US3720059A - Hydraulic system and valve therefor - Google Patents

Hydraulic system and valve therefor Download PDF

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US3720059A
US3720059A US00080665A US3720059DA US3720059A US 3720059 A US3720059 A US 3720059A US 00080665 A US00080665 A US 00080665A US 3720059D A US3720059D A US 3720059DA US 3720059 A US3720059 A US 3720059A
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path
paths
valve
auxiliary valve
pump
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S Schurawski
W Kropp
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Linde GmbH
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Linde GmbH
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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
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/17—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors using two or more pumps
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62D—MOTOR VEHICLES; TRAILERS
    • B62D11/00—Steering non-deflectable wheels; Steering endless tracks or the like
    • B62D11/02—Steering non-deflectable wheels; Steering endless tracks or the like by differentially driving ground-engaging elements on opposite vehicle sides
    • B62D11/06—Steering non-deflectable wheels; Steering endless tracks or the like by differentially driving ground-engaging elements on opposite vehicle sides by means of a single main power source
    • B62D11/10—Steering non-deflectable wheels; Steering endless tracks or the like by differentially driving ground-engaging elements on opposite vehicle sides by means of a single main power source using gearings with differential power outputs on opposite sides, e.g. twin-differential or epicyclic gears
    • B62D11/14—Steering non-deflectable wheels; Steering endless tracks or the like by differentially driving ground-engaging elements on opposite vehicle sides by means of a single main power source using gearings with differential power outputs on opposite sides, e.g. twin-differential or epicyclic gears differential power outputs being effected by additional power supply to one side, e.g. power originating from secondary power source
    • B62D11/18—Steering non-deflectable wheels; Steering endless tracks or the like by differentially driving ground-engaging elements on opposite vehicle sides by means of a single main power source using gearings with differential power outputs on opposite sides, e.g. twin-differential or epicyclic gears differential power outputs being effected by additional power supply to one side, e.g. power originating from secondary power source the additional power supply being supplied hydraulically
    • B62D11/183—Control systems therefor
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20546—Type of pump variable capacity
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/20576—Systems with pumps with multiple pumps
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/25—Pressure control functions
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30505—Non-return valves, i.e. check valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3105—Neutral or centre positions
    • F15B2211/3116—Neutral or centre positions the pump port being open in the centre position, e.g. so-called open centre
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40515—Flow control characterised by the type of flow control means or valve with variable throttles or orifices
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/45—Control of bleed-off flow, e.g. control of bypass flow to the return line
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/46—Control of flow in the return line, i.e. meter-out control
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/635—Circuits providing pilot pressure to pilot pressure-controlled fluid circuit elements
    • F15B2211/6355—Circuits providing pilot pressure to pilot pressure-controlled fluid circuit elements having valve means
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/71—Multiple output members, e.g. multiple hydraulic motors or cylinders
    • F15B2211/7142—Multiple output members, e.g. multiple hydraulic motors or cylinders the output members being arranged in multiple groups

Definitions

  • ABSTRACT A two-pump hydraulic system having a hydraulic load
  • each of the pumps circulates hydraulic fluid along a closed path to a reservoir and can be used independently to operate respective loads.
  • Our present invention relates to a hydraulic system and, more particularly, to a hydraulic system having a plurality of pumps which may be independently connected to respective hydraulic loads through controllable valve means.
  • the invention relates to a valve arrangement for enabling a plurality of pumps to be connected to a given load.
  • Hydraulic systems generally comprise a source of fluid under pressure, e.g. a motor-driven pump, adapted to circulate a hydraulic fluid from a reservoir in a closed path, controllable valve means for shunting all or a portion of this fluid to a load and a hydraulic motor forming part of this load.
  • the pump may be of the constant-displacement or variable-displacement type while the motor may be a rotary or piston motor.
  • the valve means may be controlled manually, electrically or by a control fluid and various auxiliary equipment may be associated with the hydraulic network depending upon requirements.
  • Hydraulic systems may be used in various equipment and, in some cases, a particular hydraulic network may operate a number of independently controllable loads or one or more interrelated loads.
  • load is used herein to indicate any consumer of the power fluid and is intended, therefore, to include the reciprocable or rotary hydraulic motors mentioned earlier and any force-transmitting or motion-transmitting transmission means normally associated therewith.
  • Such systems are employed in agricultural vehicles, industrial plants and elsewhere since they afford precise regulation of the operation of the load, are of sufficient versatility, with appropriate transmission means, to enable operation of many different types of loads.
  • the systems are of particular interest in dredges and the like for performing a number of movements and operating the various parts of a dredge-or other excavator.
  • rotary hydraulic motors may be provided to effect translation of the excavator vehicle and rotation of any turntable or turret carried thereby while reciprocable hydraulic motors, e.g. piston-andcylinder arrangements may be employed to operate the excavator arms, to position the bucket and to open or close the latter.
  • reciprocable hydraulic motors e.g. piston-andcylinder arrangements
  • the present invention is concerned, for the most part, with a control arrangement in which a plurality, i.e. at least two, hydraulic pumps are provided and are designed to work into respective loads or to be connected in common to a single load.
  • Systems of the latter type generally comprise individual networks for each of the pumps and respective controllable valve means in each network, connecting the respective pump with the corresponding load or loads.
  • a typical arrangement provides a pressure line running from the discharge side of the pump in a closed path to a pressureless reservoir from which the pump draws hydraulic fluid from this line to the load and returning the bypassed fluid to the reservoir.
  • the supply and return lines of the load are generally coupled to the controllable valve associated therewith so that a reversible flow of fluid is permitted to the hydraulic motor whereby the hydraulic motor operated in the double-acting sense, i.e. is-
  • a case in point is the operation of an excavating machine, such as a dredge, in which the translation of the excavator and rotation of its turntable may be effected by hydraulic motors.
  • the hydraulic pump associated with movement of the excavator or rotation of the turntable may be connected to the network supplying hydraulic fluid to the bucket-lifting means.
  • Control arrangements of this type have, for the most part, involved the use of manually operable valves.
  • One of the problems encountered with such arrangements is the feedback from one load to I another through the interconnected networks of such systems.
  • Another object of our invention is the provision of an improved valve for automatically operating such a system.
  • Yet another object of our invention is the provision of an improved hydraulic system for multiple-load installations, e.g. excavators, dredges, and the like.
  • a hydraulic system having a plurality of fluid-displacement pumps (e.g. two pumps each of which works into a respective network returning the fluid to a reservoir in a closed path), respective control-valve means connecting each of said paths with at least one load for reversible operation of the latter, depending upon the position of the valve means, at least one load operated by a respective valve means and adapted to be energizable by fluid derived from both networks or paths.
  • fluid-displacement pumps e.g. two pumps each of which works into a respective network returning the fluid to a reservoir in a closed path
  • respective control-valve means connecting each of said paths with at least one load for reversible operation of the latter, depending upon the position of the valve means, at least one load operated by a respective valve means and adapted to be energizable by fluid derived from both networks or paths.
  • the two or more fluid paths are connected together by check-valve and shunt-conduit means while an auxiliary or additional valve is provided for operation upon actuation of the load drawing upon both fluid paths.
  • the additional valve is provided in the circulating path and has a first position permitting the circulation of the fluid from the pump to the reservoir and a second position blocking such circulation such that, upon blockage of the circulation in one network, hydraulic fluid is forced into the other network through the respective check valve and shunt-conduit.
  • a connection conduit is provided between the two paths and is formed with the check valve.
  • each may have a respective auxiliary valve operable to block the respective circulation and a respective check valve connecting each path with the other to admit fluid from one path to the other when the auxiliary valve blocks the circulation of the one path.
  • control means is provided for the auxiliary valve in such manner that, upon operation of the control valve associated with one or more loads of one circulating path or network (but less than all of the loads thereof), the auxiliary valve of the other path is shifted from its open" to its closed” position to bypass some of the fluid of this other circulating path into the circulating path and supply duct of the operated load.
  • the auxiliary valve may be provided with a piston or like fluid-responsive member in fluid communication with the control input to the hydraulic input of the control valve of the load to be operated by more than one pump.
  • the control valves can be operated hydraulically, pneumatically, electrically or mechanically and we prefer a similar mode of actuation of the auxiliary valve of the other path with an operative connection between the actuating means of the control valve and the auxiliary valve of the other path.
  • each of the loads which may be rotaryhydraulic motors (see pages 194 200 of FLUID POWER, U.S. Government Printing Office, 1966) or reciprocable actuators of the piston-and-cylinder type (pages 188 194 of FLUID POWER) is reversible and is provided with two hydraulic lines interchangeably serving as supply and return lines while the control valve associated with this load is a three-position or three-way, four-port or six-port valve. In a first position thereof, i.e. one extreme position, the control valve connects one of the lines to the circulating path under pressure while the other line is connected through a pressure reducer to the closed transport path and, conversely, in another extreme'position, the lines are functionally interchanged to reverse the load.
  • means are provided to prevent operation of the auxiliary valve of the other circulating path in response to operation of the control valve of a doubly energized load of the first circulating path only when all of the loads associated with the second circulating path are in a de-energized state, i.e. when the control valves of these loads are in their neutral position.
  • each one or more loads of the second circulating path are intended to be energized by the respective control valves and the auxiliary valve of this path is shifted into its blocking position to couple the two paths together via the check valves, the loads associated with the path of the closed auxiliary valve will no longer be effective.
  • the danger that the doubly energized load will feed back energy to the hydraulic system and thereby influence an energized load of the circulating path supplying the additional medium, is precluded.
  • the auxiliary valve can be provided directly in the circulating path, i.e. in the return line which is connected with the high-pressure line of the network. It has been found to be most desirable to assemble the control valves in a control valve block, e.g. a metallic body bored with cylinders each receiving a respective valve member and provided with a common return duct. The auxiliary valve is then mounted directly in this block and is so constituted that two distinct outlets for the return fluid are provided, preferably at right angles, to one another, one of these outlets serving to accommodate the auxiliary valve.
  • a control valve block e.g. a metallic body bored with cylinders each receiving a respective valve member and provided with a common return duct.
  • the auxiliary valve is then mounted directly in this block and is so constituted that two distinct outlets for the return fluid are provided, preferably at right angles, to one another, one of these outlets serving to accommodate the auxiliary valve.
  • FIG. 1 is a hydraulic circuit diagram illustrating the invention as applied to an excavator
  • FIG. 2 is an axial cross-sectional view through an auxiliary valve as used in this system.
  • FIG. 1 of the drawing I show a housing 100 of the mobile excavator which has an internal combustion engine 101, the crankshaft of which is represented at 102 and leads into the housing 100 of the hydraulic drive.
  • the crankshaft 102 operates a mechanical transmission of the step-up type consisting of a large-diameter drive gear 3a carried by the shaft 102 and meshing with the small-diameter driven gear 3b and 30 respectively carried by the shafts la and 2a of a pair of hydraulic pumps 1 and 2.
  • the hydraulic pumps are of the variable-displacement type and may be axial piston pumps as described at pages 109 113 of FLUID POWER, cited earlier.
  • the pumps are provided with tiltable control blocks cylinder drum or the like to adjust the strokes of the axial pistons and hence the displacement of the pump.
  • the displacement-control means is represented by the tiltable control blocks, cylinder drum or the like to adjust the strokes of the axial pistons and hence the displacement of the pump.
  • displacement-control means is represented by the tiltable members lb and 4b of the pumps, these members being connected together by a link 4 pivotally coupled thereto.
  • a control-piston arrangement 7 defines a chamber 7a energized from the high-pressure line 6 of the pump 2 and a chamber 7b of equal cross-section energized by the fluid from high-pressure line 5 of pump 1, both pressures working upon a piston 7c working against a spring 7d to maintain the predetermined output of the pumps by automatic adjustment of the control members 1b and 2b.
  • the pumps 1 and 2 have intake ducts 1c and 2c drawing fluid from a sump or reservoir 8, shown to be made up of a number of sections for clarity in illustrating the hydraulic flow path, but actually constituting a single reservoir.
  • the installation comprises a valve block 9 formed .with a plurality of valves l0, l1 and 12 each of which is of the three-position, six-port type, as will be described in connection with the valve 10. Furthermore, the valves 10 12 are hydraulically actuated as also will be apparent hereinafter, each operating a respective load 15, 18 and 21.
  • the load 15, which may be a hydraulic motor of the character previously described, has a pair of hydraulic lines 13 and 14 which are connected to the ports 13a and 14a of the valve 10, respectively.
  • 'block 9 is provided with a high-pressure passage 22 which is supplied from the discharge side of pump 1 via line 5 and with a passage 23 constituting the return line.
  • Passage 23 opens via line 23a into the reservoir 8 and sustains no back pressure, the reservoir being pressureless.
  • the line 23 may, of course, have a cross-section slightly smaller than that of line 22.
  • the valve 10 is provided with a port 10a connected with the reservoir 8 via a pressure-relief or pressurelimiting valve 46 while the port 10b is connected in the circulating path 22, 23 of the pump 1.
  • the first position of the valve 10, represented at 100 blocks line 22 and connects ports 10a and 14a and ports 13a and 10b via check valves built into the valve body.
  • the hydraulic load represented by motor 15 is thereby operated in one sense.
  • the other position of the valve 10, represented at 10d likewise blocks line 22 but connects port 10a directly with port 13a and port 14a directly with port 10b for operation of the load in the other direction.
  • valve member 10 is provided with hydraulic actuators 102 and 10f effective to displace the valve member from its neutral position into either extreme position by the application of a control signal in the form of a hydraulic pressure at the line 24 or 25.
  • the motor 15 may be the drive motor for the excavator.
  • valve 11 is connected via lines 16 and 17 with the double-acting piston-cylinder arrangement 18 which may serve to operate the scoop of the excavator while control valve 12 is connected via lines 19 and 20 with a cylinder 21 for energizing the outrigger cylinders for stabilizing the excavator.
  • valves 10, 11 and 12 illustrated in FIG. 1 In the neutral positions of the valves 10, 11 and 12 illustrated in FIG. 1, these valves connect the supply duct 4 of pump 1 with a circulating conduit 22 which, in turn, is connected with the pressureless return line 23 running to the reservoir 8.
  • the control valves 10, l1 and 12 are hydraulically actuated, to which end, each of the valves is provided with a respective actuating cylinder (actuator) such as is shown at We and 10f and energizable via control lines as described.
  • the actuating cylinders for the control valve 10, for example, are energized by control lines 2 3 and 25 which, in turn, may be connected to a control and pressure regulator, a manually operated valve or other actuating lines not further illustrated.
  • the actuating cylinders of the control valve 11 are provided with control lines 26 and 27 while the actuating cylinders of control valve 12 are provided with control lines 28 and 29.
  • the doubleacting cylinder 18 constitutes a reversible hydraulic load associated with the control valve 11 and the double-acting cylinder 21 constitutes a reversible hydraulic load energized through the control valve 12, the members 15, 18 and 21 constitute three hydraulic loads associated with the pump 1 and the closed circulating paths 22 and 23 in which the pump is provided.
  • the hydraulic load 30 can be a hydraulic motor connected by suitable lines to the control valves 33, the hydraulic motor 31 may be connected to the control valve 34 and the reciprocable double-acting piston can be guided to the control valve 35 of another valve block 32 in the manner already described with reference to the loads 15, 18 and 21.
  • the control valve 33 is provided with hydraulic actuators which may be energized via control lines 36 and 37, the control valve 34 has its actuators energized via control lines 38 and 39, and the control valve 34 is energized at its actuators via the control lines 40 and 41.
  • the control lines may be tied to a regulator and other means for generating the hydraulic pressure for operating the control valve.
  • the valve block 42 is provided with the circulating passage 43 which is connected within the valve block with the pressureless return line 44 which is returned to the same reservoir 8 into which the line 23 empties.
  • the pump 2 feeds the pressure line 6 which communicates with the line 43.
  • the lines 6, 43 and 44 constitute a closed circulating path for the second pump 2.
  • the valve 46 of this path likewise serves for pressure regulation and limitation.
  • valve block may be provided with an array of pressure-relief valves 45, advantageously connected to the respective lines of each load for operation in either sense thereof to maintain a predetermined maximum pressure in each line.
  • the circulating conduit 22 is, moreover, provided upstream of the valve 47 with a duct 48 connected by a check valve 49 with the circulating conduit 43 of the other fluid-circulating path.
  • the check valve 49 is built such that the side connected valve 47 is normally a low pressure side whereas the other side is at higher pressure to maintain the valve 49 in a closed condition and prevent flow of fluid line from the path associated with pump 2 from the path associated with pump 1.
  • the line 48 opens into line 6 at or before its junction with conduit 43 and the valve block 42.
  • the auxiliary valve 47 is hydraulically actuated via a control line 50 whoch is energized via a transformation valve 51, the inputs to which are the control lines 40 and 41 of the valve 35 for piston arrangement 43 in the other circulating path.
  • an auxiliary valve 52 is provided between the circulating passage 43 and the pressureless return passage 44 and is connected via a reversing valve 56 and line 55 with the circulating path of pump 1.
  • Valve 56 is energized from control lines 28 and 29 associated with the load 21.
  • a connecting line 53 is tied to the circulating conduit 43 and communicates via a check valve 54 with the high pressure line 5 of pump 1 prior to its entry into the valve block 9.
  • the network or circuit of FIG. 1 operates as follows:
  • the circulating conduit 22 is connected with the pressureless return conduit 23 through the normally open valve 47 while the circulating passage 43 is connected with the pressureless return passage 44 via the normally open valve 52.
  • the circuit then operates in accordance with the usual practice.
  • the loads l5, 18 or 21 can be selectively connected to the pump 1 and energized in a sense dependent upon the extreme position of the control valve 10, 11 or 12 which is used.
  • actuation of one of the control valves 33, 34 and 35 connects the corresponding load 30, 31 and 32 to the pump 2 independently of whether one, two or all of the valves of the other hydraulic network being energized.
  • a pressure reduction in one of the lines 40 or 41 of the load 32 generates a pressure in line 50 sufficient to displace the valve 47 and thereby block the connection between lines 22 and 23 to build up pressure at line 48 until the check valve 49 cracks to deliver fluid to line 43 from pump 1.
  • the load 32 is, in this case, operated with the augmented flow of the two pumps. However, in this latter case when any of the valves 10, 11 or 12 are operated, actuation of valve 47 will have no effect and the two networks will operate independently and without feedback between them.
  • each of the control valves l0, 11 or 12 or 33, 34 and 35 upon displacement from its neutral position in which, for example, the valve portion 102 is effective, blocks the circulating passage 22 or 43 and permits fluid to flow only to the corresponding load. Since all of the control valves 10 12 and 33 35 are disposed between the respective auxiliary valve 47 or 52 and the corresponding pump 1 or 2, actuation of one of the control valves (10 12 or 33 35) renders the corresponding auxiliary valve (47 or 52) ineffective since no further fluid circulation is provided through this valve and the position of the valve is unimportant. It has already been observed that this arrangement prevents undesired influence from being fed back from one load to another.
  • FIG. 2 we have shown in cross-section a portion of the control block 9 (valve block) illustrating the cylinder bore for the control valve 12 by way of example.
  • the circulating passage 22 is thus seemed to be formed by a passage opening it to the bore of control valve 12.
  • the auxiliary valve 47 illustrated in FIG. 2, which may be structurally identical to the valve 52 as noted earlier, comprises a tubular piston 60 which is actually shiftable in the bore 61 against the force of a helical coil compression spring 62 and is provided with radial openings 63 which, in the indicated position of the piston 60, connects the passage 22 with the return line 23, the latter then extending radially to the bore 61.
  • the valve block 9 is provided with an annular boss 90 surrounding a recess 9b receiving a seal 90 against which the tubular boss 66a of the valve housing is seated coaxially with the bore 61.
  • the recess 9c is, moreover, coaxial with the further recess 9d defining a shoulder 9e against which the spring 62 is seated, the spring 62 being received within the recess 9d and the bore 66b of housing 66 in axial alignment therewith.
  • the bore 66b Remote from the connection of housing 66 with the valve block 9, the bore 66b is provided with a smalldiameter step 660 having an annular groove 66d receiving a seal 66e which slidably engages the head 60a of the piston.
  • a further seal 66f slidably engages the piston 60 rearwardly of the head 60a to define a compartment 68 between the seals 66d and 66f and behind the shoulder 67 of this head.
  • Both traversing bars 66g may be used to connect the housing 66 to the valve block 9 and any conventional coupling system may serve to connect the conduit 48 therewith.
  • a suitable coupling includes a ring or flange 48a bolted axially to the housing 66 by a screw traversing the boss 48b and having a shoulder 48c bearing axially upon a shoulder 48d of the duct 48.
  • a sealing ring 48 may be clamped between the flange 48fof this duct and the exposed external face of the housing 66.
  • the radial openings 63 communicate between the passage 22 and the passage 23 via an annular compartment 64 formed in the valve block 9 and constituting, together with duct 23, a pressureless return path for the fluid.
  • the piston 60 moreover, is urged by the spring 62 to the right so that its end face 65 abuts the end face 66 of the housing 66 at the righthand end of the bore 62.
  • the annular chamber 68 is, moreover, connected via a port 69 with the conduit 50 serving to supply the actuating pressure to the valve (see FIG. 1).
  • the piston 60 is urged to the left against the force of spring 62 to block communication between ducts 22 and 23 and maintain communication between ducts 22 and 48 through the interior of the valve.
  • passages 63 in the valve body and the housing portion cooperating therewith are so shaped that with increasing displacement of the valve body, the communication between passages 22 and 23 is proportionally reduced and finally completely cut off.
  • the central bore 70 of the valve piston 60 connects passages 22 and 48.
  • the housing 66 is provided directly at a part of the valve block 9 at which the pressureless return conduit communicates with line 22 thereby minimizing the cost of producing the system.
  • a hydraulic system comprising:
  • a plurality of pumps each having a pressure side and an intake side;
  • conduit means defining two distinct circulating paths including a respective circulating path for each of said pumps, each said conduit means including respective ducts connected to said pressure side and said intake side of each pump;
  • two independently operable control valves including a respective control valve connecting each of said paths with a respective hydraulically operable load;
  • auxiliary valve in at least one of said paths permitting circulation of a hydraulic medium therealong but actuatable to block such circulation, said auxiliary valve having a first position communicating between said duct connected to said pressure side and said duct connected to the intake side of the respective pump and permitting return flow of fluid from the respective path to the respective pump and a second position blocking return flow of fluid:
  • an automatically operable check valve in said shunt conduit automatically opening upon shifting of said auxiliary valve into said second position for undirectional flow of the medium between said one of said paths and said other of said paths upon blockage of circulation in said one path by said auxiliary valve and upon the fluid pressure at said shunt conduit exceeding the fluid pressure at said other path whereby a load energized through the control valve of said other path may draw upon medium from both said one of said paths and said other path.
  • a hydraulic system comprising:
  • a plurality of pumps each having a pressure side and an intake side;
  • conduit means defining a respective circulating path for each of said pumps, said conduit means including respective ducts connected to said pressure side and said intake side of each pump;
  • auxiliary valve in at least one of said paths permitting circulation of a hydraulic medium therealong but actuatable to block such circulation, said auxiliary valve having a first position communicating between said duct connected to said pressure side and said duct connected to the intake side of the respective pump and permitting return flow of fluid from the respective path to the respective pump and a second position blocking return flow of fluid;
  • an automatically operable check valve in said shunt conduit automatically opening upon shifting of said auxiliary valve into said second position for undirectional flow of the medium between said one of said paths and said other of said paths upon blockage of circulation in said one path by said auxiliary valve and upon the fluid pressure at said shunt conduit exceeding the fluid pressure at said other path whereby a load energized through the control valve of said other path may draw upon medium from both said one of said paths and said other path;
  • said auxiliary valve means interconnecting said auxiliary valve and at least one of said control valves for joint operation, said control valve of said other of said paths being provided with reversibly energizable hydraulic actuators and said actuating means includes transformation valve means energizable in parallel with said actuators for generating a control pressure regardless of the sense of operation of the control valve of said other paths, said auxiliary valve including a fluid-responsive member coupled with said transformation valve means for actuation by said control pressure.
  • a hydraulic system comprising:
  • a plurality of pumps each having a pressure side and an intake side;
  • conduit means defining a respective circulating path for each of said pumps, said conduit means including respective ducts connected to said pressure side and said intake side of each pump;
  • auxiliary valve having a first position communicating between said duct connected to said pressure side and said duct connected to the intake side of the respective pump and permitting return flow of fluid from the respective path to the respective pump a second position blocking return flow of fluid;
  • an automatically operable check valve in said shunt conduit automatically opening upon shifting of said auxiliary valve into said second position for unidirectional flow of the medium between said one of said paths and said other of said paths upon blockage of circulation in said one path by said auxiliary valve and upon the fluid pressure at said shunt conduit exceeding the fluid pressure at said other path whereby a load energized through the control valve of said other path may draw upon medium from both said one of said paths and said other path;
  • auxiliary valve means interconnecting said auxiliary valve and at least one of said control valves for joint operation, said auxiliary valve being so constructed and arranged as to maintain communication between said shunt conduit and said one path in both blocking and nonblocking positions of said auxiliary valve.
  • said other path is formed with a respective auxiliary valve actuatable for the selective blocking and unblocking of flow of the medium through said other path, said paths each including a pressureless return line for carrying medium to the intake side of the respective pump, each of said auxiliary valves being disposed between the respective control valve and return line of the corresponding path, said system further comprising another shunt conduit communicating with said other path between its control valve and auxiliary valve and connected to said one path between the pump thereof and the control valve of said one path at the duct connected to the pressure side of the latter pump, said other shunt conduit including a check valve permitting unidirectional flow of medium from said other path to said one path upon the blockage of circulation in said other path by the auxiliary valve associated therewith and upon the further shunt conduit exceeding the pressure in said one path.
  • control valve is formed in a valve block provided with a circulating duct and a return duct branching from said circulating duct, said auxiliary valve comprising a housing mounted on said block, a pressure responsive valve member shiftable in said piston for selectively blocking and unblocking communication between said circulating and return ducts, and means for connecting said shunt conduit to said housing.
  • a hydraulic system comprising a plurality of pumps
  • conduit means defining a respective circulating path including each of said pumps
  • an auxiliary valve in at least one of said paths permitting circulation of a hydraulic medium therealong but actuatable to block such circulation;
  • a shunt conduit connecting said one of said paths with another of said paths between said auxiliary valve and the pump associated with said one of said path;
  • a check valve in said shunt conduit for undirectional flow of the medium between said one of said paths and said other of said paths upon blockage of circulation in said one of path by said auxiliary valve and upon the fluid pressure at said shunt conduit exceeding the fluid pressure at said other path whereby a load energized through the control valve of said other path may draw upon medium from both said one of said paths and said other path; common actuating means for said auxiliary valve and said control valve of said other of said paths; said control valve of said other of said paths being provided with reversibly energizable hydraulic actuators and said actuating means including transformation valve means energizable in parallel with said actuators for generating a control pressure regardless of the sense of operation of the control valve of said other path, said auxiliary valve including a fluid-responsive member coupled with said transformation valve for actuation by said control pressure.
  • said auxiliary valve is so constructed and arranged as to block communication between said one path and said shunt conduit when circulation along said one path is permitted.
  • auxiliary valve is so constructed and arranged as to maintain communication between said shunt conduit and said one path in both blocking and nonblocking positions of said auxiliary valve.
  • said other path is formed with a respective auxiliary valve actuatable for the selective blocking and unblocking of flow of the medium through said other path, said paths each including a pressureless return line for carrying medium to the respective pump, each of said auxiliary valves being disposed between the respective control valve and return line along the corresponding paths, said shunt conduit communicating .with said one path between its control valve and auxiliary valve, said system further comprising another shunt conduit communicating with said other path between its control valve and auxiliary' valve and connected to said one path between the pump thereof and the control valve of said one path, said other shunt conduit including a check valve permitting unidirectional flow of medium from said other path to said one path upon the blockage of circulation of said other path by the auxiliary valve associated therewith and upon the further shunt conduit exceeding the pressure in said one path.
  • each of said paths being provided with a plurality of control valves each energizing a respective load and disposed along said path between the respective pump and auxiliary valve, the control valves of each path being so constructed and arranged as to block, upon operation, the flow ofthe medium to the respective auxiliary valve.
  • control valve is formed in a valve block provided with a circulating duct and a return duct branching from said circulating duct, said auxiliary valve comprising a housing mounted on said block, a pressure responsive valve member shiftable in said piston for selectively blocking and unblocking communication between said circulating and return ducts, and means, for connecting said shunt conduit to said housing.
  • a hydraulic system comprising:
  • conduit means defining a respective circulating path including each of said pumps
  • an auxiliary valve in at least one of said paths permitting circulation of a hydraulic medium therealong but actuatable to block such circulation;
  • a shunt conduit connecting said one of said paths with another of said paths, said shunt conduit communicating with said one of said paths between said auxiliary valve and the pressure side of the pump associated with said one of said paths;
  • a check valve in.said shunt conduit for unidirectional flow of the medium between said one of said paths and said other of said paths upon blockage of circulation in said one path by said auxiliary valve and upon the fluid pressure at said shunt conduit exceeding the fluid pressure at said other path whereby a load energized through the control valve of said other path may draw upon medium from both said one of said paths and said other path
  • said auxiliary valve being so constructed and arranged as to maintain communication between said shunt conduit and said one path in both the blocking and nonblocking positions of said auxiliary valve, said other path being formed with a respective auxiliary valve actuatable for the selective blocking and unblocking of flow of the medium through said other path, said paths each including a pressureless return line for carrying medium to the respective pump, each of said auxiliary valves being disposed between the respective control valve and return line along the corresponding paths;
  • Another shunt conduit communicating with said other path between its control valve and auxiliary valve and connected to said one path between the pressure side of the pump thereof and the control valve of said one path, said other shunt conduit including a check valve permitting unidirectional flow of medium from said other path to said one path upon the blockage of circulation of said other path by the auxiliary valve associated therewith and upon the further shunt conduit exceeding the pressure in said one path, said pumps of said one and said other paths being provided with a common reservoir and a common drive, said return lines emptying into said reservoir, each of said paths being provided with a plurality of control valves each energizing a respective load and disposed along said path between the respective pump and auxiliary valve, the control valves of each path being so constructed and arranged as to block, upon operation, the flow of the medium to the respective auxiliary valve, at least one of said control valves being provided with a pair of hydraulic actuators for reversible operation of said one of said control valves and the load associated therewith; and a transformation valve connected to said actuators for
  • control valve is formed in a valve block provided with a circulating duct and a return duct branching from said circulating duct, said auxiliary valve comprising a housing mounted on said block, a pressure responsive valve member shiftable in said piston for selectively blocking and unblocking communication between said circulating and return ducts, and means for connecting said shunt conduit to said housing.
  • a hydraulic system comprising:
  • a respective auxiliary valve in each of said networks and having a first position enabling energization of the respective load by blocking a path shunting fluid from the respective network to the respective pump, and a second position shunting fluid from the respective network to the respective pump;
  • a respective check valve connected between each network at the pressure side of its pump and the other network behind its auxiliary valve for automatically admitting fluid from a network having its said auxiliary valve in its first position to the other network;

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • General Engineering & Computer Science (AREA)
  • Automation & Control Theory (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Operation Control Of Excavators (AREA)
US00080665A 1969-10-15 1970-10-14 Hydraulic system and valve therefor Expired - Lifetime US3720059A (en)

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DE19691952034 DE1952034A1 (de) 1969-10-15 1969-10-15 Steuereinrichtung fuer eine hydraulische Anlage und Ventil hierzu

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US (1) US3720059A (enrdf_load_stackoverflow)
JP (1) JPS5417114B1 (enrdf_load_stackoverflow)
DE (1) DE1952034A1 (enrdf_load_stackoverflow)
FR (1) FR2065949A5 (enrdf_load_stackoverflow)
GB (1) GB1290247A (enrdf_load_stackoverflow)
SE (1) SE366098B (enrdf_load_stackoverflow)

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US3922855A (en) * 1971-12-13 1975-12-02 Caterpillar Tractor Co Hydraulic circuitry for an excavator
US4024710A (en) * 1976-03-25 1977-05-24 Koehring Company Load sensing hydraulic circuit having power matching means
US4030623A (en) * 1971-12-13 1977-06-21 Caterpillar Tractor Co. Hydraulic circuitry for an excavator
US4073141A (en) * 1977-03-17 1978-02-14 Caterpillar Tractor Co. Fluid control system with priority flow
US4078681A (en) * 1976-08-24 1978-03-14 Caterpillar Tractor Co. Dual pump hydraulic control system with predetermined flow crossover provision
US4112821A (en) * 1976-12-03 1978-09-12 Caterpillar Tractor Co. Fluid control system for multiple circuited work elements
US4142445A (en) * 1977-03-17 1979-03-06 Caterpillar Tractor Co. Crossover plural circuit fluid system
US4179981A (en) * 1975-10-30 1979-12-25 Poclain Device for sequentially supplying several hydraulic motors
US4208874A (en) * 1978-08-28 1980-06-24 Caterpillar Tractor Co. Apparatus for producing different flow rates of a fluid
US4210061A (en) * 1976-12-02 1980-07-01 Caterpillar Tractor Co. Three-circuit fluid system having controlled fluid combining
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
US4262554A (en) * 1978-08-18 1981-04-21 S.R.M. Hydromekanik Aktiebolag Hydraulic valve system for controlling particularly a vehicle gearbox
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JPS5779306A (en) * 1981-05-14 1982-05-18 Hitachi Constr Mach Co Ltd Hydraulic circuit
WO1982002230A1 (en) * 1980-12-24 1982-07-08 Hall Lowell R System with constant force actuator
US4342254A (en) * 1973-12-22 1982-08-03 O & K Orenstein & Koppel Aktiengesellschaft Circuit for hydrostatically operable devices
US4369625A (en) * 1979-06-27 1983-01-25 Hitachi Construction Machinery Co., Ltd. Drive system for construction machinery and method of controlling hydraulic circuit means thereof
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US4614475A (en) * 1981-05-02 1986-09-30 Hitachi Construction Machinery Company, Inc. Hydraulic circuit system for civil engineering and architectural machinery
US4738103A (en) * 1986-02-04 1988-04-19 Chs Vickers S.P.A. Hydraulic control circuit for working members of earth-moving machines with centralized braking of the actuators
US4787204A (en) * 1987-09-28 1988-11-29 J. I. Case Company Common relief valve
US5079919A (en) * 1989-03-30 1992-01-14 Hitachi Construction Machinery Co., Ltd. Hydraulic drive system for crawler mounted vehicle
US5083428A (en) * 1988-06-17 1992-01-28 Kabushiki Kaisha Kobe Seiko Sho Fluid control system for power shovel
US5127227A (en) * 1988-05-16 1992-07-07 Kabushiki Kaisha Komatsu Seisakusho Hydraulic circuit apparatus for construction vehicles
US5211014A (en) * 1991-01-15 1993-05-18 Linde Aktiengesellschaft Hydraulic drive system
US5277027A (en) * 1991-04-15 1994-01-11 Hitachi Construction Machinery Co., Ltd. Hydraulic drive system with pressure compensting valve
US5448148A (en) * 1992-06-11 1995-09-05 Caterpillar Inc. Apparatus for positioning an excavator housing
US5471839A (en) * 1989-03-24 1995-12-05 Hitachi Construction Machinery Co., Ltd. Valve apparatus and hydraulic drive system
US6276133B1 (en) * 1998-09-14 2001-08-21 Komatsu Ltd. Pressure fluid supply and delivery apparatus
US6357231B1 (en) * 2000-05-09 2002-03-19 Clark Equipment Company Hydraulic pump circuit for mini excavators
US6611415B1 (en) * 1999-10-01 2003-08-26 Kayaba Industry Co., Ltd. Fail-safe circuit
US6619037B1 (en) * 1999-01-19 2003-09-16 Hitachi Construction Machinery Co., Ltd. Hydraulic driving device of civil engineering and construction machinery
US6651426B2 (en) 2002-03-07 2003-11-25 Leon's Mfg. Company, Inc. Loader drive system
WO2005015030A1 (de) * 2003-08-08 2005-02-17 Cnh Baumaschinen Gmbh Hydraulisches steuersystem für baumaschinen, insbesondere für bagger
US20050229594A1 (en) * 2004-03-31 2005-10-20 Kobelco Construction Machinery Co., Ltd. Hydraulic control system and construction machine
US20060120892A1 (en) * 2003-01-24 2006-06-08 Sandvik Tamrock Oy Hydraulic system for mining equipment and method of adjusting power of rock drill machine
US20060236688A1 (en) * 2005-03-31 2006-10-26 Nabtesco Corporation Hydraulic circuit
EP1795657A3 (en) * 2005-12-09 2008-12-24 Volvo Construction Equipment Holding Sweden AB Hydraulic circuit for heavy construction equipment
CN102536932A (zh) * 2012-01-11 2012-07-04 中联重科股份有限公司 压缩垃圾车及其液压系统
US9677577B1 (en) * 2016-12-09 2017-06-13 Ellicott Dredge Enterprises, Llc Dredge having modular hydraulic manifolds
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US11079013B2 (en) * 2017-09-25 2021-08-03 Tesmec S.P.A. Hydraulic apparatus for stretching conductors for power lines

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DE3007787A1 (de) * 1980-02-29 1981-09-17 Linde Ag, 6200 Wiesbaden Steuereinrichtung mit einem schieberventil mit feinsteuernuten am steuerschieber
JPS5751006A (en) * 1980-09-08 1982-03-25 Toshiba Mach Co Ltd Composite control valve for conflluence
DE3044144A1 (de) * 1980-11-24 1982-09-09 Linde Ag, 6200 Wiesbaden Hydrostatisches antriebssystem mit einer einstellbaren pumpe und mehreren verbrauchern
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DE3221160C2 (de) * 1982-06-04 1986-05-07 Mannesmann Rexroth GmbH, 8770 Lohr Aus zwei Steuerblöcken bestehende Steuerventileinrichtung für mehrere hydraulische Antriebe, insbesondere von Mobilgeräten
DE3919640C2 (de) * 1989-06-16 1996-10-02 Rexroth Mannesmann Gmbh Steuerventileinrichtung mit zwei Steuerblöcken und Pumpensteuerung für mehrere hydraulische Antriebe
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Cited By (55)

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Publication number Priority date Publication date Assignee Title
US3796517A (en) * 1971-08-06 1974-03-12 Poclain Sa Device for feeding pressurized fluid
US3817153A (en) * 1971-09-29 1974-06-18 Rexroth Gmbh G L Hydraulic control circuit
US3922855A (en) * 1971-12-13 1975-12-02 Caterpillar Tractor Co Hydraulic circuitry for an excavator
US4030623A (en) * 1971-12-13 1977-06-21 Caterpillar Tractor Co. Hydraulic circuitry for an excavator
US4342254A (en) * 1973-12-22 1982-08-03 O & K Orenstein & Koppel Aktiengesellschaft Circuit for hydrostatically operable devices
US4179981A (en) * 1975-10-30 1979-12-25 Poclain Device for sequentially supplying several hydraulic motors
US4024710A (en) * 1976-03-25 1977-05-24 Koehring Company Load sensing hydraulic circuit having power matching means
US4078681A (en) * 1976-08-24 1978-03-14 Caterpillar Tractor Co. Dual pump hydraulic control system with predetermined flow crossover provision
US4210061A (en) * 1976-12-02 1980-07-01 Caterpillar Tractor Co. Three-circuit fluid system having controlled fluid combining
US4112821A (en) * 1976-12-03 1978-09-12 Caterpillar Tractor Co. Fluid control system for multiple circuited work elements
US4142445A (en) * 1977-03-17 1979-03-06 Caterpillar Tractor Co. Crossover plural circuit fluid system
US4073141A (en) * 1977-03-17 1978-02-14 Caterpillar Tractor Co. Fluid control system with priority flow
US4262554A (en) * 1978-08-18 1981-04-21 S.R.M. Hydromekanik Aktiebolag Hydraulic valve system for controlling particularly a vehicle gearbox
US4208874A (en) * 1978-08-28 1980-06-24 Caterpillar Tractor Co. Apparatus for producing different flow rates of a fluid
US4369625A (en) * 1979-06-27 1983-01-25 Hitachi Construction Machinery Co., Ltd. Drive system for construction machinery and method of controlling hydraulic circuit means thereof
US4413472A (en) * 1979-07-25 1983-11-08 Zahnradfabrik Friedrichshafen, Ag. High-pressure pump with pressure regulator
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
US4561341A (en) * 1980-07-07 1985-12-31 Kubota, Ltd. Hydraulic circuitry for a backhoe
WO1982002230A1 (en) * 1980-12-24 1982-07-08 Hall Lowell R System with constant force actuator
US4372193A (en) * 1980-12-24 1983-02-08 Caterpillar Tractor Co. System with constant force actuator
US4378675A (en) * 1981-01-14 1983-04-05 Mobil Oil Corporation Hydraulic pump interlock system
US4561824A (en) * 1981-03-03 1985-12-31 Hitachi, Ltd. Hydraulic drive system for civil engineering and construction machinery
US4614475A (en) * 1981-05-02 1986-09-30 Hitachi Construction Machinery Company, Inc. Hydraulic circuit system for civil engineering and architectural machinery
JPS5779306A (en) * 1981-05-14 1982-05-18 Hitachi Constr Mach Co Ltd Hydraulic circuit
JPS5779307A (en) * 1981-05-14 1982-05-18 Hitachi Constr Mach Co Ltd Hydraulic circuit
US4545202A (en) * 1983-10-24 1985-10-08 Sundstrand Corporation Pressure-regulating system
US4738103A (en) * 1986-02-04 1988-04-19 Chs Vickers S.P.A. Hydraulic control circuit for working members of earth-moving machines with centralized braking of the actuators
US4787204A (en) * 1987-09-28 1988-11-29 J. I. Case Company Common relief valve
US5127227A (en) * 1988-05-16 1992-07-07 Kabushiki Kaisha Komatsu Seisakusho Hydraulic circuit apparatus for construction vehicles
US5083428A (en) * 1988-06-17 1992-01-28 Kabushiki Kaisha Kobe Seiko Sho Fluid control system for power shovel
US5471839A (en) * 1989-03-24 1995-12-05 Hitachi Construction Machinery Co., Ltd. Valve apparatus and hydraulic drive system
US5079919A (en) * 1989-03-30 1992-01-14 Hitachi Construction Machinery Co., Ltd. Hydraulic drive system for crawler mounted vehicle
US5211014A (en) * 1991-01-15 1993-05-18 Linde Aktiengesellschaft Hydraulic drive system
US5277027A (en) * 1991-04-15 1994-01-11 Hitachi Construction Machinery Co., Ltd. Hydraulic drive system with pressure compensting valve
US5448148A (en) * 1992-06-11 1995-09-05 Caterpillar Inc. Apparatus for positioning an excavator housing
US6276133B1 (en) * 1998-09-14 2001-08-21 Komatsu Ltd. Pressure fluid supply and delivery apparatus
US6619037B1 (en) * 1999-01-19 2003-09-16 Hitachi Construction Machinery Co., Ltd. Hydraulic driving device of civil engineering and construction machinery
US6611415B1 (en) * 1999-10-01 2003-08-26 Kayaba Industry Co., Ltd. Fail-safe circuit
US6357231B1 (en) * 2000-05-09 2002-03-19 Clark Equipment Company Hydraulic pump circuit for mini excavators
US6651426B2 (en) 2002-03-07 2003-11-25 Leon's Mfg. Company, Inc. Loader drive system
US7900712B2 (en) 2003-01-24 2011-03-08 Sandvik Mining And Construction Oy Hydraulic system for mining equipment and method of adjusting power of rock drill machine
US20060120892A1 (en) * 2003-01-24 2006-06-08 Sandvik Tamrock Oy Hydraulic system for mining equipment and method of adjusting power of rock drill machine
US7475502B2 (en) 2003-08-08 2009-01-13 Cnh Baumaschinen Gmbh Hydraulic control system for construction vehicle, particularly excavators
US20070056437A1 (en) * 2003-08-08 2007-03-15 Volker Bosebeck Hydraulic control system for construction vehicle, particularly excavators
WO2005015030A1 (de) * 2003-08-08 2005-02-17 Cnh Baumaschinen Gmbh Hydraulisches steuersystem für baumaschinen, insbesondere für bagger
US7174711B2 (en) * 2004-03-31 2007-02-13 Kobelco Construction Machinery Co., Ltd. Hydraulic control system and construction machine
US20050229594A1 (en) * 2004-03-31 2005-10-20 Kobelco Construction Machinery Co., Ltd. Hydraulic control system and construction machine
US20060236688A1 (en) * 2005-03-31 2006-10-26 Nabtesco Corporation Hydraulic circuit
US7350353B2 (en) * 2005-03-31 2008-04-01 Nabtesco Corporation Hydraulic circuit
EP1795657A3 (en) * 2005-12-09 2008-12-24 Volvo Construction Equipment Holding Sweden AB Hydraulic circuit for heavy construction equipment
CN102536932A (zh) * 2012-01-11 2012-07-04 中联重科股份有限公司 压缩垃圾车及其液压系统
US20170234336A1 (en) * 2016-02-16 2017-08-17 Kubota Corporation Hydraulic Block
US10626891B2 (en) * 2016-02-16 2020-04-21 Kubota Corporation Hydraulic block
US9677577B1 (en) * 2016-12-09 2017-06-13 Ellicott Dredge Enterprises, Llc Dredge having modular hydraulic manifolds
US11079013B2 (en) * 2017-09-25 2021-08-03 Tesmec S.P.A. Hydraulic apparatus for stretching conductors for power lines

Also Published As

Publication number Publication date
JPS5417114B1 (enrdf_load_stackoverflow) 1979-06-27
DE1952034A1 (de) 1971-04-22
FR2065949A5 (enrdf_load_stackoverflow) 1971-08-06
SE366098B (enrdf_load_stackoverflow) 1974-04-08
GB1290247A (enrdf_load_stackoverflow) 1972-09-20

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