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EP2282029B2 - Machine autoporteuse - Google Patents

Machine autoporteuse Download PDF

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Publication number
EP2282029B2
EP2282029B2 EP09008470.8A EP09008470A EP2282029B2 EP 2282029 B2 EP2282029 B2 EP 2282029B2 EP 09008470 A EP09008470 A EP 09008470A EP 2282029 B2 EP2282029 B2 EP 2282029B2
Authority
EP
European Patent Office
Prior art keywords
hydraulic
hydraulic medium
cooling
operation temperature
combustion engine
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
EP09008470.8A
Other languages
German (de)
English (en)
Other versions
EP2282029A1 (fr
EP2282029B1 (fr
Inventor
Ralf Weiser
Tobias Noll
Andreas Letz
Martin Buschmann
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.)
Joseph Voegele AG
Original Assignee
Joseph Voegele AG
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
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Application filed by Joseph Voegele AG filed Critical Joseph Voegele AG
Priority to AT09008470T priority Critical patent/ATE503092T1/de
Priority to DE502009000490T priority patent/DE502009000490D1/de
Priority to EP09008470.8A priority patent/EP2282029B2/fr
Priority to US12/821,925 priority patent/US20100326067A1/en
Priority to CN2010102202512A priority patent/CN101936211B/zh
Priority to CN2010202491912U priority patent/CN201794654U/zh
Publication of EP2282029A1 publication Critical patent/EP2282029A1/fr
Publication of EP2282029B1 publication Critical patent/EP2282029B1/fr
Publication of EP2282029B2 publication Critical patent/EP2282029B2/fr
Application granted granted Critical
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P7/00—Controlling of coolant flow
    • F01P7/02—Controlling of coolant flow the coolant being cooling-air
    • F01P7/04—Controlling of coolant flow the coolant being cooling-air by varying pump speed, e.g. by changing pump-drive gear ratio
    • F01P7/044—Controlling of coolant flow the coolant being cooling-air by varying pump speed, e.g. by changing pump-drive gear ratio using hydraulic drives
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/226—Safety arrangements, e.g. hydraulic driven fans, preventing cavitation, leakage, overheating
    • 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
    • E01C19/48—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 laying-down the materials and consolidating them, or finishing the surface, e.g. slip forms therefor, forming kerbs or gutters in a continuous operation in situ
    • 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
    • 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
    • F15B21/0427—Heating
    • 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
    • F15B2211/66—Temperature control methods

Definitions

  • the invention relates to a self-propelled road finisher or feeder according to the preamble of claim 1.
  • a drive concept for functional and working components has become established for such road finishers and feeders, in which the internal combustion engine acts as the primary drive source, but the functional and working components are operated exclusively or almost exclusively hydraulically, for example by means of hydrostatic drive units.
  • the road finisher builds at least one surface layer with a varying working width on a subgrade made of the paving material, levels and compacts it.
  • a feeder keeps a sufficiently large supply of the paving material ready and feeds the road finisher in such a way that the road finisher can work continuously.
  • the feeder and the following road paver travel at a low paving speed on the planum, eg up to around 20 m/min. When transporting to another construction site, a transport speed of up to around 20 km/h is normal for both machines.
  • the processing of hot bituminous paving material or concrete paving material results in very special requirements for the hydraulic system and the combustion engine, for example due to the material consistency, its stickiness, its processing temperature, its drag resistance when paving on the subgrade or conveying resistance when loading, and also from the Driving resistance that varies depending on the construction site coupled with climatic influences, so that at least some hydrostatic drive units have to be extremely powerful, respond quickly and designed for continuous operation and at the same time have to be individually controlled during operation.
  • This requires powerful hydraulic pumps, sometimes long hydraulic paths between the hydraulic pumps and the hydrostatic drive units, while taking into account high safety and environmental standards.
  • a road finisher or feeder with a total weight of around 20 tons contains a considerable volume of hydraulic medium in the hydraulic circuit, for example up to 400 liters or more.
  • Hydraulic media commonly used for such machines have a behavior of the kinematic viscosity over the temperature in which the viscosity decreases strongly degressively with increasing temperature, initially up to about 60°C, and by about 100°C remains very low. temperatures of around 100°C however, critical for seals and hoses in the hydraulic circuit of such self-propelled machines. At about 60°C the viscosity is only half that at 40°C, and is only about one tenth the viscosity at about 0°C. Between about 75°C to 80°C the viscosity is even only about one fifth of the viscosity at 40°C.
  • the internal combustion engine that serves as the primary drive source has to compensate for pumping losses. In normal operation, for example, it runs with a nominal output of 160 kW at around 2000 rpm.
  • the pumping losses significantly worsen the energy efficiency or energy balance of the self-propelled machine and, based on the operating hours of such a machine per year, offer considerable potential for saving primary energy, such as diesel fuel.
  • a large multi-section cooler is used as a cooling device for the engine cooling water of the internal combustion engine, the hydraulic medium, and in this case also the charge air of the supercharged diesel engine, for example, is provided, with which optimal engine operating temperature and 100% engine performance are always ensured, even at full load operation and high outside temperatures of up to 50°C.
  • the cooling device has at least one fan that is operated as a function of the engine speed, for example.
  • the cooling device is traditionally designed for the internal combustion engine.
  • the hydraulic medium cooling area of the cooling device is designed in such a way that overheating of the hydraulic medium is reliably avoided even under extreme working conditions.
  • the cooling control takes place with regard to the optimum operating temperature of the combustion engine.
  • the hydraulic medium is cooled so much over e.g. more than 95% of the operating time that its operating temperature does not exceed approx. 40°C. Dictated by the viscosity behavior of the hydraulic medium over the operating temperature, in order to compensate for example the pumping losses of the hydraulic medium, this entails wasting a significant part of the rated engine power actually generated for the processing of the paving material.
  • a common cooling device for cooling water and hydraulic oil is known, which is associated with a common fan driven by a hydraulic motor.
  • the cooling device is controlled in such a way that the cooling water reaches a target temperature as quickly as possible at a predetermined engine speed, which is then kept constant, while at the same time the operating temperature of the hydraulic oil is brought to the same temperature of around 80° as the temperature of the cooling water. If there is an increased cooling requirement for the cooling water, the hydraulic oil may also be cooled too much.
  • the invention is based on the object of specifying a self-propelled machine for processing bituminous and/or concrete paving material, the internal combustion engine of which, despite the special requirements due to the difficult workability of the paving materials, can be operated with an improved energy balance or energy efficiency, saves a significant amount of fuel, and the environment gentle.
  • the operating temperature of the hydraulic medium is increased as quickly as possible and then regulated within an operating temperature range in which the additional load on the internal combustion engine, for example due to pumping losses of the hydraulic medium, is minimized.
  • this can be the case when the machine takes a break from operation at high outside temperatures, low humidity and unfavorable processing conditions of the paving material and difficult ground and driving conditions because it has to wait for the delivery of fresh paving material, with the combustion engine being operated at idle and the Engine cooling capacity is reduced.
  • the hydraulic medium operating temperature adjustment and control device then regulates, for example, with maximum efficiency in order to reliably avoid overheating of the hydraulic medium.
  • a considerable amount of fuel can be saved over the period of use of the machine in normal operation per year.
  • This improvement in the energy efficiency of the internal combustion engine goes hand in hand with optimized operation of the pumps and hydrostatic drive units and rapid response behavior in the hydraulic circuit at all times.
  • a hydraulic medium cooler that is separate from the cooling liquid cooling area is even provided as the hydraulic medium cooling area.
  • This at least one cooler is associated with a fan that can be speed-controlled and/or switched on and off as required, which is connected to the hydraulic medium operating temperature setting and control device.
  • the separate arrangement of the hydraulic medium cooler otherwise avoids, for example, unavoidable heating or cooling situations for the hydraulic medium cooler, which could occur when the cooling liquid cooling area and the hydraulic medium cooling area are in close proximity.
  • this concept may be advantageous for the machine in order to take account of the already cramped space conditions in the coolant cooling area and/or to improve the weight distribution in the machine.
  • a valve that can be actuated by the hydraulic medium operating temperature setting and control device is to be arranged in the hydraulic circuit in a bypass bypassing the hydraulic medium cooling area, and expediently to completely bypass the hydraulic medium cooling area via the bypass at least after the start of normal operation of the machine when the hydraulic medium is cold, e.g. also when operating a heating device for faster heating of the hydraulic medium in the hydraulic circuit or in the hydraulic circuits.
  • At least one hydraulic medium heating device is even provided in the hydraulic circuit. This is connected to the hydraulic medium operating temperature adjustment and control device and can be operated via this.
  • the heating device not only makes it possible to bring the hydraulic medium to the optimal operating temperature as quickly as possible, but also to maintain the optimal operating temperature range in normal operation if the desired increased operating temperature cannot be set or maintained simply by minimizing or switching off the cooling capacity.
  • the hydraulic medium heating device is provided on or in the reservoir of the hydraulic medium.
  • a maximum amount of the hydraulic medium is usually stored in the reservoir, for example about 400 liters, under relatively moderate return pressure, so that the heating device works efficiently and can be designed to be less pressure-resistant.
  • a circulation pump that can be controlled by the hydraulic medium operating temperature setting and regulating device is expediently provided in the hydraulic medium cooling area or adjacent to it, preferably in a short-circuit section provided between the reservoir and the hydraulic medium cooling area or in the bypass of the hydraulic circuit or hydraulic circuits.
  • the delivery rate of the hydraulic medium can be varied via the circulation pump, for example, in order to intensify or minimize the cooling.
  • At least one signal transmitter for the actual hydraulic medium temperature and/or hydraulic and/or thermal load situations of at least one selected pump and/or one selected hydrostatic drive unit is provided and connected to the hydraulic medium operating temperature adjustment and control device as a control reference variable transmitter.
  • a pump and/or a hydrostatic drive unit is appropriately selected that is extremely powerful or at which extreme hydraulic Operating situations can be expected, so that the hydraulic medium operating temperature setting and control device is quickly informed of a critical condition and can regulate accordingly.
  • a machine for processing bituminous or concrete paving material using an internal combustion engine, especially a diesel engine, as the primary drive source for at least one hydraulic system with pumps and hydrostatic drive units is operated in such a way that to improve the energy efficiency of the internal combustion engine during operation or from the start of operation of the Machine the hydraulic medium independently of the load condition of the internal combustion engine and the engine cooling control depending on the hydraulic load condition in the at least one hydraulic circuit and depending on the ambient climate brought as quickly as possible to an increased operating temperature of at least about 60 ° C and then in an operating temperature range of above about 60°C is regulated in order to waste as little as possible compensation power of the combustion engine with the optimally low viscosity of the hydraulic medium and to save as much fuel as possible.
  • FIG. 1 shows, as an example of a self-propelled machine F, a road finisher for processing bituminous and/or concrete paving material in the production of surface layers, for example of traffic areas or the like.
  • the machine F has a chassis 32 with a chassis 33 having wheels in the embodiment shown (alternatively a caterpillar chassis) and an internal combustion engine M, e.g a diesel engine, as the primary power source.
  • the machine has a large number of functional and working components that are predominantly operated hydraulically and are supplied with drive power by the internal combustion engine M.
  • a material bunker 36 is located on the chassis 32, from which a longitudinal conveyor device 37 extends in the chassis 32 to the rear end of the chassis, where a transverse distribution device 38 with a height adjustment device 47 and a drive 39 are arranged.
  • a screed 34 is articulated on the chassis 32, the angle of attack of which can be adjusted by means of leveling cylinders 41 and which can be raised by hydraulic cylinders 42.
  • Adjusting cylinders 46, hydraulically operated tampers 44 and hydraulically operated, optional pressure bars 45 are provided in the screed.
  • Bunker wall adjustment cylinders 41 are provided for the bunker 36 .
  • a cooling device K is assigned to the internal combustion engine M, for example with a multi-field cooler and a fan which is driven, for example, proportionally to the speed of the internal combustion engine M.
  • the aforementioned functional and working components of the machine F are operated for processing the paving material by means of hydrostatic drive units or cylinders.
  • At least one hydraulic circuit H ( Figures 2, 3 ) and hydraulic pumps and valve assemblies are provided.
  • the various pumps are driven by the internal combustion engine, for example via a pump transfer case.
  • a generator is driven by the internal combustion engine M, which makes electrical power available.
  • a reservoir for a hydraulic medium (hydraulic oil), which can have a capacity of several 100 liters, is also provided for the hydraulic circuit or circuits (including connecting lines and connecting hoses).
  • the cooling device K is designed in such a way that the cooling liquid of the internal combustion engine, if necessary its intake air or charge air, and also the hydraulic medium are cooled, with a cooling control system being provided which primarily treats the cooling liquid of the internal combustion engine M in such a way that the internal combustion engine during normal operation (e.g. nominal speed around 2000 rpm with a nominal output of around 160 kW) always has the optimum operating temperature.
  • a cooling control system being provided which primarily treats the cooling liquid of the internal combustion engine M in such a way that the internal combustion engine during normal operation (e.g. nominal speed around 2000 rpm with a nominal output of around 160 kW) always has the optimum operating temperature.
  • the hydraulic medium reaches an operating temperature of at least about 60° C., preferably between about 75° C. and 80° C. or slightly more, and a hydraulic medium operating temperature range of, for example, 75° C. to 80° C. in normal operation and independently of ambient climatic conditions are complied with is in accordance with 2 in the Machine F is provided with a hydraulic medium operating temperature adjustment and control device R, which preferably controls the operating temperature of the hydraulic medium independently of the cooling control system S for the coolant of the internal combustion engine M.
  • In 2 is assigned to the internal combustion engine M, for example a diesel engine, a multi-section cooler or a set of coolers 1 consisting of several coolers, which in the embodiment shown, not according to the invention, has a cooling area 1a for the intake air or charge air; a cooling area 1b for the cooling liquid of the internal combustion engine M, and a cooling area 1c for the hydraulic medium, and which is assigned a common fan 2 with a drive motor 3, which is controlled by the cooling control system S with regard to the optimal operating temperature of the internal combustion engine M. With 4 the energy supply to the drive motor 3 is indicated.
  • the drive motor 3 can be fed, for example, from the hydraulic system, or electrically via the generator G driven by the internal combustion engine M, or directly or indirectly via the crankshaft of the internal combustion engine M.
  • a pump transfer case 5 at the outputs of which several hydraulic pumps 6 are mounted, which are hydraulically connected via connecting lines or pressure hoses to various hydrostatic drive units 7, 8, 9, 10 for the basis 1 explained working and functional components of the machine are connected.
  • a common return line 11 extends from the hydrostatic drive units 7 to 10 to a hydraulic medium reservoir 12, usually a large-volume metal container, to which valve components 13, for example, can be attached.
  • the reservoir 12 can be connected to the cooling area 1c via a line 14 .
  • the return line 11 can also be connected to the cooling area 1c.
  • a bypass 15 can be provided between the reservoir 12 or the valve arrangement 13 and the return line 11, in which a valve 16, which can be controlled by the control device R, can be contained for the hydraulic medium flow.
  • the internal combustion engine M is mounted on an engine bracket 17 which is mounted on abutments 19 of the chassis 32 of the machine F via engine mounts 18 in a vibration-insulated manner.
  • the generator G which is driven, for example (not shown), by the pump transfer case 5, can be mounted on the engine bracket 17.
  • At least one heating device 20 can be provided for the hydraulic circuit or all hydraulic circuits H of the hydraulic system, for example in the return line 11, or in or on the reservoir 12, or at another suitable location in the machine F.
  • the heating device 20 is 2 eg via a controllable by the control device R Control 21 from the generator G electrically operated.
  • the heating device 20 could use the cooling water and/or waste heat from at least the internal combustion engine M.
  • a temperature sensor 22 for the operating temperature of the hydraulic medium (or a sensor for the hydraulic load condition) is arranged at least on one selected, or at several or all, hydrostatic drive units 7 to 10 (or the pumps 6) or at other suitable points of the hydraulic circuit H connected to the control device R.
  • a temperature sensor 22 can also be located on or in the reservoir 12, or in or near the cooling area 1c.
  • at least one information transmitter 23, e.g. a temperature and/or humidity sensor, is provided and connected to the control device R, which detects the ambient climate.
  • a preferably computerized main control CU of the machine F can also be connected to (or combined with) the control device R and provide information i7, e.g. in real time or in preparation, e.g.
  • the hydraulic medium operating temperature setting and control device R has a programming and/or setting section P, on which, for example, the desired operating temperature of the hydraulic medium can be set and monitored, and, expediently, a selection device W, on which a hydraulic medium operating temperature of at least about 60°C, preferably even about 75°C, to which the hydraulic medium should be brought as quickly as possible after starting operation, and an operating temperature range in normal operation of at least about 60°C, preferably about 75°C to 80°C , or preferably even up to almost 90°C, within which the operating temperature of the hydraulic medium should be maintained during normal operation of the machine when processing the paving material, regardless of how the cooling control system S controls the cooling of at least the cooling liquid for the internal combustion engine M.
  • a circulation pump 29 can be used.
  • At least one shielding or deflection device 30 is expediently provided for the hydraulic medium in the air flow path from the fan 2 to the cooling area 1c, with which the cooling capacity generated by the fan 2 can be regulated individually for the cooling area 1c, for example via an actuator 31, which is controlled by the Control device R can be actuated, or not shown, by at least one thermostat or other temperature sensor in the hydraulic circuit.
  • the shielding or deflection device 30 could, for example, include flaps, slats or other elements that control the air flow.
  • the operating temperature of the hydraulic medium in the hydraulic circuit H is independent of the control intervention of the cooling control system S, at least for the cooling liquid of the internal combustion engine M depending on hydraulic load situations in the hydraulic circuit, especially on the hydraulic pumps 6 and/or the hydrostatic drive units 7 to 10, preferably on a selected pump or drive unit from which e.g.
  • the combustion smotor M has to compensate with additional fuel consumption.
  • the cooling area 1c for the hydraulic medium is structurally separated from the cooling areas 1a and 1b of the cooling device 1.
  • the cooling area 1c is formed by an independent hydraulic medium cooler 24, which is connected, for example, to the return line 11 and the connecting line 14 connected to the reservoir 12, and to which an independent blower 2a with its own drive motor 3a and its own drive power supply 4a is assigned.
  • the fan 2a is operated via the controller R as shown.
  • the drive motor 3a can either be a hydraulic motor or an electric motor or (not shown) is driven by the crankshaft of the internal combustion engine, for example via a switchable clutch.
  • the cooler 24 can be placed in the cooling device K, or at a suitable position in the machine F.
  • cooling fins 25 are provided on the reservoir 12 and another fan 26 can be provided with a drive motor 27, which is also controlled, for example, by the control device R, in order to additionally cool the hydraulic medium in the reservoir 12 if necessary.
  • the heating device 20 is also arranged on or in the reservoir 12 in order, if required, for example to reach the desired operating temperature of at least about 60°C or more as quickly as possible, or to reliably maintain the desired operating temperature range of above 60°C, the Additional heating of the hydraulic medium.
  • the graph in 4 shows for a common hydraulic medium (hydraulic oil specification HLP 46 according to DIN 51524, part 2) the behavior of the kinematic viscosity KV plotted on the vertical axis over the operating temperature T.
  • HLP 46 hydraulic oil specification
  • the kinematic viscosity is only half of the kinematic viscosity at an operating temperature of about 40°C and substantially less than one tenth of the viscosity at about 0°C.
  • the viscosity is only about half of the viscosity at 60°C.
  • This viscosity behavior of the specified hydraulic medium (other, common hydraulic media for machines for processing paving material show a similar behavior of the kinematic viscosity over the operating temperature) is in the machine F of Figures 1 to 3 , and also the machine F in figure 5 , used to improve the energy efficiency of the internal combustion engine and save fuel by setting the relatively high operating temperature of at least about 60°C and maintaining an operating temperature range of above about 60°C, in which the hydraulic medium is individually cooled and/or heated independently of the engine cooling will.
  • figure 5 illustrates as paving material processing machine F a feeder for feeding, for example, the road finisher from 1 drives with paving material in front of the road finisher on the subgrade, is supplied with the paving material intermittently from trucks or continuously via a conveyor device, and the road finisher always fills enough paving material into the bunker 36 so that the road finisher can continuously produce a surface layer.
  • a feeder for feeding for example, the road finisher from 1 drives with paving material in front of the road finisher on the subgrade, is supplied with the paving material intermittently from trucks or continuously via a conveyor device, and the road finisher always fills enough paving material into the bunker 36 so that the road finisher can continuously produce a surface layer.
  • the feeder shown has on its chassis 32 the running gear 33, for example a caterpillar running gear, with at least one drive 43 and a very large bunker 36.
  • the feeder is self-propelled and contains the liquid-cooled internal combustion engine M, for example a diesel engine, with the cooling device K at least for the cooling liquid as the primary drive source.
  • a hydraulically operated transverse conveying device 48 can be arranged in the bunker 36, from which an ascending hydraulically operated longitudinal conveying device 49 which has a hydraulically adjustable discharge end 52 extends to the rear and upwards.
  • the conveyor device 49 can have a further hydraulic device 50 .
  • the feeder as the machine F processing the paving material contains, for example, hydrostatic drive units for the travel drives 43, the transverse conveyor device 48, bunker adjustment wall cylinders (not shown), the device 50 and the discharge end 51, for which the internal combustion engine M drives corresponding hydraulic pumps in at least one hydraulic circuit.
  • the cooling device K can according to 3 be designed to keep the hydraulic medium in the hydraulic circuit independent of the cooling set the coolant of the internal combustion engine M to a hydraulic medium operating temperature of at least about 60°C, depending on hydraulic load situations and the ambient climate, and keep it in a hydraulic medium operating temperature range of above about 60°C, preferably between 75°C and 80°C, so as to optimize the responsiveness in the hydraulic circuit, reduce the viscosity of the hydraulic medium, and reduce the fuel consumption of the internal combustion engine, which can thus drive the feeder more efficiently and actuate the hydraulic working and functional components more efficiently.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Civil Engineering (AREA)
  • Mechanical Engineering (AREA)
  • Combustion & Propulsion (AREA)
  • Mining & Mineral Resources (AREA)
  • Chemical & Material Sciences (AREA)
  • Structural Engineering (AREA)
  • Road Paving Machines (AREA)
  • Preliminary Treatment Of Fibers (AREA)
  • Control Of Position, Course, Altitude, Or Attitude Of Moving Bodies (AREA)
  • Forklifts And Lifting Vehicles (AREA)
  • Cooling, Air Intake And Gas Exhaust, And Fuel Tank Arrangements In Propulsion Units (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Control Of Temperature (AREA)

Claims (3)

  1. Finisseur ou alimentateur routier automoteur comme machine (F) de traitement de matériaux de construction bitumineux ou en béton, ayant un moteur à combustion interne (M) refroidi par un liquide en tant que source d'entraînement primaire et au moins une pompe (6), des moteurs hydrauliques ou des unités d'entraînement hydrostatiques (7 à 10) pour les composants fonctionnels et de travail au moins de la machine (F), et un circuit hydraulique (H) comprenant au moins un réservoir de milieu hydraulique (12), un dispositif de refroidissement (K) assisté par un ventilateur ayant des zones de refroidissement (1b, 1c) pour au moins le liquide de refroidissement du moteur à combustion interne (M) et le fluide hydraulique du circuit hydraulique (H), et un système de régulation de refroidissement (S) pour au moins la zone de refroidissement du fluide de refroidissement (1b) du dispositif de refroidissement (K), moyennant quoi est prévu au moins un refroidisseur de fluide hydraulique (24) structurellement séparé de la zone de refroidissement du medium de refroidissement (1b) par un ventilateur (2a, 3a, 4a), caractérisé en ce qu'il est prévu pour la zone de refroidissement du medium hydraulique (1c) un dispositif de réglage et de régulation de la température de fonctionnement du medium hydraulique (R), qui est configuré pour porter le medium hydraulique à une température de fonctionnement (T) supérieure à 60°C en fonction de l'état de charge hydraulique dans le circuit hydraulique (H) et du climat ambiant et pour le maintenir dans une plage de température de fonctionnement supérieure à 60°C, en ce que le ventilateur (2a, 3a, 4a) peut être régulé en vitesse de rotation et/ou mis en marche et arrêté et est relié au dispositif (R) de réglage et de régulation de la température de fonctionnement du milieu hydraulique, et en ce qu'une soupape (16) pouvant être actionnée par le dispositif (R) de réglage et de régulation de la température de fonctionnement du milieu hydraulique est disposée dans le circuit hydraulique (H) dans une dérivation (15) contournant la zone (1c) de refroidissement du milieu hydraulique,
    dans lequel il est prévu dans le circuit hydraulique (H) au moins un dispositif de chauffage du milieu hydraulique (20) raccordé au dispositif de réglage et de régulation de la température de fonctionnement du milieu hydraulique (R),
    et dans lequel le dispositif de chauffage du milieu hydraulique (20) est disposé sur ou dans le réservoir (12).
  2. Finisseur ou alimentateur routier selon la revendication 1, caractérisé en ce qu'une pompe de circulation (29) pouvant être commandée par le dispositif de réglage et de régulation de la température de fonctionnement du milieu hydraulique (R) est associée à la zone de refroidissement du milieu hydraulique (1c), de préférence dans un circuit de court-circuit (28) du circuit hydraulique (H) prévu entre le réservoir (12) et la zone de refroidissement du milieu hydraulique (1c).
  3. Finisseur ou alimentateur routier selon au moins l'une des revendications précédentes, caractérisé en ce qu'au moins un générateur de signaux (22) pour la température réelle du milieu hydraulique et/ou les conditions de charge hydraulique et/ou thermique est associé à au moins une pompe sélectionnée (6) et/ou un moteur hydraulique sélectionné ou une unité d'entraînement hydrostatique (7 à 10) et est raccordé en tant que générateur des variables de commande de régulation au dispositif de réglage et de régulation de la température de fonctionnement du milieu hydraulique (R).
EP09008470.8A 2009-06-29 2009-06-29 Machine autoporteuse Active EP2282029B2 (fr)

Priority Applications (6)

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AT09008470T ATE503092T1 (de) 2009-06-29 2009-06-29 Selbstfahrende maschine
DE502009000490T DE502009000490D1 (de) 2009-06-29 2009-06-29 Selbstfahrende Maschine
EP09008470.8A EP2282029B2 (fr) 2009-06-29 2009-06-29 Machine autoporteuse
US12/821,925 US20100326067A1 (en) 2009-06-29 2010-06-23 Self-propelled machine
CN2010102202512A CN101936211B (zh) 2009-06-29 2010-06-29 自驱动机械
CN2010202491912U CN201794654U (zh) 2009-06-29 2010-06-29 自驱动机械

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EP09008470.8A EP2282029B2 (fr) 2009-06-29 2009-06-29 Machine autoporteuse

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EP2282029B1 EP2282029B1 (fr) 2011-03-23
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CN (2) CN201794654U (fr)
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DE (1) DE502009000490D1 (fr)

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ATE503092T1 (de) * 2009-06-29 2011-04-15 Joseph Voegele Ag Selbstfahrende maschine
PL2530273T3 (pl) * 2011-06-01 2020-11-16 Joseph Vögele AG Maszyna budowlana z automatyczną regulacją prędkości obrotowej wentylatora
PL2578888T3 (pl) 2011-10-07 2019-05-31 Voegele Ag J Maszyna budowlana z automatyczną regulacją prędkości obrotowej wentylatora
CN103233947A (zh) * 2012-01-08 2013-08-07 钱荣华 一种冷却煤矿井下挖掘装载机及其它设备液压油的方法
PL2672008T3 (pl) * 2012-06-05 2018-07-31 Joseph Vögele AG Układarka i sposób układania materiału poddawanego mieszaniu za pomocą układarki
JP6009480B2 (ja) * 2014-03-06 2016-10-19 日立建機株式会社 建設機械の冷却ファン制御装置
US9382675B2 (en) 2014-06-16 2016-07-05 Caterpillar Paving Products Inc. Electric powered systems for paving machines
CN106795700B (zh) * 2014-10-10 2019-11-12 住友建机株式会社 沥青碾光机
CN104500716A (zh) * 2014-12-30 2015-04-08 戴纳派克（中国）压实摊铺设备有限公司 齿轮油冷却系统及具有该齿轮油冷却系统的路面机械设备
EP3075909B1 (fr) * 2015-03-30 2017-09-06 Joseph Vögele AG Engin de construction de route doté d'un réseau de communication pour la transmission de données et utilisation d'une partie d'une ligne d'alimentation
PL3091125T3 (pl) 2015-05-06 2017-12-29 Joseph Vögele AG Maszyna budowlana z urządzeniem podnoszącym dla procesu załadowczego i sposób przestawiania tylnej klapy
CN107407304B (zh) * 2015-05-26 2019-02-19 日立建机株式会社 具备预热单元的工程机械及其预热方法
CN110725741A (zh) * 2019-10-15 2020-01-24 吉林大学 一种并联组合的车辆双循环冷却系统
DE102022111963A1 (de) 2022-05-12 2023-11-16 Dynapac Gmbh Straßenbaumaschine

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DE2150710A1 (de) † 1971-10-12 1973-04-19 Gewerk Eisenhuette Westfalia Einrichtung zur erwaermung der druckfluessigkeit, insbesondere schwer entflammbarer hydraulikfluessigkeiten, fuer hydraulische betriebsanlagen u.dgl
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EP2282029A1 (fr) 2011-02-09
DE502009000490D1 (de) 2011-05-05
CN101936211B (zh) 2013-03-13
CN201794654U (zh) 2011-04-13
US20100326067A1 (en) 2010-12-30
CN101936211A (zh) 2011-01-05
EP2282029B1 (fr) 2011-03-23
ATE503092T1 (de) 2011-04-15

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