WO2011158733A1 - 作業機械 - Google Patents
作業機械 Download PDFInfo
- Publication number
- WO2011158733A1 WO2011158733A1 PCT/JP2011/063277 JP2011063277W WO2011158733A1 WO 2011158733 A1 WO2011158733 A1 WO 2011158733A1 JP 2011063277 W JP2011063277 W JP 2011063277W WO 2011158733 A1 WO2011158733 A1 WO 2011158733A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- rotational speed
- temperature
- engine
- output
- setting unit
- Prior art date
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F27/00—Control arrangements or safety devices specially adapted for heat-exchange or heat-transfer apparatus
- F28F27/02—Control arrangements or safety devices specially adapted for heat-exchange or heat-transfer apparatus for controlling the distribution of heat-exchange media between different channels
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
- F01P7/00—Controlling of coolant flow
- F01P7/02—Controlling of coolant flow the coolant being cooling-air
- F01P7/04—Controlling of coolant flow the coolant being cooling-air by varying pump speed, e.g. by changing pump-drive gear ratio
-
- 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
-
- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02F—DREDGING; SOIL-SHIFTING
- E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
- E02F9/20—Drives; Control devices
- E02F9/22—Hydraulic or pneumatic drives
- E02F9/226—Safety arrangements, e.g. hydraulic driven fans, preventing cavitation, leakage, overheating
-
- 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
- E02F9/2278—Hydraulic circuits
- E02F9/2292—Systems with two or more pumps
-
- 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
- E02F9/2278—Hydraulic circuits
- E02F9/2296—Systems with a variable displacement pump
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
- F01P11/00—Component parts, details, or accessories not provided for in, or of interest apart from, groups F01P1/00 - F01P9/00
- F01P11/08—Arrangements of lubricant coolers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
- F01P3/00—Liquid cooling
- F01P3/18—Arrangements or mounting of liquid-to-air heat-exchangers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
- F01P2025/00—Measuring
- F01P2025/08—Temperature
- F01P2025/30—Engine incoming fluid temperature
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
- F01P2025/00—Measuring
- F01P2025/60—Operating parameters
- F01P2025/64—Number of revolutions
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
- F01P7/00—Controlling of coolant flow
- F01P7/02—Controlling of coolant flow the coolant being cooling-air
- F01P7/04—Controlling of coolant flow the coolant being cooling-air by varying pump speed, e.g. by changing pump-drive gear ratio
- F01P7/044—Controlling of coolant flow the coolant being cooling-air by varying pump speed, e.g. by changing pump-drive gear ratio using hydraulic drives
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D2250/00—Engine control related to specific problems or objectives
- F02D2250/18—Control of the engine output torque
- F02D2250/26—Control of the engine output torque by applying a torque limit
Definitions
- the present invention relates to a work machine capable of switching the level of the output of an engine.
- the working machine In order to cool the cooling water of the engine of the working machine, the working machine is provided with a radiator and a cooling fan for blowing air to the radiator.
- the cooling fan may be driven by a hydraulic motor or the like which is driven independently from the engine.
- hydraulically driven cooling fans it is known that cooling can be performed efficiently by changing the rotational speed of the cooling fan according to the temperature of the engine coolant and the engine rotational speed ( Patent Document 1).
- the rotational speed of the cooling fan is merely changed according to the temperature of the engine coolant and the engine rotational speed, and particularly in relation to the engine output It did not control the rotational speed of the cooling fan.
- the working machine has a path according to the temperature of the cooling water on the engine, a radiator for cooling the engine cooling water, and a path for passing the cooling water to the radiator.
- a thermostat that opens and closes between fully closed and fully opened, a fan unit that blows outside air to the radiator, an output selection switch that switches the output of the engine, and a rotation that sets the rotational speed of the fan unit according to the temperature of the cooling water
- the rotation speed setting unit is a cooling water whose thermostat is fully opened from fully closed.
- the rotational speed setting unit includes a predetermined temperature lower than the temperature at which the thermostat starts valve opening and a predetermined temperature higher than the temperature at which the thermostat fully opens.
- a hydraulic oil cooler for cooling hydraulic oil supplied by a hydraulic pump, and a fan device according to a temperature of the hydraulic oil.
- the apparatus further comprises a hydraulic fluid temperature dependent rotational speed setting unit for setting the rotational speed, the fan device blows the outside air to the radiator and the hydraulic oil cooler, and the rotational speed adjustment unit sets the rotational speed set by the rotational speed setting unit And it is preferable to adjust the rotational speed of a fan apparatus so that it may become the rotational speed of the higher one among the rotational speeds set by the hydraulic fluid temperature dependent rotational speed setting part.
- a working fluid cooler for cooling a working fluid of a torque converter that transmits traveling driving force, and a temperature of the working fluid.
- the apparatus further comprises a working fluid temperature dependent rotational speed setting unit that sets the rotational speed of the fan device, the fan unit blows the outside air to the radiator and the working fluid cooler, and the rotational speed adjustment unit is set by the rotational speed setting unit It is preferable to adjust the rotational speed of the fan device so as to be the higher of the rotational speed and the rotational speed set by the working fluid temperature dependent rotational speed setting unit.
- a hydraulic oil cooler for cooling hydraulic oil supplied by a hydraulic pump, and a fan device of the fan device according to the temperature of the hydraulic oil.
- the fan device blows the outside air to the radiator, the hydraulic fluid cooler, and the hydraulic fluid cooler, and the rotational speed adjustment unit sets the rotational speed set by the rotational speed setting unit.
- the fan is mounted to have the highest rotational speed among the rotational speed set by the hydraulic oil temperature dependent rotational speed setting unit and the rotational speed set by the hydraulic fluid temperature dependent rotational speed setting unit.
- the rotational speed setting unit sets the temperature of the cooling water at a predetermined temperature higher than the temperature at which the thermostat is fully opened. In some cases, even if the output selector switch is switched to lower the engine output, the same rotational speed as when the output selector switch is switched to increase the engine output is set. It is preferable to do.
- FIG. 2 is a view showing a schematic configuration of a wheel loader 100.
- FIG. 3 is a diagram showing a curve of torque of the engine 1 and a curve of input torque to the torque converter 2.
- FIG. 3 is a diagram showing a curve of torque of the engine 1 and a curve of input torque to the torque converter 2. It is a figure which shows the relationship between the target engine rotational speed with respect to the depression amount of an accelerator pedal. It is a figure which shows the relationship between the target engine rotational speed with respect to the depression amount of an accelerator pedal. It is a figure which shows the relationship between the temperature of a cooling water, and the target rotational speed of the fan motor 11. As shown in FIG.
- FIG. 6 is a diagram showing the relationship between the hydraulic fluid temperature and the target rotational speed of the fan motor 11
- FIG. 6 is a diagram showing the relationship between the working fluid temperature and the target rotational speed of the fan motor 11 It is a figure which shows a modification. It is a figure which shows a modification.
- FIG. 1 is a side view of a wheel loader that is an example of a working machine according to the present embodiment.
- the wheel loader 100 includes a front vehicle body 110 having an arm 111, a bucket 112, a tire 113 and the like, and a rear vehicle body 120 having a cab 121, an engine compartment 122, a tire 123 and the like.
- the engine room 122 is covered with a building cover 131.
- a counterweight 124 is attached to the rear of the rear vehicle body 120.
- the arm 111 is pivoted (up and down) in the vertical direction by driving of an arm cylinder (not shown), and the bucket 112 is pivoted (dump or cloud) in the vertical direction by driving of the bucket cylinder 115.
- the front vehicle body 110 and the rear vehicle body 120 are rotatably connected to each other by the center pin 101, and the expansion and contraction of the steering cylinder 116 bends the front vehicle body 110 to the left and right with respect to the rear vehicle body 120.
- the radiator frame 135 includes a radiator 14 for cooling the cooling water of the engine 1, an oil cooler 16 for cooling the hydraulic fluid, and a working fluid cooler 15 for cooling the working fluid of the torque converter 2 shown in FIG. It is attached.
- the radiator frame 135 is fixed to the rear vehicle body 120.
- the air cooling fan unit 150 includes an air cooling fan 13 driven by a fan motor 11 and a fan shroud 151 shown in FIG. 2 described later, and is disposed at the rear of the radiator frame 135.
- the radiator frame 135 and the air-cooling fan unit 150 are covered with a cooler building cover 132 on the side surface and the top surface (FIG. 1).
- the cooler building cover 132 is open at the rear and is covered by an openably mounted grill 140.
- the grill 140 is a cover provided with a plurality of openings so that intake or exhaust by the air cooling fan 13 can be communicated with the outside.
- FIG. 2 is a view showing a schematic configuration of the wheel loader 100.
- An output shaft (not shown) of a torque converter 2 (hereinafter referred to as a torque converter) is connected to the output shaft of the engine 1, and an output shaft (not shown) of the torque converter 2 is connected to the transmission 3.
- the torque converter 2 is a fluid clutch comprising a known impeller, turbine and stator, and the rotation of the engine 1 is transmitted to the transmission 3 via the torque converter 2.
- the transmission 3 has a hydraulic pressure clutch that shifts its speed gear to first to fourth gears, and the rotation of the output shaft of the torque converter 2 is shifted by the transmission 3. The rotation after transmission is transmitted to the tire 6 via the propeller shaft 4 and the axle 5, and the wheel loader travels.
- the wheel loader 100 includes a working hydraulic pump 7 driven by the engine 1, a control valve 17 for controlling pressure oil discharged from the working hydraulic pump 7, and a working hydraulic cylinder 18 (for example, a bucket cylinder 115 or an arm cylinder). And).
- the wheel loader 100 includes a hydraulic pump 8 for driving the fan motor 11, a variable relief valve 9 for controlling the rotational speed of the fan motor 11, the fan motor 11 and the air cooling fan 13 described above, and a change in rotational speed of the engine 1.
- the hydraulic circuit 12a for driving the fan motor 11 is provided with a check valve 10 for preventing cavitation when the pressure becomes negative.
- Cooling water of the engine 1 flows into the radiator 14 via the thermostat 22 and is cooled by the radiator 14 and then returns to the engine 1 again.
- the thermostat 22 is provided in the middle of the cooling water piping from the engine 1 to the radiator 14, and the degree of opening is adjusted according to the temperature of the cooling water between fully closed and fully open.
- the valve opening start temperature is 85 degrees
- the fully open temperature is 95 degrees. That is, the thermostat 22 is completely closed until the temperature of the cooling water touching the thermostat 22 reaches 85 degrees, and when it exceeds 85 degrees, the thermostat 22 starts to open gradually and the opening area increases, and reaches 95 degrees. Is fully open.
- the hydraulic oil is sucked and discharged from the hydraulic oil tank 31 by the working hydraulic pump 7, flows into the oil cooler 16 via the control valve 17, is cooled by the oil cooler 16, and then returns to the hydraulic oil tank 31 again. .
- the working fluid of the torquer 2 flows from the torque converter 2 into the working fluid cooler 15, is cooled by the working fluid cooler 15, and then returns to the torque converter 2 again.
- the wheel loader 100 includes a controller 19, an engine output mode switching switch 20, an accelerator pedal operation amount detection sensor 21, and a cooling water temperature sensor 23 to control the rotation of the fan motor 11 as described later.
- the controller 19 is a control device that controls each part of the wheel loader 100.
- the engine output mode changeover switch 20 is a changeover switch for the operator to select a P mode in which the output of the engine 1 is not limited and an E mode in which the fuel consumption is reduced by limiting the output of the engine 1 at light load. It is. That is, the controller 19 does not particularly limit the output of the engine 1 when the engine output mode switch 20 is switched to the P mode, but when the engine output mode switch 20 is switched to the E mode, the controller 19 controls the engine 1. Restrict the output of as described below.
- the accelerator pedal operation amount detection sensor 21 is a sensor that detects an operation amount of an accelerator pedal (not shown).
- the cooling water temperature sensor 23 is a sensor for detecting a temperature before cooling of the temperature of the cooling water, and is provided in a pipe line or the like on the upstream side of the radiator 14.
- FIGS. 3 and 4 are diagrams showing a curve of torque of the engine 1 and a curve of input torque to the torque converter 2.
- the intersection of the torque curve of the engine 1 and the input torque curve of the torque converter 2 is the input torque actually input to the torque converter 2 for traveling of the wheel loader 100.
- the input torque to the torque converter 2 increases in proportion to the square of the rotation speed Ni of the input shaft 21 of the torque converter 2 (that is, the rotation speed of the engine 1). Therefore, when the engine maximum speed limit and the output torque are limited (when E mode is set), the input torque to the torque converter 2 is reduced as compared with the case where it is not limited (when P mode is set). That is, in FIGS. 3 and 4, the intersection of the torque curve of the engine 1 and the input torque curve of the torque converter 2 moves downward to the left.
- the input power to the torque converter 2 (that is, the output of the engine 1) is represented by the product of the input torque to the torque converter 2 and the rotational speed Ni of the input shaft (that is, the rotational speed of the engine 1).
- the input power to the torque converter 2 is reduced and the power loss in the torque converter 2 is reduced as compared with the case where the engine maximum speed limit and the output torque are not limited.
- the output of the engine is smaller than when the P mode is set.
- FIG. 5 and 6 are diagrams showing the relationship between the target engine rotational speed and the depression amount of the accelerator pedal.
- the engine maximum speed limit is not limited, and the target engine speed is the lowest speed from low idle (Lo (min)) to the highest speed according to the amount of depression of the accelerator pedal. It changes to Hi (max) (FIG. 5).
- Lo the target engine rotational speed is the minimum number of revolutions
- Hi the maximum rotation speed
- the E mode when the E mode is set, the amount of heat generation from the engine 1 is small because the output of the engine 1 is smaller than when the mode is set to the P mode. Therefore, when the mode is set to the E mode, the amount of heat radiated from the radiator 14 can be reduced as compared with the case where the mode is set to the P mode. That is, if the cooling water temperature is the same, the rotational speed of the air cooling fan 13 can be reduced.
- the air-cooling fan 13 with respect to the cooling water temperature is set to lower the rotational speed of the air-cooling fan 13 in the following manner when the E-mode is set as compared with the case where the P-mode is set.
- the target rotational speed of the fan motor 11 is set.
- the controller 19 controls the relief pressure of the variable relief valve 9 to adjust the rotational speed of the fan motor 11 so as to be the target rotational speed of the fan motor 11 set based on the cooling water temperature.
- FIG. 7 is a diagram showing the relationship between the temperature of the cooling water and the target rotational speed of the fan motor 11.
- the target rotational speed of the fan motor 11 is set as follows according to the cooling water temperature.
- the relationship between the temperature of the cooling water at the time of setting the P mode and the target rotational speed of the fan motor 11 is the case where the target rotational speed of the fan motor 11 is not changed according to the output mode of the engine 1, that is, cooling in the prior art.
- the relationship between the temperature of water and the target rotational speed of the fan motor 11 is the same.
- the target rotational speed of the fan motor 11 is set to the minimum rotational speed Nmin until the cooling water temperature reaches 80 degrees. Nmin is, for example, 500 rpm.
- the target rotation speed of the fan motor 11 gradually increases from the minimum rotation speed Nmin to reach the maximum rotation speed Nmax (1) as the cooling water temperature increases from 80 degrees to 90 degrees.
- Set to Nmax (1) is, for example, 1600 rpm.
- C1 When the cooling water temperature exceeds 90 degrees, the target rotation speed of the fan motor 11 is set to the maximum rotation speed Nmax (1).
- the target rotational speed of the fan motor 11 is set as follows according to the cooling water temperature.
- A2 The target rotational speed of the fan motor 11 is set to the minimum rotational speed Nmin until the cooling water temperature reaches 80 degrees.
- B2 As the cooling water temperature rises, the target rotation speed of the fan motor 11 gradually increases from the minimum rotation speed Nmin to reach the maximum rotation speed Nmax (3) as the cooling water temperature increases from 80 degrees to 90 degrees.
- Set to Nmax (3) is, for example, 1400 rpm.
- Nmax (2) is, for example, 1500 rpm.
- D2 As the cooling water temperature rises, the target rotation speed of the fan motor 11 gradually increases from the maximum rotation speed Nmax (2) as the cooling water temperature rises from 95 degrees to 100 degrees, and the maximum rotation speed Nmax (1) It is set to be (E2) When the cooling water temperature exceeds 100 degrees, the target rotation speed of the fan motor 11 is set to the maximum rotation speed Nmax (1).
- the cooling water temperature of 80 degrees in the above a (2) is a temperature lower than the valve opening start temperature of the thermostat, and the temperature of the parts housed in the building cover 132 at the minimum rotation speed Nmin does not become a problem 80 degrees is merely an example, as it is determined as appropriate.
- the cooling water temperature of 100 degrees in the above (e2) is a temperature higher than the full opening temperature of the thermostat and is less than the boiling point of the cooling water, and the upper limit that overheating of the car body is acceptable at the maximum rotation speed Nmax 100 degrees is merely an example, as it is determined appropriately below the temperature.
- the target rotation speed of the fan motor 11 is lower than when the cooling water temperature is set in the P mode within the range of 80 degrees to 100 degrees (that is, control of the air cooling fan in the prior art). The speed is reduced.
- the target rotational speed of the fan motor 11 is not changed according to the output mode of the engine 1 as in the prior art, the heat generation amount Qe from the engine 1 and the heat radiation amount at the radiator 14 at point A shown in FIG.
- Qr was in equilibrium.
- the cooling water temperature is assumed to be 93 degrees.
- the target rotational speed of the fan motor 11 is set to Nmax (1).
- the cooling water temperature (93 degrees) is lower than the full open temperature (95 degrees) of the thermostat 22, the thermostat 22 is not fully open, and the flow path is narrowed by the thermostat 22.
- the calorific value Qe is the same as the calorific value from the previous engine 1, if it is set to the E mode, the calorific value from the engine 1 at point B shown in FIG.
- the amount Qe and the heat release amount Qr at the radiator 14 are in an equilibrium state.
- the reason for this is that since the target rotational speed of the fan motor 11 is lower than in the conventional case, the temperature of the cooling water slightly rises compared to that in the conventional case (point A), for example 95 degrees (point B). This is because the heat radiation characteristic of the radiator 14 is improved by the rise (93 degrees.fwdarw.95 degrees), and the heat generation amount Qe from the engine 1 and the heat radiation amount Qr at the radiator 14 are balanced at 95 degrees.
- the target rotational speed of the fan motor 11 is set to Nmax (2).
- the target rotational speed of the fan motor 11 is lower than in the conventional case, that is, the relief pressure of the variable relief valve 9 (load pressure of the hydraulic pump 8) is lowered, and power consumption of the hydraulic pump 8 is reduced. Fuel consumption is reduced. Furthermore, the noise of the air cooling fan 13 is also reduced. Even when the E mode is set, when the cooling water temperature is a temperature at which the thermostat 22 is fully opened and exceeds a predetermined temperature (100 degrees in the present embodiment), the target rotational speed of the fan motor 11 is increased. Since the rotation speed is set to the same rotation speed as the maximum rotation speed Nmax (1) when the P mode is set, overheating can be prevented.
- Second embodiment A second embodiment of a working machine according to the present invention will be described with reference to FIGS.
- the same components as in the first embodiment will be assigned the same reference numerals and differences will be mainly described.
- the points that are not particularly described are the same as in the first embodiment.
- the target rotational speed of the fan motor 11 set based on the cooling water temperature the target rotational speed of the fan motor 11 set based on the operating oil temperature, and the setting based on the operating fluid temperature
- the second embodiment differs from the first embodiment in that the rotational speed of the fan motor 11 is adjusted to be the highest target rotational speed among the target rotational speeds of the fan motor 11.
- FIG. 9 is a view showing a schematic configuration of the wheel loader 100 according to the second embodiment.
- the wheel loader 100 of the second embodiment further includes a hydraulic fluid temperature sensor 24 and a hydraulic fluid temperature sensor 25 in order to control the rotation of the fan motor 11.
- the hydraulic fluid temperature sensor 24 and the hydraulic fluid temperature sensor 25 are sensors that detect the temperature of the hydraulic fluid and the temperature of the hydraulic fluid before cooling, respectively, and are respectively upstream of the oil cooler 16 and the hydraulic fluid cooler 15. It is provided in the pipeline etc.
- FIG. 10 is a diagram showing the relationship between the hydraulic oil temperature and the target rotational speed of the fan motor 11.
- the target rotational speed of the fan motor 11 is set as follows according to the hydraulic fluid temperature.
- A3 The target rotational speed of the fan motor 11 is set to the minimum rotational speed Nmin until the hydraulic oil temperature reaches 70 degrees.
- B3 As the hydraulic oil temperature rises from 70 degrees to 90 degrees, the target rotational speed of the fan motor 11 gradually increases from the minimum rotational speed Nmin as the hydraulic oil temperature rises, and the maximum rotational speed Nmax (1) Is set to be
- the target rotational speed of the fan motor 11 is set to the maximum rotational speed Nmax (1).
- FIG. 11 is a diagram showing the relationship between the working fluid temperature and the target rotational speed of the fan motor 11.
- the target rotational speed of the fan motor 11 is set as follows according to the working fluid temperature.
- A4 The target rotational speed of the fan motor 11 is set to the minimum rotational speed Nmin until the working fluid temperature reaches 80 degrees.
- B4 As the working fluid temperature rises, the target rotation speed of the fan motor 11 gradually increases from the minimum rotation speed Nmin as the working fluid temperature increases from 80 degrees to 100 degrees, and the maximum rotation speed Nmax (1) Is set to be
- the target rotational speed of the fan motor 11 is set to the maximum rotational speed Nmax (1).
- the controller 19 controls the relief pressure of the variable relief valve 9 to thereby set the target rotational speed of the fan motor 11 set based on the coolant temperature, and the target rotational speed of the fan motor 11 set based on the hydraulic oil temperature.
- the rotational speed of the fan motor 11 is adjusted to be the highest target rotational speed among the target rotational speeds of the fan motor 11 set based on the working fluid temperature.
- Cooling water, hydraulic oil, and working fluid can be cooled.
- the air-cooling fan 13 is configured to be driven by the hydraulically driven fan motor 11, but the present invention is not limited to this.
- the air cooling fan 13 may be configured to be driven by an electric motor.
- the relationship between the hydraulic fluid temperature and the target rotational speed of the fan motor 11 and the relationship between the operating fluid temperature and the target rotational speed of the fan motor 11 are determined regardless of the output mode of the engine 1
- the present invention is not limited thereto.
- the rotational speed of the air cooling fan 13 may be reduced as compared with the case of FIG.
- the present invention is not limited to the embodiment described above, and the temperature of the cooling water on the engine, the radiator for cooling the engine cooling water, and the path for passing the cooling water to the radiator
- the thermostat which opens and closes the path between fully closed and fully open, a fan device for blowing the outside air to the radiator, an output changeover switch for switching the output of the engine, and the rotation of the fan device according to the temperature of the cooling water
- a rotational speed setting means for setting the speed
- a rotational speed adjustment means for adjusting the rotational speed of the fan device so as to achieve the rotational speed set by the rotational speed setting means.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mining & Mineral Resources (AREA)
- Civil Engineering (AREA)
- Structural Engineering (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Cooling, Air Intake And Gas Exhaust, And Fuel Tank Arrangements In Propulsion Units (AREA)
- Component Parts Of Construction Machinery (AREA)
Abstract
Description
本発明の第3の態様によると、第1または第2の態様の作業機械において、油圧ポンプで供給される作動油を冷却するための作動油クーラと、作動油の温度に応じてファン装置の回転速度を設定する作動油温依存回転速度設定部とをさらに備え、ファン装置は、ラジエータおよび作動油クーラに外気を送風し、回転速度調節部は、回転速度設定部で設定された回転速度、および、作動油温依存回転速度設定部で設定された回転速度のうち、高い方の回転速度となるようにファン装置の回転速度を調節するのが好ましい。
本発明の第4の態様によると、第1または第2の態様の作業機械において、走行駆動力を伝達するトルクコンバータの作動流体を冷却するための作動流体クーラと、作動流体の温度に応じてファン装置の回転速度を設定する作動流体温度依存回転速度設定部とをさらに備え、ファン装置は、ラジエータおよび作動流体クーラに外気を送風し、回転速度調節部は、回転速度設定部で設定された回転速度、および、作動流体温度依存回転速度設定部で設定された回転速度のうち、高い方の回転速度となるようにファン装置の回転速度を調節するのが好ましい。
本発明の第5の態様によると、第1または第2の態様の作業機械において、油圧ポンプで供給される作動油を冷却するための作動油クーラと、作動油の温度に応じてファン装置の回転速度を設定する作動油温依存回転速度設定部と、走行駆動力を伝達するトルクコンバータの作動流体を冷却するための作動流体クーラと、作動流体の温度に応じてファン装置の回転速度を設定する作動流体温度依存回転速度設定部とをさらに備え、ファン装置は、ラジエータ、作動油クーラ、および作動流体クーラに外気を送風し、回転速度調節部は、回転速度設定部で設定された回転速度、作動油温依存回転速度設定部で設定された回転速度、および、作動流体温度依存回転速度設定部で設定された回転速度のうち、最も高い回転速度となるようにファン装置の回転速度を調節するのが好ましい。
本発明の第6の態様によると、第1乃至第5のいずれか一の態様の作業機械において、回転速度設定部は、冷却水の温度が、サーモスタットが全開する温度より高い所定の温度以上である場合には、エンジンの出力が低くなるように出力切り替えスイッチが切り換えられている場合であっても、エンジンの出力が高くなるように出力切り替えスイッチが切り換えられている場合と同じ回転速度に設定するのが好ましい。
図1~8を参照して、本発明による作業機械の第1の実施の形態を説明する。図1は、本実施の形態に係る作業機械の一例であるホイールローダの側面図である。ホイールローダ100は、アーム111,バケット112,タイヤ113等を有する前部車体110と、運転室121,エンジン室122,タイヤ123等を有する後部車体120とで構成される。エンジン室122は、建屋カバー131で覆われている。後部車体120の後方にはカウンタウェイト124が取り付けられている。
(動力損失)=(トルコン2への入力動力)×(1-η) (1)
ηは、トルコン2における動力の伝達効率である。
(a1) 冷却水温が80度に達するまでは、ファンモータ11の目標回転速度は、最低回転速度Nminに設定される。Nminは、たとえば500rpmとされる。
(b1) 冷却水温が80度から90度までは、冷却水温が上昇するにつれて、ファンモータ11の目標回転速度は、最低回転速度Nminから徐々に増加して最高回転速度Nmax(1)となるように設定される。Nmax(1)は、たとえば1600rpmとされる。
(c1) 冷却水温が90度を超えると、ファンモータ11の目標回転速度は、最高回転速度Nmax(1)に設定される。
(a2) 冷却水温が80度に達するまでは、ファンモータ11の目標回転速度は、最低回転速度Nminに設定される。
(b2) 冷却水温が80度から90度までは、冷却水温が上昇するにつれて、ファンモータ11の目標回転速度は、最低回転速度Nminから徐々に増加して最高回転速度Nmax(3)となるように設定される。Nmax(3)は、たとえば1400rpmとされる。
(c2) 冷却水温が90度から95度までは、冷却水温が上昇するにつれて、ファンモータ11の目標回転速度は、最高回転速度Nmax(3)から徐々に増加して最高回転速度Nmax(2)となるように設定される。Nmax(2)は、たとえば1500rpmとされる。
(d2) 冷却水温が95度から100度までは、冷却水温が上昇するにつれて、ファンモータ11の目標回転速度は、最高回転速度Nmax(2)から徐々に増加して最高回転速度Nmax(1)となるように設定される。
(e2) 冷却水温が100度を超えると、ファンモータ11の目標回転速度は、最高回転速度Nmax(1)に設定される。
なお、上記a(2)での冷却水温80度は、サーモスタットの開弁開始温度より低い温度であって、最低回転速度Nminでの建屋カバー132内に収納される部品の温度が問題とならないように適宜決定されるので、80度は単なる例示である。また上記(e2)での冷却水温100度は、サーモスタットの全開温度より高い温度であって、冷却水の沸騰点未満であり、かつ最高回転速度Nmax(1)で車体としてのオーバーヒートが許容できる上限温度以下に適宜決定されるので、100度は単なる例示である。
ので、オーバーヒートを防止できる。
図9~11を参照して、本発明による作業機械の第2の実施の形態を説明する。以下の説明では、第1の実施の形態と同じ構成要素には同じ符号を付して相違点を主に説明する。特に説明しない点については、第1の実施の形態と同じである。本実施の形態では、主に、冷却水温に基づいて設定されるファンモータ11の目標回転速度、作動油温に基づいて設定されるファンモータ11の目標回転速度、および作動流体温度に基づいて設定されるファンモータ11の目標回転速度のうち、最も高い目標回転速度となるようにファンモータ11の回転速度が調節される点で、第1の実施の形態と異なる。
(a3) 作動油温が70度に達するまでは、ファンモータ11の目標回転速度は、最低回転速度Nminに設定される。
(b3) 作動油温が70度から90度までは、作動油温が上昇するにつれて、ファンモータ11の目標回転速度は、最低回転速度Nminから徐々に増加して最高回転速度Nmax(1)となるように設定される。
(c3) 作動油温が90度を超えると、ファンモータ11の目標回転速度は、最高回転速度Nmax(1)に設定される。
(a4) 作動流体温度が80度に達するまでは、ファンモータ11の目標回転速度は、最低回転速度Nminに設定される。
(b4) 作動流体温度が80度から100度までは、作動流体温度が上昇するにつれて、ファンモータ11の目標回転速度は、最低回転速度Nminから徐々に増加して最高回転速度Nmax(1)となるように設定される。
(c4) 作動流体温度が100度を超えると、ファンモータ11の目標回転速度は、最高回転速度Nmax(1)に設定される。
(1) 上述の説明で上げた数値は例示であり、本発明は上述した数値に限定されるものではない。
(2) 上述の説明では、空冷ファン13が油圧駆動のファンモータ11で駆動されるように構成されているが、本発明はこれに限定されない。たとえば、空冷ファン13を電動モータで駆動するように構成してもよい。
日本国特許出願2010年第139087号(2010年6月18日出願)
Claims (6)
- エンジンと、
前記エンジンの冷却水を冷却するためのラジエータと、
前記冷却水を前記ラジエータに通水する経路上で、前記冷却水の温度に応じて前記経路を全閉から全開の間で開閉するサーモスタットと、
前記ラジエータに外気を送風するファン装置と、
エンジンの出力の高低を切り替える出力切り替えスイッチと、
前記冷却水の温度に応じて前記ファン装置の回転速度を設定する回転速度設定部と、
前記回転速度設定部で設定された回転速度となるように前記ファン装置の回転速度を調節する回転速度調節部とを備え、
前記回転速度設定部は、前記サーモスタットが全閉から全開する前記冷却水の温度範囲内で、前記エンジンの出力が低くなるように前記出力切り替えスイッチが切り換えられている場合には、前記エンジンの出力が高くなるように前記出力切り替えスイッチが切り換えられている場合に比べて前記ファン装置の回転速度が低くなるように設定する作業機械。 - 請求項1に記載の作業機械において、
前記回転速度設定部は、前記サーモスタットが開弁開始する温度より低い所定の温度と、前記サーモスタットが全開する温度より高い所定の温度との間の温度においても、前記エンジンの出力が低くなるように前記出力切り替えスイッチが切り換えられている場合には、前記エンジンの出力が高くなるように前記出力切り替えスイッチが切り換えられている場合に比べて前記ファン装置の回転速度が低くなるように設定する作業機械。 - 請求項1または2に記載の作業機械において、
油圧ポンプで供給される作動油を冷却するための作動油クーラと、
前記作動油の温度に応じて前記ファン装置の回転速度を設定する作動油温依存回転速度設定部とをさらに備え、
前記ファン装置は、前記ラジエータおよび前記作動油クーラに外気を送風し、
前記回転速度調節部は、前記回転速度設定部で設定された回転速度、および、前記作動油温依存回転速度設定部で設定された回転速度のうち、高い方の回転速度となるように前記ファン装置の回転速度を調節する作業機械。 - 請求項1または2に記載の作業機械において、
走行駆動力を伝達するトルクコンバータの作動流体を冷却するための作動流体クーラと、
前記作動流体の温度に応じて前記ファン装置の回転速度を設定する作動流体温度依存回転速度設定部とをさらに備え、
前記ファン装置は、前記ラジエータおよび前記作動流体クーラに外気を送風し、
前記回転速度調節部は、前記回転速度設定部で設定された回転速度、および、前記作動流体温度依存回転速度設定部で設定された回転速度のうち、高い方の回転速度となるように前記ファン装置の回転速度を調節する作業機械。 - 請求項1または2に記載の作業機械において、
油圧ポンプで供給される作動油を冷却するための作動油クーラと、
前記作動油の温度に応じて前記ファン装置の回転速度を設定する作動油温依存回転速度設定部と、
走行駆動力を伝達するトルクコンバータの作動流体を冷却するための作動流体クーラと、
前記作動流体の温度に応じて前記ファン装置の回転速度を設定する作動流体温度依存回転速度設定部とをさらに備え、
前記ファン装置は、前記ラジエータ、前記作動油クーラ、および前記作動流体クーラに外気を送風し、
前記回転速度調節部は、前記回転速度設定部で設定された回転速度、前記作動油温依存回転速度設定部で設定された回転速度、および、前記作動流体温度依存回転速度設定部で設定された回転速度のうち、最も高い回転速度となるように前記ファン装置の回転速度を調節する作業機械。 - 請求項1乃至5のいずれか一項に記載の作業機械において、
前記回転速度設定部は、前記冷却水の温度が、前記サーモスタットが全開する温度より高い所定の温度以上である場合には、前記エンジンの出力が低くなるように前記出力切り替えスイッチが切り換えられている場合であっても、前記エンジンの出力が高くなるように前記出力切り替えスイッチが切り換えられている場合と同じ回転速度に設定する作業機械。
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
KR1020127032961A KR101778642B1 (ko) | 2010-06-18 | 2011-06-09 | 작업 기계 |
CN201180030231.1A CN102947570B (zh) | 2010-06-18 | 2011-06-09 | 作业机械 |
US13/704,937 US9322603B2 (en) | 2010-06-18 | 2011-06-09 | Work machine |
EP11795640.9A EP2584164B1 (en) | 2010-06-18 | 2011-06-09 | Work machine |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2010-139087 | 2010-06-18 | ||
JP2010139087A JP5518589B2 (ja) | 2010-06-18 | 2010-06-18 | 作業機械 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2011158733A1 true WO2011158733A1 (ja) | 2011-12-22 |
Family
ID=45348134
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2011/063277 WO2011158733A1 (ja) | 2010-06-18 | 2011-06-09 | 作業機械 |
Country Status (6)
Country | Link |
---|---|
US (1) | US9322603B2 (ja) |
EP (1) | EP2584164B1 (ja) |
JP (1) | JP5518589B2 (ja) |
KR (1) | KR101778642B1 (ja) |
CN (1) | CN102947570B (ja) |
WO (1) | WO2011158733A1 (ja) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN102644503A (zh) * | 2012-04-09 | 2012-08-22 | 华南理工大学 | 一种汽车发动机冷却风扇电子控制***与方法 |
CN103016465A (zh) * | 2012-12-24 | 2013-04-03 | 湖南涉外经济学院 | 电控液压加载回路 |
Families Citing this family (16)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP5124504B2 (ja) * | 2009-02-09 | 2013-01-23 | 日立建機株式会社 | 作業車両の原動機制御装置 |
JP2013209940A (ja) * | 2012-03-30 | 2013-10-10 | Hitachi Constr Mach Co Ltd | 作業機械 |
US8973536B2 (en) * | 2013-01-25 | 2015-03-10 | Caterpillar Inc. | Engine compensation for fan power |
JP6080630B2 (ja) * | 2013-03-19 | 2017-02-15 | 株式会社タダノ | 作業車両 |
EP2988033B1 (en) * | 2013-08-08 | 2017-01-11 | Komatsu Ltd. | Wheel loader |
JP6163082B2 (ja) | 2013-11-08 | 2017-07-12 | 株式会社Kcm | ホイールローダ |
JP6009480B2 (ja) * | 2014-03-06 | 2016-10-19 | 日立建機株式会社 | 建設機械の冷却ファン制御装置 |
US9488088B2 (en) | 2014-05-16 | 2016-11-08 | Komatsu Ltd. | Work vehicle and method of controlling work vehicle |
JP6511879B2 (ja) * | 2015-03-12 | 2019-05-15 | コベルコ建機株式会社 | 建設機械 |
CN106321218B (zh) * | 2015-06-15 | 2019-04-16 | 徐工集团工程机械股份有限公司 | 散热控制***、方法以及挖掘机 |
CN109854354A (zh) * | 2017-11-30 | 2019-06-07 | 中国人民解放军陆军军事交通学院 | 柴油机变海拔变流量冷却***及其控制过程 |
US10393261B2 (en) * | 2017-12-06 | 2019-08-27 | Cnh Industrial America Llc | High ambient temperature propulsion speed control of a self-propelled agricultural product applicator |
JP2019173731A (ja) * | 2018-03-29 | 2019-10-10 | 株式会社Kcm | 作業車両 |
JP7253420B2 (ja) * | 2019-03-25 | 2023-04-06 | 日立建機株式会社 | 作業車両 |
US11781572B2 (en) | 2020-08-15 | 2023-10-10 | Kubota Corporation | Working machine |
JP7434102B2 (ja) * | 2020-08-15 | 2024-02-20 | 株式会社クボタ | 作業機 |
Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH11294164A (ja) * | 1998-04-16 | 1999-10-26 | Nissan Motor Co Ltd | 冷却ファンの制御装置 |
JP2005069203A (ja) * | 2003-08-28 | 2005-03-17 | Tcm Corp | 産業用車両の冷却装置 |
JP2005273473A (ja) * | 2004-03-23 | 2005-10-06 | Honda Motor Co Ltd | ラジエータファン制御装置 |
JP2007170236A (ja) * | 2005-12-20 | 2007-07-05 | Denso Corp | エンジン冷却装置 |
JP2009144539A (ja) * | 2007-12-12 | 2009-07-02 | Denso Corp | 冷却ファン制御装置 |
Family Cites Families (16)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH0949427A (ja) | 1995-08-09 | 1997-02-18 | Shin Caterpillar Mitsubishi Ltd | 建設機械の冷却制御装置 |
DE19535674A1 (de) * | 1995-09-26 | 1997-03-27 | Orenstein & Koppel Ag | Verfahren zur Regelung der Kühleinrichtung eines dieselmotorischen Baggerantriebes sowie Kühleinrichtung für dieselmotorische Baggerantriebe |
JP4204137B2 (ja) * | 1999-04-22 | 2009-01-07 | 株式会社小松製作所 | 冷却用ファンの駆動制御装置 |
JP4285866B2 (ja) | 1999-12-22 | 2009-06-24 | 株式会社小松製作所 | 油圧駆動冷却ファン |
CN1791742B (zh) * | 2003-10-31 | 2010-11-10 | 株式会社小松制作所 | 发动机输出控制装置 |
JP4753278B2 (ja) * | 2004-10-12 | 2011-08-24 | 臼井国際産業株式会社 | 外部制御式ファンクラッチの制御方法 |
US7373239B2 (en) * | 2005-07-06 | 2008-05-13 | Komatsu, Ltd. | Engine control device of work vehicle |
JP4785522B2 (ja) * | 2005-12-22 | 2011-10-05 | 株式会社小松製作所 | 作業車両のエンジン制御装置 |
CN101541601B (zh) * | 2006-11-30 | 2012-06-06 | 株式会社小松制作所 | 车辆的冷却用风扇的控制装置 |
US7962768B2 (en) * | 2007-02-28 | 2011-06-14 | Caterpillar Inc. | Machine system having task-adjusted economy modes |
US8374755B2 (en) * | 2007-07-31 | 2013-02-12 | Caterpillar Inc. | Machine with task-dependent control |
US8015953B2 (en) * | 2008-03-25 | 2011-09-13 | Denso International America, Inc. | Electric cooling fan control based on known vehicle load conditions |
EP2412948B1 (en) * | 2009-03-24 | 2018-08-22 | Komatsu, Ltd. | Cooling fan driving device and fan rotation number control method |
JP5039803B2 (ja) * | 2010-03-04 | 2012-10-03 | 日本サーモスタット株式会社 | 内燃機関の冷却装置 |
JP5957949B2 (ja) * | 2012-02-24 | 2016-07-27 | スズキ株式会社 | 燃焼状態制御装置 |
JP2014101876A (ja) * | 2012-11-20 | 2014-06-05 | Hyundai Motor Company Co Ltd | サーモスタットを備えたエンジンシステム |
-
2010
- 2010-06-18 JP JP2010139087A patent/JP5518589B2/ja active Active
-
2011
- 2011-06-09 EP EP11795640.9A patent/EP2584164B1/en active Active
- 2011-06-09 US US13/704,937 patent/US9322603B2/en active Active
- 2011-06-09 WO PCT/JP2011/063277 patent/WO2011158733A1/ja active Application Filing
- 2011-06-09 CN CN201180030231.1A patent/CN102947570B/zh active Active
- 2011-06-09 KR KR1020127032961A patent/KR101778642B1/ko active IP Right Grant
Patent Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH11294164A (ja) * | 1998-04-16 | 1999-10-26 | Nissan Motor Co Ltd | 冷却ファンの制御装置 |
JP2005069203A (ja) * | 2003-08-28 | 2005-03-17 | Tcm Corp | 産業用車両の冷却装置 |
JP2005273473A (ja) * | 2004-03-23 | 2005-10-06 | Honda Motor Co Ltd | ラジエータファン制御装置 |
JP2007170236A (ja) * | 2005-12-20 | 2007-07-05 | Denso Corp | エンジン冷却装置 |
JP2009144539A (ja) * | 2007-12-12 | 2009-07-02 | Denso Corp | 冷却ファン制御装置 |
Non-Patent Citations (1)
Title |
---|
See also references of EP2584164A4 * |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN102644503A (zh) * | 2012-04-09 | 2012-08-22 | 华南理工大学 | 一种汽车发动机冷却风扇电子控制***与方法 |
CN103016465A (zh) * | 2012-12-24 | 2013-04-03 | 湖南涉外经济学院 | 电控液压加载回路 |
Also Published As
Publication number | Publication date |
---|---|
KR20130120376A (ko) | 2013-11-04 |
EP2584164A4 (en) | 2014-03-05 |
CN102947570A (zh) | 2013-02-27 |
EP2584164B1 (en) | 2015-09-09 |
EP2584164A1 (en) | 2013-04-24 |
US9322603B2 (en) | 2016-04-26 |
CN102947570B (zh) | 2016-01-06 |
JP2012002161A (ja) | 2012-01-05 |
JP5518589B2 (ja) | 2014-06-11 |
KR101778642B1 (ko) | 2017-09-14 |
US20130092366A1 (en) | 2013-04-18 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
WO2011158733A1 (ja) | 作業機械 | |
JP4664246B2 (ja) | 作業車両のエンジン制御装置 | |
JP4573751B2 (ja) | 走行式作業機械の冷却ファン駆動装置 | |
US7373239B2 (en) | Engine control device of work vehicle | |
US20120004814A1 (en) | Engine Control Device for Work Vehicle | |
JP5074571B2 (ja) | 作業車両および作業車両の制御方法 | |
US11274745B2 (en) | Wheel loader | |
JP6402124B2 (ja) | 建設機械の冷却装置 | |
WO2019188415A1 (ja) | 作業車両 | |
JP2006521513A (ja) | 自動車を駆動するための動力伝達系 | |
JP4922795B2 (ja) | 作業車両の走行制御装置 | |
WO2013146392A1 (ja) | 作業機械 | |
JP6572160B2 (ja) | 作業車両 | |
JP6474750B2 (ja) | 小型油圧ショベル | |
JP2010185307A (ja) | 油圧駆動冷却ファンの制御装置 | |
JP2011184911A (ja) | 冷却ファンの駆動回路 |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
WWE | Wipo information: entry into national phase |
Ref document number: 201180030231.1 Country of ref document: CN |
|
121 | Ep: the epo has been informed by wipo that ep was designated in this application |
Ref document number: 11795640 Country of ref document: EP Kind code of ref document: A1 |
|
ENP | Entry into the national phase |
Ref document number: 20127032961 Country of ref document: KR Kind code of ref document: A |
|
WWE | Wipo information: entry into national phase |
Ref document number: 13704937 Country of ref document: US |
|
NENP | Non-entry into the national phase |
Ref country code: DE |
|
WWE | Wipo information: entry into national phase |
Ref document number: 11259/DELNP/2012 Country of ref document: IN |
|
WWE | Wipo information: entry into national phase |
Ref document number: 2011795640 Country of ref document: EP |