US20090090102A1 - Method of reducing the load of one or more engines in a large hydraulic excavator - Google Patents
Method of reducing the load of one or more engines in a large hydraulic excavator Download PDFInfo
- Publication number
- US20090090102A1 US20090090102A1 US12/299,406 US29940607A US2009090102A1 US 20090090102 A1 US20090090102 A1 US 20090090102A1 US 29940607 A US29940607 A US 29940607A US 2009090102 A1 US2009090102 A1 US 2009090102A1
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- US
- United States
- Prior art keywords
- delivery quantity
- consumer
- engine
- reducing
- hydraulic
- 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.)
- Abandoned
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Classifications
-
- 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
- E02F9/2246—Control of prime movers, e.g. depending on the hydraulic load of work tools
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- Engineering & Computer Science (AREA)
- Mining & Mineral Resources (AREA)
- Civil Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structural Engineering (AREA)
- Operation Control Of Excavators (AREA)
- Control Of Positive-Displacement Pumps (AREA)
Abstract
Description
- The invention relates to a method of reducing the load of at least one engine, in particular in an internal combustion engine, arranged in a large hydraulic excavator.
- The document DE 699 20 452 T2 describes a mobile working machine with hydraulic circuit, wherein the hydraulic circuit comprises one of the cylinders arranged in a hoisting device, which is suitable for handling a variable load. Furthermore provided is a storage battery for the recovery or feedback of the decreasing load energy.
- Among other things, the overload of a drive motor is indicated by a drop in the speed. If this speed drop is not counter-acted by reducing the load, the speed of the drive motor continues to drop until the motor stops.
- Large hydraulic excavators with an operational weight >100 tons are normally provided with installed engine capacities on the order of magnitude of 500 to 3,000 kW. The cylinder volume for these engines as a rule is in the range of 15 to 60 liters, wherein the different cylinder volumes in this case correspond to their consumable output.
- Providing engines with even larger dimensions, which could compensate for any type of overload, is tied to such high costs that these engines become uneconomical. As a result of the aforementioned reasons, engines are used that enter the overload range during certain operating conditions and, as explained in the above, react with drastic speed drops.
- It is the goal of the present invention to provide a method which in certain overload situations permits the reduction of the load of at least one engine, in particular an internal combustion engine arranged in a large hydraulic excavator and, for the most part, makes it possible to compensate for the aforementioned negative effects.
- This goal is achieved for a speed overload situation with a method of reducing the load of at least one engine, in particular an internal combustion engine, arranged in a large hydraulic excavator by lowering the delivery quantity of at least one secondary hydraulic consumer, in particular a pump, far enough so that the respective engine is again returned to its operational speed range.
- Advantageous modifications of the subject matter of the invention follow from the dependent claims.
- If the desired reduction in the delivery quantity of the secondary consumer(s) is not sufficient to return the respective engine to its operational speed range, it is additionally proposed that once the desired reduction in the delivery quantity of the secondary consumer has been achieved, the delivery quantity of at least one hydraulic main consumer, e.g. a main operating pump, is also reduced by a predetermined amount of the delivery quantity, wherein the reduction in the delivery quantity continues until the respective engine has again been returned to its normal speed range for the operation.
- Large hydraulic excavators with an operational weight of >100 tons are equipped with a plurality of hydraulic consumers (main consumers and secondary consumers), which frequently are embodied as axial piston pumps with adjustable pumping capacity. The power consumption of these pumps is added up, thus resulting in the total load for the engine or engines.
- To be able to use the smallest economically viable cylinder volume with respect to the engine and, as previously explained, reduce the drive motor speed at a relatively low overload already, e.g. when a bucket enters the material, the delivery quantity of at least one hydraulic secondary consumer (additional consumer) is initially reduced.
- According to a different idea behind the invention, when using axial piston pumps, these pumps are adjusted using pressure-proportional valves or servo valves.
- Controllable axial piston pumps are addressed herein, among other things, such as the ones used for ventilator drives in oil cooling and water cooling systems to which fixed displacement pumps are frequently assigned.
- It is furthermore advantageous if the main operating pumps are controllable high-pressure axial piston pumps, for which the delivery quantity is controlled with the aid of pressure-proportional valves or servo valves, in the same way as for the secondary consumers. The delivery quantity of these pumps is reduced only following the completion of the fine control via the initially occurring reduction in the delivery quantity of the secondary consumer.
- The subject matter of the present invention is described in the following and is illustrated in the drawing, which shows in:
-
FIGS. 1 and 2 A graphic representation of different load spectrums of an engine installed in a large hydraulic excavator. - Two examples are presented in the following:
- Engine capacity: 2×900 kW
- Delivery quantity for installed operating pumps: 4×920 l/min, corresponding to 3,680 l/min.
- Operating pressure: 280 bar
- The associated diagram shows that with a given engine capacity (1,800 kW) and a given operating pressure for the pumps (280 bar), the operating load that adjusts at the pumps will be 1,900 kW, which exceeds the capacity of the installed engine (1,800 kW).
- The engine can be returned to its capacity range at the time of installation by reducing, for example, the delivery quantity of at least one secondary hydraulic consumer that is not listed in further detail herein (e.g. a pump) by 100 kW.
- Engine capacity: 2×900 kW
- Delivery quantity of installed operating pumps: 4×920 l/min, corresponding to 3,680 l/min
- Operating pressure: 320 bar
- With a predetermined capacity for the installed engine (1,800 kW) in connection with the also predetermined operating pressure (320 bar), a necessary load of 2,200 kW would adjust for the operating pumps.
- In a first phase, the delivery quantity of the secondary consumers is reduced by 500 l/min. The diagram shows that only a reduction to 1,900 kW is possible in this case, which still exceeds the installed engine capacity of 1,800 kW.
- The engine can then be returned to the installation capacity of 1,800 kW by additionally reducing the delivery quantity of a main consumer by 100 kW and no further speed reductions will occur.
Claims (8)
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10-2006-020.441.7 | 2006-05-03 | ||
DE102006000020 | 2006-05-03 | ||
PCT/EP2007/003582 WO2007124892A2 (en) | 2006-05-03 | 2007-04-24 | Method of reducing the load of one or more engines in a large hydraulic excavator |
Publications (1)
Publication Number | Publication Date |
---|---|
US20090090102A1 true US20090090102A1 (en) | 2009-04-09 |
Family
ID=40522097
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US12/299,406 Abandoned US20090090102A1 (en) | 2006-05-03 | 2007-04-24 | Method of reducing the load of one or more engines in a large hydraulic excavator |
Country Status (1)
Country | Link |
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US (1) | US20090090102A1 (en) |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US8606451B2 (en) | 2010-10-06 | 2013-12-10 | Caterpillar Global Mining Llc | Energy system for heavy equipment |
US8626403B2 (en) | 2010-10-06 | 2014-01-07 | Caterpillar Global Mining Llc | Energy management and storage system |
US8718845B2 (en) | 2010-10-06 | 2014-05-06 | Caterpillar Global Mining Llc | Energy management system for heavy equipment |
US9190852B2 (en) | 2012-09-21 | 2015-11-17 | Caterpillar Global Mining Llc | Systems and methods for stabilizing power rate of change within generator based applications |
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US5167121A (en) * | 1991-06-25 | 1992-12-01 | University Of British Columbia | Proportional hydraulic control |
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US7356991B2 (en) * | 2004-12-16 | 2008-04-15 | Doosan Intracore Co., Ltd. | Hydraulic control device of an excavator with improved loading performance on a slope |
US7360357B2 (en) * | 2005-03-07 | 2008-04-22 | Parker-Hannifin Corporation | Hydraulic steering system with input horsepower limiting circuit and increased fan speeds at low engine RPM |
US20090056324A1 (en) * | 2005-05-18 | 2009-03-05 | Yoshiaki Itakura | Hydraulic control device of construction machinery |
US20090159143A1 (en) * | 2006-07-31 | 2009-06-25 | Shin Caterpillar Mitsubishi Ltd. | Fluid pressure circuit |
US7581449B2 (en) * | 2005-05-16 | 2009-09-01 | Wrds, Inc. | System and method for power pump performance monitoring and analysis |
US7748279B2 (en) * | 2007-09-28 | 2010-07-06 | Caterpillar Inc | Hydraulics management for bounded implements |
-
2007
- 2007-04-24 US US12/299,406 patent/US20090090102A1/en not_active Abandoned
Patent Citations (46)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3425574A (en) * | 1967-01-25 | 1969-02-04 | Bucyrus Erie Co | Hydraulic power unit for a doubleacting cylinder |
US4050478A (en) * | 1975-04-23 | 1977-09-27 | International Harvester Company | Combined fixed and variable displacement pump system |
US4230022A (en) * | 1976-10-04 | 1980-10-28 | Caterpillar Tractor Co. | Hydraulic rock breaker circuit for an excavator |
US4606313A (en) * | 1980-10-09 | 1986-08-19 | Hitachi Construction Machinery Co., Ltd. | Method of and system for controlling hydraulic power system |
US4533900A (en) * | 1981-02-06 | 1985-08-06 | Bayerische Motoren Werke Aktiengesellschaft | Service-interval display for motor vehicles |
US4875337A (en) * | 1986-09-27 | 1989-10-24 | Hitachi Construction Machinery Co., Ltd. | Construction machine dual-dump hydraulic circuit with piloted arm-boom cylinder supply priority switching valves |
US5048293A (en) * | 1988-12-29 | 1991-09-17 | Hitachi Construction Machinery Co., Ltd. | Pump controlling apparatus for construction machine |
US5295353A (en) * | 1990-06-06 | 1994-03-22 | Kabushiki Kaisha Komatsu Seisakusho | Controlling arrangement for travelling work vehicle |
US5167121A (en) * | 1991-06-25 | 1992-12-01 | University Of British Columbia | Proportional hydraulic control |
US5190442A (en) * | 1991-09-06 | 1993-03-02 | Jorritsma Johannes N | Electronic pumpcontrol system |
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US5890303A (en) * | 1995-12-27 | 1999-04-06 | Hitachi Construction Machinery Co., Ltd. | Hydraulic by-pass circuit for a hydraulic shovel |
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US5852934A (en) * | 1996-03-30 | 1998-12-29 | Samsung Heavy Industries Co., Ltd. | Fluid joining device for power construction vehicles |
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US7069674B2 (en) * | 2002-12-26 | 2006-07-04 | Kubota Corporation | Hydraulic circuit for backhoe |
US20040263342A1 (en) * | 2003-06-30 | 2004-12-30 | Matlock Milton Gregory | System for monitoring motors |
US7174826B2 (en) * | 2004-01-28 | 2007-02-13 | Bucyrus International, Inc. | Hydraulic crowd control mechanism for a mining shovel |
US7251934B2 (en) * | 2004-03-27 | 2007-08-07 | Cnh America Llc | Work vehicle hydraulic system |
US7082758B2 (en) * | 2004-05-21 | 2006-08-01 | Komatsu, Ltd. | Hydraulic machine, system for monitoring health of hydraulic machine, and method thereof |
US20070234718A1 (en) * | 2004-07-28 | 2007-10-11 | Volvo Construction Equipment Holding Sweden Ab | Hydraulic System and Work Machine Comprising Such a System |
US7146808B2 (en) * | 2004-10-29 | 2006-12-12 | Caterpillar Inc | Hydraulic system having priority based flow control |
US7356991B2 (en) * | 2004-12-16 | 2008-04-15 | Doosan Intracore Co., Ltd. | Hydraulic control device of an excavator with improved loading performance on a slope |
US7275369B2 (en) * | 2004-12-22 | 2007-10-02 | Doosan Infracore Co., Ltd. | Hydraulic control device for controlling a boom-swing frame combined motion in an excavator |
US7360357B2 (en) * | 2005-03-07 | 2008-04-22 | Parker-Hannifin Corporation | Hydraulic steering system with input horsepower limiting circuit and increased fan speeds at low engine RPM |
US7581449B2 (en) * | 2005-05-16 | 2009-09-01 | Wrds, Inc. | System and method for power pump performance monitoring and analysis |
US20090056324A1 (en) * | 2005-05-18 | 2009-03-05 | Yoshiaki Itakura | Hydraulic control device of construction machinery |
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Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US8606451B2 (en) | 2010-10-06 | 2013-12-10 | Caterpillar Global Mining Llc | Energy system for heavy equipment |
US8626403B2 (en) | 2010-10-06 | 2014-01-07 | Caterpillar Global Mining Llc | Energy management and storage system |
US8718845B2 (en) | 2010-10-06 | 2014-05-06 | Caterpillar Global Mining Llc | Energy management system for heavy equipment |
US9120387B2 (en) | 2010-10-06 | 2015-09-01 | Caterpillar Global Mining Llc | Energy management system for heavy equipment |
US9190852B2 (en) | 2012-09-21 | 2015-11-17 | Caterpillar Global Mining Llc | Systems and methods for stabilizing power rate of change within generator based applications |
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