JP2003278607A - Egr cooler - Google Patents
Egr coolerInfo
- Publication number
- JP2003278607A JP2003278607A JP2002076275A JP2002076275A JP2003278607A JP 2003278607 A JP2003278607 A JP 2003278607A JP 2002076275 A JP2002076275 A JP 2002076275A JP 2002076275 A JP2002076275 A JP 2002076275A JP 2003278607 A JP2003278607 A JP 2003278607A
- Authority
- JP
- Japan
- Prior art keywords
- evaporator
- condenser
- refrigerant
- egr cooler
- egr
- 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.)
- Pending
Links
Classifications
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/12—Improving ICE efficiencies
Landscapes
- Exhaust-Gas Circulating Devices (AREA)
Abstract
Description
【発明の詳細な説明】
【０００１】
【発明の属する技術分野】本発明は吸気系に還流される
ＥＧＲガスを冷却するＥＧＲクーラに係り、特に、エン
ジン冷却系の負荷を軽減することができるＥＧＲクーラ
に関するものである。
【０００２】
【従来の技術】吸気系に還流されるＥＧＲガスを冷却し
て燃焼温度の上昇を抑制するために、近年ではＥＧＲク
ーラを設けることが多い。しかしながら、従来ではエン
ジン冷却水の一部を利用してＥＧＲガスを冷却するよう
にしていたために、ＥＧＲガス流量が増加するとエンジ
ン冷却系の熱負荷が大きくなるために、ラジエータおよ
びウォータポンプなどを大容量化する必要性があった。
また、エンジン冷却系とＥＧＲクーラの冷却系を独立さ
せた場合においても、ウォータポンプなどの強制循環手
段を設ける必要性があるために、いずれの場合にもＥＧ
Ｒシステムのコストが上昇してしまうという不具合があ
った。
【０００３】
【発明が解決しようとする課題】本発明は上記実情に鑑
みてなされたものであって、ウォータポンプなどの強制
循環手段を用いる必要性がなく、しかも、エンジン冷却
系の熱負荷の増加をもたらすことがないＥＧＲクーラを
提供することを課題としている。
【０００４】
【課題を解決するための手段】上記課題を解決するため
に本発明は、排気系から吸気系に還流されるＥＧＲガス
と冷媒を熱交換させる沸騰式のエバポレータと、エンジ
ン冷却系から独立して設けられて前記エバポレータで発
生した蒸気を外気との熱交換で凝縮させるコンデンサを
備えている。また、前記コンデンサをエバポレータより
高所に配設している。そして、コンデンサの底部から延
びる復路の先端をエバポレータに接続する一方、エバポ
レータの頂部から延びる往路の先端を復路との接続位置
より離れた位置においてコンデンサに接続したことを特
徴としている。
【０００５】
【発明の実施の形態】以下に本発明の実施形態を図に基
づいて詳細に説明する。図１は本発明に係るＥＧＲクー
ラを備えた過給式ディーゼルエンジンの概略平面図、図
２はＥＧＲクーラの第１実施形態を示す概略正面図であ
る。
【０００６】これらの図において、ディーゼルエンジン
１の排気マニホールド２から分岐して吸気マニホールド
３に至るＥＧＲ通路４にはＥＧＲクーラ５を介装してい
る。
【０００７】ＥＧＲクーラ５は、ＥＧＲ通路４を流れる
ＥＧＲガスと冷媒を熱交換させる沸騰式のエバポレータ
６と、エンジン冷却系から独立して設けたコンデンサ７
で主要部が構成される。また、コンデンサ７をエバポレ
ータ５より高所に配設したうえで、コンデンサ７の底部
から延びる復路８の先端をエバポレータ６の底部に接続
するとともに、エバポレータ６の頂部から延びる往路９
を復路８との接続位置より高所である頂部空間において
コンデンサ７に接続している。
【０００８】そして、外気との間の熱交換容量を大きく
するためのフィンなどをコンデンサ７の外側面または内
側に設けることにより、前記エバポレータ５で発生して
往路９からコンデンサ７に送り込まれた蒸気を、例えば
自動車の走行風あるいはエンジンのクーリングファンで
誘起された風などとの間で熱交換させて凝縮させるよう
にしている。なお、図１中１０は排気ターボチャージャ
であり、該排気ターボチャージャ１０から吐出された空
気は、図示しないインタークーラで冷却された後に、吸
気マニホールド３に導かれてＥＧＲガスとともにエンジ
ン１の燃焼室に供給される。
【０００９】かかる構成になるＥＧＲクーラにおいて、
エバポレータ６においてＥＧＲガスとの間で熱交換され
た冷媒は、時間の経過とともに温度上昇して比重が次第
に小さくなる。また、ＥＧＲガスとの間の熱交換で加熱
された温度の高い冷媒がエバポレータ６の内管６ａの表
面において沸騰し、そのときの蒸発潜熱でＥＧＲガスを
冷却する。
【００１０】沸騰して蒸気となった冷媒の比重は、液体
状態の冷媒の比重に対比して著しく小さいために、比重
差によってエバポレータ６から押し出され、往路９を通
ってコンデンサ７に送り込まれる。そして、コンデンサ
７に送り込まれた冷媒の蒸気は、外気との間の熱交換で
冷却されて凝縮し、外気との熱交換で温度が低下すると
ともに比重が大きくなってコンデンサ７の底部に溜る。
【００１１】また、コンデンサ７内の冷媒はエバポレー
タ６内の冷媒より温度が低くて比重が大きいために、コ
ンデンサ７の底部に溜っている低温の冷媒が復路８から
エバポレータ６に自重で流入し、ＥＧＲガスとの熱交換
で再び蒸気となってコンデンサ７に送られて凝縮する。
【００１２】すなわち、コンデンサ７をエバポレータ６
より高所に配設してコンデンサ７の底部から延びる復路
８の先端をエバポレータ６の底部に接続する一方、エバ
ポレータ６の頂部から延びる往路９の先端を復路８との
接続位置より離れた位置でコンデンサ７に接続するとい
う簡潔構成であるにも拘らず、エバポレータ６での蒸発
によって発生した冷媒の蒸気をコンデンサ７で凝縮して
温度を低下させれば自重によってエバポレータ６に流入
するというように、冷媒の比重差を利用してエバポレー
タ６とコンデンサ７の間で冷媒を循環させることができ
る。
【００１３】このために、エネルギ消費をともなうポン
プなどの循環手段を設ける必要性がなく、しかも、冷媒
の蒸発潜熱を利用してＥＧＲガスを冷却することができ
るために、ＥＧＲクーラ５を安価に提供することができ
る。また、エンジン冷却系とは独立した冷却系を構成す
るために、多量のＥＧＲガスを還流させる場合において
もエンジン冷却系の熱負荷が増加することもない。
【００１４】なお、冷媒としてはエンジン冷却系などと
同様に水を用いることができるものであり、図示しない
逆止弁を復路８に設けることにより、冷媒の逆流をより
確実に防止することができる。
【００１５】図３は本発明に係るＥＧＲクーラの第２実
施形態を示す概略正面図、図４は図３のＡ−Ａ断面図で
ある。
【００１６】本実施形態においては、エバポレータ６を
二重管で構成し、内管６ａの内側でＥＧＲガスの流路を
構成するとともに、内管６ａと外管６ｂの間に形成され
た環状の通路６ｃで冷媒の流路を構成している。また、
本実施形態においては復路８の先端を前記環状通路６ｃ
の一端部に接続するとともに、往路９を環状通路６ｃの
他端から延設して両者の開口高さをほぼ同一としている
ために、冷媒の逆流を防止する逆止弁１１を復路８に設
けている。
【００１７】また、本実施形態においては、コンデンサ
７の底部に小室１２を形成する仕切り１３を設け、仕切
り１３の側壁下部に設けた小孔１４を介して小室１２の
内部をコンデンサ７内に連通保持させている。そして、
往路９をコンデンサ７の底壁から小室１２内に突入させ
てその先端を小室１２の頂部近傍に開口させることによ
り、往路９から送られた蒸気を小室１２内に放出すると
もに、この蒸気の熱で小室１２内の冷媒を温度上昇させ
て往路９の保温効果を維持させて不用意な凝縮を回避し
つつ、小室１２内の蒸気および冷媒を小孔１４からコン
デンサ７内に戻すようにしている。
【００１８】従って本実施形態によれば、前記第１実施
形態のように復路８の先端をエバポレータ６の底部に接
続する必要性がなく、あるいは、往路９をコンデンサ７
の頂部まで延設する必要性がないために、復路８および
往路９を短縮してＥＧＲクーラ５を軽量化することがで
きる利点がある。
【００１９】なお、上記実施形態においてはエバポレー
タ６を二重管で構成した場合について説明しているが、
エバポレータ６は必ずしも単純な二重管で構成する必要
性はなく、例えば図５に示したように軸線方向に沿う凹
凸条を壁面に形成した内管６ａを用いてＥＧＲガスと冷
媒の熱交換率を高くすることができ、あるいは、いわゆ
る多管式の熱交換器でエバポレータ６を構成することも
できる。
【００２０】
【発明の効果】以上の説明から明らかなように本発明
は、排気系から吸気系に還流されるＥＧＲガスと冷媒を
熱交換させる沸騰式のエバポレータより高所に、エンジ
ン冷却系から独立して設けられて前記エバポレータで発
生した蒸気を外気との熱交換で凝縮させるコンデンサを
配設し、コンデンサの底部から延びる復路の先端をエバ
ポレータに接続する一方、エバポレータの頂部から延び
る往路の先端を復路との接続位置より離れた位置におい
てコンデンサに接続したものであるから、冷媒の蒸発潜
熱を利用してＥＧＲガスを冷却することができる。ま
た、コンデンサをエバポレータより高所に配して冷媒を
自然循環させるようにしているために、ウォータポンプ
などの強制循環手段を用いる必要性がなく、エバポレー
タはエンジン冷却系から独立して設けたものであるか
ら、大量のＥＧＲガスを冷却するに際してもエンジン冷
却系の熱負荷が増加することがない。Description: BACKGROUND OF THE INVENTION [0001] 1. Field of the Invention [0002] The present invention relates to an EGR cooler for cooling EGR gas recirculated to an intake system, and more particularly to an EGR system capable of reducing the load on an engine cooling system. It is about cooler. 2. Description of the Related Art In recent years, an EGR cooler is often provided in order to cool EGR gas recirculated to an intake system and suppress an increase in combustion temperature. However, conventionally, a part of the engine cooling water is used to cool the EGR gas. Therefore, when the flow rate of the EGR gas increases, the heat load of the engine cooling system increases. There was a need to increase the capacity.
Even in the case where the engine cooling system and the cooling system of the EGR cooler are made independent, it is necessary to provide a forced circulation means such as a water pump.
There was a problem that the cost of the R system would increase. SUMMARY OF THE INVENTION The present invention has been made in view of the above circumstances, and does not require the use of forced circulation means such as a water pump. It is an object to provide an EGR cooler that does not cause an increase. [0004] In order to solve the above-mentioned problems, the present invention relates to a boiling evaporator for exchanging heat between a refrigerant and EGR gas which is recirculated from an exhaust system to an intake system, and an engine cooling system. A condenser is provided independently and condenses the steam generated by the evaporator by heat exchange with the outside air. Further, the condenser is disposed at a higher position than the evaporator. The forward end extending from the bottom of the condenser is connected to the evaporator, while the forward end extending from the top of the evaporator is connected to the condenser at a position farther from the connection with the return path. An embodiment of the present invention will be described below in detail with reference to the drawings. FIG. 1 is a schematic plan view of a supercharged diesel engine provided with an EGR cooler according to the present invention, and FIG. 2 is a schematic front view showing a first embodiment of the EGR cooler. In these figures, an EGR cooler 5 is interposed in an EGR passage 4 which branches off from an exhaust manifold 2 of a diesel engine 1 and reaches an intake manifold 3. The EGR cooler 5 includes a boiling evaporator 6 for exchanging heat between the EGR gas flowing through the EGR passage 4 and the refrigerant, and a condenser 7 provided independently of the engine cooling system.
The main part is composed of. Further, after arranging the condenser 7 at a position higher than the evaporator 5, the tip of the return path 8 extending from the bottom of the condenser 7 is connected to the bottom of the evaporator 6, and the outward path 9 extending from the top of the evaporator 6.
Is connected to the capacitor 7 in a top space higher than the connection position with the return path 8. By providing fins or the like on the outside or inside of the condenser 7 for increasing the heat exchange capacity with the outside air, the steam generated by the evaporator 5 and sent to the condenser 7 from the outward path 9 is provided. Is condensed by exchanging heat with, for example, a running wind of an automobile or a wind induced by a cooling fan of an engine. In FIG. 1, reference numeral 10 denotes an exhaust turbocharger. The air discharged from the exhaust turbocharger 10 is cooled by an intercooler (not shown), and then guided to the intake manifold 3 and together with the EGR gas and the combustion chamber of the engine 1. Supplied to In the EGR cooler having such a configuration,
The refrigerant that has exchanged heat with the EGR gas in the evaporator 6 increases in temperature over time and the specific gravity gradually decreases. The high-temperature refrigerant heated by the heat exchange with the EGR gas boils on the surface of the inner tube 6a of the evaporator 6, and cools the EGR gas by the latent heat of evaporation at that time. Since the specific gravity of the refrigerant that has been vaporized by boiling is significantly smaller than the specific gravity of the refrigerant in the liquid state, the refrigerant is pushed out of the evaporator 6 by the difference in specific gravity and is sent to the condenser 7 through the outward path 9. The vapor of the refrigerant sent to the condenser 7 is cooled and condensed by heat exchange with the outside air, and the temperature is lowered by heat exchange with the outside air and the specific gravity is increased, so that the vapor is accumulated at the bottom of the condenser 7. Since the refrigerant in the condenser 7 has a lower temperature and a higher specific gravity than the refrigerant in the evaporator 6, the low-temperature refrigerant accumulated at the bottom of the condenser 7 flows into the evaporator 6 from the return path 8 by its own weight. The heat is exchanged with the EGR gas to become a vapor again to be sent to the condenser 7 and condensed. That is, the condenser 7 is connected to the evaporator 6
The distal end of the return path 8 extending from the bottom of the condenser 7 is connected to the bottom of the evaporator 6 at a higher position, and the distal end of the outward path 9 extending from the top of the evaporator 6 is located at a position farther from the connection position with the return path 8. Despite the simple configuration of connecting to the condenser 7, if the refrigerant vapor generated by evaporation in the evaporator 6 is condensed in the condenser 7 to lower the temperature, the refrigerant flows into the evaporator 6 by its own weight. The refrigerant can be circulated between the evaporator 6 and the condenser 7 using the specific gravity difference of the refrigerant. Therefore, there is no need to provide a circulating means such as a pump which consumes energy, and the EGR gas can be cooled by utilizing the latent heat of evaporation of the refrigerant. Can be provided. Further, since a cooling system independent of the engine cooling system is formed, the heat load of the engine cooling system does not increase even when a large amount of EGR gas is recirculated. As the refrigerant, water can be used as in the case of the engine cooling system and the like. By providing a check valve (not shown) in the return path 8, it is possible to more reliably prevent the refrigerant from flowing backward. . FIG. 3 is a schematic front view showing a second embodiment of the EGR cooler according to the present invention, and FIG. 4 is a sectional view taken along line AA of FIG. In the present embodiment, the evaporator 6 is constituted by a double pipe, an EGR gas flow path is formed inside the inner pipe 6a, and an annular ring formed between the inner pipe 6a and the outer pipe 6b. The passage 6c forms a flow path for the refrigerant. Also,
In the present embodiment, the tip of the return path 8 is connected to the annular passage 6c.
In addition, since the forward path 9 is extended from the other end of the annular path 6c and the opening heights thereof are substantially the same, a check valve 11 for preventing the backflow of the refrigerant is provided in the return path 8. ing. Further, in the present embodiment, a partition 13 forming a small chamber 12 is provided at the bottom of the capacitor 7, and the inside of the small chamber 12 communicates with the inside of the capacitor 7 via a small hole 14 provided at a lower portion of the side wall of the partition 13. I keep it. And
By making the outward path 9 protrude into the small chamber 12 from the bottom wall of the condenser 7 and opening its tip near the top of the small chamber 12, the steam sent from the outward path 9 is discharged into the small chamber 12, and the heat of the vapor is released. The vapor in the small chamber 12 and the refrigerant are returned from the small holes 14 into the condenser 7 while raising the temperature of the refrigerant in the small chamber 12 to maintain the heat retaining effect of the outward path 9 and avoid inadvertent condensation. . Therefore, according to the present embodiment, there is no need to connect the tip of the return path 8 to the bottom of the evaporator 6 as in the first embodiment, or the forward path 9 is connected to the condenser 7.
Since there is no need to extend to the top of the EGR cooler 5, there is an advantage that the return path 8 and the outward path 9 can be shortened and the EGR cooler 5 can be reduced in weight. In the above embodiment, the case where the evaporator 6 is constituted by a double pipe has been described.
The evaporator 6 does not necessarily need to be composed of a simple double pipe, and for example, as shown in FIG. 5, the heat exchange rate between the EGR gas and the refrigerant is determined by using an inner pipe 6a having a wall with irregularities extending along the axial direction. Can be increased, or the evaporator 6 can be constituted by a so-called multi-tube heat exchanger. As is apparent from the above description, the present invention is higher than the boiling type evaporator for exchanging heat between EGR gas and refrigerant flowing from the exhaust system to the intake system. An independent condenser is provided for condensing the steam generated by the evaporator by heat exchange with the outside air, and the leading end of the return path extending from the bottom of the condenser is connected to the evaporator, while the leading end of the outward path extending from the top of the evaporator. Is connected to the condenser at a position farther from the connection position with the return path, so that the EGR gas can be cooled using the latent heat of evaporation of the refrigerant. In addition, since the condenser is arranged at a higher position than the evaporator to allow the refrigerant to circulate naturally, there is no need to use forced circulation means such as a water pump, and the evaporator is provided independently of the engine cooling system. Therefore, even when cooling a large amount of EGR gas, the heat load of the engine cooling system does not increase.
【図面の簡単な説明】
【図１】ＥＧＲクーラを備えた過給式ディーゼルエンジ
ンの概略平面図である。
【図２】本発明に係るＥＧＲクーラの第１実施形態を示
す概略正面図である。
【図３】本発明に係るＥＧＲクーラの第２実施形態を示
す概略正面図である。
【図４】図３のＡ−Ａ断面図である。
【図５】エバポレータの変形例を示す断面図である。
【符号の説明】
１ ディーゼルエンジン
２ 排気マニホールド
３ 吸気マニホールド
４ ＥＧＲ通路
５ ＥＧＲクーラ
６ エバポレータ
６ａ 内管
６ｂ 外管
６ｃ 環状通路
７ コンデンサ
８ 復路
９ 往路
１０ 排気ターボチャージャ
１１ 逆止弁
１２ 小室
１３ 仕切り
１４ 小孔BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a schematic plan view of a supercharged diesel engine provided with an EGR cooler. FIG. 2 is a schematic front view showing a first embodiment of the EGR cooler according to the present invention. FIG. 3 is a schematic front view showing a second embodiment of the EGR cooler according to the present invention. FIG. 4 is a sectional view taken along line AA of FIG. 3; FIG. 5 is a sectional view showing a modified example of the evaporator. [Description of Signs] 1 Diesel engine 2 Exhaust manifold 3 Intake manifold 4 EGR passage 5 EGR cooler 6 Evaporator 6a Inner tube 6b Outer tube 6c Annular passage 7 Capacitor 8 Return path 9 Outbound path 10 Exhaust turbocharger 11 Check valve 12 Small chamber 13 Partition 14 Small hole
Claims (1)
スと冷媒を熱交換させる沸騰式のエバポレータと、エン
ジン冷却系から独立して設けられて前記エバポレータで
発生した蒸気を外気との熱交換で凝縮させるコンデンサ
を備え、前記コンデンサをエバポレータより高所に配設
し、コンデンサの底部から延びる復路の先端をエバポレ
ータに接続する一方、エバポレータの頂部から延びる往
路の先端を復路との接続位置から離れた位置においてコ
ンデンサに接続したことを特徴とするＥＧＲクーラ。Claims: 1. A boiling evaporator for exchanging heat between a refrigerant and EGR gas recirculated from an exhaust system to an intake system, and steam generated by the evaporator provided independently of an engine cooling system. The condenser is disposed at a higher position than the evaporator, and the tip of the return path extending from the bottom of the condenser is connected to the evaporator, while the tip of the outward path extending from the top of the evaporator is connected to the return path. An EGR cooler characterized in that the EGR cooler is connected to a capacitor at a position distant from the connection position with the capacitor.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2002076275A JP2003278607A (en) | 2002-03-19 | 2002-03-19 | Egr cooler |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2002076275A JP2003278607A (en) | 2002-03-19 | 2002-03-19 | Egr cooler |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JP2003278607A true JP2003278607A (en) | 2003-10-02 |
Family
ID=29227769
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2002076275A Pending JP2003278607A (en) | 2002-03-19 | 2002-03-19 | Egr cooler |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2003278607A (en) |
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2875856A1 (en) * | 2004-09-27 | 2006-03-31 | Renault Sas | Tubular heat exchanger for e.g. heat engine, has calandria with twisted tubes inside which recycled exhaust gas circulates such that gas releases its heat to heat transfer fluid, where fluid is in heat exchange contact with coolant |
| FR2875857A1 (en) * | 2004-09-27 | 2006-03-31 | Renault Sas | Heat exchanger for internal combustion engine, has tubes through which recycled exhaust gas passes, where tubes are disposed axially and horizontally in grille between tubular input plate and tubular output plate |
| WO2007086418A1 (en) * | 2006-01-26 | 2007-08-02 | Komatsu Ltd. | Cooling apparatus of liquid |
| JP2008088810A (en) * | 2006-09-29 | 2008-04-17 | Nissan Diesel Motor Co Ltd | Egr device |
| JP2009192177A (en) * | 2008-02-15 | 2009-08-27 | Toyota Industries Corp | Ebullient cooling device |
| JP2009250107A (en) * | 2008-04-04 | 2009-10-29 | Denso Corp | Exhaust heat recovery system |
| US7721543B2 (en) * | 2006-10-23 | 2010-05-25 | Southwest Research Institute | System and method for cooling a combustion gas charge |
-
2002
- 2002-03-19 JP JP2002076275A patent/JP2003278607A/en active Pending
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2875856A1 (en) * | 2004-09-27 | 2006-03-31 | Renault Sas | Tubular heat exchanger for e.g. heat engine, has calandria with twisted tubes inside which recycled exhaust gas circulates such that gas releases its heat to heat transfer fluid, where fluid is in heat exchange contact with coolant |
| FR2875857A1 (en) * | 2004-09-27 | 2006-03-31 | Renault Sas | Heat exchanger for internal combustion engine, has tubes through which recycled exhaust gas passes, where tubes are disposed axially and horizontally in grille between tubular input plate and tubular output plate |
| WO2007086418A1 (en) * | 2006-01-26 | 2007-08-02 | Komatsu Ltd. | Cooling apparatus of liquid |
| DE112007000222T5 (en) | 2006-01-26 | 2008-11-06 | Komatsu Ltd. | Cooling device for a fluid |
| JPWO2007086418A1 (en) * | 2006-01-26 | 2009-06-18 | 株式会社小松製作所 | Fluid cooling device |
| JP2008088810A (en) * | 2006-09-29 | 2008-04-17 | Nissan Diesel Motor Co Ltd | Egr device |
| US7721543B2 (en) * | 2006-10-23 | 2010-05-25 | Southwest Research Institute | System and method for cooling a combustion gas charge |
| JP2009192177A (en) * | 2008-02-15 | 2009-08-27 | Toyota Industries Corp | Ebullient cooling device |
| JP2009250107A (en) * | 2008-04-04 | 2009-10-29 | Denso Corp | Exhaust heat recovery system |
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