CA2651029C - 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
- CA2651029C CA2651029C CA2651029A CA2651029A CA2651029C CA 2651029 C CA2651029 C CA 2651029C CA 2651029 A CA2651029 A CA 2651029A CA 2651029 A CA2651029 A CA 2651029A CA 2651029 C CA2651029 C CA 2651029C
- Authority
- CA
- Canada
- Prior art keywords
- engine
- hydraulic
- consumer
- delivery quantity
- reducing
- 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.)
- Expired - Fee Related
Links
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
-
- 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
- E02F9/2221—Control of flow rate; Load sensing arrangements
- E02F9/2225—Control of flow rate; Load sensing arrangements using pressure-compensating valves
- E02F9/2228—Control of flow rate; Load sensing arrangements using pressure-compensating valves including an electronic controller
-
- 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
- E02F9/2221—Control of flow rate; Load sensing arrangements
- E02F9/2232—Control of flow rate; Load sensing arrangements using one or more variable displacement pumps
- E02F9/2235—Control of flow rate; Load sensing arrangements using one or more variable displacement pumps including an electronic controller
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
- F04B17/05—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by internal-combustion engines
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B2203/00—Motor parameters
- F04B2203/06—Motor parameters of internal combustion engines
- F04B2203/0604—Power
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B2203/00—Motor parameters
- F04B2203/06—Motor parameters of internal combustion engines
- F04B2203/0605—Rotational speed
Abstract
Method of reducing the load of at least one engine, in particular an internal combustion engine, arranged in a large hydraulic excavator by at least one hydraulic secondary consumer, in particular a feed pump, in an overload speed situation of the respective engine, being reduced in its delivery quantity until the respective engine is returned again to its operational speed range.
Description
METHOD OF REDUCING THE LOAD OF ONE OR MORE ENGINES IN A
LARGE HYDRAULIC EXCAVATOR
[001] 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.
LARGE HYDRAULIC EXCAVATOR
[001] 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.
[002] 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.
Furthermore provided is a storage battery for the recovery or feedback of the decreasing load energy.
[003] 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.
[004] 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.
[005] 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.
[005a] According to an aspect of the present invention, there is provided a method for reducing a load of at least one engine arranged in a hydraulic excavator having an oil cooling system, the method comprising: driving at least one hydraulic main consumer with the at least one engine; driving at least one hydraulic secondary consumer for the oil cooling system with the at least one engine; and during a speed overload situation of the at least one engine, reducing a delivery quantity of the at least one hydraulic secondary consumer for the oil cooling system until the at least one engine has been returned to a desired operational speed range.
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.
[005a] According to an aspect of the present invention, there is provided a method for reducing a load of at least one engine arranged in a hydraulic excavator having an oil cooling system, the method comprising: driving at least one hydraulic main consumer with the at least one engine; driving at least one hydraulic secondary consumer for the oil cooling system with the at least one engine; and during a speed overload situation of the at least one engine, reducing a delivery quantity of the at least one hydraulic secondary consumer for the oil cooling system until the at least one engine has been returned to a desired operational speed range.
[006] Some embodiments of the present invention may 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.
[007] In some embodiments, this may be 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.
[008] Advantageous modifications of the subject matter of the invention follow from the dependent claims.
[009] 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, may also be 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.
= 68297-1149 [00101 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.
[0011] To be able to use the smallest economically viable cylinder volume with respect to the engine and, as previously explained, some embodiments may 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.
[00121 According to a different idea behind the invention, when using axial piston pumps, these pumps are adjusted using pressure-proportional valves or servo valves.
[00131 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.
[0014] 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. In some embodiments, the delivery quantity of these pumps may be reduced only following the completion of the fine control via the initially occurring reduction in the delivery quantity of the secondary consumer.
[00151 [0016] The subject matter of the present invention is described in the following and is illustrated in the drawing, which shows in:
[0017] Figures 1 and 2 A graphic representation of different load spectrums of an engine installed in a large hydraulic excavator.
[0017a] Figure 3 A schematic representation of an engine [0017b] Figures 4a-4e Flow charts depicting example methods for reducing a load of at least one engine [0018] Two examples are presented in the following:
[0019] Example 1:
Engine capacity: 2 x 900 kW
Delivery quantity for installed operating pumps: 4 x 920 I/min, corresponding to 3,680 I/min.
Operating pressure: 280 bar [0020] The associated diagram (FIG. 1) 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).
[0021] 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.
[0022] Example 2:
Engine capacity: 2 x 900 kW
Delivery quantity of installed operating pumps: 4 x 9201/min, corresponding to 3,680 l/min Operating pressure: 320 bar [0023] 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.
[0024] In a first phase, the delivery quantity of the secondary consumers is reduced by 5001/min. The diagram (FIG. 2) 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.
[0025] 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.
[0026] FIG. 3 shows an engine 1 which provides a capacity which is relieved by a hydraulic system of a machine (not shown). Adjustable pumps are linked to the engine 1, including at least a main operating pump (or main consumer) 2 and an adjustable pump (or secondary consumer) 3 for an oil cooling system. A speed sensor 5 controls the engine rotational speed of the engine 1 and monitors this speed in a control unit 4.
In the control unit 4, the present rotational speed and the actual power output of the engine 1 are monitored.
[0027] In case that an improved performance is required by the hydraulic system, which is greater than the set maximum power output of the engine 1, the rotational speed of the engine 1 will drop. In this situation a signal is sent from the control unit 4 to the control unit 6 of the oil cooling pump 3 to reduce the delivery quantity of this pump toward zero. In the event that the deactivation of the oil cooling pump 6 is not sufficient, the control unit 4 sends a second separate signal to the control unit 7 of the main pump 2. The main pump 2 reduces its delivery quantity until the rated speed and the aligned power output of the engine 1 is reached. When the engine 1 returns to its normal speed range and with this to the normal power output, first the main pump 2 and then the oil cooling pump 3 will be regulated to their normal operating conditions.
[0028] FIGs. 4a to 4e are flow charts depicting example methods of reducing the load of at least one engine as described above.
= 68297-1149 [00101 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.
[0011] To be able to use the smallest economically viable cylinder volume with respect to the engine and, as previously explained, some embodiments may 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.
[00121 According to a different idea behind the invention, when using axial piston pumps, these pumps are adjusted using pressure-proportional valves or servo valves.
[00131 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.
[0014] 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. In some embodiments, the delivery quantity of these pumps may be reduced only following the completion of the fine control via the initially occurring reduction in the delivery quantity of the secondary consumer.
[00151 [0016] The subject matter of the present invention is described in the following and is illustrated in the drawing, which shows in:
[0017] Figures 1 and 2 A graphic representation of different load spectrums of an engine installed in a large hydraulic excavator.
[0017a] Figure 3 A schematic representation of an engine [0017b] Figures 4a-4e Flow charts depicting example methods for reducing a load of at least one engine [0018] Two examples are presented in the following:
[0019] Example 1:
Engine capacity: 2 x 900 kW
Delivery quantity for installed operating pumps: 4 x 920 I/min, corresponding to 3,680 I/min.
Operating pressure: 280 bar [0020] The associated diagram (FIG. 1) 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).
[0021] 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.
[0022] Example 2:
Engine capacity: 2 x 900 kW
Delivery quantity of installed operating pumps: 4 x 9201/min, corresponding to 3,680 l/min Operating pressure: 320 bar [0023] 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.
[0024] In a first phase, the delivery quantity of the secondary consumers is reduced by 5001/min. The diagram (FIG. 2) 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.
[0025] 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.
[0026] FIG. 3 shows an engine 1 which provides a capacity which is relieved by a hydraulic system of a machine (not shown). Adjustable pumps are linked to the engine 1, including at least a main operating pump (or main consumer) 2 and an adjustable pump (or secondary consumer) 3 for an oil cooling system. A speed sensor 5 controls the engine rotational speed of the engine 1 and monitors this speed in a control unit 4.
In the control unit 4, the present rotational speed and the actual power output of the engine 1 are monitored.
[0027] In case that an improved performance is required by the hydraulic system, which is greater than the set maximum power output of the engine 1, the rotational speed of the engine 1 will drop. In this situation a signal is sent from the control unit 4 to the control unit 6 of the oil cooling pump 3 to reduce the delivery quantity of this pump toward zero. In the event that the deactivation of the oil cooling pump 6 is not sufficient, the control unit 4 sends a second separate signal to the control unit 7 of the main pump 2. The main pump 2 reduces its delivery quantity until the rated speed and the aligned power output of the engine 1 is reached. When the engine 1 returns to its normal speed range and with this to the normal power output, first the main pump 2 and then the oil cooling pump 3 will be regulated to their normal operating conditions.
[0028] FIGs. 4a to 4e are flow charts depicting example methods of reducing the load of at least one engine as described above.
Claims (8)
1. A method for reducing a load of at least one engine arranged in a hydraulic excavator having an oil cooling system, the method comprising:
driving at least one hydraulic main consumer with the at least one engine;
driving at least one hydraulic secondary consumer for the oil cooling system with the at least one engine; and during a speed overload situation of the at least one engine, reducing a delivery quantity of the at least one hydraulic secondary consumer for the oil cooling system until the at least one engine has been returned to a desired operational speed range.
driving at least one hydraulic main consumer with the at least one engine;
driving at least one hydraulic secondary consumer for the oil cooling system with the at least one engine; and during a speed overload situation of the at least one engine, reducing a delivery quantity of the at least one hydraulic secondary consumer for the oil cooling system until the at least one engine has been returned to a desired operational speed range.
2. The method according to claim 1, wherein the delivery quantity of the at least one secondary consumer is reduced by a predetermined amount.
3. The method according to claim 2, wherein the predetermined amount is relative to a total pumping capacity of the at least one secondary consumer, and that once the delivery quantity of the at least one secondary consumer has been lowered by the predetermined amount, if the at least one engine has not returned to the desired operational speed range, a delivery quantity of the at least one hydraulic main consumer is reduced by a predetermined share of the delivery quantity of the at least one hydraulic main consumer.
4. The method according to claim 3, wherein reducing the delivery quantity of the at least one hydraulic main consumer continues until the at least one engine has been returned to the desired operational speed range.
5. The method according to any one of claims 1 to 4, wherein the step of reducing the delivery quantity of the at least one hydraulic secondary consumer for the oil cooling system is performed after a predetermined overload level threshold is reached.
6. The method according to any one of claims 1 to 5, wherein the hydraulic excavator is a large hydraulic excavator with a charge weight of greater than 100 tons.
7. The method according to any one of claims 1 to 6, wherein the at least one engine is an internal combustion engine.
8. The method according to any one of claims 1 to 7, wherein the at least one hydraulic main consumer comprises a main operating pump.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102006020441.7 | 2006-05-03 | ||
| DE102006020441.7A DE102006020441B4 (en) | 2006-05-03 | 2006-05-03 | Method for reducing the load of one or more engines in a large hydraulic excavator |
| 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 (2)
| Publication Number | Publication Date |
|---|---|
| CA2651029A1 CA2651029A1 (en) | 2007-11-08 |
| CA2651029C true CA2651029C (en) | 2014-01-28 |
Family
ID=38222681
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA2651029A Expired - Fee Related CA2651029C (en) | 2006-05-03 | 2007-04-24 | Method of reducing the load of one or more engines in a large hydraulic excavator |
Country Status (6)
| Country | Link |
|---|---|
| EP (1) | EP2013423A2 (en) |
| AU (1) | AU2007245841B8 (en) |
| CA (1) | CA2651029C (en) |
| DE (1) | DE102006020441B4 (en) |
| WO (1) | WO2007124892A2 (en) |
| ZA (1) | ZA200808927B (en) |
Family Cites Families (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE2251904A1 (en) * | 1972-10-23 | 1974-04-25 | Weserhuette Ag Eisenwerk | LIMIT LOAD CONTROL FOR HYDRAULIC DRIVES |
| DE2331617A1 (en) * | 1973-06-22 | 1975-01-16 | Bosch Gmbh Robert | CONTROL DEVICE FOR HYDROPUMPS |
| DE3176207D1 (en) * | 1980-10-09 | 1987-06-25 | Hitachi Construction Machinery | Method for controlling a hydraulic power system |
| DE3611553C1 (en) * | 1986-04-07 | 1987-07-23 | Orenstein & Koppel Ag | Arrangement for operating a diesel-hydraulic drive |
| DE4102621A1 (en) * | 1991-01-30 | 1992-08-06 | Orenstein & Koppel Ag | HYDROSTATIC DRIVE FOR WORKING MACHINES |
| AU4943699A (en) * | 1998-06-27 | 2000-01-17 | Lars Bruun | Mobile working machine |
| DE10307190A1 (en) * | 2003-02-20 | 2004-09-16 | O & K Orenstein & Koppel Gmbh | Method for controlling a hydraulic system of a mobile work machine |
| DE102005017127B4 (en) * | 2005-04-14 | 2021-09-16 | Linde Material Handling Gmbh | Combustion engine powered industrial truck with overload protection |
-
2006
- 2006-05-03 DE DE102006020441.7A patent/DE102006020441B4/en not_active Expired - Fee Related
-
2007
- 2007-04-24 WO PCT/EP2007/003582 patent/WO2007124892A2/en active Application Filing
- 2007-04-24 AU AU2007245841A patent/AU2007245841B8/en not_active Ceased
- 2007-04-24 CA CA2651029A patent/CA2651029C/en not_active Expired - Fee Related
- 2007-04-24 EP EP07724512A patent/EP2013423A2/en not_active Withdrawn
-
2008
- 2008-10-21 ZA ZA200808927A patent/ZA200808927B/en unknown
Also Published As
| Publication number | Publication date |
|---|---|
| ZA200808927B (en) | 2009-07-29 |
| EP2013423A2 (en) | 2009-01-14 |
| AU2007245841A1 (en) | 2007-11-08 |
| CA2651029A1 (en) | 2007-11-08 |
| AU2007245841B8 (en) | 2013-12-12 |
| WO2007124892A3 (en) | 2008-03-20 |
| WO2007124892A2 (en) | 2007-11-08 |
| DE102006020441B4 (en) | 2017-01-26 |
| DE102006020441A1 (en) | 2007-11-15 |
| AU2007245841B2 (en) | 2013-11-28 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| EEER | Examination request | ||
| MKLA | Lapsed |
Effective date: 20200831 |