CN103339388A - Hydraulic fan circuit having energy recovery - Google Patents

Hydraulic fan circuit having energy recovery Download PDF

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Publication number
CN103339388A
CN103339388A CN2011800660769A CN201180066076A CN103339388A CN 103339388 A CN103339388 A CN 103339388A CN 2011800660769 A CN2011800660769 A CN 2011800660769A CN 201180066076 A CN201180066076 A CN 201180066076A CN 103339388 A CN103339388 A CN 103339388A
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CN
China
Prior art keywords
motor
fluid
pressure
fan
low
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Pending
Application number
CN2011800660769A
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Chinese (zh)
Inventor
B·E·尼尔森
J·T·彼得森
J·L·奎恩
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Caterpillar Inc
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Caterpillar Inc
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Publication of CN103339388A publication Critical patent/CN103339388A/en
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    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P7/00—Controlling of coolant flow
    • F01P7/02—Controlling of coolant flow the coolant being cooling-air
    • F01P7/04—Controlling of coolant flow the coolant being cooling-air by varying pump speed, e.g. by changing pump-drive gear ratio
    • F01P7/044—Controlling of coolant flow the coolant being cooling-air by varying pump speed, e.g. by changing pump-drive gear ratio using hydraulic drives
    • 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
    • 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
    • F15B2211/20561—Type of pump reversible
    • 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
    • F15B2211/27—Directional control by means of the pressure source
    • 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
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/315—Directional control characterised by the connections of the valve or valves in the circuit
    • F15B2211/31523—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source and an output member
    • F15B2211/31529—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source and an output member having a single pressure source and a single 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/625—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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/633—Electronic controllers using input signals representing a state of the prime mover, e.g. torque or rotational speed
    • 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
    • F15B2211/6336—Electronic controllers using input signals representing a state of the output member, e.g. position, speed or acceleration
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/665—Methods of control using electronic components
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/665—Methods of control using electronic components
    • F15B2211/6652—Control of the pressure source, e.g. control of the swash plate angle
    • 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
    • F15B2211/80—Other types of control related to particular problems or conditions
    • F15B2211/88—Control measures for saving energy

Abstract

A hydraulic fan circuit (10) is disclosed. The hydraulic fan circuit may have a primary pump (14), a high-pressure passage (26) fluidly connected to the primary pump, and a low-pressure passage (24) fluidly connected to the primary pump. The hydraulic fan circuit may also have at least one accumulator (68, 70) in selective fluid communication with at least one of the high- and low- pressure passages, a motor (18), and a fan (20) connected to the motor. The hydraulic fan circuit may further have a fan isolation valve (84) fluidly connected to the high- and low-pressure passages. The fan isolation valve may be movable between a flow-passing position at which the motor is fluidly connected to the primary pump via the high- and low-pressure passages, and a flow-blocking position at which the motor is substantially isolated from the primary pump.

Description

Has the hydraulic fan loop that energy reclaims
Technical field
The present invention generally relates to a kind of hydraulic fan loop, particularly a kind of hydraulic fan loop with energy recovery.
Background technique
Engine-driven machine as bulldozer, loader, excavator, motor grader and other jumbo, generally includes correlation engine and other machine assembly is cooled to cooling system below the threshold value, prepares for machine longevity thus.Cooling system comprises one or more air-airs and/or liquid-air heat exchanger, and its cool cycles is by the freezing mixture of motor and the combustion-supporting air of importing motor.The heat of freezing mixture or combustion-supporting air can be delivered to the air that flows out from fan, controls the speed of this fan based on the temperature of the temperature of motor and related fluid pressing system.
Common hydraulic driving cooling system fan.That is to say that engine-driven pump sucks low-pressure fluid and discharges the fluid in to the motor of connection fan with the pressure that improves.When the temperature of motor exceeded expection, pump and motor co-operation were to improve the speed of fan.When the temperature of motor was low, pump and motor co-operation to be reducing the speed of fan, and in some cases, even fan is stopped.Under some conditions, even the rotation of reversible fan, thereby also can make the gas flow reversing that passes heat exchanger, to be conducive to get rid of any chip that accumulates in the heat exchanger.
Though having sometimes, cooled engine effectively, other oil hydraulic circuit that drives the oil hydraulic circuit of above-mentioned cooling fan and/or uniform machinery do not use or even the excess energy of waste.Along with environmental problem receives publicity day by day, particularly to the concern of machine fuel consumption, fully use all resources to become more and more important.
U.S. Patent No. 7,444,809 have described the trial that is intended to improve oil hydraulic circuit efficient, and this patent belongs to Smith Deng the peopleIssue on November 4th, 2008 (" ' 809 patents ").Particularly, ' 809 patent has been described stability hydraulic (hyStat) system with Engine Driven Pump, and this Engine Driven Pump is connected to motor with the closed-loop path structure.When exceeding pump capacity, the charging fluid of efflux pump is stored in the accumulator in order to follow-up use.The charging fluid of storage can be used for driven pump and/or motor then, alleviates the load of motor thus.From the charging fluid of other oil hydraulic circuit of uniform machinery, for example activate the loop from instrument, also can be stored in the accumulator and optionally in order to driven pump and motor, thereby further reduce the fuel consumption of motor.
Though the system of ' 809 patent can raise the efficiency, it also has the narrow limitation of Applicable scope.That is to say that this system reclaims in the operation process at energy can not isolate motor.In some applications, drive as cooling fan, when the accumulator internal pressure changes, can cause by building up fluid-operated fan motor and turn round with unexpected speed.In addition, the drive fan motor can cause energy dissipation and possible motor too to cool off when not needing to cool off.
Above-mentioned one or more problems of enumerating and/or the other problem of prior art are intended to overcome in the hydraulic fan loop of disclosing.
Summary of the invention
On the one hand, the present invention relates to a kind of hydraulic fan loop.This hydraulic fan loop comprises main pump, the high-pressure channel that is connected with the main pump fluid and the low-pressure channel that is connected with the main pump fluid.The hydraulic fan loop also can comprise with high-pressure channel and low-pressure channel at least one optionally at least one accumulator, the motor that are connected of fluid and the fan that is connected to motor.The hydraulic fan loop also can comprise the fan separating valve that is connected with the low-pressure channel fluid with high-pressure channel.The fan separating valve can move between percolation position and choke position, and wherein, motor is connected to main pump by high-pressure channel and low-pressure channel fluid when the percolation position, and the basic and main pump isolation of motor when choke position.
On the other hand, the present invention relates to another kind of hydraulic fan loop.This hydraulic fan loop can comprise main pump, motor, be connected to the fan of motor and the closed-loop path that the main pump fluid is connected to motor.The hydraulic fan loop also can comprise and the closed-loop path high-voltage energy storage device, the low pressure accumulator that is communicated with the closed-loop path fluid, the accumulator escape cock that is communicated with high-voltage energy storage device and low pressure accumulator fluid and the fluid that are communicated with of the fluid fan separating valve that is connected to closed-loop path and motor optionally.The hydraulic fan loop can further comprise the controller that is communicated with accumulator escape cock and fan separating valve.Controller can be configured to adjust the accumulator escape cock, thereby optionally fluid is transferred to high-voltage energy storage device and is transferred to main pump from high-voltage energy storage device from main pump, and optionally fluid is transferred to the low pressure accumulator and is transferred to main pump from the low pressure accumulator from motor.Controller can further be configured to adjust the fan separating valve, in the high-voltage energy storage device discharge process motor is isolated substantially from main pump.
On the one hand, the present invention relates to from a kind of method of hydraulic fan loop recovered energy again.This method comprises with the supercharging of pump convection cell, makes charging fluid drive fan motor, and builds up the overpressurization fluid.This method can comprise that also the fluid that optionally discharging is built up is used for driven pump, and isolates fan motor substantially from pump in discharge process.
Description of drawings
Fig. 1 is illustrating of the excavation machine that discloses in the example;
Fig. 2 is the schematic representation in the hydraulic fan loop of disclosing in the example, the utilization that can combine with the excavation machine of Fig. 1 of this hydraulic fan loop; And
Fig. 3 is the schematic representation in the hydraulic fan loop of disclosing in another example, the utilization that can combine with the excavation machine of Fig. 1 of this hydraulic fan loop.
Embodiment
Fig. 1 shows in the building site 210 example machine 200 with specific function.Machine 200 can show as fixing or mobile machine, has the specific function relevant with industry, as dig up mine, build, cultivate, transport, generating, oil and gas or other industry known in the art.For example, machine 200 can be the muck haulage machine of the excavator described such as Fig. 1, and wherein, specific function comprises that from the building site 210 remove native stone material, and the topographic change in building site 210 is become required situation.Perhaps, machine 200 can show as different muck haulage machines, as motor grader or wheel loader, or is not used in the machine of muck haulage, as passenger plane motor-car, stationary power generation unit or pumping mechanism.Machine 200 can show as the work machine of any appropriate.
Machine 200 can be equipped with a plurality of systems that are beneficial in the building site 210 running machines 200, for example tool system 220, drive system 230 and the engine system 240 of power is provided to tool system 220 and drive system 230.In finishing the process of most of tasks, the power of engine system 240 can unbalanced distribution between tool system 220 and drive system 230.That is, in most cases, machine 200 can excavate between the building site mobilely and mainly supply with power to drive system 230, or is parked in and excavates the building site and by mainly supplying with power with positive mobile material to tool system 220.Machine 200 is not run at high speed usually, actively transports big load material by tool system 220 simultaneously.Therefore, the size of the adjustable motivational system 240 of haircuting, thereby the greatest requirements that provides enough power to satisfy tool system 220 or drive system 230, but can not satisfy both demand simultaneously.Though be enough to satisfy most of situations, may have following situation: total power demand of machine system (as tool system 220 and/or drive system 230) surpasses the power supply ability of engine system 240.Engine system 240 can be configured to receive and keep next time at above-mentioned condition the energy of storage, thereby improves supply capacity temporarily.If desired, this extra supply capacity produces the fuel consumption that can or optionally make engine system 240 and reduces by allowing optionally to reduce engine system 240 power.
As shown in Figure 2, engine system 240 can comprise the heat engine 12 that is equipped with hydraulic fan loop 10, for example internal-combustion engine.Hydraulic fan loop 10 can comprise the set of a plurality of assemblies, and these assemblies provide power to be used for cooled engine 12 by motor 12.Particularly, hydraulic fan loop 10 fan 20 that can comprise the main pump 14 of the machinery output 16 that is directly connected to motor 12, be connected to the motor 18 of main pump 14 and be connected to motor 18 by closed-loop path 22 fluids.Motor 12 can drive main pump 14 by machinery output 16, thereby sucks low-pressure fluid and the pressure exhaust fluid to improve.Motor 18 can receive charging fluid and convert charging fluid to machine power, and this machine power drive fan 20 produces air-flow.Air-flow can be used for direct and/or passes through the indirect cooled engine 12 of heat exchanger (not shown).
Main pump 14 can be off-centre, variable displacement or the variable delivery pump that is driven by motor 12, is used for the convection cell supercharging.For example, main pump 14 can show as pump rotation or piston actuated, and this pump has the bent axle (not shown) that is connected to motor 12 by machinery output 16, thereby the output of motor 12 rotation causes main pump 14 corresponding pumping campaigns.The pumping campaign of main pump 14 can be used for sucking the low-pressure fluid of discharging from motor 18 by low-pressure channel 24, and by high-pressure channel 26 fluid is discharged into motor 18 with the pressure that improves.Low-pressure channel 24 and high-pressure channel 26 can form closed-loop path 22 jointly.Main pump 14 can be used for only providing charging fluid to motor 18 by 26 of high-pressure channels, or if desired, also charging fluid can be offered other oil hydraulic circuit relevant with machine 200 (as the oil hydraulic circuit relevant with tool system 220, drive system 230 etc.).Equally, main pump 14 can be used for only sucking low-pressure fluid from motor 18 by 24 of low-pressure channels, or if desired, also can suck low-pressure fluid from other oil hydraulic circuit of machine 200.It should be noted that in some cases main pump 14 and motor 18 can reversely turn round, and under these situations, the pressure reversible in low-pressure channel 24 and the high-pressure channel 26 is changeed.
Motor 18 can comprise fixed displacement, rotation or fluid pressure motor in the form of piston, owing to act on the pressure imbalance on the drive element (not shown), this motor is removable, and drive element for example is impeller or piston.Fluid by main pump 14 superchargings returns from motor 18 by high-pressure channel 26 importing motor 18 and by low-pressure channel 24.Charging fluid is directed to a side of drive element and discharges fluid from the opposite side of drive element and can produce pressure difference at the drive element (not shown), and this pressure official post drive element moves or rotates.Fluid flows through the direction of motor 18 and sense of rotation and the speed that speed can determine motor 18 and fan 20, and the pressure imbalance of motor 18 can determine moment of torsion output.
Fan 20 can and be configured to produce the air-flow that is guided through exchanger pipe near liquid-air or the setting of air-air heat exchanger (not shown), is used for carrying out heat transmission with wherein freezing mixture or combustion-supporting air.Fan 20 can comprise a plurality of blades of being connected to motor 18 and to be driven by motor 18 with required air velocity and/or the required corresponding speed of engineer coolant temperature.In one embodiment, flywheel 28 can be connected on one of fan 20 and motor 18, with rotation thereupon.Flywheel 28 can show as fixedly inertial flywheel, variable inertial flywheel or have the known in the art another kind of flywheel of one or more substance for Spins, and this substance for Spin can move along with the rotation of motor 18 and fan 20.The inertia of flywheel 28 is chosen as at main pump 14 and stops drive motor 18 backs for prolonging the time that fan 20 rotates freely.In most of the cases, when driven by pump, typical closed-loop path fan can about 3 seconds or less than 3 seconds after stop the rotation.But flywheel 28 can have enough big inertia, thereby makes fan 20 rotations at least 4 seconds after main pump 14 stops drive motor 18.In another embodiment, flywheel 28 can be incorporated in the fan 20 and (that is, can enlarge the size of fan 20 for the inertia that comprises flywheel 28, make its rotatable at least 4 seconds).
Low-pressure channel 24 can interconnect by a plurality of different cross aisles with high-pressure channel 26.In example embodiment, two different cross aisles are connected to each other low-pressure channel 24 and high-pressure channel 26, and these two different cross aisles comprise supply/release channel 30 and pressure limit passage 32.Supply/release channel 30 can provide the supply fluid to low-pressure channel 24 and/or high-pressure channel 26, be used for assisting in ensuring that hydraulic fan loop 10 keeps filling fluid, and in low-pressure channel 24 and/or high-pressure channel 26 for high-pressure liquid provides leakage path, thereby can avoid the assembly in hydraulic fan loop 10 is caused damage.Pressure limit passage 32 can be provided for the pilot pressure control relevant with the discharge capacity of main pump 14.
One or more replenish valves 34, for example safety check can be positioned at supply/release channel 30, is used for optionally the output of load pump 36 being connected to low-pressure channel 24 and/or high-pressure channel 26 based on the hydrodynamic pressure in the different passages.That is to say, when the pressure in low-pressure channel 24 and/or the high-pressure channel 26 drops to when being lower than the hydrodynamic pressure of being discharged by load pump 36, can open (a plurality of) replenish valve 34 and make fluid flow into corresponding (a plurality of) passage from load pump 36.Load pump 36 can be driven by motor 12, sucks fluids to rotate along with main pump 14 and to pass through liquid case passage 40 from low pressure liquid bath 38, and discharges the fluid in to supply/release channel 30 by valve passage 42.
One or more relief valves 44 also can be positioned at supply/release channel 30.Relief valve 44 can be spring biasing and can respond the pressure of low-pressure channel 24 and/or high-pressure channel 26 and move, be used for optionally corresponding passage being connected to low-pressure channel 46, thereby discharge the interior excess fluid pressure of low-pressure channel 24 and high-pressure channel 26.The pressure relief valve 48 of extra spring biasing can be positioned at low-pressure channel 46, and optionally mobile between percolation and choked flow (shown in Fig. 2) position according to 46 pressure in the low-pressure channel, thereby can keep required pressure in low-pressure channel 46.
Resolver 50 can be arranged in the pressure limit passage 32, and relevant with pilot pressure limiter 52.Resolver 50 can be configured to be connected to pilot pressure limiter 52 with have the fluid that flows out in the passage of elevated pressures from low-pressure channel 24 and high-pressure channel 26.In most of examples, resolver 50 can be connected to the pressure of high-pressure channel 26 pilot pressure limiter 52 (shown in Fig. 2).But, when main pump 14 and motor 18 when countercurrent direction turns round or under the situation of motor 18 over-runnings, the pressure in the low-pressure channel 24 surpass the pressure in the high-pressure channel 26 probably.Under these situations, removable resolver 50 is connected to pilot pressure limiter 52 with the pressure with low-pressure channel 24.When the hydrodynamic pressure by resolver 50 surpassed the threshold value restriction, pilot pressure limiter 52 can move to the percolation position from choke position.It should be noted that if desired the threshold value restriction of pilot pressure limiter 52 is variable, in order to response capability or the performance of regulating hydraulic fan loop 10.
Pilot pressure limiter 52 can be communicated with leader channel 54 fluids, and this leader channel 54 extends between the discharge capacity actuator 56 of load pump 36 and main pump 14.Particularly, pilot pressure limiter 52 can be connected to leader channel 54 by passage 58.When pilot force-limiting device 52 moved towards above-mentioned percolation position in the ban, the pilot fluid that flows out from leader channel 54 can enter low pressure liquid bath 38.Pilot fluid is discharged the hydrodynamic pressure that can reduce in the leader channel 54 from leader channel 54.
Pilot fluid in the passage 54 optionally is communicated with discharge capacity actuator 56, thereby influences the displacement variation of main pump 14.That discharge capacity actuator 56 can show as is double-acting, the cylinder body of spring biasing, and it connects into another discharge capacity controlling mechanism of motion swash plate, relief valve or main pump 14.When the pilot fluid with enough pressure imports an end of discharge capacity actuator 56, the pressure that discharge capacity actuator 56 can corresponding fluid and move the discharge capacity controlling mechanism of main pump 14 a certain amount of.Therefore pilot pressure limiter 52 can also can limit the discharge capacity of main pump 14 based on the pressure in the hydrodynamic pressure restriction leader channel 54 in low-pressure channel 24 and the high-pressure channel 26.
In some cases, need to stop the pressure limit of pilot pressure limiter 52 execution, for example when needing the limit displacement position of main pump 14.For the above reasons, pressure overload valve 59 can be arranged in the passage 58, between pilot pressure limiter 52 and leader channel 54.Pressure overload valve 59 can be spring control valve biasing, Electromagnetically actuated, and it can move based on the order of controller 62.Pressure overload valve 59 can move between percolation position (shown in Fig. 2) and choke position, wherein, leader channel 54 is communicated with pilot pressure limiter 52 fluids by passage 58 when the percolation position, and stops the fluid by passage 58 to be communicated with when choke position.Pressure overload valve 59 can be setovered towards the percolation position spring.
Position control valve 60 can be relevant with discharge capacity actuator 56, which termination that is used for control discharge capacity actuator 56 is received the supercharging pilot fluid, and therefore, control discharge capacity actuator 56 moves (that is the direction that discharge capacity increases and discharge capacity reduces) with the discharge capacity controlling mechanism of main pump 14 to which direction.Position control valve 60 can be spring control valve biasing, Electromagnetically actuated, and it can move based on the order of controller 62.Position control valve 60 can move between primary importance and the second place, and wherein, first termination of discharge capacity actuator 56 is received the supercharging pilot fluid when primary importance, and second termination of the opposition of discharge capacity actuator 56 is received the supercharging pilot fluid when the second place.When first termination of discharge capacity actuator 56 is received the supercharging pilot fluid (, when position control valve 60 in primary importance time), second end of discharge capacity actuator 56 can be connected to low pressure liquid bath 38 simultaneously by position control valve 60.Equally, when second termination of discharge capacity actuator 56 is received the supercharging pilot fluid (, when position control valve 60 in the second place time), first end of discharge capacity actuator 56 can be connected to low pressure liquid bath 38 simultaneously by position control valve 60.One or more throttle orifices 64 can be relevant with leader channel 54, the pressure surge that the pilot fluid that is used for reducing inflow and flow out the end of discharge capacity actuator 56 exists, thereby, stablize the fluctuation that exists in the speed of pump displacement variation.
Pressure controlled valve 66 also can be relevant with discharge capacity actuator 56 with leader channel 54, and be configured to the motion by the pressure control discharge capacity actuator 56 that changes leader channel 54.Pressure controlled valve 66 can move to the second place from primary importance (shown in Figure 2), wherein, fully loaded pressure transmits by position control valve 60 when primary importance, and the part of on-load pressure is discharged into low pressure liquid bath 38 before arrival direction control valve 60 and discharge capacity actuator 56 when the second place.Pressure controlled valve 66 can overcome the spring biasing based on the order of controller 62 and move towards the second place from primary importance.It should be noted that as required, can pass through directly pilot pressure control valve 66 of solenoid (shown in Fig. 2), or by the independent solenoid valve (not shown) guide pressure controlled valve 66 that turns round.By pressure controlled valve 66 optionally being moved to the arbitrary position between first and second positions, can control the pressure of the pilot fluid that is communicated to discharge capacity actuator 56, and then the discharge capacity of control main pump 14.
At least one accumulator can be relevant with closed-loop path 22.Two accumulators have been shown in the embodiment of Fig. 2, have comprised low pressure accumulator 68 and high-voltage energy storage device 70.Low pressure drain passage 72 and high-pressure discharge passage 74 can extend to exhaust-control valve 76 respectively from low pressure accumulator 68 and high-voltage energy storage device 70.If desired, pressure relief valve 78 can be relevant with low pressure drain passage 72, is used for fluid optionally is discharged into low pressure liquid bath 38 from low pressure accumulator 68, thereby keeps required pressure in low pressure accumulator 68.Exhaust-control valve 76 can be connected to low-pressure channel 24 and high-pressure channel 26 by passage 80 and 82 fluids respectively.
Exhaust-control valve 76 can be solenoid electric valve double-acting, the spring biasing, and it can be mobile between three different positions based on the order of controller 62.At primary importance (shown in Fig. 2), can stop fluid to flow through exhaust-control valve 76.In the second place, fluid can be from passing between low pressure accumulator 68 and the low-pressure channel 24 and between high-voltage energy storage device 70 and the high-pressure channel 26.In the 3rd position, fluid can be from passing between low pressure accumulator 68 and the high-pressure channel 26 and between high-voltage energy storage device 70 and the low-pressure channel 24.But exhaust-control valve 76 springs are biased to primary importance.
Low pressure accumulator 68 and high-voltage energy storage device 70 can be communicated with leader channel 54 fluids.Especially, filling channel 81 can with low pressure discharge route 72 and high pressure discharge route 74 respectively fluid be connected to leader channel 54.It is interior between leader channel 54 and each low pressure accumulator 68 and high-voltage energy storage device 70 that safety check 83 can be arranged on filling channel 81, thereby assist in ensuring that fluid is from load pump 36 unidirectional inflow low pressure accumulators 68 and high-voltage energy storage device 70.
But high-voltage energy storage device 70 also fluid is communicated to another oil hydraulic circuit 100, and this oil hydraulic circuit 100 forms for example part of another system of tool system 220, drive system 230 or machine 200.Particularly, additional feed path 10 2 can be connected to high-voltage energy storage device 70 with oil hydraulic circuit 100 fluids, thereby fills high-voltage energy storage device 70 with the discarded or excessive fluid with rising pressure.Safety check 104 and throttle orifice 106 can be arranged in the additional feed path 10 2, make the fluid with damped vibration from oil hydraulic circuit 100 unidirectional inflow high-voltage energy storage devices 70.Inductor 108, as pressure inductor, temperature inductor, viscosity inductor etc., can be relevant with additional feed path 10 2, be used for providing to controller 62 signal of the fluid parameter that shows additional feed path 10 2 and/or high-voltage energy storage device 70.Oil hydraulic circuit 100 can comprise that instrument activates loop, transmission loop, brake circuit, turns to loop or other machine loop known in the art.
In the accumulator discharge process, be conducive to motor 18 is isolated (that is, stoping fluid to flow directly into motor 18 by low-pressure channel 24 and high-pressure channel 26 substantially) fully from low-pressure channel 24 and high-pressure channel 26, hereinafter will describe in detail.For the above reasons, but fan separating valve 84 fluids are connected to low-pressure channel 24 and high-pressure channel 26, between motor 18 and low pressure accumulator 68 and high-voltage energy storage device 70.Fan separating valve 84 can be the solenoid electric valve of spring biasing, and it can be mobile between two diverse locations based on the order of controller 62.At primary importance (shown in Fig. 2), fluid can pass fan separating valve 84 by low-pressure channel 24 and high-pressure channel 26 and flow to motor 18.In the second place, can stop fluid to flow through fan separating valve 84.But fan separating valve 84 springs are biased to primary importance.
When motor 18 is isolated by fan separating valve 84 (when fan separating valve 84 during in the second place), fluid still can be by motor 18 circulations, and fan 20 still can keep rotating.In order to help the control fluid temperature (F.T.) in this process, hydraulic fan loop 10 can comprise motor flushing valve 86 and the pair of check valves 88 that is communicated with motor replenish valve 90 fluids.Motor flushing valve 86 can be communicated with the isolated part fluid of low-pressure channel 24 and high-pressure channel 26, and is configured to based on the hydrodynamic pressure in these passages mobile between three positions.At primary importance (shown in Fig. 2), stop fluid to flow to low pressure liquid bath 38 from low-pressure channel 24 and high-pressure channel 26.When having pressure difference between low-pressure channel 24 and the high-pressure channel 26, motor flushing valve 86 is movable to the second or the 3rd position, with the high temperature fluid that removes the sub-fraction volume it is substituted by the oil of low temperature.Safety check 88 can be positioned at branched bottom 92, between motor replenish valve 90 and low-pressure channel 24 and high-pressure channel 26.Unbalanced based on the pressure between branched bottom 92 and low-pressure channel 24 or the high-pressure channel 26 can be opened safety check 88 extra fluid is entered in the isolated part in hydraulic fan loop 10.
Motor replenish valve 90 can be arranged between pressure limit passage 32 and the branched bottom 92, and moves based on the hydrodynamic pressure in the pressure limit passage 32, thereby optionally makes fluid enter branched bottom 92.Particularly, the fluids that are connected in the low pressure feed channel 94 of pressure limit passage 32 of low voltage side of resolver 50 can produce thrust at an end of motor replenish valve 90, and the fluids that are connected in the high pressure feed channel 96 of on high-tension side pressure limit passage 32 of resolver 50 can produce thrust in the opposite end of motor replenish valve 90.At set time point, the passage that has elevated pressures in low pressure feed channel 94 and the high pressure feed channel 96 can be shifted motor replenish valve 90 onto a position, and fluid flows into the branched bottom 92 from low-pressure channel on this position.Motor replenish valve 90 can be to the biasing of position spring, and fluid passes from low pressure feed channel 94 and high pressure feed channel 96 and flows to branched bottom 92 on this position.
Controller 62 can comprise one or more microprocessors, field programmable gate array (FPGA), DSP digital signal processor (DSP) etc., they have a kind of device, the running in this device respond to device 108, one or more engine induction device 110, pump displacement inductor 112 and electromotor velocity inductor 113 control hydraulic fan loops 10.A plurality of commercial microprocessor can be configured to implement the function of controller 62.Should understand that controller 62 can comprise microprocessor, its microprocessor with relevant other machine function of control separates, or controller 62 is can be with the machine microprocessor integrated and can control a plurality of machine functions and operation mode.If separate from total machine microprocessor, controller 62 can be by data link or alternate manner and total machine microprocessor communication.Other known different circuit can be relevant with controller 62, comprises that power loop, Signal Regulation loop, actuator drive telegram in reply road (that is, loop power supply solenoid, motor or piezoelectric actuator) and communication loop.
Controller 62 can be communicated with valve 59,60,66,76 and 84, thereby controls the running in hydraulic fan loop 10 based on inductor 108,110,112 at least with 113 input in the process of two different operation modes.Operation mode can comprise normal mode and energy take-back model, and wherein, main pump 14 drive motors 18 are used for cooled engine 12 under normal mode, and motor 18 drives main pump 14 recovered energies under the energy take-back model, makes its return engine 12.These operation modes will be described in more detail below, and be used for the concept that further explaination discloses.
Fig. 3 shows another embodiment in hydraulic fan loop 10.In this embodiment, variable displacement motor 114 can replace said fixing discharge capacity motor 18, and this variable displacement motor has the resolver 120 that the displacement control valve 118 of discharge capacity actuator 116,116 motions of control discharge capacity actuator of the discharge capacity of control motor 114 and control low-pressure channel 24 and high-pressure channel 26 are communicated with fluid between the displacement control valve 118.Resolver 120 is movably, makes to have the fluid that flows out in the passage of elevated pressures at the given time point from low-pressure channel 24 and high-pressure channel 26 and be communicated with displacement control valve 118.Displacement control valve 118 can be mobile between primary importance and the second place based on the order of controller 62, wherein, all direction of flow discharge capacity actuators 116 that when primary importance, flow out from resolver 120, and block a part or all fluids that flows out from resolver 120 before when the second place, arriving discharge capacity actuator 116.But displacement control valve 118 is at the hydrodynamic pressure of motion influence on discharge capacity actuator 116 between first and second positions, thereby influences the motion of discharge capacity actuator 116.Discharge capacity actuator 116 can be cylindrical body single, the spring biasing, and it is configured to when the discharge capacity that is exposed to fluid adjusting of the following time motor 114 with specified pressure.Because have and can regulate discharge capacity, motor 114 can have the unexistent additional functionality of fixed displacement motor in the accumulator discharge process, hereinafter will describe in detail.It should be noted that if desired motor 114 can be eccentrically weighted motor.
Industrial applicibility
The hydraulic fan loop of disclosing can be used for the heat engine arbitrarily of needs cooling and energy recovery.The hydraulic fan loop of disclosing can be by optionally using accumulator storage and discharging from any machine loop recovered energy.The running in hydraulic fan loop 10 hereinafter will be described.
Under the normal operation pattern, motor 12 can drive main pump 14 rotation and to fluid pressurized.Charging fluid can be discharged into high-pressure channel 26 and import motor 18 from main pump 14.Along with charging fluid passes motor 18, the hydraulic power in the fluid can be converted into machine power and be used for rotary fan 20 and flywheel 28.When fan 20 rotations, can produce the air-flow that is conducive to cooled engine 12.After step-down, the fluid that flows out motor 18 can be led back main pump 14 to repeat this circulation by low-pressure channel 24.
Can under the normal operation pattern, adjust fluid emission direction and the discharge capacity of pump 14 based on inductor 108,110,112 and/or 113 signal, for example based on engine speed signal, engine temperature signal, electromotor velocity signal, pump displacement signal, accumulator pressure signal and/or similar signal in addition.Controller 62 can receive these signals and with reference to corresponding engine speed, engine temperature, pump displacement angle, electromotor velocity, accumulator pressure or be stored in one or more in the storage and search other similar parameters in the map, determines the emission direction of expection of main pump 14 and corresponding sense of rotation and the speed of discharge capacity setting and fan 20.Controller 60 can send appropriate command, and this order is sent to position control valve 60 and pressure controlled valve 66, with the corresponding adjusting of influence to the discharge capacity of main pump 14.
Under the normal operation pattern, available at least three kinds of different modes load low pressure accumulator 68 and/or high-voltage energy storage device 70.For example, when driving main pump 14 convection cell superchargings, any excess fluid that motor 18 does not consume can be filled high-voltage energy storage device 70 by exhaust-control valve 76, and at this moment, exhaust-control valve 76 is on the second place.Equally, the fluid that flows out motor 18 can be filled low pressure accumulator 68.Have only when exhaust-control valve 76 during in the second place and the pressure in low-pressure channel 24 or the high-pressure channel 26 when exceeding pressure in low pressure accumulator 68 or the high-voltage energy storage device 70 respectively, just can fill low pressure accumulator 68 and high-voltage energy storage device 70.Otherwise when exhaust-control valve 76 moved to the second place, low pressure accumulator 68 or high-voltage energy storage device 70 can discharge the fluid in to low-pressure channel 24 or high-pressure channel 26.Can at least part of signal that provides based on pressure inductor 108, regulate the motion of exhaust-control valve 76 accurately, load and discharging low pressure accumulator 68 and high-voltage energy storage device 70 thereby can be in due course.It should be noted that one that once fills only in low pressure accumulator 68 and the high-voltage energy storage device 70, and another of low pressure accumulator 68 and high-voltage energy storage device 70 will be discharged, vice versa.
Alternatively or extraly, can continue to load low pressure accumulator 68 or high-voltage energy storage devices 70 by load pump 36.Particularly, any time in the normal operation process, when the hydrodynamic pressure that flows out load pump 36 exceeds pressure in low pressure accumulator 68 or the high-voltage energy storage device 70, fluid can flow through filling channel 81 from load pump 36, and enters corresponding low pressure accumulator 68 or high-voltage energy storage device 70 through safety check 83.Pressure relief valve 78 can assist in ensuring that low pressure accumulator 68 can superpressure in the process that load pump 36 loads.It should be noted that also the same time can only fill or discharge in low pressure accumulator 68 and the high-voltage energy storage device 70.
High-voltage energy storage device 70 also can load by oil hydraulic circuit 100.That is to say, random time point in the normal operation process, when the hydrodynamic pressure that flows out when oil hydraulic circuit 100 was higher than pressure high-voltage energy storage device 70 in, fluid can be from the loop 100 flows through additional feed path 10 2, and passed through safety check 104 and enter high-voltage energy storage device 70.
When the signal indicating of engine induction device 110 enough cooling (that is, when the needs of cooling blast have reduced) and fan 20 can slow down or even when stopping, controller 62 can be carried out the energy take-back model of running.In the energy take-back model process of running, controller 62 can order fan separating valve 84 to isolate motor 18 from main pump 14, move in the second and the 3rd position according to the expected flow direction order exhaust-control valve 76 of main pump 14 then one.Probably at one time, controller 62 can order overload valve 59 to move to choke position, and order pressure controlled valve 66 begins to reduce the stroke of main pump 14.When sending suitable valve order, can be discharged into low-pressure channel 24 or high-pressure channel 26 respectively by passage 72,74, exhaust-control valve 76 and passage 80,82 from low pressure accumulator 68 or the high-voltage energy storage device 70 interior fluids that flow out, thereby drive main pump 14 as motor.By driving main pump 14, the hydraulic power of building up fluid can be converted into machine power, and this machine power imports motor 12 by machinery output 16.The fuel consumption that this power-assisted is conducive to increase the power supply ability in the energy take-back model process of running and/or reduces motor 12.
In the discharge process of low pressure accumulator 68 or high-voltage energy storage device 70, when motor 18 was isolated from main pump 14, fan 20 can continue rotation.As indicated above, as be equipped with flywheel 28 or increase the quality that volume is used for incorporating into flywheel 28, fan 20 can be under the condition of drive motor 18 not the longer time of rotation.In example, the time of prolongation can be at least 4 seconds.In this way, cooled engine significantly in the discharge process of low pressure accumulator 68 or high-voltage energy storage device 70, and also the change in fluid pressure in the accumulator does not influence the speed of motor 18 substantially.In addition, can waste the energy of building up fluid for non-essential ground drive motor 18.
It should be noted that if desired, can select under the condition of isolating motor fully, not discharge accumulator.Particularly, controlling fan separating valve 84 moves to the arbitrary position between the first and second above-mentioned positions, thereby the charging fluid of the anticipated volume that flows out from high-voltage energy storage device 70 flows through and drive motor 114 (with reference to the embodiment of figure 2), and remaining is built up fluid and flows through and drive main pump 14.But, for required motor/fan speed is provided in the accumulator discharge process, when the pressure in the high-voltage energy storage device 70 changes (minimizings), can be based on the discharge capacity of the electromotor velocity signal-selectivity ground adjusting motor 114 of the fluid pressure signal of inductor 108 and/or inductor 113.
A plurality of ranks that the hydraulic fan loop of disclosing can have cheaper cost and can provide energy to reclaim.Especially, because the hydraulic fan loop mainly utilizes existing assembly to reclaim discarded energy, so that the cost of this system can keep is cheap.In addition, because low pressure accumulator 68 and high-voltage energy storage device 70 can be filled fluid and discharged by different modes by different sources, so can increase the yield of energy.
Can do different modifications and modification to the hydraulic fan loop of disclosing, this it will be apparent to those skilled in the art that.For example, though the pump that discloses and motor are described as device variable and fixed displacement or variable and variable displacement respectively, if desired, can predict the pump and the motor that disclose can all be the device of fixed displacement formula.Consider specification and the application in the hydraulic fan loop of disclosing, other embodiment also is apparent to those skilled in the art.Description in the literary composition and example only are used for illustrating, and claim and equivalence explanation thereof limit real scope.

Claims (10)

1. a hydraulic fan loop (10) comprising:
Main pump (14);
Fluid is connected to the high-pressure channel (26) of described main pump;
Fluid is connected to the low-pressure channel (24) of described main pump;
At least one accumulator (68,70), its with described high-pressure channel and low-pressure channel at least one optionally fluid be communicated with;
Motor (18);
Be connected to the fan (20) of described motor; And
Fluid is connected to the fan separating valve (84) of described high-pressure channel and low-pressure channel, described fan separating valve can move between percolation position and choke position, described motor is connected to described main pump by described high-pressure channel and low-pressure channel fluid when described percolation position, and described motor is isolated from described main pump substantially when described choke position.
2. hydraulic fan according to claim 1 loop, wherein, described at least one accumulator comprises:
The high-voltage energy storage device (70) relevant with described high-pressure channel; And
The low pressure accumulator (68) relevant with described low-pressure channel.
3. hydraulic fan according to claim 2 loop also comprises the escape cock (76) that is communicated with described high-voltage energy storage device and low pressure accumulator fluid, this escape cock can:
Optionally fluid is transferred to described high-voltage energy storage device and is transferred to described main pump from described high-voltage energy storage device from described main pump; And
Optionally fluid is transferred to described low pressure accumulator and is transferred to described main pump from described low pressure accumulator from described motor.
4. hydraulic fan according to claim 1 loop, also comprise escape cock (76), it is communicated with described at least one accumulator fluid and can optionally fluid is transferred to described at least one accumulator and is transferred to described main pump from described at least one accumulator from described main pump.
5. hydraulic fan according to claim 4 loop, wherein, described at least one accumulator can also receive the fluid from another oil hydraulic circuit (100).
6. hydraulic fan according to claim 1 loop, wherein:
Described main pump is variable delivery pump;
Described motor is the fixed displacement motor;
Described fan separating valve is the two-position valve and moves to described choke position in the discharge process of described at least one accumulator.
7. hydraulic fan according to claim 1 loop, wherein:
Described main pump is variable delivery pump;
Described motor is the variable displacement motor; And
Described fan separating valve can move to the arbitrary position between described percolation position and the described choke position, thereby regulates the amount that can be transferred to the fluid of described motor from described at least one accumulator.
8. hydraulic fan according to claim 7 loop also comprises:
The motor resolver (50) that is communicated with described high-pressure channel and low-pressure channel fluid; And
The motor displacement control valve (118) that is communicated with described motor resolver and described motor fluid,
Wherein, when described fan separating valve during in described choke position, described motor resolver and described motor displacement control valve are isolated substantially from described at least one accumulator and described main pump.
9. hydraulic fan according to claim 1 loop, wherein:
When described fan separating valve during in described choke position, described motor rotates freely; And
Described hydraulic fan loop also comprises the flywheel (28) that is connected to described fan, thereby prolongs the endurance that described fan rotates freely.
10. method that is used for from hydraulic fan loop (10) recovered energy comprises:
With pump (14) convection cell supercharging;
Guide described charging fluid to be used for drive fan motor (18);
Build up excessive charging fluid;
Optionally the fluid of discharging accumulation is used for driving described pump; And
In described discharge process, isolate described fan motor substantially from described pump.
CN2011800660769A 2010-11-30 2011-11-22 Hydraulic fan circuit having energy recovery Pending CN103339388A (en)

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104963903A (en) * 2015-04-12 2015-10-07 吉林大学 Hydraulic flywheel accumulator system based on largest energy accumulation rate, and control method thereof

Families Citing this family (25)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8997906B2 (en) * 2011-04-01 2015-04-07 Agco Corporation Air mover reversing for work vehicle cooling package
JP5956179B2 (en) * 2012-02-23 2016-07-27 株式会社小松製作所 Hydraulic drive system
US9574660B2 (en) 2014-02-21 2017-02-21 Federal Signal Corporation Hydraulic fan drive system
CN103867418B (en) * 2014-03-31 2016-04-27 苏州汉纳机械有限公司 A kind of diesel-driven air compressor system
US9671009B2 (en) * 2014-10-22 2017-06-06 Deere & Company Pressure and flow compensated hydraulic system
US9763388B2 (en) 2015-09-15 2017-09-19 Cnh Industrial America Llc Agricultural harvester having a header based heat exchanger
US9945396B2 (en) 2016-02-23 2018-04-17 Caterpillar Inc. Fluid systems for machines with integrated energy recovery circuit
US10273962B2 (en) 2016-09-26 2019-04-30 Caterpillar Inc. System for selectively bypassing fluid supply to one or more operational systems of a machine
DE112016000707B4 (en) * 2016-11-09 2022-10-27 Komatsu Ltd. Work vehicle and method of calibrating data
KR101985349B1 (en) * 2016-11-09 2019-06-03 가부시키가이샤 고마쓰 세이사쿠쇼 Work vehicle and control method
US10330126B2 (en) * 2016-12-16 2019-06-25 Caterpillar Inc. Fan control system with electro-hydraulic valve providing three fan motor operational positions
US11098691B2 (en) 2017-02-03 2021-08-24 General Electric Company Methods for manufacturing wind turbine rotor blades and components thereof
US10830206B2 (en) 2017-02-03 2020-11-10 General Electric Company Methods for manufacturing wind turbine rotor blades and components thereof
CN108691828B (en) 2017-04-07 2020-10-30 丹佛斯动力系统公司 Hydraulic system or closed-circuit hydraulic system for maintaining minimum low-side pressure
US10920745B2 (en) 2017-11-21 2021-02-16 General Electric Company Wind turbine rotor blade components and methods of manufacturing the same
US10913216B2 (en) 2017-11-21 2021-02-09 General Electric Company Methods for manufacturing wind turbine rotor blade panels having printed grid structures
US10865769B2 (en) 2017-11-21 2020-12-15 General Electric Company Methods for manufacturing wind turbine rotor blade panels having printed grid structures
US11248582B2 (en) 2017-11-21 2022-02-15 General Electric Company Multiple material combinations for printed reinforcement structures of rotor blades
US10821652B2 (en) 2017-11-21 2020-11-03 General Electric Company Vacuum forming mold assembly and method for creating a vacuum forming mold assembly
US11040503B2 (en) 2017-11-21 2021-06-22 General Electric Company Apparatus for manufacturing composite airfoils
US10773464B2 (en) 2017-11-21 2020-09-15 General Electric Company Method for manufacturing composite airfoils
US11390013B2 (en) 2017-11-21 2022-07-19 General Electric Company Vacuum forming mold assembly and associated methods
US11668275B2 (en) 2017-11-21 2023-06-06 General Electric Company Methods for manufacturing an outer skin of a rotor blade
US11035339B2 (en) 2018-03-26 2021-06-15 General Electric Company Shear web assembly interconnected with additive manufactured components
US10821696B2 (en) 2018-03-26 2020-11-03 General Electric Company Methods for manufacturing flatback airfoils for wind turbine rotor blades

Family Cites Families (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3662551A (en) * 1970-08-19 1972-05-16 Nutron Corp Fluid pressure controlling
US6659723B2 (en) * 2001-11-16 2003-12-09 Illinois Tool Works Inc. Fan for an engine driven generator
FR2836670B1 (en) * 2002-03-04 2004-10-08 Messier Bugatti ARCHITECTURE OF ORIENTATION CONTROL HYDRAULIC SYSTEM
US6681568B2 (en) * 2002-03-28 2004-01-27 Caterpillar Inc Fluid system for two hydraulic circuits having a common source of pressurized fluid
US6789387B2 (en) * 2002-10-01 2004-09-14 Caterpillar Inc System for recovering energy in hydraulic circuit
JP3979917B2 (en) * 2002-10-18 2007-09-19 サクサ株式会社 Hydraulic device
US6848255B2 (en) * 2002-12-18 2005-02-01 Caterpillar Inc Hydraulic fan drive system
DE102004044510A1 (en) * 2004-09-15 2006-03-30 Zf Friedrichshafen Ag Hydraulic transmission
US7240486B2 (en) * 2005-04-18 2007-07-10 Caterpillar Inc Electro-hydraulic system for fan driving and brake charging
DE102005061990A1 (en) * 2005-12-23 2007-07-05 Bosch Rexroth Aktiengesellschaft Drive with energy recovery and retarder function for construction vehicle has cooler downstream of pressure limiting valve and hydraulic motor to drive cooler fan
US7444809B2 (en) 2006-01-30 2008-11-04 Caterpillar Inc. Hydraulic regeneration system
US20080010775A1 (en) * 2006-07-17 2008-01-17 Sweepster Attachments, Llc Rotary broom with vacuum dust control
DE102006050873A1 (en) * 2006-10-27 2008-04-30 Robert Bosch Gmbh Hydrostatic drive i.e. traction drive, for e.g. wheel loader, has hydraulic pump and hydraulic motor arranged in open circuit, where downstream connection of hydraulic motor is connected with tank volume or storage unit by valve device
US7937938B2 (en) * 2008-04-23 2011-05-10 Caterpillar Inc. Hydraulic reversing fan valve and machine using same
CN102292528B (en) * 2009-01-22 2016-01-20 罗伯特·博世有限公司 Hydrostatic fan drives

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104963903A (en) * 2015-04-12 2015-10-07 吉林大学 Hydraulic flywheel accumulator system based on largest energy accumulation rate, and control method thereof

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Application publication date: 20131002