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EP2503123A1 - Kühlsystem - Google Patents

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Publication number
EP2503123A1
EP2503123A1 EP11159335A EP11159335A EP2503123A1 EP 2503123 A1 EP2503123 A1 EP 2503123A1 EP 11159335 A EP11159335 A EP 11159335A EP 11159335 A EP11159335 A EP 11159335A EP 2503123 A1 EP2503123 A1 EP 2503123A1
Authority
EP
European Patent Office
Prior art keywords
radiator
exhaust gas
coolant
cooler
conduit
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP11159335A
Other languages
English (en)
French (fr)
Other versions
EP2503123B1 (de
Inventor
Kaj Johansson
John Nilsson
Ulf Jonason
Stefan Sundemo
Kjell Nilsson
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Volvo Car Corp
Original Assignee
Volvo Car Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Volvo Car Corp filed Critical Volvo Car Corp
Priority to EP11159335.6A priority Critical patent/EP2503123B1/de
Publication of EP2503123A1 publication Critical patent/EP2503123A1/de
Application granted granted Critical
Publication of EP2503123B1 publication Critical patent/EP2503123B1/de
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P3/00—Liquid cooling
    • F01P3/18—Arrangements or mounting of liquid-to-air heat-exchangers
    • F01P2003/185—Arrangements or mounting of liquid-to-air heat-exchangers arranged in parallel
    • 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
    • F01P5/00—Pumping cooling-air or liquid coolants
    • F01P5/10—Pumping liquid coolant; Arrangements of coolant pumps
    • F01P2005/105—Using two or more pumps
    • 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
    • F01P5/00—Pumping cooling-air or liquid coolants
    • F01P5/10—Pumping liquid coolant; Arrangements of coolant pumps
    • F01P5/12—Pump-driving arrangements
    • F01P2005/125—Driving auxiliary pumps electrically

Definitions

  • the present invention relates to the field of cooling systems, and more particularly, to exhaust gas recirculation (EGR) cooling systems for engines in vehicles.
  • EGR exhaust gas recirculation
  • EGR cooling systems comprising an EGR cooler in an EGR cooling circuit.
  • the EGR cooler is a heat exchanger installed in an EGR cooling circuit of a vehicle.
  • the EGR cooling system recirculates exhaust gas back to the engine in order to reduce nitrous oxide (NOx) emissions.
  • NOx nitrous oxide
  • the EGR cooler cools the exhaust gas prior to the exhaust gas is being reintroduced into the engine. By cooling the exhaust gas, the combustion temperature is reduced and since NOx emissions are formed at higher temperatures, this result in a reduction of NOx emissions.
  • the EGR cooling systems reduces NOx production by recirculating small amounts of exhaust gases into the intake manifold where it mixes with the incoming air/fuel charge. By diluting the air/fuel mixture under these conditions, peak combustion temperatures and pressure are reduced, resulting in overall reduction of NOx output.
  • the EGR cooling circuit takes coolant from a thermostat house, upstream of thermostat controlled valve, i.e. there is always a flow to the EGR cooling circuit independent of the position of the thermostat controlled valve (either closed or more or less open).
  • An open thermostat controlled valve is also called working thermostat controlled valve.
  • the coolant temperature to the EGR cooler is always relatively high. Coolant flow is substantially a function of water pump speed.
  • the present invention relates to the field of cooling systems, such as exhaust gas recirculation (EGR) cooling systems using radiator for vehicles. It is desirable to reduce the exhaust gas temperature as much as possible with low cost and with minimum space requirements.
  • EGR exhaust gas recirculation
  • the object of the present invention is to suggest an improved and easy to implement EGR cooling system which improves exhaust gas cooling without additional costs or additional heat exchangers or parts for reducing the exhaust gas temperature.
  • an aspect of the present invention is to provide an improved solution of regulating and directing the coolant to and from an EGR cooler in the EGR cooling system which seeks to mitigate, alleviate, or eliminate one or more of the above-identified deficiencies in the art and disadvantages singly or in any combination.
  • the object of the present invention is to provide a relatively cool coolant to the EGR cooler for all positions of a first thermostat controlled valve. Thereby, the exhaust gas temperature is reduced and the risk of breakdown of the EGR cooler is minimized for all possible positions of a first thermostat controlled valve.
  • a system for cooling exhaust gas for recirculation in an engine comprising a radiator for cooling engine coolant having an upstream water tank with a radiator inlet, a central radiator part and a downstream water tank with a first radiator outlet; a first cooling circuit having an upstream radiator conduit adapted to carry coolant from the engine to the first radiator inlet and a downstream radiator conduit adapted to carry coolant from the radiator outlet and to the engine; a bypass conduit connected between the upstream radiator conduit and the downstream radiator conduit adapted to allow coolant to bypass the radiator; a first thermostat controlled valve arranged in the upstream radiator conduit at the engine outlet and connected to the bypass conduit, the first thermostat controlled valve is adapted to direct coolant flow to the radiator and/or to the bypass conduit; an exhaust gas recirculation cooler for cooling exhaust gas comprised in an exhaust gas cooling circuit; characterised in that the downstream water tank and the central radiator part of the radiator is divided in a sub-cooler part having a second radiator outlet and a main part, wherein the exhaust
  • inventive EGR cooling system improves exhaust gas cooling efficiency without additional heat exchangers or parts.
  • inventive EGR cooling system provides coolant, via the radiator, at a low temperature to the EGR cooler. No additional parts or space are required in the inventive cooling system in order to reduce the exhaust gas temperature.
  • coolant to the exhaust gas recirculation cooler is provided from the radiator regardless of the position of the first thermostat controlled valve.
  • the inventive EGR cooling system regardless of the position of the first thermostat controlled valve, always provides relatively cool coolant to the EGR cooler. Thereby, the inventive EGR cooling system allow for an EGR cooler with reduced space requirements, while still being able to improve or maintain the cooling efficiency of the EGR cooling system.
  • the system further comprises an electrical water pump arranged in the exhaust gas cooling circuit between the sub-cooler part and the exhaust gas recirculation cooler providing a coolant flow through the exhaust gas recirculation cooler and the radiator.
  • the exhaust gas recirculation cooler is arranged in the exhaust gas cooling circuit between the electrical water pump and the downstream radiator conduit.
  • the relation between the amount of radiator pipes in the sub-cooler part and in the main part of the central part of the radiator of the may be varied.
  • the first thermostat controlled valve regulates and directs the coolant to the bypass when the coolant from the engine is below a threshold level. According to the invention, the first thermostat controlled valve regulates and directs coolant to the radiator when the coolant from the engine is above a threshold level.
  • the threshold value may be varied.
  • the system further comprises a transmission oil cooler arranged in a transmission oil cooling circuit and a second thermostat controlled valve arranged between the transmission oil cooling circuit and the exhaust gas cooling circuit for directing coolant flow to the transmission oil cooling circuit or to the exhaust gas cooling circuit.
  • the coolant flow may be regulated and directed between the transmission oil cooling circuit and the exhaust gas cooling circuit.
  • the transmission oil cooler is arranged in the transmission oil cooling circuit between the second thermostat controlled valve and the downstream radiator conduit.
  • the transmission oil cooler is connected in parallel with the exhaust gas recirculation cooler.
  • the second thermostat controlled valve regulates and directs the coolant flow to the transmission oil circuit at high load and high speed.
  • the second thermostat controlled valve regulates and directs the coolant flow to the exhaust gas recirculation circuit at low and low speed.
  • FIG. 1 refers to prior art and schematically shows an engine having an EGR cooling system.
  • the EGR cooling system comprises an EGR cooler 9 in an EGR cooling circuit.
  • the dotted lines and arrows represent the coolant circuits and flows to and from the engine where the EGR cooling circuit is marked in bold dotted lines.
  • Figure 1 shows an engine 4 having an engine inlet 4a and engine outlet 4b, a water pump 6, an engine oil cooler 7, a cabin heater 8, an exhaust gas recirculation cooler 9, a bypass conduit 3, a thermostat house 5 comprising a first thermostat controlled valve 12, an upstream radiator conduit 10, a radiator 2 and a downstream radiator conduit 11.
  • the EGR cooling circuit takes coolant from a thermostat house 5, upstream of the thermostat controlled valve 12, i.e.
  • FIG. 2 refers to prior art and schematically shows an engine having an EGR cooling system.
  • the dotted lines and arrows represent the coolant circuits and flows to and from the engine 4 where a super cooled EGR cooling circuit is marked in bold lines.
  • the super cooled EGR cooling system comprises an electrical water pump 13 and an EGR cooler 9 in an EGR cooling circuit.
  • An electrical water pump (EWP) 13 is used to create a flow through the EGR cooler 9 and the radiator 2, and since the radiator 2 is used in the super cooled EGR cooling circuit a relatively low coolant temperature is obtained for the EGR cooler 9 when the thermostat controlled vale 12 is closed.
  • EWP electrical water pump
  • FIG. 2 shows a super cooled EGR cooling system for a working thermostat, i.e. open thermostat controlled valve 12, (i.e. coolant temperature has reached the thermostat opening temperature or higher) having a clockwise coolant flow.
  • a working thermostat i.e. open thermostat controlled valve 12
  • coolant temperature has reached the thermostat opening temperature or higher
  • the coolant to the super cooled EGR cooling circuit is taken from the upstream radiator conduit 10.
  • the thermostat controlled valve 12 When the thermostat controlled valve 12 is open there is a flow out to the upstream radiator conduit 10.
  • coolant pressure and flow in the upstream radiator conduit 10 are different, wherein a small opening for the thermostat controlled valve 12, equals a small flow in the upstream radiator conduit 10 and a larger opening for the thermostat controlled valve 12, equals a larger flow in the upstream radiator conduit 10.
  • the EWP power creates a flow in clockwise direction and the resulting mixed flow in to the super cooled EGR cooling circuit has an increase in coolant temperature compared to the coolant temperature from the radiator 2 (the mixed flow consist of hot water from engine via upstream radiator conduit 10 and from the radiator 2).
  • the main disadvantage is that as soon as the thermostat controlled valve 12 is in an open position, coolant of relatively high temperature enters the super cooled EGR cooling circuit. Thereby, hot engine water enters the super cooled EGR cooling circuit resulting in reduced cooling efficiency.
  • the following examples of the present invention relate, in general, to the field of cooling systems, in particularly, to EGR cooling systems using a radiator for vehicles for providing relatively cool coolant for all positions of the thermostat controlled valve 12, i.e. thermostat strokes.
  • Figure 3 shows an example of an engine having an EGR cooling system 100 according to the invention for vehicles with manual transmission.
  • the dotted lines and arrows represent the coolant circuits and flows to and from an engine 104 where an EGR cooling circuit 115 is marked in bold lines.
  • the engine 104 includes an engine inlet 104a where coolant enters the engine 104 and an engine outlet 104b where coolant leaves the engine.
  • Figure 3 shows a water pump 106, an engine oil cooler 107, a cabin heater 108, a bypass conduit 103, a thermostat house 105 comprising a first thermostat controlled valve 112, an upstream radiator conduit 110, a radiator 102, a downstream radiator conduit 111, a EWP 113 and an EGR cooler 109.
  • the EWP 113 is arranged in the EGR cooling circuit 115.
  • the EWP 113 is adapted to be able to circulate coolant through the EGR cooling circuit 115.
  • the inventive EGR cooling circuit 115 is provided with coolant via the radiator 102.
  • the radiator 102 in the inventive EGR cooling system 100 is adapted to provide relatively cool coolant to the EGR cooler 109 for all possible positions of the first thermostat controlled valve 112.
  • the EGR cooler 109 is arranged in parallel to the engine 104.
  • the EGR cooler 109 cools the exhaust gas by heat exchange with coolant from the engine cooling system, the coolant passes the radiator 102 before being supplied to the EGR cooler 109.
  • coolant for EGR cooler 109 is circulated in the EGR cooling circuit 115 which is separate from a first cooling circuit, i.e. the engine cooling circuit, but uses the same radiator 102.
  • FIG 4 shows an example of the EGR cooling system 100 according to the invention for vehicles with manual transmission where the radiator 102 with an upstream water tank 119 and a downstream water tank 121 are viewed from the front.
  • the radiator 102 comprises a central radiator part 116, the upstream water tank 119, the downstream water tank 121, a radiator inlet 120, a first radiator outlet 122a and a second radiator outlet 122b.
  • the downstream water tank 121 is divided in two chambers providing a sub-cooler part 117 and main part 118, wherein relatively cool coolant is provided to the EGR cooler 109 at all positions of the first thermostat controlled valve 112.
  • the downstream water tank 121 is divided by a divider 123 which divides the downstream water tank 121 into an upper downstream part 121 a and a lower downstream part 121 b.
  • the upper downstream part 121 a has a second radiator outlet 122b.
  • the lower downstream part 121 b has a first radiator outlet 122a.
  • the sub-cooler part 117 comprises the upper downstream part 121 a of the downstream tank 121 and the upper part of the central radiator part 116.
  • the main part 118 comprises the lower downstream part 121 b of the downstream water tank 121 and the lower part of the central radiator part 116.
  • the connection for the EGR cooling circuit 115 is connected to the sub-cooler part 117 of the downstream tank 121. Whereby, coolant always flows via the radiator 102 before being supplied the EGR cooler 109. This advantageously allows for cooler exhaust gas, which may be used more effectively in the EGR cooling system 100.
  • the divider 123 is preferably made from a light plastic material.
  • the divider 123 and the downstream water tank 121 are preferably of the same material. However, the divider 123 may be made of any suitable material.
  • the position of the divider 123 may be adapted to be adjustable within the downstream water tank 121.
  • Figure 4 show an upstream radiator conduit flow 124 where coolant flow in the upstream radiator conduit from the first thermostat controlled valve, a downstream radiator conduit flow 125 where coolant flow in the downstream radiator conduit from the EGR cooler 109 and the main part 118 and a water pump flow 126 where coolant flow towards a water pump 106.
  • Fig. 5 schematically shows a front view pictorial representation of an EGR cooling system 100 according to the invention for vehicles with manual transmission when the first thermostat controlled valve 112 is closed.
  • a first coolant flow 127 circulate in the radiator 102 as shown in figure 5 .
  • This circulating first coolant flow 127 flows through the upstream water tank 119 to the sub-cooler part 117, out from the radiator 102 via the second radiator outlet 122b through the EWP 113, through the EGR cooler 109, through the downstream radiator conduit 111 and the main part 118 of the radiator 102 via the first radiator outlet 122a and back to the upstream water tank 119.
  • the flow direction through the sub-cooler 117 is opposite of the flow direction through the main part 118.
  • Fig. 6 schematically shows a front view pictorial representation of an EGR cooling system 100 according to the invention for vehicles with manual transmission when the working first thermostat controlled valve is open.
  • a second coolant flow 128 flows in the radiator 102 as shown in figure 6 .
  • the upstream radiator conduit flow 124 flows in the upstream radiator conduit 110 through the radiator inlet 120 into the upstream water tank 119 of the radiator 102, wherein the second coolant flow 128 have the same flow direction through both the sub-cooler part 117 and the main part 118.
  • the inventive EGR cooling system 100 provides a relatively cool coolant to the EGR cooler 109 even when the flow pressure is such that the EWP 113 power is not enough to circulate the coolant. This since coolant always flows via the radiator 102 to the EGR cooling circuit 115 and the EGR cooler 109 regardless of the position of the first thermostat controlled valve 112.
  • Fig. 7 schematically shows a front view pictorial representation of an EGR cooling system 100 according to the invention for vehicles with automatic transmission.
  • Vehicles with automatic transmission normally need a transmission oil cooler 130 in cooling performance driving conditions.
  • the requirement of cooling the transmission oil cooler 130 and the EGR cooler 109 do not occur at the same time.
  • the EGR cooling circuit with the EWP 113 is used i.e. coolant flow through the EGR cooling circuit, for a vehicle with low load and low speed.
  • the transmission oil cooling circuit with the transmission oil cooler 130 is used, i.e. coolant flow through the transmission oil cooling circuit, at high load and high speed.
  • a second thermostat controlled valve 129 or an electric valve it is possible to move the coolant flow between the EGR cooling circuit and the transmission oil cooling circuit.
  • the opening temperature of this second thermostat controlled valve 129 may be set at a higher temperature than the first thermostat controlled valve 112.
  • the EGR cooler 109 is arranged in parallel to the transmission oil cooler 130 and to the second thermostat controlled valve 129.
  • the position of the divider 123 may be adjusted if the coolant flow to the transmission oil cooler needs to be adjusted.
  • the position of the divider 123 determines to the amount of radiator pipes in the sub-cooler part 117 and the main part 118 of the central part 116 of the radiator 102.
  • the amount of radiator pipes in the radiator 102 for the sub-cooler part 117 may be selected depending on the coolant flow demand to the transmission oil cooler 130.
  • the EGR cooling system 100 may be used for any type of appropriate engine in any type appropriate vehicle in the form of, for example, a car, a truck, a bus or other vehicle using radiator 102.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Exhaust-Gas Circulating Devices (AREA)
EP11159335.6A 2011-03-23 2011-03-23 Kühlsystem Active EP2503123B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP11159335.6A EP2503123B1 (de) 2011-03-23 2011-03-23 Kühlsystem

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP11159335.6A EP2503123B1 (de) 2011-03-23 2011-03-23 Kühlsystem

Publications (2)

Publication Number Publication Date
EP2503123A1 true EP2503123A1 (de) 2012-09-26
EP2503123B1 EP2503123B1 (de) 2018-09-05

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ID=44486079

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Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103114902A (zh) * 2012-10-31 2013-05-22 浙江吉利罗佑发动机有限公司 一种发动机冷却水泵总成及其流量控制方法
CN105720740A (zh) * 2014-12-18 2016-06-29 通用汽车环球科技运作有限责任公司 确定用于发热装置的冷却剂流体的有效温度的方法和设备
CN112594051A (zh) * 2020-12-10 2021-04-02 潍柴重机股份有限公司 一种柴油机高温冷却水温度的控制方法及控制系统
CN114035620A (zh) * 2022-01-10 2022-02-11 南京欧诺智能装备有限公司 用于模温机的智能流量控制方法及系统

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2435041A (en) * 1945-02-10 1948-01-27 Frederic W Hild Regulating device for cooling systems
EP1475532A2 (de) * 2003-05-06 2004-11-10 Denso Corporation Thermoelektrischer generator
EP1681456A1 (de) * 2004-12-27 2006-07-19 Valeo Systemes Thermiques Anlage zur thermischen Regelung des in einen Motor eingelassenen Gases
FR2883807A1 (fr) * 2005-04-01 2006-10-06 Renault Sas Dispositif et procede de refroidissement du moteur et d'un organe de vehicule
FR2883806A1 (fr) * 2005-03-31 2006-10-06 Valeo Systemes Thermiques Installation et procede de refroidissement d'un equipement de vehicule automobile
FR2884864A1 (fr) * 2005-04-25 2006-10-27 Renault Sas Dispositif et procede de refroidissement du moteur et d'un organe de vehicule
DE102006048527A1 (de) * 2006-10-13 2008-04-17 Volkswagen Ag Kühlkreislauf für eine Brennkraftmaschine
JP2011047305A (ja) * 2009-08-26 2011-03-10 Toyota Motor Corp 内燃機関

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2435041A (en) * 1945-02-10 1948-01-27 Frederic W Hild Regulating device for cooling systems
EP1475532A2 (de) * 2003-05-06 2004-11-10 Denso Corporation Thermoelektrischer generator
EP1681456A1 (de) * 2004-12-27 2006-07-19 Valeo Systemes Thermiques Anlage zur thermischen Regelung des in einen Motor eingelassenen Gases
FR2883806A1 (fr) * 2005-03-31 2006-10-06 Valeo Systemes Thermiques Installation et procede de refroidissement d'un equipement de vehicule automobile
FR2883807A1 (fr) * 2005-04-01 2006-10-06 Renault Sas Dispositif et procede de refroidissement du moteur et d'un organe de vehicule
FR2884864A1 (fr) * 2005-04-25 2006-10-27 Renault Sas Dispositif et procede de refroidissement du moteur et d'un organe de vehicule
DE102006048527A1 (de) * 2006-10-13 2008-04-17 Volkswagen Ag Kühlkreislauf für eine Brennkraftmaschine
JP2011047305A (ja) * 2009-08-26 2011-03-10 Toyota Motor Corp 内燃機関

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103114902A (zh) * 2012-10-31 2013-05-22 浙江吉利罗佑发动机有限公司 一种发动机冷却水泵总成及其流量控制方法
CN103114902B (zh) * 2012-10-31 2015-05-13 浙江吉利罗佑发动机有限公司 一种发动机冷却水泵总成及其流量控制方法
CN105720740A (zh) * 2014-12-18 2016-06-29 通用汽车环球科技运作有限责任公司 确定用于发热装置的冷却剂流体的有效温度的方法和设备
US9846002B2 (en) 2014-12-18 2017-12-19 GM Global Technology Operations LLC Method and apparatus to determine an effective temperature of coolant fluid for a heat generating device
CN105720740B (zh) * 2014-12-18 2018-07-13 通用汽车环球科技运作有限责任公司 确定用于发热装置的冷却剂流体的有效温度的方法和设备
CN112594051A (zh) * 2020-12-10 2021-04-02 潍柴重机股份有限公司 一种柴油机高温冷却水温度的控制方法及控制系统
CN112594051B (zh) * 2020-12-10 2021-12-21 潍柴重机股份有限公司 一种柴油机高温冷却水温度的控制方法及控制系统
CN114035620A (zh) * 2022-01-10 2022-02-11 南京欧诺智能装备有限公司 用于模温机的智能流量控制方法及系统

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