EP2628862A2 - Machine de travail mobile avec production d'énergie pour l'entraînement du refroidissement du moteur - Google Patents

Machine de travail mobile avec production d'énergie pour l'entraînement du refroidissement du moteur Download PDF

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Publication number
EP2628862A2
EP2628862A2 EP13152809.3A EP13152809A EP2628862A2 EP 2628862 A2 EP2628862 A2 EP 2628862A2 EP 13152809 A EP13152809 A EP 13152809A EP 2628862 A2 EP2628862 A2 EP 2628862A2
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EP
European Patent Office
Prior art keywords
pressure
accumulator
consumers
hydraulic
consumer
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
EP13152809.3A
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German (de)
English (en)
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EP2628862A3 (fr
EP2628862B1 (fr
Inventor
Jan Amrhein
Egon Rill
Sebastian Oschmann
Matthias Beck
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP2628862A3 publication Critical patent/EP2628862A3/fr
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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
    • F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
    • F15B21/14—Energy-recuperation 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
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66C—CRANES; LOAD-ENGAGING ELEMENTS OR DEVICES FOR CRANES, CAPSTANS, WINCHES, OR TACKLES
    • B66C13/00—Other constructional features or details
    • B66C13/18—Control systems or devices
    • B66C13/20—Control systems or devices for non-electric 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
    • 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
    • E02F9/2217—Hydraulic or pneumatic drives with energy recovery arrangements, e.g. using accumulators, flywheels
    • 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
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2278—Hydraulic circuits
    • E02F9/2292—Systems with two or more pumps
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2278—Hydraulic circuits
    • E02F9/2296—Systems with a variable displacement pump
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
    • F15B1/02—Installations or systems with accumulators
    • F15B1/024—Installations or systems with accumulators used as a supplementary power source, e.g. to store energy in idle periods to balance pump load
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/17—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors using two or more pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/20507—Type of prime mover
    • 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
    • F15B2211/20507—Type of prime mover
    • F15B2211/20523—Internal combustion engine
    • 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
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20569—Type of pump capable of working as pump and motor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/20576—Systems with pumps with multiple pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/21—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge
    • F15B2211/212—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge the pressure sources being accumulators
    • 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
    • F15B2211/40569—Flow control characterised by the type of flow control means or valve with pressure compensating valves the pressure compensating valve arranged downstream 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
    • F15B2211/41554—Flow control characterised by the connections of the flow control means in the circuit being connected to a return line 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
    • F15B2211/60—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
    • F15B2211/70—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
    • F15B2211/7142—Multiple output members, e.g. multiple hydraulic motors or cylinders the output members being arranged in multiple groups
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/80—Other types of control related to particular problems or conditions
    • F15B2211/88—Control measures for saving energy

Definitions

  • the invention relates to a mobile working machine according to the preamble of claim 1.
  • Hydrostatic Fan Drives from Rexroth from Bosch Rexroth AG, order No. RD 98 065, issue 09/2010 are various mobile machines, especially tractors, combine harvesters, excavators and bulldozers known. These mobile machines have several first hydraulic consumers, in particular a traction drive motor for driving the wheels or chains and a plurality of working drives in the form of cylinders for adjusting, for example, a cantilever arm; a dozer blade or a hoist.
  • a first variable displacement pump delivers hydraulic fluid from a tank to the first consumers. Such a variable displacement pump is particularly energy-efficient.
  • the first pump is powered by an internal combustion engine, usually a diesel engine.
  • the internal combustion engine has a liquid cooling, in which cooling liquid is passed through a cooler in the form of a finned heat exchanger to cool them by dissipating heat to the ambient air.
  • the thus cooled cooling liquid is pumped by the internal combustion engine to cool it.
  • the coolant heats up again and then flows back to the radiator.
  • the ambient air is conveyed with the help of a fan wheel through the radiator, so that a particularly intensive cooling takes place.
  • the fan wheel is set in rotation by a hydraulic fan motor.
  • a second pump is provided with adjustable displacement volume, which can promote hydraulic fluid from the tank to the fan motor.
  • the second pump is also from driven by the internal combustion engine and that usually with the same speed as the first pump. By adjusting the displacement of the second pump, the speed of the fan motor can be adjusted continuously so that the cooling liquid is cooled to the optimum temperature.
  • the object of the invention is to make the mobile machine energy-saving.
  • the operating behavior of the mobile machine should not change in a perceptible for the user.
  • the mobile machine should also be very simple.
  • a pressure accumulator for storing pressurized hydraulic fluid, wherein the pressure accumulator is in fluid communication with the first consumers, that hydraulic fluid, which flows back from at least one first consumer, flow into the pressure accumulator can, but not vice versa, wherein the pressure accumulator is in fluid communication with the second consumer so that hydraulic fluid can flow from the pressure accumulator to the second consumer.
  • Accumulators are known as energy storage.
  • the reservoir is charged with the hydraulic fluid flowing back from the first consumers.
  • the first consumers are driven exclusively by the first pump and not by the hydraulic fluid stored in the pressure accumulator, so that the perceptible operating behavior of the mobile working machine does not change for the user.
  • the stored hydraulic fluid is fittedt used to drive the second consumer and thus for cooling the internal combustion engine. As far as this changes the operating behavior of the engine cooling something, this is not perceived by the user.
  • the hydraulic fluid flowing back from the first consumers typically only flows back for a short time at high flow rates.
  • the fan drive requires a small but sustained volume flow. Through the pressure accumulator, the different time behavior of said volume flows can be easily adapted to each other. It should also be noted that the fan drive has a very low energy recovery potential, so it is not a disadvantage if energy recovery is limited to the first consumers.
  • the second pump may be arranged to also operate as a motor having an adjustable displacement volume in fluid communication with the accumulator such that hydraulic fluid can flow from the tank to the accumulator and vice versa.
  • the stored under pressure in the pressure accumulator hydraulic fluid used for motor drive of the second pump Since the first and second pumps and the internal combustion engine are in rotary drive communication with each other, the second pump drives the first pump and relieves the internal combustion engine.
  • this form of energy recovery only imperceptibly affects the performance of the mobile machine especially the first consumer.
  • At least one first consumer may be configured to raise and lower external loads against gravity.
  • Such consumers have a particularly high potential for energy recovery.
  • the hydraulic motor for driving the winch of a crane The said external load is the load attached to the crane hook.
  • the various hydraulic cylinders are called on the boom arm of a shovel.
  • the said external load is the bucket with its content.
  • a continuously adjustable return orifice and a return pressure compensator may be connected, wherein the return pressure compensator so to the return orifice is connected, that they can adjust the pressure drop across the return plate to a predetermined value.
  • the hydraulic fluid flowing back from the first consumers usually has a different pressure than the contents of the pressure accumulator, so that a pressure adjustment is required.
  • the movement speed of the consumer should only change depending on the setting of the return orifice, wherein the accumulator pressure should have no influence on the travel speed of the consumer. This is achieved by the proposed interconnection of the return orifice and return pressure compensator.
  • the fluid communication between the first consumers and the accumulator may be connected to the tank such that hydraulic fluid from the first consumers flows into the tank when the pressure in the pressure accumulator is greater than the accumulator-side pressure at the return throttle. If the pressure in the pressure accumulator is too high, the hydraulic fluid returning from the first consumers can not flow into the accumulator. So it has to flow at least indirectly into the tank. In this case, it can be thought of to let the said hydraulic fluid flow directly into the tank via the second consumer or via the second, motor-operated pump. But it is also possible to drain the said hydraulic fluid directly into the tank. With the second alternative energy is lost unused, it is much easier to realize.
  • Fig. 1 shows a hydraulic circuit diagram of a mobile work machine 10 according to the invention.
  • the mobile work machine 10 comprises an internal combustion engine 40, preferably a diesel engine, which comprises a first and a second pump 30; 32 with the same speed, namely the speed of Crankshaft, drives.
  • the first pump 30 delivers hydraulic fluid from a tank 16 to a plurality of first consumers 11; 13.
  • the individual consumers 11; 13 flowing fluid amount can be controlled by means of a valve assembly 20.
  • Each first consumer 11; 13 is assigned a separate, as a whole mountable consumer assembly 21 of the valve assembly 20.
  • the valve assembly 20 includes a pump line 22, which passes through all the consumer assemblies 21, wherein the first pump 30 is connected to the pump line 22.
  • the valve assembly 20 comprises a tank line 23, which passes through all the consumer assemblies 21, the tank line 23 being connected to the tank 16.
  • each consumer assembly 21 a (not shown) proportional directional control valve is provided which so to the pump and the tank line 22; 23 is connected, that it is the movement of the associated consumer 11; 13 can control, by the consumer 11; 13 flowing and from the consumer 11; 13 throttles back flowing fluid flow by means of continuously adjustable apertures.
  • each proportional directional valve (not shown) associated with a pressure compensator, which can adjust the pressure drop across the orifices, preferably at the aperture in the inlet to a predetermined value, so that the movement speeds of the first consumer 11; 13 depends solely on the setting of the associated proportional directional control valves, which is electrically adjusted by the control device 17.
  • valve assembly 20 the load pressures of all consumers, as far as they move, so interconnected that applied to the load pressure line 24, the highest load pressure.
  • the load pressure line 24 is connected to a delivery pressure regulator 31, which adjusts the continuously variable displacement volume of the first pump 30 so that the delivery pressure of the first pump 30 is above the said highest load pressure by a predeterminable pressure difference.
  • a possible valve assembly is for example in the DE 10 2010 009 704 A1 shown in more detail.
  • the first consumer 11 13, namely a hydraulic traction drive motor 11, with which one or more wheels 12 of the mobile working machine 10 are driven, so that it can be moved relative to the ground.
  • a hydraulic cylinder 13 is provided, with which an external load 14 can be raised against the direction of gravity 15.
  • hydraulic fluid from the cylinder 13 flows back under pressure.
  • this returning hydraulic fluid is throttled by the associated proportional directional valve and returned to the tank line 23.
  • this fluid flow is supplied to a continuously variable return orifice 60 which is connected in series with a return pressure compensator 61.
  • the return aperture 60 is preferably integrated in the associated proportional directional control valve.
  • the valve spool of the return pressure compensator 61 is pressed by a spring 62 in an open position.
  • On the spring side of the tank or memory-side pressure on the return plate 60 is connected, being connected to the spring opposite side, the consumer-side pressure on the return plate 60.
  • the return orifice 60 thus forms, together with the return pressure compensator 61, a 2-way flow control valve, so that the lowering speed of the first consumer in the form of the cylinder 11 essentially depends only on the setting of the return orifice 60.
  • the total pressure drop at the return orifice 60 and the return pressure compensator 61 corresponds to the pressure difference between the load pressure at the cylinder 11 and the pressure in the pressure accumulator 50. Consequently, not the entire load pressure is throttled by the return orifice 60 but only a part. The energy corresponding to the remaining pressure is stored in the pressure accumulator 50 in the form of pressurized hydraulic fluid.
  • a first regeneration valve 63 is provided, which is connected in series to the return pressure compensator 61 tank or storage side, wherein the regeneration valve 63, the hydraulic fluid flowing back either to the pressure accumulator 50 or can lead directly into the tank 16.
  • a regeneration pressure sensor 68 is provided which a regeneration pressure tank or memory side of the return aperture 60th measures. The regeneration pressure sensor 68 and the first regeneration valve 63 are connected to the controller 17, which includes a programmable digital computer.
  • connection lines between the control device 17 and the equipment connected thereto namely the sensors 55; 44; 68 and the electrically operable valves 63; 45; 51; 53 and the adjusting mechanism of the second pump 32; not shown.
  • a storage pressure sensor 55 is connected, which measures the accumulator pressure in the pressure accumulator 50.
  • the control device 17 sets the first regeneration valve 63 such that the returning hydraulic fluid flows either directly to the tank 16 via the tank outlet 65 or to the pressure accumulator 50 via the accumulator outlet 64. It is also conceivable that the control of the first regeneration valve 63 is accomplished purely hydraulically by means of pressure compensators. This is cheaper but less flexible.
  • the pressure accumulator 50 is connected via a storage valve 51.
  • the storage valve 51 is designed as a leakage-free seat valve. In the closed position, the accumulator valve 51 operates as a check valve, allowing only a fluid flow into the pressure accumulator 50, but not in the opposite direction. In the open position, the storage valve 51 can be flowed through in both directions. The storage valve 51 is pressed by a spring in the closed position in which only a loading of the pressure accumulator 50 is possible. By electrical control by the control device 17, it can be switched to the open position, in which the pressure accumulator 50 can be both loaded and unloaded.
  • the pressure accumulator is connected to a accumulator pressure limiting valve 52 and to an emergency evacuation valve 53, which can divert the contents of the pressure accumulator 50 into the tank 16.
  • the accumulator pressure limiting valve 52 in the form of a leakage-free seat valve limits the accumulator pressure to a predetermined maximum value, so that the pressure accumulator 50 can not burst.
  • the Emergency emptying valve 53 is also designed as a seat valve and is pressed by a spring 54 in the open position, wherein it can be switched by means of electrical control by the control device 17 in the closed position. If the control device 17 fails or is turned off, the otherwise existing electrical control signal is no longer applied to the emergency discharge valve 53, so that the pressure accumulator 50 automatically empties.
  • the fan drive motor 41 is preferably designed in the form of an external gear motor and accordingly has a constant displacement volume.
  • the fan drive motor 41 drives a rotatable fan 42, which directs an air flow to a radiator 43.
  • the cooler 43 is designed in the form of a plate heat exchanger, which is flowed through by a cooling liquid, wherein said air flow can cool the cooling liquid.
  • the cooler 43 is provided with a temperature sensor 44, which measures the temperature of the cooled cooling liquid at the outlet of the cooler 43.
  • the radiator is connected to the internal combustion engine 40 via a ring line 46, so that the coolant can be circulated by a coolant pump 47.
  • That Warm coolant flows from the engine 40 to the radiator 43 and is cooled there.
  • the cooled cooling liquid flows back from the radiator 43 to the internal combustion engine 40 and is re-identified there.
  • the waste heat of the internal combustion engine 40 is thus released via the coolant to the ambient air.
  • the pressure side of the second pump 32 is also connected to the storage port 64 of the first regeneration valve.
  • the first pump 32 sucks hydraulic fluid from the tank 16 in the normal case and conveys this to the fan drive motor 41 in order to drive it.
  • the first regeneration valve 63 is located in a switching position in which the storage port 64 is locked. By adjusting the displacement of the second pump 32, the speed of the Fan drive motor 41 can be adjusted.
  • the fan valve 45 is completely open.
  • the first regeneration valve 63 When the regeneration pressure sensor 68 indicates a higher pressure than the accumulator pressure sensor 55, the first regeneration valve 63 is switched to the left position by the control device 17, so that the one of the first consumers 11; 13, hydraulic fluid flowing back under pressure is charged into the pressure accumulator 50. If the said condition is no longer present, the first regeneration valve 63 is switched to the right switch positions.
  • the displacement of the second pump 32 is set to operate as a motor. As a result, part of the pressure accumulator contents flows via the second pump 32 into the tank 16. The drive torque generated thereby relieves the internal combustion engine 40 and thus saves diesel fuel.
  • the fan drive motor 41 can be driven solely by the second pump 32.
  • the volume flow of the second pump 32 can be set so large that the pressure accumulator 50 is charged again to the required level.
  • it can also be thought to discharge the pressure accumulator 50 with the second regeneration valve 50 on to the suction side of the second pump 32. The decision between said option must be made depending on the volume flow expected by the first consumers 11; Flows back 13, with the best possible utilization of the provided by the engine mechanical drive energy is sought.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mining & Mineral Resources (AREA)
  • Civil Engineering (AREA)
  • Structural Engineering (AREA)
  • Analytical Chemistry (AREA)
  • Chemical & Material Sciences (AREA)
  • Automation & Control Theory (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Arrangement Or Mounting Of Propulsion Units For Vehicles (AREA)
  • Cooling, Air Intake And Gas Exhaust, And Fuel Tank Arrangements In Propulsion Units (AREA)
EP13152809.3A 2012-02-18 2013-01-28 Machine de travail mobile avec production d'énergie pour l'entraînement du refroidissement du moteur Active EP2628862B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102012003320A DE102012003320A1 (de) 2012-02-18 2012-02-18 Mobile Arbeitsmaschine mit Energierückgewinnung zum Antrieb der Motorkühlung

Publications (3)

Publication Number Publication Date
EP2628862A2 true EP2628862A2 (fr) 2013-08-21
EP2628862A3 EP2628862A3 (fr) 2017-11-15
EP2628862B1 EP2628862B1 (fr) 2020-03-11

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Country Link
EP (1) EP2628862B1 (fr)
KR (1) KR20130095676A (fr)
CN (1) CN103256260B (fr)
DE (1) DE102012003320A1 (fr)

Cited By (2)

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EP2855784A4 (fr) * 2012-05-30 2016-06-01 Volvo Constr Equip Ab Procédé pour récupérer de l'énergie et système hydraulique
CN116517923A (zh) * 2023-04-12 2023-08-01 徐州徐工挖掘机械有限公司 一种温度控制系统及工程机械

Families Citing this family (8)

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KR102183217B1 (ko) * 2014-03-24 2020-11-25 두산인프라코어 주식회사 유압 활용 엔진 시스템
US9890804B2 (en) * 2014-03-24 2018-02-13 Doosan Infracore Co., Ltd. Engine system utilizing hydraulic pressure
CN103896156B (zh) * 2014-04-24 2016-02-24 徐州重型机械有限公司 一种起重机用节能液压系统及起重机
DE102014216031A1 (de) 2014-08-13 2016-03-10 Robert Bosch Gmbh Hydrostatischer Antrieb und Ventilvorrichtung dafür
CN105508331B (zh) * 2016-01-27 2017-09-29 徐州徐工挖掘机械有限公司 一种有源定比分流组件
DE102017210011A1 (de) * 2017-06-14 2018-12-20 Robert Bosch Gmbh Ventilanordnung für einen Fahrantrieb
CN108317134B (zh) * 2018-02-09 2019-10-01 东北大学 一种基于液压回路的减速带能量利用装置
DE102023101659A1 (de) * 2023-01-24 2024-07-25 Claas Selbstfahrende Erntemaschinen Gmbh Hydrauliksystem für eine landwirtschaftliche Arbeitsmaschine

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DE4342006A1 (de) * 1993-12-09 1995-06-14 Bosch Gmbh Robert Hydraulisches Bordnetz für Fahrzeuge
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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2855784A4 (fr) * 2012-05-30 2016-06-01 Volvo Constr Equip Ab Procédé pour récupérer de l'énergie et système hydraulique
CN116517923A (zh) * 2023-04-12 2023-08-01 徐州徐工挖掘机械有限公司 一种温度控制系统及工程机械

Also Published As

Publication number Publication date
EP2628862A3 (fr) 2017-11-15
DE102012003320A1 (de) 2013-08-22
CN103256260B (zh) 2017-07-14
EP2628862B1 (fr) 2020-03-11
KR20130095676A (ko) 2013-08-28
CN103256260A (zh) 2013-08-21

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