WO2006112091A1 - 建設機械の冷却装置 - Google Patents
建設機械の冷却装置 Download PDFInfo
- Publication number
- WO2006112091A1 WO2006112091A1 PCT/JP2005/023608 JP2005023608W WO2006112091A1 WO 2006112091 A1 WO2006112091 A1 WO 2006112091A1 JP 2005023608 W JP2005023608 W JP 2005023608W WO 2006112091 A1 WO2006112091 A1 WO 2006112091A1
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- WIPO (PCT)
- Prior art keywords
- cooling
- fan
- hydraulic
- temperature
- cooling fan
- Prior art date
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Classifications
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- 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
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- 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
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- 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
- F01P2025/13—Ambient temperature
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- 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
- F01P2025/40—Oil temperature
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- 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
- F01P2060/00—Cooling circuits using auxiliaries
- F01P2060/04—Lubricant cooler
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- 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
- F01P5/00—Pumping cooling-air or liquid coolants
- F01P5/02—Pumping cooling-air; Arrangements of cooling-air pumps, e.g. fans or blowers
- F01P5/04—Pump-driving arrangements
Definitions
- the present invention relates to a construction machine such as a hydraulic excavator, and more particularly to an intercooler.
- the present invention relates to a cooling device for a construction machine including a cooling fan that generates cooling air to a heat exchanger such as a radiator and an oil cooler.
- Construction machines such as hydraulic excavators, operate front working machines such as booms, arms, and buckets and upper revolving bodies by hydraulic actuators such as hydraulic cylinders and hydraulic motors. These hydraulic actuators are operated by discharge pressure oil from a hydraulic pump driven by an engine.
- the upper swing body is covered with a cover, and the engine and the hydraulic pump are arranged in an engine room provided in the cover.
- a cooling fan provided in the engine compartment is driven to introduce outside air from an intake hole provided in the cover to generate cooling air.
- a so-called axial fan (propeller fan) that is rotated by a driving force from the crankshaft of the engine is often used as the cooling fan.
- the cooling air generated by the cooling fan is introduced into the engine room, then passes through various heat exchangers, is cooled, and is discharged from the exhaust hole provided in the cover to the outside of the engine room.
- the heat exchanger includes, for example, an intercooler that cools compressed air pressurized by a turbocharger mounted on the engine, a radiator that cools engine cooling water, and an oil cooler that cools hydraulic fluid of the hydraulic drive unit. Etc.
- the rotational speed of the cooling fan is proportional to the engine rotational speed. Therefore, the cooling water in the radiator and the hydraulic oil in the oil cooler are overcooled, and it takes a long time due to warm-up operation.
- a cooling fan that is driven independently of engine rotational force
- a cooling fan that forcibly cools a radiator and an oil cooler
- a hydraulic motor for the fan that drives the cooling fan
- a hydraulic motor for the fan that drives the cooling fan
- the variable capacity fan hydraulic pump that can control the rotation speed of the engine, the cooling water temperature sensor that detects the temperature of the cooling water, and the temperature of the hydraulic oil Hydraulic oil temperature sensor, engine rotation speed sensor for detecting the engine speed, and detection signals from these sensors are input, and the hydraulic pump for fans according to the coolant temperature, hydraulic oil temperature, and engine speed
- a configuration is proposed that includes a controller that calculates and outputs a discharge capacity command value and continuously controls the rotation speed of the cooling fan by a variable capacity fan hydraulic pump (e.g., a patent document). 1).
- Patent Document 1 JP 2001-182535 A
- a hydraulically driven cooling fan that forcibly cools the radiator and the oil cooler is provided, and the rotation speed of the cooling fan is controlled according to the cooling water temperature, the hydraulic oil temperature, and the engine rotation speed. It is like that.
- the force s and intercooler are not clearly described.
- a case is assumed in which cooling air generated by a hydraulically driven cooling fan is arranged to cool not only the radiator and oil cooler but also the intercooler.
- the rotation speed of the cooling fan is low even if the outside air temperature is high, and the amount of cooling air necessary for the intercooler is secured. It may not be. Therefore, there was room for improvement.
- the present invention has been made in view of the above-mentioned matters, and an object of the present invention is to reduce the noise of the cooling fan and to ensure the necessary amount of cooling air. It is to provide a cooling device.
- the present invention provides an intercooler for cooling compressed air pressurized by a turbocharger mounted on an engine, and cooling the engine cooling water.
- Radiator an oil cooler that cools the hydraulic oil of the hydraulic drive device, a cooling fan that generates cooling air to the intercooler, the radiator, and the oil cooler, and a fan hydraulic motor that drives the cooling fan
- a fan hydraulic pump that discharges pressure oil to the fan hydraulic motor
- an air temperature detection means that detects an air temperature at the outlet of the intercooler
- a cooling water temperature detection that detects the cooling water temperature of the radiator
- a control means for outputting a control signal corresponding to the maximum value among the calculated values of the cooling fan rotation speed corresponding to each.
- a cooling fan that generates cooling air to the intercooler, the radiator, and the oil cooler, a fan hydraulic motor that drives the cooling fan, and pressure oil to the fan hydraulic motor are supplied.
- a variable displacement fan hydraulic pump for discharging is provided.
- the control means calculates the number of rotations of the cooling fan corresponding to the intercooler according to the air temperature at the outlet of the intercooler detected by the air temperature detection means, and according to the cooling water temperature of the radiator detected by the cooling water temperature detection means.
- the cooling fan speed corresponding to the radiator is calculated, and the cooling fan speed corresponding to the oil cooler is calculated according to the hydraulic oil temperature detected by the hydraulic oil temperature detecting means.
- control means selects the maximum value among the calculated values of the cooling fan rotation speed and outputs a corresponding control signal, for example, controls the discharge capacity of the fan hydraulic pump.
- the fan hydraulic motor is driven, and the number of rotations of the cooling fan is controlled to change continuously, for example.
- the rotational speed of the cooling fan is controlled according to the air temperature at the outlet of the intercooler, the cooling water temperature of the radiator, and the operating oil temperature of the oil cooler. It is possible to ensure the necessary cooling air volume for the radiator and oil cooler. Further, for example, an unnecessary increase in the number of rotations of the cooling fan can be prevented as compared with a case where an engine direct acting type cooling fan is provided, and thereby noise of the cooling fan can be reduced.
- the present invention also provides an intercooler for cooling compressed air pressurized by a turbocharger mounted on an engine, and cooling water for the engine.
- a radiator for cooling, an oil cooler for cooling the hydraulic oil of the hydraulic drive device, a condenser for cooling the refrigerant of the air conditioner for the cab, and cooling air to the intercooler, the radiator, the oil cooler, and the condenser are generated.
- Cooling fan fan hydraulic motor for driving the cooling fan, fan hydraulic pump for discharging pressure oil to the fan hydraulic motor, and air temperature detecting means for detecting the air temperature at the outlet of the intercooler Cooling water temperature detecting means for detecting the cooling water temperature of the radiator, operating oil temperature detecting means for detecting the operating oil temperature of the oil cooler, outside air temperature detecting means for detecting the outside air temperature, and the air conditioner
- the air temperature detecting means, the cooling water temperature detecting means, the hydraulic oil temperature detecting means, and the outside air temperature detecting means When the air conditioner is stopped, the control signal corresponding to the maximum value of the calculated values of the rotation speed of the cooling fan corresponding to each of the detected values is output.
- the detection values of the temperature detection means, cooling water temperature detection means, and hydraulic oil temperature detection means are input, and the control signal corresponding to the maximum value among the calculated values of the cooling fan speed corresponding to each of the detection values is input. Control means for outputting.
- a condenser for cooling the refrigerant of the air conditioner device for the cab is provided. Similar to the intercooler, radiator, and oil cooler, this condenser is cooled by cooling air generated by a cooling fan driven by a fan hydraulic motor.
- the control means is the same as (1) above, according to the detected values of the air temperature detecting means, the cooling water temperature detecting means, and the hydraulic oil temperature detecting means. , And the number of cooling fan rotations corresponding to the oil cooler. Then, the maximum value among the calculated values of the cooling fan rotational speed is selected and a corresponding control signal is output, and for example, the discharge capacity of the fan hydraulic pump is controlled.
- the air conditioner when the air conditioner is operating, it calculates the cooling fan rotation speed corresponding to each of the intercooler, the radiator, and the oil cooler, and corresponds to the capacitor according to the outside air temperature detected by the outside air temperature detecting means. Calculate the cooling fan speed. Then, the maximum value among the calculated values of the cooling fan rotational speed is selected and a corresponding control signal is output, and for example, the discharge capacity of the fan hydraulic pump is controlled. As a result, the fan hydraulic motor is driven, and the rotation speed of the cooling fan is controlled so as to change continuously, for example. It is.
- the air conditioner when the air conditioner is stopped, the amount of cooling air necessary for the intercooler, the radiator, and the oil cooler can be ensured as in (1).
- the air conditioner when the air conditioner is driven, it is possible to ensure the amount of cooling air necessary for the intercooler, radiator, oil cooler, and condenser.
- an unnecessary increase in the number of rotations of the cooling fan can be prevented compared to the case where, for example, an engine direct acting type cooling fan is provided, and this can reduce the noise of the cooling fan. it can
- the present invention also provides an intercooler that cools compressed air pressurized by a turbocharger mounted on an engine, and a radiator that cools cooling water of the engine
- An oil cooler for cooling the hydraulic oil of the hydraulic drive device, a condenser for cooling the refrigerant of the air conditioner for the cab, a cooling fan for generating cooling air to the intercooler, the radiator, the oil cooler, and the condenser.
- a fan hydraulic motor for driving the cooling fan, a fan hydraulic pump for discharging pressure oil to the fan hydraulic motor, an air temperature detecting means for detecting an air temperature at the outlet of the intercooler, Cooling water temperature detecting means for detecting the cooling water temperature of the radiator, hydraulic oil temperature detecting means for detecting the hydraulic oil temperature of the oil cooler, Outside air temperature detecting means for detecting the degree, engine speed detecting means for detecting the engine speed, and when the air conditioner is driven, the air temperature detecting means, the cooling water temperature detecting means, Of the calculated value of the cooling fan speed corresponding to each of the detected values of the oil temperature detecting means and the outside air temperature detecting means, and the lower limit value of the cooling fan speed corresponding to the detected value of the engine speed detecting means.
- Control means for outputting a control signal corresponding to the maximum value among the calculated values of the fan rotational speed.
- the discharge capacity of the fan hydraulic pump varies, and the cooling fan speed varies. That is, when the engine speed decreases, the cooling capacity of the intercooler, the radiator, the oil cooler, and the condenser decreases. Force, for example, low eye There is a demand to suppress a decrease in the cooling capacity of the condenser in an air-conditioning apparatus that may increase the load even when the engine speed is low, such as during dollar operation. Therefore, in the present invention, when the air conditioner is driven, the control means is an intercooler according to the detection values of the air temperature detection means, the cooling water temperature detection means, the hydraulic oil temperature detection means, and the outside air temperature detection means.
- the cooling fan rotation speed corresponding to each of the radiator, oil cooler, and condenser is calculated, and the lower limit value of the cooling fan rotation speed is determined according to the engine rotation speed detected by the engine rotation speed detection means (for example, according to the decrease in the engine rotation speed). To calculate the lower limit). Then, the maximum value of the calculated value and the lower limit value of the cooling fan rotation speed is selected and a corresponding control signal is output, for example, to control the discharge capacity of the fan hydraulic pump. Therefore, in the present invention, in addition to the effect described in the above (2), the cooling capacity of the condenser or the like is reduced due to the reduction of the engine speed by preventing the cooling fan speed from falling below the lower limit value. Can be suppressed.
- control means variably controls a discharge capacity of the fan hydraulic pump to thereby rotate the cooling fan. To control.
- control means variably controls a capacity of the fan hydraulic motor to control the cooling fan (25). Control the number of revolutions.
- control means controls the cooling fan rotation speed so as to continuously change.
- control means controls the cooling fan rotational speed so as to change stepwise.
- the noise of the cooling fan can be reduced, and the necessary amount of cooling air can be reliably ensured.
- FIG. 1 is a side view showing the overall structure of a hydraulic excavator as an example of a construction machine to which the present invention is applied.
- Fig. 2 is a hydraulic circuit diagram showing the first embodiment of the cooling device for the construction machine according to the present invention together with the hydraulic drive device.
- FIG. 4 is a characteristic diagram showing the number of rotations of the cooling fan with respect to the air temperature at the exit of the intercooler, showing a calculation table stored in the controller constituting the first embodiment of the cooling device for the construction machine according to the present invention. It is.
- FIG. 5 shows a calculation table stored in the controller constituting the first embodiment of the cooling device for the construction machine according to the present invention, and is a characteristic diagram showing the cooling fan rotation speed with respect to the cooling water temperature at the radiator inlet. It is.
- Fig. 6 is a characteristic diagram showing the number of rotations of the cooling fan with respect to the operating oil temperature at the oil cooler outlet, showing a calculation table stored in the controller constituting the first embodiment of the cooling device for construction equipment of the present invention. It is.
- FIG. 7 A hydraulic circuit diagram showing a second embodiment of the construction machine cooling device of the present invention together with a hydraulic drive device.
- FIG. 9 A calculation table stored in the controller constituting the second embodiment of the cooling device for a construction machine according to the present invention, and a characteristic diagram showing the number of rotations of the cooling fan with respect to the outside air temperature.
- FIG. 10 is a hydraulic circuit diagram showing a third embodiment of a cooling device for a construction machine according to the present invention together with a hydraulic drive device.
- a calculation table stored in the controller constituting the third embodiment of the cooling device for the construction machine according to the present invention is a characteristic diagram showing the lower limit value of the cooling fan rotation speed with respect to the engine rotation speed. is there.
- Air temperature sensor Air temperature detection means
- Cooling water temperature sensor (cooling water temperature detection means)
- Hydraulic oil temperature sensor (hydraulic oil temperature detection means)
- FIG. 1 is a side view showing the overall structure of a large excavator to which the present invention is applied.
- the operator's front side left side in Fig. 1
- rear side right side in Fig. 1
- left side paper surface in Fig. 1
- the right side (front side) and the right side are simply referred to as the front side, rear side, left side, and right side.
- a large hydraulic excavator includes a lower traveling body 2 having left and right endless track tracks (crawlers) 1L and 1R (only 1L is shown in FIG. 1) as traveling means,
- the upper swing body 3 that is pivotably mounted on the upper part of the lower traveling body 2 and the swing frame 4 that forms the basic lower structure of the upper swing body 3 are attached so as to be vertically rotatable (can be raised and lowered).
- a multi-joint type front working machine 5 5.
- a cap 6 that is arranged on the left side of the front part to form a driver's cab, an upper cover 7 that covers most of the part other than this cap 6, and a rear work machine that is arranged at the rear part of the revolving frame 4.
- a counterweight 8 for balancing the weight with 5 is provided.
- the lower traveling body 2 includes a substantially H-shaped track frame 9 and driving wheels 10L and 10R rotatably supported near the rear ends of the left and right sides of the track frame 9 (only 10L is shown in FIG. 1). 1), left and right traveling hydraulic motors (not shown) that drive these drive wheels 10L and 10R, respectively, and a track frame 9 that is rotatably supported in the vicinity of the left and right front ends of each track 1L , 1R, driven wheels (idlers) 11L and 11R (only 11L shown in FIG. 1) rotated by the driving force of driving wheels 10L and 10R, respectively.
- a swivel bearing (swivel wheel) 12 is disposed in the center of the lower traveling body 2, and the swing that causes the lower traveling body 2 to swivel on the swing frame 4 near the center of the swivel wheel 12.
- a hydraulic motor (not shown) is built in.
- the front work machine 5 has a boom 13 whose base end side is coupled to the revolving frame 4 so as to be rotatable about the horizontal axis direction, and the base end side of the boom 13 is rotatable to the distal end side of the boom 13.
- the boom 13, the arm 14, and the bucket 15 are operated by a pair of left and right boom hydraulic cylinders 16, 16, an arm hydraulic cylinder 17, and a packet hydraulic cylinder 18, respectively.
- the left and right crawler belts 1L and 1R, the upper swing body 3, the boom 13, the arm 14, and the packet 15 are covered by a hydraulic drive device provided in the hydraulic excavator.
- the drive member is configured.
- FIG. 2 is a hydraulic circuit diagram illustrating, with an example of a main part configuration related to driving of the boom 13 in the hydraulic drive device, together with an embodiment of the cooling device for the construction machine according to the present embodiment.
- an engine 19 a variable displacement hydraulic pump 20 driven by the engine 19, the boom hydraulic cylinder 16 (only one is shown in FIG. 2), a hydraulic pressure A control port that controls the flow of pressure oil to the hydraulic cylinder 16 for the pump and 20 pumps, and an intercooler 22 that cools the compressed air pressurized by the turbocharger 38 installed in the engine 19.
- a radiator 23 that cools the cooling water of the engine 19, an oil cooler 24 that cools the hydraulic oil, and one (or more) coolings that generate cooling air to the intercooler 22, the radiator 23, and the oil cooler 24.
- Last P fan 25 fan hydraulic motor 26 that drives this cooling fan 25, and variable capacity fan oil that is driven by the engine 19 and discharges the hydraulic oil to the fan hydraulic motor 26
- a pressure pump 27, a relief valve 28 for defining the maximum discharge pressure of the fan hydraulic pump 27, and a controller 29 are provided.
- the radiator 23 and the oil cooler 24 are arranged side by side toward the cooling fan 25, and the intercooler 22 is arranged on the upstream side (left side in FIG. 2) in the cooling air flow direction of the radiator 23 and the oil cooler 24. Has been.
- the control valve 21 receives, for example, an operation pilot pressure corresponding to the operation of an operation lever (not shown) in the cab, and the pressure from the hydraulic pump 20 to the boom hydraulic cylinder 16 in response thereto.
- the oil flow is switched.
- the engine 19 combusts the air sucked through the air cleaner 39, the turbocharger 38, and the suction flow path 30 together with the fuel, and the intercooler 22 provided in the suction flow path 30 includes The compressed air from the turbocharger 38 is cooled.
- An air temperature sensor 31 for detecting the air temperature is provided at the outlet of the intercooler 22. And a detection signal from the air temperature sensor 31 is output to the controller 29.
- the engine 19 is provided with a cooling flow path 32 through which cooling water is circulated by a pump or the like (not shown), and the radiator 23 provided in the cooling flow path 32 cools the cooling water. It is supposed to be.
- a cooling water temperature sensor 33 for detecting the temperature of the cooling water is provided at the inlet of the radiator 23, and a detection signal from the cooling water temperature sensor 33 is output to the controller 29.
- the cooling water temperature sensor 33 is not limited to the force provided at the inlet of the radiator 23, and may be provided at the outlet of the radiator 23, for example.
- the oil cooler 24 is provided in a return flow path 35 from the control valve 21 and the hydraulic motor 26 to the hydraulic oil tank 34, and cools the hydraulic oil.
- a hydraulic oil temperature sensor 36 that detects the temperature of the hydraulic oil is provided at the outlet of the oil cooler 24, and a detection signal from the hydraulic oil temperature sensor 36 is output to the controller 29.
- the hydraulic oil temperature sensor 36 is provided at the outlet of the oil cooler 24.
- the present invention is not limited to this.
- the hydraulic oil temperature sensor 36 may be provided at the inlet of the oil cooler 24, the hydraulic oil tank 34, or the like.
- the controller 29 is a calculation table that is preset and stored for the detection signals input from the air temperature sensor 31, the coolant temperature sensor 33, and the hydraulic oil temperature sensor 36 (for details, see FIGS. A predetermined calculation process is performed based on FIG. 6), and the generated control signal is output to the capacity control device 37 of the fan hydraulic pump 27. The control procedure of such a controller 29 will be described with reference to FIG.
- FIG. 3 is a flowchart showing the control processing contents of the controller 29.
- FIGS. 4 to 6 show calculation tables stored in the controller 29, and cooling with respect to the air temperature at the outlet of the intercooler 22 is shown.
- FIG. 6 is a characteristic diagram showing the fan rotation speed, the cooling fan rotation speed with respect to the coolant temperature at the inlet of the radiator 23, and the cooling fan rotation speed with respect to the hydraulic oil temperature at the oil cooler 24 outlet.
- step 100 the cooling temperature of the air temperature T at the outlet of the intercooler 22 input from the air temperature sensor 31 is determined based on the calculation table shown in FIG. Calculate the first calculation value of unrotation speed. Specifically, when the air temperature T at the outlet of the intercooler 22 is equal to or lower than the first control air temperature T, the cooling fan speed N is the minimum speed.
- the cooling fan speed ⁇ is the minimum speed.
- step 110 the cooling fan rotation is performed based on the calculation table shown in Fig. 5 with respect to the cooling water temperature T at the inlet of the radiator 23 input from the cooling water temperature sensor 33.
- the cooling fan speed N is the minimum speed N.
- the cooling fan speed N becomes the maximum speed N, and the cooling water temperature at the inlet of the radiator 23
- the cooling fan speed ⁇ is the minimum speed ⁇
- step 120 the cooling fan rotation is performed based on the calculation table shown in FIG. 6 with respect to the hydraulic oil temperature T at the outlet of the oil cooler 24 input from the hydraulic oil temperature sensor 36.
- Cooling fan speed N is the minimum speed N when the temperature is lower than the first control hydraulic fluid temperature T
- step 130 the highest value among the calculated values N, N, N of the cooling fan rotational speed is obtained.
- Step 140 Select a large value and proceed to Step 140 to generate a corresponding control signal and output it to the capacity controller 37 of the fan hydraulic pump 27.
- the capacity control device 37 of the fan hydraulic pump 27 adjusts the discharge amount per rotation by operating the tilt angle (the displacement volume) of the swash plate of the fan hydraulic pump 27 in accordance with the input control signal. It comes to adjust.
- the fan hydraulic motor 26 is driven according to the discharge capacity of the fan hydraulic pump 27, and the rotation speed of the cooling fan 25 is controlled so that the cooling fan rotation speed selected in step 130 is reached.
- the air temperature sensor 31 constitutes an air temperature detecting means for detecting the air temperature at the outlet of the intercooler described in the claims
- the cooling water temperature sensor 33 is the cooling water of the radiator.
- the coolant temperature detecting means for detecting the temperature is constituted
- the hydraulic oil temperature sensor 36 constitutes the hydraulic oil temperature detecting means for detecting the hydraulic oil temperature of the oil cooler.
- the control function shown in FIG. 3 of the controller 29 inputs the detected values of the air temperature detecting means, the cooling water temperature detecting means, and the hydraulic oil temperature detecting means, and the cooling fan rotational speed corresponding to each of the detected values. Control means for outputting a control signal corresponding to the maximum value among the calculated values is configured.
- the air temperature T at the outlet of the intercooler 22 the coolant temperature T at the inlet of the radiator 23, and the hydraulic oil temperature at the outlet of the oil cooler 24
- the number of rotations of the cooling fan 25 is controlled according to T. This allows Intercooler 22, Raje
- the cooling water temperature T and hydraulic oil temperature T are high and the air temperature T immediately after the engine is stopped.
- an unnecessary increase in the number of rotations of the cooling fan can be prevented as compared with a case where an engine direct acting type cooling fan is provided, and thereby noise of the cooling fan 22 can be reduced.
- the cooling fan for the intercooler, the radiator, and the oil cooler can be shared to reduce the number of parts, and the noise of the cooling fan 22 can be reduced.
- the air conditioner This is an embodiment in which a condenser for cooling the refrigerant is additionally provided.
- FIG. 7 is a hydraulic circuit diagram showing the construction machine cooling device according to the present embodiment together with the hydraulic drive device.
- parts that are the same as in the first embodiment are given the same reference numerals, and descriptions thereof will be omitted as appropriate.
- the air conditioner device 40 for the cab, the condenser 41 for cooling the refrigerant of the air conditioner device 40, and the output shaft of the engine 19 are provided so as to be detachable from the air conditioner device 40.
- a compressor 42 that compresses the refrigerant and supplies it to the condenser 41, and an air temperature sensor 43 and a force S, which are provided between the air tailor 39 and the turbocharger 38 and detect the outside air temperature, are provided.
- the condenser 41 is arranged upstream of the radiator 23 and the oil cooler 24 in the flow direction of the cooling air (left side in FIG. 7), and is arranged in parallel with the intercooler 22.
- the air conditioner 40 includes a driving switch that can be operated by the driver, a blower that blows cooling air into the driving chamber, and a control unit that drives and controls the compressor 42, the blower, and the like. And have. For example, when the operation switch is turned on, a drive command signal (control signal) for driving the compressor 42 is output from the control unit to the compressor 42 and the controller 44, respectively.
- the compressor 42 is connected to the output shaft of the engine 19 in response to the drive command signal and is driven.
- the controller 44 is a calculation table that is preset for each of the detection signals input from the air temperature sensor 31, the coolant temperature sensor 33, the hydraulic oil temperature sensor 36, the outside air temperature sensor 43, etc. A predetermined calculation process is performed based on the above-described FIGS. 4 to 6 and FIG. 9 described later), and the generated control signal is output to the capacity control device 37 of the fan hydraulic pump 27.
- FIG. 8 is a flowchart showing the control processing contents of the controller 44
- FIG. 9 shows one of the calculation tables stored in the controller 44.
- the cooling fan rotation with respect to the outside air temperature is shown in FIG. It is a characteristic view showing a number.
- step 200 the cooling fan for the air temperature T at the outlet of the intercooler 22 2 input from the air temperature sensor 31 is calculated based on the calculation table shown in FIG. Calculate the first calculation value of the number of revolutions and proceed to Step 210 to calculate the coolant temperature T at the inlet of the radiator 23 input from the coolant temperature sensor 33 and the calculation tape shown in Fig. 5 above.
- the second calculated value N of the cooling fan speed is calculated based on the
- Hydraulic oil temperature sensor 36 input oil cooler 24 outlet hydraulic oil temperature T
- step 230 it is determined whether the air conditioner 40 is driven by determining whether the power of the air conditioner 40 and the drive command signal for the compressor 42 are input.
- the determination at step 230 is satisfied, and the routine proceeds to step 240.
- step 240 the calculation shown in Fig. 9 is performed on the outside air temperature T input from the outside air temperature sensor 43.
- the cooling fan speed N is the minimum speed.
- the cooling fan speed N is within the range from the minimum speed N to the maximum speed N.
- step 250 the process proceeds to step 250, and among the calculated values ⁇ , ⁇ , ⁇ , and ⁇ of the cooling fan rotation speed
- Step 260 Select the maximum value of 1 2 3 4 and proceed to Step 260 to generate a corresponding control signal and output it to the capacity controller 37 of the fan hydraulic pump 27.
- the fan hydraulic motor 26 is driven according to the discharge capacity of the fan hydraulic pump 27, and the rotation speed of the cooling fan 25 is controlled so as to be the cooling fan rotation speed selected in step 250 above.
- Step 270 the calculated value of the cooling fan speed ⁇ , ,, ⁇ (in other words,
- step 260 a corresponding control signal is generated and output to the capacity control device 37 of the fan hydraulic pump 27.
- the fan hydraulic motor 26 is driven, and the number of revolutions of the cooling fan 25 is controlled so that the number of revolutions of the cooling fan selected in step 270 is reached.
- the outside air temperature sensor 43 constitutes outside air temperature detecting means for detecting the outside air temperature described in the claims.
- the control function shown in FIG. 8 of the controller 44 is the detection value of the air temperature detecting means, the cooling water temperature detecting means, the hydraulic oil temperature detecting means, and the outside air temperature detecting means when the air conditioner is operating. Is input, and a control signal corresponding to the maximum value of the calculated values of the cooling fan rotation speed corresponding to each of the detected values is output.
- the detection values of the temperature detection means, hydraulic oil temperature detection means, and outside air temperature detection means are input, and the control signal corresponding to the maximum value among the calculated values of the cooling fan speed corresponding to each of the detection values is output.
- the control means is configured.
- the speed of the cooling fan 25 is controlled according to the hydraulic oil temperature T at the outlet of the cooler 24. This
- the amount of cooling air necessary for the intercooler 22, the radiator 23, and the oil cooler 24 can be ensured as in the first embodiment.
- the air conditioner 40 when the air conditioner 40 is driven, the air temperature T at the outlet of the intercooler 22, the cooling water temperature T at the inlet of the radiator 23,
- Oil cooler 24 Number of rotations of cooling fan 25 according to hydraulic oil temperature T and outside air temperature T at outlet
- an unnecessary increase in the number of rotations of the cooling fan can be prevented as compared with a case where an engine direct acting type cooling fan is provided, and thereby noise of the cooling fan 22 can be reduced.
- the cooling fan for the intercooler, the radiator, the oil cooler, and the condenser can be shared to reduce the number of parts, and further the noise of the cooling fan 22 can be reduced.
- the controller 44 inputs a drive command signal for the compressor 42 from the air conditioner 40 to determine whether or not the air conditioner 40 is driven.
- this is not a limitation. That is, for example, it may be determined whether the air conditioner 40 is driven by inputting a signal corresponding to the ON state of the operation switch of the air conditioner 40 or a signal corresponding to the driving of the blower. In such a case, the same effect as described above can be obtained.
- a lower limit value of the calculated value of the cooling fan speed (hereinafter referred to as a lower limit value of the cooling fan speed) is set according to the engine speed.
- FIG. 10 is a hydraulic circuit diagram showing the construction machine cooling device according to the present embodiment together with the hydraulic drive device.
- parts that are the same as in the first and second embodiments are given the same reference numerals, and descriptions thereof will be omitted as appropriate.
- an engine speed sensor 45 (engine speed detecting means) for detecting the speed of the engine 19 is provided, and the detection signal is output to the controller 44A.
- the controller 44A is preset and stored with respect to detection signals input from the air temperature sensor 31, the coolant temperature sensor 33, the hydraulic oil temperature sensor 36, the outside air temperature sensor 43, the engine speed sensor 45, and the like. Based on the calculation table (for details, see Figs. 4 to 6 and 9 and Fig. 12 described later), and the generated control signal is used to control the capacity of the hydraulic pump 27 for the fan. Output to device 37.
- FIG. 11 is a flowchart showing the control processing contents of the controller 44A.
- FIG. 12 shows one of the calculation tables stored in the controller 44A, and shows the cooling fan rotation speed relative to the engine rotation speed. It is a characteristic view showing a lower limit.
- step 300 the cooling temperature of the air temperature T at the outlet of the intercooler 22 input from the air temperature sensor 31 is determined based on the calculation table shown in FIG.
- the first calculated value N of the engine speed is calculated, and the process proceeds to step 310 where the coolant temperature sensor 33
- the calculator tape shown in Fig. 5 above is used for the coolant temperature T at the inlet of the radiator 23
- the second calculated value N of the cooling fan speed is calculated based on the
- Hydraulic oil temperature sensor 36 input oil cooler 24 outlet hydraulic oil temperature T
- step 330 it is determined whether or not the air conditioner device 40 is driven. If the air conditioner 40 is operating, the determination at step 330 is satisfied, and the routine proceeds to step 340.
- step 340 the outside air temperature T input from the outside air temperature sensor 43 is
- step 350 the lower limit value N of the cooling fan speed is determined based on the calculation table shown in FIG. 12 for the engine speed E input from the engine speed sensor 45.
- the first lower limit rotational speed N (for example, the minimum rotational speed N during high idle operation).
- the engine speed E is the second engine speed E (for example, the engine speed b during low idle operation b
- the lower limit value N of the cooling fan speed is the second lower speed limit N (e.g.
- Step 360 the process proceeds to Step 360, where the calculated values N, N, N, N and
- step 380 the calculated values of the cooling fan speed N, N,
- Step 370 Select the maximum value (except 3 4) and go to Step 370 to generate the corresponding control signal and output it to the capacity controller 37 of the hydraulic pump 27 for fan.
- the fan hydraulic pump The fan hydraulic motor 26 is driven in accordance with the discharge capacity 27, and the rotation speed of the cooling fan 25 is controlled so as to be the cooling fan rotation speed selected in step 380.
- the amount of cooling air necessary for the intercooler 22, the radiator 23, and the oil cooler 24 when the air-con device 40 is stopped as in the second embodiment.
- the air conditioner 40 is driven, it is possible to reliably secure the cooling air volume required for the intercooler 22, the radiator 23, the oil cooler 24, and the condenser 41.
- the noise of the cooling fan 22 can be reduced as compared with a case where an engine direct acting type cooling fan is provided.
- a lower limit value N of the cooling fan speed that increases as the engine speed E decreases is calculated, and the cooling fan speed is increased.
- the controller 44A selects the maximum value among the calculated values N 1, N 2, N 3, N 5 and N of the cooling fan rotation speed when the air conditioner 40 is driven.
- control process for outputting the corresponding control signal has been described as an example, but the present invention is not limited to this. That is, for example, the maximum of the calculated values N, N, N, N of the cooling fan rotation speed
- the calculated value of the selected cooling fan speed is N, N, or N.
- the larger of the calculated value N and the lower limit value N for the cooling fan speed is output.
- Control processing may be performed such that a control signal corresponding to this is output. In such a case, the same effect as described above can be obtained.
- the controller 44A when the air conditioner 40 is stopped, calculates the cooling fan rotational speed N corresponding to the intercooler 22, the radiator 23, and the oil cooler 24. Select the maximum value of N and N and set the corresponding control signal
- the force described using the output control process as an example is not limited to this. That is, for example, the lower limit value N of the cooling fan speed is calculated according to the engine speed E detected by the engine speed sensor 45, and the calculated values N, N, N and the lower limit value N of the cooling fan speed are calculated. The most
- Control processing may be performed in which a large value is selected and a control signal corresponding to this value is output. Also on The engine speed sensor may be provided in the first embodiment to perform the same control process. In these cases, the same effect as described above can be obtained.
- variable capacity fan hydraulic pump 27 is controlled to control the rotation speed of the cooling fan 25
- present invention is not limited thereto. That is, for example, a constant capacity fan hydraulic pump and a variable capacity fan hydraulic motor may be provided, and the capacity of the fan hydraulic motor may be controlled to control the rotation speed of the cooling fan. ,. In such a case, the same effect as described above can be obtained.
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Component Parts Of Construction Machinery (AREA)
- Cooling, Air Intake And Gas Exhaust, And Fuel Tank Arrangements In Propulsion Units (AREA)
Abstract
Description
Claims
Priority Applications (5)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US11/658,910 US7685816B2 (en) | 2005-04-07 | 2005-12-22 | Cooling system for construction machine |
JP2007521079A JP4842264B2 (ja) | 2005-04-07 | 2005-12-22 | 建設機械の冷却装置 |
KR1020077002564A KR101134275B1 (ko) | 2005-04-07 | 2005-12-22 | 건설 기계의 냉각 장치 |
EP05819965.4A EP1870576B1 (en) | 2005-04-07 | 2005-12-22 | Cooling device for construction machine |
AU2005330847A AU2005330847B2 (en) | 2005-04-07 | 2005-12-22 | Cooling device for construction machine |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
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JP2005-110487 | 2005-04-07 | ||
JP2005110487 | 2005-04-07 |
Publications (1)
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WO2006112091A1 true WO2006112091A1 (ja) | 2006-10-26 |
Family
ID=37114833
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2005/023608 WO2006112091A1 (ja) | 2005-04-07 | 2005-12-22 | 建設機械の冷却装置 |
Country Status (7)
Country | Link |
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US (1) | US7685816B2 (ja) |
EP (1) | EP1870576B1 (ja) |
JP (1) | JP4842264B2 (ja) |
KR (1) | KR101134275B1 (ja) |
CN (1) | CN100567713C (ja) |
AU (1) | AU2005330847B2 (ja) |
WO (1) | WO2006112091A1 (ja) |
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CN115306530B (zh) * | 2022-08-29 | 2024-03-01 | 徐州徐工挖掘机械有限公司 | 一种串联空调冷凝器的独立散热***的控制方法及*** |
Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS6250219A (ja) * | 1985-08-29 | 1987-03-04 | Nissan Motor Co Ltd | フアンモ−タ制御装置 |
JPH11294162A (ja) * | 1998-04-06 | 1999-10-26 | Nissan Motor Co Ltd | 冷却ファンの回転数制御装置 |
JP2000110560A (ja) * | 1998-10-08 | 2000-04-18 | Shin Caterpillar Mitsubishi Ltd | ファン回転数制御方法およびその装置 |
JP2001182535A (ja) | 1999-12-22 | 2001-07-06 | Komatsu Ltd | 油圧駆動冷却ファン |
JP2004353554A (ja) * | 2003-05-29 | 2004-12-16 | Nissan Motor Co Ltd | 車両用冷却ファンの制御装置 |
WO2005026509A1 (ja) | 2003-09-11 | 2005-03-24 | Shin Caterpillar Mitsubishi Ltd. | ファン回転数制御方法 |
Family Cites Families (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4546742A (en) * | 1984-01-23 | 1985-10-15 | Borg-Warner Corporation | Temperature control system for internal combustion engine |
US6076488A (en) * | 1997-03-17 | 2000-06-20 | Shin Caterpillar Mitsubishi Ltd. | Cooling device for a construction machine |
US6311488B1 (en) * | 1998-10-26 | 2001-11-06 | Komatsu Ltd. | Cooling fan drive apparatus |
JP2000274243A (ja) * | 1999-03-25 | 2000-10-03 | Fuji Heavy Ind Ltd | 車両用冷却ファン制御装置 |
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 |
US6453853B1 (en) * | 2000-12-04 | 2002-09-24 | Detroit Diesel Corporation | Method of controlling a variable speed fan |
JP4439287B2 (ja) * | 2004-02-19 | 2010-03-24 | 株式会社小松製作所 | 建設機械の冷却装置 |
US7373239B2 (en) * | 2005-07-06 | 2008-05-13 | Komatsu, Ltd. | Engine control device of work vehicle |
-
2005
- 2005-12-22 WO PCT/JP2005/023608 patent/WO2006112091A1/ja not_active Application Discontinuation
- 2005-12-22 CN CNB2005800298039A patent/CN100567713C/zh active Active
- 2005-12-22 EP EP05819965.4A patent/EP1870576B1/en active Active
- 2005-12-22 JP JP2007521079A patent/JP4842264B2/ja active Active
- 2005-12-22 US US11/658,910 patent/US7685816B2/en active Active
- 2005-12-22 AU AU2005330847A patent/AU2005330847B2/en active Active
- 2005-12-22 KR KR1020077002564A patent/KR101134275B1/ko active IP Right Grant
Patent Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS6250219A (ja) * | 1985-08-29 | 1987-03-04 | Nissan Motor Co Ltd | フアンモ−タ制御装置 |
JPH11294162A (ja) * | 1998-04-06 | 1999-10-26 | Nissan Motor Co Ltd | 冷却ファンの回転数制御装置 |
JP2000110560A (ja) * | 1998-10-08 | 2000-04-18 | Shin Caterpillar Mitsubishi Ltd | ファン回転数制御方法およびその装置 |
JP2001182535A (ja) | 1999-12-22 | 2001-07-06 | Komatsu Ltd | 油圧駆動冷却ファン |
JP2004353554A (ja) * | 2003-05-29 | 2004-12-16 | Nissan Motor Co Ltd | 車両用冷却ファンの制御装置 |
WO2005026509A1 (ja) | 2003-09-11 | 2005-03-24 | Shin Caterpillar Mitsubishi Ltd. | ファン回転数制御方法 |
US20060062678A1 (en) | 2003-09-11 | 2006-03-23 | Shin Caterpillar Mitsubishi | Fan rpm control method |
Non-Patent Citations (1)
Title |
---|
See also references of EP1870576A4 |
Cited By (15)
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JP2011511202A (ja) * | 2008-02-04 | 2011-04-07 | スカニア シーブイ アクチボラグ | 冷却制御方法と装置、及びエンジン |
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US10006646B2 (en) | 2015-04-30 | 2018-06-26 | Samsung Electronics Co., Ltd. | Outdoor unit of air conditioner and control device for the outdoor unit |
JP2018059420A (ja) * | 2016-10-03 | 2018-04-12 | ボッシュ株式会社 | ファンコントロールユニット |
JP2018115587A (ja) * | 2017-01-17 | 2018-07-26 | いすゞ自動車株式会社 | ファン制御装置及びファン制御方法 |
JP2018189040A (ja) * | 2017-05-09 | 2018-11-29 | いすゞ自動車株式会社 | ファン制御装置 |
CN110159409A (zh) * | 2019-06-27 | 2019-08-23 | 北京三一智造科技有限公司 | 冷却装置、旋挖钻机及发动机冷却方法 |
CN110159409B (zh) * | 2019-06-27 | 2023-11-17 | 北京三一智造科技有限公司 | 冷却装置、旋挖钻机及发动机冷却方法 |
CN113071301A (zh) * | 2021-04-07 | 2021-07-06 | 中通客车股份有限公司 | 一种纯电动车用集成式散热***及控制方法 |
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Publication number | Publication date |
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EP1870576B1 (en) | 2014-04-30 |
EP1870576A1 (en) | 2007-12-26 |
CN101010497A (zh) | 2007-08-01 |
AU2005330847A1 (en) | 2006-10-26 |
AU2005330847B2 (en) | 2009-07-02 |
KR101134275B1 (ko) | 2012-04-12 |
EP1870576A4 (en) | 2011-07-20 |
JP4842264B2 (ja) | 2011-12-21 |
KR20070118221A (ko) | 2007-12-14 |
US20090217655A1 (en) | 2009-09-03 |
US7685816B2 (en) | 2010-03-30 |
CN100567713C (zh) | 2009-12-09 |
JPWO2006112091A1 (ja) | 2008-11-27 |
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