CN205559045U - Pressure boost gasoline engine cooling system - Google Patents
Pressure boost gasoline engine cooling system Download PDFInfo
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- CN205559045U CN205559045U CN201620148322.5U CN201620148322U CN205559045U CN 205559045 U CN205559045 U CN 205559045U CN 201620148322 U CN201620148322 U CN 201620148322U CN 205559045 U CN205559045 U CN 205559045U
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Abstract
The utility model discloses a pressure boost gasoline engine cooling system, including engine cylinder block for hold the engine pack, the water pump for carry the coolant liquid to engine cylinder block, the coolant liquid that the engine cylinder body was carried is received to the engine cylinder lid, pressure boost cooling module for carry the water -feeding pump after the coolant liquid pressure boost cooling to the engine cylinder block transport, the warm braw for through flowing through engine cylinder coolant liquid approximately with heat transfer, the water tank radiator for the receipt flow through engine cylinder lid the coolant liquid and be the thermal treatment that looses, through the coolant flow of connected temperature saver control flow warp, water pipe for it provides pipeline to carry the circulation for the coolant liquid between each part among the pressure boost gasoline engine cooling system. The utility model discloses in, simplified cooling system, improved the holistic cooling power of gasoline engine power.
Description
Technical field
This utility model relates to gasoline engine cooling system technical field, particularly relates to a kind of supercharging gasoline engine cooling system.
Background technology
The pipeline configuration of the former i.e. prior art cooling systems of type gasoline engine is complex, pipeline is many and long, have many places water pipe coiling engine body, electromotor complete machine surface is numerous and diverse, wordy, directly influence electromotor NVH (Noise, Vibration, Harshness, noise, vibration, sound vibration roughness) and reliability.
Existing engine-cooling system, is mainly made up of following several respects: water pump, thermostat, front and back warm braw, machine cooler, supercharger etc..As shown in Figure 1, former type is fetched water from cylinder cap, and coolant is divided into two-way, and a road returns to water pump through radiator (except partial circulating), machine cooler, thermostat, after another road flows through the parallel-connection structure of supercharger and warm braw, flow directly back into water pump without thermostat, radiator；Wherein machine cooler uses parallel-connection structure with main water route.In this cooling system, structural redundancy is numerous and diverse.
Utility model content
This utility model provides a kind of supercharging gasoline engine cooling system, with under the pipeline structure premise of simplified cooling system, improves the cooling capacity that gasoline engine is overall simultaneously.
In order to achieve the above object, this utility model provides a kind of supercharging gasoline engine cooling system, and described system includes:
Engine cylinder-body, is used for accommodating engine pack；
Water pump, for carrying coolant to described engine cylinder-body；
Engine cylinder cover, is connected with described engine cylinder-body, for receiving the coolant of described engine cylinder-body conveying；
Supercharging cooling assembly, flows to described water pump after the coolant pressure charging temperature reduction carrying described engine cylinder-body；Described supercharging cooling assembly specifically includes machine cooler and supercharger, and the two is connected in parallel；
Warm braw, carries heat for the coolant by flowing through engine cylinder cover, and this coolant is transported to described water pump；
Radiator of water tank, flows through the coolant of described engine cylinder cover for receiving and does radiating treatment, is controlled the coolant rate flowed through by connected thermostat, and this coolant is transported to described water pump；
Waterway pipe, for in described supercharging gasoline engine cooling system between each parts coolant conveying circulation provide conveyance conduit.
Further, described engine cylinder-body, engine cylinder cover, radiator of water tank, thermostat and water pump are connected in series, and described water pump is connected with described engine cylinder-body, form coolant circulation conveying circuit in a set of described supercharging gasoline engine cooling system.
Further, described engine cylinder-body, engine cylinder cover, warm braw and water pump are connected in series, and described water pump is connected with described engine cylinder-body, form coolant circulation conveying circuit in a set of described supercharging gasoline engine cooling system.
Further, described engine cylinder-body, machine cooler and water pump are connected in series, and engine cylinder-body, supercharger and water pump are connected in series, and described water pump is connected with described engine cylinder-body, forms coolant circulation conveying circuit in a set of described supercharging gasoline engine cooling system；Described machine cooler and described pump house are provided with choke valve, for controlling to flow through the coolant rate of described machine cooler.
Further, described supercharging gasoline engine cooling system also includes expansion tank, is connected with described engine cylinder cover, radiator of water tank and water pump respectively by described waterway pipe, for regulating the flow of coolant in coolant conveying circulation.
Further, at described choke valve, it is provided with a throttle orifice, to regulate described coolant flow in described machine cooler.
Further, described engine cylinder-body and engine cylinder cover are screwed.
Further, described warm braw specifically includes after front warm braw and rear warm braw, described front warm braw and described rear warm braw are arranged in parallel and is series between described engine cylinder cover and water pump.
Compared with prior art, this utility model at least has the advantage that
Cooling system after improvement has not only obtained bigger simplification, electromotor complete machine surface is made to seem the cleanest and the tidiest, and while improve the cooling capacity that gasoline engine is overall, also the dynamic property of electromotor, economy, emission performance is made to have obtained bigger lifting, for user and the energy-saving and emission-reduction of enterprise, increase economic benefit and serve pivotal role.
Accompanying drawing explanation
Fig. 1 is the schematic diagram of supercharging gasoline engine cooling system in prior art；
Fig. 2 is the schematic diagram of supercharging gasoline engine cooling system in this utility model
Fig. 3 is the schematic diagram with the trend curve of changes in flow rate of the pump head under the declared working condition that the utility model proposes；
Fig. 4 is the schematic diagram that the thermostat valve opening that the utility model proposes varies with temperature curve；
Drawing reference numeral illustrates:
01 engine cylinder-body and cylinder cap；
02 water pump；
03 radiator of water tank；
Warm braw before 04；
05 machine cooler；
06 choke valve；
07 supercharger；
08 thermostat；
Warm braw after 09
10 expansion tanks.
Detailed description of the invention
The utility model proposes a kind of supercharging gasoline engine cooling system, including the engine cylinder-body accommodating engine pack, it is connected with described engine cylinder-body, for receiving the engine cylinder cover of the coolant of described engine cylinder-body conveying, water pump to described engine cylinder-body conveying coolant, thermostat, the supercharging cooling assembly of the coolant pressure charging temperature reduction that described engine cylinder-body is carried, warm braw heat carried by the coolant flowing through engine cylinder cover, supercharger, receive and flow through the coolant of described engine cylinder cover and do the radiator of water tank of radiating treatment, control the thermostat of coolant rate that flows through and the waterway pipe of conveyance conduit is provided for coolant conveying circulation between each parts in described supercharging gasoline engine cooling system；Wherein, this supercharging cooling assembly specifically includes the machine cooler and supercharger being connected in parallel, and below in conjunction with the accompanying drawings, is described in detail this utility model detailed description of the invention.
In involved all waterway pipes, all flowings have coolant, and wherein, this coolant is ethylene glycol and the liquid of water equal-volume mixing, i.e. WATER/GLYCOL=50/50.
As in figure 2 it is shown, scheme of the present utility model devises coolant circulation conveying circuit in three set supercharging gasoline engine cooling systems:
Coolant circulation conveying circuit (one)
Described engine cylinder-body, engine cylinder cover, radiator of water tank, thermostat and water pump are connected in series, and described water pump is connected with described engine cylinder-body, form coolant circulation conveying circuit in a set of described supercharging gasoline engine cooling system；That is:
Water pump is connected with engine cylinder-body by waterway pipe, and engine cylinder-body and engine cylinder cover are connected by waterway pipe；Engine cylinder cover is connected with radiator of water tank by waterway pipe, and radiator of water tank and pump house are provided with thermostat, and radiator of water tank is connected with thermostat by waterway pipe, and thermostat is connected with water pump by waterway pipe.Wherein, engine cylinder-body and engine cylinder cover are connected, and are screwed between the two.Wherein, this warm braw specifically includes front warm braw and rear warm braw, and front warm braw and rear warm braw be arranged in parallel after be series between engine cylinder cover and water pump.
Coolant circulation conveying circuit (two)
Described engine cylinder-body, engine cylinder cover, warm braw and water pump are connected in series, and described water pump is connected with described engine cylinder-body, form coolant circulation conveying circuit in a set of described supercharging gasoline engine cooling system；That is:
Water pump is connected with engine cylinder-body by waterway pipe, and engine cylinder-body and engine cylinder cover are connected by waterway pipe；Engine cylinder cover is connected with warm braw by waterway pipe, and warm braw is connected with water pump by waterway pipe.
Coolant circulation conveying circuit (three)
Described engine cylinder-body, machine cooler and water pump are connected in series, and engine cylinder-body, supercharger and water pump are connected in series, and described water pump is connected with described engine cylinder-body, form coolant circulation conveying circuit in a set of described supercharging gasoline engine cooling system；That is:
Water pump is connected with engine cylinder-body by waterway pipe, and engine cylinder-body is connected with machine cooler and supercharger respectively by waterway pipe；Wherein, machine cooler and supercharger are connected in parallel between this engine cylinder-body and water pump, so,
This machine cooler is connected with water pump by waterway pipe, and this machine cooler is provided with choke valve with pump house；Wherein, at this choke valve, it is provided with a throttle orifice, to control to flow through the coolant rate of described machine cooler.
This supercharger is connected with water pump by waterway pipe.
Further, in this supercharging gasoline engine cooling system, also include expansion tank, be connected with described engine cylinder cover, radiator of water tank and water pump respectively by described waterway pipe, for regulating the flow of coolant in coolant conveying circulation.
With a specific embodiment, the supercharging gasoline engine cooling system provided in this utility model is specifically described below.
Wherein, the present embodiment does corresponding elaboration by Flowmaster model.
First, in this Flowmaster model, the parameter of each components and parts and input data are specific as follows,
[1] water pump
Pump rotary speed is when 6000rpm, and metered flow is 195L/min, and rated head is 16.8m.
See Fig. 3, for declared working condition pump head with flow changing curve.
[2] thermostat
Increasing by 90 degree of elbows in Flowmaster model and represent the pressure drop of thermostat housing, thermostat valve opening variation with temperature curve is written into program, and as shown in Figure 4, calculating thermostat in the simulation of declared working condition coolant flow is full-gear.The outlet temperature of radiator is 88 DEG C of@thermostat standard-sized sheets, the fully closed temperature of thermostat 76 DEG C.
[3] supercharger
Supercharger is simulated with a heat exchange part in Flowmaster model.Heat exchange power is 2kW.
[4] machine cooler, has another name called oil cooler
In the population structure of one-dimensional model design, machine cooler exit adds the structure of a throttle orifice, and its main purpose is to regulate coolant flow in machine cooler.In this utility model, it is that 6mm/20mm, 16mm/20mm carry out comparing calculation respectively to aperture ratio.
[5] radiator
Engine radiator is defined as constant leaving water temperature.The performance of cooler is defined by inside Flowmaster model, and i.e. no matter heat sink inlet water temperature how, and outlet temperature keeps constant.In Flowmaster model calculates, radiator outlet coolant-temperature gage is set as 100 DEG C, and during partial circulating, outlet tank temperature is set to 80 DEG C.
[6] engine drag coefficient
In one-dimensional model, in order to reflect real pressuredrop characteristic parameter, the resistance of engine cooling water jacket represents with discrete loss.Discrete being lost in software network represents by resistance.Discrete resistance is verified according to 3D-CFD (Computational Fluid Dynamics, computational fluid dynamics) model result.
[7] attribute of pipe/flexible pipe
The design of waterway pipe based on actual body and three-dimensional mathematical model (including the length of pipeline, diameter), the water pipe internal diameter such as table 1 below of primary circuit:
Table 1 water pipe internal diameter
The design of machine cooler orifice diameter has two:
(1)6mm/20mm；(2)16mm/20mm.
[8] expansion tank specification
Under the rated power of electromotor, the absolute pressure (steady pressure) of expansion tank is 1.5bar.
Expansion tank coolant volume is set as 10L；Gas volume 1.5L.
[9] main parts size pressure drop and other parameters
The pressure drop of whole parts that One-dimensional simulation is used in calculating is as shown in table 2.
Parameter in table 2 model
[10] coolant kind
Characterisitic parameter and the empirical equation of most liquid is had in Flowmaster model, here, the type of selected liquid: ethylene glycol and the mixing of water equal-volume, i.e. WATER/GLYCOL=50/50.
Concrete numerical procedure includes:
Scheme 1:
Machine cooler throttle orifice aperture ratio is (6mm/20mm), as shown in table 3 below:
Concrete, 1) declared working condition (engine speed 5000rpm, pump rotary speed 6000rpm)
1, thermostat standard-sized sheet, systemic circulation
(1) flow distribution
Total coolant rate of water pump is 228L/min.It is wherein 47.4L/min by the discharge of warm braw, accounts for the 20.8% of total flow；It is 12L/min by supercharger discharge, accounts for the 5.2% of total Water；It is 26L/min by the discharge of machine cooler, accounts for the 11.4% of total Water, when meeting rated speed, be more than the requirement of 25L/min.
(2) pressure distribution
When thermostat standard-sized sheet, pump rotary speed 6000rpm, the pressure of pump intake is 1.31bar, and outlet pressure is 2.86bar.Being 743mbar by the pressure drop of engine body cooling water, radiator pressure drop is 362.4mbar, and machine cooler pressure drop is 330mbar, and thermostat pressure drop is 4.5mbar.Supercharger pressure drop is 378mbar, and warm braw pressure drop is 216mbar.
(3) temperature rise
Cylinder body entrance is 4.42 DEG C to cylinder cap outlet coolant temperature rise, machine cooler temperature rise 3.85 DEG C, supercharger temperature rise 10.8 DEG C, and radiator coolant temperature reduces by 8.9 DEG C.Less than 10 DEG C, meet design specification.
2, thermostat is fully closed, partial circulating
(1) flow distribution: total pump discharge of water pump is 240L/min.The cooling water that wherein there are about 98.8L/min participates in circulation, and other cooling water are fully closed at thermostat, and directly reflux under partial circulating operating mode water pump, is 28.4L/min by the water yield of oil cooler, accounts for the 29% of total Water；Radiator is 0.8L/min, accounts for the 0.1% of total Water；It is 56.3L/min by the discharge of warm braw, accounts for the 57% of total flow；It is 13.2L/min by supercharger discharge, accounts for the 13% of total Water.
(2) pressure drop: when thermostat is fully closed (partial circulating), pump rotary speed 6000rpm, the pressure of pump intake is 1.4bar, and outlet pressure is 2.8bar.Being 982.0mbar by the pressure drop of engine body cooling water, water tank pressure drop is 156.5mbar, and machine cooler pressure drop is 283.9mbar, and thermostat pressure drop is 2.3mbar.Supercharger pressure drop is 327.0mbar, and warm braw pressure drop is 150.5mbar.
Declared working condition brief summary: the temperature rise statistic flowing through each part is as shown in table 4.
The calculating temperature rise situation of each components and parts of table 4 scheme 1
2) peak torque operating mode (engine speed 2200rpm, pump rotary speed 2640rpm)；
Water pump is in speed at maximum torque 2640rpm, and machine cooler throttle orifice aperture ratio is (6mm/20mm), and radiator outlet water temperature is 100 DEG C, thermostat standard-sized sheet, systemic circulation；
(1) flow
Total pump discharge 101L/min of water pump.It is wherein 11.5L/min by the water yield of oil cooler, accounts for the 11% of total Water；Radiator is 60.8L/min, accounts for the 60% of total Water；It is 20.7L/min by the discharge of warm braw, accounts for the 21% of total flow；It is 8.0L/min by supercharger flow, accounts for the 8% of total Water.
(2) pressure drop
The pressure of pump intake is 1.46bar, and outlet pressure is 1.77bar.Being 137.5mbar by the pressure drop of engine body cooling water, water tank pressure drop is 37.1mbar, and machine cooler pressure drop is 63.5mbar, and thermostat pressure drop is 0.9mbar.Supercharger pressure drop is 70.9mbar, and warm braw pressure drop is 43.1mbar.
(3) temperature rise
Water delivery side of pump coolant temperature is 110.1 DEG C, and the temperature rise of coolant cylinder body entrance and cylinder cap outlet is 9.9 DEG C；Machine cooler temperature rise is 8.7 DEG C, and radiator temperature rise is 20.0 DEG C.
3) warm braw check point: (engine speed 1200rpm, pump rotary speed 1440rpm)
According to car load demand, it is desirable to flow through warm braw water during 1200rpm is checked especially, it is desirable to the warm braw flow of this rotating speed is not less than 10.0L/min.Operating mode: thermostat standard-sized sheet, systemic circulation.
(1) flow
Total pump discharge of water pump is 54.2L/min.It is wherein 6.3L/min by the water yield of oil cooler, accounts for the 11.5% of total Water；Radiator is 32.8L/min, accounts for the 60.5% of total Water；It is 11.3L/min by the discharge of warm braw, accounts for the 20.7% of total flow, meet the requirement of car load 10.0L/min；It is 2.9L/min by supercharger flow, accounts for the 5.4% of total Water.
(2) pressure
The pressure of pump intake is 1.495bar, and outlet pressure is 1.583bar.Being 42.3mbar by the pressure drop of engine body cooling water, water tank pressure drop is 11.1mbar, and machine cooler pressure drop is 18.8mbar, and thermostat pressure drop is 0.3mbar.Supercharger pressure drop is 20.4mbar, and warm braw pressure drop is 13.2mbar.
4) idling operation
Engine speed 800rpm, pump rotary speed 960rpm, thermostat standard-sized sheet, systemic circulation.
(1) flow
During idling, total pump discharge of water pump is 36.1L/min.It is wherein 4.2L/min by the water yield of oil cooler, accounts for the 11.6% of total Water；Radiator is 21.7L/min, accounts for the 60.1% of total Water；It is 7.1L/min by the discharge of warm braw, accounts for the 19.7% of total flow, meet the requirement of 6.0L/min；It is 1.9L/min by supercharger flow, accounts for the 5.3% of total Water.
(2) pressure
The pressure of pump intake is 1.50bar, and outlet pressure is 1.54bar.Being 18.6mbar by the pressure drop of engine body cooling water, water tank pressure drop is 4.9mbar, and machine cooler pressure drop is 8.3mbar, and thermostat pressure drop is 0.1mbar.Supercharger pressure drop is 8.7mbar, and warm braw pressure drop is 5.9mbar.
Scheme 2:
Machine cooler throttle orifice aperture ratio is (16mm/20mm), as shown in table 5 below；
Concrete, 1) declared working condition, engine speed 5000rpm, pump rotary speed 6000rpm
1, thermostat standard-sized sheet, systemic circulation；
(1) flow
Total pump discharge of water pump is 237.1L/min.It is wherein 41.8L/min by the water yield of oil cooler, accounts for the 17.6% of total Water；Radiator is 134.8L/min, accounts for the 56.9% of total Water；It is 45.8L/min by the discharge of warm braw, accounts for the 19.3% of total flow；It is 11.6L/min by supercharger flow, accounts for the 4.9% of total Water.
(2) pressure drop
Thermostat standard-sized sheet, systemic circulation, the pressure of pump intake is 1.32bar, and outlet pressure is 2.83bar.Being 756.2mbar by the pressure drop of engine body cooling water, water tank pressure drop is 183.6mbar, and machine cooler pressure drop is 837.3mbar, and thermostat pressure drop is 4.1mbar.Supercharger pressure drop is 335.0mbar, and warm braw pressure drop is 202.7mbar.
(3) temperature rise
Water delivery side of pump coolant temperature is 105.40 DEG C, and the temperature rise of coolant cylinder body entrance and cylinder cap outlet is 4.26 DEG C；Machine cooler temperature rise is 2.40 DEG C, and radiator temperature rise is 9.25 DEG C.
2, thermostat is fully closed, partial circulating；
Under declared working condition, engine speed 5000rpm, during pump rotary speed 6000rpm, the flow of each component cooling water:
Total pump discharge of water pump is 207.8L/min.The cooling water that wherein there are about 74.6L/min flow participates in partial circulating, and other water pumps that all reflux: be 23.9L/min by the water yield of oil cooler account for the 32% of total Water；It is 38.8L/min by the discharge of warm braw, accounts for the 52% of total flow；It is 11.45L/min by supercharger flow, accounts for the 15% of total Water, be 0.80L/min by the discharge of warm braw, account for the 1% of total Water.
Scheme 3:
Former machine cooling system of the prior art, as shown in table 6；
In order to verify the correctness of model, the former i.e. prior art of machine cooling system is modeled type and analytical calculation, and contrast with former machine test data, result of calculation is as shown in table 7 with result of the test (about the report data presented of BJ486ZLEQ4 heat balance test).
It should be noted that owing to there is no having electronic fan when former machine is tested, compare for convenience, therefore during the modeling of former machine cooling system, also do not account for electronic fan, and carried electronic fan during improvement project modeling.
Table 7 former machine calculation and check result contrasts with measured result
By above-mentioned based on the application of Flowmaster model in this utility model, it can be deduced that as drawn a conclusion:
(1) the simulation computational analysis of BJ486 supercharging gasoline engine cooling system two schemes flow model is mainly completed.
(2) to former machine model and two improvement projects, the result of calculation under declared working condition, systemic circulation contrasts, and compared with former machine, the machine cooler flow of improvement project increases substantially, and other part flow also increased, but increasing degree is less.
(3) comparison of machine cooler throttle diameter flows through the coolant rate impact of machine cooler very greatly, flows through the flow 41.8L/min of machine cooler, compared with the big 15.9L/min of 25.9L/min during 6mm/20mm, increase by 61.5% when using throttling part 16mm/20mm.If but flow through machine cooler cooling water flow excessive, machine oil temperature rise can be caused the slowest, affect the use of automobile, 6mm/20mm scheme should be used.
(4) compared with former machine, the machine cooler temperature rise of improvement project is greatly lowered, and other part temperature rise change is little.
(5) scheme 1 cooling system is when idling thermostat standard-sized sheet, and warm braw flow is 7.4L/min, the requirement of minimum warm braw flow 6.0L/min when can meet the idling of car load proposition.But substantially meet requirement.The flow of each part of other operating mode is satisfied by car load requirement.
(6) by former machine model being carried out calculation and check, and contrast with former machine test data, it is determined that being in the main true of Simulation Calculation.
(7) calculate be flow resistance characteristics of based on cooling system part assumed condition under complete.If the flow resistance characteristics of actual parts is different from calculating hypothesis, then simulation result also can be different from experimental result.Must take into the component characteristics change impact on whole system at the trial, and arrange special project test that model is verified in exploitation experiment.
Wherein, the modules of this utility model device can be integrated in one, it is also possible to separates and disposes.Above-mentioned module can merge into a module, it is also possible to is further split into multiple submodule.
It will be appreciated by those skilled in the art that accompanying drawing is the schematic diagram of a preferred embodiment, module or flow process in accompanying drawing are not necessarily implemented necessary to this utility model.
It will be appreciated by those skilled in the art that the module in the device in embodiment can describe according to embodiment to carry out being distributed in the device of embodiment, it is also possible to carry out respective change and be disposed other than in one or more devices of the present embodiment.The module of above-described embodiment can merge into a module, it is also possible to is further split into multiple submodule.
Above-mentioned this utility model sequence number, just to describing, does not represent the quality of embodiment.
Only several specific embodiments of the present utility model disclosed above, but, this utility model is not limited to this, and the changes that any person skilled in the art can think of all should fall into protection domain of the present utility model.
Claims (8)
1. a supercharging gasoline engine cooling system, it is characterised in that described system includes:
Engine cylinder-body, is used for accommodating engine pack；
Water pump, for carrying coolant to described engine cylinder-body；
Engine cylinder cover, is connected with described engine cylinder-body, for receiving the coolant of described engine cylinder-body conveying；
Supercharging cooling assembly, flows to described water pump after the coolant pressure charging temperature reduction carrying described engine cylinder-body；Described supercharging cooling assembly specifically includes machine cooler and supercharger, and the two is connected in parallel；
Warm braw, carries heat for the coolant by flowing through engine cylinder cover, and this coolant is transported to described water pump；
Radiator of water tank, flows through the coolant of described engine cylinder cover for receiving and does radiating treatment, is controlled the coolant rate flowed through by connected thermostat, and this coolant is transported to described water pump；
Waterway pipe, for in described supercharging gasoline engine cooling system between each parts coolant conveying circulation provide conveyance conduit.
2. supercharging gasoline engine cooling system as claimed in claim 1, it is characterized in that, described engine cylinder-body, engine cylinder cover, radiator of water tank, thermostat and water pump are connected in series, and described water pump is connected with described engine cylinder-body, form coolant circulation conveying circuit in a set of described supercharging gasoline engine cooling system.
3. supercharging gasoline engine cooling system as claimed in claim 1, it is characterized in that, described engine cylinder-body, engine cylinder cover, warm braw and water pump are connected in series, and described water pump is connected with described engine cylinder-body, form coolant circulation conveying circuit in a set of described supercharging gasoline engine cooling system.
4. supercharging gasoline engine cooling system as claimed in claim 1, it is characterized in that, described engine cylinder-body, machine cooler and water pump are connected in series, and engine cylinder-body, supercharger and water pump are connected in series, and described water pump is connected with described engine cylinder-body, form coolant circulation conveying circuit in a set of described supercharging gasoline engine cooling system；Described machine cooler and described pump house are provided with choke valve, for controlling to flow through the coolant rate of described machine cooler.
5. the supercharging gasoline engine cooling system as described in any one of claim 1-4, it is characterized in that, described supercharging gasoline engine cooling system also includes expansion tank, it is connected with described engine cylinder cover, radiator of water tank and water pump respectively by described waterway pipe, for regulating the flow of coolant in coolant conveying circulation.
6. supercharging gasoline engine cooling system as claimed in claim 4, it is characterised in that be provided with a throttle orifice at described choke valve, to regulate described coolant flow in described machine cooler.
7. supercharging gasoline engine cooling system as claimed in claim 1, it is characterised in that described engine cylinder-body and engine cylinder cover are screwed.
8. supercharging gasoline engine cooling system as claimed in claim 1, it is characterised in that described warm braw specifically includes after front warm braw and rear warm braw, described front warm braw and described rear warm braw are arranged in parallel and is series between described engine cylinder cover and water pump.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201620148322.5U CN205559045U (en) | 2016-02-26 | 2016-02-26 | Pressure boost gasoline engine cooling system |
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| CN201620148322.5U CN205559045U (en) | 2016-02-26 | 2016-02-26 | Pressure boost gasoline engine cooling system |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109141887A (en) * | 2017-06-28 | 2019-01-04 | 长城汽车股份有限公司 | The test macro and test method of engine heat management performance |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109141887A (en) * | 2017-06-28 | 2019-01-04 | 长城汽车股份有限公司 | The test macro and test method of engine heat management performance |
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