EP2927371A1 - Circuit - Google Patents

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Publication number
EP2927371A1
EP2927371A1 EP15000632.8A EP15000632A EP2927371A1 EP 2927371 A1 EP2927371 A1 EP 2927371A1 EP 15000632 A EP15000632 A EP 15000632A EP 2927371 A1 EP2927371 A1 EP 2927371A1
Authority
EP
European Patent Office
Prior art keywords
valve
pressure
hydraulic
circuit arrangement
load
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.)
Granted
Application number
EP15000632.8A
Other languages
German (de)
English (en)
Other versions
EP2927371B1 (fr
Inventor
Hermann Albert
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.)
Hydac Fluidtechnik GmbH
Original Assignee
Hydac Fluidtechnik 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 Hydac Fluidtechnik GmbH filed Critical Hydac Fluidtechnik GmbH
Publication of EP2927371A1 publication Critical patent/EP2927371A1/fr
Application granted granted Critical
Publication of EP2927371B1 publication Critical patent/EP2927371B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
    • F15B11/042—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the feed line, i.e. "meter in"
    • F15B11/0423—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the feed line, i.e. "meter in" by controlling pump output or bypass, other than to maintain constant speed
    • E—FIXED CONSTRUCTIONS
    • E01—CONSTRUCTION OF ROADS, RAILWAYS, OR BRIDGES
    • E01C—CONSTRUCTION OF, OR SURFACES FOR, ROADS, SPORTS GROUNDS, OR THE LIKE; MACHINES OR AUXILIARY TOOLS FOR CONSTRUCTION OR REPAIR
    • E01C19/00—Machines, tools or auxiliary devices for preparing or distributing paving materials, for working the placed materials, or for forming, consolidating, or finishing the paving
    • E01C19/12—Machines, tools or auxiliary devices for preparing or distributing paving materials, for working the placed materials, or for forming, consolidating, or finishing the paving for distributing granular or liquid materials
    • E01C19/20—Apparatus for distributing, e.g. spreading, granular or pulverulent materials, e.g. sand, gravel, salt, dry binders
    • E01C19/201—Apparatus for distributing, e.g. spreading, granular or pulverulent materials, e.g. sand, gravel, salt, dry binders with driven loosening, discharging or spreading parts, e.g. power-driven, drive derived from road-wheels
    • 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
    • F15B2211/40—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
    • F15B2211/405—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
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40553—Flow control characterised by the type of flow control means or valve with pressure compensating valves
    • F15B2211/40561—Flow control characterised by the type of flow control means or valve with pressure compensating valves the pressure compensating valve arranged upstream of the flow control 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
    • F15B2211/40—Flow control
    • F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
    • F15B2211/41509—Flow control characterised by the connections of the flow control means in the circuit being connected to a pressure source and a 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
    • F15B2211/40—Flow control
    • F15B2211/42—Flow control characterised by the type of actuation
    • F15B2211/428—Flow control characterised by the type of actuation actuated by fluid 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
    • F15B2211/40—Flow control
    • F15B2211/455—Control of flow in the feed line, i.e. meter-in 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
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7058—Rotary output members
    • 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
    • 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
    • F15B2211/7114—Multiple output members, e.g. multiple hydraulic motors or cylinders with direct connection between the chambers of different actuators
    • F15B2211/7121—Multiple output members, e.g. multiple hydraulic motors or cylinders with direct connection between the chambers of different actuators the chambers being connected in series
    • 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
    • F15B2211/781—Control of multiple output members one or more output members having priority

Definitions

  • the invention relates to a circuit arrangement for controlling hydraulic consumers, which are connected in series and which are supplied for their operation by at least one load-sensing control pump via a pressure supply port, each operable by means of an assignable valve means between a standby mode and a working mode and vice versa is, which is arranged between the pressure supply port and a supply line of at least one hydraulic consumer and having an actuatable valve.
  • Mobile working machines such as so-called Winterdienststreuer be built with a variety of carrier vehicles as a means of transport.
  • Such work machines regularly have different controllable and operable hydraulic consumers, for example in the form of hydraulically driven constant motors.
  • a consumer with his hydraulic motor can serve to drive a transport screw, for the purpose of transporting road salt; another consumer with a corresponding engine can then include a spreading plate for distributing the road salt on the road and another consumer with controllable motor to drive a feed pump to bring, for example, a liquid road salt mixture of winter maintenance spreader on the road.
  • the LS pump is regularly operated as a fixed displacement pump with an upstream throttle valve. By closing the throttle valve, the LS pump can be switched to standby mode, with the upcoming load sensing pressure in the fluid flow direction behind the throttle valve ultimately representing the control fluid flow for the actuatable LS pump.
  • the pump flow itself is determined by the free cross section of the throttle valve.
  • the present invention seeks to ensure the known solutions, while maintaining their advantages, namely a meaningful, functionally reliable operation, to further improve that achieved by both the manufacturing effort and on the part of the control effort to be operated a reduction is.
  • the valve is exclusively hydraulically controlled, that at least one actuation signal for the pending actuation of a load tap originates at least at one of the hydraulic consumers, and that a metering orifice between the valve and at least one hydraulic consumer in the can be assigned assignable supply line, the circuit arrangement can switch hydraulically between an active operation and a standby mode automatically back and forth without the use of electrical control.
  • the hydraulic control is without electrical components and is therefore very reliable in use. Also can be dispensed with a complicated, costly electronic control structure.
  • a metering orifice is switched on and off by a hydraulically actuated directional control valve.
  • the switching signal to this comes preferably from a Last horrabgriff to the individual, connected to the circuit hydraulic consumers.
  • a low standby volume flow continues to flow. This is controlled by a second aperture which always remains open within the circuitry.
  • the load sensing control line is depressurized and the directional control valve is closed.
  • the pump only promotes the volume flow through the small aperture is requested.
  • the pressure is determined by the load-sensing pressure difference of the pump.
  • the Fig. 1 shows a circuit arrangement for driving three hydraulic consumers 10, 12, 14 in the form of hydraulic constant - speed motors, which, as shown in the Fig. 1 are connected in series and which are supplied for their operation by means of a constant displacement pump 16 via a pressure supply port P from a storage reservoir, such as a hydraulic tank 15, with predetermined fluid pressure.
  • a constant displacement pump 16 via a pressure supply port P from a storage reservoir, such as a hydraulic tank 15, with predetermined fluid pressure.
  • outer frame 18 relates to the actual area of the circuit arrangement, wherein the respective consumer 10, 12, 14 via supply lines A1, A2 and A3 and return lines B1, B2, B3 to the circuit arrangement to be described later fluid or media leading connected.
  • the respective circuit arrangements shown in the figures are intended to be used in particular for winter service gritting vehicles, wherein the first load 10 with its hydraulic motor can serve to drive a transport screw not shown for the purpose of transporting Road salt.
  • the second consumer 12 may include with its engine a spreading plate for distributing a road salt on the road and the last consumer 14 with its controllable constant motor can drive a feed pump used to bring, for example, a liquid road salt mixture of winter maintenance spreader on the road.
  • a feed pump used to bring, for example, a liquid road salt mixture of winter maintenance spreader on the road.
  • the graphic reproduction of transport screw, spreading plate and application pump was dispensed with.
  • the respective circuit arrangement according to Fig. 1 to 3 can also be used for other purposes as Winterdienststreuer use, but in which the hydraulic consumers 10, 12, 14 are always arranged in the series connection shown to each other.
  • each pressure compensator 20 is connected, wherein each pressure compensator 20 as shown in the Fig. 1 on the input and output side is connected to a common supply line 22.
  • the input C1 of the common supply line 22 opens into the supply line A1 and the output C2 of the supply line 22 opens into the last return line B3 of the indicated series circuit.
  • the return line B3 discharges from the last consumer 14 into the tank connection T.
  • an adjustable and electro-magnetically actuated pressure limiting valve 24 is connected, for example, set to a pressure of 200 bar to secure the respective hydraulic circuit in the case of over-supply, in particular in the form of an overpressure, from the pump side Fluid path via a connecting line 26 between the pressure supply port P and tank connection T produces.
  • control lines 28, 30, which are arranged on opposite sides each acting on the control piston of each pressure compensator 20, is always the inlet-side pressure in the supply lines A1, A2, A3 of each hydraulic consumer 10, 12, 14 and by means of a throttle or Aperture 32 throttled pressure in the form of a Lastabgriffs 34, which is arranged in the respective supply line A1, A2 and A3 behind a 2/2-way proportional directional control valve 36.
  • the pressure compensators 20 are constructed in the manner of a 2/2 proportional directional control valve concept.
  • the individual hydraulic consumers 10, 12, 14 connected in series with each other, so that each consumer 10, 12 or 14, the complete pump flow is available.
  • the constant displacement pump 16 In order to produce a reliable supply of the individual consumers 10, 12, 14, which are otherwise switchable due to the directional control valves 36 within the circuit and thus go into active operation, the constant displacement pump 16 must hold in a correspondingly high fluid with a predetermined pressure and should If the total volume is not consumed by the hydraulic consumers, the excess portion is given to the tank connection side T via the respective pressure compensator 20 then addressed.
  • a pertinent loss operation via the pressure compensators 20 is indeed reliable, but leads to energy losses, resulting in particular from the operation of the feed pump 16.
  • Fig. 2 proposed to provide an electrically controllable throttle valve 40, which is connected in the first supply line A1 between the pressure supply port P and the input C1 of the supply line 22 for the individual pressure compensators 20.
  • the throttle valve 40 In the direction of the Fig. 2 seen behind the throttle valve 40 in the manner of an electrically controllable 2/2-way proportional directional valve output side of the control pressure in the inlet line A1 tapped and via an LS control line 42 which is connected to a LS port of the valve assembly, for controlling the delivery volume forwarded to the corresponding control device of the LS pump 17.
  • the connected on the pressure supply side P LS pump 17 can be switched to the so-called. Standby operation, which is addressed by the addressed LS tap on the LS control line 42, the pump flow through the shared cross-section of the throttle valve 40 is determined.
  • valve 40 In the solution after the Fig. 3 is the corresponding valve 40 to the valve solution after the Fig. 2 designed as only hydraulically operated directional control valve, which in his in the Fig. 3 shown blocking position under the action of an energy storage in the form of a compression spring 41 is provided that there is no hydraulic control on the opposite control side of the valve 40.
  • the directional control valve 40 on its side facing away from the compression spring 41, opposite control side on an input for the LS control line 42, which receives its input pressure via another LS control line 44, the load tap 34 of each hydraulic consumer 10, 12, 14 coming on the LS control line 42 is opened with open check valve 43.
  • the directional control valve 40 is designed in the manner of a 2/2-way switching valve and, in the case of a corresponding hydraulic actuation via the LS control lines 42 and 44, the valve 40 is switched into its fluid-conducting passage position.
  • a metering orifice 46 is connected between the valve 40 and the entry point C1 of the supply line 22 in the first supply line A1, which preferably has a correspondingly large opening cross-section.
  • a correspondingly designed throttle can also occur.
  • a parallel branch 48 is connected to a further second orifice 50, which allows the flow of a low standby volume flow, which will be explained in more detail below.
  • the other LS control line 44 connected by means of a third orifice 52 or throttle in relieving manner to the tank side T of the circuit arrangement, for which the corresponding connection line of the third aperture 52 opens into the return line B3.
  • the volumetric flow demand is changed.
  • the metering orifice 46 is connected behind the directional control valve 40 and the flow of the orifice 46 can be controlled by the hydraulically actuated directional control valve 40, in particular switched on and off.
  • the actual switching signal for the hydraulic control of the directional control valve 40 comes from the respective Last réelleabgriff 34 in the supply lines A1, A2 and A3 to the individual hydraulic consumers 10, 12, 14.
  • a low standby volume flow is permitted, which is controlled via the second orifice 50, which always remains open with a predeterminable cross section.
  • the LS line 42, 44 is depressurized and the hydraulically controllable directional control valve 40 is closed.
  • the LS pump 17 promotes only the flow rate through the small aperture 50 is requested.
  • the pressure is determined by the necessary load sensing differential pressure of the pump 17.
  • the pressure in the LS control line 42, 44 increases because the standby volume flow now flows to the respectively assigned consumer.
  • the directional control valve 40 switches over and releases the large diaphragm 46.
  • the volumetric flow requirement rises to the pump 17, which then pivots controlled by the pressure in the load-sensing connection LS in order to provide the required operating volume flow for the consumers 10, 12, 14.
  • the functionality of the indicated series connection remains completely unaffected by the pertinent measure.
  • the system can then in turn be operated on a fixed displacement pump 16, as already shown. While with the solutions after the Fig. 1 and 2 In the prior art, the pressure relief valve 24 is electrically actuated, was in the solution after the Fig. 3 in turn selected an exclusively hydraulic solution that gets along with the hydraulic control pulse in the connecting line between the pressure supply port P and tank port T.

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  • Engineering & Computer Science (AREA)
  • Architecture (AREA)
  • Civil Engineering (AREA)
  • Structural Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
EP15000632.8A 2014-04-05 2015-03-05 Circuit Active EP2927371B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE201410004932 DE102014004932B3 (de) 2014-04-05 2014-04-05 Schaltungsanordnung

Publications (2)

Publication Number Publication Date
EP2927371A1 true EP2927371A1 (fr) 2015-10-07
EP2927371B1 EP2927371B1 (fr) 2017-10-25

Family

ID=52705917

Family Applications (1)

Application Number Title Priority Date Filing Date
EP15000632.8A Active EP2927371B1 (fr) 2014-04-05 2015-03-05 Circuit

Country Status (2)

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EP (1) EP2927371B1 (fr)
DE (1) DE102014004932B3 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10006334B2 (en) 2016-04-29 2018-06-26 Caterpillar Inc. Hydraulic driven fan system

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ITUB20159571A1 (it) * 2015-12-18 2017-06-18 Walvoil Spa Dispositivo valvolare idraulico a piu' sezioni di lavoro con sistema di controllo della pompa con linea di by-pass
US10626986B2 (en) * 2016-10-31 2020-04-21 Hydraforce, Inc. Hydraulic motor drive system for controlling high inertial load rotary components
DE102017004634A1 (de) 2017-05-15 2018-11-15 Hydac Systems & Services Gmbh Steuervorrichtung zum Versorgen mindestens eines hydraulischen Verbrauchers

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4322127A1 (de) * 1992-07-03 1994-01-05 Rexroth Sigma Hydraulische Schaltung zum Druckantrieb eines hydraulischen Verteilers des Typs mit offenem Zentrum
EP1711714B1 (fr) * 2004-02-05 2008-06-11 Hydac Fluidtechnik GmbH Ensemble circuit

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4322127A1 (de) * 1992-07-03 1994-01-05 Rexroth Sigma Hydraulische Schaltung zum Druckantrieb eines hydraulischen Verteilers des Typs mit offenem Zentrum
EP1711714B1 (fr) * 2004-02-05 2008-06-11 Hydac Fluidtechnik GmbH Ensemble circuit

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10006334B2 (en) 2016-04-29 2018-06-26 Caterpillar Inc. Hydraulic driven fan system

Also Published As

Publication number Publication date
DE102014004932B3 (de) 2015-05-13
EP2927371B1 (fr) 2017-10-25

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