EP2310692B1 - Régulation de débit - Google Patents

Régulation de débit Download PDF

Info

Publication number
EP2310692B1
EP2310692B1 EP09772437A EP09772437A EP2310692B1 EP 2310692 B1 EP2310692 B1 EP 2310692B1 EP 09772437 A EP09772437 A EP 09772437A EP 09772437 A EP09772437 A EP 09772437A EP 2310692 B1 EP2310692 B1 EP 2310692B1
Authority
EP
European Patent Office
Prior art keywords
oil
cooler
circuit
heat exchanger
bypass
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.)
Active
Application number
EP09772437A
Other languages
German (de)
English (en)
Other versions
EP2310692A1 (fr
Inventor
Richard Heindl
Andreas Brockmann
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.)
AGCO GmbH and Co
Original Assignee
AGCO GmbH 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 AGCO GmbH and Co filed Critical AGCO GmbH and Co
Publication of EP2310692A1 publication Critical patent/EP2310692A1/fr
Application granted granted Critical
Publication of EP2310692B1 publication Critical patent/EP2310692B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

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
    • F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
    • F15B21/04—Special measures taken in connection with the properties of the fluid
    • F15B21/042—Controlling the temperature of the fluid
    • F15B21/0423—Cooling
    • 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
    • F15B2211/41—Flow control characterised by the positions of the valve element
    • F15B2211/413—Flow control characterised by the positions of the valve element the positions being continuously variable, e.g. as realised by proportional 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
    • F15B2211/40—Flow control
    • F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
    • F15B2211/41581—Flow control characterised by the connections of the flow control means in the circuit being connected to an output member 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
    • F15B2211/40—Flow control
    • F15B2211/42—Flow control characterised by the type of actuation
    • F15B2211/426—Flow control characterised by the type of actuation electrically or electronically
    • 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
    • F15B2211/62—Cooling or heating 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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/6306—Electronic controllers using input signals representing a 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
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/6343—Electronic controllers using input signals representing a temperature
    • 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
    • F15B2211/665—Methods of control using electronic components
    • F15B2211/6654—Flow rate control

Definitions

  • the invention relates to a device for controlling the flow of oil through oil cooler.
  • the invention relates to such a device for use on vehicles, such as agricultural machines.
  • FIG. 1 by way of example shows a block diagram of working or transmission hydraulics, as are usual in mobile machines.
  • An oil tank I holds a volume of oil.
  • An oil-air cooler 4 is arranged in front of this.
  • This cooler 4 has a bypass valve 5 connected in parallel.
  • the actual circuit of the vehicle can vary greatly depending upon the scope of application and is simply represented by symbol 6.
  • An oil pump 7 with constant displacement is used for supplying the circuit 6.
  • Other pumps with constant or variable displacement can also be used in addition to this pump. If only one pump is used, usually this works with constant displacement.
  • a sensor 8 is provided for determining the dynamic pressure.
  • the bypass valve 5 connected in parallel has a spring tension of 5 bar for example.
  • valve 5 represents a simple and reliable means of protection for the cooler 4.
  • a disadvantage of this arrangement is that even at low oil temperatures oil always flows through the cooler 4.
  • the constant, actually unwanted, cooling of the oil at low temperatures is a side effect of this arrangement. It stems from the fact that oil warms up relatively slowly. Slow warming of the oil produces losses of efficiency and can also result in malfunction of valves or cavitation in pumps.
  • the disadvantages mentioned occur even if an oil-oil heat exchanger or an oil-water heat exchanger is used instead of the oil-air cooler 4.
  • outside air is not used as cooling agent for the cooling medium but a second oil. This oil originates from another oil circuit and, as cooling agent, has a lower temperature than the medium to be cooled.
  • Fig. 2 shows an alternative embodiment to Fig. 1 .
  • the bypass valve 5 has been replaced by a thermostatically-controlled oil temperature regulator OETR 5.
  • the OETR 5 has as many intermediate positions as desired. In position a, the OETR 5 opens a bypass branch 9 to the tank I and completely closes the inflow 10 to the cooler 4. This position is assumed at low temperatures.
  • An expanding material element 17 which is provided on one side of the OETR 5 ensures that in the basic setting the OETR 5 assumes a position, wherein the entire oil is directed via the bypass branch 9, is provided on one side of the OETR 5. The expanding material element 17 expands when the oil temperature rises.
  • the disadvantage of this circuitry is that the OETR 5 represents a comparatively large and expensive component.
  • the total amount of oil must always flow through the OETR and the oil reacts relatively sluggishly to changes in temperature.
  • the switching response cannot be influenced, for example to adapt to different operating conditions.
  • the disadvantages mentioned occur even if an oil-oil heat exchanger or an oil-water heat exchanger is used instead of the oil-air cooler 4.
  • Other examples of cooling arrangements can be found in US 6354089 and EP 1985869 .
  • an oil cooling arrangement comprising a first transmission oil cooling circuit including a first oil pump, a first oil tank, a first oil temperature sensing means and an oil cooler; a second separate oil cooling circuit for hydraulic consumers including a second oil pump, a second oil tank and a second oil temperature sensing means; the two circuits being thermally interconnected by a heater exchanger through which both circuits flow separately; bypass means in the first circuit for bypassing flow in the first circuit around the cooler and heat exchanger; bypass means in the second circuit for bypassing flow in the second circuit around the heat exchanger, and control means arranged to receive signals from the first and second temperature sensing means and for opening at least one of the bypass means in a predictable manner dependent on the temperature signals received by the control means.
  • predictive means the prognostic control of the oil flow.
  • Such control prevents temperature spikes in the oil, which can develop if a circuit reacts too slowly to a rise in temperature.
  • Predictive control for example can be implemented by data determined by a temperature sensor being passed onto an engine control unit and evaluated by this.
  • the oil temperature in this case is used as a control variable of a characteristic diagram.
  • the engine control unit Based on this the engine control unit continually calculates a temperature gradient, that is to say the temperature rise or temperature fall is continually monitored over time. If a high temperature gradient is detected, a higher cooling capacity demand results in order to prevent the permissible limit temperature of the oil from being exceeded. By closing the means for controlling the oil flow, a larger quantity of oil is fed to the cooler and thus the cooling capacity is increased.
  • the cooler and heat exchanger in the first circuit may each have their own bypass means which is controlled by the control means and the heat exchanger has its own bypass means in the second circuit also controlled by the control means.
  • Each bypass means way comprise a solenoid operated fluid flow control valve connected in parallel to the cooler and heat exchanger in the first and second circuits.
  • the cooler and heat exchanger each have their own bypass means in the first and second circuits, the bypass means for the heat exchanger in the first and second circuits comprising solenoid operated fluid flow control valves operated by the control means, and the bypass means for the cooler comprises a spring loaded check valve.
  • the cooler and heat exchanger may have single bypass means which bypasses both the cooler and heat exchanger and which is operated by the control means.
  • the means for cooling the oil temperature is an oil-air cooler and/or an oil-oil heat exchanger and/or an oil-water heat exchanger.
  • the flow control device has a reflux filter.
  • this reflux filter can be freely circumvented via a bypass valve.
  • Fig. 3 shows a flow control device through which oil from an oil tank 1 flows.
  • the device has a flow control means 11, with as many intermediate positions as desired, for controlling the oil flow.
  • a temperature sensor 12 which is present in the system, continuously measures the oil temperature in the inflow 10 of the cooler 4 and transmits this to an engine control unit (ECU) 13.
  • the engine control unit 13 has an output, which can be a pulse-width-modulation (PWM) output which activates an oil flow control means 11. If the oil is cold there is no activation of the oil flow control means; thus the bypass branch 9 is completely open in operating position a.
  • PWM pulse-width-modulation
  • the oil flow control means 11 When the oil temperature increases the oil flow control means 11 is activated, to operating position b directing a portion of the oil flow, dependent upon the level of increase in the oil temperature, to the cooler inflow 10 and the remaining portion to the bypass branch 9. With higher oil temperatures and demands for higher cooling capacity the oil flow control means I is completely closed, to operating position c, and the entire oil flow is directed to the cooler 4.
  • a characteristic diagram which is based on measurements or calculations can be programmed in the engine control unit 13.
  • Fig. 4 shows a flow control device.
  • a 2/2 on-off valve is used as oil flow control means 11.
  • the two fixed operating positions c and a are provided.
  • the advantages specified in Fig. 3 are also valid for Fig. 4 with the difference that on and off switching of the cooler 4 takes place without intermediate steps.
  • Fig. 5 shows a further flow control device.
  • This preferred embodiment as the oil flow control means 11, has an electrically-operated check valve 11.
  • This check valve by way of example has a response pressure of 5 bar.
  • the check valve 11 is opened by an electric current, directing the oil flow to the bypass 9 and ensuring that the cooling capacity is reduced, in order to guarantee fast oil warming.
  • the check valve 11 changes to the bypass position a and therefore ensures that the bypass 9 is opened and the cooler 4 does not suffer damage in cold weather starting conditions.
  • the fail safe function of the means 11 fulfils both the requirement to limit the cooler internal pressure and providing the cooling capacity, without making additional emergency hand operation necessary.
  • Fig. 6 shows a preferred embodiment, in which the circuit for the working and transmission hydraulics are separate.
  • An oil pump 7a with constant displacement draws from a tank 1a and feeds the working hydraulics circuit 6a.
  • the working hydraulics circuit 6a can also be supplied by further pumps not illustrated here. In this case only further circuitry of the working hydraulics circuit 6a is fed by the pump 7a.
  • the flow control means 11a which is connected in parallel to a heat exchanger 14 is located in the further circuitry.
  • An oil pump 7b with constant displacement draws from a tank 1b and feeds the hydraulic system 6b.
  • the transmission hydraulic system 6b can also be supplied by further pumps, not illustrated here. Of significance here is that the further circuitry of the transmission hydraulics 6b is only fed by pump 7b.
  • a cooling means 4 which is protected by the parallel-connected means 11c is located in the further circuitry.
  • the second side of the heat exchanger 14 is located in the further circuitry of the cooler 4.
  • the heat exchanger 14 can be of a plate or of a tube bundle construction.
  • the heat exchanger 14 is designed to transfer the heat energy of the oil circuit at the higher temperature to the circuit at the lower temperature.
  • the temperatures of the transmission oil circuit 6b are measured by the temperature sensors 12b and 12c, the temperature of the working hydraulic system 6a being measured by the temperature sensor 12a.
  • the sensors 12a, 12b and 12c are connected to the engine control unit 13, so that the flow control means 11a, 11b and 11c are activated.
  • each of the individual coolers has an element to control the temperature and to control the cooling capacity. The advantages of the cooler control therefore have an effect in each of the individual circuits.
  • the temperature at sensor 12c rises above a certain level, it is necessary to dissipate heat energy from the vehicle into the environment. This takes place by energizing the flow control means 11c. By specific activation of the flow control means 11c the cooling capacity of the cooling means can be regulated within certain limits. In the event that the transmission oil becomes hot due to fast road travel, the flow control means 11c and 11b are opened. The oil in circuit 6a remains at a low temperature for a long time if the working hydraulics 6a are not running, as is usual in the case of road travel. This is particularly the case if circuit 6a is equipped with one or more variable pumps (not illustrated). Due to the low-loss standby operation of this type of pump the oil only warms up very slowly.
  • the preferred embodiment solves this problem as follows: above a certain temperature difference between temperature sensors 12b and 12a, the flow control means 11a is activated and closed, and the medium to be warmed up in circuit 6a is directed to the heat exchanger 14. Thus the temperature in the circuit 6a rises and the temperature in the circuit 6b falls. This heat transfer has the consequence that the temperature in the circuit 6b reduces and the oil in circuit 6a warms up. The heating of the oil in circuit 6a reduces the likelihood of cavities forming in the pumps in circuit 6a. Furthermore as a result of the heating of the oil, the switching times of the solenoid valves in circuit 6a are reduced, and their operational reliability improved.
  • the circuit - not illustrated in detail - under certain circumstances may be simplified, while other means for heating the oil can be dispensed with.
  • Fig. 7 shows a further preferred embodiment of the invention.
  • the flow control means 11c has been replaced by the check valve 16.
  • the check valve 16 takes over the function of protecting the cooler 4 from too high internal pressure and indirectly takes over the flow control and thus the cooling performance.
  • Fig. 8 shows a further preferred embodiment of the invention.
  • the flow control means 11b and 11c from Fig. 6 or 11b and the check valve 16 from Fig. 7 are replaced by a single control means 11b, in order to reduce the component complexity and the costs.
  • heat energy can be transferred in a controlled way from circuit 6a to 6b and from circuit 6b to circuit 6a.
  • the circuit according to Fig. 8 does not offer the possibility of separating the control for the performance of cooler 4 from the control for the performance of heat exchanger 14.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • General Details Of Gearings (AREA)
  • Fluid-Pressure Circuits (AREA)

Claims (8)

  1. Agencement de refroidissement d'huile comprenant :
    un premier circuit de refroidissement d'huile de transmission (6b) comportant une première pompe à huile (7b), un premier réservoir d'huile (1b), un premier moyen de détection de température d'huile (12b) et un refroidisseur d'huile (4) ;
    un second circuit de refroidissement d'huile distinct (6a) destiné à des consommateurs hydrauliques comportant une seconde pompe à huile (7a), un second réservoir d'huile (1a) et un second moyen de détection de température d'huile (12a) ;
    les deux circuits étant couplés thermiquement ensemble par un échangeur thermique (14) à travers lequel les deux circuits s'écoulent séparément ;
    caractérisé par :
    des moyens de dérivation (11c, 11b) sur le premier circuit (6b) destinés à dériver l'écoulement dans le premier circuit par rapport au refroidisseur (4) et à l'échangeur thermique (14);
    des moyens de dérivation (11a) sur le second circuit (6a) destinés à dériver l'écoulement dans le second circuit par rapport à l'échangeur thermique (14), et
    un moyen de commande (13) agencé afin de recevoir des signaux à partir des premier et second moyens de détection de température (12b, 12a) et d'ouvrir au moins l'un des moyens de dérivation d'une manière prévisible en fonction des signaux de température reçus par le moyen de commande.
  2. Agencement selon la revendication 1, caractérisé en ce que le refroidisseur (4) et l'échangeur thermique (14) sur le premier circuit (6b) comportent chacun leur propre moyen de dérivation (11c, 11b) qui est commandé par le moyen de commande (13) et l'échangeur thermique (14) comporte son propre moyen de dérivation (11a) sur le second circuit (6a) aussi commandé par le moyen de commande (13).
  3. Agencement selon la revendication 2, caractérisé en ce que les moyens de dérivation comprennent chacun des vannes de commande de débit hydraulique commandées par solénoïde (11c, 11b, 11a) raccordées en parallèle au refroidisseur (4) et à l'échangeur thermique (14) sur les premiers et seconds circuits (6b, 6a).
  4. Agencement selon la revendication 1, caractérisé en ce que le refroidisseur (4) et l'échangeur thermique (14) comportent chacun leur propre moyen de dérivation sur les premier et second circuits (6b, 6a), les moyens de dérivation de l'échangeur thermique sur les premier et second circuits comprenant des vannes de commande de débit hydraulique commandées par solénoïde (11b, 11a) commandées par le moyen de commande, et le moyen de dérivation pour le refroidisseur comprend un clapet anti-retour préchargé par ressort (16).
  5. Agencement selon la revendication 1, caractérisé en ce que le refroidisseur (4) et l'échangeur thermique (14) comportent un moyen de dérivation unique (11b) qui contourne à la fois le refroidisseur et l'échangeur thermique et qui est commandé par le moyen de commande (13).
  6. Agencement selon la revendication 5, caractérisé en ce que le moyen de dérivation unique comprend une seule vanne de commande de débit hydraulique commandée par solénoïde (11b) commandée par le moyen de commande (13).
  7. Agencement selon la revendication 5 ou 6, caractérisé en ce que le moyen de dérivation pour l'échangeur thermique (14) sur le second circuit (6a) comprend une vanne de commande de débit hydraulique commandées par solénoïde (11a) commandée par le moyen de commande.
  8. Tracteur caractérisé par l'intégration d'un agencement de refroidissement d'huile selon l'une quelconque des revendications 1 à 7.
EP09772437A 2008-06-30 2009-06-30 Régulation de débit Active EP2310692B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102008030969A DE102008030969A1 (de) 2008-06-30 2008-06-30 Durchflusssteuerung
PCT/EP2009/058181 WO2010000737A1 (fr) 2008-06-30 2009-06-30 Régulation de débit

Publications (2)

Publication Number Publication Date
EP2310692A1 EP2310692A1 (fr) 2011-04-20
EP2310692B1 true EP2310692B1 (fr) 2012-10-24

Family

ID=41100737

Family Applications (1)

Application Number Title Priority Date Filing Date
EP09772437A Active EP2310692B1 (fr) 2008-06-30 2009-06-30 Régulation de débit

Country Status (4)

Country Link
US (1) US20110132012A1 (fr)
EP (1) EP2310692B1 (fr)
DE (1) DE102008030969A1 (fr)
WO (1) WO2010000737A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105526155A (zh) * 2014-09-30 2016-04-27 中联重科股份有限公司 闭式液压泵测试系统温度控制方法、设备以及系统

Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102013203756A1 (de) * 2013-03-05 2014-09-11 Bentec Gmbh Drilling & Oilfield Systems Antriebsvorrichtung zum Antrieb von Bohrgestänge und Verfahren zum Betrieb einer solchen Antriebsvorrichtung
US10260824B2 (en) 2013-12-13 2019-04-16 Cnh Industrial America Llc Fluid cooler bypass system for an agricultural work vehicle
CN103806497A (zh) * 2014-02-14 2014-05-21 上海三一重机有限公司 一种自动调节油温的回油系统及挖掘机
JP5954360B2 (ja) * 2014-06-09 2016-07-20 コベルコ建機株式会社 建設機械
DE102016014303A1 (de) * 2016-12-01 2018-06-07 Hydac Filter Systems Gmbh Abscheidevorrichtung
DE102017101090A1 (de) * 2017-01-20 2018-07-26 Man Diesel & Turbo Se Ölversorgungssystem und Verfahren zum Betreiben desselben
DE102017201225A1 (de) 2017-01-26 2018-07-26 Zf Friedrichshafen Ag Verfahren zum Betreiben eines Hydrauliksystems mit einem ersten Schaltventil, mit einem zweiten Schaltventil und mit einem Druckfilter
US11725550B2 (en) * 2020-03-16 2023-08-15 Volvo Truck Corporation Control method, controller, and control program for controlling lubricating system, computer-readable medium carrying control program, lubricating system, and vehicle
DE102020203458A1 (de) 2020-03-18 2021-09-23 Mahle International Gmbh Getriebeölfiltermodul
CN112268038B (zh) * 2020-10-19 2022-08-09 江苏徐工工程机械研究院有限公司 新型液压油冷却系统
DE102022111288A1 (de) 2022-05-06 2023-11-09 Jungheinrich Aktiengesellschaft Hydrauliksystem für ein Flurförderzeug und Flurförderzeug

Family Cites Families (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1396778A (en) * 1972-03-28 1975-06-04 Af Hydraulics Fluid supply systems
DE2943526C2 (de) * 1979-10-27 1985-10-24 Klöckner-Humboldt-Deutz AG, 5000 Köln Vorrichtung zum Anwärmen der Druckflüssigkeit für die Arbeitshydraulik eines Kraftfahrzeugs
SE8903739D0 (sv) * 1989-11-08 1989-11-08 Haakan Ingvast Metod och anordning i en hydraulanlaeggning
US5666807A (en) * 1995-12-13 1997-09-16 Caterpillar Inc. Oil processor circuit
US5890509A (en) * 1997-03-31 1999-04-06 Ford Global Technologies, Inc. Hydraulic temperature compensated cooler bypass control for an automatic transmission
DE19942543A1 (de) * 1999-09-07 2001-03-22 Fluidtech Gmbh Fluidkühlvorrichtung
DE19950052A1 (de) * 1999-10-16 2001-05-31 Fluidtech Gmbh Fluidkühlvorrichtung
US6354089B1 (en) * 2000-03-08 2002-03-12 Case Corporation Apparatus and method for cooling multiple fluids on a work vehicle
DE10125350A1 (de) * 2001-05-23 2002-11-28 Linde Ag Vorrichtung zur Kühlung von Bauteilen mittels Hydraulikflüssigkeit aus einem hydraulischen Kreislauf
US6614353B2 (en) * 2002-01-14 2003-09-02 Smc Kabushiki Kaisha Constant-temperature liquid circulating device having a proportional valve based predictive system for pre-estimating a need for maintenance
US6749016B2 (en) * 2002-01-14 2004-06-15 Smc Kabushiki Kaisha Brine temperature control apparatus using a three-way proportional valve
JP3932277B2 (ja) * 2002-10-18 2007-06-20 日本サーモスタット株式会社 電子制御サーモスタットの制御方法
JP2004268752A (ja) * 2003-03-10 2004-09-30 Denso Corp 熱管理システム
DE10335743A1 (de) * 2003-08-05 2005-02-24 Robert Bosch Gmbh Steuerventil, insbesondere für einen Kühlkreislauf
DE102004015505B4 (de) * 2004-03-28 2006-02-16 Hydac S.A. Kühlvorrichtung
US20050252635A1 (en) * 2004-05-14 2005-11-17 Cnh America Llc Tractor cooling system
DE102005043110B4 (de) * 2005-09-10 2010-07-29 Terex Gmbh Verfahren und Einrichtung zur Regelung der Temperatur von Hydrauliköl
US20070095504A1 (en) * 2005-10-24 2007-05-03 Tuntland John E Radiator for a work machine
JP4432898B2 (ja) * 2005-12-20 2010-03-17 トヨタ自動車株式会社 内燃機関の冷却装置
JP4725345B2 (ja) * 2006-02-08 2011-07-13 日立建機株式会社 油圧駆動式産業機械
US20070295005A1 (en) * 2006-06-23 2007-12-27 Deere & Company, A Delaware Corporation Work machine hydraulic system with bypass conditioning and associated method

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105526155A (zh) * 2014-09-30 2016-04-27 中联重科股份有限公司 闭式液压泵测试系统温度控制方法、设备以及系统

Also Published As

Publication number Publication date
EP2310692A1 (fr) 2011-04-20
WO2010000737A1 (fr) 2010-01-07
DE102008030969A1 (de) 2009-12-31
US20110132012A1 (en) 2011-06-09

Similar Documents

Publication Publication Date Title
EP2310692B1 (fr) Régulation de débit
JP5919031B2 (ja) 冷却水制御バルブ装置
EP2864607B1 (fr) Dispositif de commande d'écoulement de fluide
US7287374B2 (en) System and method for controlling viscosity of a fluid and a working vehicle containing such a system
US9581177B2 (en) Clutch transmission
EP2037097B1 (fr) Système de refroidissement et dispositif de thermostat pour véhicule à moteur
EP0812280A1 (fr) Procede et systeme hydraulique pour automobiles
CN109072731B (zh) 流体供给系统
EP2935821B1 (fr) Système de refroidissement destiné à un véhicule hybride propulsé mécaniquement et hydrauliquement
US20150369113A1 (en) Hydro-actuated thermostats
CN107939546B (zh) 在发动机停机后使冷却剂流过排气热回收系统的方法
US5778693A (en) Automotive hydraulic engine cooling system with thermostatic control by hydraulic actuation
JP2005509116A (ja) 車両用の駆動部
US9360005B2 (en) Auxiliary device for an agricultural working machine
EP2932061B1 (fr) Système de refroidissement
US9222399B2 (en) Liquid cooled internal combustion engine with coolant circuit, and method for operation of the liquid cooled internal combustion engine
EP2935822B1 (fr) Système de refroidissement dans un véhicule
US20190331209A1 (en) Rear axle lubrication oil temperature control using exhaust heat recovery and a thermal battery
US20130213023A1 (en) Hydraulic system having low-speed operating mode
JP2005155698A (ja) 油圧作業機械の油圧回路
JP2014145326A (ja) 内燃機関
CN106523476B (zh) 集成式液压油散热器
CN219549525U (zh) 一种液力变矩器和油底壳的油温控制系统
EP2309125B1 (fr) Système de réfrigération auxiliaire et méthode d'exploitation
CN117605721A (zh) 液压控制系统及工程机械

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20110131

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO SE SI SK TR

AX Request for extension of the european patent

Extension state: AL BA RS

DAX Request for extension of the european patent (deleted)
GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO SE SI SK TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: AT

Ref legal event code: REF

Ref document number: 581111

Country of ref document: AT

Kind code of ref document: T

Effective date: 20121115

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 602009010690

Country of ref document: DE

Effective date: 20121220

REG Reference to a national code

Ref country code: AT

Ref legal event code: MK05

Ref document number: 581111

Country of ref document: AT

Kind code of ref document: T

Effective date: 20121024

REG Reference to a national code

Ref country code: NL

Ref legal event code: VDEP

Effective date: 20121024

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130204

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20121024

Ref country code: HR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20121024

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130224

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20121024

Ref country code: NO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130124

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20121024

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130125

Ref country code: BE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20121024

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20121024

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20121024

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20121024

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130225

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20121024

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20121024

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130124

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20121024

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20121024

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20121024

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20121024

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20130725

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 602009010690

Country of ref document: DE

Effective date: 20130725

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20121024

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MC

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20121024

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

REG Reference to a national code

Ref country code: IE

Ref legal event code: MM4A

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20130630

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20130630

Ref country code: IE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20130630

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20121024

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20121024

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: TR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20121024

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20121024

Ref country code: HU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO

Effective date: 20090630

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20130630

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 8

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 9

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 10

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: IT

Payment date: 20180622

Year of fee payment: 10

Ref country code: GB

Payment date: 20180620

Year of fee payment: 10

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20190630

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20190630

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20190630

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20210622

Year of fee payment: 13

REG Reference to a national code

Ref country code: DE

Ref legal event code: R084

Ref document number: 602009010690

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20220630

P01 Opt-out of the competence of the unified patent court (upc) registered

Effective date: 20230518

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20230620

Year of fee payment: 15