FI124754B

FI124754B - Menetelmä polttomoottorin käyttämiseksi

Info

Publication number: FI124754B
Application number: FI20136024A
Authority: FI
Inventors: Andreas Westerlund; Matias Björklund; Andreas Hjort
Original assignee: Wärtsilä Finland Oy
Priority date: 2013-10-16
Filing date: 2013-10-16
Publication date: 2015-01-15
Also published as: EP3066313B1; KR20160042185A; EP3066313A1; CN105637192B; KR101671680B1; CN105637192A; WO2015055891A1; FI20136024A

Description

Method for operating an internal combustion engine

TECHNICAL FIELD

[001] The present invention relates to a method for operating a turbocharged internal combustion engine, which comprises a cooling liquid circuit for engine cooling liquid, in which method - charge air is pressurised at a turbo charger, - the pressurised charge air is cooled by a charge air cooler, - a dew point of the pressurised charge air downstream of the charge air cooler is defined, and - the temperature of the charge air leaving the charge air cooler is adjusted to be higher than the dew point by controlling temperature of the cooling liquid fed into the charge air cooler, - lubrication oil for engine lubrication in a lubrication oil circuit is cooled by a lubrication oil cooler.

BACKGROUND OF THE INVENTION

[002] In turbocharged internal combustion piston engines the pressure of the charge air is increased at least in one stage by a compressor. After the compressor, the pressurised charge air is typically cooled by a charge air cooler. If charge air pressure, temperature and humidity are at a certain level, water vapour in charge air condenses into water. Condense (water droplets, mist) may cause corrosion and erosion to the engine components, e.g. turbocharger compressor impeller (in 2-stage turbocharging), charge air receiver, inlet channels and inlet valves. The amount of condense can be high especially on high pressure side of the charge air system if the humidity of the intake air is high. The dew point is the temperature where water vapour condenses into liquid water.

[003] With two stage turbo charged engines, the boost pressure is high and also the temperature of charged air is high. This causes some challenges for the cooling water system design and control: The charge air cooling need is high compared to a single stage turbo charged engine. The combustion air or receiver air, or charge air as it is called here, temperature must be kept low for avoiding knock in certain engine types. Especially in dry conditions cold charge air is needed. Correspondingly humid conditions increases the knock margin and thus higher receiver air temp can be allowed in humid conditions. Also the lubrication oil temperature must be kept within limits for safe operation of the engine.

[004] It is known from the state of art a document WO 2011/073512 disclosing a method of operating a turbocharged piston engine, which comprises a low-temperature cooling circuit for low-temperature cooling liquid, a high-temperature cooling circuit for high-temperature cooling liquid, and a charge air cooler connected to the low-temperature cooling circuit. In the method charge air is pressurised at least in one stage, the pressurised charge air is cooled by the charge air cooler into which low-temperature cooling liquid is fed, a dew point of the pressurised charge air downstream of the charge air cooler is defined, and temperature of the charge air leaving the charge air cooler is adjusted to be higher than the dew point by controlling temperature of the low-temperature cooling liquid fed into the charge air cooler. The temperature of the low-temperature cooling liquid is controlled by adding high-temperature cooling liquid thereto.

SUMMARY OF THE INVENTION

[005] The objective of the present invention is to improve further the control of the charge air in a turbo charged engine, especially in a two stage turbo charged engine.

[006] The present invention comprises a method wherein there are provided at least two lubrication oil coolers which are configured to the cooling liquid circuit so that one lubrication oil cooler is connected to an upstream position in relation to the charge air cooler and one lubrication oil cooler is connected to a downstream position in relation to the charge air cooler, the temperature of the charge air after said charge air cooler is kept higher than corresponding dew point and the temperature of the lubrication oil is kept within an operational range by controlling the heat exchange power of said lubrication oil coolers.

[007] Clear benefits can be achieved by means of the invention. The amount of condense in the charge air system can be reduced, which in turn reduces corrosion and erosion damages of the engine components. Also the controllability of the engine lubrication oil and cooling liquid is improved, it is easier to ensure that the temperature of the returning lubrication oil is at optimum range. A term excess heat is used within this description to describe the amount of heat or heating power causing a rise of temperature of the relevant medium above the target or wanted temperature range.

BRIEF DESCRIPTION OF DRAWINGS

[008] In the following the invention will be described with the reference to the accompanying drawings where

Fig. 1 presents a general schematic view of the present piston engine,

Fig 2. presents an embodiment of the present piston engine schematic,

Fig 3. present another embodiment of the present piston engine schematic, Figs. 4 to 13 presents different alternatives to arrange the lubrication oil circuit and the cooling liquid circuit in respect to each others.

DETAILED DESCRIPTION

[009] Figure 1 is a schematic view of the piston engine 1. The engine 1 comprises in that embodiment one turbocharger compressor 6. The engine 1 is a reciprocating internal combustion comprising multiple cylinders 3. The engine is used, for example, as main and auxiliary engines in ships and in power plants. The method of operating this turbocharged internal combustion engine 1, which comprises a cooling liquid circuit 13 for engine 1 cooling liquid, is the following: - charge air in an inlet channel 2 is pressurised at a turbo charger 6, - the pressurised charge air is cooled by a charge air cooler 10, - a dew point Td of the pressurised charge air downstream of the charge air cooler 10 is defined, and - the temperature of the charge air leaving the charge air cooler 10 is adjusted to be higher than the dew point Td by controlling temperature of the cooling liquid fed into the charge aircooler 10, - lubrication oil for engine lubrication in a lubrication oil circuit 15 is cooled by a lubrication oil cooler 14a, 14b, - there are provided at least two lubrication oil coolers 14a, 14b which are configured to the cooling liquid circuit 13 so that one lubrication oil cooler 14a is connected to an upstream position in relation to the charge air cooler 11 and one lubrication oil cooler 14b is connected to a downstream position in relation to the charge air cooler 10, the temperature of the charge air after said charge air cooler 10 is kept higher than corresponding dew point Td and the temperature of the lubrication oil is kept within an operational range Tlo by controlling the heat exchange power of said lubrication oil coolers 14a, 14b. The cooling liquid is conducted through a radiator 18 (when needed) to remove the excess heat from the cooling liquid, and then the cooling liquid is returned to the circulation 13. In the Figs. 1 to 3 it is not presented a direction of circulation for lubrication oil in the lubrication oil circuit 15 because it can be arranged according to different alternatives which are presented in more detail in Figs. 4 to 13. The operational range Tlo of the lubrication oil temperature means the temperature of the lubrication oil by an inlet of engine, shown only schematically in the figures.

[010] The dew point Td (or Td1, Td2 in figures 2 and 3) of the charge air is defined on the basis of the measurements of charge air pressure, temperature and humidity. There are many options to do this in practise, but these are not explained here in more detail.

[011] In Fig. 2 it is presented an embodiment of the invention wherein. - charge air is pressurised at a first stage by a low pressure turbo charger 6, - the charge air pressurised at the first stage is cooled by a low pressure charge air cooler 11 - a first dew point Td1 of the pressurised charge air downstream of the low pressure charge air cooler 11 is defined, and - the temperature of the charge air leaving the low pressure charge air cooler 11 is adjusted to be higher than the first dew point Td1 by controlling temperature of the cooling liquid fed into the low pressure charge air cooler 11, - charge air is pressurised at a second stage by a high pressure turbo charger 9, - the charge air pressurised at the second stage is cooled by a high pressure charge air cooler 12, - a second dew point Td2 of the pressurised charge air downstream of the high pressure charge air cooler 12 is defined, and - the temperature of the charge air leaving the high pressure charge air cooler 12 is adjusted to be higher than the second dew point Td2 by controlling temperature of the cooling liquid fed into the high pressure charge air cooler 12, - there are provided at least two lubrication oil coolers 14a, 14b which are configured to the cooling liquid circuit 13 so that one lubrication oil cooler 14a is connected to an upstream position in relation to the high pressure charge air cooler 12 and one lubrication oil cooler 14b is connected to a downstream position in relation to the low pressure charge air cooler 11, the temperatures of the charge air after said low pressure charge air cooler 11 and after said high pressure charge air cooler 12 are kept higher than corresponding dew points Td1, Td2 and the temperature of the lubrication oil is kept within an operational range Tlo by controlling the heat exchange power of said lubrication oil coolers 14a, 14b. This enables safe operation of the engine by having means for keeping the relevant temperatures within safe and well functioning ranges. The heat exchange power means the power or rate of heat transfer at the heat exchanger, so basically the amount of heat transfered per time unit.

[012] The embodiments of Fig. 1 and Fig. 2 presents a configuration, where the excess heat of lubrication oil, or more precisely the heat exchange power is divided between said lubrication oil coolers 14a, 14b. This can be done for example so that the heat exchange power of at least one of the lubrication oil coolers 14a, 14b is controllable by adjusting the flow of lubrication oil throught a bypass channel 14a1, 14b1. The adjustment of flow through the bypass channel 14a1, 14b1 or through the heat exchanger 14a, 14b can be done with a valve connected to said bypass channel or intersection of the line to the heat exchanger and the bypass channel. When the lubrication oil runs throught the bypass channel the flow through the heat exchanger diminishes. This causes the amount of heat transfered from a circuit to another to diminish, so the fluid inlet and outlet temperatures are more close to each others, thus the heat exchange power in that particular bypassed (or partially bypassed) heat exchanger is smaller. So for example if the valve in connection with bypass channel 14a1 is opened, the heat exchanger 14a receives less lubrication oil and therefore the heat exchange power is smaller. In general a bypass channel can be arraged to a primary circuit or to a secondary circuit of a heat exchanger. This means that the bypass channel can be at the lubrication oil circuit 15 or at the cooling liquid circuit 13 of the lubrication oil cooler 14a, 14b to control the heat exchange power of said lubrication oil cooler.

[013] In Fig. 3 it is presented a further embodiment having most of the features the same with the embodiment of Fig. 2, but in addition the low pressure charge air cooler 11 is divided in two stages, stage one 111 and stage two 112. This enables even more precise adjustment of heat exchange power or heat transfer between the three fluids: the charge air, the lubrication oil and the cooling liquid.

[014] The lubrication oil coolers 14a, 14b are configurable to at least three basic mode alternatives which can be selected based on initial charge air properties, one for cold charge air, one for hot and dry charge air and one for hot and moist charge air. Basically this can be done with the embodiments of Fig. 1, Fig. 2 and Fig. 3, but the embodiment of Fig. 3 gives the more advanced tools to perform the task. In the following the three ambient air property dependent configurations are explained in more detail.

[015] The mode for cold charge air comprises a configuration where the lubrication oil cooler 14b is in the cooling liquid circuit 13 at the position downstream of the low pressure charge air cooler 11, 112 and where the excess heat of lubrication oil is transfered to the cooling liquid.

[016] The mode for hot and dry charge air comprises a configuration where the lubrication oil cooler 14b is in the cooling liquid circuit 13 at the position downstream of a stage two of low pressure charge air cooler 11, 112 where the majority of excess heat of lubrication oil is transfered to the cooling liquid, the majority of excess low pressure charge air heat is transfered at a stage one of low pressure charge air cooler 111 to the cooling liquid circuit.

[017] The mode for hot and humid charge air comprises a configuration where one lubrication oil cooler 14b is in the cooling liquid circuit 13 at the position downstream of a stage two of low pressure charge air cooler 112 where a major part of excess heat of lubrication oil is transfered to the cooling liquid and a minor part of excess heat of lubrication oil is transfered to the cooling liquid at a second lubrication oil cooler 14a, which is connected in the cooling liquid circuit 13 at a position upstream of high pressure charge air cooler 12, a major part of low pressure charge air excess heat is transfered at a stage one of low pressure charge air cooler 111 to the cooling liquid circuit 13.

[018] In figures 4 to 13 there are schematically presented several embodiments to configure the lubrication oil coolers 14a, 14b, bypasses 14a1, 14a2, 14b1, 14b2, charge air cooler 10, engine 1, cooling liquid circuit 13 and lubrication oil circuit 15. Flere they are shortly noted: - Fig 4: lubrication oil bypass 14a1, 14b1 for both lubrication oil coolers 14a, 14b, - Fig. 5: cooling liquid bypass 14a2, 14b2 for both lubrication oil coolers 14a, 14b. - Fig 6: lubrication oil bypass 14a1 for lubrication oil cooler 14a and cooling liquid bypass 14b2 for lubrication oil cooler 14b. - Fig. 7: cooling liquid bypass 14a2 for lubrication oil cooler 14 and lubrication oil bypass 14b1 for lubrication oil cooler 14b.

In Fig. 8 to Fig. 13 the direction of circulation of lubrication oil is reversed in relation to Fig. 4. to Fig. 7. - Fig. 8: lubrication oil bypass 14a1 for lubrication oil cooler 14a. - Fig. 9: lubrication oil bypass 14a1, 14b1 for both lubrication oil coolers 14a, 14b. - Fig. 10: cooling liquid bypass 14a2 for lubrication oil cooler 14a. - Fig. 11: cooling liquid bypass 14a2, 14b2 for both lubrication oil coolers 14a, 14b. - Fig. 12: lubrication oil bypass 14a1 for lubrication oil cooler 14a and cooling liquid bypass 14b2 for lubrication oil cooler 14b. - Fig. 13: cooling liquid bypass 14a2 for lubrication oil cooler 14a and lubrication oil bypass 14b1 for lubrication oil cooler 14b.

Basically the presented embodiments are quite equal in controllability, but it depends more about other factors and the engine / powerplant layout or design and such which is in practise the most attractive option.

[019] For the purpose of advanced controllability the heat exchangers are advantageously reasonable oversized so that the bypass channels can be used effectively. If the heat exchangers are just in the limit of the capacity, the effect of a bypass channel is somewhat deteriorated.

[020] As evident to those skilled in the art, the invention and its embodiments are not limited to the above-described embodiment examples. Expressions representing the existence of characteristics, such as "the engine comprises a cooling liquid circuit", are non-restrictive such that the description of characteristics does not exclude or prerequisite the existence of such other characteristics which are not presented in the independent or dependent claims.

Reference signs in Figures: 1 engine 2 inlet channel 3 cylinders 4 exhaust channel 6 turbo charger, low pressure turbo charger (compressor) 9 high pressure turbo charger (compressor) 10 charge air cooler 11 low pressure charge air cooler 111 stage one of low pressure charge air cooler 112 stage two of low pressure charge air cooler

Td1 first dew point 12 high pressure charge air cooler

Td2 second dew point 13 cooling liquid circuit 14a lubrication oil cooler 14a1 lubrication oil cooler bypass (oil) 14a2 lubrication oil cooler bypass (cooling liquid) 14b lubrication oil cooler 14b1 lubrication oil cooler bypass (oil) 14b2 lubrication oil cooler bypass (cooling liquid) 15 lubrication oil circuit 18 heat exchanger, radiator

Claims

1. Menetelmä turboahdetun polttomoottorin (1), joka käsittää jäähdytysnes-tepiirin (13) moottorin (1) jäähdytysnesteelle, käyttämiseksi, jossa menetelmässä - paineistetaan ahtoilmaa turboahtimessa (6), -jäähdytetään paineistettu ilmaahtoilmajäähdyttimellä (10), - määritellään paineistetun ilman kastepiste (Td) myötäsuuntaan ahtoilmajääh-dyttimestä (10), ja - säädetään ahtoilmajäähdyttimestä (10) lähtevän ahtoilman lämpötila kaste-pistettä (Td) korkeammaksi ahtoilmajäähdyttimeen (10) syötetyn jäähdytysnesteen lämpötilaa säätelemällä, -jäähdytetään moottorin voiteluun tarkoitettua, voiteluöljypiirissä (15) olevaa voiteluöljyä voiteluöljyjäähdyttimellä (14a, 14b), - pidetään ahtoilman lämpötila mainitun ahtoilmajäähdyttimen (10) jälkeen vastaavaa kastepistettä (Td) korkeammalla, tunnettu siitä, että - on järjestetty käyttöön ainakin kaksi voiteluöljyjäähdytintä (14a, 14b), jotka on konfiguroitu jäähdytysnestepiiriin (13) niin, että toinen voiteluöljyjäähdytin (14a) on liitetty vastasuunnassa sijaitsevaan kohtaan suhteessa ahtoilmajäähdyttimeen (11), ja toinen voiteluöljyjäähdytin (14b) on liitetty myötäsuunnassa sijaitsevaan kohtaan suhteessa ahtoilmajäähdyttimeen (10), ja voiteluöljyn lämpötila pidetään käyttöalueella (Tlo) mainittujen voiteluöljyjäähdyttimien (14a, 14b) lämmönsiirtotehoa säätelemällä.

2. Patenttivaatimuksen 1 mukainen menetelmä, jossa - paineistetaan ahtoilmaa ensimmäisessä vaiheessa matalapaineturboahtimel-la (6), - jäähdytetään ensimmäisessä vaiheessa paineistettua ahtoilmaa matala-paineahtoilmajäähdyttimellä (11,111,112), - määritellään paineistetun ahtoilman ensimmäinen kastepiste (Td1) myötäsuuntaan matalapaineahtoilmajäähdyttimestä (11,111,112), - säädetään matalapaineahtoilmajäähdyttimestä (11,111,112) lähtevän ahtoilman lämpötila ensimmäistä kastepistettä korkeammaksi matalapaineahtoilmajäähdyttimeen (11,111,112) syötetyn jäähdytysnesteen lämpötilaa säätelemällä, - paineistetaan ahtoilmaa toisessa vaiheessa korkeapaineturboahtimella (9), - jäähdytetään toisessa vaiheessa paineistettua ahtoilmaa korkeapaineahtoil-majäähdyttimellä (12), - määritellään paineistetun ahtoilman toinen kastepiste (Td2) myötäsuuntaan korkeapaineahtoilmajäähdyttimestä (12), ja - säädetään korkeapaineahtoilmajäähdyttimestä (12) lähtevän ahtoilman lämpötila toista kastepistettä (Td2) korkeammaksi korkeapaineahtoilmajäähdyttimeen (12) syötetyn jäähdytysnesteen lämpötilaa säätelemällä, - on järjestetty käyttöön ainakin kaksi voiteluöljyjäähdytintä (14a, 14b), jotka on konfiguroitu jäähdytysnestepiiriin (13) niin, että toinen voiteluöljyjäähdytin (14a) on liitetty vastasuunnassa sijaitsevaan kohtaan suhteessa korkeapaineahtoil-majäähdyttimeen (12), ja toinen voiteluöljyjäähdytin (14b) on liitetty myötä-suunnassa sijaitsevaan kohtaan suhteessa matalapaineahtoilmajäähdyttimeen (11, 111, 112), jolloin ahtoilman lämpötilat mainitun matalapaineahtoilmajääh-dyttimen (11,111,112) ja mainitun korkeapaineahtoilmajäähdyttimen (12) jälkeen pidetään vastaavia kastepisteitä (Td1, Td2) korkeampina, ja voiteluöljyn lämpötila pidetään käyttöalueella (Tlo) mainittujen voiteluöljyjäähdyttimien (14a, 14b) lämmönsiirtotehoa säätelemällä.

3. Patenttivaatimuksen 1 mukainen menetelmä, tunnettu siitä, että mainittu lämmönsiirtoteho jaetaan mainittujen voiteluöljyjäähdyttimien (14a, 14b) kesken.

4. Patenttivaatimuksen 1 tai 2 mukainen menetelmä, tunnettu siitä, että ainakin toisen voiteluöljyjäähdyttimistä (14a, 14b) lämmönsiirtoteho on säädeltävissä voiteluöljyvirtausta ohituskanavan (14a1,14b1) kautta säätelemällä.

5. Jonkin patenttivaatimuksista 1 - 3 mukainen menetelmä, tunnettu siitä, että ainakin toisen voiteluöljyjäähdyttimistä (14a, 14b) lämmönsiirtoteho on säädeltävissä jäähdytysnestevirtausta ohituskanavan (14a2,14b2) kautta säätelemällä.

6. Patenttivaatimuksen 1 mukainen menetelmä, tunnettu siitä, että voitelu-öljyjäähdyttimet (14a, 14b) ovat konfiguroitavissa ainakin kolmeen, ahtoilman alkuominaisuuksien perusteella valittavissa olevaan perusvaihtoehtoon, joista yksi on kylmää ahtoilmaa varten, yksi kuumaa ja kuivaa ahtoilmaa varten ja yksi kuumaa ja kosteaa ahtoilmaa varten.

7. Patenttivaatimuksen 5 mukainen menetelmä, tunnettu siitä, että kylmää ahtoilmaa varten oleva vaihtoehto käsittää konfiguraation, jossa voiteluöljy-jäähdytin (14b) on jäähdytysnestepiirissä (13) myötäsuuntaan matalapaineah-toilmajäähdyttimestä (11,112) sijaitsevassa kohdassa ja jossa voiteluöljyn liika-lämpö siirtyy jäähdytysnesteeseen.

8. Patenttivaatimuksen 5 mukainen menetelmä, tunnettu siitä, että matala-paineahtoilmajäähdytin on jaettu kahteen vaiheeseen.

9. Patenttivaatimuksen 6 mukainen menetelmä, tunnettu siitä, että kuumaa ja kuivaa ahtoilmaa varten oleva vaihtoehto käsittää konfiguraation, jossa voi-teluöljyjäähdytin (14b) on jäähdytysnestepiirissä (13) myötäsuuntaan matala-paineahtoilmajäähdyttimen (11, 112) vaiheesta kaksi sijaitsevassa kohdassa, jolloin suurin osa voiteluöljyn liikalämmöstä siirtyy jäähdytysnesteeseen, jolloin suurin osa matalapaineahtoilman liikalämmöstä siirtyy matalapaineahtoilma-jäähdyttimen (111) vaiheessa yksi jäähdytysnestepiiriin.

10. Patenttivaatimuksen 6 mukainen menetelmä, tunnettu siitä, että kuumaa ja kosteaa ahtoilmaa varten oleva vaihtoehto käsittää konfiguraation, jossa toinen voiteluöljyjäähdytin (14b) on jäähdytysnestepiirissä (13) myötäsuuntaan matalapaineahtoilmajäähdyttimen (112) vaiheesta kaksi sijaitsevassa kohdassa, jolloin suuri osa voiteluöljyn liikalämmöstä siirtyy jäähdytysnesteeseen, ja pieni osa voiteluöljyn liikalämmöstä siirtyy jäähdytysnesteeseen toisessa voite-luöljyjäähdyttimessä (14a), joka on liitetty jäähdytysnestepiirissä (13) vas-tasuuntaan korkeapaineahtoilmajäähdyttimestä (12) sijaitsevaan kohtaan, jolloin suuri osa matalapaineahtoilman liikalämmöstä siirtyy matalapaineahtoilma-jäähdyttimen (111) vaiheessa yksi jäähdytysnestepiiriin (13).

11. Patenttivaatimuksen 2 mukainen menetelmä, tunnettu siitä, että ahtoil-man kastepiste (Td1, Td2) määritellään ahtoilman paineen, lämpötilan ja kosteuden mittausten perusteella.