EP0042547B1 - Circuit hydraulique comprenant une pompe à débit variable commandée par l'excédent du débit - Google Patents
Circuit hydraulique comprenant une pompe à débit variable commandée par l'excédent du débit Download PDFInfo
- Publication number
- EP0042547B1 EP0042547B1 EP81104489A EP81104489A EP0042547B1 EP 0042547 B1 EP0042547 B1 EP 0042547B1 EP 81104489 A EP81104489 A EP 81104489A EP 81104489 A EP81104489 A EP 81104489A EP 0042547 B1 EP0042547 B1 EP 0042547B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- valve
- pump
- port
- pressure
- control valve
- 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
Links
- 238000006073 displacement reaction Methods 0.000 claims description 27
- 230000007423 decrease Effects 0.000 claims description 3
- 239000012530 fluid Substances 0.000 claims 7
- 230000003247 decreasing effect Effects 0.000 claims 1
- 230000001419 dependent effect Effects 0.000 description 8
- 230000002441 reversible effect Effects 0.000 description 2
- 238000010276 construction Methods 0.000 description 1
- 230000005284 excitation Effects 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 238000005259 measurement Methods 0.000 description 1
Images
Classifications
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- 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
- 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 thus block the oil flow coming from the pump, so that there is an increase in pressure.
- the oil flow is divided between the open center position and the work outlets, 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-3465519.
- 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 variable control in order to reduce the pump delivery rate as a function of the increasing excess current.
- This system avoids connecting functions of equal priority in parallel to a common oil supply, or in situations where a second pump is required, supply the maximum amount of oil that the functions could require.
- the invention has for its object to provide an adjustment control for a variable displacement pump in a hydraulic system of the type described at the outset, which is pressure-dependent on the pressure drop at excess outlets of two control valves for optionally controlling a pair of functions connected in parallel.
- 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-3 718 159, with the exception that some control valves comprise only one function control part which is associated with a supply part is plugged together, while the patented embodiment discloses control parts for three functions which 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 plugged together with 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 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 corresponds approximately to the supply part 20 of the control valve 12, ie also has an inlet 42 and an excess outlet 44.
- the swing control member 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 identical and each comprise 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 feed 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 drive 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 associated valve seat at the same time can (see also Fig. 3 of US-A-3863449).
- any 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 to the pressure-dependent adjustment control 70 via a control line 104 the variable displacement pump 66 connected.
- 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 has its second inlet 114 to the control line 104 and its outlet 116 to the pressure-dependent adjustment control 72 of the adjustment pump 68 connected 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, which cooperate with first and second valve seats 126 and 128. Between the shut-off balls 122, 124, a plunger 130 is displaceably arranged back and forth in the valve bore 120, the length of which is dimensioned such that a simultaneous abutment of the shut-off balls on their valve seats precludes.
- 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 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 that of 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 comprise 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 each displaceably arranged in the small and large sections of the chamber 140.
- a pair of centering springs 156, 158 which urge the piston 152 to a central position in the large portion 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 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 forked line 148 and in turn to a drop in pressure 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.
- the outlet 170 of an electromagnetically pilot-controlled pressure relief valve 172 which is connected with its inlet 174 to the feed line 76 via a section of the bypass line 132 downstream of the one-way valve 134.
- the pressure relief valve 172 is shown in the usual dropped position , in which it prevents a flow connection between the line 132 and the control line 104.
- the pressure relief valve 172 is expediently actuated as a function of the drop in the output speed of the excavator to a predetermined minimum. Any known speed measurement circuit can be used to measure the output speed of the machine and energize the spool of the pressure relief valve 172 at the predetermined minimum speed.
- the pressure relief valve 172 connects to the Lei device 132 and thus with the output 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 off the machine and thereby prevents its speed from falling.
- the control valves 12, 14, 16 and 18 divide existing oil flow between the function performed in each case and the excess outlet of the valve. So z. B. the portion of the incoming at the support foot control valve 12 oil flow, which is not required for the function, passed on to the right and left travel control valve 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 than is necessary to actuate the support foot and / or driving functions.
- the pressure selection valve 112 operates in dependence on the liquid pressure in the control line 104 and in the excess line 108 in order to connect the respectively lower pressure to the control line 118 and thereby to the adjusting device 72 of the variable pump 68. If the pressure in line 108 is greater than that 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.
- bypass circuit and the pressure selection valve 112 can be dispensed with; the excess line 108 is then connected directly to the adjusting device 72.
Landscapes
- 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)
Claims (5)
caractérisé par les particularités suivantes:
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE8383109740T DE3176898D1 (en) | 1980-06-19 | 1981-06-11 | Hydraulic circuit with two variable flow pumps controlled by excess flow |
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 Child Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP83109740.7 Division-Into | 1981-06-11 |
Publications (3)
Publication Number | Publication Date |
---|---|
EP0042547A2 EP0042547A2 (fr) | 1981-12-30 |
EP0042547A3 EP0042547A3 (en) | 1982-08-04 |
EP0042547B1 true EP0042547B1 (fr) | 1984-11-21 |
Family
ID=22579741
Family Applications (2)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP81104489A Expired EP0042547B1 (fr) | 1980-06-19 | 1981-06-11 | Circuit hydraulique comprenant une pompe à débit variable commandée par l'excédent du débit |
EP83109740A Expired EP0105473B1 (fr) | 1980-06-19 | 1981-06-11 | Circuit hydraulique comprenant deux pompes à débit variable commandées par l'excédent du débit |
Family Applications After (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP83109740A Expired EP0105473B1 (fr) | 1980-06-19 | 1981-06-11 | Circuit hydraulique comprenant deux pompes à débit variable commandées par l'excédent du débit |
Country Status (11)
Country | Link |
---|---|
US (1) | US4335577A (fr) |
EP (2) | EP0042547B1 (fr) |
JP (1) | JPS5729801A (fr) |
AR (1) | AR227546A1 (fr) |
AU (1) | AU544947B2 (fr) |
BR (1) | BR8103841A (fr) |
CA (1) | CA1148446A (fr) |
DE (1) | DE3167292D1 (fr) |
ES (1) | ES8300959A1 (fr) |
MX (1) | MX153742A (fr) |
ZA (1) | ZA814125B (fr) |
Families Citing this family (21)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
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 |
KR20140074324A (ko) | 2011-10-07 | 2014-06-17 | 볼보 컨스트럭션 이큅먼트 에이비 | 건설기계용 우선 제어시스템 |
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 |
Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3455210A (en) * | 1966-10-26 | 1969-07-15 | Eaton Yale & Towne | Adjustable,metered,directional flow control arrangement |
US3465519A (en) * | 1967-08-18 | 1969-09-09 | Webster Electric Co Inc | Hydraulic flow controlling apparatus |
US3718159A (en) * | 1971-01-20 | 1973-02-27 | Hydraulic Industries | Control valve |
US3863449A (en) * | 1973-08-27 | 1975-02-04 | Trw Inc | Hydraulic motor fluid flow circuitry |
Family Cites Families (15)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2716995A (en) * | 1950-09-23 | 1955-09-06 | Gen Motors Corp | Valve for reversible fluid pump |
US2892311A (en) * | 1958-01-08 | 1959-06-30 | Deere & Co | Hydraulic apparatus |
LU52175A1 (fr) * | 1965-10-21 | 1966-12-19 | ||
US3760689A (en) * | 1972-02-24 | 1973-09-25 | Harnischfeger Corp | Control system for automatically sequencing operation of a plurality of hydraulic pumps for supplying a plurality of hydraulic actuators |
DE2435602C3 (de) * | 1974-07-24 | 1980-06-12 | International Harvester Company Mbh, 4040 Neuss | Selbsttätige Steuereinrichtung zur Verteilung des Druckmittels auf zwei Hydrauliksysteme |
US3987623A (en) * | 1976-01-23 | 1976-10-26 | Caterpillar Tractor Co. | Controlled priority fluid system of a crawler type vehicle |
US3998053A (en) * | 1976-03-15 | 1976-12-21 | Caterpillar Tractor Co. | Three-pump - three-circuit fluid system of a work vehicle having controlled fluid-combining means |
US3991571A (en) * | 1976-03-15 | 1976-11-16 | Caterpillar Tractor Co. | Fluid system of a work vehicle having fluid combining means and signal combining means |
US4024710A (en) * | 1976-03-25 | 1977-05-24 | Koehring Company | Load sensing hydraulic circuit having power matching means |
US4023364A (en) * | 1976-07-19 | 1977-05-17 | Caterpillar Tractor Co. | Swing flow supplemental travel for an excavator |
US4044786A (en) * | 1976-07-26 | 1977-08-30 | Eaton Corporation | Load sensing steering system with dual power source |
US4055046A (en) * | 1976-12-22 | 1977-10-25 | Caterpillar Tractor Co. | Control system having override for fluid operated work elements |
US4116001A (en) * | 1977-08-01 | 1978-09-26 | International Harvester Company | Simplified load sensitive hydraulic system for use with a vehicle steering system |
US4286502A (en) * | 1979-10-15 | 1981-09-01 | Caterpillar Tractor Co. | Hydraulic load lifting system with automatic blocking valve |
JPH0155322B2 (fr) * | 1980-04-07 | 1989-11-24 | Caterpillar Inc |
-
1980
- 1980-06-19 US US06/161,082 patent/US4335577A/en not_active Expired - Lifetime
-
1981
- 1981-05-08 AU AU70261/81A patent/AU544947B2/en not_active Ceased
- 1981-05-13 MX MX187290A patent/MX153742A/es unknown
- 1981-05-27 CA CA000378456A patent/CA1148446A/fr not_active Expired
- 1981-06-11 EP EP81104489A patent/EP0042547B1/fr not_active Expired
- 1981-06-11 DE DE8181104489T patent/DE3167292D1/de not_active Expired
- 1981-06-11 EP EP83109740A patent/EP0105473B1/fr not_active Expired
- 1981-06-17 BR BR8103841A patent/BR8103841A/pt unknown
- 1981-06-17 ES ES503127A patent/ES8300959A1/es not_active Expired
- 1981-06-18 ZA ZA814125A patent/ZA814125B/xx unknown
- 1981-06-19 AR AR285788A patent/AR227546A1/es active
- 1981-06-19 JP JP9517981A patent/JPS5729801A/ja active Granted
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3455210A (en) * | 1966-10-26 | 1969-07-15 | Eaton Yale & Towne | Adjustable,metered,directional flow control arrangement |
US3465519A (en) * | 1967-08-18 | 1969-09-09 | Webster Electric Co Inc | Hydraulic flow controlling apparatus |
US3718159A (en) * | 1971-01-20 | 1973-02-27 | Hydraulic Industries | Control valve |
US3863449A (en) * | 1973-08-27 | 1975-02-04 | Trw Inc | Hydraulic motor fluid flow circuitry |
Non-Patent Citations (1)
Title |
---|
ÖLHYDRAULIK UND PNEUMATIK, Band 18, Nr. 2, Februar 1974, Seiten 103-109, Mainz, DE. F. BRÜCKLE: "Hydraulische Antriebe in Baggern",Seiten 106-107,Abschnitt 2.5;Figur 11 * |
Also Published As
Publication number | Publication date |
---|---|
US4335577A (en) | 1982-06-22 |
DE3167292D1 (en) | 1985-01-03 |
BR8103841A (pt) | 1982-03-09 |
ZA814125B (en) | 1983-01-26 |
AR227546A1 (es) | 1982-11-15 |
MX153742A (es) | 1986-12-30 |
ES503127A0 (es) | 1982-11-01 |
EP0042547A3 (en) | 1982-08-04 |
ES8300959A1 (es) | 1982-11-01 |
EP0105473B1 (fr) | 1988-10-05 |
EP0105473A2 (fr) | 1984-04-18 |
EP0105473A3 (en) | 1987-01-28 |
CA1148446A (fr) | 1983-06-21 |
AU544947B2 (en) | 1985-06-27 |
AU7026181A (en) | 1981-12-24 |
JPS5729801A (en) | 1982-02-17 |
EP0042547A2 (fr) | 1981-12-30 |
JPH0213164B2 (fr) | 1990-04-03 |
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