure
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/60Circuit components or control therefor
    • F15B2211/635Circuits providing pilot pressure to pilot pressure-controlled fluid circuit elements
    • F15B2211/6355Circuits providing pilot pressure to pilot pressure-controlled fluid circuit elements having valve means
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/70Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/75Control of speed of the output member
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/70Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/775Combined control, e.g. control of speed and force for providing a high speed approach stroke with low force followed by a low speed working stroke with high force, e.g. for a hydraulic press

Description

May 22, 194-5. I s v 2,376,519
' 'VALVE CONTROL FOR PRESSES AND THE LIKE Fild July 29,, 1945 INVENTOR V Thogzas 7'? 320g ATTORNEYS i Patented May 22, 1945 2,378,519 VALVE CONTROL FOR PBESSES AND THE LIKE Thomas F. Stacy, Plqua, Ohio, asslgnor to The FrenchOll Mill Machinery Company, Plqna,
Ohio
Application July 29, 1943, Serial No. 496,602 8 Claims. (01.121-38) uld under pressure which is delivered to and ex- This invention relates to improvements in operating or control valve mechanisms for fluid- -pressure-actuated presses and the like, a primary purpose of my invention being to provide a valve mechanism adapted to effect a very high speed of operation of the press with the use of the minimum volume of pressure fluid in order to conserve pressure fluid and avoid the necessity for maintaining or pumping a large quantity thereof.
Another object of the invention is to provide an eflicient, practical and desirable operating or control valve mechanism for presses and the like which is of novel, improved construction; which is adapted to effect a rapid initial movement of the press ram or movable member with the minimum use of pressure fluid, and then increase the operating pressure on the press ram or member when it encounters a predeterminedresistance to its movement, and a rapid return or pull-back movement of the press ram or member.
Further objects and advantages of the invention will appear from the following specification of the preferred embodiment of the invention, shown in the accompanying drawing, and the novel features of the invention are set forth in the appended claims.
In said drawing, the flgure is a schematic view, artly in section, of a press operating valve mechanism embodying the invention, showing by solid lines the positions occupied bythe parts during the initial rapid portion of the work stroke of the press ram before the maximum pressure is applied; and indicating by broken lines the positions of the movable valve elements for the application of maximum pressure'and for the pull-back or return movement of the press ram.
Referring to the drawing, l represents astatio'nary member or cylinder and II the movable ram piston or member of a press actuated by hydraulic or fluid pressure. ,The chamber II, or portion of the cylinder at one side or end of the piston, constitutes tile work chamberin which the pressure acts on the larger area of this end face of the pistonfor producing the work stroke of the piston, and the cylinder chamber l3 'at the opposite side or end of the piston forms a pullback chamber l3 in which the pressure acts,
against the other end face of the piston, which is of smaller area, to pull back or return the piston or movable press member. The work and pullback chambers are shown as chambers in a single cylinder, but the invention is not restricted to this form of pressure actuating means for the movable press ram or member.
l5 represents an accumulator or source of liqhausted from the press chambers l2 and I3 for operating the press under the control of a valve or device A and valves B and C, which, for con venience of description, are herein respectively designated the operating valve, the main control valve and the auxiliary control valve. The main and auxiliary valves B and C control the passages ofthe pressure fluid to and from the work and pull-back chambers of the press, and the operating device A serves as a pilot valve for actuating the control valves B and C.
The control valves B and C may be of similar construction each, as shown, comprising a cylindrical casing in which a valve element is adapted to be moved endwise in one or the other direction by fluid pressure in opposed actuating cylinders or chambers, preferably at opposite ends of the valve casing. Referring first to main valve B, its casing forms a central valve chamber l6 and opposite end actuating cylinders I1 and i8, and its movable element comprises a body l9 having spaced lands or enlarged portions 2|] and 20a slidably fitting in the valve chamber l6, a'reduced central or waist portion and pistons 2| and 22 at its opposite ends, one piston 2l working in the cylinder i1 and the other piston .working in the cylinder l8. Pistons 2i and 22 are of different cross sectional areas, the piston 2| being the larger, so that the pressure on this piston can move the valve element to the right, as seen in the drawing, in opposition to pressure on the other piston. The auxiliary control valve C is similar to the valve B, as thus far described, and the corresponding parts are designated by the like reference numerals.
As illustrated, the operating valve A comprises a cylindrical casing23 in which a movable element, comprising spaced pistons or lands 24 and 26 on a rod or stem, is movable endwise, the rod or stem 28 projecting out of one end of the cylinder to enable actuation of the valve, as by means of a foot pedal or member 2i which when 1 depressed, pushes the movable element inwardly or in one direction, while opposite movement of the element may be efiected as by a spring 28, located between the inner end of the movable element and the adjacent end of the valve casing. An intermediate port in the casing of operating valve A is connected by a pipe or conduit 30 with the accumulator, and said valve casing has ports, one connected by a pipe 3| and branches to the actuating cylinders ll of the main and auxiliary control valves B and C, and the other connected by a pipe or conduit 32 and branches to-the opposed actuating cylinder ll! of the control valves B and C. Said pipe or conduit 3| also connects with the work chamber l2 of the press cylinder. Main control valve B has an intermediate port connecting by a pipe or conduit 35 with the aca chamber port of auxiliary valve C, and the chamber of auxiliary valve C has an intermediate port connected by a pipe or conduit 38 with the pull-back chamber I3 of the press, and another intermediate port connected by a pipe or conduit 39 with the work chamber |2 of the press, as by juncture with the pipe 36. An exhaust pipe or conduit 40 is also connected by branches with the opposite ends of the chamber l6 of the main valve B, and by branches 4| and 42 with opposite end portions of the casing of the operating valve A.
In the pipe 3|, between its connections with the two control valves B and C, is a check valve 45 adapted to open freely, as indicated by the arrow, in the direction to admit pressure to the actuating cylinder I! of the auxiliary valve C. A bypass bleeder passage 46 permits slow leakage or only a restricted passage of pressure liquid through pipe 3| in the opposite direction past this check valve 45 when closed. In the same pipe 3|, between its connections with the press chamber l2 and the auxiliary control valve is a check valve 41 adapted to open freely, as shown by the arrow, in the direction to admit passage of pressure from the work chamber |2 of the press cylinder; and also in the sameportion of pipe 3| is a pressure relief valve or device 43 of any'usual or suitable construction adapted to open to permit passage of pressure fluid from the work chamber l2 of the press to the actuating cylinder I! of the auxiliary control valve 0 when the pressure in work chamber 2 reaches a predetermined value for which the ressure relief valve 48 is set.
The operation of the press operating or con trol-mechanism may be described as follows: The drawing shows by solid lines the positions of the movable parts of the mechanism when operating valve A has been actuated by depression of its pedal 21 to start the work stroke of the press ram or member. In this position of the operat'-- ing valve A, liquid is delivered from the accumulatqr through pipe 30, operating valve casing 23 and pipe 32 to the smaller actuating cylinders I8 of the two control valves B and C, thereby moving and holding their movable elements to the left, as shown in the drawing. Any opposing liquid pressure in the other valve actuating cylinders I! can exhaust through pipe 3|, bleeder bypass 46, operating valve casing 23 and exhaust pipe 42, thus permitting the left hand movement of the control valves B and C. Pressure liquid then will be delivered from the accumulator through Pipe 35, casing of main control valve B and pipe 36 to the work chamber |2 of the press to produce a working stroke of the Press raih or member. At this time, pipes 38 and 39 and the chamber of the auxiliary valve C connect the pull-back and'work chambers l3 and I2 of the press so that liquid can flow freely from the pull-back chamber into the work chamber, thus producing rapid motion of the press piston member in its working stroke. The free flow of the liquid from the pull-back chamber into the work chamber of the press in this way reduces the volume of pressure liquid required to be supplied by the accumulator to produce the working stroke of the press ram and effects a rapid movement of the latter. When, because of increasing resistance of the work to this work stroke of the press ram or member, the liquid pressure in work chamber I2 reaches the value for which the pressure relief valve 48 is set, this valve is opened by the liquid pressure from the work chamber I2 and the liquid will flow past the check valve 4'! and pressure relief valve 48 into the actuating cylinder ll of auxiliary valve 0. Since the piston 2| is of larger diameter than the opposing piston 22, the movable element of auxiliary valve C will be moved to the right, as seen in the drawings, to the position indicated by the broken lines. Similar actuation of the main control valve B at this time by the pressure from the work cham-. ber l2 of the press is prevented because the cylinder ll of main valve B is open to exhaust beyond the check valve 45 and bleeder bypass 46, and main control valve B will remain in the left hand position shown. In this position of the two valves, the liquid will continue to pass from the accumulator to the work chamber |2 of the press through the pipes 35 and 36, as before, but the liquid will discharge from the pull-back chamber 3 through pipe 38, chamber l6 of auxiliary valve C, pipe 31 and chamber of valve B to the exhaust pipe 40 through its branch which connects with the right hand end of control valve B. Full pressure is thus applied to the press ram member to permit the maximum pressure thereof on the work.
When the working stroke of the press ram has been completed, the pedal 21 is released to permit the operating valve element to be moved by its spring to its other Or left hand position, indicated by broken lines in the drawing. In this position, operating valve will cut oil? the supply of liquid from the accumulator through pipes 30 and 32 to the right hand cylinders of control valves B and C and will connect supply pipe 30 with pipe 3|, thus delivering the pressure liquid to the left hand cylinder I! of the main control valve B and shifting the movable element of this valve to the position indicated by broken lines in the drawing. The auxiliary control valve C had already been moved to this right hand position, as before explained, and is there held by admission of pressure from the pipe 3| to the left hand cylinder ll of auxiliary valve C. In this position of the valves, work chamber l2 of the press will be connected to the exhaust pipe 40 through pipe 36, chamber l6 of main valve B and the left hand branch of the exhaust pipe 40, while liquid will be delivered from the accumulator through pipe 35, chamber l6 of main v'alve B, pipe 31, chamber of auxiliary valve 0. and pipe 38 to the pullback chamber l3 of the press cylinder, thereby eifecting a rapid return or movement to the left of the press ram or member. The parts will remain in this position with the press ram in its retracted position until the operating valve is again operated by depression of its pedal to return the valves to the position shown by solid lines in the drawings to effect the next operation of the press.
Upon such subsequent actuation of the operating valve, the pressure liquid will be admitted, as before explained, to the right hand cylinders ll! of control valves B and C, and at this time the left hand cylinder ll of the main valve B will be connected with the exhaust pipe 40 through the pipe 3| and casing 23 of operating valve A and branch 42 of exhaust pipe, and the left hand cylinder of the auxiliary control valve C will be similarly connected to the exhaust through pipe 3i and the bleeder bypass 46 o! the check valve 45, which will thus permit the pressure on the smaller piston 22 of auxiliary valve C to overcome the pressure on the larger piston 2| thereof and thus restore this valve to the solid line position shown, that is, to the left hand psition in the valve casing, thus permitting the working stroke of the press ram as before explained.
I claim as my invention:
1. In an operating mechanism for an hydraulic press or the like having a movable member, a source of liquid under pressure, main and pullback chambers, and means on which pressure liquid supplied to said chambers acts respectively to produce working and return strokes of said press member, the improved construction comprising a main valve having a movable element controlling ports and passages arranged to supply liquid from said supply source to said main press chamber and to exhaust liquid from said main and pull-back chambers, an auxiliary valvethaving a movable element controlling ports connecting with a port in the main valve and with said main and pull-back chambers, said main and auxiliary valves in a first position of their said elements I connecting said main press chamber with said supply source and connecting said pull-back chamber with said main chamber for effecting a rapid work stroke of the press member, and said valves in said first position of said main valve element and in a second position of said auxiliary valve element connecting said main chamber with said supply source and opening said pull-back chamber to exhaust for increasing pressure on the press member, and said main and auxiliary valves in. the second position of their elements opening said main chamber to exhaust and connecting said pull-back chamber with saidsupply source for returning said press member, first pressure actuated devices for moving said main and auxiliary valve elements to said first position and second pressure actuated devices for moving said main and auxiliary valve elements to said second position, an operating valve having a movable element controlling ports and passages arranged to supply liquid from said said supply source to and exhaust liquid from said pressure actuated devices for said main and auxiliary valves, said passage to said second pressure actuating devices also connecting with said main press chamber, means which controls saidpassage and allows flow of pressure liquid from said main press chamber to said'second actuating device of said auxiliary valve when the movable press member encounters a predetermined resistance but prevents flow through said passage to said main chamber, and a check valve which controls said passage between said second actuating devices for said main and auxiliary valves and allows iree flow of liquid to the actuating device of said auxiliary 'valve and has a bleeder bypass which allows restricted opposite flow of liquid.
2. In an operating mechanism for an hydraulic press or the like having a movable member, a source of liquid under pressure, main and pullback chambers, and means on which pressure liquid supplied to said chambers a'cts respectively to produce working and return strokes of said press member, the improved construction comprising a main valve having a movable element controlling ports and passages arranged to supply liquid from said supply source to said main press chamber and to exhaust liquid from said main and pull-back chambers, an auxiliary valve haying a movable element controlling ports connecting .with a port in the main valve and with said main and pull-back chambers, said main and auxiliary valves in a first position of their said elements connecting said main press chamber with said supply source and connecting said pull-back'chamber with said main chamber for effecting a rapid work strok of the press member, and said valves in said first position of said main valve element and in a second position of said auxiliary valve element connecting said main chamber with said supply source and opening said pull-back chamber to exhaust for increasing pressure on the press member, and said main and auxiliary valves in the second position of their elements opening said main chamber to exhaust and connecting said pull-back chamber with said supply source for returning said press member, first pressure actuated devices for moving said main and auxiliary valve elements to said first position and second pressure actuated devices for moving said main and auxiliary valve elements to said second position, an operating valve having a movable element controlling ports and passages arranged to supply liquid from said supply source to and exhaust liquid from said pressure actuated devices for said main and auxiliary valves, said passages to said second pressure actuating devices also connecting with said main press chamber, a check valve and a pres sure relief valve which control said passage and prevent liquid flow therethrough to said main press chamber but allow fiow of pressure liquid from the main press chamber to said second actuating device of said auxiliary valve when the movable press member encounters a predetermined resistance, and a check valve which controls said passage between said second actutaing devices for said main and auxiliaryvalves and allows free fiow of liquid to the actuating device of said auxiliary valve and has a bleeder bypass which allows restricted opposite flow of liquid.
3. In an operating mechanism for an hydraulic press or the like having a movable member, a sourc of liquid under pressure, main and pullback chambers, and means on which pressure liquid supplied to said chambers acts respectively to produce working and return strokesof said press member, the improved construction comprising main and auxiliary valves each having a reciprocable element with. opposed actuating pistons of different pressure areas working in correspondingly different pressure cylinders, said main valve element controlling ports and passages arranged to supply liquid from said supply source to said main press chamber and to exhaust liquid from said main and pull-back chambers, and said auxiliary valve element controlling ports connecting with a port in the main valve and with said main and pull-back chambers, said main and auxiliary valves in a first position of their said elements connecting said main press chamber with said supply source and connecting said pull-back chamber with said main chamber for effecting a rapid work stroke of the press memher, and said valves in'said first position-of said,
main valve element and in a second position of said auxiliary valve element connecting said main chamber with said supply source and opening said pull-back chamber to exhaust for increasing pressure on the press member, and said main and auxiliary valves in the second position of their said elements opening said main chamber ber with said supply source for returning said press member, an operating valve and passages constructed and arranged to supply liquid from said source to and exhaust liquid from said actuating cylinders for moving said main and auxiliary valve elements to said first and second positions, said passage to the cylinders of larger area also connecting with said main press chamber, means which controls said passage and allows flow of pressure liquid from said main press chamber to the actuating cylinder of said auxiliary valve when the movable press member encounters a predetermined resistance but prevents flow through said passage to the main press chamber, and a check valve which controls sai passage between its connections with the actuating cylinders for said main and auxiliary valves and allows free flow of liquid to the actuating cylinder of said auxiliary valve and has a bleeder bypass which allows only restricted opposite flow oi liquid.
4. In-an operating system for a fluid actuated operating said main valve to vent said advancing chamber and connect said source to said auxiliary valve, and for operating said auxiliary valve to break said direct connection between said chambers and connect sald'retracting chamber to said source through said main valve, and means automatically responsive to fluid pressure in said advanein chamber for separately causing operation or said auxiliary valve to break the direct connection between said chambers whenever the fluid pressure in said advancing chamber is above a predetermined pressure.
6. In an operating system for a fluid actuated motor of that type having advancing and retracting chambers, a working element operated by pressure alternately in said chambers, and a source of actuating fluid under pressure, that improvement in the control of the movement of said element which comprises means for connecting said source alternately to said chambers and venting the chamber not connected to said source,
motor of the type having advancing and retracting chambers, a working element operated by pressure alternately in said chambers, and a source of actuating fluid under pressure, that improvement in the control of the movement of said element which comprises a main valve and an auxiliary valve each having two conditions of operation. and pilot controlled means for operating said valves into said conditions, connections by which said auxiliary valve when in one condition connects said chambers directly to each other and when in another condition disconnects said chambers from each other and connects said retracting chamber to said main valve, connections by whichsaid main valve when in one condition connects said source to said advancing chamber and connects said auxiliary valve to exhaust, and in another condition connects said source to said auxiliary valve and connects said advancing chamber to exhaust, a control valve, and direct connections independent of said main and auxiliary valves between said source, said control valve and said pilot controlled means for causing operations of said main and auxiliary valves upon operation of said control valve, and means automatically responsive to the pressure in said advancing chamber for causing operation of said auxiliary valve into its said another condition while the pressure in said advancing chamher is above a predetermined pressure.
5. In an operating system for a fluid actuated motor of the type having advancing and retracting chambers, a working element operated by pressure alternately in said chambers, and a source of actuating fluid under pressure, that improvement in the control of the movement of said element which comprises a main valve, an auxiliary valve, connections controlled by said auxiliary valve for alternately connecting said chambers directly together, and for breaking said direct connections and connectingsaid retracting chamber to said main valve, connections controlled by said main valve for connecting said source alternately to said advancing chamber and to said auxiilary valve, and for venting any connections not connected to said source, a control valve, means controlled by said control valve and operating independently of said main and auxiliary valves for either causing operation of said main valve to connect said source to said advancing chamber and operation or said auxiliary valve to connect said chambers directly, or for means for breaking the connection from said source to said retracting chamber and instead connecting said retracting chamber directly to said advancing chamber, selectively controlled means operating independently of said first and second mentioned means to cause operation of said first means to connect said source to said advancing chamber and concurrently of said second means to directly connect said chambers, or to cause operation of said first means to vent the connection to said advancing chamber and connect said source through said first means to said retracting chamber, and means responsive to the fluid pressure in said advancing chamber and free of the control of said controlled means, for
. forcibly operating said second means to break the fluid supplied to said chambers acts respectively to produce working and return strokes of said motor member, the improved construction comprising a main valve having a movable element controlling ports and passages arranged to supply fluid from said supply source to said main chamber and to exhaust liquid from said main and pull-back chambers, an auxiliary valve having a movable element controlling ports connecting with a port in the main valve and with said main and pull-back chambers, said main and auxiliary valves in a first position of their said elements connecting said main press chamber with said supply source and connecting said pullback chamber with said -main chamber for effecting a rapid work stroke of the motor mem ber, and said valves in said first position of said main valve element and in a second position of said auxiliary valve element connecting said main said first and last mentioned relative positions, and means actuated under control or fluid pressure from said main chamber when the movable motor member encounters a predetermined resistance for effecting said second mentioned relative positions or said main and auxiliary valve elements.
8. In an operating mechanism for a fluid actuated motor having a movable member, a source of fluid under pressure, main and pull-back chambers, and means on which pressure fluid supplied to said chambers acts repectively to produce working and return strokes of said motor member, the improved construction comprising a main valve having a movable element controlling ports and passages arranged to supply fluid from said supply source to said main chamber and to exhaust fluid from said main and pull-back chambers, an auxiliary valve having a movable element controlling ports connecting with a port in the main valve and with said main and pull-back chambers, said main and auxiliary valves in a first position of their said elements connecting said main chamber with said supply source and connecting said pull-back chamber with said main chamber for eifecting a rapid work stroke of the motor member, and said valves in said first posi tion of said main valve element and in a second position of said auxiliary valve element connecting said main chamber with said supply source and opening said pull-back chamber to exhaust for increasing pressure on'the motor member, and
said main and auxiliary valves in the second position of their elements opening said main chamber to exhaust and connecting said pull-back chamber with said supply source for returning said motor member, first pressure actuated devices for moving said main and auxiliary valve elements to said first position and second pressure actuated devices for moving said main and auxiliary valve elements to said second position,
an operating valve having a movable element movable motor member encounters a predetermined resistance but prevents flow through said passage to said main chamber, and means which controls said passage between said second actuating devices for said mainand auxiliary valves and allows free flow of fluid to the actuating device of said auxiliary valve and allows only restricted opposite'flow of fluid.
THOMAS F. STACY;
US496602A 1943-07-29 1943-07-29 Valve control for presses and the like Expired - Lifetime US2376519A (en)

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Cited By (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2552067A (en) * 1944-12-29 1951-05-08 French Oil Mill Machinery Hydraulic control system
US2636346A (en) * 1948-11-26 1953-04-28 Lake Erie Engineering Corp Pressure accumulator circuit for hydraulic presses
US2641228A (en) * 1950-05-26 1953-06-09 Denison Eng Co Control valve mechanism for hydraulic motors
US2666292A (en) * 1948-03-18 1954-01-19 United Eng Foundry Co Control system for hydraulic presses
US2739445A (en) * 1952-09-20 1956-03-27 Lorant Hugo Hydraulic machinery
US2849986A (en) * 1954-09-11 1958-09-02 Klopp Friedrich Hydraulic control mechanism for planing machines
US2890683A (en) * 1952-02-06 1959-06-16 John S Pilch Fluid actuated control valve means for fluid motors
US3133472A (en) * 1961-09-05 1964-05-19 Electro Mechanics Inc Impact device control system
US3200713A (en) * 1961-04-04 1965-08-17 Philips Corp Hydraulic servo-mechanism
US3211424A (en) * 1964-08-19 1965-10-12 Chrysler Corp Control mechanism for adjustable gas turbine nozzle
DE977301C (en) * 1951-09-23 1965-11-11 A Pelissier Nachf Maschf Hydraulic press with a differential piston that forms an annular space on its back with the press cylinder
US3298284A (en) * 1964-09-11 1967-01-17 Rockwell Mfg Co Servo operated reversing tool
US3408897A (en) * 1964-11-18 1968-11-05 Champion Inc Fluid power hammer having accumulator means to drive the hammer through its working stroke independent of the system pump
US3654837A (en) * 1969-12-29 1972-04-11 Abex Corp Hydraulic control systems
US3795177A (en) * 1971-11-04 1974-03-05 Caterpillar Tractor Co Fluid motor control circuit providing selective fast motion
US3981228A (en) * 1973-11-13 1976-09-21 Robert Bosch G.M.B.H. Hydraulic control system
US4397221A (en) * 1981-06-01 1983-08-09 Deere & Company Regenerative valve
US5226363A (en) * 1990-09-11 1993-07-13 The Langston Corporation Dual pressure preload system for maintaining a member
US10670201B1 (en) * 2019-06-19 2020-06-02 5.11, Inc. Headlamp with light source on removable slotted body

Cited By (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2552067A (en) * 1944-12-29 1951-05-08 French Oil Mill Machinery Hydraulic control system
US2666292A (en) * 1948-03-18 1954-01-19 United Eng Foundry Co Control system for hydraulic presses
US2636346A (en) * 1948-11-26 1953-04-28 Lake Erie Engineering Corp Pressure accumulator circuit for hydraulic presses
US2641228A (en) * 1950-05-26 1953-06-09 Denison Eng Co Control valve mechanism for hydraulic motors
DE977301C (en) * 1951-09-23 1965-11-11 A Pelissier Nachf Maschf Hydraulic press with a differential piston that forms an annular space on its back with the press cylinder
US2890683A (en) * 1952-02-06 1959-06-16 John S Pilch Fluid actuated control valve means for fluid motors
US2739445A (en) * 1952-09-20 1956-03-27 Lorant Hugo Hydraulic machinery
US2849986A (en) * 1954-09-11 1958-09-02 Klopp Friedrich Hydraulic control mechanism for planing machines
US3200713A (en) * 1961-04-04 1965-08-17 Philips Corp Hydraulic servo-mechanism
US3133472A (en) * 1961-09-05 1964-05-19 Electro Mechanics Inc Impact device control system
US3211424A (en) * 1964-08-19 1965-10-12 Chrysler Corp Control mechanism for adjustable gas turbine nozzle
US3298284A (en) * 1964-09-11 1967-01-17 Rockwell Mfg Co Servo operated reversing tool
US3408897A (en) * 1964-11-18 1968-11-05 Champion Inc Fluid power hammer having accumulator means to drive the hammer through its working stroke independent of the system pump
US3654837A (en) * 1969-12-29 1972-04-11 Abex Corp Hydraulic control systems
US3795177A (en) * 1971-11-04 1974-03-05 Caterpillar Tractor Co Fluid motor control circuit providing selective fast motion
US3981228A (en) * 1973-11-13 1976-09-21 Robert Bosch G.M.B.H. Hydraulic control system
US4397221A (en) * 1981-06-01 1983-08-09 Deere & Company Regenerative valve
US5226363A (en) * 1990-09-11 1993-07-13 The Langston Corporation Dual pressure preload system for maintaining a member
US10670201B1 (en) * 2019-06-19 2020-06-02 5.11, Inc. Headlamp with light source on removable slotted body

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