US3908515A - Hydraulic circuit with selectively actuatable float control - Google Patents
Hydraulic circuit with selectively actuatable float control Download PDFInfo
- Publication number
- US3908515A US3908515A US395647A US39564773A US3908515A US 3908515 A US3908515 A US 3908515A US 395647 A US395647 A US 395647A US 39564773 A US39564773 A US 39564773A US 3908515 A US3908515 A US 3908515A
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- Prior art keywords
- motor
- valve
- control valve
- fluid
- valve means
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- 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
- F15B13/01—Locking-valves or other detent i.e. load-holding devices
Definitions
- the present invention relates to hydraulic circuits and pertains particularly to a circuit having a lock valve selectively actuatablc to provide a floating-condition for a hydraulicjack.
- FIG. 1 is a schematic layout of a Circuit in accordance with the present invention.
- FIG. 2 is a schematic of a modification of an auxiliary valve for the circuit of FIG. 1.
- a hydraulic circuit in accordance with the present invention generally comprises a source of pressurized fluid including a pump 11 which draws fluid from a sump or reservoir 12.
- the pump supplies pressurized fluid by way of a supply conduit 13 to a main control valve 14 with fluid exhausted from the control valve being returned to the reservoir through a return line or conduit 15.
- a relief valve 16 interconnects the supply conduit 13 and the return conduit to relieve excessive pressure in the hydraulic circuit.
- the control valve 14 is of the type that has three positions attainable by actuation of a control lever 17 to one of the three positions indicated by the letters R, N, and L.
- the control valve is operative in selecting one of the R or L positions to direct fluid via supply lines 21 and 22 to either the head or rod end of a double act- ,ing..hydr aulic motor orjac k 23.
- both of a pair of control eonduits 18 and 19 are in communication with the return conduit 15 to: reservoir 12.
- the conduits l8 and 19 communicate fluid'from the control valve 14 to a pilot operable lock valve 20, where the fluid is communicated by way of motor supply lines 21 and 22 to jack 23.
- the hydraulic jac k 23 is controlled by the lock valve through conduits 21 and 22.
- the lock valve 20 includes a valve body'24 having a bore 2 5-extending longitudinally therethrough.
- a first pair of axially'spa ced radial ports 26 and 27 are formed in. the body and. communicate the conduits l8 and 19, respectively, with the bore 25.
- a second pair of axially spaced radial ports 28 and 29 are formed in the body and communicate the conduits 21 and 22, respectively, with the bore.
- the valve body has a third radial port 30 formed therein intermediate the ports 26 and 27.
- a pair of solenoid control valves 48 and 4) are in communicationwith the port 30 and Chamber 45v of the valve body through a conduit 50.
- the valve 48 is normally open and in communication with reservoir 12 through a return conduit 51.
- the solenoid valve 49 is normally closed and communicates with the lluid supply conduit 13 through a branch or by-pass conduit 52.
- a suitable conductor 53 electically connects the solenoid valves to a normally open toggle switch 54 which is connected to a suitable electrical source such as a battery 55.
- the solenoid operated valves 48 and 49 of FIG. 1 may be replaced with a single 2-position, 3-way solenoid control valve 56 which normally communicates the conduit 50 with the return conduit 51. (losing the toggle switch 54 energizes the solenoid control valve causing it to shift to a position to communicate the branch conduit 52 with the conduit 50. This communicates pressufrized fluid to chamber 45 which forces pistons 41 and 42 to unseat ball check valves 35 and 36 to thereby disable the lock valve 20. i
- the toggle switch 54 is open so that the chamber 45 is vented to the reservoir 12 through the conduit 50, the normally open solenoid valve 48, and the return conduit 51.
- the lock valve 20 functions as a Conventional lock valve whereby fluid from both ends of the hydrostatic jack 23 is blocked by the respective check valve assemblies 31 and 32 of the lock valve.
- the control valve 14 is shifted to direct pressurized fluid through conduit 18 to the lock valve, the ball 35 of the check valve assembly 31 is unseated by the pressurized fluid which is then transmitted to the hydraulic jack through conduit 21. Simultaneously, the pressurized fluid entering the lock valve through the conduit 18 acts upon the actuator piston 41 shifting it and the actuator piston 42 to the right.
- the toggle switch 54 is closed to direct electrical energy to the solenoid control valves 48 and 49.
- the valve 48 is shifted to a closed position blocking communication therethrough while valve 49 is shifted to an open position to direct pressurized fluid from the pump 11 through conduits 13, 52 and 50 into the chamber 45 of the lock valve 20.
- the pressurized fluid in chamber 45 urges the actuator pistons 41 and 42 in opposite directions to unseat the balls 35 and 36 of both check valve assemblies 31 and 32. This communicates both the head end and the rod end of the hydraulic jack 23 with the reservoir 12 through the various conduits and provides the float condition.
- a linear double-acting hydraulic motor connected to a work member, a source of fluid pressure including a sump and a pump for supplying fluid for operating said motor, a three position directional control valve in a valve housing and having a neutral position, and raise and lower positions for selectively directing fluid from said source to either end of said motor for operation of said motor for positioning said work member, a single control lever for operating said control valve, lock valve means including first and second passage means communicating said fluid respectively with alternate ends of said motor, check valve means disposed in each said passage means to normally block flow of said fluid from said motor and including pressure-responsive piston and plunger means in each said passage means for unseating said check valve means to provide communication between both ends of said motor and sump by way of said directional control valve, said check valve means disposed between said control valve means and said hydraulic motor for normally locking said motor in a selected position; solenoid operated auxiliary valve means separate spaced from and independent of said directional control valve and valve housing disposed between said source of fluid pressure and said lock valve means for bypassing said directional
- control means for said solenoid operated auxiliary valve means comprising a source of electrical power and switch means for selectively activating said solenoids.
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
A hydraulic system having the combination of a source of pressurized fluid, a linear hydraulic motor, a main control valve to selectively direct hydraulic fluid to the motor, and a lock valve disposed between the control valve and motor is provided with an auxiliary valve to by-pass the main control valve to disable the lock valve to provide a float condition for the motor.
Description
United States Patent Johnson 1 Sept. 30, 1975 [54] HYDRAULIC CIRCUIT WITH 3.274.902 9/1966 Klcckncr 91/420 SELECTIVELY ACTUATABLE FLOAT 3.381.587 5/1968 Parquet 91/420 CONTROL 3.543.647 12/1970 -Hall et a1. 91/420 3.558 102 1/1971 Cruse 91/447 X [75] Inventor: Howard L. Johnson, Jolict. 111. 3.583.438 6/1971 Ru hs 37/596 3.608.431 9/1971 Pczlse 91/454 X 1 Asslgneel CaterPIllar Tractor y. 3,730207 5 1973 Christensen 91 437 x Peoria, 111.
[22] Filed: Sept 10, 1973 Primary E.\aminerlrwin C. Cohen Attorney, Agent, 0" Firm-Phillips Moore, PP 395.647 Wcissenberger Lempio & Strabala 52 us. Cl. 91/420; 91/437; 91/445; 1 ABSTRACT 91/447; 91/453; 91/464 A hydraulic system having the combination of a [51 1 Int. Cl.'- F1513 11/08; F1513 13/042; source of pressurized fluid, a linear hydraulic motor, a FlSB 13/043 main control valve to selectively direct hydraulic fluid [58] Field of Search 91/420, 445, 437, 447, to the motor, and a lock valve disposed between the.
91/453, 464; 137/596.l2, 596.13 control valve and motor is provided with an auxiliary valve to by-pass the main control valve to disable the [56] References Cited lock valve to provide a float condition for the motor.
UNITED STATES PATENTS 2.517.164 8/1950 Arps 91/420 X' 3 Claims, 2 Drawing Figures f -1T1 'E' IIIJ -25 L .LL
Z4- Z0 +5 Z5 3 0 3 1 28 1'2 BACKGROUND OF THE INVENTION The present invention relates to hydraulic circuits and pertains particularly to a circuit having a lock valve selectively actuatablc to provide a floating-condition for a hydraulicjack.
It is common practice to utilize anearthmoving vehi cle for ancillary operations. by attaching an auxiliary implement thereto. For example, motor graders are'frequently employed for snow removal by attaching a snow plow to the forward end thereof. In many cases, the auxiliary implement, suchtas the snow plow, operates more efficiently if it is free to ride or float on the surface so it can follow the surface contour. However, many of the hydraulic control systems of such vehicles employ a lock valve which would prevent free floating of the blade. Thus, one of the difficulties encountered in using a vehicle for ancillary operations is that of providing an attachment type control circuit which provides a float position-without employing a sophisticated and expensive control valve, and which is compatible with. the basic hydraulic circuit of the vehicle.
SUMMARY OF THE INVENTION A BRIEF-DESCRIPTION OF THE DRAWINGS Other objects and advantages of the present invention will become apparent from the following description when read in conjunction with the accompanying drawings wherein:
FIG. 1 is a schematic layout of a Circuit in accordance with the present invention; and
FIG. 2 is a schematic of a modification of an auxiliary valve for the circuit of FIG. 1.
DETAILED DESCRIPTION OF PREFERRED EMBODIMENTS Referring more particularly to FIG. 1 of the drawing, a hydraulic circuit in accordance with the present invention generally comprises a source of pressurized fluid including a pump 11 which draws fluid from a sump or reservoir 12. The pump supplies pressurized fluid by way of a supply conduit 13 to a main control valve 14 with fluid exhausted from the control valve being returned to the reservoir through a return line or conduit 15. A relief valve 16 interconnects the supply conduit 13 and the return conduit to relieve excessive pressure in the hydraulic circuit.
The control valve 14 is of the type that has three positions attainable by actuation of a control lever 17 to one of the three positions indicated by the letters R, N, and L. The control valve is operative in selecting one of the R or L positions to direct fluid via supply lines 21 and 22 to either the head or rod end of a double act- ,ing..hydr aulic motor orjac k 23. when the control valve is in theneutral position, both of a pair of control eonduits 18 and 19 are in communication with the return conduit 15 to: reservoir 12. The conduits l8 and 19 communicate fluid'from the control valve 14 to a pilot operable lock valve 20, where the fluid is communicated by way of motor supply lines 21 and 22 to jack 23. The hydraulic jac k 23is controlled by the lock valve through conduits 21 and 22.
The lock valve 20 includes a valve body'24 having a bore 2 5-extending longitudinally therethrough. A first pair of axially'spa ced radial ports 26 and 27 are formed in. the body and. communicate the conduits l8 and 19, respectively, with the bore 25. A second pair of axially spaced radial ports 28 and 29 are formed in the body and communicate the conduits 21 and 22, respectively, with the bore. The valve body has a third radial port 30 formed therein intermediate the ports 26 and 27.
' A pair of identical check valve assemblies 31 and 32 are individually disposed in opposite ends of the bore and secured in place by a respective one of a pair of plugs 33 and 34 individually threadably secured in the open end of the bore. Check valve assembly 31 normally blocks port 2 8 from port 26 while check valve assembly 32 normally blocks port 29 from port 27. Each check valve assembly includes a ball 35 and 36 resiliently urged against a seat 37 and 38 by a compression .check valve assembly.
A pair of solenoid control valves 48 and 4) are in communicationwith the port 30 and Chamber 45v of the valve body through a conduit 50. The valve 48 is normally open and in communication with reservoir 12 through a return conduit 51. The solenoid valve 49 is normally closed and communicates with the lluid supply conduit 13 through a branch or by-pass conduit 52. A suitable conductor 53 electically connects the solenoid valves to a normally open toggle switch 54 which is connected to a suitable electrical source such as a battery 55.
In an alternate embodiment as shown in FIG. 2, the solenoid operated valves 48 and 49 of FIG. 1 may be replaced with a single 2-position, 3-way solenoid control valve 56 which normally communicates the conduit 50 with the return conduit 51. (losing the toggle switch 54 energizes the solenoid control valve causing it to shift to a position to communicate the branch conduit 52 with the conduit 50. This communicates pressufrized fluid to chamber 45 which forces pistons 41 and 42 to unseat ball check valves 35 and 36 to thereby disable the lock valve 20. i
OPERATION During normal vehicular operation, the toggle switch 54 is open so that the chamber 45 is vented to the reservoir 12 through the conduit 50, the normally open solenoid valve 48, and the return conduit 51. With ehanv ber 45 vented, the lock valve 20 functions as a Conventional lock valve whereby fluid from both ends of the hydrostatic jack 23 is blocked by the respective check valve assemblies 31 and 32 of the lock valve. When the control valve 14 is shifted to direct pressurized fluid through conduit 18 to the lock valve, the ball 35 of the check valve assembly 31 is unseated by the pressurized fluid which is then transmitted to the hydraulic jack through conduit 21. Simultaneously, the pressurized fluid entering the lock valve through the conduit 18 acts upon the actuator piston 41 shifting it and the actuator piston 42 to the right. The plunger 47 of the piston 42 engages and unseats the ball 36 of the check valve assembly 32 permitting fluid exhausted from the hydraulic jack through the conduit 22 to be exhausted through conduit 19, the control valve 14 and the return conduit to the reservoir 12. Conversely, pressurized fluid directed through conduit 19 passes through the lock valve in a similar manner and to the head end of the hydraulic jack through conduit 22. The fluid exhausted through conduit 21 passes through the lock valve 20, conduit 18, control valve 14, and return conduit 15 to the reservoir. 1
To obtain a float position of the hydraulic jack 23, the toggle switch 54 is closed to direct electrical energy to the solenoid control valves 48 and 49. Simultaneously, the valve 48 is shifted to a closed position blocking communication therethrough while valve 49 is shifted to an open position to direct pressurized fluid from the pump 11 through conduits 13, 52 and 50 into the chamber 45 of the lock valve 20. The pressurized fluid in chamber 45 urges the actuator pistons 41 and 42 in opposite directions to unseat the balls 35 and 36 of both check valve assemblies 31 and 32. This communicates both the head end and the rod end of the hydraulic jack 23 with the reservoir 12 through the various conduits and provides the float condition.
What is claimed is:
1. In a hydraulic system for selectively positioning a work member in selected fixed positions the combination comprising:
a linear double-acting hydraulic motor connected to a work member, a source of fluid pressure including a sump and a pump for supplying fluid for operating said motor, a three position directional control valve in a valve housing and having a neutral position, and raise and lower positions for selectively directing fluid from said source to either end of said motor for operation of said motor for positioning said work member, a single control lever for operating said control valve, lock valve means including first and second passage means communicating said fluid respectively with alternate ends of said motor, check valve means disposed in each said passage means to normally block flow of said fluid from said motor and including pressure-responsive piston and plunger means in each said passage means for unseating said check valve means to provide communication between both ends of said motor and sump by way of said directional control valve, said check valve means disposed between said control valve means and said hydraulic motor for normally locking said motor in a selected position; solenoid operated auxiliary valve means separate spaced from and independent of said directional control valve and valve housing disposed between said source of fluid pressure and said lock valve means for bypassing said directional control valve for directing fluid solely to each said piston and plunger means solely for unseating each said check valve means for communicating both ends of said motor with said sump by way of said directional control valve for enabling free floating movement of said hydraulic motor when said main control valve is in a neutral position between said raise and said lower positions. 2. The hydraulic system of claim 1 wherein said solenoid operated auxiliary valve means comprises a pair of solenoid operated two-position valves.
3. The hydraulic system of claim 2 including control means for said solenoid operated auxiliary valve means comprising a source of electrical power and switch means for selectively activating said solenoids.
Claims (3)
1. In a hydraulic system for selectively positioning a work member in selected fixed positions the combination comprising: a linear double-acting hydraulic motor connected to a work member, a source of fluid pressure including a sump and a pump for supplying fluid for operating said motor, a three position directional control valve in a valve housing and having a neutral position, and raise and lower positions for selectively directing fluid from said source to either end of said motor for operation of said motor for positioning said work member, a single control lever for operating said control valve, lock valve means including first and second passage means communicating said fluid respectively with alternate ends of said motor, check valve means disposed in each said passage means to normally block flow of said fluid from said motor and including pressure-responsive piston and plunger means in each said passage means for unseating said check valve means to provide communication between both ends of said motor and sump by way of said directional control valve, said check valve means disposed between said control valve means and said hydraulic motor for normally locking said motor in a selected position; solenoid operated auxiliary valve means separate spaced from and independent of said directional control valve and valve housing disposed between said source of fluid pressure and said lock valve means for bypassing said directional control valve for directing fluid solely to each said piston and plunger means solely for unseating each said check valve means for communicating both ends of said motor with said sump by way of said directional control valve for enabling free floating movement of said hydraulic motor when said main control valve is in a neutral position between said raise and said lower positions.
2. The hydraulic system of claim 1 wherein said solenoid operated auxiliary valve means comprises a pair of solenoid operated two-position valves.
3. The hydraulic system of claim 2 including control means for said solenoid operated auxiliary valve means comprising a source of electrical power and switch means for selectively activating said solenoids.
Priority Applications (8)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US395647A US3908515A (en) | 1973-09-10 | 1973-09-10 | Hydraulic circuit with selectively actuatable float control |
JP2728974A JPS5535563B2 (en) | 1973-09-10 | 1974-03-11 | |
CA204,191A CA1025326A (en) | 1973-09-10 | 1974-07-05 | Hydraulic circuit with selectively actuatable float control |
ZA00744408A ZA744408B (en) | 1973-09-10 | 1974-07-09 | Hydraulic circuit with selectively actuatable float control |
AU71750/74A AU482064B2 (en) | 1973-09-10 | 1974-07-29 | Hydraulic circuit with selectively actuatable float control |
BR6750/74A BR7406750D0 (en) | 1973-09-10 | 1974-08-15 | HYDRAULIC SYSTEM TO SELECTIVELY POSITION A WORK ACCESSORY |
BE148361A BE819721A (en) | 1973-09-10 | 1974-09-10 | HYDRAULIC CIRCUIT WITH FLOATING CONTROL SELECTIVELY ACTIONABLE |
BE164820A BE839147R (en) | 1973-09-10 | 1976-03-03 | HYDRAULIC CIRCUIT WITH FLOATING CONTROL SELECTIVELY ACTIONABLE |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US395647A US3908515A (en) | 1973-09-10 | 1973-09-10 | Hydraulic circuit with selectively actuatable float control |
Publications (1)
Publication Number | Publication Date |
---|---|
US3908515A true US3908515A (en) | 1975-09-30 |
Family
ID=23563901
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US395647A Expired - Lifetime US3908515A (en) | 1973-09-10 | 1973-09-10 | Hydraulic circuit with selectively actuatable float control |
Country Status (6)
Country | Link |
---|---|
US (1) | US3908515A (en) |
JP (1) | JPS5535563B2 (en) |
BE (1) | BE819721A (en) |
BR (1) | BR7406750D0 (en) |
CA (1) | CA1025326A (en) |
ZA (1) | ZA744408B (en) |
Cited By (41)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4018350A (en) * | 1975-03-17 | 1977-04-19 | Pettibone Corporation | Hydraulic cyliner systems with safeguarded float action |
US4039085A (en) * | 1976-06-10 | 1977-08-02 | Koehring Company | Crane with a pivoted boom and a float valve therefor |
US4128047A (en) * | 1975-08-14 | 1978-12-05 | Textron Inc. | Actuator with locking valves |
US4130049A (en) * | 1977-04-07 | 1978-12-19 | Caterpillar Tractor Co. | Vent control for cylinder mounted load check valves |
US4165675A (en) * | 1977-04-07 | 1979-08-28 | Caterpillar Tractor Co. | Load check valve cylinder mounted |
US4167892A (en) * | 1977-04-07 | 1979-09-18 | Caterpillar Tractor Co. | Load check with mechanical venting means |
US4170279A (en) * | 1976-04-30 | 1979-10-09 | Societe Anonyme Potain Pioclain Materiel (P.P.M.) | Fluid flow control devices |
US4170246A (en) * | 1977-05-23 | 1979-10-09 | Sta-Rite Industries, Inc. | Pilot operator valve |
WO1981000600A1 (en) * | 1979-08-30 | 1981-03-05 | Caterpillar Tractor Co | Lock valve with variable length piston and hydraulic system for a work implement using the same |
US4367673A (en) * | 1981-01-09 | 1983-01-11 | Dresser Industries, Inc. | System and method for controlling the elevation of a boom hoist device |
US4417502A (en) * | 1980-11-17 | 1983-11-29 | Dresser Industries, Inc. | Load supporting hydraulic circuit with emergency automatic load restraint |
US4523513A (en) * | 1982-07-08 | 1985-06-18 | Wabco Westinghouse Fahrzeugbremsen Gmbh | Pneumatic door-operating arrangement |
US4558630A (en) * | 1980-06-05 | 1985-12-17 | Oy Tampella Ab | Hydraulic mechanism with elastically backed piston parts and cooperating valve means |
US4619187A (en) * | 1982-10-25 | 1986-10-28 | Caterpillar Inc. | Fluid control for two independent actuators |
US4754693A (en) * | 1986-04-23 | 1988-07-05 | Concordia Fluidtechnik Gmbh | Valve |
US4761954A (en) * | 1987-03-16 | 1988-08-09 | Dynamic Hydraulic Systems, Inc. | Fork-lift system |
US4761953A (en) * | 1984-04-18 | 1988-08-09 | Dynamic Hydraulic Systems, Inc. | Hydraulic elevator mechanism |
US4768420A (en) * | 1986-04-04 | 1988-09-06 | Ernst Korthaus | Control arrangement for controlling a hydraulic drive for driving a piston pump |
US4852660A (en) * | 1987-11-21 | 1989-08-01 | O & K Orenstein & Koppel Aktiengesellschaft | Grader blade having a pressurized float position |
FR2629304A1 (en) * | 1988-03-30 | 1989-10-06 | Steyr Daimler Puch Ag | LIFT BAR CONNECTING A LIFT ARM TO A LOWER HITCH LEVER IN A LIFT DEVICE FOR A TRACTOR |
US5036750A (en) * | 1989-08-29 | 1991-08-06 | Nippon Air Brake Kabushiki Kaisha | Pilot-operated dual check valve assembly with cross-line flow valving pilot pistons |
WO1991019108A1 (en) * | 1990-05-26 | 1991-12-12 | Robert Bosch Gmbh | Piston-cylinder control device |
US5235896A (en) * | 1991-03-20 | 1993-08-17 | Hoerbiger Fluidtechnik Gmbh | Hydraulic cylinder/piston mechanism |
US5284083A (en) * | 1991-11-26 | 1994-02-08 | Messier-Bugatti | System for powering the driving actuator of an aircraft undercarriage |
US5934176A (en) * | 1995-02-01 | 1999-08-10 | Applied Power Inc. | Hydraulic operating system |
US5988028A (en) * | 1993-02-02 | 1999-11-23 | Putzmeister Aktiengesellschaft | Process for conveying thick matter containing preshredded scrap metal or similar solids |
US6131610A (en) * | 1996-11-22 | 2000-10-17 | Smc Kabushiki Kaisha | Speed controller with pilot check valve |
DE19919014A1 (en) * | 1999-04-27 | 2000-11-09 | Danfoss Fluid Power As | Hydraulic valve with locking and floating function has housing bore, in which switch channel optionally providable with pressure and with connecting channels on both sides is connectable by control valve with pressure source and tank |
US6293181B1 (en) | 1998-04-16 | 2001-09-25 | Caterpillar Inc. | Control system providing a float condition for a hydraulic cylinder |
US20030111117A1 (en) * | 1999-12-13 | 2003-06-19 | Horn Edward R. | Valve arrangement including release valve |
EP1310680A3 (en) * | 2001-11-08 | 2005-08-10 | Botschafter-Knopff, IIse | Stop valve arrangement and control valve with such a stop valve arrangement |
US20060027092A1 (en) * | 1999-09-28 | 2006-02-09 | Caterpillar Inc. | Hydraulic system with an actuator having independent meter-in meter-out control |
US20080121101A1 (en) * | 2006-11-29 | 2008-05-29 | Volvo Construction Equipment Holding Sweden Ab | Double check valve having floating function |
US20090014074A1 (en) * | 2007-07-12 | 2009-01-15 | Sauer-Danfoss Aps | Hydraulic valve arrangement |
US20090078111A1 (en) * | 2007-09-20 | 2009-03-26 | Volvo Construction Equipment Holding Sweden Ab. | Double check valve having floating function |
US20100218746A1 (en) * | 2008-07-03 | 2010-09-02 | Vianney Rabhi | Ball-lift electrohydraulic valve for a hydraulic power unit of a variable compression ratio engine |
CN102135196A (en) * | 2010-01-27 | 2011-07-27 | 马克阀门公司 | Proportional pressure controller |
WO2012082355A2 (en) * | 2010-12-15 | 2012-06-21 | Caterpillar Inc. | Hydraulic system having load lock valve |
US20130055886A1 (en) * | 2010-05-18 | 2013-03-07 | Volvo Construction Equipment Ab | Double check valve for construction equipment |
US9429174B1 (en) * | 2013-03-15 | 2016-08-30 | Clark Equipment Company | Enabling valve having separate float and lift down positions |
IT201900005056A1 (en) * | 2019-04-04 | 2020-10-04 | Nem S R L | HYDRAULIC DRIVE CIRCUIT FOR OPERATING MACHINE WITH MECHANICAL ARTICULATION EQUIPPED WITH FLOATING FUNCTION. |
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US2517164A (en) * | 1947-02-19 | 1950-08-01 | Bruno F Arps | Two-speed hydraulic ram |
US3274902A (en) * | 1965-10-22 | 1966-09-27 | Deere & Co | Hydraulic control system |
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JPS4423873Y1 (en) * | 1965-05-12 | 1969-10-08 |
-
1973
- 1973-09-10 US US395647A patent/US3908515A/en not_active Expired - Lifetime
-
1974
- 1974-03-11 JP JP2728974A patent/JPS5535563B2/ja not_active Expired
- 1974-07-05 CA CA204,191A patent/CA1025326A/en not_active Expired
- 1974-07-09 ZA ZA00744408A patent/ZA744408B/en unknown
- 1974-08-15 BR BR6750/74A patent/BR7406750D0/en unknown
- 1974-09-10 BE BE148361A patent/BE819721A/en not_active IP Right Cessation
Patent Citations (8)
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US2517164A (en) * | 1947-02-19 | 1950-08-01 | Bruno F Arps | Two-speed hydraulic ram |
US3381587A (en) * | 1965-09-10 | 1968-05-07 | Deere & Co | Hydraulic control system |
US3274902A (en) * | 1965-10-22 | 1966-09-27 | Deere & Co | Hydraulic control system |
US3583438A (en) * | 1968-08-17 | 1971-06-08 | Herion Werke Dg Fa | Safety arrangements in servo operated systems |
US3558102A (en) * | 1969-01-10 | 1971-01-26 | William M Cruse | Theater stage set control system |
US3543647A (en) * | 1969-05-02 | 1970-12-01 | Deere & Co | Control valve means for a two-way hydraulic cylinder |
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Cited By (59)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4018350A (en) * | 1975-03-17 | 1977-04-19 | Pettibone Corporation | Hydraulic cyliner systems with safeguarded float action |
US4128047A (en) * | 1975-08-14 | 1978-12-05 | Textron Inc. | Actuator with locking valves |
US4170279A (en) * | 1976-04-30 | 1979-10-09 | Societe Anonyme Potain Pioclain Materiel (P.P.M.) | Fluid flow control devices |
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Also Published As
Publication number | Publication date |
---|---|
BE819721A (en) | 1975-03-10 |
JPS5535563B2 (en) | 1980-09-16 |
JPS5054778A (en) | 1975-05-14 |
ZA744408B (en) | 1975-08-27 |
CA1025326A (en) | 1978-01-31 |
AU7175074A (en) | 1976-01-29 |
BR7406750D0 (en) | 1975-09-09 |
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Legal Events
Date | Code | Title | Description |
---|---|---|---|
AS | Assignment |
Owner name: CATERPILLAR INC., 100 N.E. ADAMS STREET, PEORIA, I Free format text: ASSIGNMENT OF ASSIGNORS INTEREST.;ASSIGNOR:CATERPILLAR TRACTOR CO., A CORP. OF CALIF.;REEL/FRAME:004669/0905 Effective date: 19860515 Owner name: CATERPILLAR INC., A CORP. OF DE.,ILLINOIS Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:CATERPILLAR TRACTOR CO., A CORP. OF CALIF.;REEL/FRAME:004669/0905 Effective date: 19860515 |