US20170030256A1 - Air management system for under-hood heat control - Google Patents
Air management system for under-hood heat control Download PDFInfo
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- US20170030256A1 US20170030256A1 US15/295,624 US201615295624A US2017030256A1 US 20170030256 A1 US20170030256 A1 US 20170030256A1 US 201615295624 A US201615295624 A US 201615295624A US 2017030256 A1 US2017030256 A1 US 2017030256A1
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- vehicle
- engine compartment
- radiator
- engine
- ventilating system
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Classifications
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K11/00—Arrangement in connection with cooling of propulsion units
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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
- F01P11/00—Component parts, details, or accessories not provided for in, or of interest apart from, groups F01P1/00 - F01P9/00
- F01P11/10—Guiding or ducting cooling-air, to, or from, liquid-to-air heat exchangers
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K11/00—Arrangement in connection with cooling of propulsion units
- B60K11/08—Air inlets for cooling; Shutters or blinds therefor
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
- B62D—MOTOR VEHICLES; TRAILERS
- B62D25/00—Superstructure or monocoque structure sub-units; Parts or details thereof not otherwise provided for
- B62D25/08—Front or rear portions
- B62D25/10—Bonnets or lids, e.g. for trucks, tractors, busses, work vehicles
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
- B62D—MOTOR VEHICLES; TRAILERS
- B62D25/00—Superstructure or monocoque structure sub-units; Parts or details thereof not otherwise provided for
- B62D25/08—Front or rear portions
- B62D25/10—Bonnets or lids, e.g. for trucks, tractors, busses, work vehicles
- B62D25/12—Parts or details thereof
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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
- F01P1/00—Air cooling
- F01P1/06—Arrangements for cooling other engine or machine parts
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60Y—INDEXING SCHEME RELATING TO ASPECTS CROSS-CUTTING VEHICLE TECHNOLOGY
- B60Y2200/00—Type of vehicle
- B60Y2200/10—Road Vehicles
- B60Y2200/14—Trucks; Load vehicles, Busses
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60Y—INDEXING SCHEME RELATING TO ASPECTS CROSS-CUTTING VEHICLE TECHNOLOGY
- B60Y2200/00—Type of vehicle
- B60Y2200/10—Road Vehicles
- B60Y2200/14—Trucks; Load vehicles, Busses
- B60Y2200/142—Heavy duty trucks
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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
- F01P1/00—Air cooling
- F01P2001/005—Cooling engine rooms
Definitions
- This invention relates to systems for reducing temperatures under the hood of a vehicle. It has particular, but not exclusive, application to such systems for use in a heavy duty truck, more particularly to the tractor portion of a tractor-trailer rig.
- Heavy duty trucks are typically over-the-road and vocational vehicles considered as weight class 4 to 8.
- Class 4 is generally considered to include vehicles with a gross vehicle weight of 14,001 lb to 16,000 lb (6350 kg to 7257 kg).
- the invention is particularly useful with weight class 6 to 8 vehicles, most particularly class 7 to 8 vehicles.
- Class 6 includes vehicles with a gross vehicle weight of 19,501 lb to 26,000 lb (8846 kg to 11,793 kg).
- Class 7 vehicles have a gross vehicle weight of 26,001 lb to 33,000 lb (11,794 kg to 14,969 kg).
- Vocational heavy duty trucks are adapted for various off-road jobs such as concrete mixer trucks, log-hauling trucks and other trucks which carry heavy loads and are required to operate over rough and uneven ground under off-road conditions. Such trucks are generally also capable of on-road highway travel.
- the internal combustion engine of a heavy duty truck produces great quantities of heat.
- Heat is taken from the engine block by a liquid coolant system, including a radiator spaced in front of the engine block.
- the heat is dissipated by natural convection, primarily by air flow caused by motion of the vehicle, and by the air which is blown through the radiator and over the engine by an axial fan.
- the axial fan is run directly from the engine crank shaft, through a clutch.
- the fan is electric. In either, the efficiency of the fan is relatively low, frequently on the order of forty percent. This is caused in part by the natural inefficiency of the fan itself.
- a heavy duty truck engine may produce on the order of 1.5 million BTUs (1.6 million kilojoules) an hour at a speed of sixty miles per hour (97 km/hr), producing less than twelve miles per gallon (5 km/I) of fuel usage, and may utilize up to a thirty-two inch (0.8 m) diameter fan nominally pulling 9,500 cubic feet (270 cubic meters) per minute to disperse the heat put out by the radiator. It is estimated that roughly one-third of the output of the engine is utilized to propel the truck, one-third is in the heated exhaust (as heat and unburned fuel), and one-third must be handled by the cooling system.
- the engine block In addition to the heat carried from the engine block to the radiator by the coolant, the engine block itself radiates substantial heat, estimated to be up to about 20,000 BTUs (22,000 kJ) an hour at highway speeds.
- EGR exhaust gas recirculation
- Trucks equipped with engines over 250 horsepower (186 kW) have consequently begun to experience severe under-hood heat problems.
- the EGR system recirculates a portion (typically about 15%-30%) of the exhaust gas to the engine air intake. Because the exhaust gas has a temperature of about 1200° F. to about 1500° F. (about 650° C. to about 815° C.), it is cooled to about 600° F. (315° C.) by running it through an EGR heat exchanger before introducing it into the cylinders of the engine.
- the EGR system adds about thirty percent to the cooling system heat load, about 150,000 BTUs (160,000 kJ) per hour, most of which must be dispersed by the radiator. Because much of this heat is directed back into the engine compartment, under-hood heat loads are dramatically increased. The EGR system itself also radiates heat directly into the engine compartment.
- auxiliary devices are run by the engine and generate further heat.
- an air compressor is required for operation of brakes and other components.
- the air compressor may have a surface temperature on the order of 250° F. (121° C.).
- a turbocharger powered by the exhaust gasses, generates further heat, estimated to be on the order of 32,000 BTUs (34,000 kJ) per hour.
- the turbocharger may have an operating surface temperature of about 800° F. to 1200° F. (425° C. to 650° C.).
- the additional heat produced under the hood of a modern heavy duty truck has raised temperatures under the hood to unacceptable levels.
- the additional heat and temperature reduce the lives of components in the engine compartment and reduce engine efficiency. They sometimes melt plastic components and overheat fluids in the engine compartment.
- the heat also can transfer into the vehicle operator cab and can make both the air temperature in the cab and surface temperatures on the floor and front wall of the cab uncomfortably high. Attempts to enlarge the radiator, by repositioning it, tilting it, or splitting it, have not been sufficient. Enlarging the fan is likewise impractical and would increase the power requirements for running it.
- a modern heavy duty truck requires aerodynamic design considerations that sometimes make the hood design smaller. Packing more equipment in the engine compartment further makes airflow more difficult. All of these considerations require a completely new approach to under-hood air management.
- the present invention provides a system for removing heat from the engine compartment of a vehicle by isolating heat from the radiator from the engine compartment (above and to the sides of the engine block).
- the invention provides a new design which separates the heat loads and provides separate exhaust exits, but allows the systems to operate together or separately as needed.
- Heat from the radiator is taken from a plenum behind the radiator, preferably by centrifugal squirrel cage blowers, and is directed out of the engine compartment, rather than against the engine block.
- the blowers are preferably controlled thermostatically to allow some or all of the blowers to operate as needed. The use of predictive computer control of the blowers is also contemplated.
- the engine block and its associated devices are cooled by a separate system which draws ambient air generally from back to front of the engine compartment, preferably by cowl induction, without the use of ram air from the vicinity of the radiator.
- Both the radiator ventilating system and the engine compartment ventilating system preferably exit to ambient through side walls of the engine compartment, near the front of the engine compartment.
- the exits are preferably configured to exhaust hot air into the slip stream of the truck, which tends to draw air from the system.
- the exit of the engine compartment ventilating system is preferably behind the exit of the radiator ventilating system and is configured to utilize the flow of air from the radiator ventilating system to ambient to draw air out of the engine compartment. Air flow around each exit is preferably primarily laminar.
- the systems of the invention may include one or more standard radiator, plenum and blower packages sized for particular classes of vehicles or engine sizes. It may also include a standard cowl induction system also sized for particular classes of vehicles or engine sizes. Ducting for each system, however, is likely to be dependent on particular vehicle designs, including such considerations as available space in the engine compartment, internal configuration of the engine compartment and placement of engine components inside the engine compartment affecting air flow within the engine compartment, combustion air intake configuration of the engine, and air flow patterns around the outside of the engine compartment.
- FIG. 1 is a schematic sectional view in side elevation of an internal combustion engine compartment in a heavy duty truck, modified in accordance with one embodiment of the present invention.
- FIG. 2 is a view in top plan, showing air flow through a part of an illustrative embodiment of the system of FIG. 1 .
- FIG. 3 is a view in rear elevation, showing an illustrative radiator cooling system package of the present invention.
- FIG. 4 is a view in side elevation of the package of FIG. 3 .
- FIG. 5 is a view in perspective of parts of the system of FIGS. 2-4 , taken along line 5 - 5 of FIG. 2 .
- FIG. 6 is a view in perspective of an engine compartment air outlet of the system of FIGS. 2-5 .
- FIG. 7 is a schematic view in perspective showing a cowl induction scoop in accordance with an embodiment of another part of the invention.
- FIG. 8 is a view in perspective of an over-the-road truck incorporating the embodiment of FIGS. 1-7 .
- an internal combustion engine in a large heavy duty truck 2 ( FIGS. 1 and 8 ) includes the engine block 3 , air intake 5 , and a radiator 7 which cools coolant circulated from inside the engine block 3 through passages 8 . All of these components of the engine are contained in an engine compartment 9 having a front 10 (usually at or just ahead of the radiator), a top 11 , and sides 12 . The top and much of the sides are generally formed as a raisable hood 13 ( FIG. 8 ), which is typically hinged to the body of the truck in the area of a lower front end of the truck. At the back of the engine compartment 9 , a fire wall 14 separates the engine compartment from an operator cab 15 .
- a turbocharger 16 , exhaust piping 17 , and an air compressor 19 add to the heat load in the engine compartment 9 .
- the heat radiated by the engine and the heat blown back into the engine compartment by an axial fan raise the temperature of the engine compartment.
- an exhaust gas recirculation (EGR) system including an EGR valve 20 , adds further to the heat load on the radiator and the temperature in the engine compartment, particularly because the EGR system typically circulates on the order of 15% to on the order of 30% of the hot exhaust gas back into the engine.
- the total heat load in the engine compartment 9 of a modern heavy duty truck 2 is estimated to be about 60,000 BTUs (63,000 kJ) per hour.
- This illustrative embodiment of the invention removes the axial fan and replaces it with an isolated radiator ventilating system 21 including a plenum 23 mounted to the back of the radiator 7 , preferably in sealing relationship with the radiator. Therefore, all ram air reaching the radiator 7 when the truck is in forward motion is directed through the radiator 7 and is concentrated in the plenum 23 .
- Mounted on the plenum 23 preferably on its back, are multiple motors 25 driving squirrel cage (centrifugal) fans 27 behind the plenum 23 .
- the squirrel cage fans 27 draw heated air axially from the plenum and redirect the air 90° to discharge it outwardly (laterally) into air ducts 43 as described hereinafter.
- the back side of the plenum 23 , the fans 27 , and air ducts 43 may be provided with insulating material in the form of a coating or a separate insulative layer or barrier.
- this arrangement effectively shields the engine, its components, and add-ons in the engine compartment 9 from the approximately 650,000 BTUs (700,000 kJ) or more per hour being dissipated to ambient by the radiator 7 when the truck 2 is at highway speed. Exhausting the heated air in this fashion will remove the constant reinforcement of heat into the engine compartment. The problem of heat generation in the engine compartment is thus reduced to the 60,000 BTUs (63,000 kJ) per hour generated under the hood by the turbocharger 16 , EGR 20 , engine block 3 , and other engine compartment components.
- the motors 25 are operated thermostatically, with individual motors or groups of motors being operated only when required.
- Predictive algorithms for controlling the operation of the cooling fans 27 will be apparent to those skilled in the art. Such algorithms may include such factors as engine coolant temperature, rate of rise of coolant temperature, engine surface or oil temperature, engine compartment temperature, ambient temperature, engine speed, and truck speed, for example.
- the arrangement thus far described has the further advantages that it reduces the power (estimated to be sixty-five horsepower) required to operate a bladed fan. This could provide considerable fuel savings (7-9%). It also eliminates the fan clutch that has shown to be a high maintenance item.
- the electric squirrel cage fan blowers 27 are far more efficient in removing heat from the radiator 7 than the bladed axial fan. Because plural fan blowers 27 are preferably provided, air flow can be stepped up and down and controlled more effectively by controlling which blowers are powered. Moreover, the fan blower's DC motor can become a generator when it is off and free wheeling from ram air, thereby charging the truck's batteries.
- the isolated radiator ventilating system 21 described thus far may be implemented in a standard package 35 ; a few such packages will accommodate a wide range of heavy duty trucks.
- the package 35 may include a radiator 7 , a plenum 23 , and a plurality of fans 27 .
- a radiator 7 having a height of from about two to three feet (0.5 m to one meter) and a width of about 18′′ to about 36′′ (0.4 m to one meter), with a plenum 23 about one to two inches (2.5 cm to 5 cm) deep, sized to fit the back of the radiator.
- the package 35 may be mated to a ductwork system which is tailored to a particular truck style to create both the radiator ventilating system 21 and a part of an engine compartment ventilating system.
- a radiator and plenum 33′′ (84 cm) tall by 22′′ (56 cm) wide may be provided as a standard package 35 .
- the radiator 7 is illustratively 6′′ (15 cm) deep with a flange 36 extending around its periphery, and the plenum is 1.25′′ (3 cm) deep and includes a peripheral flange 37 attached to the flange 36 of the radiator. As best seen in FIG.
- each fan draws 530 cfm (15 cubic meters per minute) of air, and has a brushless 3′′ (7.6 cm) diameter, 3,000 rpm, 24 volt DC motor.
- the draws of the centrifugal fans are sized for particular applications.
- each fan 27 is about 9′′ wide by about 10′′ tall by about 4′′ deep (22.5 ⁇ 25.5 ⁇ 10 cm), and each housing has a 4′′ (10 cm) square outlet 39 .
- the upper left fan 27 A and the two lower right fans 27 B′ and 27 C′ have the same handedness (clockwise rotation), and that the upper right fan 27 A′ and the two lower left fans 27 B and 27 C have the opposite handedness (counterclockwise rotation).
- the lowermost fans 27 C and 27 C′ have extended outlets 39 ′, exiting between the exits of the two fans above them, so that all of the outlets on each side of the plenum align vertically to form a 12′′ by 4′′ (30 ⁇ 10 cm) rectangular outlet 40 on each side of the package.
- each motor 25 is individually electrically connected to a control system 41 having inputs, illustratively T 1 representing coolant temperature, T 2 representing engine compartment temperature, RPM representing engine speed, MPG representing instantaneous or integrated fuel consumption, and MPH representing vehicle speed.
- T 1 representing coolant temperature
- T 2 representing engine compartment temperature
- RPM representing engine speed
- MPG representing instantaneous or integrated fuel consumption
- MPH representing vehicle speed.
- This radiator cooling package 35 is mated to a duct system 43 .
- At least the rearward portion of duct system 43 is preferably, but not necessarily, mounted on the inside of the hood 13 .
- the juncture between the hood-mounted ducts 43 and the package 35 may be sealed in any known manner.
- the rectangular outlet 40 of the package 35 may terminate in a compound bevel 42 having a gasket on its open (upper) face to seal with a complementarily sloped bevel on the hood-mounted ducts. This arrangement permits unimpeded opening of the hood 13 and seals the duct system 43 to the package 35 when the hood 13 is closed.
- an end section of the package duct or the hood-mounted duct may be longitudinally moveable via an automatic or manual operating mechanism to mate with the other section of the duct.
- the duct system may be permanently attached to the radiator ventilating system package 35 and may simply align with an opening in each side 12 of the hood.
- the duct system 43 of this illustrative embodiment includes a curved outside wall 44 mated to a forward wall of the outlet 40 and a curved inside wall 45 mated to a rearward wall of the outlet 40 .
- the outside wall 44 terminates in a generally flat vertical rectangular opening 46 having a peripheral edge 47 aligned with a rectangular opening of similar size in the side wall 12 of the hood of the truck. It will be noted that the shape of this opening will be to some extent dictated by the contour of the truck's hood.
- the opening 46 is substantially twelve inches (30 cm) tall, the same height as the outlet 40 of the radiator ventilating package.
- the inside wall 45 of the duct system 43 is spaced four inches from the outside wall 44 along a curved inlet portion attached to the outlet 40 . When the inside wall 45 reaches a position opposite the opening 46 , it then curves gently outward into the rear edge 47 of the opening 46 .
- the outside and inside walls 44 and 45 are connected to each other by upper and lower horizontal walls 48 . It will be seen that the walls 44 , 45 and 48 form a smooth open channel guiding air exhausted from the radiator ventilating system 21 into the ambient slip stream of the heavy duty truck when the truck is moving forward.
- a separate engine compartment ventilating system 51 is provided.
- the second ventilating system 51 in this illustrative embodiment is sized to remove the approximately 60,000 BTUs (63,000 kJ) per hour of heat produced in the engine compartment.
- the 60,000 BTUs (63,000 kJ) per hour can be effectively controlled by cowl air induction strategically located on top of the hood, using the high pressure area at the windshield to flow cool ram air into the engine compartment and causing the engine compartment air to exit through hood side ducts arranged to draw air into a low pressure area adjacent the exit of radiator fan air into ambient. As shown in FIGS.
- the engine compartment ventilating system 51 includes an induction cowl 53 in front of the windshield 55 of the truck 2 .
- Cowl induction systems have long been used in race cars, but their use in a heavy duty truck is believed to be novel.
- the rear 56 of the cowl 53 adjacent the windshield, is open to the engine compartment. At operating speeds, even relatively low operating speeds, air is compressed at the base of the windshield 55 and is drawn into the engine compartment through the rear of the cowl 53 as shown at 56 .
- Air within the engine compartment 9 is expelled through air exit ducts 57 mounted on the inside walls 45 of the ducts 43 , as shown particularly in FIGS. 2-6 .
- the exit ducts 57 are in this embodiment about nine inches high and three inches wide (23 cm ⁇ 8 cm) at their mouths 59 , and are vertically centered on the inside walls 45 of the ducts 43 .
- the inside walls 45 of the ducts 43 include rectangular openings 61 into which exit ducts 57 empty.
- Each exit duct 57 includes a vertical inner wall 63 , which curves to meet the inside wall 45 at its rear, and upper and lower horizontal walls 65 which join the inner wall 63 of the exit duct to the inner wall 45 of the radiator ventilating duct 43 .
- the exit ducts 57 are entirely open to ambient, they are also in the slip stream of the hot air being forcibly expelled through the exits 46 of the radiator ventilating system 21 and in the slip stream of the truck. Therefore, air is further drawn out of the engine compartment by a venturi effect created by the flow of hot air from the plenum through the exits 46 .
- ram air represented by arrows R at the front of the heavy duty truck is directed entirely through the radiator 7 and into the radiator ventilating system 21 , while the engine compartment 9 is cooled by cowl induction air, represented by the arrows C, moving generally from the rear to the front of the engine compartment. Movement of air from back to front of the engine compartment 9 also removes heat from the area of the fire wall 14 and reduces the heat load on the cab 15 .
- guards are preferably provided over all accessible openings. Numerous such guards are well known and may include, for example, thin horizontal vanes.
- the engine compartment cooling system may include other air inlets in the top or sides of the engine compartment, including induction air systems and ram air inlets. Preferably, the air inlets are spaced away from the front of the truck. Ram air inlets in general are not presently preferred except for use in a cab-over design.
- the engine compartment cooling system may include other exhaust ports and may include powered fans of various sorts if desired.
- powered fans could be provided at the outlets of the engine compartment ventilating system.
- Many temperature-controlled systems are known or easily adapted for controlling the operation of the fans, or for moving baffles and the like.
- other motors including for example variable speed motors and, less desirably, hydraulic motors may be used to operate the squirrel cage fans; the size and number of fans may be altered as required for an application; and the shapes, numbers and sizes of the blades of the squirrel cage fan may be changed to suit the requirements of particular applications.
- Electric fan motors may be driven from different voltages, illustratively 12V to 42V.
- the bottom of the engine compartment may be enclosed for aerodynamic or internal air flow purposes. These variations are merely illustrative.
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- Transportation (AREA)
- General Engineering & Computer Science (AREA)
- Cooling, Air Intake And Gas Exhaust, And Fuel Tank Arrangements In Propulsion Units (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
A system for removing heat from the engine compartment (9) of a heavy duty truck. A first ventilating system removes heat from the radiator. It is isolated from a second ventilating system that removes heat from the engine compartment. The first system takes heat from the radiator through a plenum by centrifugal squirrel cage blowers, and is directs it out to ambient by ductwork. The second system draws ambient air generally from back to front of the engine compartment, preferably by cowl induction, without the use of ram air from the vicinity of the radiator. The exits of the two systems are into a slip stream of the heavy duty truck, and the exit of the second ventilating system is into a slip stream of the first, to scavenge air out of the engine compartment.
Description
- This application is a continuation of pending U.S. Non-Provisional application Ser. No. 14/247,069, filed Apr. 7, 2014, which is a continuation of U.S. Non-Provisional application Ser. No. 13/590,616, filed Aug. 21, 2012, now abandoned, which is a continuation of U.S. Non-Provisional application Ser. No. 12/427,400, filed Apr. 21, 2009, now U.S. Pat. No. 8,556,013 which is a continuation of U.S. Non-Provisional application Ser. No. 11/932,393, filed Oct. 31, 2007, now U.S. Pat. No. 7,537,072, and PCT/US07/83190 filed Oct. 31, 2007, and is related to and claims the benefit of U.S. Provisional Application 60/863,740, filed Oct. 31, 2006, the disclosures of all which are hereby incorporated by reference.
- Not Applicable.
- This invention relates to systems for reducing temperatures under the hood of a vehicle. It has particular, but not exclusive, application to such systems for use in a heavy duty truck, more particularly to the tractor portion of a tractor-trailer rig. Heavy duty trucks are typically over-the-road and vocational vehicles considered as weight class 4 to 8. Class 4 is generally considered to include vehicles with a gross vehicle weight of 14,001 lb to 16,000 lb (6350 kg to 7257 kg). The invention is particularly useful with weight class 6 to 8 vehicles, most particularly
class 7 to 8 vehicles. Class 6 includes vehicles with a gross vehicle weight of 19,501 lb to 26,000 lb (8846 kg to 11,793 kg).Class 7 vehicles have a gross vehicle weight of 26,001 lb to 33,000 lb (11,794 kg to 14,969 kg). - Vocational heavy duty trucks are adapted for various off-road jobs such as concrete mixer trucks, log-hauling trucks and other trucks which carry heavy loads and are required to operate over rough and uneven ground under off-road conditions. Such trucks are generally also capable of on-road highway travel.
- The internal combustion engine of a heavy duty truck produces great quantities of heat. Heat is taken from the engine block by a liquid coolant system, including a radiator spaced in front of the engine block. The heat is dissipated by natural convection, primarily by air flow caused by motion of the vehicle, and by the air which is blown through the radiator and over the engine by an axial fan. In most trucks, the axial fan is run directly from the engine crank shaft, through a clutch. In other vehicles, the fan is electric. In either, the efficiency of the fan is relatively low, frequently on the order of forty percent. This is caused in part by the natural inefficiency of the fan itself. The short distance between the fan and the engine block is also a factor; the engine block forms a natural barrier to air flow and creates a dead space between the fan and the engine block in which positive pressure tends to prevent air flow. A heavy duty truck engine may produce on the order of 1.5 million BTUs (1.6 million kilojoules) an hour at a speed of sixty miles per hour (97 km/hr), producing less than twelve miles per gallon (5 km/I) of fuel usage, and may utilize up to a thirty-two inch (0.8 m) diameter fan nominally pulling 9,500 cubic feet (270 cubic meters) per minute to disperse the heat put out by the radiator. It is estimated that roughly one-third of the output of the engine is utilized to propel the truck, one-third is in the heated exhaust (as heat and unburned fuel), and one-third must be handled by the cooling system.
- In addition to the heat carried from the engine block to the radiator by the coolant, the engine block itself radiates substantial heat, estimated to be up to about 20,000 BTUs (22,000 kJ) an hour at highway speeds.
- Recently, large diesel trucks have begun to include exhaust gas recirculation (EGR) systems. Trucks equipped with engines over 250 horsepower (186 kW) have consequently begun to experience severe under-hood heat problems. The EGR system recirculates a portion (typically about 15%-30%) of the exhaust gas to the engine air intake. Because the exhaust gas has a temperature of about 1200° F. to about 1500° F. (about 650° C. to about 815° C.), it is cooled to about 600° F. (315° C.) by running it through an EGR heat exchanger before introducing it into the cylinders of the engine. The EGR system adds about thirty percent to the cooling system heat load, about 150,000 BTUs (160,000 kJ) per hour, most of which must be dispersed by the radiator. Because much of this heat is directed back into the engine compartment, under-hood heat loads are dramatically increased. The EGR system itself also radiates heat directly into the engine compartment.
- Other auxiliary devices are run by the engine and generate further heat. For example, an air compressor is required for operation of brakes and other components. The air compressor may have a surface temperature on the order of 250° F. (121° C.).
- To meet environmental standards and to increase efficiency, a number of other devices have been added to the engine. A turbocharger, powered by the exhaust gasses, generates further heat, estimated to be on the order of 32,000 BTUs (34,000 kJ) per hour. The turbocharger may have an operating surface temperature of about 800° F. to 1200° F. (425° C. to 650° C.).
- The additional heat produced under the hood of a modern heavy duty truck has raised temperatures under the hood to unacceptable levels. The additional heat and temperature reduce the lives of components in the engine compartment and reduce engine efficiency. They sometimes melt plastic components and overheat fluids in the engine compartment. The heat also can transfer into the vehicle operator cab and can make both the air temperature in the cab and surface temperatures on the floor and front wall of the cab uncomfortably high. Attempts to enlarge the radiator, by repositioning it, tilting it, or splitting it, have not been sufficient. Enlarging the fan is likewise impractical and would increase the power requirements for running it.
- A modern heavy duty truck requires aerodynamic design considerations that sometimes make the hood design smaller. Packing more equipment in the engine compartment further makes airflow more difficult. All of these considerations require a completely new approach to under-hood air management.
- Various attempts have been made to solve somewhat similar problems with automobiles and off-highway vehicles. For example, Charles, U.S. Pat. Nos. 4,979,584 and 5,495,909 disclose an automotive engine bay ventilation system using ram air through openings around the radiator of a transverse-engine automobile. Likewise, Corwin et al., U.S. Pat. No. 6,216,778, discloses a cooling system for an off-highway vehicle which is stationary or moves at very low ground speed. These systems are not easily adaptable to the needs of a heavy duty truck.
- Briefly stated, the present invention provides a system for removing heat from the engine compartment of a vehicle by isolating heat from the radiator from the engine compartment (above and to the sides of the engine block). The invention provides a new design which separates the heat loads and provides separate exhaust exits, but allows the systems to operate together or separately as needed.
- Heat from the radiator is taken from a plenum behind the radiator, preferably by centrifugal squirrel cage blowers, and is directed out of the engine compartment, rather than against the engine block. The blowers are preferably controlled thermostatically to allow some or all of the blowers to operate as needed. The use of predictive computer control of the blowers is also contemplated.
- The engine block and its associated devices (such as the EGR valve and the turbocharger) are cooled by a separate system which draws ambient air generally from back to front of the engine compartment, preferably by cowl induction, without the use of ram air from the vicinity of the radiator.
- Both the radiator ventilating system and the engine compartment ventilating system preferably exit to ambient through side walls of the engine compartment, near the front of the engine compartment. The exits are preferably configured to exhaust hot air into the slip stream of the truck, which tends to draw air from the system. Further, the exit of the engine compartment ventilating system is preferably behind the exit of the radiator ventilating system and is configured to utilize the flow of air from the radiator ventilating system to ambient to draw air out of the engine compartment. Air flow around each exit is preferably primarily laminar.
- The systems of the invention may include one or more standard radiator, plenum and blower packages sized for particular classes of vehicles or engine sizes. It may also include a standard cowl induction system also sized for particular classes of vehicles or engine sizes. Ducting for each system, however, is likely to be dependent on particular vehicle designs, including such considerations as available space in the engine compartment, internal configuration of the engine compartment and placement of engine components inside the engine compartment affecting air flow within the engine compartment, combustion air intake configuration of the engine, and air flow patterns around the outside of the engine compartment.
- The foregoing and other objects, features, and advantages of the invention as well as presently preferred embodiments thereof will become more apparent from the reading of the following description in connection with the accompanying drawings.
- In the accompanying drawings which form part of the specification:
-
FIG. 1 is a schematic sectional view in side elevation of an internal combustion engine compartment in a heavy duty truck, modified in accordance with one embodiment of the present invention. -
FIG. 2 is a view in top plan, showing air flow through a part of an illustrative embodiment of the system ofFIG. 1 . -
FIG. 3 is a view in rear elevation, showing an illustrative radiator cooling system package of the present invention. -
FIG. 4 is a view in side elevation of the package ofFIG. 3 . -
FIG. 5 is a view in perspective of parts of the system ofFIGS. 2-4 , taken along line 5-5 ofFIG. 2 . -
FIG. 6 is a view in perspective of an engine compartment air outlet of the system ofFIGS. 2-5 . -
FIG. 7 is a schematic view in perspective showing a cowl induction scoop in accordance with an embodiment of another part of the invention. -
FIG. 8 is a view in perspective of an over-the-road truck incorporating the embodiment ofFIGS. 1-7 . - Corresponding reference numerals indicate corresponding parts throughout the several figures of the drawings.
- The following detailed description illustrates the invention by way of example and not by way of limitation. The description clearly enables one skilled in the art to make and use the invention, describes several embodiments, adaptations, variations, alternatives, and uses of the invention, including what is presently believed to be the best mode of carrying out the invention.
- As shown in the FIGURES, an internal combustion engine in a large heavy duty truck 2 (
FIGS. 1 and 8 ) includes theengine block 3,air intake 5, and aradiator 7 which cools coolant circulated from inside theengine block 3 throughpassages 8. All of these components of the engine are contained in anengine compartment 9 having a front 10 (usually at or just ahead of the radiator), a top 11, and sides 12. The top and much of the sides are generally formed as a raisable hood 13 (FIG. 8 ), which is typically hinged to the body of the truck in the area of a lower front end of the truck. At the back of theengine compartment 9, afire wall 14 separates the engine compartment from anoperator cab 15. Aturbocharger 16, exhaust piping 17, and anair compressor 19 add to the heat load in theengine compartment 9. In a conventional heavy duty truck, the heat radiated by the engine and the heat blown back into the engine compartment by an axial fan raise the temperature of the engine compartment. In recent years, an exhaust gas recirculation (EGR) system, including anEGR valve 20, adds further to the heat load on the radiator and the temperature in the engine compartment, particularly because the EGR system typically circulates on the order of 15% to on the order of 30% of the hot exhaust gas back into the engine. The total heat load in theengine compartment 9 of a modernheavy duty truck 2, other than that emitted by theradiator 7, is estimated to be about 60,000 BTUs (63,000 kJ) per hour. - This illustrative embodiment of the invention removes the axial fan and replaces it with an isolated
radiator ventilating system 21 including aplenum 23 mounted to the back of theradiator 7, preferably in sealing relationship with the radiator. Therefore, all ram air reaching theradiator 7 when the truck is in forward motion is directed through theradiator 7 and is concentrated in theplenum 23. Mounted on theplenum 23, preferably on its back, aremultiple motors 25 driving squirrel cage (centrifugal)fans 27 behind theplenum 23. Thesquirrel cage fans 27 draw heated air axially from the plenum and redirect the air 90° to discharge it outwardly (laterally) intoair ducts 43 as described hereinafter. - If desired, the back side of the
plenum 23, thefans 27, andair ducts 43 may be provided with insulating material in the form of a coating or a separate insulative layer or barrier. As indicated bybroken line 33, this arrangement effectively shields the engine, its components, and add-ons in theengine compartment 9 from the approximately 650,000 BTUs (700,000 kJ) or more per hour being dissipated to ambient by theradiator 7 when thetruck 2 is at highway speed. Exhausting the heated air in this fashion will remove the constant reinforcement of heat into the engine compartment. The problem of heat generation in the engine compartment is thus reduced to the 60,000 BTUs (63,000 kJ) per hour generated under the hood by theturbocharger 16,EGR 20,engine block 3, and other engine compartment components. - The
motors 25 are operated thermostatically, with individual motors or groups of motors being operated only when required. Predictive algorithms for controlling the operation of the coolingfans 27 will be apparent to those skilled in the art. Such algorithms may include such factors as engine coolant temperature, rate of rise of coolant temperature, engine surface or oil temperature, engine compartment temperature, ambient temperature, engine speed, and truck speed, for example. - The arrangement thus far described has the further advantages that it reduces the power (estimated to be sixty-five horsepower) required to operate a bladed fan. This could provide considerable fuel savings (7-9%). It also eliminates the fan clutch that has shown to be a high maintenance item. The electric squirrel
cage fan blowers 27 are far more efficient in removing heat from theradiator 7 than the bladed axial fan. Becauseplural fan blowers 27 are preferably provided, air flow can be stepped up and down and controlled more effectively by controlling which blowers are powered. Moreover, the fan blower's DC motor can become a generator when it is off and free wheeling from ram air, thereby charging the truck's batteries. - The isolated
radiator ventilating system 21 described thus far may be implemented in astandard package 35; a few such packages will accommodate a wide range of heavy duty trucks. Thepackage 35 may include aradiator 7, aplenum 23, and a plurality offans 27. Such a package may include aradiator 7 having a height of from about two to three feet (0.5 m to one meter) and a width of about 18″ to about 36″ (0.4 m to one meter), with aplenum 23 about one to two inches (2.5 cm to 5 cm) deep, sized to fit the back of the radiator. Thepackage 35 may be mated to a ductwork system which is tailored to a particular truck style to create both theradiator ventilating system 21 and a part of an engine compartment ventilating system. - As shown in
FIGS. 2-7 , for example, a radiator andplenum 33″ (84 cm) tall by 22″ (56 cm) wide may be provided as astandard package 35. Theradiator 7 is illustratively 6″ (15 cm) deep with aflange 36 extending around its periphery, and the plenum is 1.25″ (3 cm) deep and includes aperipheral flange 37 attached to theflange 36 of the radiator. As best seen inFIG. 3 , attached to the plenum are sixsquirrel cage fans motor squirrel cage impeller 26, and ahousing 38 having aside outlet 39. Illustratively, each fan draws 530 cfm (15 cubic meters per minute) of air, and has abrushless 3″ (7.6 cm) diameter, 3,000 rpm, 24 volt DC motor. The draws of the centrifugal fans are sized for particular applications. Thehousing 38 of eachfan 27 is about 9″ wide by about 10″ tall by about 4″ deep (22.5×25.5×10 cm), and each housing has a 4″ (10 cm)square outlet 39. It will be seen that the upperleft fan 27A and the two lowerright fans 27B′ and 27C′ have the same handedness (clockwise rotation), and that the upperright fan 27A′ and the two lowerleft fans lowermost fans outlets 39′, exiting between the exits of the two fans above them, so that all of the outlets on each side of the plenum align vertically to form a 12″ by 4″ (30×10 cm)rectangular outlet 40 on each side of the package. - As shown particularly in
FIG. 3 , eachmotor 25 is individually electrically connected to acontrol system 41 having inputs, illustratively T1 representing coolant temperature, T2 representing engine compartment temperature, RPM representing engine speed, MPG representing instantaneous or integrated fuel consumption, and MPH representing vehicle speed. These inputs permit the controller to operate thefans 27 individually or in groups in order to insure that engine temperature remains in a desired range, in accordance with algorithms which will be easily applied by those skilled in the art. In simplest form, the fans are turned on in pairs as the temperature of the coolant, represented by T1, exceeds predetermined values and turned off when T1 drops below a second value. They also permit operation of the fans in unusual circumstances when T2 exceeds a predetermined value while T1 is relatively low, to cool theengine compartment 9, as described hereinafter. Inputs RPM, MPG and MPH permit predictive operation of some or all of thefans 27, to begin drawing ram air through the radiator to provide cooling while the temperature of the coolant is still rising. The controller will also make possible the regenerative use of the fans to charge the battery of the truck when ram air is flowing through them and they are not energized. - This
radiator cooling package 35 is mated to aduct system 43. At least the rearward portion ofduct system 43 is preferably, but not necessarily, mounted on the inside of thehood 13. The juncture between the hood-mountedducts 43 and thepackage 35 may be sealed in any known manner. For example, as shown solely inFIGS. 2 and 3 , therectangular outlet 40 of thepackage 35 may terminate in acompound bevel 42 having a gasket on its open (upper) face to seal with a complementarily sloped bevel on the hood-mounted ducts. This arrangement permits unimpeded opening of thehood 13 and seals theduct system 43 to thepackage 35 when thehood 13 is closed. Alternatively, an end section of the package duct or the hood-mounted duct may be longitudinally moveable via an automatic or manual operating mechanism to mate with the other section of the duct. Likewise, the duct system may be permanently attached to the radiatorventilating system package 35 and may simply align with an opening in eachside 12 of the hood. - The
duct system 43 of this illustrative embodiment includes a curvedoutside wall 44 mated to a forward wall of theoutlet 40 and a curvedinside wall 45 mated to a rearward wall of theoutlet 40. Theoutside wall 44 terminates in a generally flat verticalrectangular opening 46 having aperipheral edge 47 aligned with a rectangular opening of similar size in theside wall 12 of the hood of the truck. It will be noted that the shape of this opening will be to some extent dictated by the contour of the truck's hood. In this embodiment, theopening 46 is substantially twelve inches (30 cm) tall, the same height as theoutlet 40 of the radiator ventilating package. Theinside wall 45 of theduct system 43 is spaced four inches from theoutside wall 44 along a curved inlet portion attached to theoutlet 40. When theinside wall 45 reaches a position opposite theopening 46, it then curves gently outward into therear edge 47 of theopening 46. The outside and insidewalls horizontal walls 48. It will be seen that thewalls radiator ventilating system 21 into the ambient slip stream of the heavy duty truck when the truck is moving forward. - To cool the
engine block 3 and its associated under-hood components in the engine compartment, a separate enginecompartment ventilating system 51 is provided. Thesecond ventilating system 51 in this illustrative embodiment is sized to remove the approximately 60,000 BTUs (63,000 kJ) per hour of heat produced in the engine compartment. In brief, the 60,000 BTUs (63,000 kJ) per hour can be effectively controlled by cowl air induction strategically located on top of the hood, using the high pressure area at the windshield to flow cool ram air into the engine compartment and causing the engine compartment air to exit through hood side ducts arranged to draw air into a low pressure area adjacent the exit of radiator fan air into ambient. As shown inFIGS. 1, 2, and 8 , the enginecompartment ventilating system 51 includes aninduction cowl 53 in front of thewindshield 55 of thetruck 2. Cowl induction systems have long been used in race cars, but their use in a heavy duty truck is believed to be novel. As is known, the rear 56 of thecowl 53, adjacent the windshield, is open to the engine compartment. At operating speeds, even relatively low operating speeds, air is compressed at the base of thewindshield 55 and is drawn into the engine compartment through the rear of thecowl 53 as shown at 56. - Air within the
engine compartment 9 is expelled throughair exit ducts 57 mounted on theinside walls 45 of theducts 43, as shown particularly inFIGS. 2-6 . As seen particularly inFIGS. 3 and 4 , theexit ducts 57 are in this embodiment about nine inches high and three inches wide (23 cm×8 cm) at theirmouths 59, and are vertically centered on theinside walls 45 of theducts 43. Theinside walls 45 of theducts 43 includerectangular openings 61 into which exitducts 57 empty. Eachexit duct 57 includes a verticalinner wall 63, which curves to meet theinside wall 45 at its rear, and upper and lowerhorizontal walls 65 which join theinner wall 63 of the exit duct to theinner wall 45 of theradiator ventilating duct 43. Although theexit ducts 57 are entirely open to ambient, they are also in the slip stream of the hot air being forcibly expelled through theexits 46 of theradiator ventilating system 21 and in the slip stream of the truck. Therefore, air is further drawn out of the engine compartment by a venturi effect created by the flow of hot air from the plenum through theexits 46. Forward movement of thetruck 2 will also create a slip stream tending to pull hot air from both theexits 46 of theducts 43 and theexits 57 from theengine compartment 9. In the unlikely circumstance that the engine compartment were to reach an undesirable temperature while thefans 27 are turned off, thefan motors 25 can be turned on to draw air through theducts 43 and suck air out of theengine compartment 9. - As shown in
FIGS. 1 and 2 , ram air represented by arrows R at the front of the heavy duty truck, is directed entirely through theradiator 7 and into theradiator ventilating system 21, while theengine compartment 9 is cooled by cowl induction air, represented by the arrows C, moving generally from the rear to the front of the engine compartment. Movement of air from back to front of theengine compartment 9 also removes heat from the area of thefire wall 14 and reduces the heat load on thecab 15. - Appropriate guards are preferably provided over all accessible openings. Numerous such guards are well known and may include, for example, thin horizontal vanes.
- Numerous variations in the vehicle under-hood temperature control system of the invention, within the scope of the appended claims, will occur to those skilled in the art in light of the foregoing disclosure. Merely by way of example, other closed systems for cooling the radiator may be provided. As previously noted, the configuration and size of the exhaust ducts will of course be varied somewhat to accommodate the geometries and engine compartments of different trucks, as exemplified in
FIG. 8 . The engine compartment cooling system may include other air inlets in the top or sides of the engine compartment, including induction air systems and ram air inlets. Preferably, the air inlets are spaced away from the front of the truck. Ram air inlets in general are not presently preferred except for use in a cab-over design. The engine compartment cooling system may include other exhaust ports and may include powered fans of various sorts if desired. For example, powered fans could be provided at the outlets of the engine compartment ventilating system. Many temperature-controlled systems are known or easily adapted for controlling the operation of the fans, or for moving baffles and the like. In the illustrative embodiment, other motors, including for example variable speed motors and, less desirably, hydraulic motors may be used to operate the squirrel cage fans; the size and number of fans may be altered as required for an application; and the shapes, numbers and sizes of the blades of the squirrel cage fan may be changed to suit the requirements of particular applications. Electric fan motors may be driven from different voltages, illustratively 12V to 42V. The bottom of the engine compartment may be enclosed for aerodynamic or internal air flow purposes. These variations are merely illustrative. - As various changes could be made in the above constructions without departing from the scope of the invention, it is intended that all matter contained in the above description or shown in the accompanying drawings shall be interpreted as illustrative and not in a limiting sense.
- All patents and patent applications mentioned herein are hereby incorporated by reference.
Claims (10)
1. A vehicle capable of on-road highway travel, the vehicle comprising an operator compartment; an engine compartment, the engine compartment being defined at least in part by a raisable hood having a top and sides; an engine in the engine compartment; a radiator, the radiator receiving coolant from the engine; a first ventilating system downstream of the radiator, the first ventilating system comprising ducting having an exhaust exit to ambient through the hood and at least one electric or hydraulic fan adapted to draw air through the radiator, through the ducting, and out the exhaust exit of the first ventilating system, the first ventilating system being constructed to prevent air drawn through the radiator from entering the engine compartment; and a second ventilating system constructed to remove heat from the engine compartment, the second ventilating system being constructed to flow ambient air into a rear part of the engine compartment and to exhaust air heated by the engine compartment out of an exhaust exit toward a forward part of the engine compartment through the hood.
2. The vehicle of claim 1 wherein the second ventilating system further comprises air induction structure on at least one of the top or sides of the engine compartment, the air induction structure being adapted to flow ambient air into the engine compartment when the vehicle is moving forward.
3. The vehicle of claim 1 wherein the exhaust exit of the second ventilating system is positioned in a low pressure area of the first ventilating system, the system being so constructed and arranged that exhaust air from the first ventilating system draws air out the exit of the second ventilating system.
4. The vehicle of claim 1 wherein the vehicle has a gross vehicle weight of at least 6350 kilograms and is capable of a highway speed of ninety-seven kilometers per hour.
5. The vehicle of claim 4 wherein the vehicle is a heavy duty truck having a gross vehicle weight of at least 11,794 kilograms.
6. The vehicle of claim 5 wherein the vehicle is a vocational heavy duty truck adapted for off-road use as well as on-road highway travel.
7. The vehicle of claim 5 wherein the vehicle is a tractor portion of a tractor-trailer over-the-road rig.
8. The vehicle of claim 1 wherein the second ventilating system comprises an air outlet in a wall of the engine compartment.
9. A vehicle capable of on-road highway travel, the vehicle comprising an operator compartment; an engine compartment; a hood defining at least a part of the engine compartment, the hood being rotatably mounted to a body of the vehicle, an engine in the engine compartment; a radiator in front of the engine, the radiator receiving coolant from the engine; a ventilating system behind the radiator, the ventilating system comprising ducting having an exhaust exit to ambient through the hood, and at least one powered fan adapted to draw air through the radiator, through the ducting, and out the exhaust exit, the ducting comprising a first section fixed with respect to the radiator and a second section attached to the hood.
10. The vehicle of claim 9 further comprising a gasket between the first section and the second section of the ducting.
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Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US10865746B2 (en) | 2018-05-29 | 2020-12-15 | Achates Power, Inc. | Opposed-piston engine in a light-duty truck |
Families Citing this family (52)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP4847073B2 (en) * | 2005-08-29 | 2011-12-28 | ヤンマー株式会社 | Tractor |
EP2011977A1 (en) * | 2006-04-04 | 2009-01-07 | Calsonic Kansei Corporation | Heat exchanger for vehicle |
DE102008021259A1 (en) * | 2008-04-29 | 2009-11-05 | Bayerische Motoren Werke Aktiengesellschaft | Motor vehicle, has bonnet limiting engine compartment on top side, where ambient air entering through inlet port is guided to lateral discharge opening formed within area of A-column of body of motor vehicle during driving |
WO2009142555A1 (en) * | 2008-05-23 | 2009-11-26 | Volvo Construction Equipment Ab | Ventilating system for ventilating an engine space in vehicle, a vehicle comprising the ventilating system and a work machine comprising the ventilating system |
US20100301638A1 (en) * | 2009-05-29 | 2010-12-02 | Hinshaw Eric J | Integrated Air Intake System |
JP5331666B2 (en) * | 2009-11-30 | 2013-10-30 | 株式会社日立製作所 | Electric vehicle cooling system |
US8622162B2 (en) * | 2009-12-11 | 2014-01-07 | Thomas Karl | Engine compartment cooling system |
JP5171888B2 (en) * | 2010-06-09 | 2013-03-27 | 日立建機株式会社 | Construction machinery |
IT1401209B1 (en) * | 2010-07-02 | 2013-07-12 | Cnh Italia Spa | CABIN FOR AGRICULTURAL VEHICLE EQUIPPED WITH A VENTILATION AND AIR-CONDITIONING SYSTEM |
US8919469B2 (en) * | 2010-08-26 | 2014-12-30 | Caterpillar Inc. | Ventilation system for engine and aftertreatment compartments and components |
JP5329519B2 (en) * | 2010-12-27 | 2013-10-30 | 日立建機株式会社 | Construction machinery |
KR101231539B1 (en) * | 2011-03-10 | 2013-02-07 | 기아자동차주식회사 | Wind Flux Concentration Guiding Device and Engine Room Layout Thereof |
US8757300B2 (en) * | 2011-03-17 | 2014-06-24 | Toyota Motor Engineering & Manufacturing North America, Inc. | Ram air generator for an automobile |
US8939733B2 (en) * | 2011-06-22 | 2015-01-27 | Caterpillar Inc. | Hydraulic fan assembly for an engine ventilation system |
US8453777B2 (en) * | 2011-10-24 | 2013-06-04 | Deere & Company | Cooling fan duct assembly |
KR20130050051A (en) * | 2011-11-07 | 2013-05-15 | 현대자동차주식회사 | Cooling apparatus for vehicle |
GB2497143B (en) | 2012-01-20 | 2014-07-30 | Jaguar Land Rover Ltd | Motor vehicle with improved air intake apparatus |
JP5948966B2 (en) * | 2012-03-01 | 2016-07-06 | コベルコ建機株式会社 | Construction machine intake structure |
CN103889756A (en) * | 2012-04-24 | 2014-06-25 | 丰田自动车株式会社 | Cooling device for vehicle |
US8960136B2 (en) | 2012-05-17 | 2015-02-24 | Spartan Motors, Inc. | Method and apparatus for managing airflow and powertrain cooling |
EP2871106A4 (en) * | 2012-07-05 | 2016-05-11 | Volvo Constr Equip Ab | Battery charging system for hybrid construction machinery by using rotational force of fan and charging method therefor |
JP5329009B1 (en) * | 2013-02-22 | 2013-10-30 | 株式会社小松製作所 | Wheel loader |
US10363811B2 (en) * | 2013-06-13 | 2019-07-30 | Ford Global Technologies, Llc | Vehicle speed controlled active grille shutter system |
JP6126954B2 (en) * | 2013-09-11 | 2017-05-10 | 本田技研工業株式会社 | Saddle riding vehicle |
US9074343B2 (en) * | 2013-09-25 | 2015-07-07 | Komatsu Ltd. | Work vehicle |
EP2899230A1 (en) | 2014-01-22 | 2015-07-29 | Solvay Specialty Polymers USA, LLC. | Automotive articles |
FR3018743B1 (en) * | 2014-03-18 | 2016-03-25 | Peugeot Citroen Automobiles Sa | AUTOMOTIVE VEHICLE AIR COOLING AIR COOLER GRILLE |
CN104039576B (en) * | 2014-03-31 | 2016-08-31 | 株式会社小松制作所 | Working truck |
JP2015217829A (en) * | 2014-05-19 | 2015-12-07 | 本田技研工業株式会社 | Vehicle cooling structure |
DE102014008477B4 (en) * | 2014-06-05 | 2019-07-04 | Liebherr-Mining Equipment Colmar Sas | Dump truck or truck with a diesel-electric traction drive, a cooling system and a hydraulic motor |
DE102014109811A1 (en) * | 2014-07-14 | 2016-01-14 | Dr. Ing. H.C. F. Porsche Aktiengesellschaft | Air guiding device for exhaust air guidance |
GB2531544A (en) * | 2014-10-21 | 2016-04-27 | Daimler Ag | Grille for a vehicle, in particular a commercial vehicle as well as a vehicle |
DE102014117007A1 (en) * | 2014-11-20 | 2016-05-25 | Valeo Klimasysteme Gmbh | Cooling module of a vehicle air conditioning system and assembly for cooling a motor vehicle engine with such a cooling module |
JP6380212B2 (en) * | 2014-12-09 | 2018-08-29 | 株式会社デンソー | Cooling device and cooling module |
US10059192B2 (en) | 2015-06-17 | 2018-08-28 | Cnh Industrial America Llc | System and method for adjusting air flow in an engine compartment of an off-road vehicle |
USD753195S1 (en) | 2015-06-17 | 2016-04-05 | Cnh Industrial America Llc | Engine hood of an agricultural vehicle |
USD765740S1 (en) | 2015-06-17 | 2016-09-06 | Cnh Industrial America Llc | Engine hood of an agricultural vehicle |
USD766340S1 (en) | 2015-06-17 | 2016-09-13 | Cnh Industrial America Llc | Engine hood of an agricultural vehicle |
KR20170005561A (en) * | 2015-07-06 | 2017-01-16 | 현대자동차주식회사 | Under cover for heat suction |
US10450939B2 (en) | 2016-04-28 | 2019-10-22 | Deere & Company | Multiple plane recirculation fan control for a cooling package |
FR3052856B1 (en) * | 2016-06-21 | 2019-06-14 | Valeo Systemes Thermiques | CIRCULATING LOOP OF A REFRIGERANT FLUID FOR A VEHICLE |
US10059330B2 (en) | 2016-09-22 | 2018-08-28 | Toyota Motor Engineering & Manufacturing North America, Inc. | Drafting detection and vehicle operation optimization system |
US9897121B1 (en) * | 2016-09-28 | 2018-02-20 | Atieva, Inc. | Automotive air intake utilizing a vortex generating airflow system |
FR3063686A1 (en) * | 2017-03-09 | 2018-09-14 | Gilbert Camara | DEVICE FOR CHANNELING AND MANAGING THE FLOW OF COOLING AIR FLOW OF A VEHICLE AND SUPPORTING ONE OR MORE EOLIANS ELECTRIC GENERATORS. |
KR102215763B1 (en) * | 2017-03-14 | 2021-02-15 | 현대자동차주식회사 | Structure of duct for cooling brake |
CN106989618A (en) * | 2017-04-26 | 2017-07-28 | 贵州理工学院 | Cooling system inside large volume goaf filling body |
US20180354355A1 (en) | 2017-06-12 | 2018-12-13 | Paccar Inc | Air ducts for airflow management, and associated systems and methods |
CN108625971A (en) * | 2018-04-28 | 2018-10-09 | 泰铂(上海)环保科技股份有限公司 | A kind of the automobile cooling device and application method of band centrifugation fan structure |
FR3096308A1 (en) * | 2019-05-24 | 2020-11-27 | Valeo Systemes Thermiques | TANGENTIAL TURBOMACHINE ELECTRIC MOTOR VEHICLE COOLING MODULE |
CN112761770A (en) * | 2019-11-06 | 2021-05-07 | 广州汽车集团股份有限公司 | Cooling device beneficial to heat dissipation of automobile engine room |
US11384680B2 (en) * | 2019-12-30 | 2022-07-12 | Woven Planet North America, Inc. | Systems and methods for automobile radiator cooling control |
CN114961961A (en) * | 2021-02-19 | 2022-08-30 | Tvs电机股份有限公司 | Cooling assembly for internal combustion engine |
Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5632673A (en) * | 1995-10-30 | 1997-05-27 | Chrysler Corporation | Ventilation system for lightweight automobile |
US5794733A (en) * | 1996-08-16 | 1998-08-18 | Volvo Gm Heavy Truck Corporation | Vehicle air intake and method |
Family Cites Families (57)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2242494A (en) | 1932-04-07 | 1941-05-20 | Austin M Wolf | Ventilating and cooling system for motor vehicles |
US3232368A (en) | 1963-10-14 | 1966-02-01 | Int Harvester Co | Motor truck body structure and mounting means therefor |
DE2133737A1 (en) * | 1971-07-07 | 1973-01-18 | Daimler Benz Ag | CAB OF COMMERCIAL VEHICLES |
AT354863B (en) * | 1975-06-13 | 1980-02-11 | List Hans | MOTOR VEHICLE WITH A SOUND INSULATING CAPSULE FOR THE ENGINE OR. THE ENGINE-GEAR UNIT |
US4235298A (en) * | 1979-02-28 | 1980-11-25 | Freightliner Corporation | Truck or truck tractor windshield air ram arrangement |
US4372409A (en) | 1980-07-28 | 1983-02-08 | Eaton Corporation | Cross-flow fan for transverse engine vehicle |
US4382481A (en) * | 1981-02-02 | 1983-05-10 | Dresser Industries, Inc. | Dual fan engine cooling system |
US4417636A (en) * | 1981-06-22 | 1983-11-29 | Eaton Corporation | Cooling fan ducting |
DE3322338A1 (en) * | 1982-07-01 | 1984-01-05 | AVL Gesellschaft für Verbrennungskraftmaschinen und Messtechnik mbH, Prof. Dr.Dr.H.C. Hans List, 8020 Graz | MOTOR VEHICLE WITH A WATER-COOLED INTERNAL COMBUSTION ENGINE AS A DRIVE ENGINE |
US4519343A (en) * | 1982-11-08 | 1985-05-28 | Aisin Seiki Kabushiki Kaisha | Engine cooling system |
DE3321804C2 (en) * | 1983-06-16 | 1987-01-29 | Daimler-Benz Ag, 7000 Stuttgart | Device for removing warm air from the engine compartment of motor vehicles |
US4726326A (en) * | 1983-09-26 | 1988-02-23 | Charles Herbert N | Drag reducing cooling system for a vehicle |
US4597463A (en) * | 1984-01-23 | 1986-07-01 | Richard Barnard | Electric vehicle using the vehicle's kinetic and mechanical power to regenerate it's energy storage device |
DE8427839U1 (en) * | 1984-09-21 | 1985-02-07 | Dr.Ing.H.C. F. Porsche Ag, 7000 Stuttgart | MOTOR VEHICLE WITH A BOW-SIDED RADIATOR ARRANGEMENT, INCLUDING FRONT AIR INLETS AND SIDE VENTILATION OPENINGS |
GB2174652A (en) * | 1985-05-09 | 1986-11-12 | Ford Motor Co | Engine cooling system |
JPS6229928U (en) * | 1985-08-08 | 1987-02-23 | ||
JPH01141163A (en) * | 1986-02-11 | 1989-06-02 | Alsthom Atlantique Sa | Ventilatign device for fluid cooling and/or rheostat of locomotive |
US4778029A (en) * | 1987-04-29 | 1988-10-18 | General Motors Coporation | Engine air inlet and silencer for motor vehicle |
JPH01111140U (en) * | 1988-01-18 | 1989-07-26 | ||
JPH07664Y2 (en) * | 1988-03-30 | 1995-01-11 | カルソニック株式会社 | Car cooling system |
JP2621044B2 (en) * | 1988-04-22 | 1997-06-18 | スズキ株式会社 | Car engine room ventilation structure |
US4846258A (en) * | 1988-06-03 | 1989-07-11 | Bendix Electronics Limited | Non-ram cooling system |
US4979584A (en) * | 1989-05-25 | 1990-12-25 | Siemens-Bendix Automotive Electronics Limited | Automotive vehicle engine bay ventilation |
US4971172A (en) * | 1989-06-30 | 1990-11-20 | Navistar International Transportation Corp. | Truck hood engine air induction system |
US5046554A (en) * | 1990-02-22 | 1991-09-10 | Calsonic International, Inc. | Cooling module |
JP3116231B2 (en) * | 1990-02-28 | 2000-12-11 | 臼井国際産業株式会社 | Radiator radiator using air duct |
US5193609A (en) * | 1990-04-19 | 1993-03-16 | Cowart Darrow W | Low profile heating and colling unit for vehicles |
US5042603A (en) * | 1990-04-23 | 1991-08-27 | Navistar International Transportation Corp. | Engine air intake apparatus |
EP0564522B1 (en) * | 1991-01-03 | 1995-08-09 | Siemens Aktiengesellschaft | Automotive vehicle engine bay ventilation by ducted-fan-operated ejector |
DE4122512A1 (en) * | 1991-05-28 | 1992-12-03 | Kloeckner Humboldt Deutz Ag | COMPACT HEAT EXCHANGER FAN UNIT |
JPH07664A (en) * | 1993-06-14 | 1995-01-06 | Hirose Mfg Co Ltd | Sewing machine part |
US5588482A (en) * | 1994-09-26 | 1996-12-31 | Ford Motor Company | Ducted cooling system for an automotive vehicle |
US5579858A (en) * | 1994-10-31 | 1996-12-03 | Ford Motor Company | Automotive air intake assembly |
US5590624A (en) * | 1995-03-31 | 1997-01-07 | Caterpillar Inc. | Engine cooling systems |
US5775450A (en) | 1996-05-06 | 1998-07-07 | General Motors Corporation | Vehicle underhood component cooling system |
US6230832B1 (en) * | 1996-09-04 | 2001-05-15 | Freightliner Llc | Truck underhood air flow management system |
US6142213A (en) * | 1997-11-25 | 2000-11-07 | Siemens Canada Limited | Ducted cooling system with radial-flow fan |
US6059061A (en) * | 1998-07-22 | 2000-05-09 | Economoff; Peter P. | Air cooling of vehicle radiators |
US6216778B1 (en) * | 1998-12-30 | 2001-04-17 | Case Corporation | Cooling system for an off-highway vehicle |
DE19950753A1 (en) * | 1999-10-21 | 2001-04-26 | Modine Mfg Co | Cooling system I |
US6401801B1 (en) * | 1999-12-10 | 2002-06-11 | Caterpillar Inc. | Twin fan cooling system |
US6463891B2 (en) | 1999-12-17 | 2002-10-15 | Caterpillar Inc. | Twin fan control system and method |
JP2002021565A (en) * | 2000-07-11 | 2002-01-23 | Komatsu Ltd | Engine enclosure for construction vehicle |
US6491502B2 (en) | 2000-08-23 | 2002-12-10 | Siemens Canada Limited | Center mounted fan module with even airflow distribution features |
DE10052331A1 (en) * | 2000-10-17 | 2002-05-02 | Stribel Gmbh | A fan installation |
US6354096B1 (en) * | 2000-10-20 | 2002-03-12 | Nicholas R. Siler | Vehicular cooling system |
DE10053146A1 (en) | 2000-10-26 | 2002-05-08 | Mann & Hummel Filter | intake system |
DE10119591A1 (en) * | 2001-04-21 | 2002-10-24 | Modine Mfg Co | Cooling system for motor vehicles |
DE10120483A1 (en) * | 2001-04-25 | 2002-10-31 | Modine Mfg Co | Arrangement for cooling |
AT5483U1 (en) * | 2001-07-02 | 2002-07-25 | Avl List Gmbh | SHUTTER FOR LOCKING OPENINGS |
EP1284343B1 (en) * | 2001-08-17 | 2008-07-30 | Behr GmbH & Co. KG | Cooling system for a motor vehicle and related motor vehicle |
US6809484B2 (en) * | 2001-09-25 | 2004-10-26 | Siemens Vdo Automotive Inc. | Multiple electronically commutated motor control apparatus and method |
US6871697B2 (en) * | 2002-01-18 | 2005-03-29 | Clark Equipment Company | Integrated fluid reservoir and heat exchanger ducts |
US6732681B1 (en) * | 2003-02-19 | 2004-05-11 | International Truck Intellectual Property Company, Llc | Modular engine cooling system with hydraulic fan drive |
JP4179088B2 (en) * | 2003-07-24 | 2008-11-12 | 株式会社デンソー | Vehicle cooling system |
US20050224267A1 (en) * | 2004-04-08 | 2005-10-13 | Callas James J | Cooling system for a vehicular engine |
US7406835B2 (en) * | 2005-05-10 | 2008-08-05 | Emp Advanced Development, Llc | Cooling system and method for cooling a heat producing system |
-
2007
- 2007-10-31 AU AU2007313695A patent/AU2007313695B2/en not_active Ceased
- 2007-10-31 RU RU2009120563/11A patent/RU2460652C2/en not_active IP Right Cessation
- 2007-10-31 US US11/932,393 patent/US7537072B2/en active Active
- 2007-10-31 CA CA2667958A patent/CA2667958C/en active Active
- 2007-10-31 BR BRPI0718255A patent/BRPI0718255B1/en not_active IP Right Cessation
- 2007-10-31 EP EP07863715.4A patent/EP2081790B1/en active Active
- 2007-10-31 KR KR1020097008839A patent/KR101422548B1/en active IP Right Grant
- 2007-10-31 WO PCT/US2007/083190 patent/WO2008055216A2/en active Application Filing
- 2007-10-31 JP JP2009535446A patent/JP5323711B2/en not_active Expired - Fee Related
- 2007-10-31 CN CN2007800408095A patent/CN101547809B/en not_active Expired - Fee Related
- 2007-10-31 MX MX2009004614A patent/MX2009004614A/en active IP Right Grant
-
2009
- 2009-04-21 US US12/427,400 patent/US8556013B2/en active Active
- 2009-04-30 ZA ZA200902997A patent/ZA200902997B/en unknown
-
2012
- 2012-08-21 US US13/590,616 patent/US20120318593A1/en not_active Abandoned
-
2014
- 2014-04-07 US US14/247,069 patent/US9470135B2/en active Active
-
2016
- 2016-10-17 US US15/295,624 patent/US20170030256A1/en not_active Abandoned
Patent Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5632673A (en) * | 1995-10-30 | 1997-05-27 | Chrysler Corporation | Ventilation system for lightweight automobile |
US5794733A (en) * | 1996-08-16 | 1998-08-18 | Volvo Gm Heavy Truck Corporation | Vehicle air intake and method |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US10865746B2 (en) | 2018-05-29 | 2020-12-15 | Achates Power, Inc. | Opposed-piston engine in a light-duty truck |
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RU2460652C2 (en) | 2012-09-10 |
US20090277706A1 (en) | 2009-11-12 |
JP5323711B2 (en) | 2013-10-23 |
BRPI0718255A2 (en) | 2014-01-21 |
US20080099261A1 (en) | 2008-05-01 |
WO2008055216A2 (en) | 2008-05-08 |
CA2667958C (en) | 2012-01-03 |
ZA200902997B (en) | 2010-03-31 |
MX2009004614A (en) | 2009-07-02 |
US8556013B2 (en) | 2013-10-15 |
RU2009120563A (en) | 2010-12-10 |
KR20090085042A (en) | 2009-08-06 |
EP2081790A2 (en) | 2009-07-29 |
JP2010508206A (en) | 2010-03-18 |
EP2081790B1 (en) | 2013-10-23 |
US9470135B2 (en) | 2016-10-18 |
US20140230759A1 (en) | 2014-08-21 |
WO2008055216A3 (en) | 2008-10-09 |
US20120318593A1 (en) | 2012-12-20 |
EP2081790A4 (en) | 2011-08-17 |
CA2667958A1 (en) | 2008-05-08 |
BRPI0718255B1 (en) | 2020-04-22 |
AU2007313695B2 (en) | 2012-07-05 |
US7537072B2 (en) | 2009-05-26 |
CN101547809B (en) | 2013-07-17 |
CN101547809A (en) | 2009-09-30 |
KR101422548B1 (en) | 2014-07-24 |
AU2007313695A1 (en) | 2008-05-08 |
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