JP2000180085A - Tube for heat exchanger - Google Patents
Tube for heat exchangerInfo
- Publication number
- JP2000180085A JP2000180085A JP10355702A JP35570298A JP2000180085A JP 2000180085 A JP2000180085 A JP 2000180085A JP 10355702 A JP10355702 A JP 10355702A JP 35570298 A JP35570298 A JP 35570298A JP 2000180085 A JP2000180085 A JP 2000180085A
- Authority
- JP
- Japan
- Prior art keywords
- spiral member
- spiral
- fluid
- grooves
- notch groove
- 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
- F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
- F28F13/12—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media by creating turbulence, e.g. by stirring, by increasing the force of circulation
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
- F28D21/0001—Recuperative heat exchangers
- F28D21/0003—Recuperative heat exchangers the heat being recuperated from exhaust gases
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】本発明は、排気系からＥＧＲ
管路を介して吸気マニホールドに再循環されるＥＧＲガ
スを冷却するためのＥＧＲガス冷却装置等に使用される
熱交換器用チューブに関する。[0001] The present invention relates to an EGR system for an exhaust system.
The present invention relates to a heat exchanger tube used for an EGR gas cooling device for cooling EGR gas recirculated to an intake manifold via a pipeline.
【０００２】[0002]
【従来の技術】従来、エンジンでは、排気ガス中におけ
る窒素酸化物（ＮＯｘ）を低減させるために、排気ガス
の一部を排気系から取り出し、混合気に加えるＥＧＲ
（Exhaust Gas Recirculation：排気再循環）が行われ
ている。このようなＥＧＲを行うためのＥＧＲ装置は、
排気系からの排気ガスの一部をＥＧＲガスとして燃焼室
に吸入される混合気に再循環させるように構成されてお
り、例えば、図４に示すように、排気マニホールド（ま
たは排気管）１と吸気マニホールド２との間を接続する
ＥＧＲ通路３と、このＥＧＲ通路３に設けられたＥＧＲ
弁４とを備えている。2. Description of the Related Art Conventionally, in an engine, in order to reduce nitrogen oxides (NOx) in the exhaust gas, a part of the exhaust gas is taken out of an exhaust system and added to an air-fuel mixture.
(Exhaust Gas Recirculation). An EGR device for performing such EGR includes:
A part of the exhaust gas from the exhaust system is recirculated as an EGR gas to the air-fuel mixture sucked into the combustion chamber. For example, as shown in FIG. 4, an exhaust manifold (or exhaust pipe) 1 An EGR passage 3 connecting the intake manifold 2 and an EGR passage provided in the EGR passage 3
And a valve 4.
【０００３】そして、ＥＧＲ弁４の開度をエンジンの運
転状態に応じて適宜に制御することにより、吸入混合気
に対するＥＧＲガスの割合が調整される。このようなＥ
ＧＲ装置では、ＥＧＲガスが混合気と共に燃焼室に取り
込まれるため、ＥＧＲガスの温度を適度な温度に維持す
る必要がある。[0003] The ratio of the EGR gas to the intake air-fuel mixture is adjusted by appropriately controlling the opening of the EGR valve 4 according to the operating state of the engine. Such an E
In the GR device, since the EGR gas is taken into the combustion chamber together with the air-fuel mixture, it is necessary to maintain the temperature of the EGR gas at an appropriate temperature.
【０００４】すなわち、ＥＧＲガスは、本来高温である
が、このＥＧＲガスの温度が高すぎると、混合気が加熱
されて熱膨張することにより空気の充填効率が悪くな
り、混合気の燃焼率が悪化してエンジンの出力低下を招
く虞がある。一方、ＥＧＲガスの温度が低すぎると、Ｅ
ＧＲガス中のタール等の付着物質の粘度が増加して、付
着物質がＥＧＲ通路，ＥＧＲ弁等に付着し易くなり、装
置の信頼性を低下させる虞がある。[0004] That is, EGR gas is inherently high in temperature. If the temperature of this EGR gas is too high, the air-fuel mixture is heated and thermally expanded, thereby lowering the air filling efficiency and reducing the combustion rate of the air-fuel mixture. There is a possibility that the output will deteriorate and the output of the engine will decrease. On the other hand, if the temperature of the EGR gas is too low, E
The viscosity of the adhering substance such as tar in the GR gas increases, so that the adhering substance easily adheres to the EGR passage, the EGR valve, and the like, which may reduce the reliability of the apparatus.
【０００５】従来、ＥＧＲガスを冷却するＥＧＲガス冷
却装置として、例えば、特開平９−８９４９１号公報等
に開示されるものが知られている。図５は、この種のＥ
ＧＲガス冷却装置を示すもので、この冷却装置は、排気
マニホールドとＥＧＲ弁とを接続する管路に配置されて
いる。この冷却装置は、外筒５の軸長方向に、多数のチ
ューブ６を配置して構成されており、図６に示すよう
に、チューブ６の両端が端板７に支持されている。Conventionally, as an EGR gas cooling device for cooling EGR gas, for example, a device disclosed in Japanese Patent Application Laid-Open No. 9-89491 is known. FIG. 5 shows this type of E
1 shows a GR gas cooling device, which is disposed in a pipeline connecting an exhaust manifold and an EGR valve. This cooling device is configured by arranging a number of tubes 6 in the axial direction of the outer cylinder 5, and both ends of the tubes 6 are supported by end plates 7 as shown in FIG. 6.
【０００６】外筒５の外周には、冷却水の入口パイプ８
および出口パイプ９が開口されている。また、外筒５の
上端および下端には、フランジ部１０，１１が形成され
ている。上端のフランジ部１０には、排気マニホールド
からの配管１２が取付フランジ１３を介して連結され、
下端のフランジ部１１には、ＥＧＲ弁への配管１４が取
付フランジ１５を介して連結されている。At the outer periphery of the outer cylinder 5, an inlet pipe 8 for cooling water is provided.
And an outlet pipe 9 is opened. Further, flange portions 10 and 11 are formed at the upper end and the lower end of the outer cylinder 5. A pipe 12 from an exhaust manifold is connected to the upper flange 10 via a mounting flange 13.
A pipe 14 to the EGR valve is connected to the lower flange portion 11 via a mounting flange 15.
【０００７】この冷却装置では、排気マニホールド側の
配管１２からＥＧＲガスが外筒５内に導入され、外筒５
内のチューブ６の間を流れる冷却水により冷却された
後、ＥＧＲ弁側の配管１４に導出される。[0007] In this cooling device, EGR gas is introduced into the outer cylinder 5 from the pipe 12 on the exhaust manifold side.
After being cooled by the cooling water flowing between the tubes 6 inside, it is led out to the pipe 14 on the EGR valve side.
【０００８】[0008]
【発明が解決しようとする課題】しかしながら、このよ
うな従来のＥＧＲガス冷却装置では、チューブ６に単な
る円筒状の部材を使用しているため、チューブ６内を流
れるＥＧＲガスと、このチューブ６の外側を流れる冷却
水との熱交換効率が比較的低く、従って、ＥＧＲガスを
所定の温度に冷却するためには、チューブ６の長さを長
く、あるいは、チューブ６の本数を増大する必要があ
り、装置が大きくなるという問題があった。However, in such a conventional EGR gas cooling apparatus, since a simple cylindrical member is used for the tube 6, the EGR gas flowing through the tube 6 and the EGR gas flowing through the tube 6 are hardened. The heat exchange efficiency with the cooling water flowing outside is relatively low. Therefore, in order to cool the EGR gas to a predetermined temperature, it is necessary to lengthen the tube 6 or increase the number of tubes 6. However, there is a problem that the device becomes large.
【０００９】本発明は、かかる従来の問題を解決するた
めになされたもので、従来より大幅に熱交換効率を向上
することができる熱交換器用チューブを提供することを
目的とする。[0009] The present invention has been made to solve such a conventional problem, and an object of the present invention is to provide a tube for a heat exchanger capable of greatly improving heat exchange efficiency as compared with the conventional one.
【００１０】[0010]
【課題を解決するための手段】請求項１の熱交換器用チ
ューブは、円筒状の管部材の内周に、螺旋部材を嵌挿
し、この螺旋部材の外周に間隔を置いて複数の切欠溝を
形成するとともに、前記切欠溝の深さを、前記螺旋部材
の直径の０．１倍以下の値にしてなることを特徴とす
る。According to a first aspect of the present invention, there is provided a heat exchanger tube in which a spiral member is inserted into an inner periphery of a cylindrical tube member, and a plurality of cutout grooves are formed on the outer periphery of the spiral member at intervals. The depth of the notch groove is set to a value of 0.1 times or less of the diameter of the spiral member.
【００１１】請求項２の熱交換器用チューブは、請求項
１記載の熱交換器用チューブにおいて、前記複数の切欠
溝の面積を合計した総切欠溝面積の値を、前記螺旋部材
の面積の０．５％以上で４％以下の値にしてなることを
特徴とする。According to a second aspect of the present invention, in the heat exchanger tube according to the first aspect, a value of a total notch groove area obtained by summing up the areas of the plurality of notch grooves is set to 0.1% of an area of the spiral member. It is characterized in that it is set to a value of 5% or more and 4% or less.
【００１２】（作用）請求項１の熱交換器用チューブで
は、円筒状の管部材の内周に、螺旋部材を嵌挿したの
で、ＥＧＲガス等の流体の流れが加速され、かつ、流体
直径が減少し、管部材への熱伝達率が向上される。(Function) In the heat exchanger tube of the first aspect, since the spiral member is inserted into the inner periphery of the cylindrical tube member, the flow of the fluid such as EGR gas is accelerated, and the diameter of the fluid is reduced. The heat transfer coefficient to the pipe member is improved.
【００１３】また、螺旋部材の外周に間隔を置いて複数
の切欠溝を形成したので、切欠溝により管部材の内面近
傍の流体の流れが乱され、管部材への熱伝達率が向上さ
れる。そして、切欠溝の深さを、螺旋部材の直径の０．
１倍以下の値にしたので、切欠溝を流れる流体の主流へ
の影響は殆どなく、流体の圧力損失は僅かしか生じな
い。Further, since a plurality of notches are formed at intervals on the outer periphery of the spiral member, the flow of the fluid near the inner surface of the tube member is disturbed by the notches, and the heat transfer coefficient to the tube member is improved. . Then, the depth of the notch groove is set to 0.
Since the value is not more than one time, there is almost no influence on the main flow of the fluid flowing through the notch groove, and only a small pressure loss of the fluid occurs.
【００１４】すなわち、切欠溝の深さが、螺旋部材の直
径の０．１倍を越えると、切欠溝を通過して比較的多量
の流体が流れるようになるため、螺旋部材に沿う流体の
旋回方向速度が低下し、管部材への熱伝達率が低下す
る。請求項２の熱交換器用チューブでは、複数の切欠溝
の面積を合計した総切欠溝面積の値が、螺旋部材の面積
の０．５％以上で４％以下の値にされる。That is, when the depth of the notch groove exceeds 0.1 times the diameter of the spiral member, a relatively large amount of fluid flows through the notch groove, so that the fluid swirls along the spiral member. The directional speed decreases, and the heat transfer coefficient to the pipe member decreases. In the heat exchanger tube according to the second aspect, the value of the total notch groove area obtained by adding the areas of the plurality of notch grooves is set to a value of 0.5% or more and 4% or less of the area of the spiral member.
【００１５】すなわち、総切欠溝面積の値が、螺旋部材
の面積の４％を越えると、切欠溝を流れる流体の主流へ
の影響が顕著になり、螺旋部材に沿う流体の旋回方向速
度が低下し、管部材への熱伝達率が低下する。一方、総
切欠溝面積の値が、螺旋部材の面積の０．５％未満の場
合には、切欠溝により管部材の内面近傍の流体の流れを
充分に乱すことが困難になり、管部材への熱伝達率が低
下する。That is, when the value of the total notch groove area exceeds 4% of the area of the spiral member, the influence of the fluid flowing through the notch groove on the main flow becomes remarkable, and the rotational speed of the fluid along the spiral member decreases. As a result, the heat transfer coefficient to the pipe member decreases. On the other hand, when the value of the total notch groove area is less than 0.5% of the area of the spiral member, it becomes difficult to sufficiently disturb the flow of the fluid near the inner surface of the pipe member due to the notch groove, and The heat transfer coefficient is reduced.
【００１６】[0016]
【発明の実施の形態】以下、本発明の詳細を図面に示す
実施形態について説明する。図１は、図２の螺旋部材を
展開した状態を示しており、図２は、本発明の熱交換器
用チューブの一実施形態を示している。図２において符
号２１は、ＥＧＲガスからなる流体が流通される管部材
を示している。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, embodiments of the present invention will be described with reference to the drawings. FIG. 1 shows a state in which the spiral member of FIG. 2 is expanded, and FIG. 2 shows an embodiment of a heat exchanger tube of the present invention. In FIG. 2, reference numeral 21 denotes a pipe member through which a fluid composed of EGR gas flows.
【００１７】この管部材２１は、円筒状をしておりステ
ンレス鋼により形成されている。この管部材２１の内面
には、螺旋部材２３が嵌挿されている。螺旋部材２３
は、ステンレス鋼からなり、管部材２１の内面にニッケ
ルろう付けされている。この実施形態では、螺旋部材２
３は、図１に示すような長尺状の板材２５を捻り加工す
ることにより形成されている。The tube member 21 has a cylindrical shape and is made of stainless steel. A spiral member 23 is fitted on the inner surface of the tube member 21. Spiral member 23
Is made of stainless steel and is nickel brazed to the inner surface of the pipe member 21. In this embodiment, the spiral member 2
3 is formed by twisting a long plate material 25 as shown in FIG.
【００１８】捻り加工は、例えば、板材２５の両端を一
対の治具により把持し、一方の治具を回転することによ
り行われる。そして、この実施形態では、螺旋部材２３
を形成するための板材２５の外周には、間隔Ｌを置いて
複数の切欠溝２７が形成されている。この実施形態で
は、切欠溝２７の間隔Ｌは、螺旋部材２３の１ピッチＰ
内に３個の切欠溝２７が位置するような寸法に形成され
ている。The twisting is performed, for example, by holding both ends of the plate member 25 with a pair of jigs and rotating one of the jigs. And in this embodiment, the spiral member 23
A plurality of cutout grooves 27 are formed at intervals L on the outer periphery of the plate member 25 for forming the notch. In this embodiment, the interval L between the notch grooves 27 is one pitch P of the spiral member 23.
It is formed in such a size that three notch grooves 27 are located therein.
【００１９】この切欠溝２７は、四角形状をしており、
各切欠溝２７の深さＸが、螺旋部材２３の直径Ｄの０．
１倍以下の値、例えば、０．０７５倍にされている。そ
して、板材２５に形成される全ての切欠溝２７の面積を
合計した総切欠溝面積の値が、板材２５、すなわち螺旋
部材２３の面積Ｓの０．５％以上で４％以下の値（以下
この値を総切欠開口率という）にされている。The notch 27 has a square shape.
The depth X of each notch 27 is equal to 0.
The value is set to a value of 1 or less, for example, 0.075 times. Then, the value of the total notch groove area obtained by summing the areas of all the notch grooves 27 formed in the plate member 25 is 0.5% or more and 4% or less of the area S of the plate member 25, that is, the spiral member 23 (hereinafter, not more than 4%). This value is referred to as a total notch opening ratio).
【００２０】なお、この総切欠開口率は、後述する実験
結果から明らかなように、例えば、１．５％から２．０
％の範囲の値にするのが最も望ましい。上述した熱交換
器用チューブは、図１に示した板材２５を捻り加工する
ことにより螺旋部材２３を形成し、この螺旋部材２３を
管部材２１内に嵌挿し、熱処理を行い螺旋部材２３の外
周を管部材２１の内面にニッケルろう付けして形成され
る。The total notch opening ratio is, for example, from 1.5% to 2.0%, as apparent from the experimental results described later.
Most preferably, it is in the range of%. The above-mentioned heat exchanger tube forms the spiral member 23 by twisting the plate member 25 shown in FIG. 1, inserts the spiral member 23 into the tube member 21, heat-treats the outer periphery of the spiral member 23. The inner surface of the tube member 21 is formed by nickel brazing.
【００２１】以上のように構成された熱交換器用チュー
ブでは、円筒状の管部材２１の内周に、螺旋部材２３を
嵌挿し、この螺旋部材２３の外周に間隔Ｌを置いて複数
の切欠溝２７を形成し、切欠溝２７の深さＸを、螺旋部
材２３の直径Ｄの０．１倍以下の値にしたので、従来よ
り大幅に熱交換効率を向上することができる。すなわ
ち、上述した熱交換器用チューブでは、円筒状の管部材
２１の内周に、螺旋部材２３を嵌挿したので、ＥＧＲガ
ス等の流体の流れが加速され、かつ、流体直径が減少
し、管部材２１への熱伝達率が向上する。In the heat exchanger tube constructed as described above, a spiral member 23 is inserted into the inner periphery of a cylindrical tube member 21 and a plurality of notched grooves are provided on the outer periphery of the spiral member 23 at intervals L. 27, and the depth X of the cutout groove 27 is set to a value not more than 0.1 times the diameter D of the spiral member 23, so that the heat exchange efficiency can be greatly improved as compared with the conventional case. That is, in the above-described heat exchanger tube, since the spiral member 23 is inserted into the inner periphery of the cylindrical tube member 21, the flow of the fluid such as EGR gas is accelerated, and the fluid diameter is reduced. The heat transfer coefficient to the member 21 is improved.
【００２２】また、螺旋部材２３の外周に間隔Ｌを置い
て複数の切欠溝２７を形成したので、切欠溝２７により
管部材２１の内面近傍の流体の流れが乱され、管部材２
１への熱伝達率が向上する。そして、切欠溝２７の深さ
Ｘを、螺旋部材２３の直径Ｄの０．１倍以下の値にした
ので、切欠溝２７を流れる流体の主流への影響は殆どな
く、流体の圧力損失は僅かしか生じない。Further, since a plurality of notches 27 are formed on the outer periphery of the spiral member 23 at intervals L, the flow of fluid near the inner surface of the pipe member 21 is disturbed by the notches 27, and
1 is improved. Since the depth X of the notch groove 27 is set to a value not more than 0.1 times the diameter D of the spiral member 23, there is almost no effect on the main flow of the fluid flowing through the notch groove 27, and the pressure loss of the fluid is slight. Only occurs.
【００２３】すなわち、切欠溝２７の深さＸが、螺旋部
材２３の直径Ｄの０．１倍を越えると、切欠溝２７を通
過して比較的多量の流体が流れるようになるため、螺旋
部材２３に沿う流体の旋回方向速度が低下し、管部材２
１への熱伝達率が低下するが、本発明では、切欠溝２７
の深さＸを、螺旋部材２３の直径Ｄの０．１倍以下の値
にしたので、切欠溝２７を流れる流体の主流への影響は
殆どなく、流体の圧力損失、および、この圧力損失によ
る旋回方向速度の低下を僅かなものにすることができ
る。That is, when the depth X of the notch groove 27 exceeds 0.1 times the diameter D of the spiral member 23, a relatively large amount of fluid flows through the notch groove 27, so that the spiral member 23, the swirling speed of the fluid along the pipe member 23 is reduced.
1, the heat transfer coefficient to the notch groove 27 is reduced in the present invention.
Is set to a value not more than 0.1 times the diameter D of the spiral member 23, so that there is almost no influence on the main flow of the fluid flowing through the cutout groove 27, and the pressure loss of the fluid and the pressure loss The decrease in the turning speed can be made small.
【００２４】そして、上述した熱交換器用チューブで
は、複数の切欠溝２７の面積を合計した総切欠溝面積の
値を、螺旋部材２３の面積Ｓの０．５％以上で４％以下
の値にしたので、切欠溝２７を流れる流体の主流への影
響を殆どなくした状態で、切欠溝２７により管部材２１
の内面近傍の流体の流れを充分に乱すことができる。す
なわち、総切欠溝面積の値が、螺旋部材２３の面積Ｓの
４％を越えると、切欠溝２７を流れる流体の主流への影
響が顕著になり、螺旋部材２３に沿う流体の旋回方向速
度が低下し、管部材２１への熱伝達率が低下し、一方、
総切欠溝面積の値が、螺旋部材２３の面積Ｓの０．５％
未満の場合には、切欠溝２７により管部材２１の内面近
傍の流体の流れを充分に乱すことが困難になり、管部材
２１への熱伝達率が低下するが、この実施形態では、総
切欠溝面積の値を、螺旋部材２３の面積Ｓの０．５％以
上で４％以下の値にしたので、切欠溝２７を流れる流体
の主流への影響を殆どなくした状態で、切欠溝２７によ
り管部材２１の内面近傍の流体の流れを充分に乱すこと
ができる。In the above-described heat exchanger tube, the total notch groove area value obtained by summing the areas of the plurality of notch grooves 27 is set to a value of 0.5% or more and 4% or less of the area S of the spiral member 23. Therefore, the pipe member 21 can be removed by the notch groove 27 while the influence of the fluid flowing through the notch groove 27 on the main flow is almost eliminated.
Can sufficiently disturb the flow of fluid near the inner surface. That is, when the value of the total notch groove area exceeds 4% of the area S of the spiral member 23, the influence of the fluid flowing through the notch groove 27 on the main flow becomes remarkable, and the rotational speed of the fluid along the spiral member 23 decreases. And the heat transfer coefficient to the pipe member 21 decreases.
The value of the total notch groove area is 0.5% of the area S of the spiral member 23.
If it is less than 0.0, it is difficult for the notch groove 27 to sufficiently disturb the flow of the fluid near the inner surface of the pipe member 21 and the heat transfer coefficient to the pipe member 21 is reduced. Since the value of the groove area is set to a value of 0.5% or more and 4% or less of the area S of the spiral member 23, the effect of the notch groove 27 with the influence of the fluid flowing through the notch groove 27 on the main flow is almost eliminated. The flow of the fluid near the inner surface of the pipe member 21 can be sufficiently disturbed.
【００２５】図３は、実験により得られた上述した熱交
換器用チューブの総切欠開口率と熱伝達向上率との関係
を示している。なお、この図では、上述した螺旋部材２
３に切欠溝２７を形成していない熱交換器用チューブの
熱伝達率が１とされ、この熱交換器用チューブを基準と
して、例えば、熱伝達率が２割向上した場合には、熱伝
達向上率が１．２とされ、熱伝達率が２割低減した場合
には、熱伝達向上率が０．８とされている。FIG. 3 shows the relationship between the total notch opening ratio and the heat transfer improvement ratio of the above-described heat exchanger tubes obtained by experiments. In this figure, the above-mentioned spiral member 2
The heat transfer coefficient of the heat exchanger tube in which the notch groove 27 is not formed in the heat exchanger tube 3 is set to 1, for example, when the heat transfer coefficient is improved by 20% with respect to the heat exchanger tube, Is set to 1.2, and when the heat transfer coefficient is reduced by 20%, the heat transfer improvement rate is set to 0.8.
【００２６】この図において、曲線Ａは、切欠溝２７の
深さＸを螺旋部材２３の直径Ｄの０．０７５倍にし、切
欠溝２７の幅Ｗを変更することにより総切欠開口率を変
更した場合を、曲線Ｂは、切欠溝２７の深さＸを螺旋部
材２３の直径Ｄの０．１倍にし、切欠溝２７の幅Ｗを変
更することにより総切欠開口率を変更した場合を示して
いる。In this figure, the curve A is obtained by changing the depth X of the notch groove 27 to 0.075 times the diameter D of the spiral member 23 and changing the width W of the notch groove 27 to change the total notch opening ratio. The curve B shows the case where the depth X of the notch groove 27 is set to 0.1 times the diameter D of the spiral member 23 and the width W of the notch groove 27 is changed to change the total notch opening ratio. I have.
【００２７】そして、曲線Ｃは、切欠溝２７の深さＸを
螺旋部材２３の直径Ｄの０．１５倍にし、切欠溝２７の
幅Ｗを変更することにより総切欠開口率を変更した場合
を示している。この図から、曲線ＡおよびＢでは、特
に、総切欠開口率が１．５％から２．０％の範囲におい
て良好になっていることが分かる。The curve C shows the case where the depth X of the notch groove 27 is 0.15 times the diameter D of the spiral member 23 and the width W of the notch groove 27 is changed to change the total notch opening ratio. Is shown. From this figure, it can be seen that curves A and B are particularly good when the total notch opening ratio is in the range of 1.5% to 2.0%.
【００２８】また、曲線Ｃでは、熱伝達向上率が切欠溝
を形成しない場合より劣っているのが分かる。なお、上
述した実施形態では、ＥＧＲガス冷却装置に使用される
熱交換器用チューブに本発明を適用した例について説明
したが、本発明はかかる実施形態に限定されるものでは
なく、空気，ガス等の流体が流通される熱交換器用チュ
ーブに広く適用することができる。Further, it can be seen from the curve C that the rate of improvement in heat transfer is inferior to the case where the notched groove is not formed. In the above-described embodiment, an example in which the present invention is applied to a tube for a heat exchanger used in an EGR gas cooling device has been described. However, the present invention is not limited to such an embodiment. The present invention can be widely applied to tubes for heat exchangers through which the above fluid flows.
【００２９】[0029]
【発明の効果】以上述べたように、請求項１の熱交換器
用チューブでは、円筒状の管部材の内周に、螺旋部材を
嵌挿し、この螺旋部材の外周に間隔を置いて複数の切欠
溝を形成し、切欠溝の深さを、螺旋部材の直径の０．１
倍以下の値にしたので、従来より大幅に熱交換効率を向
上することができる。As described above, in the heat exchanger tube according to the first aspect, a spiral member is inserted into the inner periphery of the cylindrical tube member, and a plurality of notches are provided at intervals on the outer periphery of the spiral member. A groove is formed, and the depth of the notch groove is set to 0.1 of the diameter of the spiral member.
Since the value is twice or less, the heat exchange efficiency can be greatly improved as compared with the conventional case.
【００３０】請求項２の熱交換器用チューブでは、複数
の切欠溝の面積を合計した総切欠溝面積の値を、螺旋部
材の面積の０．５％以上で４％以下の値にしたので、切
欠溝を流れる流体の主流への影響を殆どなくした状態
で、切欠溝により管部材の内面近傍の流体の流れを充分
に乱すことができる。In the heat exchanger tube of the second aspect, the value of the total notch groove area obtained by summing the areas of the plurality of notch grooves is set to a value of 0.5% or more and 4% or less of the area of the spiral member. The flow of the fluid near the inner surface of the pipe member can be sufficiently disturbed by the notch groove while the influence of the fluid flowing through the notch groove on the main flow is almost eliminated.
【図１】図２の螺旋部材を展開して示す説明図である。FIG. 1 is an explanatory view showing a spiral member of FIG. 2 in a developed state.
【図２】本発明の熱交換器用チューブの一実施形態を示
す断面図である。FIG. 2 is a cross-sectional view showing one embodiment of the heat exchanger tube of the present invention.
【図３】図２の熱交換器用チューブの総切欠開口率と熱
伝達向上率との関係を示す説明図である。FIG. 3 is an explanatory diagram showing a relationship between a total notch opening ratio of the heat exchanger tube of FIG. 2 and a heat transfer improvement ratio.
【図４】従来のＥＧＲ装置を示す説明図である。FIG. 4 is an explanatory view showing a conventional EGR device.
【図５】従来のＥＧＲガス冷却装置を示す側面図であ
る。FIG. 5 is a side view showing a conventional EGR gas cooling device.
【図６】図５のＥＧＲガス冷却装置の要部の詳細を示す
断面図である。FIG. 6 is a sectional view showing details of a main part of the EGR gas cooling device of FIG. 5;
２１ 管部材 ２３ 螺旋部材 ２７ 切欠溝 21 pipe member 23 spiral member 27 notch groove
───────────────────────────────────────────────────── フロントページの続き (72)発明者 吉田 宏行 東京都中野区南台５丁目24番15号 カルソ ニック株式会社内 (72)発明者 小澤 達央 東京都中野区南台５丁目24番15号 カルソ ニック株式会社内 (72)発明者 木村 茂樹 神奈川県川崎市川崎区藤崎３丁目５番１号 東京ラヂエーター製造株式会社内 ──────────────────────────────────────────────────続 き Continuing on the front page (72) Inventor Hiroyuki Yoshida 5-24-15 Minamidai, Nakano-ku, Tokyo Calsonic Corporation (72) Inventor Tatsuo Ozawa 5-24-15 Minamidai, Nakano-ku, Tokyo Calso Nick Co., Ltd. (72) Inventor Shigeki Kimura 3-5-1 Fujisaki, Kawasaki-ku, Kawasaki-shi, Kanagawa Prefecture Tokyo Radiator Manufacturing Co., Ltd.
Claims (2)
部材（２３）を嵌挿し、この螺旋部材（２３）の外周に
間隔を置いて複数の切欠溝（２７）を形成するととも
に、前記切欠溝（２７）の深さ（Ｘ）を、前記螺旋部材
（２３）の直径（Ｄ）の０．１倍以下の値にしてなるこ
とを特徴とする熱交換器用チューブ。1. A spiral member (23) is inserted into the inner periphery of a cylindrical tube member (21), and a plurality of cutout grooves (27) are formed at intervals on the outer periphery of the spiral member (23). And a depth (X) of the cutout groove (27) is set to a value not more than 0.1 times a diameter (D) of the spiral member (23).
いて、 前記複数の切欠溝（２７）の面積を合計した総切欠溝面
積の値を、前記螺旋部材（２３）の面積（Ｓ）の０．５
％以上で４％以下の値にしてなることを特徴とする熱交
換器用チューブ。2. The tube for a heat exchanger according to claim 1, wherein a value of a total notch groove area obtained by summing an area of the plurality of notch grooves (27) is equal to 0 of an area (S) of the spiral member (23). .5
A heat exchanger tube characterized by having a value of not less than 4% and not more than 4%.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP10355702A JP2000180085A (en) | 1998-12-15 | 1998-12-15 | Tube for heat exchanger |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP10355702A JP2000180085A (en) | 1998-12-15 | 1998-12-15 | Tube for heat exchanger |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JP2000180085A true JP2000180085A (en) | 2000-06-30 |
Family
ID=18445335
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP10355702A Pending JP2000180085A (en) | 1998-12-15 | 1998-12-15 | Tube for heat exchanger |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2000180085A (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP3379190A4 (en) * | 2015-11-20 | 2019-09-18 | Hideyuki Haruyama | Heat exchange mixing device and solution conveying/cooling device |
| CN111457774A (en) * | 2020-04-01 | 2020-07-28 | 常州大学 | Enhanced heat transfer tube with opening and spiral insertion sheet |
| KR102266226B1 (en) * | 2019-12-23 | 2021-06-17 | (주)대주기계 | Performance improvement of a tubular heat exchanger with rectangular cut twist thin plate |
-
1998
- 1998-12-15 JP JP10355702A patent/JP2000180085A/en active Pending
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP3379190A4 (en) * | 2015-11-20 | 2019-09-18 | Hideyuki Haruyama | Heat exchange mixing device and solution conveying/cooling device |
| KR102266226B1 (en) * | 2019-12-23 | 2021-06-17 | (주)대주기계 | Performance improvement of a tubular heat exchanger with rectangular cut twist thin plate |
| CN111457774A (en) * | 2020-04-01 | 2020-07-28 | 常州大学 | Enhanced heat transfer tube with opening and spiral insertion sheet |
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