EP2628862A2 - Mobile work machine with energy recovery for driving the motor cooling - Google Patents

Mobile work machine with energy recovery for driving the motor cooling 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
Other languages
German (de)
French (fr)
Other versions
EP2628862A3 (en
EP2628862B1 (en
Inventor
Jan Amrhein
Egon Rill
Sebastian Oschmann
Matthias Beck
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
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Robert Bosch GmbH
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Filing date
Publication date
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Publication of EP2628862A2 publication Critical patent/EP2628862A2/en
Publication of EP2628862A3 publication Critical patent/EP2628862A3/en
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Publication of EP2628862B1 publication Critical patent/EP2628862B1/en
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Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • 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.

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Abstract

The mobile working machine (10) has multiple hydraulic consumers (11,13) and another hydraulic consumer, where one of the former consumers has a traveling drive and an operating drive of the mobile working machine. A pressure storage (50) is provided for storing the hydraulic fluid stands under pressure, where the pressure storage stands in fluidic connection with the former consumers such that the hydraulic fluid flows back from the former consumers, in which the pressure storage runs, but not vice versa. An independent claim is included for a hydraulic drive system with a return pressure balance.

Description

Die Erfindung betrifft eine mobile Arbeitsmaschine gemäß dem Oberbegriff von Anspruch 1.The invention relates to a mobile working machine according to the preamble of claim 1.

Aus der Druckschrift " Weniger Emissionen, weniger Kosten. Hydrostatische Lüfterantriebe von Rexroth" der Bosch Rexroth AG; Bestell-Nr. RD 98 065; Ausgabe 09/2010 sind verschiede mobile Arbeitsmaschinen, insbesondere Traktoren, Mähdrescher, Bagger und Planierraupen bekannt. Diese mobilen Arbeitsmaschinen besitzen mehrer erste hydraulische Verbraucher, insbesondere einen Fahrantriebsmotor zum Antrieb der Räder bzw. der Ketten und mehrere Arbeitsantriebe in Form von Zylindern zur Verstellung beispielsweise eines Auslegerarmes; eines Planierschildes oder eines Hubwerks. Eine erste Pumpe mit verstellbarem Verdrängungsvolumen fördert Hydraulikfluid aus einem Tank zu den ersten Verbrauchern. Eine derartige Verstellpumpe ist besonders energiesparend. Die erste Pumpe wird von einem Verbrennungsmotor, meist einem Dieselmotor angetrieben. Der Verbrennungsmotor besitzt eine Flüssigkeitskühlung, bei der Kühlflüssigkeit durch einen Kühler in Form eines Lamellenwärmetauschers geleitet wird, um diese durch Wärmeabgabe an die Umgebungsluft abzukühlen. Die so abgekühlte Kühlflüssigkeit wird durch den Verbrennungsmotor gepumpt um diesen zu kühlen. Dabei heizt sich die Kühlflüssigkeit wieder auf und fließt anschließend zum Kühler zurück.From the publication " Less emissions, less costs. 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.

Die Umgebungsluft wird mit Hilfe eines Lüfterrades durch den Kühler gefördert, damit eine besonders intensive Kühlung stattfindet. Das Lüfterrad wird dabei von einem hydraulischen Lüftermotor in Drehbewegung versetzt. Weiter ist eine zweite Pumpe mit verstellbarem Verdrängungsvolumen vorgesehen, welche Hydraulikfluid aus dem Tank zu dem Lüftermotor fördern kann. Die zweite Pumpe wird ebenfalls von dem Verbrennungsmotor angetrieben und zwar in der Regel mit der gleichen Drehzahl wie die erste Pumpe. Durch Verstellung des Verdrängungsvolumens der zweiten Pumpe kann die die Drehzahl des Lüftermotors stufenlos so eingestellt werden, dass die Kühlflüssigkeit auf die optimale Temperatur abgekühlt wird.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. Further, 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.

Die Aufgabe der Erfindung besteht darin, die mobile Arbeitsmaschine energiesparender zu gestallten. Dabei soll sich das Betriebsverhalten der mobilen Arbeitsmaschine nicht in einer für den Benutzer wahrnehmbaren Weise ändern. Die mobile Arbeitsmaschine soll außerdem besonders einfach aufgebaut sein.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.

Gemäß dem selbständigen Anspruch wird diese Aufgabe dadurch gelöst, dass ein Druckspeicher zum Speichern von unter Druck stehendem Hydraulikfluid vorgesehen ist, wobei der Druckspeicher derart in Fluidverbindung mit den ersten Verbrauchern steht, dass Hydraulikfluid, welches von wenigstens einem ersten Verbraucher zurückfließt, in den Druckspeicher fließen kann, nicht aber umgekehrt, wobei der Druckspeicher derart in Fluidverbindung mit dem zweiten Verbraucher steht, dass Hydraulikfluid von dem Druckspeicher zum zweiten Verbraucher fließen kann. Druckspeicher sind als Energiespeicher bekannt. Erfindungsgemäß wird der Speicher mit dem von den ersten Verbrauchern zurückfließenden Hydraulikfluid geladen. Die ersten Verbraucher werden aber dennoch ausschließlich durch die erste Pumpe angetrieben und nicht durch das in dem Druckspeicher gespeicherte Hydraulikfluid, so dass sich das für den Benutzer wahrnehmbare Betriebsverhalten der mobilen Arbeitsmaschine nicht ändert. Das gespeicherte Hydraulikfluid wird ausschließlicht zum Antrieb des zweiten Verbrauchers und mithin zur Kühlung des Verbrennungsmotors verwendet. Soweit sich hierdurch das Betriebsverhalten der Motorkühlung etwas ändert, wird dies vom Benutzer nicht wahrgenommen.According to the independent claim, this object is achieved in that a pressure accumulator is provided 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. According to the invention, the reservoir is charged with the hydraulic fluid flowing back from the first consumers. Nevertheless, 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 ausschließlicht 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.

Anzumerken ist, dass das von den ersten Verbrauchern zurückfließende Hydraulikfluid typischerweise mit hohen Volumenströmen aber jeweils nur für kurze Zeit zurückfließt. Demgegenüber benötigt der Lüfterantrieb einen geringen aber andauernden Volumenstrom. Durch den Druckspeicher kann das unterschiedliche Zeitverhalten der genannten Volumenströme einfach einander angepasst werden. Weiter ist anzumerken, dass der Lüfterantrieb ein sehr geringes Energierückgewinnungspotential aufweist, so dass es kein Nachteil ist, wenn die Energierückgewinnung auf die ersten Verbraucher beschränkt wird.It should be noted that the hydraulic fluid flowing back from the first consumers typically only flows back for a short time at high flow rates. In contrast, 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.

In den abhängigen Ansprüchen sind vorteilhafte Weiterbildungen und Verbesserungen der Erfindung angegeben.In the dependent claims advantageous refinements and improvements of the invention are given.

Die zweite Pumpe kann so eingerichtet sein, dass sie auch als Motor betrieben werden kann, wobei sie ein verstellbares Verdrängungsvolumen aufweist, wobei sie derart in Fluidverbindung mit dem Druckspeicher steht, dass Hydraulikfluid aus dem Tank in den Druckspeicher und umgekehrt fließen kann. Damit kann das in den Druckspeicher unter Druck gespeicherte Hydraulikfluid zum motorischen Antrieb der zweiten Pumpe genutzt. Da die erste und die zweite Pumpe und der Verbrennungsmotor in Drehantriebsverbindung miteinander stehen, treibt die zweite Pumpe die erste Pumpe an und entlastet den Verbrennungsmotor. Damit können in den Fällen, in denen im Druckspeicher mehr Hydraulikfluid gespeichert ist als der zweite Verbraucher benötigt auch die ersten Verbraucher angetrieben werden. Dabei ist anzumerken, dass sich diese Form der Energierückgewinnung nur unmerklich auf das Betriebsverhalten der mobilen Arbeitsmaschine insbesondere der ersten Verbraucher auswirkt.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. Thus, 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. Thus, in cases where more hydraulic fluid is stored in the accumulator than the second consumer also requires the first consumer to be driven. It should be noted that this form of energy recovery only imperceptibly affects the performance of the mobile machine especially the first consumer.

Wenigstens ein erster Verbraucher kann dazu ausgebildet sein, äußere Lasten gegen die Schwerkraft anzuheben und abzusenken. Derartige Verbraucher besitzen ein besonders hohes Potential zur Energierückgewinnung. Als Beispiel für einen derartigen ersten Verbraucher sei die der hydraulische Motor zum Antrieb der Seilwinde eines Krans genannt. Dabei ist die genannte äußere Last die am Kranhaken angehängte Last. Als weiteres Beispiel seien die verschiedenen hydraulischen Zylinder am Auslegerarm eines Schaufelbaggers genannte. Die genannte äußere Last ist dabei die Baggerschaufel mit ihrem Inhalt.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. As an example of such a first consumer that is called the hydraulic motor for driving the winch of a crane. The said external load is the load attached to the crane hook. As another example, the various hydraulic cylinders are called on the boom arm of a shovel. The said external load is the bucket with its content.

In die Fluidverbindung zwischen den ersten Verbrauchern und dem Druckspeicher können eine stetig verstellbare Rücklaufblende und eine Rücklaufdruckwaage geschaltet sein, wobei die Rücklaufdruckwaage so an die Rücklaufblende angeschlossen ist, dass sie den Druckabfall an der Rücklaufblende auf einen vorgebbaren Wert einregeln kann. Das von den ersten Verbrauchern zurückfließende Hydraulikfluid hat meist einen anderen Druck als der Inhalt des Druckspeichers, so dass eine Druckanpassung erforderlich ist. Dabei soll sich die Bewegungsgeschwindigkeit des Verbrauchers nur abhängig von der Einstellung der Rücklaufblende ändern, wobei der Speicherdruck keinen Einfluss auf die Verfahrgeschwindigkeit des Verbrauchers haben soll. Eben dies wird durch die vorgeschlagene Zusammenschaltung von Rücklaufblende und Rücklaufdruckwaage erreicht.In the fluid connection between the first consumers and the accumulator, 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.

Die Fluidverbindung zwischen den ersten Verbrauchern und dem Druckspeicher kann so mit dem Tank verbunden sein, dass Hydraulikfluid von den ersten Verbrauchern in den Tank fließt, wenn der Druck im Druckspeicher größer als der speicherseitige Druck an der Rücklaufdrossel ist. Wenn der Druck im Druckspeicher zu hoch ist, kann das von den ersten Verbrauchern zurückfließende Hydraulikfluid nicht in den Speicher fließen. Damit muss es wenigstens mittelbar in den Tank abfließen. Hierbei kann daran gedacht sein, das genannte Hydraulikfluid unmittelbar über den zweiten Verbraucher oder über die zweite, motorisch arbeitende Pumpe, in den Tank abfließen zu lassen. Es ist aber auch möglich das genannte Hydraulikfluid direkt in den Tank abfließen zu lassen. Mit der zweiten Alternative geht zwar Energie ungenutzt verloren, sie ist dafür wesentlich einfacher realisierbar.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.

Die Erfindung wird im Folgenden anhand der beigefügten Zeichnung näher erläutert. Es stellt dar:

Fig. 1
einen hydraulischen Schaltplan einer erfindungsgemäßen mobilen Arbeitsmaschine.
The invention will be explained in more detail below with reference to the accompanying drawings. It shows:
Fig. 1
a hydraulic circuit diagram of a mobile working machine according to the invention.

Fig. 1 zeigt einen hydraulischen Schaltplan einer erfindungsgemäßen mobilen Arbeitsmaschine 10. Die mobile Arbeitsmaschine 10 umfasst einen Verbrennungsmotor 40, vorzugsweise einen Dieselmotor, welcher eine erste und eine zweite Pumpe 30; 32 mit der gleichen Drehzahl, nämlich der Drehzahl der Kurbelwelle, antreibt. Die erste Pumpe 30 fördert Hydraulikfluid aus einem Tank 16 zu mehreren ersten Verbrauchern 11; 13. Die zu den einzelnen Verbrauchern 11; 13 fließende Fluidmenge kann mittels einer Ventilbaugruppe 20 gesteuert werden. Jedem ersten Verbraucher 11; 13 ist dabei eine gesonderte, als Ganzes montierbare Verbraucherbaugruppe 21 der Ventilbaugruppe 20 zugeordnet. Die Ventilbaugruppe 20 umfasst eine Pumpenleitung 22, welche alle Verbraucherbaugruppen 21 durchsetzt, wobei die erste Pumpe 30 an die Pumpenleitung 22 angeschlossen ist. Weiter umfasst die Ventilbaugruppe 20 eine Tankleitung 23, welche alle Verbraucherbaugruppen 21 durchsetzt, wobei die Tankleitung 23 an den Tank 16 angeschlossen ist. 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. Furthermore, 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.

In jeder Verbraucherbaugruppe 21 ist ein (nicht dargestelltes) Proportionalwegeventil vorgesehen, welches so an die Pumpen- und die Tankleitung 22; 23 angeschlossen ist, dass es die Bewegung des zugeordneten Verbraucher 11; 13 steuern kann, indem es den zum Verbraucher 11; 13 fließenden und vom Verbraucher 11; 13 zurückfließenden Fluidstrom mittels stetig verstellbarer Blenden androsselt. Vorzugsweise ist jedem Proportionalwegeventil eine (nicht dargestellte) Druckwaage zugeordnet, welche den Druckabfall an den Blenden, vorzugsweise an den Blenden im Zulauf, auf einen vorgebbaren Wert einregeln kann, so dass die Bewegungsgeschwindigkeiten der ersten Verbraucher 11; 13 allein von der Einstellung der zugeordneten Proportionalwegeventile abhängt, welche von der Steuervorrichtung 17 elektrisch eingestellt wird.In 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. Preferably, 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.

Weiter sind in der Ventilbaugruppe 20 die Lastdrücke aller Verbraucher, soweit diese sich bewegen, so zusammengeschaltet, dass an der Lastdruckleitung 24 der höchste Lastdruck anliegt. Die Lastdruckleitung 24 ist an einen Förderdruckregler 31 angeschlossen, welcher das stetig verstellbare Verdrängungsvolumen der ersten Pumpe 30 so einstellt, dass der Förderdruck der ersten Pumpe 30 um eine vorgebbare Druckdifferenz über dem genannten höchsten Lastdruck liegt. Eine mögliche Ventilbaugruppe ist beispielsweise in der DE 10 2010 009 704 A1 genauer gezeigt.Further, in the 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.

An die Ventilbaugruppe 20 sind die ersten Verbraucher 11; 13 angeschlossen, nämlich ein hydraulischer Fahrantriebsmotor 11, mit welchem ein oder mehrere Räder 12 der mobilen Arbeitsmaschine 10 angetrieben werden, so dass diese gegenüber dem Untergrund bewegt werden kann. Weiter ist ein hydraulischer Zylinder 13 vorgesehen, mit welchem eine äußere Last 14 gegen die Richtung der Schwerkraft 15 angehoben werden kann. Beim Absenken der äußeren Last 14 strömt Hydraulikfluid vom Zylinder 13 unter Druck zurück. Üblicherweise wird dieses zurückfließende Hydraulikfluid vom zugeordneten Proportionalwegeventil angedrosselt und in die Tankleitung 23 zurückgeleitet.To the valve assembly 20, 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. Further, a hydraulic cylinder 13 is provided, with which an external load 14 can be raised against the direction of gravity 15. When lowering the outer load 14, hydraulic fluid from the cylinder 13 flows back under pressure. Usually, this returning hydraulic fluid is throttled by the associated proportional directional valve and returned to the tank line 23.

Bei der vorliegenden Erfindung wird dieser Fluidstrom einer stetig verstellbaren Rücklaufblende 60 zugeleitet, welche mit einer Rücklaufdruckwaage 61 in Reihe geschaltet ist. Die Rücklaufblende 60 ist dabei vorzugsweise in das zugeordnete Proportionalwegeventil integriert. Der Ventilschieber der Rücklaufdruckwaage 61 wird von einer Feder 62 in eine geöffnete Stellung gedrückt. An der Federseite ist der tank- bzw. speicherseitige Druck an der Rücklaufblende 60 angeschlossen, wobei an der Federgegenseite, der verbraucherseitige Druck an der Rücklaufblende 60 angeschlossen ist. Die Rücklaufblende 60 bildet damit zusammen mit der Rücklaufdruckwaage 61 ein 2-Wege-Stromregelventil, so dass die Senkgeschwindigkeit des ersten Verbrauchers in Form des Zylinders 11 im Wesentlichen nur von der Einstellung der Rücklaufblende 60 abhängt. Der Gesamtdruckabfall an der Rücklaufblende 60 und der Rücklaufdruckwaage 61 entspricht dem Druckunterschied zwischen dem Lastdruck am Zylinder 11 und dem Druck in dem Druckspeicher 50. Folglich wird durch die Rücklaufblende 60 nicht der gesamte Lastdruck abgedrosselt sondern nur ein Teil. Die Energie welche dem verbleibenden Druck entspricht wird in dem Druckspeicher 50 in Form von unter Druck stehendem Hydraulikfluid gespeichert.In the present invention, 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.

Für den Fall, dass der genannte Lastdruck kleiner als der Druck im Speicher 50 ist, ist ein erstes Regenerationsventil 63 vorgesehen, welches der Rücklaufdruckwaage 61 tank- bzw. speicherseitig in Reihe geschaltet ist, wobei das Regenerationsventil 63 das zurückströmende Hydraulikfluid wahlweise zum Druckspeicher 50 oder unmittelbar in den Tank 16 leiten kann. Weiter ist ein Regenerationsdrucksensor 68 vorgesehen, welcher einen Regenerationsdruck tank- bzw. speicherseitig an der Rücklaufblende 60 misst. Der Regenerationsdrucksensor 68 und das erste Regenerationsventil 63 sind an die Steuervorrichtung 17 angeschlossen, welche einen programmierbaren Digitalrechner umfasst. Der Übersichtlichkeit halber sind in Fig. 1 alle Verbindungsleitungen zwischen der Steuervorrichtung 17 und den daran angeschlossenen Gerätschaften, nämlich den Sensoren 55; 44; 68 und den elektrisch betätigbaren Ventilen 63; 45; 51; 53 und dem Verstellmechanismus der zweiten Pumpe 32; nicht dargestellt. An die Steuervorrichtung 17 ist ein Speicherdrucksensor 55 angeschlossen, welcher den Speicherdruck im Druckspeicher 50 misst. Abhängig vom Regenerationsdruck und vom Speicherdruck, stellt die Steuervorrichtung 17 das erste Regenerationsventil 63 so ein, dass das zurückfließende Hydraulikfluid entweder über den Tankausgang 65 unmittelbar in den Tank 16 oder über den Speicherausgang 64 zum Druckspeicher 50 fließt. Es ist dabei ebenso denkbar, dass die Ansteuerung des ersten Regenerationsventils 63 rein hydraulisch mittels Druckwaagen bewerkstelligt wird. Dies ist kostengünstiger aber weniger flexibel.In the event that said load pressure is less than the pressure in the memory 50, 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. Further, 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. For the sake of clarity, in Fig. 1 all 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. To the control device 17, a storage pressure sensor 55 is connected, which measures the accumulator pressure in the pressure accumulator 50. Depending on the regeneration pressure and the accumulator pressure, 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.

An den Speicherausgang 64 des ersten Regenerationsventils 63 ist der Druckspeicher 50 über ein Speicherventil 51 angeschlossen. Das Speicherventil 51 ist als leckagefreies Sitzventil ausgebildet. In der geschlossenen Stellung arbeitet das Speicherventil 51 als Rückschlagventil wobei es ausschließlich einen Fluidstrom in den Druckspeicher 50 hinein zulässt, nicht jedoch in die umgekehrte Richtung. In der geöffneten Stellung kann das Speicherventil 51 in beide Richtungen durchströmt werden. Das Speicherventil 51 wird von einer Feder in die geschlossene Stellung gedrückt, in der nur ein Beladen des Druckspeichers 50 möglich ist. Durch elektrische Ansteuerung seitens der Steuervorrichtung 17 kann es in die geöffnete Stellung geschaltet werden, in welcher der Druckspeicher 50 sowohl beladen als auch entladen werden kann.To the memory output 64 of the first regeneration valve 63, 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.

Der Druckspeicher ist der Sicherheit halber an ein Speicherdruckbegrenzungsventil 52 und ein Notentleerungsventil 53 angeschlossen, welche den Inhalt des Druckspeichers 50 in den Tank 16 ableiten können. Das Speicherdruckbegrenzungsventil 52 in Form eines leckagefreien Sitzventils begrenzt den Speicherdruck auf einen vorgegebenen Maximalwert, so dass der Druckspeicher 50 nicht bersten kann. Das Notentleerungsventil 53 ist ebenfalls als Sitzventil ausgebildet und wird von einer Feder 54 in die geöffnete Stellung gedrückt, wobei es mittels elektrischer Ansteuerung seitens der Steuervorrichtung 17 in die geschlossene Stellung geschaltet werden kann. Wenn die Steuervorrichtung 17 ausfällt oder ausgeschaltet wird, liegt das sonst vorhandene elektrische Ansteuersignal nicht mehr am Notentleerungsventil 53 an, so dass sich der Druckspeicher 50 selbsttätig entleert.For safety's sake, 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.

An den Speicherausgang 64 des ersten Regenerationsventils 63 ist weiter der zweite Verbraucher in Form des hydraulischen Lüfterantriebsmotors 41 angeschlossen. Der Lüfterantriebsmotor 41 ist vorzugsweise in Form eines Außenzahnradmotors ausgeführt und besitzt demgemäß ein konstantes Verdrängungsvolumen. Der Lüfterantriebsmotor 41 treibt ein drehbares Lüfterrad 42 an, welches einen Luftstrom auf einen Kühler 43 lenkt. Der Kühler 43 ist in Form eines Lamellenwärmetauschers ausgeführt, welcher von einer Kühlflüssigkeit durchströmt wird, wobei der genannte Luftstrom die Kühlflüssigkeit abkühlen kann. Der Kühler 43 ist mit einem Temperatursensor 44 versehen, welcher die Temperatur der abgekühlten Kühlflüssigkeit am Ausgang des Kühlers 43 misst. Der Kühler ist mit dem Verbrennungsmotor 40 über eine Ringleitung 46 verbunden, so dass die Kühlflüssigkeit von einer Kühlmittelpumpe 47 im Kreislauf gefördert werden kann. D.h. warme Kühlflüssigkeit strömt vom Verbrennungsmotor 40 zum Kühler 43 und wird dort abgekühlt. Die abgekühlte Kühlflüssigkeit strömt vom Kühler 43 wieder zum Verbrennungsmotor 40 zurück und wird dort wieder erwärt. Die Abwärme des Verbrennungsmotors 40 wird damit über die Kühlflüssigkeit an die Umgebungsluft abgegeben.To the memory output 64 of the first regeneration valve 63, the second consumer in the form of the hydraulic fan drive motor 41 is further connected. 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.

Die Druckseite der zweiten Pumpe 32 ist ebenfalls an den Speicheranschluss 64 des ersten Regenerationsventils angeschlossen. Die erste Pumpe 32 saugt im Normalfall Hydraulikfluid aus dem Tank 16 an und fördert dieses zum Lüfterantriebsmotor 41, um diesen anzutreiben. Das erste Regenerationsventil 63 befindet sich dabei in einer Schaltstellung in welcher der Speicheranschluss 64 gesperrt ist. Durch Verstellen des Verdrängungsvolumens der zweiten Pumpe 32 kann dabei die Drehzahl des Lüfterantriebsmotors 41 eingestellt werden. Das Lüfterventil 45 ist dabei ganz geöffnet.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.

Wenn der Regenerationsdrucksensor 68 einen höheren Druck als der Speicherdrucksensor 55 anzeigt, wird das erste Regenerationsventil 63 von der Steuervorrichtung 17 in die linke Stellung geschaltet, so dass das von den ersten Verbrauchern 11; 13 unter Druck zurückfließende Hydraulikfluid in den Druckspeicher 50 geladen wird. Wenn die genannte Bedingung nicht mehr vorliegt, wird das erste Regenerationsventil 63 in die recht Schaltstellungen geschaltet.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.

Wenn der Speicherdruck genügend hoch ist, wird das Verdrängungsvolumen der zweiten Pumpe auf Null gestellt, wobei das Speicherventil 51 geöffnet wird. Damit kann Hydraulikfluid aus dem Druckspeicher 50 zum Lüfterantriebsmotor 41 fließen. Die Drehzahl des Lüfterantriebsmotors 41 wird dabei mit dem Lüfterventil 45 gesteuert.When the accumulator pressure is sufficiently high, the displacement of the second pump is zeroed, and the accumulator valve 51 is opened. Thus, hydraulic fluid can flow from the pressure accumulator 50 to the fan drive motor 41. The speed of the fan drive motor 41 is controlled by the fan valve 45.

Ist der Speicherdruck zu hoch, wird das Verdrängungsvolumen der zweiten Pumpe 32 so eingestellt, dass diese als Motor arbeitet. In der Folge fließt ein Teil des Druckspeicherinhalts über die zweite Pumpe 32 in den Tank 16. Das hierdurch erzeugte Antriebsdrehmoment entlastet den Verbrennungsmotor 40 und spart damit Dieselkraftstoff ein.If the accumulator pressure is too high, 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.

Ist der Speicherdruck zu gering, um den Lüfterantriebsmotor 41 anzutreiben, bestehen mehre Möglichkeiten. Der Lüfterantriebsmotor 41 kann allein durch die zweite Pumpe 32 angetrieben werden. Zusätzlich kann der Volumenstrom der zweiten Pumpe 32 so groß eingestellt werden, dass der Druckspeicher 50 wieder auf das erforderliche Maß geladen wird. Es kann aber auch daran gedacht sein, den Druckspeicher 50 mit dem zweiten Regenerationsventil 50 weiter zur Saugseite der zweiten Pumpe 32 hin zu entladen. Die Entscheidung zwischen den genannten Möglichkeit muss abhängig von dem Volumenstrom getroffen werden, der erwartungsgemäß von den ersten Verbrauchern 11; 13 zurückfließt, wobei eine bestmögliche Ausnutzung der vom Verbrennungsmotor bereitgestellten mechanischen Antriebsenergie angestrebt wird.If the accumulator pressure is too low to drive the fan drive motor 41, there are several possibilities. The fan drive motor 41 can be driven solely by the second pump 32. In addition, 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. However, 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.

BezugszeichenlisteLIST OF REFERENCE NUMBERS

1010
Mobile ArbeitsmaschineMobile work machine
1111
FahrantriebsmotorTraction drive motor
1212
Radwheel
1313
Zylindercylinder
1414
äußere Lastexternal load
1515
Richtung der SchwerkraftDirection of gravity
1616
Tanktank
1717
Steuervorrichtungcontrol device
2020
Ventilbaugruppevalve assembly
2121
Verbraucherbaugruppeconsumers assembly
2222
Pumpenleitungpump line
2323
Tankleitungtank line
2424
LastdruckleitungLast pressure line
3030
erste Pumpefirst pump
3131
FörderdruckreglerDelivery pressure regulator
3232
zweite Pumpesecond pump
4040
Verbrennungsmotorinternal combustion engine
4141
LüfterantriebsmotorFan drive motor
4242
Lüfterradfan
4343
Kühlercooler
4444
Temperatursensortemperature sensor
4545
Lüfterventilfan valve
4646
Ringleitungloop
4747
KühlmittelpumpeCoolant pump
5050
Druckspeicheraccumulator
5151
Speicherventilmemory valve
5252
SpeicherdruckbegrenzungsventilStorage pressure limiting valve
5353
NotentleerungsventilNotentleerungsventil
5454
Feder des NotentleerungsventilsSpring of emergency drain valve
5555
SpeicherdrucksensorAccumulator pressure sensor
6060
RücklaufblendeReturn panel
6161
RücklaufdruckwaageReturn pressure compensator
6262
Feder der RücklaufdruckwaageSpring of the return pressure balance
6363
erstes Regenerationsventilfirst regeneration valve
6464
Speicherausgangmemory output
6565
Tankausgangtank outlet
6868
RegenerationsdrucksensorRegeneration pressure sensor

Claims (5)

Mobile Arbeitsmaschine (10) mit mehreren ersten hydraulischen Verbrauchern (11; 13) und einem zweiten hydraulischen Verbraucher (41), wobei die ersten Verbraucher (11; 13) einen Fahrantrieb und/oder einen Arbeitsantrieb der mobilen Arbeitsmaschine (10) umfassen, wobei eine erste Pumpe (30) mit verstellbarem Verdrängungsvolumen Hydraulikfluid aus einem Tank (16) zu den ersten Verbrauchern (11; 13) fördern kann, wobei eine zweite Pumpe (32) Hydraulikfluid aus dem Tank (16) zu dem zweiten Verbraucher (41) fördern kann, wobei ein Verbrennungsmotor (40) vorgesehen ist, der mit der ersten und der zweiten Pumpe (30; 32) in Drehantriebsverbindung steht, wobei der zweite Verbraucher (41) ein drehbares Lüfterrad (42) zur Kühlung des Verbrennungsmotors (40) antreibt,
dadurch gekennzeichnet, dass ein Druckspeicher (50) zum Speichern von unter Druck stehendem Hydraulikfluid vorgesehen ist, wobei der Druckspeicher (50) derart in Fluidverbindung mit den ersten Verbrauchern (11; 13) steht, dass Hydraulikfluid, welches von wenigstens einem ersten Verbraucher (13) zurückfließt, in den Druckspeicher (50) fließen kann, nicht aber umgekehrt, wobei der Druckspeicher (50) derart in Fluidverbindung mit dem zweiten Verbraucher (41) steht, dass Hydraulikfluid von dem Druckspeicher (50) zum zweiten Verbraucher fließen kann.Mobile work machine (10) having a plurality of first hydraulic consumers (11; 13) and a second hydraulic consumer (41), wherein the first consumers (11; 13) comprise a travel drive and / or a working drive of the mobile work machine (10), wherein a first variable displacement pump (30) may deliver hydraulic fluid from a tank (16) to the first consumers (11; 13), wherein a second pump (32) may deliver hydraulic fluid from the tank (16) to the second consumer (41) wherein an internal combustion engine (40) is provided in rotational drive communication with the first and second pumps (30; 32), the second consumer (41) driving a rotatable fan (42) to cool the internal combustion engine (40),
characterized in that a pressure accumulator (50) is provided for storing pressurized hydraulic fluid, the accumulator (50) being in fluid communication with the first consumers (11; 13), hydraulic fluid supplied from at least one first consumer (13 ), can flow into the pressure accumulator (50), but not vice versa, wherein the accumulator (50) is in fluid communication with the second load (41) such that hydraulic fluid can flow from the pressure accumulator (50) to the second consumer. Mobile Arbeitsmaschine nach Anspruch 1,
dadurch gekennzeichnet, dass die zweite Pumpe (32) so eingerichtet ist, dass sie auch als Motor betrieben werden kann, wobei sie ein verstellbares Verdrängungsvolumen aufweist, wobei sie derart in Fluidverbindung mit dem Druckspeicher (50) steht, dass Hydraulikfluid aus dem Tank (16) in den Druckspeicher (50) und umgekehrt fließen kann.Mobile work machine according to claim 1,
characterized in that the second pump (32) is adapted to also be operated as a motor, having an adjustable displacement volume in fluid communication with the accumulator (50) such that hydraulic fluid from the tank (16 ) can flow into the accumulator (50) and vice versa. Hydraulisches Antriebssystem nach einem der vorstehenden Ansprüche,
dadurch gekennzeichnet, dass wenigstens ein erster Verbraucher dazu ausgebildet ist, äußere Lasten gegen die Schwerkraft anzuheben und abzusenken.Hydraulic drive system according to one of the preceding claims,
characterized in that at least one first consumer is adapted to raise and lower external loads against gravity. Hydraulisches Antriebssystem nach einem der vorstehenden Ansprüche,
dadurch gekennzeichnet, dass in die Fluidverbindung zwischen den ersten Verbrauchern (11; 13) und dem Druckspeicher (50) eine stetig verstellbare Rücklaufblende (60) und eine Rücklaufdruckwaage (61) geschaltet sind, wobei die Rücklaufdruckwaage (61) so an die Rücklaufblende (60) angeschlossen ist, dass sie den Druckabfall an der Rücklaufblende (60) auf einen vorgebbaren Wert einregeln kann.Hydraulic drive system according to one of the preceding claims,
characterized in that in the fluid connection between the first consumers (11; 13) and the pressure accumulator (50) a continuously adjustable return orifice (60) and a return pressure compensator (61) are connected, wherein the return pressure compensator (61) to the return orifice (60 ) is connected, that they can adjust the pressure drop at the return aperture (60) to a predetermined value. Hydraulisches Antriebssystem nach Anspruch 4,
dadurch gekennzeichnet, dass die Fluidverbindung zwischen den ersten Verbrauchern (11; 13) und dem Druckspeicher (50) so mit dem Tank verbunden ist, dass Hydraulikfluid von den ersten Verbrauchern (11; 13) in den Tank fließt, wenn der Druck im Druckspeicher (50) größer als der speicherseitige Druck an der Rücklaufdrossel (60) ist.Hydraulic drive system according to claim 4,
characterized in that the fluid communication between the first consumers (11; 13) and the accumulator (50) is connected to the tank such that hydraulic fluid from the first consumers (11; 13) flows into the tank when the pressure in the pressure accumulator ( 50) is greater than the memory-side pressure at the return throttle (60).
EP13152809.3A 2012-02-18 2013-01-28 Mobile work machine with energy recovery for driving the motor cooling Active EP2628862B1 (en)

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EP2628862B1 (en) 2020-03-11

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