EP0105473B1 - Hydrauliksystem mit zwei Verstellpumpen, die durch Überschuss-Ölströme gesteuert werden - Google Patents

Hydrauliksystem mit zwei Verstellpumpen, die durch Überschuss-Ölströme gesteuert werden Download PDF

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Publication number
EP0105473B1
EP0105473B1 EP83109740A EP83109740A EP0105473B1 EP 0105473 B1 EP0105473 B1 EP 0105473B1 EP 83109740 A EP83109740 A EP 83109740A EP 83109740 A EP83109740 A EP 83109740A EP 0105473 B1 EP0105473 B1 EP 0105473B1
Authority
EP
European Patent Office
Prior art keywords
valve
control
pressure
variable displacement
line
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
Application number
EP83109740A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0105473A3 (en
EP0105473A2 (de
Inventor
Raymond Joseph Lobmeyer
James Anton Miller
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Deere and Co
Original Assignee
Deere and Co
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 Deere and Co filed Critical Deere and Co
Publication of EP0105473A2 publication Critical patent/EP0105473A2/de
Publication of EP0105473A3 publication Critical patent/EP0105473A3/de
Application granted granted Critical
Publication of EP0105473B1 publication Critical patent/EP0105473B1/de
Expired legal-status Critical Current

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Classifications

    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2246—Control of prime movers, e.g. depending on the hydraulic load of work tools
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2221—Control of flow rate; Load sensing arrangements
    • E02F9/2232—Control of flow rate; Load sensing arrangements using one or more variable displacement pumps
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2221—Control of flow rate; Load sensing arrangements
    • E02F9/2239—Control of flow rate; Load sensing arrangements using two or more pumps with cross-assistance
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2278—Hydraulic circuits
    • E02F9/2292—Systems with two or more pumps
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2278—Hydraulic circuits
    • E02F9/2296—Systems with a variable displacement pump
    • 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
    • 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
    • F15B2211/20553—Type of pump variable capacity with pilot circuit, e.g. for controlling a swash plate
    • 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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/605—Load sensing circuits
    • F15B2211/6051—Load sensing circuits having valve means between output member and the load sensing circuit
    • F15B2211/6054—Load sensing circuits having valve means between output member and the load sensing circuit using shuttle 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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/65—Methods of control of the load sensing pressure
    • 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
    • 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
    • F15B2211/78—Control of multiple output members

Definitions

  • the invention relates to a hydraulic system with two variable displacement pumps, each of which feeds a group of control valves with excess outlet, wherein a pressure medium can be fed from one system to the other.
  • Such a hydraulic system known for example from US-A-4024710, has two hydraulic pumps with variable delivery quantities (variable displacement pumps), the displacement of which is automatically controlled as a function of the requirements of several hydraulic functions, represented by excess oil flows which are determined for the various functions Control valves originate.
  • spool valves with an open center position are mostly used for function control for excess valves.
  • the control spools are closed in the middle position and block the oil flow coming from the pump, resulting in an increase in pressure.
  • the oil flow is divided between the open center position and the work outlets, with the oil flow being directed through the open center position into the excess outlet while the oil return is returned to the reservoir.
  • Current sharing of this type makes it difficult for an operator to control the speed of a function to be performed since changes in the functional load must be compensated for by shifting the slide valve.
  • variable displacement hydraulic pumps that are automatically controlled to meet the fast demands of the system.
  • An example of a system with a variable displacement pump controlled in this way is disclosed in the aforementioned US-A-3,465,519.
  • This previously known system comprises a single variable pump, a multiplicity of functions to be carried out, for which control valves are provided, in which the excess flow of the last control valve is passed to a pressure-dependent displacement control in order to reduce the pump delivery rate as a function of the increasing excess current.
  • This system avoids connecting functions of the same priority in parallel to a common oil supply or, in situations where a second pump is required, supplying the maximum amount of oil that the functions could require.
  • the invention has for its object to add the excess flow of the second variable displacement pump to the flow of the first variable displacement pump when the pressure of the excess flow of the control valve originating from the second variable displacement pump is greater than the pressure of the excess flow of the control valve originating from the first variable displacement pump.
  • this object is achieved in that the first inlet of a pressure selection valve to the excess outlet of a privileged control valve fed by the second variable displacement pump, the second inlet of the pressure selection valve to the excess outlet of a downstream control valve fed by the first variable displacement pump, and to the pressure-dependent displacement control of the first
  • the variable displacement pump and the outlet of the pressure selection valve are connected to the pressure-dependent adjustment control of the second adjustment pump, that the pressure selection valve transmits the lower of the two inlet pressures to the adjustment control of the second adjustment pump, and that a bypass is provided with a bypass line which is the first inlet of the pressure selection valve connects to the inlet of the preferential control valve fed by the first variable displacement pump and has a one-way valve which prevents a flow of flow in the direction of the pressure selection valve.
  • FIG. 1 an exemplary embodiment of the invention is shown.
  • the drawing shows schematically a hydraulic control system for an excavator.
  • the hydraulic system as a whole is designated by the reference number 10 and comprises a plurality of control valves which are pressure-compensated, have an excess outlet and correspond essentially to the embodiment according to US-A-3718159, with the exception that some control valves only comprise a function control part which is provided with a supply part is plugged together, while the patented embodiment control parts open for three functions beard that are plugged together with a supply part.
  • the control system 10 comprises a support foot control valve 12, a control valve 14 for pivoting the cabin, and a right and a left travel control valve 16, 18, all of which are shown in a simplified representation as a block.
  • the support foot control valve 12 comprises a supply part 20 which is connected to a main boom, a bucket boom and a bucket control part 22, 24 and 26.
  • the supply part 20 has an inlet 28 and an excess outlet 30 and encloses an unillustrated pressure-compensated flow control valve, which divides the oil flow entering the inlet between the excess outlet and an outlet leading to the function control part in accordance with the arrangement of corresponding control slide valves in the control parts and the like Need a function to be controlled.
  • the main boom, bucket boom, and bucket control parts each have a pair of outlet ports 32, 34, 36, each for connecting the opposite ends of double-acting hydraulic cylinders.
  • the control valve 14 for pivoting the cabin has a supply part 38 which is plugged together with a swivel control part 40 and approximately corresponds to the supply part 20 of the control valve 12, that is to say also has an inlet 42 and an excess outlet 44.
  • the swing control part 40 includes a pair of outlet ports 45 for connecting the opposite outputs of a reversible swing motor.
  • the right and left travel control valves 16, 18 are of identical design and each include a supply part 46 and 48 and travel control valves 50, 52.
  • the supply parts 46, 48 have inlets 54, 56 and excess outlets 58, 60.
  • the travel control valves 50, 52 each include a pair of outlet ports 62, 64 to which the opposite ports of a reversible right and left travel motor can be connected.
  • a first and a second hydraulic pump 66, 68 with a variable delivery rate (variable pump) are used to apply oil to the control valves, which are each connected to a pressure-dependent adjustment control 70, 72, which increase the delivery rate of the pumps as a function of pressure drop signals.
  • variable displacement pump 66 is connected with its inlet to a pump sump 74 and with its outlet to the inlet 28 of the supply part 20 of the support foot control valve 12 via a flow line 76.
  • a first excess line 78 is connected at one end to the excess outlet 30 of the supply part 20 and at the other forked end to the inlet connections 54, 56 of the travel control valves 16, 18.
  • the excess outlets 58, 60 of the two travel control valves 16, 18 are connected via a second and a third excess line 80, 82 to the first inlet 84 and the second inlet 86 of a pressure selection valve 88, respectively.
  • the latter has an outlet 90 which is connected to the two inlets 84, 86 via a central valve bore 92.
  • a first and a second shut-off ball 94, 96 are arranged on both sides of the connection for the outlet 90 and act together with a first and second valve seat 98, 100 to prevent oil flow from the inlets 84, 86 to the outlet 90.
  • a reciprocating plunger 102 is arranged between the two shut-off balls 94, 96, which is longer than the distance between the two valve seats mentioned, so that only one of the two shut-off balls abuts against the valve seat assigned to them at the same time can (see also Figure 3 of US-A-3 863 449).
  • each pressure increase in the excess lines 80, 82 causes one of the two shut-off balls 94, 96 to be pressed against its valve seat and thereby to lift the other shut-off ball from its valve seat, so that a pressure drop in the lines 80, 82 is transmitted to the outlet 90 .
  • the latter is connected via a control line 104 to the pressure-dependent adjustment control 70 of the adjustment pump 66.
  • the pump 68 is connected with its inlet to a pump sump 74 and with its outlet via a flow line 106 to the inlet 42 of the control valve 14.
  • a fourth excess line 108 connects the excess outlet 44 to a first inlet 110 of a pressure selection valve 112, which is identical in construction to the pressure selection valve 88 described above.
  • the pressure selection valve 112 is connected to the control line 104 with its second inlet 114 and to the control line 104 with its outlet 116 pressure-dependent adjustment control 72 of the adjustment pump 68 is connected, specifically via a control line 118.
  • a central valve bore 120 connects the connections 110, 114 and 116.
  • first and second shut-off balls 122, 124 are provided, that cooperate with first and second valve seats 126 and 128. Between the shut-off balls 122, 124, a plunger 130 is slidably arranged back and forth in the valve bore 120, the length of which is dimensioned in such a way that the shut-off balls do not lie against their valve seats at the same time.
  • the pressure selection valve 112 therefore connects the respectively lower pressure, which exists in the control line 104 or the fourth excess line 108, to the control line 118 and thereby to the adjustment control 72 of the adjustment pump 68.
  • a bypass circuit comprises a bypass line 132 which is connected between the fourth excess line 108 and the flow line 76 and has a one-way valve 134 which only allows the oil flow in the direction from line 108 to line 76.
  • pressure selection valve 112 prevents oil flow from line 108 to the control line 118; the pressure in line 108 then opens valve 134 and thereby connects excess line 108 to flow line 76, so that the delivery volume generated by pump 68 is added to pump 66.
  • a pair of line compensators 136, 138 are provided in the circuit leading to the valve 12 or leading away from this valve.
  • the latter each include stepped cylindrical chambers 140, 142, of which the chamber 140 is connected to the flow line 76 with a small end via a line 144, while the chamber 142 is connected with a small end to the first excess line 78 via a line 146.
  • Both chambers 140, 142 are each connected with their large ends to one another and to the control line 104 via a forked line 148.
  • a small and a large piston 150 and 152 which are connected to one another via a piston rod 154, are displaceably arranged in the small and large sections of the chamber 140.
  • a pair of centering springs 156, 158 are provided which press the piston 152 into a central position in the large section of the chamber 140.
  • the chamber 142 also has a small and a large piston 160, 162, which are arranged such that they can be moved back and forth and are connected to one another via a piston rod 164.
  • a pair of centering springs 166, 168 are provided on the opposite sides of the large piston 162.
  • the excess current in the excess line 78 will decrease and thus reduce the pressure acting on the small piston 160 of the line compensator 138.
  • the piston 160 is then shifted to the left due to the unbalanced forces resulting from an increase in volume in the end of the large section of the chamber 142, which leads to a decrease in pressure in the bifurcated line 148 and, in turn, a pressure drop in the control line 104 .
  • the adjustment control 70 of the adjustment pump 66 will react to this pressure drop by increasing the pump delivery rate.
  • a solenoid actuated pressure relief valve 172 which has its inlet 174 connected to the flow line 76 via a portion of the bypass line 132 downstream of the one-way valve 134.
  • the pressure relief valve 172 is more commonly decayed Position shown in which it prevents a flow connection between the line 132 and the control line 104.
  • the pressure-limiting valve 172 is expediently actuated as a function of the drop in the output speed of the excavator drive motor to a predetermined minimum. Any known speed measurement circuit for said output speed can be used to energize the solenoid of the pressure relief valve 172 when the engine speed drops below a predetermined minimum.
  • the pressure relief valve 172 provides the connection to the line 132 and thus to the outlet of the pump 66 and the oil flow flowing through the one-way valve 134 into the control line 104.
  • the pressure in the adjustment control 70 is increased, which in turn reduces the delivery rate of the pump 66, which in turn takes a partial load on the drive motor and thereby prevents its drop in speed.
  • the control valves 12, 14, 16 and 18 divide the existing oil flow between the function performed in each case and the excess outlet of the valve. For example, the portion of the oil flow arriving at the support foot control valve 12, which is not required for the function, is passed on to the right and left travel control valves 16, 18 via the excess line 78. The proportion of this oil flow arriving at the control valves 16, 18, which is not required to actuate the driving functions, is passed on to the excess lines 80, 82.
  • the pressure selection valve 88 then operates as a function of the pressure increase in the lines 80, 82 in order to pass on pressure drops in the lines 80, 82 to the control line 104 and thus to the adjustment control 70 of the adjustment pump 66.
  • the adjustment control 70 operates in dependence on the pressure prevailing in the control line 104 in order to bring about a pump adjustment which only leads to a slightly larger amount of oil delivered by the pump 66, that is to say it is necessary to actuate the support foot and / or driving functions.
  • the pressure selection valve 112 operates depending on the liquid pressure in the control line 104 and in the over shot line 108 to connect the respectively lower pressure with the control line 118 and thereby with the adjusting device 72 of the variable pump 68. If the pressure in line 108 is greater than in line 132, the one-way valve 134 opens and thereby connects the oil flow of the excess line 108 to the oil quantity delivered by the variable pump 66. As a result, the pump 68 can temporarily support the pump 66 in supplying the support leg and driving functions with unusually high amounts of oil. As a result, the pump 66 manages with a smaller adjustment than would otherwise be the case.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mining & Mineral Resources (AREA)
  • Civil Engineering (AREA)
  • Structural Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Operation Control Of Excavators (AREA)
  • Lifting Devices For Agricultural Implements (AREA)
EP83109740A 1980-06-19 1981-06-11 Hydrauliksystem mit zwei Verstellpumpen, die durch Überschuss-Ölströme gesteuert werden Expired EP0105473B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US06/161,082 US4335577A (en) 1980-06-19 1980-06-19 Hydraulic system having variable displacement pumps controlled by power beyond flow
US161082 1980-06-19

Related Parent Applications (1)

Application Number Title Priority Date Filing Date
EP81104489.0 Division 1981-06-11

Publications (3)

Publication Number Publication Date
EP0105473A2 EP0105473A2 (de) 1984-04-18
EP0105473A3 EP0105473A3 (en) 1987-01-28
EP0105473B1 true EP0105473B1 (de) 1988-10-05

Family

ID=22579741

Family Applications (2)

Application Number Title Priority Date Filing Date
EP81104489A Expired EP0042547B1 (de) 1980-06-19 1981-06-11 Hydrauliksystem mit einer Verstellpumpe, die durch einen Überschuss-Ölstrom gesteuert wird
EP83109740A Expired EP0105473B1 (de) 1980-06-19 1981-06-11 Hydrauliksystem mit zwei Verstellpumpen, die durch Überschuss-Ölströme gesteuert werden

Family Applications Before (1)

Application Number Title Priority Date Filing Date
EP81104489A Expired EP0042547B1 (de) 1980-06-19 1981-06-11 Hydrauliksystem mit einer Verstellpumpe, die durch einen Überschuss-Ölstrom gesteuert wird

Country Status (11)

Country Link
US (1) US4335577A (es)
EP (2) EP0042547B1 (es)
JP (1) JPS5729801A (es)
AR (1) AR227546A1 (es)
AU (1) AU544947B2 (es)
BR (1) BR8103841A (es)
CA (1) CA1148446A (es)
DE (1) DE3167292D1 (es)
ES (1) ES8300959A1 (es)
MX (1) MX153742A (es)
ZA (1) ZA814125B (es)

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US4479349A (en) * 1981-11-19 1984-10-30 General Signal Corporation Hydraulic control system
DE3513452A1 (de) * 1985-04-15 1986-10-16 Mannesmann Rexroth GmbH, 8770 Lohr Hydrauliksystem fuer die versorgung einer hydrostatischen lenkung
DE4100988C2 (de) * 1991-01-15 2001-05-10 Linde Ag Hydraulisches Antriebssystem
US5540050A (en) * 1994-03-01 1996-07-30 Caterpillar Inc. Hydraulic system providing a positive actuator force
US5615553A (en) * 1995-06-28 1997-04-01 Case Corporation Hydraulic circuit with load sensing feature
US6672399B2 (en) 2001-10-19 2004-01-06 Deere & Company Hydraulic diverting system for utility vehicle
US6735908B2 (en) 2002-04-22 2004-05-18 Inscape Corporation Straddle bin
SE0402233L (sv) * 2004-07-26 2006-02-28 Volvo Constr Equip Holding Se Arrangemang och förfarande för styrning av ett arbetsfordon
DE102004048684A1 (de) * 2004-10-06 2006-04-13 Bosch Rexroth Ag Hydraulische Steueranordnung
US7401465B2 (en) * 2005-11-16 2008-07-22 Deere & Company Dual pump dual pressure hydraulic circuit
US7954317B2 (en) * 2007-12-21 2011-06-07 Deere & Company Hydraulic system
US9133837B2 (en) * 2008-04-24 2015-09-15 Caterpillar Inc. Method of controlling a hydraulic system
US8483916B2 (en) 2011-02-28 2013-07-09 Caterpillar Inc. Hydraulic control system implementing pump torque limiting
EP2765244A4 (en) 2011-10-07 2015-05-27 Volvo Constr Equip Ab PRIORITY CONTROL SYSTEM FOR CONSTRUCTION MACHINES
US9347200B2 (en) 2012-06-04 2016-05-24 Cnh Industrial America Llc Fluid control system for work vehicle
GB201419777D0 (en) 2014-11-06 2014-12-24 Agco Int Gmbh Hydraulic pressure supply system
CN106678099B (zh) * 2017-01-20 2018-06-22 徐州徐工施维英机械有限公司 混凝土施工机械的双动力液压系统和混凝土施工机械
DE102017005479A1 (de) * 2017-06-08 2018-12-13 Hydac Systems & Services Gmbh Druckversorgungsvorrichtung
DE102017126505B4 (de) 2017-11-10 2023-06-15 Syn Trac Gmbh Hydrauliksystem für ein Fahrzeug sowie ein Fahrzeug mit einem solchen Hydrauliksystem
JP6917871B2 (ja) * 2017-11-22 2021-08-11 キャタピラー エス エー アール エル 建設機械の油圧制御回路
CN113638809B (zh) * 2021-07-26 2022-11-18 中国联合重型燃气轮机技术有限公司 重型燃机的危急遮断装置

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Also Published As

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AU544947B2 (en) 1985-06-27
AR227546A1 (es) 1982-11-15
JPS5729801A (en) 1982-02-17
EP0042547A2 (de) 1981-12-30
BR8103841A (pt) 1982-03-09
ES503127A0 (es) 1982-11-01
MX153742A (es) 1986-12-30
ZA814125B (en) 1983-01-26
CA1148446A (en) 1983-06-21
EP0042547A3 (en) 1982-08-04
DE3167292D1 (en) 1985-01-03
EP0042547B1 (de) 1984-11-21
ES8300959A1 (es) 1982-11-01
US4335577A (en) 1982-06-22
JPH0213164B2 (es) 1990-04-03
AU7026181A (en) 1981-12-24
EP0105473A3 (en) 1987-01-28
EP0105473A2 (de) 1984-04-18

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