EP1243799A2 - Système hydraulique pour deux pompes à débits constants - Google Patents

Système hydraulique pour deux pompes à débits constants Download PDF

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Publication number
EP1243799A2
EP1243799A2 EP02005602A EP02005602A EP1243799A2 EP 1243799 A2 EP1243799 A2 EP 1243799A2 EP 02005602 A EP02005602 A EP 02005602A EP 02005602 A EP02005602 A EP 02005602A EP 1243799 A2 EP1243799 A2 EP 1243799A2
Authority
EP
European Patent Office
Prior art keywords
pressure
hydraulic system
connection
valve
module
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.)
Withdrawn
Application number
EP02005602A
Other languages
German (de)
English (en)
Other versions
EP1243799A3 (fr
Inventor
Gottfried Olbrich
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.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
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 Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP1243799A2 publication Critical patent/EP1243799A2/fr
Publication of EP1243799A3 publication Critical patent/EP1243799A3/fr
Withdrawn legal-status Critical Current

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Classifications

    • 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
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B23/00—Pumping installations or systems
    • F04B23/04—Combinations of two or more pumps
    • F04B23/06—Combinations of two or more pumps the pumps being all of reciprocating positive-displacement type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/08—Regulating by delivery 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
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B2013/002—Modular valves, i.e. consisting of an assembly of interchangeable components
    • F15B2013/006—Modular components with multiple uses, e.g. kits for either normally-open or normally-closed valves, interchangeable or reprogrammable manifolds
    • 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
    • F15B2211/30—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
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • F15B2211/3053—In combination with a pressure compensating valve
    • F15B2211/30535—In combination with a pressure compensating valve the pressure compensating valve is arranged between pressure source and directional control valve
    • 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
    • F15B2211/3111—Neutral or centre positions the pump port being closed in the centre position, e.g. so-called closed 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
    • F15B2211/40507—Flow control characterised by the type of flow control means or valve with constant 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
    • F15B2211/46—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
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50536—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using unloading valves controlling the supply pressure by diverting fluid 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
    • F15B2211/50—Pressure control
    • F15B2211/515—Pressure control characterised by the connections of the pressure control means in the circuit
    • F15B2211/5157—Pressure control characterised by the connections of the pressure control means in the circuit being connected to a pressure source and a 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
    • F15B2211/50—Pressure control
    • F15B2211/57—Control of a differential 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
    • F15B2211/60—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

Definitions

  • the invention is based on a hydraulic system according to the Preamble of claim 1 specified genus.
  • connection plate It is such a hydraulic system with one Connection plate known from EP 0 190 431 B1, in which several consumer groups with LS directional control valves Flow adjustment of two constant pumps with each a pressure compensator can be supplied with pressure medium.
  • the Connection plate itself takes only one of the first pumps assigned pressure compensator, while the second pump with the assigned second pressure compensator is arranged externally and is connected via lines; the two have Pressure compensators a different spring preload, so that they work with different control pressure differences to achieve a cascaded connection of the pumps.
  • Such Connection plates often have a complex construction anyway, which is why they are poorly suited for design variants. Further no information is given here, as in the hydraulic system an additional group of consumers, e.g. a brake valve, can be connected upstream. Would with such a facility upstream of such a valve and thus the sum of the pressure medium flows of both pumps received, this could lead to undesirable energy losses to lead.
  • This connection plate is also for the special one Use case provided and does not indicate any other application.
  • a hydraulic system is known from US Pat. No. 4,212,165 known, with several consumer groups of two Constant pumps are supplied with pressure medium, one first constant pump via a flow control valve privileged steering group with a constant current supplied while a residual current with the current of the second Constant pump is combined and several additional Consumer groups with LS directional control valves with pressure medium provided.
  • the second is the constant pump, which has a Check valve is coupled to the residual current side, one Pressure compensator assigned, and the additional A brake valve is connected upstream of consumer circuits.
  • This hydraulic system also builds relatively elaborate and can help with their flow power supply from flow control valve and pressure compensator to corresponding Lead energy losses, especially with regard to the upstream brake valve. Notes on a connection plate for flexible use in different There are no use cases here.
  • the hydraulic system according to the invention with the characteristic Features of claim 1 has the advantage that flexible with a relatively simple design different applications is applicable and also at an operation with two constant pumps with one each assigned pressure compensator an energy-saving way of working especially allowed if an upstream hydromodule, such as. in the form of a brake valve.
  • the Hydraulic system can be used if necessary without much effort an operation with two constant pumps on one with a constant pump.
  • the hydraulic system with your Connection plate is particularly suitable for applications for those with a subsequent addition of a single-pump concept using a two-pump concept two constant pumps with assigned pressure compensators should be transferred.
  • the Hydromodule is executed as an add-on module, so that it can be attached directly to the connection plate, expedient this can be achieved according to claim 3 if the interrupted inlet channel in an acreage Forms intermediate connections, which is a connection of the Enable add-on module in a simple way. Most of all will thereby a simple and compact design and a flexible handling in different applications favored. Appropriate training courses also result the remaining claims; with regard to the multitude of too fulfilling functions build the connection plate relatively space-saving and inexpensive. More beneficial Refinements result from the description and the Drawing.
  • FIG. 1 shows an inventive Hydraulic system with a connection plate in strong simplified representation
  • Figure 2 is an interchangeable Add-on module with integrated brake valve for attachment to the Connection plate according to Figure 1 and Figure 3, a second Embodiment of the hydraulic system with connection plate in simplified representation
  • Figure 4 shows a third Embodiment of the hydraulic system with the Connection plate separate hydromodule.
  • FIG. 1 shows a hydraulic system in schematic form 10, in which with 11 a first constant pump and with 12 a second constant pump are designated, the pressure medium suck a tank 13 and each via a first Delivery line 14 or a second delivery line 15 to one Promote connection plate 16.
  • connection plate 16 has one with the first feed line 14 connected inlet connection 17, of which an inlet channel 18 to a mouth 19 in one Flange surface 21 of the connecting plate 16 leads.
  • the Inlet channel 18 is the section up to Mouth 19 reaching the first delivery line 14.
  • This inlet channel 18 is in the connection plate 16 interrupted so that it was an upstream first Section 22 and a second downstream Section 23 forms.
  • the connection plate 16 has a Cultivation area 24 in which the end of the first Section 22 a first intermediate connection 25 and the second section 23 a second intermediate connection 26 form.
  • a hydromodule in the form of an add-on module 27 is attached, which has a connecting channel 28 in its interior, which the two intermediate connections 25 and 26 with each other connects, especially immediately and unthrottled.
  • the first pressure compensator 31 is assigned to the first constant pump 11 and has a four Path-controlling slide valve 35, which is also in a residual current channel 36 going out from the current regulator 32 which is connected downstream of the pressure compensator 31 also opens into the return line 34.
  • the Constant current of the current regulator 32 becomes the additional control valve 33 supplied that in unspecified Way is mechanically actuated.
  • the second, downstream section 23 is furthermore via a branch channel 37 with a second connection 40 in Connection to which the second delivery line 15 is connected is.
  • each Directional control valve 45, 46 has a neutral position 0, two Working positions 1 and 2 and a free position F on, with one in each of working positions 1 and 2 Measuring throttle 47 is effective.
  • the respective load pressures of the Consumers are in the conventional manner in the Directional control valves 45, 46 downstream of the measuring throttle 47 tapped and with control lines 48, 49 with Pressure selection valves in the form of shuttle valves 51 in Control circuit 52 selected and returned so that each the greatest prevailing load pressure over the first Control line 39 on the spring side 38 on the first Pressure compensator 31 takes effect.
  • the two directional control valves 45 and 46 are on one Supply channel 53 connected to the mouth 19 in the flange surface 21 communicates and which of the End plate 44 is shut off. Furthermore, both are directional valves 45, 46 crossed by a return channel 54, which also the Terminal plate 16 penetrates and with the return line 34th Has connection.
  • the via the second delivery line 15 in the connection plate 16 promoting second constant pump 12 is by a Check valve 57 in the delivery line 15 from the first Constant pump 11 decoupled. From the delivery line 15 in The area between pump 12 and check valve 57 branches a bypass line 58 to the tank 13, into which a second pressure compensator 59 is connected, that of the second Constant pump 12 is assigned.
  • a control slide 61 second pressure compensator 59 is on one side of a second measuring spring 62 and via a fifth control line 63 acted upon by the maximum load pressure while on the other side of the second control slide 61 the pressure in the delivery line 15 via a sixth control line 64 takes effect.
  • the fifth control line 63 is in the Control circuit 52 performed that on the spring sides of the two Pressure compensators 31 and 59 always have the same pressure.
  • the sixth control line 64 takes the pressure from the second Delivery line 15 downstream from the check valve 57.
  • the second pressure compensator 59 is a two-way, two-position valve performed; her second also shows Spring 62 has a lower preload than the first Spring 38 of the first pressure compensator 31. So can for example the first pressure compensator 31 with a Control pressure difference from 10 to 12 bar work while the second pressure compensator 59 to a control pressure difference of 8.5 is set to 9.5 bar, so that a total Cascade-like connection of the pressure medium flows takes place.
  • a Pressure relief valve 65 provided that as direct controlled valve from the pressure in the second delivery line 15 is applied.
  • FIG. 2 shows a second hydromodule in the form of a Add-on module 66, which instead of the first add-on module 27 the mounting surface 24 of the connection plate 16 is attachable.
  • the second add-on module 66 has a simplified inside Hydraulic pilot-controlled trailer brake valve shown 67 on how it is principally from the beginning mentioned prior art is already known.
  • the second Add-on module 66 has 68 connections in its mounting surface on to the intermediate connections 25 and 26 and to Drain channel 56 are arranged appropriately.
  • the first directional valve 45 If the first directional valve 45 is now actuated, the load pressure signal tapped downstream of the measuring throttle 47 the first pressure compensator 31 activated, which causes the pressure the first constant pump 11 throttled to the working level and the desired oil flow to the associated consumer ascribes.
  • the second constant pump 12 operates for the time being in neutral circulation since they are controlled by the check valve 57 from the first constant pump 11 is decoupled and the second Pressure compensator 59 with one compared to the first pressure compensator 31 lower control pressure difference works.
  • the maximum pressure in the hydraulic system 10 can be mastered by a single pressure relief valve 65, which is acted upon by the pressure in the second delivery line 15 and that as a directly controlled valve directly to the tank 13 relieved.
  • This cascade connection of the pressure medium flow second constant pump 12 can also be achieved when instead of the first directional valve 45, the second directional valve 46 or both directional control valves can be operated together. at joint actuation of both directional control valves 45, 46 is always the largest load pressure is selected via the control circuit 52 and forwarded to control both pressure compensators 31 and 59.
  • the hydraulic system 10 according to FIG upstream brake valve 67 are operated, so the first add-on module 27 removed from the connection plate 16 and for this, the second add-on module 66 is flanged. That’s it Brake valve 67 in the inlet channel 18, the directional valves 45 and 46 upstream.
  • This arrangement of the second add-on module 66 allows an energy-saving way of working.
  • the Pressure medium flow of the first constant pump 11 over the Brake valve 67 to the first pressure compensator 31 or to the Directional control valves 45, 46 are guided so that the Flow resistance of the brake valve 67 is relatively low is held.
  • the pressure medium flow of the second Constant pump 12 can, however, regardless of Flow resistance of the brake valve 67 on the Delivery line 15 and the second connection 40 unthrottled in the inlet channel 18 are fed; the second add-on module 66 therefore does not cause pressure losses in the second Pressure medium flow of the second constant pump 12, so that too with a total flow of both pumps to the directional control valves 45 or 46 overall the pressure fluid losses remain low.
  • connection plate 16 also has the advantage that it has a high connection flexibility because it instead of the concept shown with two constant pumps 11 and 12 can also be used if only a single pump 11 for the pressure medium supply to the assigned consumers is used.
  • the connection plate 16 With such a one-pump concept the connected via the second delivery line is omitted Constant pump 12 with assigned pressure compensator 59, the Second connection 40 shut off by a screw plug becomes. Accordingly, the fifth control line 63 is also on Output in the connection plate 16 blocked.
  • This one-pump concept is both with the first add-on module 27 also with the second add-on module 66 with the brake valve 67 feasible.
  • the connection plate 16 can thus without appreciable increase in their complexity as a result of the first Pressure compensator 31 in a variety of applications be used, especially when operating with two Constant pumps achieve an energy-saving way of working leaves.
  • the functions of the second pressure compensator 59, the Check valve 57 and the pressure relief 65 can be advantageously in a common housing accommodate that is assembled with the pump 12.
  • the pressure compensator 59 can be expediently arrange easily in a cover of the pump housing.
  • the two can also Constant pumps 11 and 12 as a tandem pump assembly are carried out, for example, the Main pressure relief valve 65 in the pump cover of one Constant pump and the second pressure compensator 59 immediately on Pressure connection of the second constant pump 12 directly is flanged on.
  • FIG. 3 shows a second in a highly simplified form Embodiment of a second hydraulic system 70 with a Connection plate 71, which differs from that of Figure 1 like follows differs, being the same for the same components Reference numerals are used.
  • the second Connection plate 71 is now the inlet port 17 on the Front 72 arranged so that it is opposite to Mouth 19 lies in the flange surface 21.
  • the first Pressure compensator 31 is designed as a 2/2 control valve here the connection of an additional control valve 33 is omitted. in the remaining is clearly recognizable here that the control slide both pressure balances 31 and 59 of the same pressure difference are acted upon. Operation of hydraulic system 70 corresponds to that of the first hydraulic system 16 according to FIG. 1.
  • FIG. 4 shows a third in a simplified form Hydraulic system 80, which is different from the second hydraulic system 70 as shown in Fig. 3 differs as follows, being the same Components with the same reference numerals are used.
  • the third hydraulic system 80 has a connecting plate 81, in which the inlet channel 18 is not interrupted and thus forms no intermediate connections; the hydromodule 82 that here is designed as a brake valve, is upstream of the Connection plate 81 switched into the first delivery line 14 and not attached to the connection plate 81.
  • the mode of operation of the third hydraulic system 80 corresponds analogous to that of the first hydraulic system 10 with the Brake valve 67 as add-on module 66; through the upstream Brake valves in the hydraulic module 82 are in the hydraulic system 80 the same energy savings possible.
  • the embodiments shown are Changes possible without the spirit of the invention departing. So the second pressure compensator 59 can also be used as run a 3/2 control valve that goes directly into the second Delivery line 15 is switched.
  • directly controlled pressure relief valve 65 can also be a pilot operated pressure limitation are used, in which the Control slide of the second pressure compensator 59 as the main slide serves for the printing function.
  • the selection and forwarding the maximum load pressure can also be with a control circuit take place instead of the shuttle valves with simple Check valves work as they do as well Pressure selection valves are known.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Fluid-Pressure Circuits (AREA)
EP02005602A 2001-03-22 2002-03-12 Système hydraulique pour deux pompes à débits constants Withdrawn EP1243799A3 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE2001114042 DE10114042B4 (de) 2001-03-22 2001-03-22 Hydraulikanlage für zwei Konstantpumpen
DE10114042 2001-03-22

Publications (2)

Publication Number Publication Date
EP1243799A2 true EP1243799A2 (fr) 2002-09-25
EP1243799A3 EP1243799A3 (fr) 2004-03-17

Family

ID=7678563

Family Applications (1)

Application Number Title Priority Date Filing Date
EP02005602A Withdrawn EP1243799A3 (fr) 2001-03-22 2002-03-12 Système hydraulique pour deux pompes à débits constants

Country Status (2)

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EP (1) EP1243799A3 (fr)
DE (1) DE10114042B4 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2406618A (en) * 2003-10-01 2005-04-06 Husco Int Inc Pump unloading arrangement
CN104192709A (zh) * 2014-09-22 2014-12-10 徐州重型机械有限公司 一种起重机及其多路阀液压系统
WO2015055276A1 (fr) * 2013-10-15 2015-04-23 Hydac Filtertechnik Gmbh Dispositif de commande
CN114233601A (zh) * 2021-12-17 2022-03-25 中国船舶重工集团公司第七一五研究所 一种应用多泵组冗余控制策略的节能液压系统

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4212165A (en) 1978-02-25 1980-07-15 Robert Bosch Gmbh Hydraulic control arrangement
EP0190431B1 (fr) 1985-02-02 1989-03-08 Robert Bosch Gmbh Système hydraulique

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3434394B2 (ja) * 1995-07-11 2003-08-04 日立建機株式会社 建設機械の制御回路
DE19603899A1 (de) * 1996-02-03 1997-08-07 Rexroth Mannesmann Gmbh Hydraulische Steuervorrichtung zur Druckmittelversorgung mehrerer hydraulischer Verbraucher

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4212165A (en) 1978-02-25 1980-07-15 Robert Bosch Gmbh Hydraulic control arrangement
EP0190431B1 (fr) 1985-02-02 1989-03-08 Robert Bosch Gmbh Système hydraulique

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2406618A (en) * 2003-10-01 2005-04-06 Husco Int Inc Pump unloading arrangement
GB2406618B (en) * 2003-10-01 2007-04-11 Husco Int Inc Power conserving hydraulic pump bypass compensator circuit
WO2015055276A1 (fr) * 2013-10-15 2015-04-23 Hydac Filtertechnik Gmbh Dispositif de commande
US10119558B2 (en) 2013-10-15 2018-11-06 Hydac Filtertechnik Gmbh Control apparatus
CN104192709A (zh) * 2014-09-22 2014-12-10 徐州重型机械有限公司 一种起重机及其多路阀液压系统
CN114233601A (zh) * 2021-12-17 2022-03-25 中国船舶重工集团公司第七一五研究所 一种应用多泵组冗余控制策略的节能液压系统
CN114233601B (zh) * 2021-12-17 2023-06-13 中国船舶重工集团公司第七一五研究所 一种应用多泵组冗余控制策略的节能液压系统

Also Published As

Publication number Publication date
DE10114042A1 (de) 2002-09-26
DE10114042B4 (de) 2008-04-10
EP1243799A3 (fr) 2004-03-17

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