CN102414413A - Engine cooling device - Google Patents
Engine cooling device Download PDFInfo
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- CN102414413A CN102414413A CN2009801589491A CN200980158949A CN102414413A CN 102414413 A CN102414413 A CN 102414413A CN 2009801589491 A CN2009801589491 A CN 2009801589491A CN 200980158949 A CN200980158949 A CN 200980158949A CN 102414413 A CN102414413 A CN 102414413A
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- 238000001816 cooling Methods 0.000 title claims abstract description 75
- 230000007246 mechanism Effects 0.000 claims description 149
- 239000003795 chemical substances by application Substances 0.000 claims description 68
- 238000005057 refrigeration Methods 0.000 claims description 68
- 239000003507 refrigerant Substances 0.000 claims description 47
- 238000012937 correction Methods 0.000 claims description 19
- 230000015572 biosynthetic process Effects 0.000 claims description 5
- 239000000498 cooling water Substances 0.000 abstract description 126
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 abstract description 125
- 239000007921 spray Substances 0.000 description 24
- 230000007704 transition Effects 0.000 description 19
- 230000007423 decrease Effects 0.000 description 17
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- 244000287680 Garcinia dulcis Species 0.000 description 9
- 238000009835 boiling Methods 0.000 description 9
- 239000002826 coolant Substances 0.000 description 9
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- 101100524639 Toxoplasma gondii ROM3 gene Proteins 0.000 description 7
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- 239000003054 catalyst Substances 0.000 description 6
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- 101100328887 Caenorhabditis elegans col-34 gene Proteins 0.000 description 3
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- 239000010970 precious metal Substances 0.000 description 3
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- 238000012545 processing Methods 0.000 description 3
- 238000002485 combustion reaction Methods 0.000 description 2
- 238000004891 communication Methods 0.000 description 2
- 238000001514 detection method Methods 0.000 description 2
- 239000000446 fuel Substances 0.000 description 2
- 238000010926 purge Methods 0.000 description 2
- 238000005507 spraying Methods 0.000 description 2
- 230000006641 stabilisation Effects 0.000 description 2
- 238000011105 stabilization Methods 0.000 description 2
- 238000004781 supercooling Methods 0.000 description 2
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- 230000008878 coupling Effects 0.000 description 1
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Images
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
- F01P7/00—Controlling of coolant flow
- F01P7/14—Controlling of coolant flow the coolant being liquid
- F01P7/16—Controlling of coolant flow the coolant being liquid by thermostatic control
- F01P7/164—Controlling of coolant flow the coolant being liquid by thermostatic control by varying pump speed
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
- F01N3/00—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust
- F01N3/02—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for cooling, or for removing solid constituents of, exhaust
- F01N3/04—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for cooling, or for removing solid constituents of, exhaust using liquids
- F01N3/043—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for cooling, or for removing solid constituents of, exhaust using liquids without contact between liquid and exhaust gases
- F01N3/046—Exhaust manifolds with cooling jacket
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
- F01P2060/00—Cooling circuits using auxiliaries
- F01P2060/08—Cabin heater
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
- F01P2060/00—Cooling circuits using auxiliaries
- F01P2060/16—Outlet manifold
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/12—Improving ICE efficiencies
Abstract
A cooling device (100A) is equipped with an ECU (1A), a water pump (10), an engine (20), a water-cooled exhaust manifold (30), and a radiator (50). A first flow rate determination means that determines the flow rate of cooling water (W) allowed to flow through the water-cooled exhaust manifold (30) when the engine (20) is operating at a steady state based on the amount of air intake (GA) by the engine (20), and a second flow rate determination means that determines the flow rate of cooling water (W) allowed to flow through the water-cooled exhaust manifold (30) when the engine (20) is in a transitional state based on cooling loss (Qw), are functionally realized by the ECU (1A).
Description
Technical field
The present invention relates to the cooling unit of motor, especially relate to the cooling unit of the motor that comprises exhaust systems cool mechanism, this exhaust systems cool mechanism utilizes the refrigeration agent that flows that engine's exhaust system is cooled off.
Background technique
In the past, known have a kind of refrigeration agents such as water technology that (particularly for example gas exhaust manifold) cools off to engine's exhaust system of utilizing.About this technology, for example in patent documentation 1, disclose a kind of technology that has relevance with the present invention of thinking.In patent documentation 1, disclose a kind of exhaust manifold device, be included in the water jacket that forms of gas exhaust manifold on every side and be the water spraying mechanism of spray form ground to this water jacket water-spraying.In addition, as thinking the technology that has relevance with the present invention, for example in patent documentation 2, disclose a kind of cooling controller of internal-combustion engine, it comprises can change the flow control valve of cooling medium for the supply ratio of a plurality of cooling parts respectively.Particularly, in patent documentation 2, disclose a kind of at the cooling controller that on the cooling water path of a plurality of cooling part guide cooling waters such as relief opening, is respectively equipped with the internal-combustion engine of flow control valve.
Patent documentation 1: japanese kokai publication sho 63-208607 communique
Patent documentation 2: TOHKEMY 2007-132313 communique
Summary of the invention
Yet, in motor, as to the countermeasure of environmental problem and pursue the minimizing exhaust emission.About this point, mainly contain when reduce light in during exhaust emission during load operation, three-way catalyst is formed the configuration near motor, and makes the method for three-way catalyst preheating in advance.
On the other hand, under the state that has used said method, in order to reduce the high capacity exhaust emission in when running, and motor is turned round near theoretical air fuel ratio or chemically correct fuel.Yet in this case, owing to dispose catalyzer near motor, and that catalyzer may take place is overheated, and the result was that acred is given birth to the deterioration that deterioration or too much deterioration cause exhaust emission.Thus, when considering the exhaust emission that reduces the high capacity operation range, three-way catalyst is configured away from motor.Yet, like this, make the minimizing of the exhaust emission in the load operation zone in catalyst warm-up light possibly become insufficient in advance, therefore need increase the amount of the precious metal of the purification that promotes catalyzer.Yet these precious metals are rare materials, and therefore increasing precious metal may increase cost.
With respect to this; According to above-mentioned situation; Further be reduced to purpose with what take into account the exhaust emission of further minimizing during that make the exhaust emission in the load operation zone in catalyst warm-up light in advance rightly, considered to utilize refrigeration agent that vent systems is cooled off and make the situation of delivery temperature decline with the high capacity running.So, can also suppress the overheated of catalyzer.Therefore like this; Can be with catalyzer near engine configurations; The further minimizing of the exhaust emission in the time of thus, can taking into account the further minimizing that makes the exhaust emission in the load operation zone in catalyst warm-up light in advance rightly and turn round with high capacity the two.
Yet when so utilizing refrigeration agent that vent systems is cooled off, from cost face grade, reasonably situation is to use and the shared refrigeration agent of refrigeration agent (for example the cooling water of motor is long-acting freezing mixture) that in engine main body, flows.
And the refrigeration agent that in engine main body, flows carries out force feed by mechanical water pump usually, and wherein this water pump is driven by the output of motor.Therefore when using with the shared refrigeration agent of the refrigeration agent that in engine main body, flows, from cost face grade, reasonably situation is to use mechanical water pump as refrigeration agent force feed device.
Yet, in this case, the problem shown in existence is following.At this, utilize under the situation about vent systems being cooled off with the shared refrigeration agent of engine main body, need refrigeration agent be maintained in proper temperature.
About this point, the refrigeration agent in engine main body, flowing carries out the cooling based on cooler (for example radiator) usually.And; For the refrigeration agent that in engine main body, flows; Usually the part of the outlet side of detection of engine main body or just flow through refrigerant temperature in the flow path after the engine main body as the refrigerant temperature of engine main body (below, be called the motor refrigerant temperature).
Therefore, when refrigeration agent is maintained in proper temperature, for example consider to regulate the situation of flow of the refrigeration agent of inflow radiator according to the motor refrigerant temperature.
Yet above-mentioned motor refrigerant temperature can't be represented refrigerant temperature in the exhaust systems cool mechanism (below, be called the vent systems refrigerant temperature).Particularly, shown in figure 21, there be the tendency of vent systems refrigerant temperature usually greater than the motor refrigerant temperature.This is because the size ratio engine main body of exhaust systems cool mechanism is little usually, so the thermal capacity of exhaust systems cool mechanism is less than the thermal capacity of engine main body.Therefore, in the exhaust systems cool mechanism in this case, refrigeration agent might take place overheated or boiling.In other words, through the motor refrigerant temperature, be difficult to hold the overheated or boiling phenomenon of the refrigeration agent in the exhaust systems cool mechanism.
But,, for example also can consider to tackle as follows about this point.At this, can know from Figure 21, the mean temperature after finishing about preheating, vent systems refrigerant temperature ratio engine refrigerant temperature exceeds approximately certain degree.Therefore about this point, for example also can consider if with the motor refrigerant temperature reset than actual detected to temperature exceed certain degree.
Yet, utilize the mechanical type water pump will with the shared refrigeration agent of engine main body when exhaust systems cool mechanism carries out force feed, the problem shown in below also existing.
At this, the spray volume of mechanical water pump rotating speed common and motor increases and decreases pro rata.Therefore when the operating condition of motor was height rotation high capacity, the flow of the refrigeration agent in the exhaust systems cool mechanism also increased.On the other hand, in this case, suck air quantity and increase, the heating value of motor increases, so the received heat that exhaust systems cool mechanism accepts from exhaust also increases.Therefore, in this case, heat can be trapped in the wall portion of the stream of the formation blast air warp in the exhaust systems cool mechanism, and consequently, this wall portion becomes high temperature.
Then, the operating condition of supposing motor is rotated the operating condition transfer of the operating condition of high capacity to low rotation high capacity from height.In this case, above-mentioned wall portion keeps the condition of high temperature during temporary transient.Yet, on the other hand, in this case, follow the decline of engine speed, and the flow of the refrigeration agent of exhaust systems cool mechanism descends.Therefore in this case, in exhaust systems cool mechanism, can take place self-purging received heat to surpass the situation of the heat dissipating capacity of refrigeration agent.That is, in this case, with respect to the heating value of motor, there is temporary transient some not enough situation in the flow of the refrigeration agent in the exhaust systems cool mechanism.
On the other hand, with respect to this,, also can't tackle the deficiency of the flow of refrigeration agent in the exhaust systems cool mechanism even for example above-mentioned that kind is regulated the flow of the refrigeration agent of inflow radiator corresponding to the motor refrigerant temperature.Therefore in this case, though the motor refrigerant temperature is reset than actual detected to temperature exceed under the situation to a certain degree, the refrigeration agent in the exhaust systems cool mechanism may remain problem in aspect overheated or boiling.
Summary of the invention
Therefore; The present invention makes in view of above-mentioned problem; Its purpose is to provide a kind of cooling unit of motor; It is comprising when utilizing the exhaust systems cool mechanism that comes engine's exhaust system is cooled off with the shared refrigeration agent of refrigeration agent that in engine main body, flows, and can prevent or suppress refrigeration agent and in exhaust systems cool mechanism, take place overheated or seethe with excitement.
Be used to solve the cooling unit that the present invention relates to a kind of motor of above-mentioned problem, comprise: refrigeration agent force feed device, the shared refrigeration agent in said refrigeration agent force feed device force feed a plurality of refrigerant cycle path; Motor, the engine main body of said motor are assembled at least one the refrigerant cycle path in said a plurality of refrigerant cycle path; Exhaust systems cool mechanism; Said exhaust systems cool mechanism is assembled at least one the refrigerant cycle path in said a plurality of refrigerant cycle path; And the refrigeration agent that utilize to flow cools off said engine's exhaust system, and the thermal capacity of the said engine main body of ratio of heat capacities of said exhaust systems cool mechanism is little; Cooler, said cooler are assembled at least one the refrigerant cycle path in said a plurality of refrigerant cycle path, and the refrigeration agent that flows is cooled off; And flow confirms mechanism, and said flow confirms that mechanism confirms to flow to the flow of the refrigeration agent of said exhaust systems cool mechanism based on the suction air quantity of said motor.
In addition, the present invention relates to a kind of cooling unit of motor, comprising: refrigeration agent force feed device, the shared refrigeration agent in said refrigeration agent force feed device force feed a plurality of refrigerant cycle path; Motor, the engine main body of said motor are assembled at least one the refrigerant cycle path in said a plurality of refrigerant cycle path; Exhaust systems cool mechanism; Said exhaust systems cool mechanism is assembled at least one the refrigerant cycle path in said a plurality of refrigerant cycle path; And the refrigeration agent that utilize to flow cools off said engine's exhaust system, and the thermal capacity of the said engine main body of ratio of heat capacities of said exhaust systems cool mechanism is little; Cooler, said cooler are assembled at least one the refrigerant cycle path in said a plurality of refrigerant cycle path, and the refrigeration agent that flows is cooled off; And flow confirms mechanism, and said flow is confirmed the received heat that mechanism accepts from exhaust in said exhaust systems cool mechanism based on refrigeration agent, confirms to flow to the flow of the refrigeration agent of said exhaust systems cool mechanism.
In addition, the present invention preferably also comprises: estimate mechanism, said estimation mechanism estimates the temperature of wall portion of the stream of the formation blast air warp in the said exhaust systems cool mechanism; And correction mechanism, said correction mechanism is revised the flow of being confirmed the refrigeration agent that mechanism confirms by said flow based on said estimation.
[invention effect]
According to the present invention; Can prevent or suppress refrigeration agent situation overheated or that seethe with excitement takes place in exhaust systems cool mechanism when utilizing the exhaust systems cool mechanism that comes engine's exhaust system is cooled off with the shared refrigeration agent of refrigeration agent that in engine main body, flows comprising.
Description of drawings
Fig. 1 is the figure of the cooling unit that schematically shows embodiment 1 motor (below, abbreviate cooling unit as) 100A.In Fig. 1; Pipe arrangement of cooling water circulating path when utilizing dotted line to represent that constituting thermostat 60 closes valve during cold conditions etc.; Pipe arrangement of cooling water circulating path when utilizing solid line to represent that constituting thermostat 60 drives valve during the temperature attitude etc., and utilize arrow to represent the flow direction of cooling water W for these.Need to prove, this situation in Fig. 5 to Figure 10 too.
Fig. 2 is the figure that schematically shows water cooled exhaust manifold 30.
Fig. 3 is the figure that is illustrated in the Flow characteristics of the cooling water W that flows in the water cooled exhaust manifold 30.
Fig. 4 is the figure that schematically shows flow varistructure 70.Dotted line is represented the state of free pulley 74 when the state of solid line is pressed into line belt 73.
Fig. 5 is the figure of the expression first cooling water circulating path 81.
Fig. 6 is the figure of the expression second cooling water circulating path 82.
Fig. 7 is the figure of expression the 3rd cooling water circulating path 83.
Fig. 8 is the figure of expression the 4th cooling water circulating path 84.
Fig. 9 is the figure of expression the 5th cooling water circulating path 85.
Figure 10 is the figure of expression the 6th cooling water circulating path 86.
Figure 11 schematically shows ECU (Electronic Control Unit: the figure of the concrete structure of 1A electric control device).
Figure 12 is expression (ethw+etha) * NE/100 * GA and the figure of the relation of actual cooling loss Qw.R
2Be the value of the relevant degree of expression, high more near the relevant degree of 1 expression more.Need to prove, this situation in Figure 14 too.
Figure 13 utilizes flow chart to represent the figure of the action of ECU1A.
Figure 14 is the figure that expression sucks air amount G A and the relation of actual cooling loss Qw.
Figure 15 schematically shows the figure of mapping (enum) data that sucks the flow correction amount of the corresponding setting of air quantity ∑ GA with accumulative total.
Figure 16 is the flow chart of the action of expression ECU1B.
Figure 17 is an example of the sequential chart corresponding with the action of ECU1B.
Figure 18 is the sequential chart of the notion of the flow control that is used to explain that ECU1B carries out.The situation that the operating condition that solid line is represented motor 20 shifts to the operating condition of low rotation and non-high capacity from the operating condition of height rotation high capacity, dotted line is represented operating condition the variation when the operating condition of low rotation high capacity shift of the operating condition of motor 20 from height rotation high capacity.
Figure 19 is provided with window and realizes visually at water cooled exhaust manifold 30, observes the situation of the cooling water W in the water cooled exhaust manifold 30 corresponding to sucking air amount G A, and has gathered the mensuration result's of the water temperature in the water cooled exhaust manifold 30 figure.
Figure 20 is the figure that schematically shows changable type Water-pump belt wheel 76 and line belt 73B.Particularly, in (a), represent the belt wheel 76 of the state of each belt wheel member 76a butt, in (b), represent the belt wheel 76 of the state that each belt wheel member 76a separates.
Figure 21 is that a example with the variation of motor refrigerant temperature behind the engine cold starting and vent systems refrigerant temperature is with the figure shown in the speed of a motor vehicle, engine speed and the throttle opening.
Embodiment
Below, with reference to accompanying drawing, explanation at length is used for the mode of embodiment of the present invention.
Use Fig. 1 to Figure 11, cooling unit 100A is described.As shown in Figure 1, cooling unit 100A comprises ECU1A, water pump 10, motor 20, water cooled exhaust manifold 30, heater core 40, radiator 50 and thermostat 60.Water pump 10 is assembled in motor 20.Water pump 10 is the mechanical pumps that utilize the output of motor 20 to drive, and is that refrigeration agent carries out force feed to cooling water W.The rotational speed N E of the spray volume of water pump 10 and motor 20 increases and decreases pro rata.
Motor 20 has engine main body 21.Engine main body 21 is made up of not shown cylinder head and cylinder block.Be formed with water jacket 22, bypass path 23, access 24 at engine main body 21.Cooling water W flows in water jacket 22, and the cooling water W that in water jacket 22, flows cools off engine main body 21.Bypass path 23 makes cooling water W flow to thermostat 60 from water jacket 22.Bypass path 23 is with the part and the external communications of the outlet side in the water jacket 22.Access 24 is with the part and the external communications of the inlet side of bypass path 23.Being provided with the temperature that detects cooling water W at engine main body 21 is the cooling-water temperature sensor 91 of coolant water temperature THW and the engine rotation speed sensor 92 that uses for the rotational speed N E of detection of engine 20.The part that cooling-water temperature sensor 91 is provided in the outlet side of water jacket 22 detects coolant water temperature THW.
Water cooled exhaust manifold 30 is assembled in engine main body 21.Water cooled exhaust manifold 30 makes the exhaust interflow of discharging from each cylinder of motor 20.As shown in Figure 2, water cooled exhaust manifold 30 comprises the outside wall portions 302 of a plurality of outlet pipes 301 of integrity ground parcel.Between outside wall portions 302 and a plurality of outlet pipe 301, be formed with the cooling water stream.In water cooled exhaust manifold 30, supply with cooling water W from cooling water introducing port 303 to the cooling water stream, and discharge cooling water W via cooling water outlet 304 from the cooling water stream.The flow of the cooling water W that in water cooled exhaust manifold 30, flows and the rotational speed N E of motor 20 increase and decrease (with reference to Fig. 3) pro rata.In the present embodiment, water cooled exhaust manifold 30 is an exhaust systems cool mechanism, and a plurality of outlet pipes 301 are the wall portion of the stream of formation blast air warp.
Turn back to Fig. 1, heater core 40 is carried out heat exchange between cooling water W and air.Heater core 40 is used in not shown aircondition.Aircondition is through bringing into play function to the indoor air-supply of the car of vehicle as heating equipment with the air after heater core 40 heating.The heat radiation of the cooling water W that radiator 50 promotes through the air-supply of moving wind or not shown electric fan to flow, and cooling water W cooled off.In the present embodiment, radiator 50 becomes cooler.Thermostat 60 is with through closing valve when the cold conditions and driving valve during in warm attitude and control the mode that flows of cooling water W and work.
Final controlling element 75 is arranged to can be along can be to the direction driving pulley 74 of line belt 73 pressurization.As above-mentioned final controlling element 75, can use for example combination that the stepping motor of straight-moving mechanism is arranged.
The action of flow varistructure 70 is described below.In motor 20 running, belt wheel 71 rotates with bent axle.The rotation of belt wheel 71 is transmitted to belt wheel 72 via line belt 73.Then, when belt wheel 72 rotations, water pump 10 drives accordingly therewith.At this moment, water pump 10 carries out force feed with the spray volume corresponding with rotational speed N E to cooling water W.
On the other hand, 75 pairs of belt wheels 74 of final controlling element drive, and belt wheel 74 are being pressed under the situation of line belt 73, and the tension force of line belt 73 raises.Shown in dotted line, when line belt 73 was pressed into by belt wheel 74, line belt 73 moved from distolateral a sideslip to the littler the other end of diameter on belt wheel 72 then.Thus, the reduced of the belt wheel 72 corresponding with line belt 73.Therefore, the rotation of water pump 10 raises, and spray volume increases.Need to prove that the spray volume of water pump 10 can reduce through making final controlling element 75 carry out opposite action.
To shown in Figure 10, cooling unit 100A has a plurality of cooling water circulating paths 81～86 of suitable with a plurality of refrigerant cycle path first to the 6th like Fig. 5.First, second and third cooling water circulating path 81,82,83 becomes the circulating path that when thermostat 60 closes valve, allows cooling water W to flow.And the 4th, the 5th and the 6th cooling water circulating path 84,85,86 becomes the circulating path that when valve left by thermostat 60, allows cooling water W to flow.Particularly, the shared cooling water W of these cooling water circulating paths of water pump 10 force feeds 81～86.In the present embodiment, water pump 10 is a refrigeration agent force feed device.
In a plurality of cooling water circulating paths 81～86, can suitably pack in water pump 10, motor 20, water cooled exhaust manifold 30, heater core 40, radiator 50 or the thermostat 60 any.And in a plurality of cooling water circulating paths 81～86, above-mentioned each structure directly or via pipe arrangement interconnects.Next, a plurality of cooling water circulating paths 81～86 more specifically are described.
Particularly, the first cooling water circulating path 81 is the water pump 10 of packing into, engine main body 21, heater core 40, thermostat 60, and according to this circulating path that cooling water W is flowed.And when in engine main body 21, flowing, particularly cooling water W flows in water jacket 22.
Particularly, the second cooling water circulating path 82 is the water pump 10 of packing into, engine main body 21, thermostat 60, and according to this circulating path that cooling water W is flowed.And when in engine main body 21, flowing, particularly, cooling water W flows in water jacket 22, bypass path 23 successively.
Particularly, the 3rd cooling water circulating path 83 is the water pump 10 of packing into, water cooled exhaust manifold 30, engine main body 21, thermostat 60, and according to this circulating path that cooling water W is flowed.And when in engine main body 21, flowing, particularly, cooling water W flows in access 24, bypass path 23 successively.
First to the 3rd flow of cooling water path 81～83 is not for comprising the circulating path of radiator 50.
Particularly, the 4th cooling water circulating path 84 is the water pump 10 of packing into, engine main body 21, heater core 40, thermostat 60, and according to this circulating path that cooling water W is flowed.And when in engine main body 21, flowing, particularly, cooling water W flows in water jacket 22.
Particularly, the 5th cooling water circulating path 85 is the water pump 10 of packing into, engine main body 21, radiator 50, thermostat 60, and according to this circulating path that cooling water W is flowed.And when in engine main body 21, flowing, particularly, cooling water W flows in water jacket 22.
Particularly, the 6th cooling water circulating path 86 is the water pump 10 of packing into, water cooled exhaust manifold 30, radiator 50, thermostat 60, and according to this circulating path that cooling water W is flowed.
And in a plurality of cooling water circulating paths 81～86 that so constitute, when valve left by thermostat 60 and when closing valve, cooling water W flows in water cooled exhaust manifold 30.Therefore, flow varistructure 70 when closing valve (in motor 20 runnings), can both appropriate change flows to the flow of the cooling water W of water cooled exhaust manifold 30 when valve left by thermostat 60.
Shown in figure 11, ECU1A comprises microcomputer and the input output loop 5,6 that is made up of CPU2, ROM3, RAM4 etc.These CPU2, ROM3, RAM4 and input output loop 5,6 connect through bus 7 each other.ECU1A constitutes major control motor 20.Particularly, ECU1A for example controls not shown Fuelinjection nozzle.And ECU1A also controls final controlling element 75.Above-mentioned controlling object is electrically connected with ECU1A.
In addition, various sensors such as cooling-water temperature sensor 91, engine rotation speed sensor 92, Air flow meter 93 (more specifically being to suck air quantity sensor 93a and inhalation temperature sensor 93b), engine load sensor 94 are electrically connected with ECU1A.And; Coolant water temperature THW is detected by ECU1A based on the output of cooling-water temperature sensor 91; Rotational speed N E is detected by ECU1A based on the output of engine rotation speed sensor 92; The suction air amount G A of motor 20 and inhalation temperature THA are detected by ECU1A based on the output of Air flow meter 93, and the aperture TA of the closure (not shown) of adjusting suction air amount G A is detected by ECU1A based on the output of engine load sensor 94.
ROM3 is the structure that is used to store program or the mapping (enum) data etc. of the performed various processing of record of CPU2.CPU2 is based on ROM3 institute program stored, utilizes the temporary storage area of RAM4 as required and carries out simultaneously and handle, thereby in ECU1A, functionally realize various control mechanisms, decision mechanism, feeler mechanism, calculate mechanism etc.
About this point; In ECU1A, for example can functionally realize feeler mechanism and estimate mechanism that a plurality of estimation factors of the suction air amount G A that comprises motor 20 detect in said feeler mechanism; Said estimation mechanism (below; Be called cooling loss and estimate mechanism) based on by the detected a plurality of estimation factors of feeler mechanism, estimate cooling loss Qw, said cooling loss Qw is the received heat that refrigeration agent is accepted from exhaust in water cooled exhaust manifold 30.
Above-mentioned a plurality of estimation factors comprise that sucking air amount G A is because suction air amount G A and cooling loss Qw have the dependency relation of high linearity.
And, above-mentioned a plurality of estimation factors preferably also comprise among coolant water temperature THW, inhalation temperature THA or the rotational speed N E as refrigerant temperature at least any.This is because these four factors are the factors that cooling loss Qw had big influence power.
Particularly, when the running environmental conditions of motors 20 such as for example original state not simultaneously, cooling loss Qw is also different.With respect to this, coolant water temperature THW and inhalation temperature THA can represent the running environmental conditions of motor 20.And if the frictional force of motor 20 increases, the heat that then produces from motor 20 increases, so also there is the tendency of increase in cooling loss Qw.With respect to this, rotational speed N E can represent the size of the frictional force of motor 20.Therefore, when estimating cooling loss Qw with higher precision, preferably also comprise among coolant water temperature THW, inhalation temperature THA or the rotational speed N E at least any.
And cooling loss Qw is most preferably based on comprising that all the following formula (1) of these four factors is estimated.
Qw=(THW+THA) * NE * GA ... Formula (1)
That is, cooling loss Qw most preferably based on through coolant water temperature THW and inhalation temperature THA with multiply by rotational speed N E, suck the value that air amount G A calculated and estimate.This be because; Operating condition comprises that the result of bench test of the motor 20 of steady state and transition state is; When estimating cooling loss Qw based on formula (1), confirmed and the cooling loss Qw of reality between have the dependency relation (with reference to Figure 12) of the highest linearity.Therefore in ECU1A, particularly, estimate cooling loss Qw based on formula (1).
In addition; In ECU1A; As the decision mechanism of the operating condition of judging motor 20, realize that functionally aperture change DeltaT A based on closure judges that the operating condition of motor 20 is steady state or the mechanism of transition state (below, be called the first operating condition decision mechanism).Particularly, the first operating condition decision mechanism is by being realized as follows: at aperture change DeltaT A is that predetermined value is judged to be steady state when following, is judged to be transition state during less than predetermined value at aperture change DeltaT A.
In addition, in ECU1A, functionally realize confirming to flow to definite mechanism (below, be called first flow and confirm mechanism) of flow of the cooling water W of water cooled exhaust manifold 30 based on sucking air amount G A.Particularly, in the present embodiment, first flow confirms that mechanism is by being realized as follows: when the operating condition of motor 20 is steady state, confirm to flow to the flow of the cooling water W of water cooled exhaust manifold 30 based on sucking air amount G A.
And, in ECU1A, functionally realize confirming to flow to definite mechanism (below, be called second flow and confirm mechanism) of flow of the cooling water W of water cooled exhaust manifold 30 based on cooling loss Qw.Particularly, second flow confirms that mechanism is by being realized as follows: when the operating condition of motor 20 is transition state, estimate that based on cooling loss the estimated cooling loss Qw that goes out of mechanism confirms to flow to the flow of the cooling water W of water cooled exhaust manifold 30.
In addition, in ECU1A, functionally realize carrying out the control mechanism (below, be called flow control mechanism) of the flow control of cooling water W.Particularly; Flow control mechanism is by being realized as follows: flow varistructure 70 (particularly being final controlling element 75) as controlling object, is become first or second flow with the flow control of the cooling water W that flows to water cooled exhaust manifold 30 and confirms the determined flow of mechanism.Need to prove,, can confirm to reach the flow of control flows simultaneously to the cooling water W of water cooled exhaust manifold 30 through confirming to reach the spray volume of control of pump 10.
Next, use flow chart shown in Figure 13 that the action of ECU1A is described.Need to prove that this flow process is carried out with the extremely short time lag repeatedly in motor 20 runnings.ECU1A detects throttle opening TA, and calculates throttle opening change DeltaT A (step S1).Next, ECU1A judges that the aperture change DeltaT A calculate is whether below predetermined value (step S2).If step S2 is for judging that certainly the operating condition that then is judged to be motor 20 is a steady state.At this moment, ECU1A detects and sucks air amount G A (step S3).
Next, ECU1A confirms the spray volume (step S4) of water pump 10 based on detected suction air amount G A.At this moment, particularly, ECU1A confirms the spray volume of water pump 10 based on the cooling water flow flow characteristic corresponding with sucking air amount G A (below, be called the first cooling water flow flow characteristic).Next, ECU1A controls final controlling element 75, and the spray volume of water pump 10 is changed into determined spray volume (step S8).After step S8, temporary transient process ends.
On the other hand, if judge that for negative the operating condition that then is judged to be motor 20 is a transition state at step S2.At this moment, ECU1A detects coolant water temperature THW, inhalation temperature THA, rotational speed N E and sucks air amount G A (step S5).Next, ECU1A calculates (estimation) cooling loss Qw (step S6) based on formula (1).Then, ECU1A confirms the spray volume (step S7) of water pump 10 based on the cooling loss Qw that calculates.At this moment, particularly, ECU1A confirms the spray volume of water pump 10 based on the cooling water flow flow characteristic corresponding with cooling loss Qw (below, be called the second cooling water flow flow characteristic).After step S7, S8 advances to step.
Yet the first above-mentioned cooling water flow flow characteristic is defined by the mapping (enum) data that is stored in advance among the ROM3.And, in this mapping (enum) data, set and suck the spray volume of water pump 10 for air amount G A and increase and decrease pro rata.And the flow that will flow to the cooling water W of water cooled exhaust manifold 30 is thus simultaneously also set and is sucked air amount G A for and increases and decreases pro rata.
Likewise, the second above-mentioned cooling water flow flow characteristic is defined by the mapping (enum) data that is stored in advance among the ROM3.And, in this mapping (enum) data, the spray volume of water pump 10 set for cooling loss Qw increase and decrease pro rata.And the flow that will flow to the cooling water W of water cooled exhaust manifold 30 is thus simultaneously also set for cooling loss Qw and is increased and decreased pro rata.
First and second cooling water flow flow characteristic for example is ready for use on when the cold conditions of switching whenever the nowed forming that carries out cooling water W between a plurality of cooling water circulating paths 81～86 and during warm attitude.And, even under the situation that the nowed forming that carries out cooling water W switches, also can utilize flow varistructure 70 to carry out more suitable flow control.
Next, the action effect of cooling unit 100A is described.At this, in order to prevent or to suppress cooling water W overheated in the water cooled exhaust manifold 30, and when change flows to the flow of cooling water W of water cooled exhaust manifold 30, for example also can consider to make the flow increase and decrease pro rata with rotational speed N E.Yet, when the operating condition of motor 20 is steady state, suck the dependency relation (with reference to Figure 14) that air amount G A and actual cooling loss Qw have high linearity.And, consider from the viewpoint of the heating value of motor 20, the cooling water flow flow characteristic we can say preferably can with make the characteristic of the flow increase and decrease of cooling water W pro rata with air displacement suction air amount G A about equally.
With respect to this, in cooling unit 100A, when stablizing, ECU1A confirms and changes the spray volume (in other words, flowing to the flow of the cooling water W of water cooled exhaust manifold 30) of water pump 10 based on the first cooling water flow flow characteristic.That is, in cooling unit 100A,, can both when heating value is big more, more suitably increase the flow of the cooling water W that flows to water cooled exhaust manifold 30 according to the heating value of the motor that is in steady state 20 regardless of rotational speed N E and delivery temperature.Therefore, cooling unit 100A when stablizing, can suitably prevent or suppress cooling water W in water cooled exhaust manifold 30, take place overheated or the boiling situation.More particularly, can prevent or suppress thus the decline of the exhaust cooling effectiveness of water cooled exhaust manifold 30 for example, because of durability or the decline of reliability and the situation that deterioration takes place cooling water W of the water cooled exhaust manifold 30 that thermal distortion causes take place.
On the other hand, when the operating condition of motor 20 was transition state, the difference of the change of ignition timing or the operating condition before transition state shifts can impact the heating value of motor 20.With respect to this, shown in figure 12, when transition, have the dependency relation of high linearity based on the cooling loss Qw and the actual cooling loss Qw of formula (1).And in cooling unit 100A, when transition, ECU1A confirms and changes the spray volume (in other words, flowing to the flow of the cooling water W of water cooled exhaust manifold 30) of water pump 10 based on the second cooling water flow flow characteristic.That is, in cooling unit 100A, can when heating value is big more, more suitably increase the flow of the cooling water W that flows to water cooled exhaust manifold 30 according to the heating value of motor in an interim state 20.Therefore cooling unit 100A also can suitably prevent or suppress cooling water W situation overheated or that seethe with excitement takes place in water cooled exhaust manifold 30 when transition.
And cooling unit 100A comprises flow varistructure 70.Even therefore cooling unit 100A is when utilizing 10 couples of cooling water W of mechanical water pump to carry out force feed, also can change the flow of the cooling water W that in water cooled exhaust manifold 30, flows.
Need to prove, when in transition, prevent or when suppressing cooling water W overheated in the water cooled exhaust manifold 30, also can consider for example to set the flow of the cooling water W that the maximum heating value with motor 20 matches.Yet in this case, when the smaller transition of heating value, it is big that the flow of cooling water W can unnecessarily become.Therefore in this case, water cooled exhaust manifold 30 sinks into the supercooling state, consequently, might cause bad influence to the oil consumption rate of motor 20, the durability and the reliability of water cooled exhaust manifold 30.With respect to this, in cooling unit 100A, ECU1A changes the flow of cooling water W according to the heating value of motor in an interim state 20.Therefore, cooling unit 100A also can prevent or suppress water cooled exhaust manifold 30 and sink into above-mentioned supercooling state.
The cooling unit 100B of present embodiment comprises the point of ECU1B except replacing ECU1A, and is identical in fact with cooling unit 100A.And ECU1B is except also functionally realizing decision mechanism, estimate the point of mechanism and correction mechanism shown in following, and is identical in fact with ECU1A.Therefore omit diagram cooling unit 100B and ECU1B in the present embodiment.
In ECU1B,, functionally realize judging that based on sucking air amount G A whether the operating condition of motor 20 is the mechanism (below, be called the second operating condition decision mechanism) of high rotation high capacity as the decision mechanism of the operating condition of judging motor 20.Particularly, the second operating condition decision mechanism is by being realized as follows: sucking air amount G A is that predetermined value is judged to be high rotation high capacity when above, when sucking air amount G A less than predetermined value, is judged to be not to be high rotation high capacity.
In addition, in ECU1B, the estimation mechanism of the temperature of the wall portion (particularly being a plurality of outlet pipes 301) of the stream of the formation blast air warp in the water cooled exhaust manifold 30 of realization estimation functionally (below, be called wall portion temperature and estimate mechanism).In the present embodiment, particularly, wall portion temperature estimates that mechanism is realized as follows: when the operating condition of motor 20 was rotated high capacity for height, being estimated as wall portion was high temperature.
In addition; In ECU1B; Functionally realize estimating that based on wall portion temperature the estimation of mechanism comes first or second flow is confirmed the correction mechanism that in the mechanism and operating condition corresponding flow motor 20 confirm the spray volume of the determined water pump 10 of mechanism and revise (below, be called flow correction mechanism).About this point, can revise the flow of the cooling water W that flows to water cooled exhaust manifold 30 simultaneously through the spray volume of revising water pump 10.
Particularly, flow correction mechanism realizes with being described below.That is, when being high temperature in wall portion, flow correction mechanism sucks air quantity ∑ GA through suction air amount G A is added up to calculate accumulative total.Then, the accumulative total that adds and calculate in the spray volume of the water pump 10 of the corresponding cooling water flow flow characteristic of the operating condition with motor 20 of flow correction mechanism in being set at the first or second cooling water flow flow characteristic sucks air quantity ∑ GA corresponding flow reduction value.
In addition, when the temperature of wall portion was not high temperature, flow correction mechanism deducted current suction air amount G A through sucking air quantity ∑ GA from accumulative total, sucks air quantity ∑ GA and upgrade accumulative total.Then; It is predetermined value (for example zero) when above that the accumulative total of flow correction mechanism after renewal sucks air quantity ∑ GA, adds and totally suck air quantity ∑ GA corresponding flow reduction value in the flow of the cooling water W of the cooling water flow flow characteristic that the operating condition with motor 20 in being set at the first or second cooling water flow flow characteristic is corresponding.
Particularly, shown in figure 15, the accumulative total that the flow correction amount is set in the mapping (enum) data that is stored in ROM3 in advance corresponding to high load area sucks air quantity ∑ GA, and increases and decreases proportionally.
Next, utilize flow chart shown in Figure 16,, the action of ECU1B is described with reference to sequential chart shown in Figure 17.Shown in figure 16, ECU1B at first detects and sucks air amount G A (step S11).Next, ECU1B judges whether detected suction air amount G A is predetermined value above (step S12), and said predetermined value is the decision threshold that high capacity is judged.If step S12 is for judge certainly, the operating condition that then is judged to be motor 20 is high rotation high capacity.And, if step S12 is for judging that certainly then being estimated as wall portion is high temperature.At this moment, ECU1B forms ON (step S13) with the high capacity determination flag.In Figure 17, the state of time T 1 is corresponding to the state of this moment.
Next, ECU1B adds up detected suction air amount G A, calculates accumulative total and sucks air quantity ∑ GA (step 14).Then, add in the spray volume of the water pump 10 of the corresponding cooling water flow flow characteristic of the operating condition with motor 20 of ECU1B in being set at the first or second cooling water flow flow characteristic with accumulative total and suck air quantity ∑ GA corresponding flow reduction value (step S15).After step S15, temporary transient process ends.And for during before negate judging, ECU1B is the processing shown in the execution in step S11 to S15 repeatedly at step S12.
On the other hand, if step S12 is for negating to judge, the operating condition that then is judged to be motor 20 is not high rotation high capacity.And if step S12 is for negating judgement, then being judged to be wall portion is not high temperature.At this moment, ECU1B forms OFF (step S16) with the high capacity determination flag.In Figure 17, the state of time T 2 is corresponding to the state of this moment.Next ECU1B sucks air quantity ∑ GA from accumulative total and deducts current suction air amount G A, upgrades (step S17) and accumulative total is sucked air quantity ∑ GA.ECU1B judges whether the accumulative total of calculating sucks air quantity ∑ GA is more than the predetermined value (is zero at this) (step S18) then.
When at step S18 when judging certainly, S15 advances to step.And during before step S18 is negative judgement, ECU1B carries out above-mentioned processing repeatedly.On the other hand, when judging certainly, ECU1B sucks air quantity ∑ GA reset (step S19) to accumulative total at step S18.In Figure 17, time T 3 is corresponding to the state of this moment.And through a series of action so far, the flow correction amount increases the corresponding amount of area that sucks air quantity ∑ GA with illustrated accumulative total.
Next, the action effect of cooling unit 100B is described.At this, suppose that the operating condition of motor 20 is changed to the operating condition of low rotation from the operating condition of height rotation high capacity.In this case, shown in figure 18, rotational speed N E descends, and sucks air amount G A (being the heating value of motor 20) decline.Yet, because next self-purging being heated during high rotation high capacity and heat is trapped in the wall portion of water cooled exhaust manifold 30.And especially the operating condition of motor 20 is when the operating condition of height rotation high capacity changes to the operating condition of low rotation high capacity, and shown in the dotted line among Figure 18, the temperature of the wall portion of water cooled exhaust manifold 30 temporarily remains high state.
On the other hand, in this case, owing to the decline along with rotational speed N E of the flow of cooling water W descends, so the cooling capacity of water cooled exhaust manifold 30 descends.Therefore in this case, only utilize the flow definite not enough for cooling, thereby cooling water W might take place overheated or boiling in water cooled exhaust manifold 30 based on sucking air amount G A or cooling loss Qw.Particularly, shown in figure 19, can form that high temperatureization takes place cooling water W and can confirm the state of boiling phenomenon in the part.And in this case; Particularly, can take place for example the to seethe with excitement deterioration of cooling water W of decline or boiling of durability and reliability of decline, the caused water cooled exhaust manifold 30 of thermal distortion that produces because of the temperature difference of each several part of exhaust cooling effectiveness of the water cooled exhaust manifold 30 on the position.
With respect to this; In cooling unit 100B, add in the spray volume of the water pump 10 of the cooling water flow flow characteristic that the operating condition with motor 20 of ECU1B in being set at the first or second cooling water flow flow characteristic is corresponding with accumulative total to suck air quantity ∑ GA corresponding flow reduction value.Thus, can further be increased in the flow of the cooling water W that flows in the water cooled exhaust manifold 30.Therefore, can carry out suitable cooling to the wall portion of the water cooled exhaust manifold 30 of the state that temporarily remains high temperature.Even therefore the operating condition at motor 20 is to hang down under the situation of the operating condition of rotation high capacity from the operating condition transfer of height rotation high capacity again, cooling unit 100B also can suitably prevent or suppress cooling water W and in water cooled exhaust manifold 30, take place overheated or boiling.
The above embodiments are preferred embodiments of the present invention.But, be not defined in this, in the scope that does not break away from aim of the present invention, can carry out various distortion and implement.
For example in the above embodiments, the situation of flow varistructure 70 as the flow changeable mechanism that comprise has been described.Yet the present invention is not limited thereto, and the flow changeable mechanism also can be other the suitable structure that can change the flow of refrigeration agent.
About this point, particularly, the flow changeable mechanism also can be realized through changable type Water-pump belt wheel 76 for example shown in Figure 20.This belt wheel 76 can replace belt wheel 72 to be used.In this case, do not need free pulley 74 to be used to regulate the tension force of line belt 73, and do not need final controlling element 75.
Belt wheel 76 comprises a pair of belt wheel member 76a of circular cone shape.It can be center and with the structure that is separated from each other, approaching mode drives each belt wheel member 76a with axial central authorities that belt wheel 76 has.Line belt 73 hangs on the belt wheel 76 with the mode that hangs over equably on each belt wheel member 76a.Belt wheel 76 is hydraulic drive types, replaces final controlling element 75 and uses as controlling object, thereby under the control of ECU1A, can drive each belt wheel member 76a through switching hydraulic pressure.
Shown in Figure 20 (a), the fixed position of each belt wheel member 76a becomes the position of the mutual butt of each belt wheel member 76a.And, shown in Figure 20 (b), when the direction that is separated from each other drives each belt wheel member 76a, follow in this, dwindled on belt wheel 76 with line belt 73 corresponding diameters.Therefore, can improve the rotation and the increase spray volume of water pump 10.And through making belt wheel 76 counteragents, and can reduce the spray volume of water pump 10.Even and comprise above-mentioned belt wheel 76 as the flow changeable mechanism, also can when utilizing 10 couples of cooling water W of mechanical water pump to carry out force feed, change the flow of cooling water W.
In addition; In the above embodiments; Situation to following is illustrated: because high with the dependency relation of the cooling loss Qw of reality; The aspect that can carry out more suitable flow control is preferred, therefore when stablizing, utilizes first flow to confirm that mechanism confirms flow, when transition, utilizes second flow to confirm that mechanism confirms flow.
Yet, be not limited thereto in the present invention, for example when stablizing and during transition, flow confirms that mechanism can be that first flow confirms that the mechanism or second flow confirm that the arbitrary flow in the mechanism confirms mechanism.In this case, can realize the simplification controlled.And in this case; In the time of can preventing to stablize and under the situation of in the relatively shorter time, carrying out repeatedly during transition; Confirm that through first flow the mechanism and second flow confirm that mechanism interimly changes the situation of flow repeatedly; Thus, can realize raising and the stabilization of control of the reliability of flow changeable mechanism.
In addition, in the present invention, for example both can when stablizing, utilize first flow to confirm that mechanism confirms flow at least, and also can when transition, utilize second flow to confirm that mechanism confirms flow at least.
In addition; First or second flow confirms that the arbitrary flow in the mechanism confirms that mechanism confirms under the situation of flow when stablizing and during transition; Integral body can carry out more suitable flow control aspect, more preferably confirm that based on the received heat of exhaust systems cool mechanism second flow of flow confirms mechanism.
In addition, first flow confirms that the mechanism or second flow confirm that arbitrary flow in the mechanism confirms that mechanism confirms under the situation of flow when stablizing and during transition, and correction mechanism can confirm that the determined flow of mechanism revises to this flow.
In addition; Confirm that mechanism confirms flow and when transition, utilizes second flow to confirm that mechanism confirms under the situation of flow even when stablizing, utilize first flow; Correction mechanism also can utilize first or second flow to confirm that the arbitrary flow in the mechanism confirms that mechanism's (for example second flow is confirmed mechanism) confirms flow when modified flow rate.In this case, can realize raising and the stabilization of control of the reliability of flow changeable mechanism.
In addition, in the above embodiments, because therefore refrigeration agent force feed device preferred mechanical formula water pump 10 has explained above-mentioned situation.Yet the present invention is not limited thereto, is under the situation of electric water pump at for example refrigeration agent force feed device, also can suitably prevent or suppress refrigeration agent through suitable the present invention situation overheated or boiling takes place in the exhaust cooling mechanism.
In addition, explained that in the above embodiments exhaust systems cool mechanism is the situation of water cooled exhaust manifold 30.Yet the present invention is not limited thereto, exhaust systems cool mechanism also can be the refrigeration agent that utilize to flow cool off engine's exhaust system other suitable structure.About this point, exhaust systems cool mechanism also can be through for example being provided with between gas exhaust manifold and the motor and the coupling that they are connected realized.
In addition; Though various mechanisms such as flow is confirmed mechanism, estimated mechanism, correction mechanism mainly realize it being reasonably by the ECU1 of control motor 20, for example also can realize through hardware such as other electric control device, special-purpose circuit or their combination.About this point, various mechanisms such as flow is confirmed mechanism, estimated mechanism, correction mechanism also can be for example combination through hardware such as a plurality of electric control devices, a plurality of circuit or hardware such as electric control device and circuit realize with the mode of decentralized control.
[symbol description]
1?ECU
10 water pumps
20 motors
30 water cooled exhaust manifolds
301 outlet pipes
40 heater core
50 radiators
60 thermostats
100 cooling units
Claims (3)
1. the cooling unit of a motor comprises:
Refrigeration agent force feed device, the shared refrigeration agent in said refrigeration agent force feed device force feed a plurality of refrigerant cycle path;
Motor, the engine main body of said motor are assembled at least one the refrigerant cycle path in said a plurality of refrigerant cycle path;
Exhaust systems cool mechanism; Said exhaust systems cool mechanism is assembled at least one the refrigerant cycle path in said a plurality of refrigerant cycle path; And the refrigeration agent that utilize to flow cools off said engine's exhaust system, and the thermal capacity of the said engine main body of ratio of heat capacities of said exhaust systems cool mechanism is little;
Cooler, said cooler are assembled at least one the refrigerant cycle path in said a plurality of refrigerant cycle path, and the refrigeration agent that flows is cooled off; And
Flow is confirmed mechanism, and said flow confirms that mechanism confirms to flow to the flow of the refrigeration agent of said exhaust systems cool mechanism based on the suction air quantity of said motor.
2. the cooling unit of a motor comprises:
Refrigeration agent force feed device, the shared refrigeration agent in said refrigeration agent force feed device force feed a plurality of refrigerant cycle path;
Motor, the engine main body of said motor are assembled at least one the refrigerant cycle path in said a plurality of refrigerant cycle path;
Exhaust systems cool mechanism; Said exhaust systems cool mechanism is assembled at least one the refrigerant cycle path in said a plurality of refrigerant cycle path; And the refrigeration agent that utilize to flow cools off said engine's exhaust system, and the thermal capacity of the said engine main body of ratio of heat capacities of said exhaust systems cool mechanism is little;
Cooler, said cooler are assembled at least one the refrigerant cycle path in said a plurality of refrigerant cycle path, and the refrigeration agent that flows is cooled off; And
Flow is confirmed mechanism, and said flow is confirmed the received heat that mechanism accepts from exhaust in said exhaust systems cool mechanism based on refrigeration agent, confirms to flow to the flow of the refrigeration agent of said exhaust systems cool mechanism.
3. the cooling unit of motor according to claim 1 and 2 also comprises:
Estimate mechanism, said estimation mechanism estimates the temperature of wall portion of the stream of the formation blast air warp in the said exhaust systems cool mechanism; And
Correction mechanism, said correction mechanism are revised the flow of being confirmed the refrigeration agent that mechanism confirms by said flow based on said estimation.
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| PCT/JP2009/058657 WO2010128549A1 (en) | 2009-05-08 | 2009-05-08 | Engine cooling device |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN102414413A true CN102414413A (en) | 2012-04-11 |
Family
ID=43050062
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2009801589491A Pending CN102414413A (en) | 2009-05-08 | 2009-05-08 | Engine cooling device |
Country Status (4)
| Country | Link |
|---|---|
| US (1) | US20120047893A1 (en) |
| JP (1) | JP5196014B2 (en) |
| CN (1) | CN102414413A (en) |
| WO (1) | WO2010128549A1 (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2013007338A (en) * | 2011-06-24 | 2013-01-10 | Toyota Motor Corp | Cooling water circulating device for internal combustion engine |
| FR2987871B1 (en) * | 2012-03-06 | 2015-10-16 | Renault Sas | QUICK COOLING DEVICE FOR MOTOR VEHICLE COMPRISING A PIECE WITH A DIFFUSER |
| FR3002281A1 (en) * | 2013-02-19 | 2014-08-22 | Peugeot Citroen Automobiles Sa | Cooling circuit for thermal engine of car, has thermostatic valve located in inlet manifold upstream of feed pump, where valve blocks flow of coolant in inlet manifold as long as coolant temperature is below threshold temperature |
Family Cites Families (15)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH03179122A (en) * | 1989-12-07 | 1991-08-05 | Fuji Heavy Ind Ltd | Temperature control device of catalyst converter |
| US6564757B2 (en) * | 2000-06-22 | 2003-05-20 | Toyota Jidosha Kabushiki Kaisha | Internal combustion engine including heat accumulation system, and heat carrier supply control system |
| JP2002256839A (en) * | 2001-02-28 | 2002-09-11 | Sanshin Ind Co Ltd | Dry sump lubricating structure of small craft |
| US20060086546A1 (en) * | 2002-02-08 | 2006-04-27 | Green Vision Technology, Llc | Internal combustion engines for hybrid power train |
| JP4023176B2 (en) * | 2002-02-13 | 2007-12-19 | トヨタ自動車株式会社 | Cooling device for internal combustion engine |
| US7156056B2 (en) * | 2004-06-10 | 2007-01-02 | Achates Power, Llc | Two-cycle, opposed-piston internal combustion engine |
| JP2006112233A (en) * | 2004-10-12 | 2006-04-27 | Aisan Ind Co Ltd | Engine cooling system |
| US7013646B1 (en) * | 2004-11-18 | 2006-03-21 | The Gates Corporation | Auxiliary power system for a motor vehicle |
| US20060107920A1 (en) * | 2004-11-18 | 2006-05-25 | Alexander Serkh | Auxiliary power system for a motor vehicle |
| JP2006258007A (en) * | 2005-03-18 | 2006-09-28 | Toyota Motor Corp | Control device of internal combustion engine |
| JP2006342680A (en) * | 2005-06-07 | 2006-12-21 | Toyota Motor Corp | Cooling system of internal combustion engine |
| US7461628B2 (en) * | 2006-12-01 | 2008-12-09 | Ford Global Technologies, Llc | Multiple combustion mode engine using direct alcohol injection |
| JP2008231942A (en) * | 2007-03-16 | 2008-10-02 | Toyota Motor Corp | Cooling system of internal combustion engine |
| JP2008255871A (en) * | 2007-04-04 | 2008-10-23 | Toyota Motor Corp | Cooling system |
| US20080264036A1 (en) * | 2007-04-24 | 2008-10-30 | Bellovary Nicholas J | Advanced engine control |
-
2009
- 2009-05-08 US US13/201,717 patent/US20120047893A1/en not_active Abandoned
- 2009-05-08 JP JP2011512281A patent/JP5196014B2/en not_active Expired - Fee Related
- 2009-05-08 WO PCT/JP2009/058657 patent/WO2010128549A1/en active Application Filing
- 2009-05-08 CN CN2009801589491A patent/CN102414413A/en active Pending
Also Published As
| Publication number | Publication date |
|---|---|
| JPWO2010128549A1 (en) | 2012-11-01 |
| US20120047893A1 (en) | 2012-03-01 |
| JP5196014B2 (en) | 2013-05-15 |
| WO2010128549A1 (en) | 2010-11-11 |
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Application publication date: 20120411 |