JP2004198020A - Heat storage type heat exchanger - Google Patents
Heat storage type heat exchanger Download PDFInfo
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- JP2004198020A JP2004198020A JP2002366362A JP2002366362A JP2004198020A JP 2004198020 A JP2004198020 A JP 2004198020A JP 2002366362 A JP2002366362 A JP 2002366362A JP 2002366362 A JP2002366362 A JP 2002366362A JP 2004198020 A JP2004198020 A JP 2004198020A
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- heat exchanger
- regenerative heat
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- exchanger according
- metal sheet
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- 238000005338 heat storage Methods 0.000 title claims abstract description 7
- 239000002184 metal Substances 0.000 claims abstract description 30
- 229910052751 metal Inorganic materials 0.000 claims abstract description 30
- 230000002093 peripheral effect Effects 0.000 claims abstract description 12
- 239000011148 porous material Substances 0.000 claims description 30
- 230000001172 regenerating effect Effects 0.000 claims description 25
- 239000000463 material Substances 0.000 claims description 14
- 238000010030 laminating Methods 0.000 abstract description 6
- 238000013461 design Methods 0.000 abstract description 4
- 238000005530 etching Methods 0.000 abstract description 2
- 238000005266 casting Methods 0.000 abstract 1
- 238000012545 processing Methods 0.000 description 8
- 238000000034 method Methods 0.000 description 7
- 238000012546 transfer Methods 0.000 description 5
- 238000003475 lamination Methods 0.000 description 4
- 239000011295 pitch Substances 0.000 description 4
- 239000000470 constituent Substances 0.000 description 3
- PXHVJJICTQNCMI-UHFFFAOYSA-N Nickel Chemical compound [Ni] PXHVJJICTQNCMI-UHFFFAOYSA-N 0.000 description 2
- 238000005260 corrosion Methods 0.000 description 2
- 230000007797 corrosion Effects 0.000 description 2
- 238000002788 crimping Methods 0.000 description 2
- 230000007423 decrease Effects 0.000 description 2
- 239000000835 fiber Substances 0.000 description 2
- 238000005304 joining Methods 0.000 description 2
- 238000007747 plating Methods 0.000 description 2
- 230000008929 regeneration Effects 0.000 description 2
- 238000011069 regeneration method Methods 0.000 description 2
- RYGMFSIKBFXOCR-UHFFFAOYSA-N Copper Chemical compound [Cu] RYGMFSIKBFXOCR-UHFFFAOYSA-N 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 229910052802 copper Inorganic materials 0.000 description 1
- 239000010949 copper Substances 0.000 description 1
- 230000008021 deposition Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000005323 electroforming Methods 0.000 description 1
- 230000003628 erosive effect Effects 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 238000003754 machining Methods 0.000 description 1
- 238000000465 moulding Methods 0.000 description 1
- 229910052759 nickel Inorganic materials 0.000 description 1
- 239000002245 particle Substances 0.000 description 1
- 238000011056 performance test Methods 0.000 description 1
- 238000004080 punching Methods 0.000 description 1
- 229910001220 stainless steel Inorganic materials 0.000 description 1
- 239000010935 stainless steel Substances 0.000 description 1
- 238000012360 testing method Methods 0.000 description 1
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- 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
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E60/00—Enabling technologies; Technologies with a potential or indirect contribution to GHG emissions mitigation
- Y02E60/14—Thermal energy storage
Abstract
Description
【0001】
【発明の属する技術分野】
本発明は、スターリングエンジンやスターリング冷凍機、ビィルミエサイクル機器、パルスチューブ冷凍機、熱音響機器を始めとする熱再生機構を有する機関、並びに再生式ガスタービンの蓄熱式熱交換器に関する。
【0002】
【従来の技術】
図9乃至図11は従来の蓄熱式熱交換器を概略的に示した図であって、金網、発泡金属、マット状金属繊維、スプリングメッシュによる積層形(図10参照)、細管、ハニカム、ヘリパック、ねじり線による配列形(図11参照)、綿状金属繊維、ペブル(粒子)によるパック形(図12参照)がある。積層形は比表面積が大きく、作動ガスとの間の熱伝達率も高く、かつ、流動損失もそれほど大きくなく、配列形は流動損失をかなり低減できるが、比表面積が小さく、熱伝達率も低く、パック形は比表面積が大きく流動損失の調整も可能であるが、2つの性能を両立させる事は難しく、取扱い性が悪い。したがって、性能的には積層形が優れており、スターリングエンジンおよびスターリング冷凍機の実機試験において積層金網の優位性が実証され、多くの機関に使用されている。
【0003】
【発明が解決しようとする課題】
前記のような積層金網を蓄熱式熱交換器に利用する場合に、金網を成形する際に生じる金網の歪み、端部のほつれ、低い加工精度により、積層する際の取扱い性は非常に悪く、価格が高くなる欠点があり、金網の歪み、端部のほつれ、低い加工精度により、機関性能を低下させる。また、価格を考慮すると金網は既製品を利用する事になり、線径や線のピッチ、線の素材が決まってしまう。
【0004】
それは、金網が細い金属線で織込まれているので、既製の広い金網のシートから小さな径(通常5〜9cm)にプレス加工等で打ち抜いて成型すると、金網が平にならず歪んでしまう。これをケーシングに収まるように積層(通常300〜500枚程度)する際に非常に手間がかかり、さらには金網間に隙間が生じて、無効容積が増加して圧縮比が低下して機関性能を低下させる。また、加工された端部はほつれやすく、ほつれた金属線は組み立て性を著しく低下させるばかりではなく、ほつれの部分でケーシングと積層金網の間に隙間が生じて、その隙間を作動ガスの一部が漏れ通って熱交換器を通過しない事で、機関効率を低下させる。また、プレス加工等で打ち抜き成型する場合は、細い金属線を種々の方向から切断する事になり、加工精度が悪くなって、組み立て性が悪く、かつ、ケーシングと積層金網の間に隙間が生じて、その隙間を作動ガスの一部が漏れ通って積層金網内を通過しない事で、機関効率を低下させる。また、実際に使用される金網は既製品が多く、その線径、ピッチ、素材が決まっており、機関に最適な熱伝達、摩擦損失特性を得るように最適設計値の適用や調整ができない。
【0005】
本発明は、前記従来の問題を解決するためになされたもので、その目的は、積層部材の歪み、端部のほつれを無くし、高い加工精度をもって、積層する際の取扱い性を良くし、価格を安くする事を可能とし、数値計算等による結果に基づいた最適設計にしたがって形状を決定する事で機関性能を向上させることが可能な蓄熱式熱交換器を提供する事にある。
【0006】
【課題を解決するための手段】
前記の目的を達成するために本発明は、厚さ0.1 〜0.2 mm程度の金属薄板にエッチング(腐食液による侵食作用により金属を加工する方法)あるいは電鋳方式(電極により金属をベースパターン上に析出する方法)により多数の細孔を開け、この薄板の片面あるいは両面に細孔を結ぶ溝を設け、薄板の外周部には細孔をなくして高い寸法精度を得るようにした事を特徴とする。
また、機器に合わせて径方向あるいは長手方向の作動ガスの流れや熱交換量を調節できるように、細孔の径は場所によって異なるものとし、溝の位置、形状を変える事を特徴とする。
さらに、薄板の表面の材質を熱伝導率の低いものとして、蓄熱式再生器の高温側から低温側へ熱伝導による損失を低減する事を特徴とする。
【0007】
【発明の実施の形態】
以下、発明の一実施例を図1及至図8に従い具体的に説明する。
蓄熱式熱交換器を構成する1枚の金属薄板は、図1に示すように、薄板1に細孔2を密に多く設けた構造となっている。なお、図2に示す細孔2は方形、千鳥配列(60度)になっているが、その他の円形など細孔の形、およびその他の細孔の配列(碁盤目配列)でも可能である。
細孔2の径およびピッチ等の寸法は、その蓄熱式熱交換器を適用する機器によって最適値を決めるが、3kW級スターリングエンジンの場合には穴の寸法は0.24×0.24mmから0.30×0.30mm、ピッチ0.44mm程度、板厚み0.1mm のもの500 枚程度積層したものを採用して、従来のメッシュシートを採用した構造に比較し、軸出力が約7〜15%、熱効率が約10〜20%向上(図9参照)した。
【0008】
さらに、作動ガスが流れる際の流動損失を低減する目的で、図3に示すように、細孔2と細孔2を溝3で結ぶ事も可能である。この溝3は薄板1の両側に設ける事ができる。なお、溝3の配置、数、寸法は、その熱再生式熱交換器を適用する機器によって特有の最適値を有するが、上述の3kW級スターリングエンジンの場合には図のような配置として溝幅約0.12mm、深さ約0.06mmとした。
【0009】
図4に示したように、蓄熱式熱交換器4内の流れ(スターリング機器の場合は往復流、ガスタービンの場合には一方向流あるいは対向流)がその構造上不均一の場合にはその流れを均一にする目的で、薄板5、6における細孔の大きさ及び配置は、薄板上の場所によって自由に設計、設置する事ができる。また、その細孔の大きさ及び配置が異なる薄板をそれぞれ積層することが可能である。
【0010】
また、図5に示したように、蓄熱式熱交換器4内の流れがその構造上不均一の場合にはその流れを均一にする目的で、薄板7、8における細孔を結ぶ溝の寸法、配置は薄板上の場所によって変える事ができる。また、その溝の寸法、配置が異なる薄板をそれぞれ積層することが可能である。
【0011】
また、図6に示したように薄板1の外周部9に、外周縁方向に連続して、細孔を有しない平滑面領域を設けて、薄板の加工精度を向上させ、作動ガスの漏れ損失を低減させる。一般に、金網の場合には7cmの外径に対して+・− 0.1mmの寸法公差となるが、この発明の方式ではさらに精度をあげる事ができ、+・− 0.029〜+・−0.010 mmとすることができる。なお、図7の横断面図のように外周部9の厚みを外周縁方向に連続して一段薄くすることで、積層した場合の接触による積層方向への熱伝導損失を低減している。さらに、外周部9の縁に窪み10をつける事により、積層した時の薄板の回転方向が外観からの目視により容易に判断でき、位置合わせをすることができる。
【0012】
なお、図8に示したように、薄板の表面を異なる性質を有する金属で形成して、熱伝導損失を低下したり、腐食を防ぐ事を可能とする。例えば、熱伝導率のよく、熱容量が大きい銅やニッケルなどの母材12の表面に、熱伝導率の悪く耐食性の強いステンレス等の材料からなる表面材13を複合させる事が可能である。また、薄板表面の荒さを数ミクロンから数百ミクロン程度に荒くしたり、溝のついていない面に数ミクロンから数百ミクロンの深さのスクラッチ(平行溝)加工やヘアライン(細い溝)加工を設けることで、薄板間の熱接触抵抗を増加させ、熱伝導損失を低下させることもできる。図8中のメッキ方法は母材のみで作成した薄板をメッキ処理したものである。
【0013】
また、図6に示した薄板1の中央にある穴11は積層する際に通し棒を通す穴であり、組み立て性を考慮したものである。この部分に穴をあけずに、圧着や接合用のつけしろとして使用する事ができる。また、この部分にも細孔を設けて、外周部を圧着や接合用のつけしろとして使用する事ができる。
【0014】
薄板の片面のみに細孔を結ぶ溝を設けた場合には、その溝のある面を低温の作動ガスが流れる方向(または、一方向のみ作動ガスが流れる場合にはその方向)に向ける事で、作動ガスが流れる際に発生する摩擦を低減する事が可能である。3kW級スターリングエンジンでは低温側に溝付き面を向けて積層することで、作動ガスがこの熱交換器を流れる際に発生する摩擦による損失を50W 低下する事ができた。また、積層する際に発生する熱伝導損失を低減する目的で、溝の付いた面を交互に(裏表に)組み合わせる事が可能である。
【0015】
【発明の効果】
本発明の蓄熱式熱交換器によれば、積層部材の歪み、端部のほつれを無くし、高い加工精度をもって、積層する際の取扱い性を良くし、価格を安くする事を可能とし、数値計算等の結果により得られた最適設計値にしたがって細孔、溝の形状寸法を決定する事で機関性能を向上させることが達成される。
試作した本発明の蓄熱式熱交換器においては、従来品の積層金網と比較して伝熱特性を表すヌッセルト数が約2倍になり、伝熱特性が向上することを確認した。因に、本発明の蓄熱式熱交換器を用いる事で、3kW級スターリングエンジンの場合にはその軸出力が約7〜15%、熱効率が10〜20%向上(図9参照)したことを確認している。
【図面の簡単な説明】
【図1】本発明の一実施例による蓄熱式熱交換器の金属薄板を示した概略平面図である。
【図2】同金属薄板の細孔を示した概略拡大図である。
【図3】同金属薄板の細孔と細孔を結ぶ溝を示した概略拡大図である。
【図4】同金属薄板の細孔が部分的に異なる寸法、形状をもつ薄板を示した蓄熱式熱交換器の概略図である。
【図5】同金属薄板の細孔を結ぶ溝が部分的に異なる寸法、形状をもつ薄板を示した蓄熱式熱交換器の概略図である。
【図6】本発明の他の実施例による蓄熱式熱交換器の金属薄板を示した概略平面図である。
【図7】同一部の拡大断面図である。
【図8】本発明のさらに他の実施例による蓄熱式熱交換器の金属薄板を示した横断面図である。
【図9】本発明の一実施例による蓄熱式熱交換器の性能試験のデータを示すグラフ図である。
【図10】従来の蓄熱式熱交換器の構成材料を示す要部の拡大図である。
【図11】従来の蓄熱式熱交換器の他の構成材料を示す要部の拡大図である。
【図12】従来の蓄熱式熱交換器の他の構成材料を示す要部の拡大図である。
【符号の説明】
1…薄板、2…細孔、3…薄板上の溝、4…蓄熱式熱交換器(ケース)、5…部分的に細孔の寸法、配置を変えた薄板、6…全体に細孔の寸法、配置を揃えた薄板、7…部分的に細孔を結ぶ溝の寸法、配置を変えた薄板、8…全体に細孔を結ぶ溝の寸法、配置を揃えた薄板、9…外周部、10…外周部の窪み、11…穴、12…母材、13…表面材[0001]
TECHNICAL FIELD OF THE INVENTION
The present invention relates to an engine having a heat regeneration mechanism such as a Stirling engine, a Stirling refrigerator, a Birmier cycle device, a pulse tube refrigerator, a thermoacoustic device, and a regenerative heat exchanger of a regenerative gas turbine.
[0002]
[Prior art]
9 to 11 schematically show a conventional heat storage type heat exchanger, which is a lamination type (see FIG. 10) using a wire mesh, a foamed metal, a mat-like metal fiber, a spring mesh (see FIG. 10), a thin tube, a honeycomb, and a helipack. , A twisted wire arrangement (see FIG. 11), a flocculent metal fiber, and a pebble (particle) pack (see FIG. 12). The laminated type has a large specific surface area, a high heat transfer coefficient with the working gas, and the flow loss is not so large.The array type can considerably reduce the flow loss, but has a small specific surface area and a low heat transfer coefficient. The pack type has a large specific surface area and can adjust the flow loss, but it is difficult to make the two performances compatible, and the handleability is poor. Therefore, the laminated type is excellent in performance, and the superiority of the laminated wire netting is demonstrated in the actual machine test of the Stirling engine and the Stirling refrigerator, and is used in many engines.
[0003]
[Problems to be solved by the invention]
When using such a laminated wire mesh for a regenerative heat exchanger, the strain of the wire mesh generated when forming the wire mesh, fraying of the ends, low processing accuracy, the handling at the time of lamination is very poor, It has the disadvantage of increasing the price, and reduces the engine performance due to wire mesh distortion, edge fraying, and low machining accuracy. In addition, considering the price, the wire mesh uses an off-the-shelf product, and the wire diameter, wire pitch, and wire material are determined.
[0004]
Since the wire mesh is woven with a thin metal wire, if the material is punched out from a wide sheet of a ready-made wire mesh into a small diameter (usually 5 to 9 cm) by press working or the like, the wire mesh is not flat but distorted. It takes a lot of time and effort to stack the sheets (usually about 300 to 500 sheets) so as to fit in the casing, and furthermore, a gap is formed between the wire meshes, the ineffective volume increases, the compression ratio decreases, and the engine performance decreases. Lower. In addition, the processed end is easily frayed, and the frayed metal wire not only significantly lowers the assemblability, but also creates a gap between the casing and the laminated wire mesh at the frayed part, and the gap is part of the working gas. Does not pass through the heat exchanger to reduce engine efficiency. Also, in the case of punching and molding by press working, etc., a thin metal wire is cut from various directions, processing accuracy is deteriorated, assemblability is poor, and a gap is generated between the casing and the laminated wire mesh. Thus, a part of the working gas leaks through the gap and does not pass through the laminated wire mesh, thereby lowering the engine efficiency. In addition, many wire meshes actually used are off-the-shelf products, and their wire diameters, pitches, and materials are fixed, and it is not possible to apply or adjust the optimal design values so as to obtain optimal heat transfer and friction loss characteristics for the engine.
[0005]
The present invention has been made to solve the above-mentioned conventional problems, and its object is to eliminate the distortion of the laminated member and the fray of the end, to improve the processing accuracy, to improve the handling at the time of laminating, and to reduce the cost. It is an object of the present invention to provide a regenerative heat exchanger capable of improving engine performance by determining the shape according to an optimal design based on the results of numerical calculations and the like.
[0006]
[Means for Solving the Problems]
In order to achieve the above object, the present invention provides a method of etching a metal thin plate having a thickness of about 0.1 to 0.2 mm (a method of processing a metal by erosion by a corrosive liquid) or an electroforming method (the metal is formed on a base pattern by an electrode). A large number of pores are opened by the method of deposition), grooves are formed on one or both sides of this thin plate to connect the pores, and the outer peripheral portion of the thin plate has no pores to obtain high dimensional accuracy. I do.
In addition, the diameter of the pores is varied depending on the location and the position and shape of the groove are changed so that the flow of the working gas and the heat exchange amount in the radial direction or the longitudinal direction can be adjusted according to the equipment.
Further, the material of the surface of the thin plate has a low thermal conductivity to reduce the loss due to heat conduction from the high-temperature side to the low-temperature side of the regenerator.
[0007]
BEST MODE FOR CARRYING OUT THE INVENTION
Hereinafter, an embodiment of the present invention will be specifically described with reference to FIGS.
As shown in FIG. 1, one metal thin plate constituting the heat storage type heat exchanger has a structure in which a large number of
The optimum values for the diameter and pitch of the
[0008]
Further, in order to reduce the flow loss when the working gas flows, as shown in FIG. The
[0009]
As shown in FIG. 4, when the flow in the regenerative heat exchanger 4 (reciprocating flow in the case of a Stirling device, unidirectional flow or counterflow in the case of a gas turbine) is not uniform due to its structure, In order to make the flow uniform, the size and arrangement of the pores in the
[0010]
As shown in FIG. 5, when the flow in the
[0011]
Further, as shown in FIG. 6, a smooth surface area having no pores is continuously provided in the outer peripheral portion 9 of the thin plate 1 in the outer peripheral direction, thereby improving the processing accuracy of the thin plate, and reducing the leakage loss of the working gas. Is reduced. Generally, in the case of a wire mesh, a dimensional tolerance of +0.1 mm is given for an outer diameter of 7 cm. However, with the method of the present invention, the accuracy can be further improved. can do. In addition, as shown in the cross-sectional view of FIG. 7, the thickness of the outer peripheral portion 9 is reduced one step continuously in the outer peripheral edge direction, so that heat conduction loss in the laminating direction due to contact in the case of lamination is reduced. Further, by providing the
[0012]
As shown in FIG. 8, the surface of the thin plate is formed of a metal having different properties, thereby making it possible to reduce heat conduction loss and prevent corrosion. For example, it is possible to combine a
[0013]
The hole 11 in the center of the thin plate 1 shown in FIG. 6 is a hole through which a through rod is passed when laminating, and is designed for ease of assembly. Without making a hole in this part, it can be used as a margin for crimping or joining. Also, by providing a pore in this portion, the outer peripheral portion can be used as a margin for crimping or joining.
[0014]
When a groove connecting the pores is provided only on one side of the thin plate, the surface with the groove is oriented in the direction in which the low-temperature working gas flows (or in the case where the working gas flows in only one direction, the direction). In addition, it is possible to reduce friction generated when the working gas flows. By stacking the 3kW class Stirling engine with the grooved surface facing the low temperature side, the loss due to friction generated when the working gas flows through this heat exchanger could be reduced by 50W. Also, for the purpose of reducing the heat conduction loss that occurs at the time of lamination, it is possible to alternately combine the surfaces with grooves (front and back).
[0015]
【The invention's effect】
ADVANTAGE OF THE INVENTION According to the regenerative heat exchanger of the present invention, it is possible to eliminate the distortion of the laminated member and the fraying of the end portion, to achieve high processing accuracy, to improve the handling at the time of laminating, to reduce the price, and to perform numerical calculation. The engine performance can be improved by determining the shapes and dimensions of the pores and grooves according to the optimum design values obtained from the results of the above.
It was confirmed that the prototype heat storage heat exchanger of the present invention had about twice the Nusselt number representing the heat transfer characteristics as compared with the conventional laminated wire mesh, and improved the heat transfer characteristics. By using the regenerative heat exchanger of the present invention, it was confirmed that the shaft output of the 3 kW class Stirling engine was improved by about 7 to 15% and the thermal efficiency was improved by 10 to 20% (see FIG. 9). are doing.
[Brief description of the drawings]
FIG. 1 is a schematic plan view showing a thin metal plate of a regenerative heat exchanger according to one embodiment of the present invention.
FIG. 2 is a schematic enlarged view showing pores of the metal thin plate.
FIG. 3 is a schematic enlarged view showing pores of the thin metal plate and grooves connecting the pores.
FIG. 4 is a schematic diagram of a regenerative heat exchanger showing a thin metal plate having pores partially different in size and shape.
FIG. 5 is a schematic view of a heat storage type heat exchanger showing a thin plate in which grooves connecting pores of the thin metal plate have partially different sizes and shapes.
FIG. 6 is a schematic plan view showing a thin metal plate of a regenerative heat exchanger according to another embodiment of the present invention.
FIG. 7 is an enlarged sectional view of the same part.
FIG. 8 is a cross-sectional view showing a thin metal plate of a regenerative heat exchanger according to still another embodiment of the present invention.
FIG. 9 is a graph showing data of a performance test of the regenerative heat exchanger according to one embodiment of the present invention.
FIG. 10 is an enlarged view of a main part showing constituent materials of a conventional regenerative heat exchanger.
FIG. 11 is an enlarged view of a main part showing another constituent material of the conventional regenerative heat exchanger.
FIG. 12 is an enlarged view of a main part showing another constituent material of a conventional regenerative heat exchanger.
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 1 ... thin plate, 2 ... pore, 3 ... groove on thin plate, 4 ... regenerative heat exchanger (case), 5 ... thin plate with partially changed pore size and arrangement, 6 ... whole pore A thin plate with the same dimensions and arrangement, 7 ... a thin plate with a partially changed pore size and arrangement, a thin plate with a different arrangement, 8 ... a thin plate with a uniform pore size and arrangement with the pores, 9 ... an outer peripheral portion, 10: depression at outer periphery, 11: hole, 12: base material, 13: surface material
Claims (8)
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JP2002366362A JP3677551B2 (en) | 2002-12-18 | 2002-12-18 | Regenerative heat exchanger |
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JP2002366362A JP3677551B2 (en) | 2002-12-18 | 2002-12-18 | Regenerative heat exchanger |
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Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2006073005A1 (en) * | 2005-01-07 | 2006-07-13 | The Doshisha | Heat exchanger and thermoacoustic device using the same |
JP2011149600A (en) * | 2010-01-20 | 2011-08-04 | Sumitomo Heavy Ind Ltd | Pulse tube refrigerator |
JP2012202586A (en) * | 2011-03-24 | 2012-10-22 | Nippon Telegr & Teleph Corp <Ntt> | Stack for thermoacoustic device and manufacturing method of stack for thermoacoustic device |
JP2015021671A (en) * | 2013-07-19 | 2015-02-02 | いすゞ自動車株式会社 | Accumulator and accumulator manufacturing method |
EP2543860A3 (en) * | 2011-07-04 | 2015-07-01 | GPI Gesellschaft Für Prüfstanduntersuchungen und Ingenieurdienstleistungen MbH | Thermal engine |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
TWI718795B (en) * | 2019-12-04 | 2021-02-11 | 淡江大學 | Regenerator |
-
2002
- 2002-12-18 JP JP2002366362A patent/JP3677551B2/en not_active Expired - Lifetime
Cited By (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2006073005A1 (en) * | 2005-01-07 | 2006-07-13 | The Doshisha | Heat exchanger and thermoacoustic device using the same |
US8931286B2 (en) | 2005-01-07 | 2015-01-13 | The Doshisha | Heat exchanger and thermoacoustic device using the same |
JP2011149600A (en) * | 2010-01-20 | 2011-08-04 | Sumitomo Heavy Ind Ltd | Pulse tube refrigerator |
JP2012202586A (en) * | 2011-03-24 | 2012-10-22 | Nippon Telegr & Teleph Corp <Ntt> | Stack for thermoacoustic device and manufacturing method of stack for thermoacoustic device |
EP2543860A3 (en) * | 2011-07-04 | 2015-07-01 | GPI Gesellschaft Für Prüfstanduntersuchungen und Ingenieurdienstleistungen MbH | Thermal engine |
JP2015021671A (en) * | 2013-07-19 | 2015-02-02 | いすゞ自動車株式会社 | Accumulator and accumulator manufacturing method |
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