US2698517A - Automatic means to control and reverse fluid-operated cylinder-and-piston units - Google Patents

Automatic means to control and reverse fluid-operated cylinder-and-piston units Download PDF

Info

Publication number
US2698517A
US2698517A US289042A US28904252A US2698517A US 2698517 A US2698517 A US 2698517A US 289042 A US289042 A US 289042A US 28904252 A US28904252 A US 28904252A US 2698517 A US2698517 A US 2698517A
Authority
US
United States
Prior art keywords
valve
cylinder
piston
pipe
hand
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
US289042A
Inventor
Kenneth F Witt
Original Assignee
Kenneth F Witt
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Kenneth F Witt filed Critical Kenneth F Witt
Priority to US289042A priority Critical patent/US2698517A/en
Application granted granted Critical
Publication of US2698517A publication Critical patent/US2698517A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01LCYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L25/00Drive, or adjustment during the operation, or distribution or expansion valves by non-mechanical means
    • F01L25/02Drive, or adjustment during the operation, or distribution or expansion valves by non-mechanical means by fluid means
    • F01L25/04Drive, or adjustment during the operation, or distribution or expansion valves by non-mechanical means by fluid means by working-fluid of machine or engine, e.g. free-piston machine
    • F01L25/06Arrangements with main and auxiliary valves, at least one of them being fluid-driven
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03CPOSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00Reciprocating-piston liquid engines
    • F03C1/007Reciprocating-piston liquid engines with single cylinder, double-acting piston
    • 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
    • F15B11/16Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • 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
    • F15B2211/605Load sensing circuits
    • F15B2211/6051Load sensing circuits having valve means between output member and the load sensing circuit
    • F15B2211/6055Load sensing circuits having valve means between output member and the load sensing circuit using pressure relief valves
    • 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
    • F15B2211/705Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7051Linear output members
    • F15B2211/7053Double-acting output members
    • 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
    • F15B2211/77Control of direction of movement of the output member
    • F15B2211/7725Control of direction of movement of the output member with automatic reciprocation
    • 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
    • F15B2211/78Control of multiple output members

Description

2,698,51 7 -OPERATED Jan. 4, 1955 K. F. WITT AUTOMATIC MEANS TO CONTROL AND REVERSE FLUID CYLINDER-AND-PISTON UNITS 3 Sheets-Sheet 1 Filed May 21, 1952 Fig.2
INVENTOR. KENNETH F. W |TT. mam/FM ATT'Y.
K. F. WlTT Jan. 4, 1955 2,698,517 OPE.RATED AUTOMATIC MEANS TO CONTROL AND REVERSE FLUID CYLINDER-AND-PISTON UNITS 3 Sheets-Sheet 2 Filed May 21, 1952 QLW. 41% I ATTY K. F. WITT 2,698,517 AUTOMATIC MEANS T0 CONTROL AND REVERSE FLUID-OPERATED Jan. 4, 1955 CYLINDER-AND-PISTON UNITS 3 Sheets-Sheet 3 Y Filed May 21, 1952 JNVENTOR.
KENNETH F. WITT.
ATT'Y.
United States Patent AUTOMATIC MEANS TO CONTROL AND RE- VERSE FLUID-OPERATED CYLINDER-AND- PISTON UNITS Kenneth F. Witt, Winchendon, Mass.
Application May 21, 1952, Serial No. 289,042
1 Claim. (Cl. 60-97) This invention relates to fluid-operated cylinder-andpiston units and to the automatic control and reversal thereof.
It is the general object of the present invention to provide means controlled by the pressure in the active cylinder and effective to reverse the main valve at the completion of a piston stroke in either direction.
I also provide means to control the operation of two cylinder-and-piston units simultaneously, but with the pistons moving in opposite directions. A construction is also shown in which two controlled pistons operate successively and in the same direction.
My invention further relates to arrangements and combinations of parts which will be hereinafter described and more particularly pointed out in the appended claim.
A preferred form of the invention is shown in the drawings, in which Fig. 1 is a sectional plan view of certain fluid-operated mechanism involving my invention;
1Fig. 2 is a sectional elevation of my improved control va ve;
Fig. 3 is a fragmentary sectional elevation showing a slight modification to be described;
Fig. 4 is a plan view, partly in section, of a duplex mechanism, with the fluid-operated pistons moving simultaneously in opposite directions; and
Fig. 5 is a view similar to Fig. 4 but showing a pair of pistons arranged for successive operation in the same direction.
Referring particularly to Figs. 1 and 2, I have shown a power unit comprising a main cylinder C having a piston P slidable therein and connected to a piston rod R by which anv desired moving parts may be actuated. The head end of the cylinder C is connected by a passage and pipe 11 to a main valve V2, and the rod end of the cy inder C is simil rlv nnected by a passage 12 and pipe 14 to the same valve V2.
Fluid under pressure is supplied to the valve V2 through a pipe 15, and the valve V2 is provided with exhaust pass ve 16 and 17. A f ur-part iston or spool 20 is freely slidab e in the valve V2, and the valve is connected at its ends throu h pipes 21 and 22 t special control valves V3 and V4. A start-and-stop or shut-off valve V5 is supplied in the pipe 15, and a valve V6 in a by-pass 24 is provided for a purpose to be described.
The control valve V3 is shown in detail in Fig. 2 and is connected to the passage 10 in the cylinder C by a short pipe 26. The valve V4 is of identical c nstruction and is connected to the passage 12 by a pipe 27.
The valve V3 comprises a piston slidable in a cylinder 31 and normally held in the left-hand-position shown in Fig. 2 by a com ression s ring 32, which is interposed between a shoulder 33 of the piston 30 and a shoulder 34 at the inner end of an adiusting screw 35. The screw 35 is threaded in the cylinder 31 and may be gamed in or out to vary the compression of the spring The screw 35 has an axial recess 36 to loosely receive the piston rod 37, and the recess has a vent 38 to relieve the pressure therein. At its left-hand end, the piston 30 has an axial projection 39 which serves as a stop and ghicl'zt checks the piston 30 in the position shown in With the associated parts in the position shown in Fig. 1. fluid under ressure from the sup ly pipe 15 will flow through the pipe 14 and passage 12 to the righthand or rod end of the cylinder C will move the pis- ICC ton P to the left. The tension of the spring 32 in the valve V4 is sufiicient to prevent the piston 30 in said valve from being moved to the right so long as the piston P is free to move to the left in the cylinder C.
When the piston P reaches its limit of travel, however, as by engagement with the end of the cylinder, the fluid pressure will then build up in the right-hand end of the cylinder C and in the passage 12 and will eventually overcome the spring 32 and force the piston 30 to the right to uncover the pipe 22.
Strong pressure will then be applied through the pipe 22 to the main valve V2 and will shift the piston or spool 20 to its extreme left-hand position, thus reversing the main valve and the supply and exhaust connections of the main cylinder C and causing the main piston P to begin its travel to the right.
When the right-hand limit of travel is reached, pressure will build up in the left-hand end of the cylinder C and the valve V3 will thereupon be opened to supply pressure through the pipe 21 to again reverse the piston 20 and the main valve V2.
The piston P will thus be reciprocated between its defined limits of travel in both directions, and the direction of travel will be automatically reversed at the end of each stroke through the operation of the control valves V3 and V4 and without reliance on reversing dogs or other mechanical or electrical devices.
The only moving control parts are the pistons 30 in the valves V3 and V4, and these movements take place in one direction on the application of relatively heavy pressure through one of the pipes 26 or 27, and take place in the opposite direction as soon as the pressure in the associated pipe 26 or 27 is relieved. The entire operation is extremely reliable and satisfactory.
In Fig. 3, I have shown a needle valve interposed in a small passage 46 connecting the pipe 26a to the cylinder C. This needle valve may be adjusted as desired to control the speed of operation of the piston 30 in the associated valve V3 or V4.
The valve V6 in the bypass 24 may be opened manually to shift the main valve piston 20 to the left at any time and to thus apply pressure in the head end of the cylinder. If the valves V5 and V6 are both closed, all operations cease.
In the duplex construction shown in Fig. 4, two main cylinders C2 and C3 are provided. The cylinder C2 is connected by pipes 50 and 51 to a main valve V7 corresponding in all respects to the main valve V2 shown in Fig. 1. The right-hand or rod end of the cylinder C2 is connected to the main valve through a pressure-re- .sponsive control valve V8 which is identical with the valve V3 shown in Fig. 2. The valve V8 is connected to the cylinder C2 by a pipe 52 and is connected by a pipe 53 to a pipe 54 which connects the adjacent ends of the main valve V7 and a second main valve V9.
The cylinder C3 is connected by pipes and 61 to said main valve V9, which valve is of the same construction as the main valve V7 (Fig. 4) and the main valve V2 (Fig. 1). Fluid under pressure is supplied through a main supply pipe 63 and branch pipes 64 and 65.
A by-pass pipe 66 is connected into the left-hand end of the main valve V7 and is also connected through a cross pipe 67 to a pipe 68 which extends from a control valve V10 for the cylinder C3 to the right-hand end of the main valve V9.
the pipe 63 between the by-pass pipe 66 and the branch pipes 64 and 65.
In this duplex machine, the pistons 68 and 69 in the cylinders C2 and C3 are operated simultaneously but in opposite directions. Consequently, the piston of either cylinder may perform a working stroke while the piston of the opposite cylinder is performing a return stroke.
By momentarily opening the by-pass valve V11, the main valves V7 and V9 may be placed in the positions shown in Fig. 4. If the valve V12 is then opened, fluid under pressure will flow to the right-hand end of the cylinder C2 and to the left-hand end of the cylinder C3.
The piston 68 will then move to the left and the piston 69 to the right until the pistons reach the ends of their Fatented Jan. 4, 1955 respective strokes, whereupon pressures will be built up in the control valve V8, and the slidable pistons in the main valves V7 and V9 will be shifted to the left and to the right respectively, to reverse the operating connections of the main cylinders C2 and C3.
It will be noted that the cross pipe 54 connects the adjacent ends of the valves V7 and V9, while the cross pipe 67 similarly connects the outside ends. Consequently, when the piston 68 completes its stroke to the left and pressure builds up in the right-hand end of the cylinder C2, the control valve V8 will operate to admit pressure to the pipes 53 and 54 and to thus shift the piston in the valve V7 to the left and the piston in the valve V9 to the right. The piston 68 will then begin a movement to the right and the piston 69 to the left, which movement will continue until pressure is built up in the right-hand end of the cylinder C3.
The valve V10 will then admit pressure to the pipes 68 and 67, thus again reversing the main valves V7 and V9, whereupon the described cycle of operations will start over.
The valve V11 may be manually opened at any time to place the main valves V7 and V9 in the positions shown, and the valve V12 may be closed at any time to stop all further operations of the duplex machine.
In the duplex construction shown in Fig. 5, two main cylinders C and C6 are provided. The cylinder C5 is connected by pipes 70 and 71 to a main valve V14 corresponding in all respects to the main valve V2 shown in Fig. 1. The cylinder C6 is similarly connected by pipes 72 and 73 to a main valve V15. Pressure-responsive valves V20 to V23 are provided at the opposite ends of the cylinders C5 and C6 as shown.
The valve V20 at the closed end of the cylinder C5 is connected by a pipe 80 to the right-hand end of the main valve V15. The valve V21 at the rod end of the cylinder C5 is connected by a pipe 81 to the left-hand end of the main valve V15. The valve V22 at the lefthand or closed end of the cylinder C6 is connected by a pipe 82 to the left-hand end of the main valve V14, and the valve V23 at the right-hand or rod end of the cylinder C6 is connected by a pipe 83 to the right-hand end of the main valve V14.
Fluid under pressure is furnished through a supply pipe 85 and branch pipes 86 and 87 to the intakes 88 .and 89 for the main valves V14 and V15 respectively.
The usual exhaust connections 90 are also provided for the valves V14 and V15. A shut-off valve V25 is provided in the supply pipe 85, and a setting valve V26 is provided in the pipe 70.
Assuming that the parts are in the position shown in Fig. 5, the operation is as follows:
Fluid under pressure will be supplied through the supply pipe 85, branch pipe 86, intake 88 and pipe 70 to the left-hand or closed end of the cylinder C5, thus forcing the piston P to the right. When the piston has completed its right-hand stroke, pressure will be built up in the left-hand or closed end of the cylinder C5, which pressure will eventually overcome the valve V20 and will admit fluid under pressure through pipe 80 to the right-hand end of the main valve V15.
This will move the valve piston to the left and will admit fluid under pressure through the branch pipe 87, intake 89 and pipe 72 to the left-hand or closed end of the cylinder C6, thus moving'the piston P2 to the right.
After this stroke is completed, pressure is built up to open the valve V22 and admit fluid under pressure through the pipe 82 to the left-hand end of the valve V14, thus forcing the valve piston to the right and admitting fluid under pressure through the pipe 71 to the right-hand or rod end of the cylinder C5 and thereupon shifting the piston P to the left.
When this stroke is completed, pressure will be built up in the rod end of the cylinder C5 to overcome the valve V21 and admit fluid under pressure through the pipe 81 to the left-hand end of the valve V15, thus moving the valve piston to the right and admitting fluid under pressure through the pipe 73 to the right-hand end of the cylinder C6, with resultant movement of the piston P2 to the left.
When this movement is completed, pressure will be built up to open the valve V23 and admit fluid under pressure through the pipe 83 to the right-hand end of the main valve V14, thus returning the valve piston to its original position. Both pistons P and P2 are then in their original or extreme left-hand positions, and the described cycle of operations will thereupon be repeated.
The setting valve V26 may be closed as soon as the piston P2 in the cylinder C6 completes its stroke to the left, thus holding both pistons P and P2 in their extreme left-hand or loading position for as long a period as may be desired. All operations may be stopped at any time by closing the shut-off valve V25.
I have thus provided improved automatic mechanism for controlling the movement and reversal of one or more cylinder-and-piston units entirely by cylinder pressures and without the use of dogs or other mechanical or electrical devices.
Having thus described my invention and the advantages thereof, I do not wish to be limited to the details herein disclosed, otherwise than as set forth in the claim, but what I claim is:
In a fluid-operated mechanism, two cylinder-and-piston power units, a main valve for each power unit and having a cylinder with a reversing piston slidable therein, a pressure-responsive control valve for each end of each power-unit cylinder, and direct connections from each control valve of each power unit to one end of the main valve for the other power unit, whereby a substantial rise in pressure in either power-unit cylinder will act directly on the main valve for the other power-unit cylinder and will thereby shift said main valve and reverse said other power unit.
References Cited in the file of this patent UNITED STATES PATENTS 1,938,758 Ernst Dec. 12, 1933 1,952,690 Strom, Sr. Mar. 27, 1934 2,223,792 Muir Dec. 3, 1940 2,287,709 Ringman June 23, 1942 2,342,450 Campbell Feb. 22, 1944 2,617,257 Douglas Nov. 11, 1952
US289042A 1952-05-21 1952-05-21 Automatic means to control and reverse fluid-operated cylinder-and-piston units Expired - Lifetime US2698517A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
US289042A US2698517A (en) 1952-05-21 1952-05-21 Automatic means to control and reverse fluid-operated cylinder-and-piston units

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US289042A US2698517A (en) 1952-05-21 1952-05-21 Automatic means to control and reverse fluid-operated cylinder-and-piston units

Publications (1)

Publication Number Publication Date
US2698517A true US2698517A (en) 1955-01-04

Family

ID=23109778

Family Applications (1)

Application Number Title Priority Date Filing Date
US289042A Expired - Lifetime US2698517A (en) 1952-05-21 1952-05-21 Automatic means to control and reverse fluid-operated cylinder-and-piston units

Country Status (1)

Country Link
US (1) US2698517A (en)

Cited By (42)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2725918A (en) * 1955-01-11 1955-12-06 Ingersoll Rand Co Tube rolling device
US2812055A (en) * 1954-09-30 1957-11-05 Harvey M Wenger Barn cleaning apparatus
US2847978A (en) * 1955-02-09 1958-08-19 Gen Motors Corp Windshield wiper actuating mechanism
US2858744A (en) * 1955-10-14 1958-11-04 Colonial Broach & Machine Comp Automatic broach handling mechanism
US2864342A (en) * 1955-08-29 1958-12-16 Lynn J Ziegelmeyer Hydraulically operated motor and control means therefor
US2935050A (en) * 1957-03-25 1960-05-03 Curtiss Wright Corp Hydraulic actuator systems for reciprocating fluid operated motors
US2944530A (en) * 1959-04-29 1960-07-12 Alfred C Johnson Pneumatic control means for reciprocable pistons
US2965077A (en) * 1958-09-29 1960-12-20 Shell Oil Co Prime mover comprising two hydraulic single-cylinder piston engines
US2970579A (en) * 1959-11-23 1961-02-07 Tomlon Corp Hydraulic reversing control
US2972338A (en) * 1956-12-14 1961-02-21 Westinghouse Electric Corp Pressure derivative feedback valve
US2987886A (en) * 1958-09-02 1961-06-13 Union Oil Co Apparatus for valve sequence operation
US3018630A (en) * 1960-02-25 1962-01-30 City Tank Corp Automatic valve
US3019773A (en) * 1959-10-08 1962-02-06 Grover Smith Mfg Corp Fluid motor
US3035548A (en) * 1959-11-24 1962-05-22 Ingbuero Dipl Ing Friedrich He Hydraulically operated percussion devices
US3071116A (en) * 1959-12-14 1963-01-01 Martonair Ltd Pneumatic hammer
US3084359A (en) * 1956-12-13 1963-04-09 Grip Nut Co Machine for indenting nut sides to produce locking portions therein
US3092269A (en) * 1959-04-28 1963-06-04 City Tank Corp Packer assembly
US3094842A (en) * 1961-04-21 1963-06-25 Rufus B Johnston Hydraulic pumping system
US3095906A (en) * 1959-03-05 1963-07-02 Moog Servocontrols Inc Flow control servo valve with dynamic load pressure feedback
US3150549A (en) * 1959-11-09 1964-09-29 Jack N Binns Hydraulic control system for contour rool-turning lathe
US3216201A (en) * 1959-10-12 1965-11-09 Coal Industry Patents Ltd Mine roof supports
US3225663A (en) * 1963-04-09 1965-12-28 Hispano Suiza Sa Hydraulic control systems including double action receiver apparatus
US3228199A (en) * 1962-05-30 1966-01-11 Dowty Mining Equipment Ltd Mining apparatus
US3257012A (en) * 1961-07-13 1966-06-21 Berolzheimer Henry Refuse collection loading and packing mechanism
US3292498A (en) * 1965-01-08 1966-12-20 Raymond S Zimmerman Fluid motor including reciprocating fluid responsive valves
US3358563A (en) * 1965-07-09 1967-12-19 Scovill Manufacturing Co Air cylinder cycling apparatus
US3530681A (en) * 1968-08-05 1970-09-29 Hughes Aircraft Co Hydraulically driven cryogenic refrigerator
US3707881A (en) * 1970-03-12 1973-01-02 Uhde Gmbh Friedrich Control system for hydraulic fluid-feed mechanism
US3771421A (en) * 1970-04-01 1973-11-13 Krueger Gmbh H Thrust piston motors
US3896701A (en) * 1973-09-17 1975-07-29 Cleveland Vibrator Co Impactor-vibrator
US4002103A (en) * 1974-07-01 1977-01-11 The West Company Reciprocating apparatus with a controllable dwell time at each end of the stroke
US4082032A (en) * 1974-11-13 1978-04-04 Raymond International, Inc. Control of hydraulically powered equipment
US4096875A (en) * 1975-03-07 1978-06-27 Pneupac Limited Pressure fluid-actuated oscillator
US4114515A (en) * 1975-07-30 1978-09-19 Pauliukonis Richard S Adjustable self-reciprocating operator
US4121499A (en) * 1976-01-29 1978-10-24 The Secretary Of State For Industry In Her Britannic Majesty's Government Of The United Kingdom Of Great Britain And Northern Ireland Switching mechanism
US4213298A (en) * 1978-07-03 1980-07-22 Offshore Devices, Inc. Self-reversing hydraulic control system and self-reversing pump incorporating such system
US4580590A (en) * 1984-09-13 1986-04-08 Isi Fluid Power, Inc. Automatic air valve assembly
US4638886A (en) * 1985-10-21 1987-01-27 Sta-Rite Industries, Inc. Apparatus for disabling an obstructed lift mechanism
US4821622A (en) * 1986-12-22 1989-04-18 Deere & Company Extension and retraction sequencing circuit
US4953579A (en) * 1987-02-20 1990-09-04 Phillips Robert E Quick acting diversion valves
US20050183770A1 (en) * 2004-02-19 2005-08-25 Robert Metzinger Linear fluid drive system with detent
CN102747970A (en) * 2012-07-17 2012-10-24 宝鸡石油机械有限责任公司 Automatic control system of filling valve of marine drilling riser

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1938758A (en) * 1929-05-13 1933-12-12 Cincinnati Grinders Inc Spindle oscillator
US1952690A (en) * 1931-10-03 1934-03-27 Racine Stoker Mfg Company Automatic reverse valve for stokers
US2223792A (en) * 1938-04-12 1940-12-03 Dominion Eng Works Ltd Hydraulic apparatus for operating machine tools and the like
US2287709A (en) * 1940-01-30 1942-06-23 Nat Supply Co Hydraulic well pumping mechanism
US2342450A (en) * 1941-12-12 1944-02-22 John Eley Jr Selector valve with automatic return
US2617257A (en) * 1948-12-10 1952-11-11 Oilgear Co Control valve and operating means therefor

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1938758A (en) * 1929-05-13 1933-12-12 Cincinnati Grinders Inc Spindle oscillator
US1952690A (en) * 1931-10-03 1934-03-27 Racine Stoker Mfg Company Automatic reverse valve for stokers
US2223792A (en) * 1938-04-12 1940-12-03 Dominion Eng Works Ltd Hydraulic apparatus for operating machine tools and the like
US2287709A (en) * 1940-01-30 1942-06-23 Nat Supply Co Hydraulic well pumping mechanism
US2342450A (en) * 1941-12-12 1944-02-22 John Eley Jr Selector valve with automatic return
US2617257A (en) * 1948-12-10 1952-11-11 Oilgear Co Control valve and operating means therefor

Cited By (43)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2812055A (en) * 1954-09-30 1957-11-05 Harvey M Wenger Barn cleaning apparatus
US2725918A (en) * 1955-01-11 1955-12-06 Ingersoll Rand Co Tube rolling device
US2847978A (en) * 1955-02-09 1958-08-19 Gen Motors Corp Windshield wiper actuating mechanism
US2864342A (en) * 1955-08-29 1958-12-16 Lynn J Ziegelmeyer Hydraulically operated motor and control means therefor
US2858744A (en) * 1955-10-14 1958-11-04 Colonial Broach & Machine Comp Automatic broach handling mechanism
US3084359A (en) * 1956-12-13 1963-04-09 Grip Nut Co Machine for indenting nut sides to produce locking portions therein
US2972338A (en) * 1956-12-14 1961-02-21 Westinghouse Electric Corp Pressure derivative feedback valve
US2935050A (en) * 1957-03-25 1960-05-03 Curtiss Wright Corp Hydraulic actuator systems for reciprocating fluid operated motors
US2987886A (en) * 1958-09-02 1961-06-13 Union Oil Co Apparatus for valve sequence operation
US2965077A (en) * 1958-09-29 1960-12-20 Shell Oil Co Prime mover comprising two hydraulic single-cylinder piston engines
US3095906A (en) * 1959-03-05 1963-07-02 Moog Servocontrols Inc Flow control servo valve with dynamic load pressure feedback
US3092269A (en) * 1959-04-28 1963-06-04 City Tank Corp Packer assembly
US2944530A (en) * 1959-04-29 1960-07-12 Alfred C Johnson Pneumatic control means for reciprocable pistons
US3019773A (en) * 1959-10-08 1962-02-06 Grover Smith Mfg Corp Fluid motor
US3216201A (en) * 1959-10-12 1965-11-09 Coal Industry Patents Ltd Mine roof supports
US3150549A (en) * 1959-11-09 1964-09-29 Jack N Binns Hydraulic control system for contour rool-turning lathe
US2970579A (en) * 1959-11-23 1961-02-07 Tomlon Corp Hydraulic reversing control
US3035548A (en) * 1959-11-24 1962-05-22 Ingbuero Dipl Ing Friedrich He Hydraulically operated percussion devices
US3071116A (en) * 1959-12-14 1963-01-01 Martonair Ltd Pneumatic hammer
US3018630A (en) * 1960-02-25 1962-01-30 City Tank Corp Automatic valve
US3094842A (en) * 1961-04-21 1963-06-25 Rufus B Johnston Hydraulic pumping system
US3257012A (en) * 1961-07-13 1966-06-21 Berolzheimer Henry Refuse collection loading and packing mechanism
US3228199A (en) * 1962-05-30 1966-01-11 Dowty Mining Equipment Ltd Mining apparatus
US3225663A (en) * 1963-04-09 1965-12-28 Hispano Suiza Sa Hydraulic control systems including double action receiver apparatus
US3292498A (en) * 1965-01-08 1966-12-20 Raymond S Zimmerman Fluid motor including reciprocating fluid responsive valves
US3358563A (en) * 1965-07-09 1967-12-19 Scovill Manufacturing Co Air cylinder cycling apparatus
US3530681A (en) * 1968-08-05 1970-09-29 Hughes Aircraft Co Hydraulically driven cryogenic refrigerator
US3707881A (en) * 1970-03-12 1973-01-02 Uhde Gmbh Friedrich Control system for hydraulic fluid-feed mechanism
US3771421A (en) * 1970-04-01 1973-11-13 Krueger Gmbh H Thrust piston motors
US3896701A (en) * 1973-09-17 1975-07-29 Cleveland Vibrator Co Impactor-vibrator
US4002103A (en) * 1974-07-01 1977-01-11 The West Company Reciprocating apparatus with a controllable dwell time at each end of the stroke
US4082032A (en) * 1974-11-13 1978-04-04 Raymond International, Inc. Control of hydraulically powered equipment
US4096875A (en) * 1975-03-07 1978-06-27 Pneupac Limited Pressure fluid-actuated oscillator
US4114515A (en) * 1975-07-30 1978-09-19 Pauliukonis Richard S Adjustable self-reciprocating operator
US4121499A (en) * 1976-01-29 1978-10-24 The Secretary Of State For Industry In Her Britannic Majesty's Government Of The United Kingdom Of Great Britain And Northern Ireland Switching mechanism
US4213298A (en) * 1978-07-03 1980-07-22 Offshore Devices, Inc. Self-reversing hydraulic control system and self-reversing pump incorporating such system
US4580590A (en) * 1984-09-13 1986-04-08 Isi Fluid Power, Inc. Automatic air valve assembly
US4638886A (en) * 1985-10-21 1987-01-27 Sta-Rite Industries, Inc. Apparatus for disabling an obstructed lift mechanism
US4821622A (en) * 1986-12-22 1989-04-18 Deere & Company Extension and retraction sequencing circuit
US4953579A (en) * 1987-02-20 1990-09-04 Phillips Robert E Quick acting diversion valves
US20050183770A1 (en) * 2004-02-19 2005-08-25 Robert Metzinger Linear fluid drive system with detent
CN102747970B (en) * 2012-07-17 2015-01-21 宝鸡石油机械有限责任公司 Automatic control system of filling valve of marine drilling riser
CN102747970A (en) * 2012-07-17 2012-10-24 宝鸡石油机械有限责任公司 Automatic control system of filling valve of marine drilling riser

Similar Documents

Publication Publication Date Title
US2618121A (en) Locking control circuit for fluid-actuated motors
KR20160140669A (en) Gearbox control system
US2648346A (en) Locking valve for hydraulic motors
US2261444A (en) Follow-up valve
US2276895A (en) Hydraulic transmission means
US3769881A (en) Hydraulic device
US2803110A (en) Hydraulic power drive for reciprocating members
US2513083A (en) Wobbler drive mechanism
US2550723A (en) Reversing valve mechanism
US9689407B2 (en) Hydraulic drive with rapid stroke and load stroke
GB1068863A (en) Improvements in or relating to reciprocating pumps
US3792643A (en) Fluid system
US3407601A (en) Air-hydraulic system and apparatus
US2826149A (en) Booster pump
US2432305A (en) Hydraulic operating circuit for machine tools and the like
US2771907A (en) Pilot controlled piston type reversing valve
US1927583A (en) Hydraulic motor control means
EP1357298A3 (en) Actuation valve for a double-acting pneumatic cylinder and use of such a valve for a pneumatic-cylinder actuated creel
US2443333A (en) Rotary valve actuating device
US2233521A (en) Double-acting check valve device
US2804883A (en) Open-center follow-up control valve
US4790728A (en) Dual-rigid-hollow-stem actuators in opposite-phase slurry pump drive having variable pumping speed and force
US2467509A (en) Hydraulic system
US20170108014A1 (en) Hydraulic system
US3476266A (en) Binary-code controlled apparatus