CN113942381A - Energy optimization method for hydraulic hybrid power wheel loader based on working condition mode - Google Patents
Energy optimization method for hydraulic hybrid power wheel loader based on working condition mode Download PDFInfo
- Publication number
- CN113942381A CN113942381A CN202111078690.9A CN202111078690A CN113942381A CN 113942381 A CN113942381 A CN 113942381A CN 202111078690 A CN202111078690 A CN 202111078690A CN 113942381 A CN113942381 A CN 113942381A
- Authority
- CN
- China
- Prior art keywords
- loader
- hydraulic
- accumulator
- pressure
- energy
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Images
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
- B60K6/08—Prime-movers comprising combustion engines and mechanical or fluid energy storing means
- B60K6/12—Prime-movers comprising combustion engines and mechanical or fluid energy storing means by means of a chargeable fluidic accumulator
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60L—PROPULSION OF ELECTRICALLY-PROPELLED VEHICLES; SUPPLYING ELECTRIC POWER FOR AUXILIARY EQUIPMENT OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRODYNAMIC BRAKE SYSTEMS FOR VEHICLES IN GENERAL; MAGNETIC SUSPENSION OR LEVITATION FOR VEHICLES; MONITORING OPERATING VARIABLES OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRIC SAFETY DEVICES FOR ELECTRICALLY-PROPELLED VEHICLES
- B60L7/00—Electrodynamic brake systems for vehicles in general
- B60L7/10—Dynamic electric regenerative braking
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60L—PROPULSION OF ELECTRICALLY-PROPELLED VEHICLES; SUPPLYING ELECTRIC POWER FOR AUXILIARY EQUIPMENT OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRODYNAMIC BRAKE SYSTEMS FOR VEHICLES IN GENERAL; MAGNETIC SUSPENSION OR LEVITATION FOR VEHICLES; MONITORING OPERATING VARIABLES OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRIC SAFETY DEVICES FOR ELECTRICALLY-PROPELLED VEHICLES
- B60L2240/00—Control parameters of input or output; Target parameters
- B60L2240/40—Drive Train control parameters
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60L—PROPULSION OF ELECTRICALLY-PROPELLED VEHICLES; SUPPLYING ELECTRIC POWER FOR AUXILIARY EQUIPMENT OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRODYNAMIC BRAKE SYSTEMS FOR VEHICLES IN GENERAL; MAGNETIC SUSPENSION OR LEVITATION FOR VEHICLES; MONITORING OPERATING VARIABLES OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRIC SAFETY DEVICES FOR ELECTRICALLY-PROPELLED VEHICLES
- B60L2260/00—Operating Modes
- B60L2260/20—Drive modes; Transition between modes
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/60—Other road transportation technologies with climate change mitigation effect
- Y02T10/62—Hybrid vehicles
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/80—Technologies aiming to reduce greenhouse gasses emissions common to all road transportation technologies
- Y02T10/84—Data processing systems or methods, management, administration
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/80—Technologies aiming to reduce greenhouse gasses emissions common to all road transportation technologies
- Y02T10/92—Energy efficient charging or discharging systems for batteries, ultracapacitors, supercapacitors or double-layer capacitors specially adapted for vehicles
Landscapes
- Engineering & Computer Science (AREA)
- Transportation (AREA)
- Mechanical Engineering (AREA)
- Power Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Operation Control Of Excavators (AREA)
Abstract
The invention discloses a method for optimizing energy of a hydraulic hybrid wheel loader based on a working condition mode. The method comprises the following steps: dividing the working modes of the loader based on the power requirement of the loader under the current working condition; setting a pressure state change curve of a hydraulic accumulator of the loader according to the working mode of the loader; the current working condition of the loader is repeated, the pressure state change curve of the hydraulic energy accumulator of the loader is optimized according to the energy consumption of the loader, the optimized pressure state change curve of the hydraulic energy accumulator is obtained, the optimized pressure state change curve of the hydraulic energy accumulator is utilized to optimize energy distribution and the working point of an engine, and finally the energy conversion efficiency and the power performance of the loader are improved. The invention realizes energy recovery, reduces emission and improves the dynamic performance of the vehicle.
Description
Technical Field
The invention belongs to an energy optimization method for a loader in the field of engineering machinery, and relates to an energy optimization method for a hydraulic hybrid wheel loader based on a working condition mode.
Background
In recent years, to achieve the goal of "carbon neutralization", countries have established a series of emission standards for non-road mobile vehicles such as construction machines, agricultural machines. Hybrid power is an important development trend of the present vehicle power system in order to reduce carbon emission of the construction machine. The hybrid vehicle can be combined with the engine through an auxiliary power source, so that the working state of the engine is optimized, the oil consumption is reduced, and the carbon emission is reduced.
In a road vehicle, a hybrid power technology is widely applied, but the existing energy optimization method of the road vehicle is not suitable for working conditions with high repeatability and predictability of engineering machinery, and the working cycle of the engineering machinery has larger energy recovery potential.
Disclosure of Invention
Aiming at the defects of the prior art, the invention aims to provide a method for optimizing the energy of a hydraulic hybrid wheel loader based on a working condition mode, which is suitable for the hydraulic hybrid wheel loader and realizes the distribution of required power between a main power source and a hydraulic accumulator. Compared with the existing energy optimization method, the method is suitable for the working condition of the engineering machinery, energy recovery is realized through the hydraulic accumulator, energy is saved, and meanwhile, the power performance of the system is improved.
The invention aims at the work cycle of the wheel loader, and carries out energy recovery on braking energy by determining the SOC change curve of the hydraulic accumulator. The invention has certain adaptability, optimizes the strategy through parameter training aiming at the repeated working condition, improves the maximum output power, reduces the peak value of the output power of the main power source and improves the energy conversion efficiency.
The technical scheme of the invention is as follows:
the invention comprises the following steps:
step 1: dividing the working modes of the loader based on the power requirement of the loader under the current working condition;
step 2: setting a pressure state change curve of a hydraulic accumulator of the loader according to the working mode of the loader;
and step 3: the current working condition of the loader is repeated, the pressure state change curve of the hydraulic energy accumulator of the loader is optimized according to the energy consumption of the loader, the optimized pressure state change curve of the hydraulic energy accumulator is obtained, the optimized pressure state change curve of the hydraulic energy accumulator is utilized to optimize energy distribution and the working point of an engine, and finally the energy conversion efficiency and the power performance of the loader are improved.
In the step 1, the working modes of the loader are divided into a starting mode, an accelerating mode and a decelerating mode.
When the loader is in the starting mode, the power demand of the loader is low, and the main power source of the loader provides energy; when the loader is in the acceleration mode, the power requirement of the loader is high, and the main power source of the loader and the hydraulic accumulator provide energy together; when the loader is in the deceleration mode, the power demand of the loader is negative, the loader stores energy in the hydraulic accumulator after energy recovery, and the energy in the deceleration mode is provided by a main power source and a brake source of the loader.
When the loader is in the starting mode, the pressure of a hydraulic accumulator of the loader is kept unchanged; when the loader is in the acceleration mode, a hydraulic accumulator of the loader releases energy, and the pressure of the hydraulic accumulator decreases along with time; when the loader is in the deceleration mode, the hydraulic accumulator of the loader stores energy in and out, the pressure of the hydraulic accumulator rises along with the time, and finally the pressure returns to the initial pressure.
The step 3 specifically comprises the following steps:
3.1) determining the maximum value and the minimum value of the pressure of the hydraulic accumulator and the energy consumption of the loader under the current pressure state change curve of the hydraulic accumulator according to the pressure state change curve of the hydraulic accumulator of the loader, and setting the lower limit of the maximum value and the lower limit of the minimum value of the pressure of the hydraulic accumulator;
3.2) under the maximum value of the current pressure of the hydraulic energy accumulator, reducing the minimum value of the pressure of the hydraulic energy accumulator by preset step length, updating the pressure state change curve of the hydraulic energy accumulator, repeating the current working condition of the loader, and calculating the energy consumption of the loader under the updated pressure state change curve of the hydraulic energy accumulator;
3.3) continuously repeating the step 3.2) until the minimum value of the pressure of the hydraulic energy accumulator is smaller than the lower limit of the minimum value, obtaining the energy consumption of the loader corresponding to the minimum value of the pressure of each hydraulic energy accumulator under the maximum value of the pressure of the current hydraulic energy accumulator, and selecting the minimum value of the pressure of the hydraulic energy accumulator corresponding to the lowest energy consumption of the loader as the minimum value of the pressure of the optimal hydraulic energy accumulator corresponding to the maximum value of the pressure of the current hydraulic energy accumulator;
3.4) reducing the maximum value of the pressure of the hydraulic energy accumulator under the preset step length, and continuously repeating the steps 3.2) -3.3) until the maximum value of the pressure of the hydraulic energy accumulator is smaller than the lower limit of the maximum value, so as to obtain the minimum value of the optimal pressure of the hydraulic energy accumulator corresponding to the maximum value of the pressure of each hydraulic energy accumulator and the energy consumption of the loader;
3.5) selecting the maximum value of the pressure of the hydraulic energy accumulator with the lowest energy consumption of the loader in the step 3.4) and the corresponding minimum value of the optimal pressure of the hydraulic energy accumulator as the maximum value and the minimum value of the optimal pressure of the hydraulic energy accumulator to obtain an optimized pressure state change curve of the hydraulic energy accumulator;
the invention has the following beneficial effects:
1) the working cycle of the loader is analyzed, the requirements of the loader on power and energy consumption in each working stage are fully known, the energy distribution of the two power sources is determined according to the power requirements of the loader, the maximum power requirement of the main power source is reduced, the power performance of the loader is improved, and energy recovery is realized.
2) The method carries out parameter real-time optimization on the SOC change curve of the hydraulic accumulator, further improves the power performance of the loader and reduces the fuel consumption.
Drawings
FIG. 1 is a flow chart of the present invention;
FIG. 2 is a schematic diagram of the mode division and hydraulic accumulator SOC curves of the present invention;
FIG. 3 is a flow chart of parameter training of a hydraulic accumulator SOC curve of the present invention;
FIG. 4 is a schematic diagram of a tandem oil hybrid wheel loader;
FIG. 5 is a control schematic of the loader;
in the figure, the hydraulic control system comprises a main pump 1, an engine 2, a main pump 3, a one-way valve 4, a high-pressure accumulator 5, a speed reducing system and wheels 6, a hydraulic motor 7, a low-pressure accumulator 8, an overflow valve 9, an oil tank 10, an oil supplementing pump 11 and a second one-way valve.
Detailed Description
In order to make the objects, technical solutions and advantages of the present invention more clear, the present invention is further described in detail below with reference to the accompanying drawings.
In this embodiment, as shown in fig. 4, the loader is a tandem type oil hybrid wheel loader configuration, and includes an engine 1, a main pump 2, a first check valve 3, a high-pressure accumulator 4, a deceleration system and wheels 5, a hydraulic motor 6, a low-pressure accumulator 7, an overflow valve 8, an oil tank 9, an oil supply pump 10, and a second check valve 11.
An output shaft of the engine 1 is coaxially connected with an input shaft of a main pump 2, an output shaft of the main pump 2 is coaxially connected with an input shaft of an oil supplementing pump 10, an oil inlet of the oil supplementing pump 10 is communicated with an oil tank 9, an oil outlet of the oil supplementing pump 10 is communicated with an oil inlet of a second one-way valve 11, an oil outlet of the second one-way valve 11 is communicated with the oil tank through an overflow valve 8, an oil inlet of the main pump 2, an oil outlet of the oil supplementing pump 10, an oil inlet and outlet of a low-pressure energy accumulator 7 and a low-pressure oil inlet and outlet of a hydraulic motor 6 are communicated with each other, an oil outlet of the main pump 2 is communicated with an oil inlet of a first one-way valve 3, an oil inlet and outlet of a high-pressure energy accumulator 4 and a high-pressure oil inlet and outlet of the hydraulic motor 6 are communicated with each other; the output shaft of the hydraulic motor 6 is coaxially connected with the input shaft of the wheel 5 and the speed reduction system. The high-pressure accumulator 4 and the low-pressure accumulator 7 form a hydraulic accumulator of the loader, the engine 1 is a main power source of the loader, and the hydraulic motor 6, the deceleration system and the wheels 5 form a braking source of the loader.
A main loop of a hydraulic driving module of a serial oil hybrid power wheel loader is formed by connecting a main pump, a hydraulic motor, a high-pressure energy accumulator and a one-way valve in series, wherein an engine drives the main pump to provide power, the high-pressure energy accumulator is used for storing hydraulic energy for auxiliary energy supply, the one-way valve is used for limiting the steering direction and the energy flowing direction of the main pump, and the hydraulic motor drives wheels of the loader through a speed reducer; the hydraulic oil supplementing loop of the tandem type oil hybrid power wheel loader structure is composed of an oil supplementing pump, an overflow valve, a low-pressure energy accumulator and a one-way valve, wherein the oil supplementing pump is driven by an engine and is mainly used for supplementing oil when a main pump runs at a high speed, the low-pressure energy accumulator is mainly used for supplementing oil when the main pump runs at a low speed, and the one-way valve and the overflow valve are used for ensuring the safety of the loop.
As shown in fig. 1, the present invention comprises the following steps:
step 1: and dividing the working modes of the loader based on the power requirement of the loader under the current working condition. In this embodiment, the current operating condition is specifically running according to a certain rule, and the speed curve is fitted by selecting a cosine function and repeatedly runs, as shown in fig. 2;
in this embodiment, the formula of the speed of one-time movement in the working cycle of the wheel loader is fitted as follows:
v(t)＝v_0/2-v_0/2cos(2πt/T)
where v _0 is the maximum speed of the loader movement, T is the total time of one movement, T represents the time, and v (T) represents the speed of the loader.
The invention discloses a typical work cycle of a wheel loader, which can be decomposed into a plurality of unidirectional movements, aiming at the characteristics of high repeatability and predictability of the work cycle of the loader, the invention divides one movement into three stages of a starting mode, an accelerating mode and a decelerating mode, and each mode is characterized as follows:
starting a mode: 0-t _1 second after the movement starts is a starting mode, the speed is low when the vehicle is started, the acceleration is low, and the overall power requirement is low;
an acceleration mode: after the starting mode is ended, the time t _ 1-t _2+ t _1 seconds is an acceleration mode, the duration time is t _2, the average speed is high in the vehicle acceleration mode, the average acceleration is high, and the overall power requirement is high;
and (3) deceleration mode: and after the acceleration mode is finished, the t _1+ t _ 2-t _1+ t _2+ t _3 seconds are the deceleration mode, the vehicle deceleration braking duration is t _3, the vehicle speed reduction acceleration is a negative value, and the braking energy is reversely input into the hydraulic system to recover the energy.
Step 2: according to the working mode Of the loader, a State Of Charge curve (SOC curve for short) Of the hydraulic accumulator pressure State Of the loader is set, and as shown in fig. 2, fig. 2 shows a speed curve, an SOC change curve and mode division conditions Of a primary motion. The primary motion time is T _1+ T _2+ T _3, wherein T _1, T _2 and T _3 are respectively the duration time of the starting mode, the accelerating mode and the decelerating mode, and the SOC curve is a cosine curve, so that the shock of sudden change of the pressure change rate on a pump-motor of a hydraulic system is prevented. The pressure state change curve of the hydraulic accumulator is related to the current working condition.
When the loader is in the starting mode, the power demand of the loader is low, and the main power source of the loader provides energy; when the loader is in an acceleration mode, the power requirement of the loader is high, and a main power source of the loader and a hydraulic accumulator provide energy together; when the loader is in a deceleration mode, the power demand of the loader is negative, the loader stores energy in the hydraulic accumulator after energy recovery, and the energy in the deceleration mode is provided by a main power source and a brake source of the loader.
When the loader is in a starting mode, the pressure of a hydraulic accumulator of the loader is kept unchanged; when the loader is in an acceleration mode, the hydraulic energy accumulator of the loader releases energy, the pressure of the hydraulic energy accumulator is reduced along with time, and the pressure of the hydraulic energy accumulator reaches a lowest value SOC _ l after the acceleration mode is finished; when the loader is in a deceleration mode, the hydraulic accumulator of the loader stores energy in and out, the pressure of the hydraulic accumulator rises along with time, and finally returns to the initial pressure SOC _ h to prepare for starting the next movement.
And step 3: the current working condition of the loader is repeated, the pressure state change curve of the hydraulic energy accumulator of the loader is optimized according to the energy consumption of the loader, the optimized pressure state change curve of the hydraulic energy accumulator is obtained, the optimized pressure state change curve of the hydraulic energy accumulator is utilized to optimize energy distribution and the working point of an engine, and finally the energy conversion efficiency and the power performance of the loader are improved.
As shown in fig. 3, step 3 specifically includes:
3.1) determining the maximum value SOC _ h and the minimum value SOC _ l of the pressure of the hydraulic accumulator and the energy consumption of the loader under the current pressure state change curve of the hydraulic accumulator according to the pressure state change curve of the hydraulic accumulator of the loader, and setting the lower limit of the maximum value and the lower limit of the minimum value of the pressure of the hydraulic accumulator;
3.2) under the maximum value of the current pressure of the hydraulic energy accumulator, reducing the minimum value of the pressure of the hydraulic energy accumulator by preset step length, updating the pressure state change curve of the hydraulic energy accumulator, repeating the current working condition of the loader, and calculating the energy consumption of the loader under the updated pressure state change curve of the hydraulic energy accumulator;
3.3) continuously repeating the step 3.2) until the minimum value of the pressure of the hydraulic energy accumulator is smaller than the lower limit of the minimum value, obtaining the energy consumption of the loader corresponding to the minimum value of the pressure of each hydraulic energy accumulator under the maximum value of the pressure of the current hydraulic energy accumulator, and selecting the minimum value of the pressure of the hydraulic energy accumulator corresponding to the lowest energy consumption of the loader as the minimum value of the pressure of the optimal hydraulic energy accumulator corresponding to the maximum value of the pressure of the current hydraulic energy accumulator;
3.4) reducing the maximum value of the pressure of the hydraulic energy accumulator under the preset step length, and continuously repeating the steps 3.2) -3.3) until the maximum value of the pressure of the hydraulic energy accumulator is smaller than the lower limit of the maximum value, so as to obtain the minimum value of the optimal pressure of the hydraulic energy accumulator corresponding to the maximum value of the pressure of each hydraulic energy accumulator and the energy consumption of the loader;
3.5) in the specified training time, selecting the maximum value of the pressure of the hydraulic energy accumulator with the lowest energy consumption of the loader in the step 3.4) and the corresponding minimum value of the optimal pressure of the hydraulic energy accumulator as the maximum value and the minimum value of the optimal pressure of the hydraulic energy accumulator, and obtaining the optimized pressure state change curve of the hydraulic energy accumulator;
in this embodiment, the hydraulic accumulator SOC variation curve formula set in the energy distribution strategy is as follows:
startup mode (0 to t _ 1):
SOC(t)＝SOC_h
acceleration mode (t _1 to t _2+ t _ 1):
SOC(t)＝((SOC_h+SOC_l))/2+((SOC_h-SOC_l))/2 cos(π/t_2(t-t_1))
deceleration pattern (t _1+ t _2 to t _1+ t _2+ t _ 3):
SOC(t)＝((SOC_h+SOC_l))/2-((SOC_h-SOC_l))/2cos(π/t_3(t-t_1-t_2))
wherein t _1, t _2 and t _3 are the starting, accelerating and decelerating mode duration.
As shown in fig. 5, the high pressure accumulator pressure closed loop control principle is shown. In the embodiment, the loader driving system is provided with two controllers, the pressure controller is used for controlling the SOC of the high-pressure energy accumulator, and the control variable is the output torque of the engine; the vehicle speed controller is used for controlling the speed of the wheel loader, and the control variable is the displacement of the main pump.
The invention realizes the recovery of braking energy, can be applied to an oil-liquid hybrid power wheel loader, optimizes the working state of an engine, can optimize parameters, reduces the energy consumption and has good real-time performance.
The above-mentioned embodiments are merely illustrative of the preferred embodiments of the present invention, and do not limit the scope of the present invention, and various modifications and improvements made to the technical solution of the present invention by those skilled in the art without departing from the spirit of the present invention should fall within the protection scope defined by the claims of the present invention.
Claims (5)
1. A hydraulic hybrid wheel loader energy optimization method based on working condition modes is characterized by comprising the following steps:
step 1: dividing the working modes of the loader based on the power requirement of the loader under the current working condition;
step 2: setting a pressure state change curve of a hydraulic accumulator of the loader according to the working mode of the loader;
and step 3: the current working condition of the loader is repeated, the pressure state change curve of the hydraulic energy accumulator of the loader is optimized according to the energy consumption of the loader, the optimized pressure state change curve of the hydraulic energy accumulator is obtained, the optimized pressure state change curve of the hydraulic energy accumulator is utilized to optimize energy distribution and the working point of an engine, and finally the energy conversion efficiency and the power performance of the loader are improved.
2. The energy optimization method for hydraulic hybrid wheel loaders according to claim 1, wherein in step 1, the operation modes of the loader are divided into a start mode, an acceleration mode and a deceleration mode.
3. The method of claim 2, wherein when the loader is in the start mode, the power demand of the loader is low and the power is supplied by the main power source of the loader; when the loader is in the acceleration mode, the power requirement of the loader is high, and the main power source of the loader and the hydraulic accumulator provide energy together; when the loader is in the deceleration mode, the power demand of the loader is negative, the loader stores energy in the hydraulic accumulator after energy recovery, and the energy in the deceleration mode is provided by a main power source and a brake source of the loader.
4. The method of claim 2, wherein the hydraulic accumulator pressure of the loader remains constant while the loader is in the start mode; when the loader is in the acceleration mode, a hydraulic accumulator of the loader releases energy, and the pressure of the hydraulic accumulator decreases along with time; when the loader is in the deceleration mode, the hydraulic accumulator of the loader stores energy in and out, the pressure of the hydraulic accumulator rises along with the time, and finally the pressure returns to the initial pressure.
5. The method for optimizing energy of a hydraulic hybrid wheel loader according to claim 1, wherein step 3 is specifically:
3.1) determining the maximum value and the minimum value of the pressure of the hydraulic accumulator and the energy consumption of the loader under the current pressure state change curve of the hydraulic accumulator according to the pressure state change curve of the hydraulic accumulator of the loader, and setting the lower limit of the maximum value and the lower limit of the minimum value of the pressure of the hydraulic accumulator;
3.2) under the maximum value of the current pressure of the hydraulic energy accumulator, reducing the minimum value of the pressure of the hydraulic energy accumulator by preset step length, updating the pressure state change curve of the hydraulic energy accumulator, repeating the current working condition of the loader, and calculating the energy consumption of the loader under the updated pressure state change curve of the hydraulic energy accumulator;
3.3) continuously repeating the step 3.2) until the minimum value of the pressure of the hydraulic energy accumulator is smaller than the lower limit of the minimum value, obtaining the energy consumption of the loader corresponding to the minimum value of the pressure of each hydraulic energy accumulator under the maximum value of the pressure of the current hydraulic energy accumulator, and selecting the minimum value of the pressure of the hydraulic energy accumulator corresponding to the lowest energy consumption of the loader as the minimum value of the pressure of the optimal hydraulic energy accumulator corresponding to the maximum value of the pressure of the current hydraulic energy accumulator;
3.4) reducing the maximum value of the pressure of the hydraulic energy accumulator under the preset step length, and continuously repeating the steps 3.2) -3.3) until the maximum value of the pressure of the hydraulic energy accumulator is smaller than the lower limit of the maximum value, so as to obtain the minimum value of the optimal pressure of the hydraulic energy accumulator corresponding to the maximum value of the pressure of each hydraulic energy accumulator and the energy consumption of the loader;
3.5) selecting the maximum value of the pressure of the hydraulic accumulator with the lowest energy consumption of the loader in the step 3.4) and the corresponding minimum value of the optimal pressure of the hydraulic accumulator, and taking the maximum value and the minimum value of the optimal pressure of the hydraulic accumulator to obtain an optimized pressure state change curve of the hydraulic accumulator.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202111078690.9A CN113942381B (en) | 2021-09-15 | 2021-09-15 | Hydraulic hybrid power wheel loader energy optimization method based on working condition mode |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202111078690.9A CN113942381B (en) | 2021-09-15 | 2021-09-15 | Hydraulic hybrid power wheel loader energy optimization method based on working condition mode |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN113942381A true CN113942381A (en) | 2022-01-18 |
| CN113942381B CN113942381B (en) | 2023-04-25 |
Family
ID=79328425
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202111078690.9A Active CN113942381B (en) | 2021-09-15 | 2021-09-15 | Hydraulic hybrid power wheel loader energy optimization method based on working condition mode |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN113942381B (en) |
Citations (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0044252A1 (en) * | 1980-07-10 | 1982-01-20 | Jean Paul Jardinier | Method and system for the propulsion of a wheeled vehicle, comprising a hydraulic transmission |
| US20070096555A1 (en) * | 2006-11-29 | 2007-05-03 | Telcom Marketing Group, Inc. | Regenerative braking system for a work machine |
| CN101920722A (en) * | 2010-07-16 | 2010-12-22 | 徐工集团工程机械股份有限公司江苏徐州工程机械研究院 | Parallel-connected torque control system and method for hydraulic hybrid power vehicles |
| CN202345360U (en) * | 2011-06-29 | 2012-07-25 | 徐工集团工程机械股份有限公司江苏徐州工程机械研究院 | Hydrostatic transmission hybrid power drive apparatus based on hydraulic transformer vehicles |
| CN103057393A (en) * | 2012-12-30 | 2013-04-24 | 徐工集团工程机械股份有限公司江苏徐州工程机械研究院 | Control strategy of fluid and power combination hybrid power system and method for optimizing control parameter |
| CN104010854A (en) * | 2011-12-22 | 2014-08-27 | 罗伯特·博世有限公司 | Method For Operating A Serial Hydraulic Hybrid Drive System |
| DE102013006408A1 (en) * | 2013-04-15 | 2014-10-16 | Atlas Weyhausen Gmbh | working machine |
| CN104401219A (en) * | 2014-12-08 | 2015-03-11 | 吉林大学 | Power split type hydraulic hybrid power system of loading machine |
| US20160115672A1 (en) * | 2013-06-03 | 2016-04-28 | Volvo Construction Equipment Ab | A power system for a working machine |
| CN105980185A (en) * | 2014-02-04 | 2016-09-28 | 意大利德纳股份有限公司 | Controller for a series hydraulic hybrid transmission |
| CN107010031A (en) * | 2017-03-13 | 2017-08-04 | 同济大学 | The characteristic parameter matching method of key componentses in a kind of load mechanism kinetic energy reclaiming system |
| US20180030690A1 (en) * | 2015-08-25 | 2018-02-01 | Hitachi Construction Machinery Co., Ltd. | Hybrid Construction Machine |
-
2021
- 2021-09-15 CN CN202111078690.9A patent/CN113942381B/en active Active
Patent Citations (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0044252A1 (en) * | 1980-07-10 | 1982-01-20 | Jean Paul Jardinier | Method and system for the propulsion of a wheeled vehicle, comprising a hydraulic transmission |
| US20070096555A1 (en) * | 2006-11-29 | 2007-05-03 | Telcom Marketing Group, Inc. | Regenerative braking system for a work machine |
| CN101920722A (en) * | 2010-07-16 | 2010-12-22 | 徐工集团工程机械股份有限公司江苏徐州工程机械研究院 | Parallel-connected torque control system and method for hydraulic hybrid power vehicles |
| CN202345360U (en) * | 2011-06-29 | 2012-07-25 | 徐工集团工程机械股份有限公司江苏徐州工程机械研究院 | Hydrostatic transmission hybrid power drive apparatus based on hydraulic transformer vehicles |
| CN104010854A (en) * | 2011-12-22 | 2014-08-27 | 罗伯特·博世有限公司 | Method For Operating A Serial Hydraulic Hybrid Drive System |
| CN103057393A (en) * | 2012-12-30 | 2013-04-24 | 徐工集团工程机械股份有限公司江苏徐州工程机械研究院 | Control strategy of fluid and power combination hybrid power system and method for optimizing control parameter |
| DE102013006408A1 (en) * | 2013-04-15 | 2014-10-16 | Atlas Weyhausen Gmbh | working machine |
| US20160115672A1 (en) * | 2013-06-03 | 2016-04-28 | Volvo Construction Equipment Ab | A power system for a working machine |
| CN105980185A (en) * | 2014-02-04 | 2016-09-28 | 意大利德纳股份有限公司 | Controller for a series hydraulic hybrid transmission |
| CN104401219A (en) * | 2014-12-08 | 2015-03-11 | 吉林大学 | Power split type hydraulic hybrid power system of loading machine |
| US20180030690A1 (en) * | 2015-08-25 | 2018-02-01 | Hitachi Construction Machinery Co., Ltd. | Hybrid Construction Machine |
| CN107010031A (en) * | 2017-03-13 | 2017-08-04 | 同济大学 | The characteristic parameter matching method of key componentses in a kind of load mechanism kinetic energy reclaiming system |
Also Published As
| Publication number | Publication date |
|---|---|
| CN113942381B (en) | 2023-04-25 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN100436886C (en) | Electric oil pump control system in hybrid vehicle | |
| CN106274444B (en) | Engineering machinery mixed connection dynamical system | |
| CN103552454B (en) | Series parallel type hydraulic hybrid vehicle power assembly system | |
| CN101389516B (en) | Method for operating a hybrid vehicle | |
| CN103802836A (en) | Method for controlling hybrid electric vehicle | |
| CN102372025B (en) | Electric control closed type hydraulic steering system, control method and vehicle having system | |
| CN205136169U (en) | Hydraulic pressure traveling system by motor speed controller | |
| CN106891711B (en) | Series-parallel hydraulic hybrid power control system and control method for loader | |
| CN108560632B (en) | Electro-hydraulic hybrid-driven loader | |
| CN210554230U (en) | Hybrid power supply system for engineering machinery | |
| CN113942381B (en) | Hydraulic hybrid power wheel loader energy optimization method based on working condition mode | |
| CN210132998U (en) | Double-planet-row hybrid power system and hybrid power vehicle | |
| CN113738711B (en) | Hybrid energy storage unit of electrostatic liquid and flywheel | |
| CN115503685A (en) | Mode switching control method for dump truck with E-power architecture | |
| CN104669997A (en) | Power system and power control method of sanitation vehicle | |
| CN111267828B (en) | Hybrid power control system and method for vehicle | |
| CN107458387B (en) | Hydraulic auxiliary acceleration system for electro-hydraulic rail car | |
| CN103661922A (en) | Electricity-gas hybrid power plant used for servo mechanism | |
| CN103419620A (en) | Compressed-air power car with electronic control system | |
| CN212171941U (en) | Hybrid power system of heavy forklift | |
| CN110562028A (en) | Restraint piston type electromechanical hybrid power system | |
| CN217864334U (en) | Steering power-assisted system of pure electric commercial vehicle | |
| CN217347476U (en) | Hybrid loader and power device thereof | |
| CN113879098A (en) | Series-parallel connection type electro-hydraulic hybrid power system | |
| CN113580912A (en) | Series-type electro-hydraulic hybrid power system |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |