CN101209669A - Cooling system of heat exchanger row row with strategical arrangement - Google Patents

Cooling system of heat exchanger row row with strategical arrangement Download PDF

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Publication number
CN101209669A
CN101209669A CNA2006101566943A CN200610156694A CN101209669A CN 101209669 A CN101209669 A CN 101209669A CN A2006101566943 A CNA2006101566943 A CN A2006101566943A CN 200610156694 A CN200610156694 A CN 200610156694A CN 101209669 A CN101209669 A CN 101209669A
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CN
China
Prior art keywords
heat exchanger
fluid
heat
air
pressure fluid
Prior art date
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Granted
Application number
CNA2006101566943A
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Chinese (zh)
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CN101209669B (en
Inventor
金文波
詹尼弗·艳芳·吴
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Caterpillar Inc
Original Assignee
Caterpillar R&D Center China Co Ltd
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Filing date
Publication date
Application filed by Caterpillar R&D Center China Co Ltd filed Critical Caterpillar R&D Center China Co Ltd
Priority to CN2006101566943A priority Critical patent/CN101209669B/en
Priority to RU2009129260/06A priority patent/RU2468219C2/en
Priority to PCT/CN2007/003861 priority patent/WO2008080305A1/en
Publication of CN101209669A publication Critical patent/CN101209669A/en
Application granted granted Critical
Publication of CN101209669B publication Critical patent/CN101209669B/en
Expired - Fee Related legal-status Critical Current
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/0408—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids
    • F28D1/0426—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids with units having particular arrangement relative to the large body of fluid, e.g. with interleaved units or with adjacent heat exchange units in common air flow or with units extending at an angle to each other or with units arranged around a central element
    • F28D1/0452—Combination of units extending one behind the other with units extending one beside or one above the other
    • 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
    • B60K11/02—Arrangement in connection with cooling of propulsion units with liquid cooling
    • B60K11/04—Arrangement or mounting of radiators, radiator shutters, or radiator blinds
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P3/00—Liquid cooling
    • F01P3/18—Arrangements or mounting of liquid-to-air heat-exchangers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
    • F28D1/0535—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight the conduits having a non-circular cross-section
    • F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
    • F28D1/05383—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/126—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element consisting of zig-zag shaped fins
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60Y—INDEXING SCHEME RELATING TO ASPECTS CROSS-CUTTING VEHICLE TECHNOLOGY
    • B60Y2200/00—Type of vehicle
    • B60Y2200/40—Special vehicles
    • B60Y2200/41—Construction vehicles, e.g. graders, excavators
    • B60Y2200/411—Bulldozers, Graders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P3/00—Liquid cooling
    • F01P3/18—Arrangements or mounting of liquid-to-air heat-exchangers
    • F01P2003/182—Arrangements or mounting of liquid-to-air heat-exchangers with multiple heat-exchangers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/008—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for vehicles
    • F28D2021/0082—Charged air coolers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/008—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for vehicles
    • F28D2021/0089—Oil coolers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/008—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for vehicles
    • F28D2021/0091—Radiators
    • F28D2021/0094—Radiators for recooling the engine coolant

Abstract

The invention discloses a cooling system used for machines. The cooling system is provided with a first heat exchanger and a second heat exchanger which is basically in the same plane with the first heat exchanger; the first heat exchanger is provided with a first heat dissipation quantity. The second heat exchanger is provided with a second heat dissipation quantity which is larger than the first heat dissipation quantity. The cooling system can also be provided with a third heat exchanger which is not in the same plane with the first heat exchanger and the second exchanger; the third heat exchanger is provided with inlet temperature and lower output temperature. The third heat exchanger can be arranged like this: the part of the third heat exchanger which receives the fluid at the inlet temperature can also receive the airflow which is guided into the second heat exchanger and the part of the third heat exchanger which drains the fluid at the low outlet temperature can receive the airflow which is guided into the first heat exchanger.

Description

Cooling system with heat exchanger row of tactic arrangement
Technical field
Present invention relates in general to a kind of cooling system, relate in particular to and have tactic and be arranged in multiple row with the cooling system of a plurality of heat exchangers of heat-dissipation effectively with a plurality of heat exchangers.
Background technology
Machine comprises track type tractor, wheel type loader, haul truck and other heavy construction and mining equipment, is used to various operations.In order to finish these operations, in typical case, machine includes combustion engine, as diesel engine, spark ignition engine or the dry gas engine by combustion fuel/a large amount of power of air-blending deposits yields.The a large amount of heat of this combustion process generation in order to guarantee normal, the efficient operation of driving engine, needs cooling system to come the fluid of inflow or outflow driving engine is cooled off.
For example, the common fluid of combustion engine be connected to a plurality of different liquid to air and/or air to air heat exchanger, with cooling on-cycle liquids and gases in driving engine.These heat exchangers draw close usually together and/or near driving engine to save the space on the machine.The front that is arranged on driving engine/heat exchanger assembly by engine-driven fan makes it to pass heat exchanger and driving engine with blow air, perhaps is arranged between heat exchanger and the driving engine, makes it through heat exchanger and with the blows air over driving engine with suction air.
The size and the power of driving engine export the amount of cooling water that small part depends on to be provided driving engine to.That is to say that driving engine can have maximum range of temperatures and actv. temperature range of operation, the operation of driving engine is subjected to making the restriction of capacity of the relevant heat exchanger of temperature maintenance below maximum limit and in the optimum range of driving engine.In addition, under the situation of the space constraint of given specific engines shell, the size of heat exchanger also may be restricted.Therefore, be necessary under given space constraint, to make the cooling effectiveness maximization.
It is difficult making cooling effectiveness maximization, particularly when the heat exchanger package of the heat exchanger of a plurality of driving engines and non-driving engine is fitted together.That is to say that under some structure, the cooling vessel of speed change system and/or hydraulic oil and engine heat exchanger coexistence are together to utilize the windstream that is produced by engine-driven fan.In these cases, the heat transfer of oil cooler can influence the heat transfer of the radiator of driving engine, and takies the space in the machinery space.
In given machinery space, make machine cool off No. 749 open files of patent US2004/0045749 (' that a maximized example is documented in disclosed Jaura on the 11st March in 2004 etc.) in.Should a kind of cooling system that is used for hybrid electric vehicle be described ' No. 749 open file.This cooling system comprises electric fan, air-conditioning condenser, transmission oil cooler and radiator, and all these import the windstream that electric fan produces, and electric fan is arranged in the aspirator, makes it to pass ECU electronic control unit with basic mode suction air uniformly.The cooling air flow that is produced by the electric fan of 42 volts of power drives can controllably change based on car speed and ambient air temperature, thereby realizing sufficiently cooling off thisly requires very tight Vehicular system to cooling.
Although the cooling system of ' No. 749 open file can provide sufficient cooling by a plurality of heat exchangers that series connection fits together in finite space, this cooling system lacks the required efficient of best heat radiation.That is to say, some heat exchangers, with other heat exchanger in the same assembly relatively, operate under the higher mean temperature and/or discharge and give the coolant air more heat.In this case, if the heat exchanger of higher temperature (promptly, heat exchanger with higher mean temperature and heat dissipation capacity) be arranged on the upstream of colder downstream heat exchanger, perhaps be arranged on the upstream of the colder part of downstream heat exchanger, the efficient of downstream heat exchanger may be subjected to significant adverse effect.The cooling system of ' No. 749 open file does not illustrate these situations.
Cooling system purpose of the present invention is to overcome one of foregoing problems or multinomial.
Summary of the invention
On the one hand, the present invention relates to a kind of cooling system.This cooling system comprises second heat exchanger of first heat exchanger with first heat dissipation capacity and basic and the first heat exchanger coplane.Second heat exchanger has second heat dissipation capacity greater than first heat dissipation capacity.This cooling system also can comprise and first heat exchanger and second heat exchanger coplane and have inlet temperature and the 3rd heat exchanger of low temperature out not.Described the 3rd heat exchanger can be arranged like this: the part that the reception of the 3rd heat exchanger is in the fluid of inlet temperature is configured to receive the windstream that imports described second heat exchanger, and the discharge of the 3rd heat exchanger is in the windstream that the part of hanging down the fluid of temperature out is configured to receive described first heat exchanger of importing.
On the other hand, the present invention relates to a kind of cooling method.This method comprises: the generation pressure fluid is first-class, pressure fluid second flows and pressure fluid the 3rd stream.The mean temperature of pressure fluid second stream is greater than pressure fluid five star mean temperature.The flow direction and the pressure fluid five star flow direction of pressure fluid second stream are basic identical.The direction of pressure fluid the 3rd stream is basically perpendicular to first-class and second stream of pressure fluid.This method also comprise the guiding windstream first-class from described pressure fluid, second stream and the 3rd stream take away heat.Described the 3rd flowing pressure fluid is at first cooled off by the air that also is directed with cooling fluid second stream, and then, the 3rd flowing pressure fluid cools off with cooling pressure fluid five star air by also being directed.
Description of drawings
Fig. 1 is the scheme drawing of exemplary disclosed machine;
Fig. 2 is signal and the schematic diagram that is used for the exemplary disclosed cooling system of Fig. 1 machine;
Fig. 3 is the scheme drawing that is used for the heat exchanger of Fig. 2 cooling system;
Fig. 4 is the part scheme drawing that is used for the exemplary disclosed cold sink of Fig. 3 cooling system;
Fig. 5 A and 5B are the cross sectional drawings of exemplary disclosed cold sink among Fig. 4; And
Fig. 6 is the part scheme drawing of exemplary disclosed cold sink among Fig. 4.
The specific embodiment
Fig. 1 illustrates the machine 10 with driving engine 12.Machine 10 can be carried out and for example mining industry, building industry, agricultural, generating or the relevant certain operations of any other industry known in the art.For example, machine 10 specifically can be a kind of muck haulage machine, for example bulldozer, loader, grab excavator, excavating machine, road grader, tip car or any other suitable muck haulage machine.Machine 10 also can be for example work machine of generator set, pump or another kind of form of a kind of stationary machine.
Driving engine 12 can comprise a plurality of parts, and the collaborative combustion fuel/air mixture of described a plurality of parts also produces horsepower output.Especially, driving engine 12 can comprise engine block 14, and engine block 14 comprises a plurality of cylinders 16, is slidably disposed on each cylinder 16 in-to-in piston 18 and each cylinder 16 cooresponding cylinder cover (not shown).Can expect that driving engine 12 can comprise additional or different parts, for example the corresponding air-valve assembly of each cylinder cover, one or more fuel injector and other parts well known in the art.In order to describe the present invention, driving engine 12 illustrates and is described as a kind of four stroke diesel engine.But, it will be recognized by those skilled in the art that driving engine 12 can be the combustion engine of any other type, for example gasoline or dry gas engine.
Cylinder 16, piston 18 and cylinder cover can form combustion chamber 20.In the embodiment shown, driving engine 12 comprises four combustion chambers 20.But, can expect that driving engine 12 can comprise more or less combustion chamber 20, and combustion chamber 20 can be arranged to inline type structure, " V " shape structure or any other appropriate structures.
Also illustrate as Fig. 1, driving engine 12 can include the one or more systems that machine 10 operations and driving engine 12 power are exported that are beneficial to.Especially, machine 10 can comprise driving engine 12 air air gulp system 22, driving engine 12 is operably connected to the speed change system 24 of one or more ground engagement device 26, the hydraulic executing system 28 that is installed to the operation tool 30 on the machine 10 and cooling module 32, this cooling module 32 is arranged to be used for removing the heat in driving engine 12, air gulp system 22, speed change system 24 and the hydraulic executing system 28.Can expect, driving engine 12 can comprise additional system, for example fuel system, lubricating system, brake system, a/c system, control system and the known system of other this class, these systems can be used for the heat that makes things convenient for the operation of machine and also can utilize cooling module 32 to discharge.
Air air gulp system 22 can comprise the device of supercharged air being introduced the combustion chamber 20 of driving engine 12.For example, air air gulp system 22 can comprise the one or more compressors 35 (only showing among Fig. 1) that are communicated with one or more inlet (not shown) fluids of each cylinder cover.Can expect, can comprise additional parts and/or other parts in the air air gulp system 22, for example, one or more air filters, waste gate or bypass disc, flow regulating valve, recirculation valve and other device that is used for introducing supercharged air as known in the art to combustion chamber 20.
Compressor 35 can arrive predetermined pressure stage with the air compression of inflow engine 12.Compressor 35 can be arranged in parallel, and compressor specifically can be the compressor of fixed geometry, the compressor of geometry-variable or the compressor of any other type as known in the art.Can expect that compressor also can change series connection setting into, perhaps air air gulp system 22 can only comprise a compressor 35.
Speed change system 24 comprises that mutual action is to be delivered to power the element of ground engagement device 26 from driving engine 12 in the scope of an output speed ratio.One of them element can comprise tor-con 34.Tor-con 34 can comprise for example a pair of relative hydraulic pressure impeller by the pressure oil driving, and described hydraulic pressure impeller makes driving engine 12 be connected with a mechanical stepping speed change system/step change transmission (not shown) selectivity, the part connects and/or releasing connects.Tor-con 34 can allow driving engine 12 to be independent of the speed change system rotation to a certain extent.By adjusting the oil pressure of supplying with tor-con 34, can change the independent rotation amount between driving engine 12 and the described speed change system.
Hydraulic executing system 28 comprises the fluidic component of a plurality of collaborative move operation instruments 30.Especially, hydraulic executing system 28 can comprise one or more hydraulic linear actuating mechanisms 36 that driven by pressure oil, hydraulic linear actuating mechanism 36 operation response persons' order and optionally stretch out and withdraw, thus improve and reduce operation tool 30 with respect to machine 10.Can expect, if necessary, hydraulic executing system 28 also can comprise or comprise alternatively the rotary actuating mechanism (not shown) that is used for rotary manipulation instrument 30, and/or described hydraulic actuating unit 36 can be used for operating machine 10, braking machine 10, perhaps finish other the task relevant with machine.
Cooling module 32 can comprise that common cooperation is to take away the parts of heat from driving engine 12, air gulp system 22, speed change system 24 and hydraulic executing system 28.For example, cooling module 32 can comprise coplane heat exchanger first row 38, coplane heat exchanger secondary series 40 and be arranged on driving engine 12 and first row 38, secondary series 40 between cooling fan 42.
Cooling fan 42 can be driven indirectly by driving engine 12.Especially, as shown in Figure 2, cooling fan 42 can comprise input equipment 44, for example belt-driving pulley, hydraulic drive motor or be installed to driving engine 12 or machine 10 on electrical motor and fixing or adjustable the fan blade 46 that is connected on this input equipment 44.Cooling fan 42 can make it to pass successively first row 38 and secondary series 40 to impel fan blade 46 blow air by driving engine 12 power supplies.
First row 38 can comprise two heat exchangers 48,50 with respect to the gravity direction horizontal location.Heat exchanger 48 can be vertically set on the top of heat exchanger 50, and links to each other with air air gulp system 22.For example, heat exchanger 48 can be that fluid connects with the air that is used for before inrush of air driving engine 12 cooling compressor 35 upstreams or air downstream to air after cooler (ATAAC).Windstream from compressor 35 can be vertically downward, and the inlet that passes top first side 52 of heat exchanger 48 arrives first end 54.Can change about 90 ° from the direction of intake air stream, arrive second opposed end 56 essentially horizontally to flow through heat exchanger 48, and change about 90 ° direction once more, to flow through the outlet of top first side 52 on the contrary vertically upward with the air admission direction.Top first side 52 of heat exchanger 48 can be oppositely arranged with heat exchanger 50.
Heat exchanger 48 is compared with heat exchanger 50, can have higher average running temperature, and discharge more heat.That is to say that when machine 10 was worked under specified situation, the inlet temperature of heat exchanger 48 was approximately 150 ℃, the inlet mass velocity is approximately 0.188 Kilograms Per Second.Like this, when the air themperature of cooling fan 42 discharges was approximately 40 ℃, the temperature out of heat exchanger 48 was approximately 62 ℃, discharges the heat of about 30kW.
Heat exchanger 50, concrete example such as hydraulic oil cooler (HOC) can link to each other with hydraulic executing system 28.The oily stream that flows into and/or flow out hydraulic actuating unit 36 can horizontal flow be crossed the inlet on first end 58 of heat exchanger 50, and the outlet of passing on the second opposed end 60 is flowed out.When machine 10 was worked under specified situation, the inlet temperature of heat exchanger 50 was approximately 86 ℃, and the inlet flow velocity is approximately 80L/min.Like this, when the air themperature of cooling fan 42 discharges was approximately 40 ℃, the temperature out of heat exchanger 50 was approximately 76 ℃, discharges the heat of about 20kW.
With respect to the windstream that cooling fan 42 produces, secondary series 40 is arranged on the downstream of first row 38, and secondary series 40 comprises two vertical orientated heat exchangers 62,64.Heat exchanger 62 can be configured to receive respectively the windstream from the end 56,60 of heat exchanger 48,50, and heat exchanger 64 can be configured to receive the windstream from opposite end 54,58.Similarly, the upper end of two heat exchangers 62,64 (promptly, flow into the relevant end of stream with the fluid of heat) can be configured to receive windstream from heat exchanger 48, and the lower end of two heat exchangers 62,64 (flowing out the relevant end of stream with cold fluid) can be configured to receive the windstream from heat exchanger 50.Two heat exchangers 62,64 are compared with in the heat exchanger 48,50 any one, can have higher average running temperature, and discharge more heat.
Heat exchanger 62 is specially radiator, is arranged to be used for being released in the heat of the air mixture of on-cycle water, ethylene glycol, water/ethylene glycol mixture or mixing in the driving engine 12.Cooling system conditioner from driving engine 12 can flow vertically downward, passes the inlet on top first end 66 of heat exchanger 62 along the direction substantially parallel with gravity, arrives relative bottom second end 68.
Heat exchanger 62 is compared with heat exchanger 64, can have lower average running temperature, and discharges less heat.That is to say that when machine 10 was worked under specified situation, the inlet temperature of heat exchanger 62 was approximately 99 ℃, the inlet flow velocity is approximately 250L/min.Like this, when the air themperature of cooling fan 42 discharges was approximately 40 ℃, the temperature out of heat exchanger 62 was approximately 86 ℃, discharges the heat of about 56.5kW.
Heat exchanger 64, concrete example such as torque converter oil cooler (TCOC) can link to each other with speed change system 24.The oil of inflow and/or outflow tor-con 34 flows the inlet on first end 70 that also can flow through heat exchanger 64 vertically downward, and the outlet of passing on the second opposed end 72 is flowed out.When machine 10 was worked under specified situation, the inlet temperature of heat exchanger 64 was approximately 117 ℃, and the inlet flow velocity is approximately 80L/min.Like this, when the air themperature of cooling fan 42 discharges was approximately 40 ℃, the temperature out of heat exchanger 64 was approximately 94 ℃, discharges the heat of about 61kW.
Fig. 3 illustrates the embodiment of an exemplary heat exchanger.Although it is similar that the embodiment of Fig. 3 is described as with the embodiment of heat exchanger 50, perhaps be described as a kind of hydraulic oil cooler that is connected on combustion engine and the construction machine, heat exchanger 48,62 can just in time have same or similar hardware construction with 64.It will also be appreciated that although the heat exchanger embodiments of Fig. 3 is described to the heat exchanger of a kind of air to liquid, under the situation of needs, this heat exchanger also can use in conjunction with two kinds of liquid coolants or two kinds of gaseous coolants alternatively.
The many pipelines 78 that heat exchanger 50 can comprise first end cap 74, second end cap 76, extend between first end cap 74 and second end cap 76 and between two-layer pipeline 78 a plurality of radiating gills 80 of horizontally set.Pipeline 78 can be that it passes first and second end caps 74,76 by first end 58 and extends to second end 60 by the heat-conducting metal straight fluid conduit systems of hollow basically made of aluminium, copper or corrosion-resistant steel for example.The oil that flows out from hydraulic executing system 28 can flow into the pipeline 78 on first end 58 dispersedly, and the pipeline 78 from second end 60 is assembled to turn back to hydraulic executing system 28.In one embodiment, can arrange three pipelines 78 among each coplane row.
Radiating gill 80 can be connected on the pipeline 78 with heat conduction and be arranged between two discharge pipes 78.Particularly, a plurality of radiating gills of being made by heat-conducting metal such as aluminium, copper or corrosion-resistant steel 80 can be basically perpendicular to the length direction of pipeline 78 and arrange, and be arranged between two discharge pipes 78, thereby the air that cooling fan 42 is discharged can flow and is passed in the passage that forms between two radiating gills 80.Because air flows through passage and oil flows through conduit 78, air can contact heat spreader 80 and/or the outside face of pipeline 78, discharges with the heat conduction that the oil in the pipeline 78 are carried.Empty both temperature of G﹠O and flow velocity can influence capacity of heat transmission between the two.
As shown in Figure 4, a plurality ofly be trapezoidal passage 82 substantially and can form by cold sink 80.That is to say that cold sink 80 can be seen as the separately sidewall sections of each passage 82.Each radiating gill 80 can be not parallel to the radiating gill of direct neighbor, but is parallel to radiating gill with interval, thereby can repeat to form essentially identical passage 82.In addition, each radiating gill 80 can be the passage 82a of two direct neighbors, the sidewall sections of 82b, and each among passage 82a, the 82b of direct neighbor is inverted mutually.Like this, flow through a passage for example passage 82a air can with the outside face direct contact of last discharge pipe 78, and flow through adjacency channel for example passage 82b air can with the outside face direct contact of following discharge pipe 78.
Each passage 82 can cross bending.That is to say that each passage 82 can form has similar substantially sinusoidal repetition S shape 84, repeat S shape 84 and be positioned on the horizontal transverse plane of each passage 82.In other words, first distance on the length direction of each passage 82, the symmetrical center line 86 of passage 82 can be provided with (with reference to Fig. 3) apart from first end cap, 74 first distances, and the second distance place on each passage 82 length direction, line of centers 86 can be apart from the 74 second distance settings of first end cap.
Each passage 82 can change on the length direction of each passage 82 at the width " w " at border surface 88 places of the radiating gill 80 that connects two direct neighbors.That is to say that each passage 82 can have a height dimension " h ", two adjacent radiating gills 80 are symmetrical substantially about this passage.Size " h " can keep substantially constant along the length direction of each passage 82.But the interior angle θ that forms between the radiating gill 80 of border surface 88 and direct neighbor can change.For example, the cross sectional drawing shown in Fig. 5 A illustrates on the length direction of passage 82 first distance (that is, being in the intermediate point between the sinusoidal adjacent vertex substantially), the interior angle θ that forms between the radiating gill 80 of border surface 88 and direct neighbor 1It can be the obtuse angle.Similarly, the exemplary cross section shown in Fig. 5 B illustrates on the length direction of passage 82 at the second distance place (that is, sinusoidal apex portion), the interior angle θ that forms between the radiating gill 80 of border surface 88 and direct neighbor 2It can be acute angle.That is to say the width " w at place, horizontal sinusoidal summit on the passage 82 1" can be greater than the width " w at basic intermediate point place between two summits 2".Should note, even if consider the change width of described horizontal sine curve, border surface 88 and angle θ (promptly, radiating gill 80 is with respect to the angle direction of border surface 88) alternately obtuse angle-acute nature, passage 82 is gone up the cross-sectional area at any qualifying bit place of putting along its length and the constraint that causes thus can keep substantially constant.
In alternate embodiment shown in Figure 6, passage 82 can replace with on another direction that is basically perpendicular to each passage 82 length direction crooked, perhaps except that sine curve, on another direction that is basically perpendicular to each passage 82 length direction, bending is arranged also with described horizontal orientation.That is to say that on the direction of height dimension " h ", each passage 82 can form to have and be similar to sinusoidal repetition S shape 90 substantially, this repetition S shape 90 is located in about its symmetrical vertical plane at the adjacent radiating gill 80 in any qualifying bit place of putting.In other words, first distance on each passage 82 length direction, the border surface 88 of passage 82 can be provided with (with reference to Fig. 3) apart from first discharge pipe, 78 first distances, and the second distance place on each passage 82 length direction, border surface 88 can be apart from the 78 second distance settings of first discharge pipe.
The vertical curve of each passage 82 can be discontinuous.Particularly, section 92 (being the inside and outside of border surface) of the border surface 88 at each sinusoidal concave vertex and concave crown point place can be roughly flat, and are parallel to each other basically.The length of section 92 can change, and this depends on its application, the coolant fluid that imports and pass through heat exchanger 50, the temperature and/or the flow rate of fluid of cooling system conditioner.
Industrial applicibility
Cooling system of the present invention can be used in must be with in a plurality of heat exchangers are closely assembled and high efficiency and heat radiation is the very important any machine and power system application.Especially, cooling system of the present invention can provide unique heat exchanger assembling strategy, and this strategy makes and improve radiating efficiency in limited space.System of the present invention also provides novel radiating gill to arrange that this layout is used in and makes maximum heat transfer in the heat exchanger, simultaneously the constraint minimum to flowing.The operation of explanation cooling module 32 now.
In machine 10 operational processs, various fluids, air gulp system 22, speed change system 24 and hydraulic executing system 28 in the driving engine 12 can be heated.For example, in order to cool off, engine coolant can circulate and therefrom absorb heat in the outer wall of engine block 14, cylinder 16 and/or cylinder cover.The air of compressor 35 compression can heat up because be compressed, and, when temperature with fuel mix and when burning can raise more.The pressure oil that flows through the impeller of tor-con 34 may be worked continuously, and this can make its temperature build-up.Similarly, the pressure oil that is used for move operation instrument 30 can work and be heated continuously.If do not solve, the temperature of rising may weaken validity, perhaps even cause these corresponding system et out of orders.
In order to keep the normal operating temperature of various machines and engine system, the fluid of each system can import special-purpose heat exchanger and dispel the heat.For example, the upstream of compressor 35 or air downstream can import and flow through heat exchanger 48 (ATAAC).Oil from tor-con 34 can import and flow through heat exchanger 64 (TCOC).Oil from hydraulic actuating unit 36 can import and flow through heat exchanger 50 (HOC).Cooling system conditioner from driving engine 12 can import and flow through heat exchanger 62 (radiator).When these fluids flow through their separately heat exchangers, can make cooling fan 42 rotations, at first import and pass heat exchanger 48 and 50 thereby produce, pass the windstream of heat exchanger 62 and 64 then.
Because have the heat exchanger of a row coplane heat exchanger of maximum average temperature and maximum heat dissipation capacity and the hottest part install in series of another row heat exchanger, so the efficient of cooling module 32 can be optimum.That is to say that hot air can have very big influence to cold downstream heat exchanger, but little or less at least to the downstream heat exchanger influence of heat, this is because the downstream heat exchanger of heat still and have the bigger temperature difference between the inlet air.On the contrary, when running into hot air, there is the less temperature difference between colder downstream heat exchanger and the air, gives the heat of air less thereby can discharge.
The following describes the operation of an exemplary heat exchanger.When oil flow through the pipeline 78 of heat exchanger 50, the air that cooling fan 42 is discharged can import and pass passage 82 and absorb the heat of the outside face of radiating gill 80, border surface 88 and pipeline 78.Because described horizontal sine curve (referring to Fig. 4) may cause importing the air atom and radiating gill 80 collisions of each passage 82.This collision can cause the three-dimensional motion of air atom, and this has improved the turbulent flow melange effect of heat exchanger 50.And, because the total cross-sectional area of any qualification position on the passage 82 whole length can remain unchanged, so that fluid passes the influence that the constraint of passage is subjected to is little.
As for the embodiment among Fig. 6, also can realize with Fig. 4 in the roughly the same operation of embodiment and obtain identical effect.But, compare with the embodiment of Fig. 4, as mentioned above, the sine curve of Fig. 6 can comprise par 92 at its place, summit.Since the air atom among the embodiment of Fig. 4 flows forward and with the collision of summit opposition side, particulate might reflect and leaves border surface 88 owing to the extreme angle variation of track.Par 92 can be used for weakening this extreme angle variation and reflect the possibility of leaving border surface 88, plays the heat transfer capability of raising heat exchanger 50 and/or the effect of efficient.
For one of ordinary skill in the art, without departing from the present invention, obviously can carry out various modifications and variations to cooling system of the present invention.Consider the explanation and the practice of cooling system disclosed herein, other embodiment of described cooling system is conspicuous for one of ordinary skill in the art.Should be appreciated that above-mentioned explanation and example should be regarded as merely exemplary, true scope of the present invention is defined by claims and their counterpart.
Reference numeral
10. machine 12. engines
14. engine block 16. cylinders
18. piston 20. combustion chambers
22. air suction system 24. speed change systems
26. ground engagement system 28. hydraulic executing systems
30. operation tool 32. cooling packages
34. tor-con 36. hydraulic linear actuating mechanisms
38. first row, 40. secondary series
42. cooling fan 44. input equipments
46. fan blade 48. heat exchangers (ATAAC)
50. heat exchanger (HOC) 52. tops first sides (heat exchanger 48)
54. first end (heat exchanger 48), 56. second ends (heat exchanger 48)
58. first end (heat exchanger 50), 60. second ends (heat exchanger 50)
62. heat exchanger (radiator) 64. heat exchangers (TCOC)
66. top first end (heat exchanger 62) 68. bottoms, second ends (heat exchanger 62)
70. first end (heat exchanger 64), 72. second ends (heat exchanger 64)
74. first end cap, 76. second end caps
78. pipeline 80. radiating gills
82. passage 82a passage 82b passage
84.S shape 86. line of centerss
88. border surface 90.S shape

Claims (20)

1. cooling system comprises:
First heat exchanger with first heat dissipation capacity;
Basic and the first heat exchanger coplane and second heat exchanger with second heat dissipation capacity, this second heat dissipation capacity is greater than described first heat dissipation capacity; And
With first heat exchanger and second heat exchanger coplane and have inlet temperature and the 3rd heat exchanger of low temperature out not, described the 3rd heat exchanger is arranged like this: the reception of the 3rd heat exchanger is in the part of the fluid of inlet temperature to be arranged to also receive the windstream that imports described second heat exchanger, and the discharge of the 3rd heat exchanger is in the windstream that the part of hanging down the fluid of temperature out is configured to receive described first heat exchanger of importing.
2. cooling system as claimed in claim 1 is characterized in that:
The flow through direction of described first heat exchanger of fluid is basically parallel to the flow through direction of described second heat exchanger of fluid.
3. cooling system as claimed in claim 2 is characterized in that:
The heat dissipation capacity of described the 3rd heat exchanger is less than the heat dissipation capacity of described first heat exchanger and described second heat exchanger; And
The flow through direction of described the 3rd heat exchanger of fluid is basically perpendicular to the flow through direction of described first heat exchanger and described second heat exchanger of fluid.
4. cooling system as claimed in claim 3 is characterized in that:
The flow direction of described the 3rd heat exchanger entrance fluid and outlet fluid is basically parallel to the flow through direction of described first heat exchanger and described second heat exchanger of fluid.
5. cooling system as claimed in claim 3 is characterized in that:
This cooling system also comprises the 4th heat exchanger basic and described the 3rd heat exchanger coplane, and the 4th heat exchanger heat dissipation capacity is less than the heat dissipation capacity of described the 3rd heat exchanger.
6. cooling system as claimed in claim 5 is characterized in that:
Described the 4th heat exchanger has second inlet temperature and the second low temperature out, described the 4th heat exchanger is arranged like this: the reception of the 4th heat exchanger is in the part of the fluid of second inlet temperature to be arranged to also receive the windstream that imports described second heat exchanger, and the discharge of the 4th heat exchanger is in the windstream that second part of hanging down the fluid of temperature out is configured to receive described first heat exchanger of importing.
7. cooling system as claimed in claim 6 is characterized in that:
The flow through direction of described the 4th heat exchanger of fluid is substantially consistent with the flow through direction of described the 3rd heat exchanger of fluid.
8. cooling system as claimed in claim 5 is characterized in that:
Described first heat exchanger has the 3rd inlet temperature and the 3rd low temperature out;
Described second heat exchanger has the 4th inlet temperature and the 4th low temperature out; And
Described the 3rd heat exchanger and the 4th heat exchanger are arranged like this: the part that the reception of described first and second heat exchangers is in the fluid of third and fourth inlet temperature is arranged to also receive the windstream from described the 3rd heat exchanger, and the discharge of described first and second heat exchangers part that is in the fluid of the third and fourth low temperature out is configured to receive the windstream from described the 4th heat exchanger.
9. cooling system as claimed in claim 5 is characterized in that:
Described first heat exchanger is the radiator of combustion engine; And
Described second heat exchanger is a transmission oil cooler.
10. cooling system as claimed in claim 9 is characterized in that:
Described the 3rd heat exchanger is the air cooler relevant with the air of the described combustion engine of flowing through; And
Described the 4th heat exchanger is the hydraulic executing system oil cooler.
11. cooling system as claimed in claim 5 is characterized in that:
This cooling system also comprises being configured to produce and flows through described first, second, third and the fan of the windstream of the 4th heat exchanger.
12. cooling system as claimed in claim 11 is characterized in that:
Described fan is arranged to suction air to be made it through driving engine, and with blows air over described first, second, third and the 4th heat exchanger.
13. a cooling method comprises:
The generation pressure fluid is first-class;
Produce pressure fluid second stream, the mean temperature of pressure fluid second stream is greater than pressure fluid five star mean temperature, and the flow direction and the pressure fluid five star flow direction of pressure fluid second stream are basic identical;
Generation is basically perpendicular to first-class and second pressure fluid the 3rd stream that flows of pressure fluid; And
The guiding air flows with remove described pressure fluid first, second and the 3rd stream heat;
Wherein, the pressure fluid of the 3rd stream is at first cooled off by the air that also is directed with cooling fluid second stream, then, cools off with cooling pressure fluid five star air by also being directed.
14. method as claimed in claim 13 is characterized in that, also comprises:
Produce pressure fluid the 4th stream; And
The guiding air flows is so that also take away heat from pressure fluid the 4th stream;
Wherein, the 4th flowing pressure fluid is at first cooled off by the air that also is directed with cooling fluid second stream, then, cools off with cooling pressure fluid five star air by also being directed.
15. method as claimed in claim 14 is characterized in that:
The heat of taking away from pressure fluid second stream is greater than from the first-class heat of taking away of pressure fluid.
16. method as claimed in claim 15 is characterized in that:
The heat of taking away from pressure fluid the 3rd stream is greater than the heat of taking away from pressure fluid the 4th stream.
17. method as claimed in claim 16 is characterized in that:
The mean temperature of pressure fluid second stream is higher than pressure fluid five star mean temperature; And the mean temperature of pressure fluid the 3rd stream is higher than the mean temperature of pressure fluid the 4th stream.
18. a power system comprises:
Combustion engine;
Produce the fan of windstream by internal combustion engine drive;
Be configured for the radiator of circulating coolant in driving engine, this radiator has the first average running temperature;
With the transmission oil cooler that described radiator is provided with in essentially identical plane, this transmission oil cooler has the second average running temperature that is higher than the first average running temperature;
Hydraulic oil cooler with first inlet temperature and first low temperature out, described hydraulic oil cooler is arranged like this: the reception of hydraulic oil cooler is in the part of the fluid of first inlet temperature to be arranged to also receive the windstream that imports described transmission oil cooler, and the discharge of hydraulic oil cooler is in the windstream that first part of hanging down the fluid of temperature out is configured to receive the described radiator of importing; And
With the essentially identical plane of described hydraulic oil cooler in be provided with air cooler, this air cooler has second inlet temperature and the second low temperature out, this air cooler is arranged like this: the reception of air cooler is in the part of the fluid of second inlet temperature to be arranged to also receive the windstream that imports described transmission oil cooler, and the discharge of air cooler is in the windstream that second part of hanging down the fluid of temperature out is configured to receive the described radiator of importing.
19. power system as claimed in claim 18 is characterized in that:
The direction that fluid flows through described radiator is basically parallel to the direction that fluid flows through described transmission oil cooler;
Fluid flows through the direction of described hydraulic oil cooler and direction that fluid flows through described air cooler is basically perpendicular to the direction that fluid flows through described radiator and described transmission oil cooler; And
The fluid flow direction of described air cooler entrance and exit is basically parallel to the direction that fluid flows through described radiator and described transmission oil cooler.
20. power system as claimed in claim 18 is characterized in that:
Described radiator has the 3rd inlet temperature and the 3rd low temperature out;
Described transmission oil cooler has the 4th inlet temperature and the 4th low temperature out; And
Described hydraulic oil cooler and described air cooler are arranged like this: the part that the reception of described radiator and transmission oil cooler is in the fluid of third and fourth inlet temperature is arranged to also receive the windstream from described air cooler, and the discharge of described radiator and the transmission oil cooler part that is in the fluid of the third and fourth low temperature out is configured to receive the windstream from described hydraulic oil cooler.
CN2006101566943A 2006-12-30 2006-12-30 Cooling system of heat exchanger row row with strategical arrangement Expired - Fee Related CN101209669B (en)

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CN2006101566943A CN101209669B (en) 2006-12-30 2006-12-30 Cooling system of heat exchanger row row with strategical arrangement
RU2009129260/06A RU2468219C2 (en) 2006-12-30 2007-12-28 Cooling system, cooling method and energy saving system
PCT/CN2007/003861 WO2008080305A1 (en) 2006-12-30 2007-12-28 Cooling system having strategically arranged tiers of exchangers

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CN107317557A (en) * 2017-06-22 2017-11-03 成都希塔科技有限公司 The system cooling system of high power power amplifier
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CN101209669B (en) 2012-05-16

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