CN113137411A - Power distribution system and engineering machinery - Google Patents

Power distribution system and engineering machinery Download PDF

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Publication number
CN113137411A
CN113137411A CN202110441224.6A CN202110441224A CN113137411A CN 113137411 A CN113137411 A CN 113137411A CN 202110441224 A CN202110441224 A CN 202110441224A CN 113137411 A CN113137411 A CN 113137411A
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China
Prior art keywords
hydraulic
controller
driving system
isg motor
hydraulic system
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Granted
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CN202110441224.6A
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Chinese (zh)
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CN113137411B (en
Inventor
韩嫔
王小虎
魏加洁
郁干
路振坡
程然
孟令超
王桂珍
陈辉
李伯宇
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Science and Technology Branch of XCMG
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Science and Technology Branch of XCMG
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Priority to CN202110441224.6A priority Critical patent/CN113137411B/en
Publication of CN113137411A publication Critical patent/CN113137411A/en
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    • 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
    • F15B21/08—Servomotor systems incorporating electrically operated 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
    • F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
    • F15B1/02—Installations or systems with 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
    • 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
    • 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
    • F15B13/06—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with two or more servomotors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/0021—Generation or control of line pressure
    • F16H61/0025—Supply of control fluid; Pumps therefore
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02J—CIRCUIT ARRANGEMENTS OR SYSTEMS FOR SUPPLYING OR DISTRIBUTING ELECTRIC POWER; SYSTEMS FOR STORING ELECTRIC ENERGY
    • H02J7/00—Circuit arrangements for charging or depolarising batteries or for supplying loads from batteries
    • H02J7/14—Circuit arrangements for charging or depolarising batteries or for supplying loads from batteries for charging batteries from dynamo-electric generators driven at varying speed, e.g. on vehicle
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/10—Structural association with clutches, brakes, gears, pulleys or mechanical starters
    • 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
    • F15B2211/20515—Electric 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
    • F15B2211/20507—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
    • F15B2211/60—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
    • F15B2211/6656—Closed loop control, i.e. control using feedback
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/0021—Generation or control of line pressure
    • F16H2061/0034—Accumulators for fluid pressure supply; Control thereof

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

Abstract

The invention discloses a power distribution system and engineering machinery, which comprise a controller, an ISG motor, an engine, a storage battery, a driving system and a hydraulic system, wherein the ISG motor is connected with the engine; the controller acquires the running states of the driving system and the hydraulic system and judges whether the driving system and the hydraulic system run coordinately: if yes, the controller controls the ISG motor to store energy and charge the storage battery; if the driving system and the hydraulic system are not coordinated in operation, the controller controls the ISG motor to output extra power increment to the hydraulic system; if the driving system and the hydraulic system still run uncoordinated after the power increment is output, the controller reduces the power output of the driving system by controlling the driving system, so that the power output of the engine to the hydraulic system is increased until the two systems can run coordinately. The invention carries out power compensation on the hydraulic system through the ISG motor and can change the power distribution of the engine according to the operating states of the driving system and the hydraulic system.

Description

Power distribution system and engineering machinery
Technical Field
The invention relates to a power distribution system and engineering machinery, and belongs to the technical field of engineering machinery.
Background
In the prior art, the power distribution problem of a hydraulic system and a driving system exists. The common situation is that when a loader works in a full load, a driver often rolls an accelerator with large feet and lifts a movable arm in order to improve the working efficiency, namely the movable arm is lifted while walking.
When lifting alone in order to satisfy the operation demand, every duty cycle all need wait for several seconds, leads to work efficiency relatively poor, because when lifting fully loaded, there is the problem of work of can not coordinating between hydraulic system and the actuating system for hydraulic system and actuating system's operation rhythm is not matchd, and actuating system's walking speed can be faster than hydraulic system's lifting speed, consequently, has hydraulic system and actuating system power consumption's power distribution problem, causes the energy waste.
Disclosure of Invention
The invention aims to overcome the defects in the prior art, provides a power distribution system and an engineering machine, and solves the problem of unmatched power distribution of power consumption of a hydraulic system and a driving system.
In order to achieve the purpose, the invention is realized by adopting the following technical scheme:
in one aspect, the present invention provides a power distribution system comprising a controller, an ISG motor, an engine, a battery, a drive system, and a hydraulic system; the controller acquires the running states of the driving system and the hydraulic system and judges whether the driving system and the hydraulic system run coordinately: if yes, the controller controls the ISG motor to store energy and charge the storage battery; if the driving system and the hydraulic system are not coordinated in operation, the controller controls the ISG motor to output extra power increment to the hydraulic system; if the driving system and the hydraulic system still run uncoordinated after the power increment is output, the controller reduces the power output of the driving system by controlling the driving system, so that the power output of the engine to the hydraulic system is increased until the two systems can run coordinately.
As a preferred embodiment, the driving system comprises an electric proportional overflow valve connected with a controller, and a hydraulic control valve, a clutch and a transmission device which are sequentially connected with the electric proportional overflow valve, and the controller controls the electric proportional overflow valve to reduce the power output of the driving system.
As a preferred embodiment, the hydraulic system comprises a hydraulic pump, a sensor, a lifting cylinder and a multi-way valve, wherein the sensor is respectively connected with the controller and the lifting cylinder, and the hydraulic pump is sequentially connected with the multi-way valve and the lifting cylinder.
As a preferred embodiment, the controller controls the operation states of the ISG motor, the driving system and the hydraulic system by acquiring the lifting speed of the lifting cylinder transmitted by the sensor;
when the lifting speed of the lifting cylinder is smaller than a set value, the controller controls the ISG motor to output extra power increment to the hydraulic system;
or the controller controls the ISG motor to output extra power increment to the hydraulic system, and simultaneously controls the driving system to reduce the power output of the driving system, so that the power output of the engine to the hydraulic system is increased, and the coordinated operation of the lifting cylinder and the driving system is realized.
In a preferred embodiment, the working port K of the electric proportional overflow valve is connected to the control port H of the electric proportional overflow valve, and the working port D of the hydraulic control valve is connected to the control port E of the hydraulic control valve.
As a preferred embodiment, the driving system is further provided with an energy accumulator, and the energy accumulator is connected with a working oil port K oil way of the electric proportional overflow valve.
As a preferred embodiment, the system further comprises a gearbox, and the gearbox is respectively connected with the ISG motor and the hydraulic pump.
As a preferred embodiment, the electric proportional overflow valve further comprises an oil tank, and an oil discharge port G of the electric proportional overflow valve, an oil discharge port B of the hydraulic control valve, an oil return port of the multi-way valve, and an oil inlet of the hydraulic pump are connected with the oil tank.
In a preferred embodiment, the gearbox, the engine and the ISG motor are arranged on the same axial line.
In another aspect, the present disclosure also provides a working machine including the power distribution system.
Compared with the prior art, the invention has the following beneficial effects:
1. the power distribution system provided by the invention can coordinate the work of the driving system and the hydraulic system through the combined action of the controller, the engine, the gearbox, the storage battery and the ISG motor, when the driving system and the hydraulic system can coordinate the operation, the ISG motor charges the storage battery, and the controller outputs rated current to the driving system; when the two systems cannot work in a coordinated mode, the controller outputs extra current to the ISG motor through the storage battery, so that the ISG motor can output extra power increment to the hydraulic system; if the two systems can not work in a coordinated mode, the controller sends signals to the driving system to reduce power output to the driving system, increase power output to the hydraulic system and change power distribution of the engine, namely the power distribution is more reasonable, and therefore a better energy-saving effect is achieved.
2. Compared with the common system, the power distribution system provided by the invention has the advantages that the number of elements is small, the principle is simple, and once a fault occurs, a maintainer can quickly check the fault, so that the maintenance cost can be reduced; the driving system and the hydraulic system work in a coordinated mode, when the controller receives signals, the controller immediately outputs control signals to the ISG motor, and meanwhile outputs corresponding current to the electric proportional overflow valve, so that the valve core of the electric proportional overflow valve acts rapidly, the engaging pressure of the clutch is controlled, the total power is redistributed, and the sensitivity of the power distribution system can be improved.
3. The power distribution system provided by the invention can adaptively adjust the power of the hydraulic system and the driving system, correspondingly reduce the working time of each working cycle, reduce the waiting time of a driver and further improve the working efficiency of the whole operation.
4. The engineering machinery provided by the invention can compensate the power of the hydraulic system, so that the loader can coordinate the operation mode of lifting while walking, the waiting time of a driver can be reduced, and the work efficiency can be improved by about 6% on average according to the operation habit of a skilled driver.
Drawings
FIG. 1 is a schematic diagram of a power distribution system according to an embodiment of the present invention;
in the figure: 1. a transmission device; 2. a clutch; 3. a hydraulic control valve; 4. an oil tank; 5. an electric proportional relief valve; 6. an accumulator; 7. a lifting cylinder; 71. a large cavity; 72. a small cavity; 8. a multi-way valve; 9. a hydraulic pump; 10. a gearbox; 11. an ISG motor; 12. a controller; 13. an engine; 14. a storage battery; 15. a sensor.
Detailed Description
The invention is further described below with reference to the accompanying drawings. The following examples are only for illustrating the technical solutions of the present invention more clearly, and the protection scope of the present invention is not limited thereby.
In the description of the present invention, it is to be understood that the terms "center", "longitudinal", "lateral", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", and the like, indicate orientations or positional relationships based on those shown in the drawings, and are used only for convenience in describing the present invention and for simplicity in description, and do not indicate or imply that the referenced devices or elements must have a particular orientation, be constructed and operated in a particular orientation, and thus, are not to be construed as limiting the present invention. Furthermore, the terms "first", "second", etc. are used for descriptive purposes only and are not to be construed as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defined as "first," "second," etc. may explicitly or implicitly include one or more of that feature. In the description of the present invention, "a plurality" means two or more unless otherwise specified.
In the description of the present invention, it should be noted that, unless otherwise explicitly specified or limited, the terms "mounted," "connected," and "connected" are to be construed broadly, e.g., as meaning either a fixed connection, a removable connection, or an integral connection; can be mechanically or electrically connected; they may be connected directly or indirectly through intervening media, or they may be interconnected between two elements. The specific meaning of the above terms in the present invention can be understood by those of ordinary skill in the art through specific situations.
The first embodiment is as follows:
the present embodiment provides a power distribution system, referring to fig. 1, including a controller 12, an engine 13, a transmission 10, a battery 14, an ISG (starter/generator integrated) motor 11, a drive system, and a hydraulic system. The output end of the controller 12 is respectively electrically connected with the driving system, the ISG motor 11 and the storage battery 14, the input end of the controller 12 is respectively electrically connected with the ISG motor 11, the storage battery 14 and the generator, the gearbox 10 is mechanically connected with the hydraulic system, and the ISG motor 11 is respectively connected with the engine 13 and the gearbox 10. Preferably, the engine 13, the ISG motor 11 and the transmission case 10 are mechanically connected through a coupling, and as a preferred embodiment, the transmission case 10, the engine 13 and the ISG motor 11 are disposed on the same axial line.
In this embodiment, the driving system includes an electric proportional overflow valve 5, a hydraulic control valve 3, a clutch 2, an energy accumulator 6, an oil tank 4, and a transmission device 1, the controller 12 is electrically connected to the electric proportional overflow valve 5, a working oil port K of the electric proportional overflow valve 5 is connected to an oil path of a working oil port C of the hydraulic control valve 3, a working oil port D of the hydraulic control valve 3 is connected to an oil path of an oil port input end of the clutch 2, the clutch 2 is mechanically connected to the transmission device 1, and specifically, the clutch 2 and the transmission device 1 may be flange-connected or may be connected by a transmission shaft.
The hydraulic system comprises a hydraulic pump 9, a sensor 15, a lifting cylinder 7 and a multi-way valve 8, wherein an oil inlet of the hydraulic pump 9 is connected with an oil tank 4, the hydraulic pump 9 is mechanically connected with a gearbox 10 through a spline, the sensor 15 is electrically connected with a controller 12, the lifting cylinder 7 is electrically connected with the sensor 15, correspondingly, the hydraulic pump 9, the multi-way valve 8 and the lifting cylinder 7 are in oil circuit connection, and the sensor 15 can be a speed sensor, a displacement sensor or a speed displacement sensor.
The lifting cylinder 7 is provided with two, the lifting cylinder 7 comprises a large cavity 71 and a small cavity 72, the multi-way valve 8 is respectively connected with the large cavity 71 and the small cavity 72 of the two lifting cylinders 7 to realize lifting and descending of the lifting cylinder 7, and an oil return port of the multi-way valve 8 is connected with the oil tank 4 to ensure oil circuit oil return of the lifting cylinder 7.
The hydraulic system oil circuit connection state is as follows: an oil source flows to the multi-way valve 8 through an oil inlet of the hydraulic pump 9, the multi-way valve 8 is respectively connected with a large cavity 71 and a small cavity 72 of the two lifting cylinders 7, and when the lifting action is carried out, oil returns to the oil tank 4 from the small cavity 72 through the multi-way valve 8.
In this embodiment, the working port K of the electric proportional overflow valve 5 is connected to the control port H of the electric proportional overflow valve 5, the working port D of the hydraulic control valve 3 is connected to the control port E of the hydraulic control valve 3, the driving system is further provided with the energy accumulator 6, the energy accumulator 6 is connected to the working port K oil path of the electric proportional overflow valve 5 and the working port C of the hydraulic control valve 3, and the energy accumulator 6 can buffer pressure changes of the working port K and the working port C to enable the pressure change of the working port C to be in a relatively stable state, so that the clutch 2 can be relatively stable when pressure is engaged, and pressure impact is reduced.
The output end of the controller 12 is connected with the driving system, specifically, the output end of the controller 12 is connected with the electric proportional overflow valve 5, the working oil port D of the hydraulic control valve 3 is connected with the oil port input end of the clutch 2, the oil discharge port G of the electric proportional overflow valve 5 is connected with the oil tank 4, and the oil discharge port B of the hydraulic control valve 3 is connected with the oil tank 4.
The oil way connection state of the power distribution system is as follows: the oil source P enters a working oil port D of the hydraulic control valve 3 through a working oil port A of the hydraulic control valve 3, the working oil port D of the hydraulic control valve 3 is communicated with a control oil port E of the hydraulic control valve 3, the working oil port D of the hydraulic control valve 3 is connected with an oil port input end of the clutch 2, and an oil discharge port B of the hydraulic control valve 3 is connected with an oil tank 4; the other path of the oil source is respectively connected with an oil port input end of the energy accumulator 6 and a working oil port C of the hydraulic control valve 3 through a working oil port F, and is simultaneously connected with a working oil port K and a control oil port H of the electric proportional overflow valve 5.
When the driving system and the hydraulic system can operate in a coordinated manner, the ISG motor 11 charges the storage battery 14 through the controller 12, the controller 12 outputs rated current to the electric proportional relief valve 5, and the engine 13 can drive the ISG motor 11, the gearbox 10 and the hydraulic pump 9 to operate. At this time, the working port K and the control port H of the electric proportional overflow valve 5 are disconnected, the oil source P flows to the working port a of the hydraulic control valve 3, then flows to the working port D of the hydraulic control valve 3 through the working port a, and then flows to the port input end of the clutch 2 through the working port D.
When the lifting speed of the lifting cylinder of the hydraulic system is too low and is not matched with the running speed, that is, the driving system and the hydraulic system cannot achieve a coordinated operation state, at this time, the controller 12 outputs extra current to the ISG motor 11 through the storage battery 14, so that the ISG motor 11 can output extra power to the hydraulic system, the hydraulic pump 9 has higher rotating speed and torsion, and the driving system and the hydraulic system can be operated in a coordinated manner.
Specifically, when the lifting speed of the hydraulic system is too slow, which results in poor comprehensive efficiency, and the driving system and the hydraulic system cannot achieve a coordinated operation state, the engine 13 may cause the rotation speed thereof to decrease in order to meet the torque and power requirements of the load, thereby causing the rotation speed of the hydraulic pump 9 to decrease, so that the lifting speed of the lifting cylinder 7 is slow. In order to meet the working efficiency, after the controller 12 detects a rotation speed signal of the engine 13, the controller 12 sends a signal to the storage battery 14 and the ISG simultaneously, the ISG motor 11 is switched to the charging state of the storage battery 14, a rated current (alternating current) is output to the ISG motor 11 through the storage battery 14, the ISG motor 11 drives the engine 13 to increase the rotation speed of the engine 13, so that the hydraulic pump 9 has a higher rotation speed, at this time, the lifting speed of the lifting cylinder 7 is increased, the controller 12 dynamically monitors the lifting speed of the lifting cylinder 7 through the sensor 15, if the controller 12 detects that the lifting speed of the lifting cylinder 7 is still smaller than a set value (150mm/s), the controller 12 sends a signal to the electric proportional overflow valve 5 driving the hydraulic system to reduce the current of the electric proportional overflow valve 5, correspondingly, the valve core of the electric proportional overflow valve 5 moves to the left, namely, the working oil port K of the electric proportional overflow valve 5 is partially communicated with the working oil port G (communicated with the oil tank 4), the pressure of the hydraulic oil from the oil source is reduced at the working oil port K, the working oil port F and the working oil port C, the valve core of the hydraulic control valve 3 moves leftwards, after the working oil port D and the oil discharge port B (communicated oil tank 4) are partially communicated, the pressure oil flow from the oil source at the port P to the working oil port D through the working oil port A is reduced, the pressure of the working oil port D is correspondingly reduced, and therefore the engaging pressure of the clutch 2 is reduced. Therefore, the torque and power output to the transmission 1 are reduced, so that the driving speed is reduced, and at the moment, the driving torque is reduced, so that the rotating speed of the engine 13 is increased, and the generated increment enables the hydraulic pump 9 to have higher rotating speed, so that the lifting speed of the lifting cylinder 7 is further increased, and at the moment, the power distribution is more reasonable, so that the combined operation is efficiently carried out, and the energy waste is avoided.
When the two systems can work in a coordinated mode, the controller 12 recovers to output rated current to the electric proportional relief valve 5, and stops outputting extra current to the ISG motor 11, and accordingly, the ISG motor 11 recovers to charge the storage battery 14.
Example two:
the invention further provides engineering machinery, and the power distribution system in the first embodiment is arranged on the engineering machinery.
In a preferred embodiment, the work machine may be a loader, and the power distribution system is provided on the loader.
When the loader is running normally, the hydraulic system is not working, the lifting cylinder 7 is not acting, and the hydraulic system basically does not consume power. The engine 13 can drive the ISG motor 11, the gearbox 10 and the hydraulic pump 9 operate, at this moment, the ISG motor 11 charges to the storage battery 14 through the controller 12, the controller 12 outputs rated current to the driving system, namely the controller 12 outputs rated current to the electric proportional overflow valve 5, at this moment, the working port K and the working port H of the electric proportional overflow valve 5 are disconnected, the oil source P flows to the working port a of the hydraulic control valve 3, and then flows to the working port D of the hydraulic control valve 3 through the working port a, and the oil port end of the clutch 2 is reached by the working port D, because the working port D and the working port E are completely communicated, the clutch 2 is completely closed, and the loader can run according to the gear speed hung by the driver.
When the loader is in a heavy load or overload state, and lifting operation is required at the same time, and the loader operates at a higher gear (normally two-gear driving) speed, the controller 12 first detects the lifting speed of the lifting cylinder 7, and if the lifting speed is smaller than a set target value of 150mm/s, an extra current is output to the ISG motor 11 through the storage battery 14, so that the ISG motor 11 can output extra power to the hydraulic system, and at this time, the ISG motor 11 can output extra torque and power increment to the hydraulic pump 9, so that the hydraulic pump 9 has higher rotation speed and torque, and thus power and torque compensation are performed on the existing hydraulic system, so as to improve the lifting efficiency of the lifting cylinder 7, i.e., the lifting time is shortened by outputting extra torque and power increment to the hydraulic pump 9.
When the lifting time of the lifting cylinder 7 is exactly equal to the time of walking to the transport vehicle, namely the lifting cylinder is in the best matching state, namely the lifting cylinder is in coordination with the transport vehicle, at the moment, the power distribution of the power distribution system is more reasonable, and therefore a better energy-saving effect can be achieved.
If the driving system and the hydraulic system cannot be coordinated, in other words, the lift cylinder 7 is still relatively slow to the running speed of the loader, at this time, the controller 12 detects that the lift speed of the lift cylinder 7 is less than the set value, the controller 12 sends a signal to the electric proportional relief valve 5 to reduce the current of the electric proportional relief valve 5, so that the torque and the power of the clutch 2 of the transmission 10 are reduced to reduce the power consumed by the driving system, i.e. slow down the running speed of the loader, and the boom can obtain more power through the power distribution of the engine 13 to shorten the time for lifting the boom, so that the running speed of the loader and the boom lift speed are coordinated: that is, when the movable arm of the loader is lifted to the top, the loader can reach the optimal discharging position of the material transporting vehicle.
It will be appreciated by those skilled in the art that when the driver is engaged in full load or overload lift while engaged in gear, the engine 13 will have its speed reduced too much to meet the torque and power requirements of the load, thereby causing the hydraulic pump 9 to rotate at a reduced speed to lift the lift cylinders 7 without any force. In order to meet the working efficiency, after the controller 12 detects a rotation speed signal of the engine 13, the controller 12 sends a signal to the storage battery 14 and the ISG simultaneously, the ISG motor 11 is switched to the charging state of the storage battery 14, a rated current (alternating current) is output to the ISG motor 11 through the storage battery 14, the ISG motor 11 drives the engine 13 to increase the rotation speed of the engine 13, so that the hydraulic pump 9 has a higher rotation speed, at this time, the lifting speed of the lifting cylinder 7 is increased, the controller 12 dynamically monitors the lifting speed of the lifting cylinder 7 through the sensor 15, if the controller 12 detects that the lifting speed of the lifting cylinder 7 is still smaller than a set value (150mm/s), the controller 12 sends a signal to the electric proportional overflow valve 5 driving the hydraulic system to reduce the current of the electric proportional overflow valve 5, correspondingly, the valve core of the electric proportional overflow valve 5 moves to the left, namely, the working oil port K of the electric proportional overflow valve 5 is partially communicated with the working oil port G (communicated with the oil tank 4), the pressure of the hydraulic oil from the oil source is reduced at the working oil port K, the working oil port F and the working oil port C, the valve core of the hydraulic control valve 3 moves to the left, after the working oil port D and the working oil port B (the communicated oil tank 4) are partially communicated, the pressure oil flow from the oil source at the port P to the working oil port D through the working oil port A is reduced, the pressure of the working oil port D is correspondingly reduced, and therefore the engaging pressure of the clutch 2 is reduced. Thus, the torque and power output to the transmission 1 are also reduced, reducing the speed of travel, and the drive torque is reduced, thus increasing the rotational speed of the engine 13, which increases the speed of the hydraulic pump 9 to a higher rotational speed, further increasing the lift speed of the lift cylinders 7, and coordinating the drive system with the timing of the lifting of the lift cylinders 7: namely, the whole machine lifting cylinder 7 is just lifted to the top, and the loader runs just before the optimal unloading position of the material transporting vehicle.
When the movable arm is lifted to the top, the controller 12 resumes the output of the rated current to the electric proportional relief valve 5, and at the same time, stops the output of the large current to the ISG, and reversely charges the storage battery 14 through the ISG. It should be noted that the set value of the lifting speed of the lifting cylinder 7 may also be set to 120-160 mm/s, and the lifting speed of the lifting cylinder 7 may be set according to actual requirements.
In the process of lifting while walking, the whole machine firstly uses the ISG motor 11 to provide extra torque and power for a hydraulic system, so as to improve the lifting time of a movable arm, and when the lifting time still needs to be shortened, the power redistribution of the reduction of the driving power and the increase of the power of the hydraulic system is carried out, so as to meet the operation requirement; when the movable arm is lifted to the top, the lifting action is stopped, and the normal running function is recovered.
Similarly, when the ISG motor 11 stops outputting power to the hydraulic system and charges the battery 14 in the form of a generator during the idle running or the light load operation, the controller 12 outputs a rated current to the electric proportional relief valve 5 to secure a running speed for driving the loader.
According to the invention, the ISG motor 11 is adopted to compensate the power of the hydraulic system, and meanwhile, the power of the driving system and the hydraulic system is redistributed, so that the power distribution of the existing engine 13 is changed, the stop waiting time of a driver can be reduced, the working efficiency can be improved by about more than 6% through a single working cycle according to the operation habits of skilled drivers, and the working efficiency of the driver is greatly improved.
The above description is only a preferred embodiment of the present invention, and it should be noted that, for those skilled in the art, several modifications and variations can be made without departing from the technical principle of the present invention, and these modifications and variations should also be regarded as the protection scope of the present invention.

Claims (10)

1. A power distribution system is characterized by comprising a controller, an ISG motor, an engine, a storage battery, a driving system and a hydraulic system;
the controller acquires the running states of the driving system and the hydraulic system and judges whether the driving system and the hydraulic system run coordinately: if yes, the controller controls the ISG motor to charge the storage battery; if the driving system and the hydraulic system are not coordinated in operation, the controller controls the ISG motor to output extra power increment to the hydraulic system; if the driving system and the hydraulic system still run uncoordinated after the power increment is output, the controller reduces the power output of the driving system by controlling the driving system, so that the power output of the engine to the hydraulic system is increased until the two systems can run coordinately.
2. The power distribution system of claim 1, wherein the drive system includes an electric proportional relief valve connected to a controller that controls the electric proportional relief valve to reduce the power output of the drive system, and a pilot operated valve, a clutch, and a transmission that are in turn connected to the electric proportional relief valve.
3. The power distribution system of claim 2, wherein the hydraulic system comprises a hydraulic pump, a sensor, a lift cylinder, and a multi-way valve, the sensor is connected to the controller and the lift cylinder, respectively, and the hydraulic pump is in turn connected to the multi-way valve and the lift cylinder.
4. The power distribution system of claim 3, wherein the controller controls the operation states of the ISG motor, the driving system, and the hydraulic system by acquiring the lifting speed of the lifting cylinder transmitted from the sensor;
when the lifting speed of the lifting cylinder is smaller than a set value, the controller controls the ISG motor to output extra power increment to the hydraulic system;
or the controller controls the ISG motor to output extra power increment to the hydraulic system, and simultaneously controls the driving system to reduce the power output of the driving system, so that the power output of the engine to the hydraulic system is increased, and the coordinated operation of the lifting cylinder and the driving system is realized.
5. The power distribution system of claim 2, wherein the working port K of the electric proportional overflow valve is connected with the control port H of the electric proportional overflow valve, and the working port D of the hydraulic control valve is connected with the control port E of the hydraulic control valve.
6. The power distribution system of claim 2, wherein the driving system is further provided with an energy accumulator, and the energy accumulator is connected with a working oil port K oil way of the electric proportional overflow valve.
7. The power distribution system of claim 3, further comprising a gearbox coupled to the ISG motor and the hydraulic pump, respectively.
8. The power distribution system of claim 3, further comprising an oil tank, wherein the oil discharge port G of the electric proportional overflow valve, the oil discharge port B of the hydraulic control valve, the oil return port of the multi-way valve, and the oil inlet of the hydraulic pump are connected with the oil tank.
9. The power distribution system of claim 7, wherein the gearbox, engine, and ISG motor are disposed on a common axis.
10. A construction machine comprising the power distribution system according to any one of claims 1 to 9.
CN202110441224.6A 2021-04-23 2021-04-23 Power distribution system and engineering machinery Active CN113137411B (en)

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Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN202609873U (en) * 2012-03-23 2012-12-19 三一集团有限公司 Oil-electricity hybrid motive power stacking machine
CN108360600A (en) * 2018-04-04 2018-08-03 徐工集团工程机械股份有限公司科技分公司 A kind of loading mechanomotive force distribution control system and control method
CN110778704A (en) * 2019-10-25 2020-02-11 浙江吉利汽车研究院有限公司 Hybrid power hydraulic system and vehicle

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN202609873U (en) * 2012-03-23 2012-12-19 三一集团有限公司 Oil-electricity hybrid motive power stacking machine
CN108360600A (en) * 2018-04-04 2018-08-03 徐工集团工程机械股份有限公司科技分公司 A kind of loading mechanomotive force distribution control system and control method
CN110778704A (en) * 2019-10-25 2020-02-11 浙江吉利汽车研究院有限公司 Hybrid power hydraulic system and vehicle

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