CN1170812A - Cooling system for cylinder jacket of internal combustion engine - Google Patents
Cooling system for cylinder jacket of internal combustion engine Download PDFInfo
- Publication number
- CN1170812A CN1170812A CN97112732A CN97112732A CN1170812A CN 1170812 A CN1170812 A CN 1170812A CN 97112732 A CN97112732 A CN 97112732A CN 97112732 A CN97112732 A CN 97112732A CN 1170812 A CN1170812 A CN 1170812A
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- Prior art keywords
- cylinder
- cylinder liner
- freezing mixture
- cooling system
- temperature
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
- F01P3/00—Liquid cooling
- F01P3/02—Arrangements for cooling cylinders or cylinder heads
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
- F02F1/00—Cylinders; Cylinder heads
- F02F1/02—Cylinders; Cylinder heads having cooling means
- F02F1/10—Cylinders; Cylinder heads having cooling means for liquid cooling
- F02F1/14—Cylinders with means for directing, guiding or distributing liquid stream
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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
- 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
- F01P7/165—Controlling of coolant flow the coolant being liquid by thermostatic control characterised by systems with two or more loops
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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
- F01P3/00—Liquid cooling
- F01P2003/006—Liquid cooling the liquid being oil
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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
- F01P3/00—Liquid cooling
- F01P3/02—Arrangements for cooling cylinders or cylinder heads
- F01P2003/021—Cooling cylinders
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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
- F01P3/00—Liquid cooling
- F01P3/02—Arrangements for cooling cylinders or cylinder heads
- F01P2003/024—Cooling cylinder heads
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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
- F01P3/00—Liquid cooling
- F01P3/02—Arrangements for cooling cylinders or cylinder heads
- F01P2003/028—Cooling cylinders and cylinder heads in series
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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
- F01P2007/143—Controlling of coolant flow the coolant being liquid using restrictions
-
- 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
- F01P2007/146—Controlling of coolant flow the coolant being liquid using valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
- F01P2025/00—Measuring
- F01P2025/08—Temperature
- F01P2025/31—Cylinder temperature
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
- F01P2025/00—Measuring
- F01P2025/08—Temperature
- F01P2025/32—Engine outcoming fluid temperature
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
- 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B3/00—Engines characterised by air compression and subsequent fuel addition
- F02B3/06—Engines characterised by air compression and subsequent fuel addition with compression ignition
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
- F02F7/00—Casings, e.g. crankcases or frames
- F02F2007/0097—Casings, e.g. crankcases or frames for large diesel engines
Abstract
The cooling system supplies the coolant through the cylinder cap (5,7), in which it is preheated. The preheated coolant may then be supplied at a preset temperature to the coolant channels (11) and clearance cavities (12) of the cylinder sleeve (1). The preheating within the preset temperature range may be achieved with heat which is at least partly created in the region of the cylinder sleeve. The coolant may be taken through the cylinder cap or through the region of TDC of the piston in the cylinder sleeve (1) and preheated there.
Description
The present invention relates to the cooling system of internal-combustion engine.
Large-scale diesel engine generally is configured to for example have upright cylinder.The known cooling system of large-scale diesel engine is arranged to freezing mixture especially and is flowed from the bottom up.Quite cold inlet freezing mixture is the cooling air casing wall at first.This freezing mixture to the upper reaches, flows to cylinder head from this end along the direction of the upper end portion of leading to cylinder jacket then.Therefore except may exist toward dirty part, freezing mixture is to flow to the top from the bottom basically.
It is to consider that the reason of this configuration is removed outside many other factorses, and freezing mixture is heated in cooling system, and the freezing mixture that is heated can be naturally and understandably toward the upper reaches.Because temperature difference thereby also be the circulation that natural convection that the density difference causes helps freezing mixture.
Yet the cooling of cooling off the wall of cylinder liner 1 particularly not should with fully not controlled way carry out.When for example burning contains the fuel of a large amount of sulphur, except that producing other corrosivity products of combustion, also form sulphurous acid (H
2SO
3).The dew point of sulphurous acid is between 130 to 140 ℃ temperature.Sulphurous acid liquefies under this temperature.If cooling air cylinder liner too doughtily, then sulphurous acid will condense upon the lower area of cylinder liner.If quite cold freezing mixture is incorporated into the bottom of cylinder jacket, then makes the wall temperature of cylinder liner too low probably.
Freezing mixture heating gradually to the upper reaches is further heated again when flowing to the upper area of cylinder liner, yet is flowed upward to cylinder head.Thereby cylinder liner at the wall temperature of upper area significantly than higher, in fact do not have the danger of corrosivity products of combustion liquefaction at this place.Therefore say definitely that the upper area at cylinder liner needs strong especially cooling just, promptly needs extra high cooling power.Otherwise, then only require limited cooling at the middle part and the lower area of cylinder liner, and should avoid cooling action too strong that temperature range reaches and for example makes the corrosivity products of combustion condense upon this situation on the cylinder surface.
The improved cooling system that the purpose of this invention is to provide a kind of for example cooling large-sized diesel liner.According to the present invention, the coolant feed that is used for cylinder liner that will have a certain temperature in the predetermined temperature range is given cooling system, wherein, at least the upper area of cylinder liner is made The pre-heat treatment partly in given temperature range.
In this cooling system, cold freezing mixture at first flows through the upper area of cylinder head and/or cylinder liner, and absorbs heat from the latter and make self heating.Comparing with known cooling system, owing between cold freezing mixture and the zone to be cooled the bigger temperature difference is arranged, is that the upper area of cylinder head and cylinder liner is subjected to stronger cooling so need the part of strong cooling especially.Then the freezing mixture of preheating is sent into the middle part and the lower area of cylinder liner, what need at this place is heating rather than cooling, so that prevent for example cohesion of highly corrosive products of combustion.Heat exchange not only is subjected to the influence of pre-hot coolant, and is subjected to the influence of liquid stream conditioned disjunction flow velocity and flow.
Below with reference to schematic view illustrating the present invention with specify the operation of cooling system, these schematic representation illustrate the exemplary embodiments of cooling air cylinder liner of the present invention.These accompanying drawings are:
Fig. 1 is the cooling system of cylinder liner, and freezing mixture only flows around the top of cylinder liner length in this system;
Fig. 2 is the cooling system of the cylinder liner of Fig. 1, but the freezing mixture in this system around cylinder liner until the major length of the relief opening of cylinder liner exhaust partly flow.
The cooling line of the cylinder liner 1 of two-stroke large diesel machine is described below with reference to Fig. 1.Recycle pump 2 is sent for example freezing mixture of constant basis into cylinder head 5 by inlet pipe 3 and distribution loop 4, flows through coolant channel not shown in the cylinder head 5 then.Coolant entrance is positioned on the distribution loop 4 on cylinder head 5 lower limbs.Coolant outlet 6 is arranged in the uppermost position of the valve casing 7 that is contained in cylinder head 5.
Heated freezing mixture enters coolant channel 11 in cylinder liner 1 upper area by pipeline 8,9 and distribution loop 10 in cylinder head 5 and valve casing 7, and is subjected to further heating.The freezing mixture respective streams is crossed the cooling hole or the coolant channel 11 of cylinder liner 1, and enters and be positioned at more following chamber, gap 12.
The flow velocity that for example is decided to be freezing mixture in cylinder liner and the size of surrounding the chamber, annular space 12 between the supporting ring 17 of this cylinder liner is not less than certain value under minimum probable discharge.If flow is the flow of stipulating so far in the known two-stroke large diesel machine, then for new cooling system, the gap size between cylinder liner 1 and supporting ring 17 requires in the scope of for example 3mm.
In example shown in Figure 1, freezing mixture leaves chamber, gap 12 in supporting ring 17 underparts by outlet radially, with after collecting ring 18 flows into Returning pipes 19.
Dress adjustable restrictive valve 13 between the inlet pipe 9 of the freezing mixture of cylinder liner and outlet conduit 19.Throttle valve 13 is by 25 controls of reference wall temperature or the adjusting of cylinder liner 1.When throttle valve 13 cut out, all freezing mixtures flow through the cooling hole 11 and the chamber, gap 12 of cylinder liner 1.Therefore top and the heat exchange between following chamber, gap 12 at cylinder liner 1 is the strongest.
When throttle valve 13 was opened, only some freezing mixture flow through the cooling hole 11 of cylinder liner 1 and is positioned at following chamber, gap 12.Therefore the heat exchange degree in the cylinder liner 1 reduces.When throttle valve 13 was opened fully, the minimum coolant flow of the cylinder liner 1 of flowing through was by the size decision in the aperture 14 of throttle valve 13 back.Part freezing mixture enters cooler 16 through controllable throttle valve 13, aperture 14 and temperature control valve (TCV) 15, flow back into recycle pump 2 again after logical a certain amount of freezing mixture mixes with being close to then.
It is advantageous that coolant flow is adjusted to constant in the coolant temperature maintenance at outlet 6 places of valve casing 7.Temperature difference between inlet pipe 3 and outlet conduit 8 depends on the total amount of heat that must lead away from cylinder head 5, valve casing 7 and cylinder liner 1.Freezing mixture is minimum in the inlet temperature on the cylinder head 5 when internal-combustion engine turns round under rated power, and increases with combustion engine powered minimizing.
The coolant temperature at cylinder liner 1 ingress, pipeline 9 and distribution loop 10 places is identical with the coolant temperature of locating in the outlet 6 (pipeline 8) of valve casing 7, and is therefore quite constant in this regional temperature.
Heat exchange in cylinder liner 1 is by the flow velocity decision of freezing mixture in the physical dimension in the hole in the upper sleeve and the chamber, gap 12.The wall temperature 25 of cylinder liner 1, thereby also be that the reference temperature that is used to control throttle valve 13 or control coolant flow depends on design, the cooling hole 11 of freezing mixture and the size and the configuration of chamber, gap 12 promptly depended on.
The cylinder liner wall temperature comprises that the control system of all cylinders of internal-combustion engine, one group of cylinder or each cylinder can install separately.25 needs of wall temperature of all cylinders of control entire internal combustion engine are adorned a modulating valve 13 (Fig. 1 and Fig. 2), and indivedual wall temperatures of control individual cylinder generally need be provided with the modulating valve 13 of each cylinder.When the wall temperature of control individual cylinder group, be preferably in throttle valve 13 is installed on the individual cylinder group.
Yet also might remove the throttle valve 13 that control flows is crossed the coolant flow of cylinder liner 1 fully, and only decide the coolant flow that flows through cylinder liner 1 with the size in aperture 14.Under wall temperature quite little feasible control of its difference in its whole usage range of cylinder liner 1 was unnecessary situation, this was possible.Equally, also may make coolant flow by the pump output of regulating coolant pump 2 is that cooling capacity satisfies each other requirement.
In fact, will not be for known large-scale diesel engine owing to adopting new cooling system to change the structural design of cylinder head 5.What only need to change is the distribution loop 4 of cylinder head 5 ingress.Distribution loop 10 for cylinder liner 1 upper end portion also is like this.
The structural design of chamber, gap 12 is that sizing is based on the internal diameter that makes supporting ring 17 and the wall thickness of cylinder liner 1 is complementary.The external diameter of supporting ring 17 not necessarily needs to change previous existing size.
In having the internal-combustion engine of long stroke very, freezing mixture is flow to above the relief opening 20, as shown in Figure 2 in the 12a of the chamber, gap of a lengthening below supporting ring 17.
Generally speaking, if the ratio of stroke of piston and cylinder bore is equal to or greater than 2 (stroke/bore 〉=2), then this internal-combustion engine is called the long stroke machine.
If guarantee the coolant flow speed that can keep minimum in all flow of coolant zones, then cooling system to sealing or the gas that captures, air particularly the receptance of steam bubble be very low.In addition, the size of cooling hole and chamber, gap can be decided to be and make issuable air bubble, steam bubble and bubble take away simultaneously by flowing coolant.
Cyclone separator can be set in circulate coolant make the freezing mixture exhausting air or the degassing effectively.Yet also can make gas flow out cooling system by automatic air-breather 21.The freezing mixture that loses in the cooling system can be replenished from cryogen tank 22 with transfer pump 23.Above-mentioned cooling system is suitable for working with the supercharging storage 24 of elevated trough or sealing equally.With elevated trough that atmosphere communicates in, the temperature of freezing mixture is subjected to the restriction of freezing mixture boiling temperature, and the boiling temperature of freezing mixture becomes higher when pressure increases in the pressurised reservoir of sealing.
In known cooling system, in the temperature of the freezing mixture at inlet 6 places of valve casing 7 between 80～90 ℃.For example, for known large-scale diesel engine, the temperature difference of cylinder freezing mixture between outlet temperature and inlet temperature is normal at 10～30 ℃.Therefore the freezing mixture in this example must be to be about 70 ℃ in the temperature that enters cylinder jacket, and this colder relatively freezing mixture flows through the intermediate portion of cylinder liner 1 then.This may cause the wall temperature of cylinder liner 1 too low and products of combustion is condensed upon on the wall of cylinder liner 1, thereby causes above-mentioned etching condition, and internal-combustion engine is suffered damage.
In cooling system of the present invention, than higher,, be subjected to false add heat at this place and promptly be preheated because this freezing mixture at first flows through cylinder head 5 and valve casing 7 at the coolant temperature of cylinder liner 1 ingress.Therefore the temperature of this freezing mixture for example is 85 ℃ when it leaves valve casing 7.During cooling hole in flowing through the upper sleeve of cylinder liner, this coolant temperature increases about 3～7 ℃ again.Therefore the intermediate portion of cylinder liner 1 is subjected to temperature for example in the cooling of 88～92 ℃ freezing mixture.This temperature is than high about 20 ℃ of the temperature of known cooling system.Because with the coolant cools of temperature, so the temperature of the inwall of cylinder liner 1 is remained on be higher than the dew point temperature of harmful corrosivity products of combustion.
Concrete freezing mixture in the above-described embodiments is a water.Wherein may be mixed with anticorrosive additive.Yet can also make freezing mixture with oil, for example use internal combustion (IC) engine lubricating oil itself, or use independent cold oil in the circulation loop that separates with lubricant oil.Because various freezing mixtures have different specific heat, so can revise the size and/or the coolant flow speed of coolant path.For help in the cylinder liner 1 piston 1 ' lubricated, it also is favourable making the inwall of cylinder liner 1 remain on high relatively temperature.This temperature can be at about 200 ℃ or higher.
Can also imagine such cooling system, in this system, some zone for example cylinder head 5 can be with for example water cooling of first freezing mixture, and another zone for example cylinder liner 1,11,12 usefulness second freezing mixture for example oil cooling is but.Between two subtense angles, can provide heat exchanger,, meet the requirements of chilling temperature so that carry out heat exchange.
Cooling action or cooling system by the present invention explanation can comprise this zone well, in this zone the internal-combustion engine member particularly cylinder liner 1 be subjected to the heating of freezing mixture, but see that from whole internal-combustion engine nature is that freezing mixture is led away heat.
According to the present invention explanation, cylinder region said " top " is meant that reversing point on the piston is promptly away from the zone of bent axle.Equally, cylinder region said " bottom " is meant the zone of the promptly close bent axle of piston 1 ' following reversing point.Therefore term " top " and " bottom " are interpreted as the location independent with cylinder.Generally be meant whether have cylinder jacket cylinder liner really or do not adopt the difference cylinder structure-irrelevant when in this explanation, adopting the term cylinder liner with cylinder.
When the cylinder liner of cooling air cylinder liner 1, particularly cooling large-sized diesel engine, freezing mixture at first flows through cylinder head 5 and preheating therein.Make the freezing mixture that is preheating to predetermined temperature send into the cooling channel 11 and the chamber, gap 12 of cylinder liner 1 then.Owing to the heat that produces in partial cylinders lining zone (cooling channel 11) at least makes freezing mixture be preheating to predetermined temperature range.Because the freezing mixture of input preheating, so can prevent for example degree of sulphurous acid of products of combustion that the temperature of the inner wall area of cylinder liner 1 is not cooled on the inwall of cylinder liner 1 the cohesion severe corrosive.
Claims (10)
1. the cooling system of a cooling internal combustion engines cylinder, it specifically is the liquid-cooling system of cooling large-sized diesel liner (1), it is characterized in that, the coolant temperature that is transported to cylinder liner (1) is a temperature in the predetermined temperature range, freezing mixture is preheating to this predetermined temperature range at least partly in the zone (5,7) of cylinder.
2. cooling system as claimed in claim 1, wherein, in cylinder head (5,7) zone and/or produce the heat of pre-hot coolant in the cooling channel (11) of cylinder liner (1) upper area, be used for the middle part and/or the lower area of cooling air cylinder liner (1) in predetermined temperature range.
3. cooling system as claimed in claim 1 or 2, wherein, freezing mixture flows through cylinder head (5,7) and/or the middle piston (1 ') of cylinder liner (1) is gone up reversing point zone (11), and preheating therein.
4. as claim 1,2 or 3 described cooling systems, wherein, the flow of coolant direction in cylinder liner (1) generally is the following reversing point from the last reversing point field flow orientation piston (1 ') of piston (1 ').
5. as each described cooling system in the claim 1～4, wherein, select the predetermined temperature of freezing mixture like this, make the temperature of cylinder liner (1) inwall be higher than the dew point temperature of corrosivity products of combustion/waste gas in the combustion chamber of air cylinder.
6. cooling system as claimed in claim 5 wherein, is selected the temperature of freezing mixture like this, makes that at least the temperature of inwall is at least 130 ℃ in the firing chamber of the central region of cylinder liner (1), more preferably greater than 135 ℃.
7. as each described cooling system in the claim 1～6, wherein, freezing mixture is a turbulent flow in a part of zone of cylinder liner (1) at least.
8. large-scale diesel engine, wherein, cylinder liner (1) is by each described cooling system cooling in the claim 1～7, cylinder can be individually or in groups or all the concentrated area supply with freezing mixture.
9. large-scale diesel engine as claimed in claim 8 wherein, can be supplied with all cylinders with the freezing mixture common land with regulating, or each independent cylinder, or respectively organizes cylinder.
10. large-scale diesel engine as claimed in claim 8 or 9 has the cylinder of upright configuration.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| EP96810414.1 | 1996-06-20 | ||
| EP96810414A EP0814243B1 (en) | 1996-06-20 | 1996-06-20 | Cooling system for the cylinder jacket of an internal combustion engine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1170812A true CN1170812A (en) | 1998-01-21 |
| CN1093909C CN1093909C (en) | 2002-11-06 |
Family
ID=8225634
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN97112732A Expired - Fee Related CN1093909C (en) | 1996-06-20 | 1997-06-17 | Cooling system for cylinder jacket of internal combustion engine |
Country Status (6)
| Country | Link |
|---|---|
| EP (1) | EP0814243B1 (en) |
| JP (2) | JPH1054240A (en) |
| KR (1) | KR100560550B1 (en) |
| CN (1) | CN1093909C (en) |
| DE (1) | DE59610349D1 (en) |
| DK (1) | DK0814243T3 (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1093909C (en) * | 1996-06-20 | 2002-11-06 | 瓦特西拉瑞士有限公司 | Cooling system for cylinder jacket of internal combustion engine |
| CN103998756A (en) * | 2011-12-16 | 2014-08-20 | 卡特彼勒发动机有限及两合公司 | Cylinder liner and cylinder head for internal combustion engine |
| CN112901327A (en) * | 2019-11-19 | 2021-06-04 | 交通知识产权控股有限公司 | Coolant system for an engine and cylinder thereof and method of cooling an engine |
Families Citing this family (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20060086327A1 (en) * | 2004-10-25 | 2006-04-27 | General Electric Company | Engine power assembly |
| DE102005040637A1 (en) * | 2005-08-27 | 2007-03-01 | Deutz Ag | Internal combustion engine |
| JP5459503B2 (en) * | 2010-07-14 | 2014-04-02 | 株式会社Ｉｈｉ | Diesel engine cylinder bore corrosion prevention system |
| WO2017017717A1 (en) * | 2015-07-24 | 2017-02-02 | 日本郵船株式会社 | Device for specifying ease of occurrence of low-temperature corrosion in engine cylinder, program and recording medium |
| JP7241512B2 (en) | 2018-11-19 | 2023-03-17 | 株式会社ジャパンエンジンコーポレーション | cooling structure |
| EP3693566A1 (en) * | 2019-02-08 | 2020-08-12 | Winterthur Gas & Diesel AG | Cylinder assembly for a large-size engine and cooling method |
| CN111456863B (en) * | 2020-05-18 | 2024-05-07 | 安徽华菱汽车有限公司 | Cylinder sleeve cooling device capable of accurately shunting |
| DE102020120712A1 (en) | 2020-08-05 | 2022-02-10 | Audi Aktiengesellschaft | Drive device for a motor vehicle |
| CN114790951B (en) * | 2022-03-03 | 2024-02-13 | 深圳市燃气集团股份有限公司 | Method and related device for controlling cylinder liner water temperature of gas generator |
Family Cites Families (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB131719A (en) * | 1918-08-24 | 1919-08-25 | Vickers Ltd | Improvements in or relating to the Water Cooling of Internal Combustion Engines. |
| DE803449C (en) * | 1949-09-17 | 1951-04-02 | Buessing Nutzkraftwagen G M B | Circulation cooling for internal combustion engines |
| FR2225041A5 (en) * | 1973-04-03 | 1974-10-31 | Amiot F | |
| SE424348B (en) * | 1980-07-10 | 1982-07-12 | Nordstjernan Rederi Ab | PROCEDURE AND DEVICE FOR COOLING OF COMBUSTION ENGINE TO REDUCE CORROSIVE WEAR OF CYLINDER INLETS AND PISTON RINGS |
| JPS59185818A (en) * | 1983-04-06 | 1984-10-22 | Mitsubishi Heavy Ind Ltd | Cylinder liner cooling system of water-cooled engine |
| JPS6043119A (en) * | 1983-08-19 | 1985-03-07 | Toyota Motor Corp | Cooling apparatus for internal-combustion engine |
| JPS6170120A (en) * | 1984-09-13 | 1986-04-10 | Mitsubishi Heavy Ind Ltd | Cooling system of internal-combustion engine |
| FR2570439B1 (en) * | 1984-09-20 | 1989-03-31 | Semt | METHOD AND DEVICE FOR REGULATING THE TEMPERATURE OF THE INTERNAL SURFACE OF THE CYLINDER LINERS OF AN INTERNAL COMBUSTION ENGINE |
| JPH0713460B2 (en) * | 1986-04-25 | 1995-02-15 | 石川島播磨重工業株式会社 | Cylinder liner temperature control device for internal combustion engine |
| JPS63108514U (en) * | 1986-12-29 | 1988-07-13 | ||
| EP0814243B1 (en) * | 1996-06-20 | 2003-04-16 | Wärtsilä Schweiz AG | Cooling system for the cylinder jacket of an internal combustion engine |
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1996
- 1996-06-20 EP EP96810414A patent/EP0814243B1/en not_active Expired - Lifetime
- 1996-06-20 DK DK96810414T patent/DK0814243T3/en active
- 1996-06-20 DE DE59610349T patent/DE59610349D1/en not_active Expired - Fee Related
-
1997
- 1997-05-26 KR KR1019970020601A patent/KR100560550B1/en not_active IP Right Cessation
- 1997-06-17 CN CN97112732A patent/CN1093909C/en not_active Expired - Fee Related
- 1997-06-20 JP JP9164424A patent/JPH1054240A/en active Pending
-
2007
- 2007-11-14 JP JP2007295636A patent/JP2008057546A/en active Pending
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1093909C (en) * | 1996-06-20 | 2002-11-06 | 瓦特西拉瑞士有限公司 | Cooling system for cylinder jacket of internal combustion engine |
| CN103998756A (en) * | 2011-12-16 | 2014-08-20 | 卡特彼勒发动机有限及两合公司 | Cylinder liner and cylinder head for internal combustion engine |
| CN103998756B (en) * | 2011-12-16 | 2017-03-08 | 卡特彼勒发动机有限及两合公司 | Cylinder liner for explosive motor and cylinder head |
| CN112901327A (en) * | 2019-11-19 | 2021-06-04 | 交通知识产权控股有限公司 | Coolant system for an engine and cylinder thereof and method of cooling an engine |
| CN112901327B (en) * | 2019-11-19 | 2022-07-22 | 交通知识产权控股有限公司 | Coolant system for an engine and cylinder thereof and method of cooling an engine |
Also Published As
| Publication number | Publication date |
|---|---|
| DK0814243T3 (en) | 2003-06-02 |
| JPH1054240A (en) | 1998-02-24 |
| JP2008057546A (en) | 2008-03-13 |
| KR100560550B1 (en) | 2006-08-23 |
| DE59610349D1 (en) | 2003-05-22 |
| CN1093909C (en) | 2002-11-06 |
| EP0814243A1 (en) | 1997-12-29 |
| EP0814243B1 (en) | 2003-04-16 |
| KR980002682A (en) | 1998-03-30 |
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